The input object AirLoopHVAC:UnitarySystem
provide a “virtual” component that collect and control a set
of components: fan, heating coil, cooling coil, and/or reheat
coil. Reheat coil is modeled for controlling high zone
humidity levels. The unit may be configured to have either a
blow through or draw through fan. In a blow through
configuration, fan is generally the fist component upstream of
heating ro cooling coil. In a draw through fan configuration,
fan is placed directly after the heating coil and before
reheat coil.
Schematic of the EnergyPlus
Unitary System (Blow Through Configuration)
As described previously, the unitary system is a “virtual”
component consisting of a fan, heating coil, cooling coil and
reheat coil. The sole purpose of the unitary system model is
to properly coordinate the operation of the various system
components. The following sections describe the flow of
information within the model, as well as the differences
between cycling and continuous supply air fan operation.
There are two types of control types allowed to be
specified in the unitary system which are setpoint based and
load based. Each control type is described in detail
below.
Setpoint based control:
The unitary system calculates the current sensible load
using the temperature of the inlet node and the System Node
Setpoint Temp on the control node. If the control node is not
the outlet node, the desired outlet node temperature is
adjusted for the current temperature difference between the
outlet node and the control node. Likewise, the current latent
load is calculated using the humidity ratio of the inlet node
and the System Node Humidity Ratio Max on the control node.
The controls determine the required coil run-time fraction and
dehumidification mode (if applicable) using the steps outlined
below.
The controls first attempt to meet the sensible
requirement. The specified coil model is called with a
part-load ratio (PLR) of 1.0 to determine the full-load output
of the coil. This is compared with the desired outlet node
temperature and a sensible PLR is calculated. If the PLR is
<1.0, a Regula-Falsi iteration routine is called to
determine the coil run-time fraction which results in the
desired outlet node temperature. For a variable-speed DX
cooling coil, if the load is smaller than the sensible
capacity at the lowest speed, the coil run-time fraction is
determined in the same way as a single-speed DX cooling coil.
Otherwise, its speed number and speed ratio between two
neighboring speeds are selected to match the load.
If dehumidification controls are active, the leaving
humidity ratio resulting from operation to meet the sensible
load (Step 1 above) is compared with the desired outlet node
humidity ratio. If the humidity requirement is already met,
then no further control action is taken. If the humidity
requirement has not been met, then the coil is re-simulated
depending on the type of humidity control.
If the humidity control type is MultiMode, then the coil’s
enhanced dehumidification mode is activated when the coil type
is Coil:Cooling:DX:TwoStageWithHumidityControlMode
and Step 1 above is repeated to meet the sensible load using
the coil performance resulting from the enhanced
dehumidificaiton mode. This is a semi-passive approach to
dehumidification which may fall short or may exceed the
dehumidification requirement.
If the humidity control type is CoolReheat, the coil is
re-simulated to achieve the desired outlet node humidity
ratio. This option is valid for all cooling coil types. When
the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode,
only the cooling performance mode is used for this step and
enhanced dehumidification mode is not activated.
Load based control:
While the unitary system may be configured to serve
multiple zones, system operation is controlled by a thermostat
located in a single “control” zone. One of the key parameters
for the unitary system component is the fraction of the total
system air flow that goes through the control zone. This
fraction is calculated as the ratio of the maximum air mass
flow rate for the air loop’s supply inlet node for the control
zone (e.g., AirTerminal:SingleDuct:Uncontrolled,
field = Maximum Air Flow Rate, converted to mass flow) to the
sum of the maximum air mass flow rates for the air loop’s
supply inlet nodes for all zones served by this air loop. The
unitary system module scales the calculated load for the
control zone upward based on this fraction to determine the
total load to be met by the unitary system. The module then
proceeds to calculate the required part-load ratio for the
system coil and the supply air fan to meet this total load.
The heating or cooling capacity delivered by the unitary
system is distributed to all of the zones served by this
system via the terminal units that supply air to each zone.
The supply air fraction that goes though the control zone is
calculated as follows:
\[Control Zone Air
Flow\,Fraction = \frac{{{{\dot
m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones}
{{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot
m_{TUMax\,ControlledZone}}\) =maximum air mass flow
rate for the air loop’s supply inlet node (terminal unit) for
the control zone (kg/s)
\({\dot
m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for
the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of
zones, or number of air loop supply air inlet nodes for all
zones served by the air loop (-)
The unitary system component is able to model supply air
fan operation in two modes: cycling fan - cycling coil (i.e.,
AUTO fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff
must be used to model AUTO fan, while Fan:OnOff
or Fan:ConstantVolume
can be used to model fan ON. The fan operation mode is
specified using a supply air fan operating mode schedule where
schedule values of 0 denote cycling fan operation and schedule
values other than 0 (a 1 is usually used) denote continuous
fan operation. Using this schedule, the unitary system fan may
be cycled with cooling or heating coil operation or operated
continuously based on time of day (e.g., cycling fan operation
at night and continuous fan operation during the daytime). If
the fan operating mode schedule name field is left blank in
the unitary system object, the unitary system assumes cycling
or AUTO fan mode operation throughout the simulation.
The unitary system operates based on the user-specified (or
autosized) design supply air flow rate(s). The ‘design’ supply
air mass flow rate may be different for cooling, heating, and
when no cooling or heating is required and the fan operates
continuously based on user-specified inputs.
Cooling Operation
If EnergyPlus determines that the unitary system must
supply cooling to the control zone to meet the zone air
temperature setpoint, then the model computes the total
sensible cooling load to be met by the unitary system based on
the control zone sensible cooling load and the fraction of the
unitary system air flow that goes through the control
zone.
If the supply air fan operating mode schedule requests
cycling fan operation, the model first checks for the presence
of an ecomomizer in the outside air system serving the unitary
system’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an
outside air system is not present or if an air-side economizer
is not used, the unitary system’s compressor is used to meet
the unitary system cooling load. If an air-side economizer is
used and is active (i.e., economizer controls indicate that
conditions are favorable to increase the outside air flow
rate), the unitary system will try to meet the cooling load by
operating only the supply air fan. If the fan is able to
satisfy the unitary system cooling load, the compressor
remains off for the entire simulation time step. If the
operation of the fan alone is unable to meet the entire
cooling load, then the compressor is enabled and additional
calculations are performed to determine the compressor’s
part-load ratio.
The model then calculates the unitary system’s sensible
cooling energy rate delivered to the zones being served when
the system runs at full-load conditions and when the cooling
coil is OFF. If the supply air fan cycles with the compressor,
then the sensible cooling energy rate is zero when the cooling
coil is OFF. However if the fan is configured to run
continuously regardless of coil operation, then the sensible
cooling energy rate will probably not be zero when the cooling
coil is OFF. Calculating the sensible cooling energy rate
involves modeling the supply air fan (and associated fan
heat), the cooling coil, and the heating and reheat coil
(simply to pass the air properties and mass flow rate from its
inlet node to its outlet node). For each of these cases (full
load and cooling coil OFF), the sensible cooling energy rate
delivered by the unitary system is calculated as follows:
With the calculated sensible cooling energy rates and the
total sensible cooling load to be met by the system, the
part-load ratio for the unitary system is estimated.
Since the part-load performance of the cooling coil is
frequently non-linear, and the supply air fan heat varies
based on cooling coil operation for the case of cycling
fan/cycling coil (AUTO fan), the final part-load ratio for the
cooling coil compressor and fan are determined through
iterative calculations (successive modeling of the cooling
coil and fan) until the unitary system’s cooling output
matches the cooling load to be met within the convergence
tolerance. The convergence tolerance is fixed at 0.001 and is
calculated based on the difference between the load to be met
and the unitary system’s cooling output divided by the load to
be met.
\({Q_{UnitarySystem}}\) =
Unitary system delivered sensible capacity (W)
If the unitary system has been specified with cycling
fan/cycling coil (AUTO fan), then the unitary system’s
operating supply air mass flow rate is multiplied by
PartLoadRatio to determine the average air mass flow rate for
the system simulation time step. In this case, the air
conditions at nodes downstream of the cooling coil represent
the full-load (steady-state) values when the coil is
operating.
If the fan operates continuously (i.e., when the supply air
fan operating mode schedule values are NOT equal to 0), the
operating air mass flow rate through the unitary system is
calculated as the average of the user-specified air flow rate
when the cooling coil is ON and the user-specified air flow
rate when the cooling coil is OFF (user-specified supply air
volumetric flow rates converted to dry air mass flow
rates).
\(\mathop m\limits^
\bullet CoolCoilON\) = air mass flow rate through
unitary system when the cooling coil is ON (kg/s)
\(\mathop m\limits^
\bullet CoilOFF\) = air mass flow rate through unitary
system when no cooling or heating is needed (kg/s)
In this case, the air conditions at nodes downstream of the
cooling coil are calculated as the average conditions over the
simulation time step (i.e., the weighted average of full-load
conditions when the coil is operating and inlet air conditions
when the coil is OFF).
Cooling Operation (multi or variable speed
coils)
After the unitary system cooling load is determined as
described in Eq. above, the multi or variable speed cooling
coil models calculations are described in this section.
The model calculates the unitary system’s sensible cooling
energy rate delivered to the zones being served when the
system runs at full-load conditions at the highest speed and
when the DX cooling coil is OFF. If the supply air fan cycles
with the compressor, then the sensible cooling energy rate is
zero when the cooling coil is OFF. However if the fan is
scheduled to run continuously regardless of coil operation,
then the sensible cooling energy rate will not be zero when
the cooling coil is OFF. Calculating the sensible cooling
energy rate involves modeling the supply air fan (and
associated fan heat) and the multi/variable speed DX cooling
coil. The multi/variable speed DX heating coil and the
supplemental heating coil are also modeled, but only to pass
the air properties and mass flow rate from their inlet nodes
to their outlet nodes. For each of these cases (full load at
highest cooling speed and DX cooling coil OFF), the sensible
cooling energy rate delivered by the unitary system is
calculated as follows:
If the unitary system’s sensible cooling rate at the
highest speed (full load, no cycling) is insufficient to meet
the entire cooling load, the controlled zone conditions will
not be met. The reported cycling rate and speed ratio are 1,
and the speed number is set to the highest index number. If
the total sensible cooling load to be met by the system is
less than the sensible cooling rate at the highest speed, then
the following steps are performed.
Calculate the sensible cooling energy rate at Speed 1
If the sensible cooling energy rate delivered by the
unitary system at Speed 1 is greater or equal to the sensible
load, the cycling ratio (part-load ratio) for the unitary
system is estimated.
AddedFanHeat = generated supply air fan heat, which is a
function of part load ratio and as internal component cooling
load [W].
AddedFanHeatSpeed1 = generated supply air fan
heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX cooling coil is
frequently non-linear,and the supply air fan heat varies based
on cooling coil operation for the case of cycling fan/cycling
coil (AUTO fan), the final part-load ratio for the cooling
coil compressor and fan are determined through iterative
calculations (successive modeling of the cooling coil and fan)
until the unitary system’s cooling output matches the cooling
load to be met within the convergence tolerance. The
convergence tolerance is fixed at 0.001 and is calculated
based on the difference between the load to be met and the
unitary system’s cooling output divided by the load to be
met.
\({\dot
m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply
inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the
required cooling load, the speed ratio is set to zero and
speed number is equal to 1.
If the unitary system’s cooling output at full load for
Speed 1 is insufficient to meet the entire cooling load, the
Cycling ratio is set equal to 1.0 (compressor and fan are not
cycling). Then the cooling speed is increased and the
delivered sensible capacity is calculated. If the full load
sensible capacity at Speed n is greater than or equal to the
sensible load, the speed ratio for the unitary system is
estimated:
Although a linear relationship is assumed by applying the
speed ratio to obtain the effective capacity and mass flow
rate between speed n and n-1, the outlet air node conditions
are dependent on the combined outputs and may not be linear.
In addition, the supply air fan heat varies with the speed
ratio due to different supply mass flow rates between speed n
and n-1 . Therefore, the final speed ratio for the cooling
coil compressor and fan are determined through iterative
calculations (successive modeling of the cooling coil and fan)
until the unitary system’s cooling output matches the cooling
load to be met within the convergence tolerance. The
convergence tolerance is fixed at 0.001 and is calculated
based on the difference between the load to be met and the
unitary system’s cooling output divided by the load to be
met.
If the unitary system has been specified with cycling
fan/cycling coil (AUTO fan), then the unitary system’s
operating supply air mass flow rate is determined by the
cycling ratio (PartLoadRatio) for Speed 1. The supply air mass
flow rate is multiplied by the cycling ratio to determine the
average air mass flow rate for the system simulation time
step. The air conditions at nodes downstream of the cooling
coils represent the full-load (steady-state) values when the
coil is operating.
If the fan operates continuously (i.e., when the supply air
fan operating mode schedule values are NOT equal to 0), the
operating air mass flow rate through the unitary system is
calculated as the average of the user-specified air flow rate
when the unitary system cooling coil is ON at Speed 1 and the
user-specified air flow rate when the unitary system cooling
coil is OFF (user-specified supply air volumetric flow rates
converted to dry air mass flow rates).
\({\mathop m\limits^
\bullet _{UnitarySystem}}\) = average air mass flow
rate through unitary system [kg/s]
\({\dot m_{Speed1}}\) =
air mass flow rate through unitary system when cooling coil is
ON at Speed 1 [kg/s]
\({\dot m_{CoilOff}}\) =
air mass flow rate through unitary system when no heating or
cooling is needed [kg/s]
In this case, the air conditions at nodes downstream of the
cooling coils are calculated as the average conditions over
the simulation time step (i.e., the weighted average of
full-load conditions when the coil is operating and inlet air
conditions when the coil is OFF).
When the unitary system operates at higher speeds to meet
the required cooling load, the supply air mass flow rate is
linearly interpolated between two consecutive speeds:
\({\mathop m\limits^
\bullet _{UnitarySystem}}\) = average air mass flow
rate through the unitary system for the time step [kg/s]
\({\dot m_{Speed\;n}}\) =
air mass flow rate through unitary system when cooling coil is
ON at Speed n [kg/s]
\({\dot m_{Speed\;n -
1}}\) = air mass flow rate through unitary system when
cooling coil is ON at Speed n-1 [kg/s]
For this case of higher speed operation, the air conditions
at nodes downstream of the cooling coils are determined by the
delivered cooling capacity and supply air mass flow rates
between two consecutive speeds.
Although the above sections present the capacity and air
mass flow rate calculation separately, they are dependent and
change every iteration until convergence is reached for the
time step being simulated.
Heating Operation
Calculations for heating operation are similar to those for
cooling operation in most respects. However, due to the
inclusion of a supplemental heating coil, additional
calculations are necessary to properly meet the total heating
load for the zones being served.
If EnergyPlus determines that the unitary system must
supply heating to the control zone to meet the zone air
temperature setpoint, then the unitary system model computes
the total sensible heating load to be delivered to the zones
being served based on the control zone sensible heating load
and the control zone airflow fraction.
The model then calculates the unitary system’s sensible
heating energy rate delivered to the zones being served when
the system runs at full-load conditions and when the heating
coil is OFF (without supplemental heater operation in either
case). If the supply air fan cycles with the compressor, then
the sensible heating energy rate is zero when the compressor
is OFF. However if the fan is scheduled to run continuously
regardless of coil operation, then the sensible heating energy
rate will not be zero when the compressor is OFF. Calculating
the sensible heating energy rate involves modeling the supply
air fan (and associated fan heat), the cooling coil (simply to
pass the air properties and mass flow rate from its inlet node
to its outlet node), the heating coil, and the supplemental
heating coil (simply to pass the air properties and mass flow
rate from its inlet node to its outlet node). For each of
these cases (full load and heating coil OFF, without
supplemental heater operation in either case), the sensible
heating energy rate delivered by the unitary system is
calculated as follows:
\(\rm{Mass Flow Rate}_{\rm{full
load}}\) = air mass flow rate through unitary system at
full-load conditions, kg/s
\(h_{out, full load}\) =
enthalpy of air exiting the unitary system at full-load
conditions, J/kg
\(h_{control zone}\) =
enthalpy of air leaving the control zone (where thermostat is
located), J/kg
HRmin = enthalpies evaluated at a
constant humidity ratio, the minimum humidity ratio of the
unitary system exiting air or the air leaving the control
zone
\(\rm{Mass Flow Rate}_{coil
off}\) = air mass flow rate through the unitary system
with the heating coil OFF, kg/s
\(h_{out, coil off}\) =
enthalpy of air exiting the unitary system with the heating
coil OFF, J/kg
\(\Delta_{sen, full
load}\) = Sensible load difference between the system
output node and the zone inlet node at full-load
conditions
With the calculated sensible heating energy rates and the
total sensible heating load to be met by the system, the
part-load ratio for the unitary system is estimated.
Since the part-load performance of the heating coil is
frequently non-linear, and the supply air fan heat varies
based on heating coil operation for the case of cycling
fan/cycling coil (AUTO fan), the final part-load ratio for the
heating coil compressor and fan are determined through
iterative calculations (successive modeling of the heating
coil and fan) until the unitary system’s heating output
matches the heating load to be met within the convergence
tolerance. The convergence tolerance is fixed at 0.001 and is
calculated based on the difference between the load to be met
and the unitary system’s heating output divided by the load to
be met.
\({Q_{UnitarySystem}}\) =
Unitary system delivered sensible capacity (W)
If the unitary system’s heating coil output at full load is
insufficient to meet the entire heating load, PartLoadRatio is
set equal to 1.0 (compressor and fan are not cycling) and the
remaining heating load is passed to the supplemental heating
coil. If the unitary system model determines that the outdoor
air temperature is below the minimum outdoor air temperature
for compressor operation, the compressor is turned off and the
entire heating load is passed to the supplemental gas or
electric heating coil. The unitary system exiting air
conditions and energy consumption are calculated and reported
by the individual component models (fan, heating coil, and
supplemental gas or electric heating coil).
If the unitary system has been specified with cycling
fan/cycling coil (AUTO fan), then the unitary system’s
operating supply air mass flow rate is multiplied by
PartLoadRatio to determine the average air mass flow rate for
the system simulation time step. The air conditions at nodes
downstream of the heating coils represent the full-load
(steady-state) values when the coils are operating. If the fan
operates continuously (i.e., when the supply air fan operating
mode schedule values are NOT equal to 0), the operating air
mass flow rate through the unitary system is calculated as the
average of the user-specified air flow rate when the unitary
system heating coil is ON and the user-specified air flow rate
when the unitary system heating coil is OFF (user-specified
supply air volumetric flow rates converted to dry air mass
flow rates).
\(\mathop m\limits^
\bullet HeatCoilON\) = air mass flow rate through
unitary system when the heating coil is ON (kg/s)
\(\mathop m\limits^
\bullet CoilOFF\) = air mass flow rate through unitary
system when no heating or cooling is needed (kg/s)
In this case, the air conditions at nodes downstream of the
heating coils are calculated as the average conditions over
the simulation time step (i.e., the weighted average of
full-load conditions when the coils are operating and inlet
air conditions when the coils are OFF).
Heating
Operation (multi or variable speed coils )[LINK]
After the unitary system heating load is determined as
described in Eq. above, the multi or variable speed heating
coil models calculation are described in this section.
The model calculates the unitary system’s sensible heating
energy rate delivered to the zones being served when the
system runs at full-load conditions at the highest speed and
when the DX heating coil is OFF (without supplemental heater
operation in either case). If the supply air fan cycles with
the compressor, then the sensible heating energy rate is zero
when the compressor is OFF. However if the fan is scheduled to
run continuously regardless of coil operation, then the
sensible heating energy rate will not be zero when the
compressor is OFF. Calculating the sensible heating energy
rate involves modeling the supply air fan (and associated fan
heat), the DX cooling coil (simply to pass the air properties
and mass flow rate from its inlet node to its outlet node),
the DX heating coil, and the supplemental heating coil (simply
to pass the air properties and mass flow rate from its inlet
node to its outlet node). For each of these cases (full load
and DX heating coil OFF, without supplemental heater operation
in either case), the sensible heating energy rate delivered by
the unitary system is calculated as follows:
\({\dot
m_{HighestSpeed}}\) = air mass flow rate through
unitary system at the highest heating speed [kg/s]
\(h_{out, full load}\) =
enthalpy of air exiting the unitary system at full-load
conditions [J/kg]
\(h_{control zone}\) =
enthalpy of air leaving the control zone (where thermostat is
located) [J/kg]
HRmin = enthalpies evaluated at a
constant humidity ratio, the minimum humidity ratio of the
unitary system exiting air or the air leaving the control
zone
\({\dot m_{CoilOff}}\) =
air mass flow rate through the unitary system with the heating
coil OFF [kg/s]
\(h_{out,coil off}\) =
enthalpy of air exiting the unitary system with the heating
coil OFF [J/kg]
\(\Delta_{sen, full
load}\) = Sensible load difference between the system
output node and the zone inlet node at full-load
conditions
If the unitary system’s DX heating coil output full load at
the highest speed is insufficient to meet the entire heating
load, the remaining heating load is passed to the supplemental
heating coil. If the unitary system model determines that the
outdoor air temperature is below the minimum outdoor air
temperature for compressor operation (specified by the user),
the compressor is turned off and the entire heating load is
passed to the supplemental gas or electric heating coil. The
unitary system exiting air conditions and energy consumption
are calculated and reported by the individual component models
(fan, DX heating coil, and supplemental gas or electric
heating coil).
If the total heating load to be met by the system is less
than the sensible heating rate at the highest speed, then the
following steps are performed.
Calculate the sensible heating energy rate at Speed 1
If the sensible heating energy rate delivered by the
unitary system at Speed 1 is greater or equal to the sensible
load, the cycling ratio (part-load ratio) for the unitary
system is estimated.
AddedFanHeat= generated supply air fan heat, which is a
function of part load ratio and as internal component heating
load [W].
AddedFanHeatSpeed1= generated supply air fan
heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX heating coil is
frequently non-linear, and the supply air fan heat varies
based on heating coil operation for the case of cycling
fan/cycling coil (AUTO fan), the final part-load ratio for the
heating coil compressor and fan are determined through
iterative calculations (successive modeling of the heating
coil and fan) until the unitary system’s heating output
matches the heating load to be met within the convergence
tolerance. The convergence tolerance is fixed at 0.001 and is
calculated based on the difference between the load to be met
and the unitary system’s heating output divided by the load to
be met.
\({\dot
m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply
inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the
required heating load, the speed ratio is set to zero and
speed number is equal to 1.
If the unitary system’s heating output at full load for
Speed 1 is insufficient to meet the entire heatling load, the
Cycling ratio (PartLoadRatio) is set equal to 1.0 (compressor
and fan are not cycling). Then the heating speed is increased
and the delivered sensible capacity is calculated. If the full
load sensible capacity at Speed n is greater than or equal to
the sensible load, the speed ratio for the unitary system is
estimated:
Although a linear relationship is assumed by applying the
speed ratio to obtain the effective capacity and air mass flow
rate between speed n and n-1, the outlet node conditions are
dependent on the combined outputs and may not be linear. In
addition, the supply air fan heat varies based on heating coil
operation for the case of cycling fan/cycling coil (AUTO fan).
Therefore, the final speed ratio for the heating coil
compressor and fan are determined through iterative
calculations (successive modeling of the heating coil and fan)
until the unitary system’s heating output matches the heating
load to be met within the convergence tolerance. The
convergence tolerance is fixed at 0.001 and is calculated
based on the difference between the load to be met and the
unitary system’s heating output divided by the load to be
met.
The specific configuration of the unitary system with
supplemental heating coil is shown above (see Figure 227).
This figure shows the fan placement when a blow through fan is
specified. If a draw through fan is specified, the fan is
located between the heating coil and the supplemental heating
coil. The system is controlled to keep the high relative
humidity in the control zone from exceeding the setpoint
specified in the object ZoneControl:Humidistat.
This option is available when the supply air fan operates
continuously (i.e., the supply air fan operating mode schedule
values are never equal to 0) or the supply air fan cycles with
the compressor. In addition, when high humidity control is
specified and the compressor operates, the unitary system
operates at the cooling air flow rate when a zone heating load
is present as determined by the zone thermostat. High humidity
control is specified as either None, MultiMode, or CoolReheat
in the Dehumidification Control Type input field. MultiMode is
specified when a heat exchanger is used to improve the
dehumidification performance of the cooling coil. The heat
exchanger will be activated when the sensible part-load ratio
is insufficient to meet the zone latent load. CoolReheat is
specified when a cooling coil is used to over-cool the supply
air stream in order to meet the zone latent load. In this
case, a supplemental heating coil will ensure the zone
temperature does not fall below the zone heating temperature
set point. When a heat exchanger is used in conjunction with a
cooling coil and CoolReheat is specified as the
Dehumidification Control Type, the heat exchanger is “locked
on” to meet either the sensible or latent cooling load. If the
dehumidification control type is selected as None and a heat
exchanger assisted cooling coil is used, the heat exchanger is
“locked on” and the air conditioner runs only to meet the
sensible cooling load. A supplemental heating coil is required
for all dehumidification control types.
The model first calculates the PartLoadRatio
required to meet the sensible cooling load. The unitary
system’s sensible cooling load is determined from the control
zone sensible cooling load to the cooling setpoint and the
control zone air flow fraction to maintain the dry-bulb
temperature setpoint in the control zone.:
The unitary system’s sensible cooling load to be met and
the full load cooling output are used to calculate the
sensible the part-load ratio iteratively based on user
specified convergence criterion.
hen the unitary system’s sensible cooling capacity meets
the system sensible cooling load at a given sensible part load
ratio, then the Unitary system meets the controlled zone
cooling setpoint temperature. If a moisture (latent) load
exists because the control zone humidity has exceeded the
setpoint, the total moisture load to be met by the unitary
systems (Unitary systemMoistureLoad) is calculated based on
the control zone moisture load and the control zone air flow
fraction.
Then the LatentPartLoadRatio required to meet the
high humidity setpoint is calculated as follows:
\(LatentPartLoadRatio = MIN\left(
{PL{R_{Min}},\frac{{\left( {UnitarySystemMoistureLoad -
NoLatentOutput} \right)}}{{\left( {FullLatentOutput -
NoLatentOutput} \right)}}} \right)\) The model uses the
greater of the two part-load ratios, PartLoadRatio or
LatentPartLoadRatio, to determine the operating
part-load ratio of the Unitary system’s DX cooling coil.
As previously described, iterations are performed to
converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\)
= the control zone sensible cooling load to the cooling
setpoint, (W).
\(ControlZoneMoistureLoad\) = the
control zone moisture load to the dehumidifying relative
humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) =
the supply air fraction that goes though the control zone,
(-).
\(FullLatentOutput\) = the
Unitary system’s latent cooling energy rate at full-load
conditions, W
\(NoLatentOutput\) = the
Unitary system’s latent cooling energy rate with cooling coil
OFF, W
\(PartLoadRatio\) = the
unitary system’s part-load-ratio required to meet system
sensible load, (-).
\(LatentPartLoadRatio\) =
the unitary system’s part-load-ratio required to meet system
moisture load, (-).
\(PL{R_{Min}}\) = the
minimum part-load ratio, which is usually 0.0. For the case
when the latent capacity degradation model is used (Ref: DX
Cooling Coil Model), this value is the minimum part-load ratio
at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the
heating setpoint and if there is a dehumidification load, the
supplemental heating coil load is required to offset the
excess cooling as shown in Figure 228. If the model determines
that the LatentPartLoadRatio is to be used as the operating
part-load ratio of the unitary system’s cooling coil, the
supplemental heating coil is used to offset the excess
sensible capacity provided by the unitary system cooling coil.
The model first checks the sensible load that exists for the
current simulation time step (predicted zone temperature with
no HVAC operation compared to the thermostat setpoint
temperatures). If a sensible cooling load or no sensible
cooling or heating load exists, the model calculates the
difference between the sensible heating load required to reach
or maintain the heating dry-bulb temperature setpoint and the
actual sensible cooling energy rate delivered by the unit
(with LatentPartLoadRatio). In this case, the supplemental
heating coil is used to offset the excess sensible cooling
energy provided by the cooling coil (if any) that could have
caused an overshoot of the heating dry-bulb temperature
setpoint. Note that when a humidistat is used and high
humidity control is required, the zone dry-bulb temperature
will typically move toward the heating temperature setpoint
when a high moisture (latent) load exists.
Supplemental heating coil load
when predicted zone air temperature is above the heating
Setpoint
If a heating load exists (Figure 229), the supplemental
heating coil is used to meet the heating coil load and at the
same time offset the entire sensible cooling energy rate of
the cooling coil (to meet the humidistat setpoint). Note that
when a heating load exists and high humidity control is
required, the unitary system operates at the user-specified
cooling air flow rate for the entire simulation time step. As
with the fan, and cooling coil, report variables associated
with supplemental heating coil performance (e.g., heating coil
energy, heating coil rate, heating coil gas or electric
energy, heating coil runtime fraction, etc.) are managed in
the supplemental (heating) coil object.
Supplemental heating coil load
when predicted zone air temperature is below the heating
setpoint
Waste heat calculations are done when the multi speed
cooling and heating coils are specified in the unitary system
and the heat recovery is active (the value of the Design Heat
Recovery Water Flow Rate field is greater than 0), the outlet
node temperature of heat recovery is calculated based on the
recoverable waste heat generated by the child objects Coil:Cooling:DX:MultiSpeed
and Coil:Heating:DX:MultiSpeed:
Toutlet = outlet node temperature of heat
recovery, C
Tinlet = inlet node temperature of heat
recovery, C
QWasteHeat = recoverable waste heat generated by
its child objects, W
Cp = inlet node temperature of heat recovery,
C
\({\dot m_{hr}}\) = mass
flow rate of heat recovery, kg/s
If the outlet node temperature is above the value of the
Maximum Temp for Heat Recovery field, the outlet node
temperature is reset to the value of Maximum Temp for Heat
Recovery.
Forced-Air
Furnace and Central Air Conditioning[LINK]
The input objects AirLoopHVAC:Unitary:Furnace:HeatOnly
and AirLoopHVAC:Unitary:Furnace:HeatCool
provide a “virtual” component that collect and control a set
of components: an on/off or constant volume fan component and
a gas or electric heating coil component. If the HeatCool
version is selected, then a DX cooling coil is also modeled as
part of the system as shown in Figure 221 below. For the
HeatCool version, an optional reheat coil may also be modeled
for controlling high zone humidity levels and the furnace’s
configuration when specifying this option is shown in Figure
222 below. The unit may be configured to have either a blow
through or draw through fan. If a blow through fan
configuration is specified, the furnace fan is placed before
the heating coil for the HeatOnly version, or before the
cooling coil for the HeatCool version as shown in the figure
below. If a draw through fan configuration is specified, the
fan is placed directly after the heating coil.
Note: the coil order shown here has been revised from
previous versions of Energyplus to configure the cooling coil
upstream of the heating coil. This configuration provides
uniformity with all unitary equipment. However, for unitary
HeatCool systems that do not use a reheat coil, the heating
coil can also be placed upstream of the cooling coil. This
optional coil placement is retained to allow compatibility
with previous versions of Energyplus. For input files
developed using previous versions of Energyplus, it is
recommended that the coil order be revised according to the
figure below.
Schematic of the EnergyPlus
Furnace (Blow Through Configuration)
While the furnace may be configured to serve multiple
zones, system operation is controlled by a thermostat located
in a single “control” zone. One of the key parameters for the
furnace component is the fraction of the total system air flow
that goes through the control zone. This fraction is
calculated as the ratio of the maximum air mass flow rate for
the air loop’s supply inlet node for the control zone (e.g.,
AirTerminal:SingleDuct:Uncontrolled,
field = Maximum Air Flow Rate, converted to mass flow) to the
sum of the maximum air mass flow rates for the air loop’s
supply inlet nodes for all zones served by this air loop. The
furnace module scales the calculated load for the control zone
upward based on this fraction to determine the total load to
be met by the furnace. The module then proceeds to calculate
the required part-load ratio for the system coil and the
supply air fan to meet this total load. The heating or cooling
capacity delivered by the furnace is distributed to all of the
zones served by this system via the terminal units that supply
air to each zone. The supply air fraction that goes though the
control zone is calculated as follows:
\[Control Zone Air
Flow\,Fraction = \frac{{{{\dot
m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones}
{{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot
m_{TUMax\,ControlledZone}}\) =maximum air mass flow
rate for the air loop’s supply inlet node (terminal unit) for
the control zone (kg/s)
\({\dot
m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for
the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of
zones, or number of air loop supply air inlet nodes for all
zones served by the air loop (-)
The furnace component is able to model supply air fan
operation in two modes: cycling fan - cycling coil (i.e., AUTO
fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff
must be used to model AUTO fan, while Fan:OnOff
or Fan:ConstantVolume
can be used to model fan ON. The fan operation mode is
specified using a supply air fan operating mode schedule where
schedule values of 0 denote cycling fan operation and schedule
values other than 0 (a 1 is usually used) denote continuous
fan operation. Using this schedule, the furnace fan may be
cycled with cooling or heating coil operation or operated
continuously based on time of day (e.g., cycling fan operation
at night and continuous fan operation during the daytime). If
the fan operating mode schedule name field is left blank in
the furnace object, the furnace assumes cycling or AUTO fan
mode operation throughout the simulation.
The only output variables reported by the furnace object
are the fan part-load ratio and the compressor part-load ratio
(HeatCool only). The fan part-load ratio is defined as the
actual air mass flow rate through the system for the time step
divided by the design supply air mass flow rate specified for
the furnace (\(\dot{m}_{actual} /
\dot{m}_{design}\)). The furnace operates based on the
user-specified (or autosized) design supply air flow rate(s).
The ‘design’ supply air mass flow rate may be different for
cooling, heating, and when no cooling or heating is required
and the fan operates continuously based on user-specified
inputs (HeatCool only). For the HeatCool version, If alternate
air flow rates are specified for cooling, heating, and when no
cooling or heating is required, the design supply air mass
flow rate is the maximum of these specified values. Also for
the HeatCool version, the compressor part-load ratio is
reported as the ratio of the actual cooling load to the
full-load sensible capacity (see Eqn. ). Reporting of other
variables of interest for the furnace (heating rate, cooling
rate, energy consumption, etc.) is done by the individual
system components (fan, heating coil and DX cooling coil).
As described previously, the furnace is a “virtual”
component consisting of a fan, heating coil and, for the
HeatCool version, a cooling coil with an optional reheat coil.
The sole purpose of the furnace model is to properly
coordinate the operation of the various system components. The
following sections describe the flow of information within the
model for both the HeatOnly and HeatCool configurations, as
well as the differences between cycling and continuous supply
air fan operation. The last section describes the optional
control of high zone humidity with a reheat coil for the
HeatCool configuration.
The HeatOnly configuration consists of an on/off or
constant volume fan and an electric or gas heating coil. When
the model is first called during an EnergyPlus simulation, all
of the input data specified for each furnace in the input data
file are read into data structures for use throughout the
remainder of the simulation.
For each simulation time step when the performance of a
heat-only furnace is being modeled, the first step is to
retrieve the heating load required to meet the thermostat
setpoint for the “control” zone (see Figure 221. Schematic of
the EnergyPlus Furnace). See the section “Summary of
Predictor-Corrector Procedure” elsewhere in this document for
more details regarding load calculations. Since the furnace
may be specified to serve several zones but controlled based
on the load calculated for the “control” zone, the total
heating load to be met by the furnace is determined from the
following equation:
The model then calculates the furnace’s sensible heating
energy rate delivered to the zones being served when the
system runs at full-load conditions and when the heating coil
is OFF. If the supply air fan cycles on and off with the
heater, then the sensible heating energy rate is zero when the
heating coil is OFF. However if the fan is scheduled to run
continuously regardless of coil operation, then the sensible
heating energy rate will not be zero when the heating coil is
OFF. Calculating the sensible heating energy rate involves
modeling the supply air fan (and associated fan heat) and the
heating coil. For each of these cases (full load and heating
coil OFF), the sensible heating energy rate delivered by the
furnace is calculated as follows:
With the calculated sensible heating energy rates and the
total sensible heating load to be met by the system, the
part-load ratio for the furnace is estimated.
The part-load ratio calculated above is used to determine
the required heating coil capacity as \(Qheating\,coil =
Qdesign\,*PartLoadRatio\) where
Qdesign is the nominal heating coil
capacity as specified in the heating coil object. If the fan
cycles on and off with the heating coil (i.e., when the supply
air fan operating mode schedule values are equal to 0), then
this part-load ratio is also used to determine the operating
mass flow rate of the furnace as
If the fan operates continuously (i.e. fan ON), the
operating mass flow rate is specified as \({\dot m_{design}}\) . The
furnace’s fan and heating coil are then re-simulated to
determine the furnace’s delivered sensible heating capacity at
the above calculated part-load ratio.
\(Qfurnace\) = sensible
heating capacity delivered by the furnace (W)
\({\dot m_{furnace}}\) =
air mass flow rate through the furnace (kg/s)
\(h_{\rm{out,actual}}\) =
enthalpy of air exiting the furnace (J/kg)
\(h_{\rm{out,control
zone}}\) = enthalpy of air in the control zone
(J/kg)
HRmin = enthalpies evaluated at a
constant humidity ratio, the minimum humidity ratio of the
furnace exiting air or the air in the control zone
\(\Delta_{\rm{sen,actual}}\) =
Sensible load difference between the system output node and
the zone inlet node at the above calculated part-load
ratio.
Since the part-load performance of the heating coil can be
non-linear, and the supply air fan heat varies based on
heating coil operation for the case of cycling fan/cycling
coil (AUTO fan), the final part-load ratio for the heating
coil and fan are determined through iterative calculations
(successive modeling of the heating coil and fan) until the
furnace’s heating output matches the heating load to be met
within the heating convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the furnace’s
heating output divided by the load to be met.
If the furnace has been specified with cycling fan/cycling
coil (AUTO fan), then the furnace’s design air mass flow rate
is multiplied by PartLoadRatio to determine the average air
mass flow rate for the system simulation time step. The air
conditions at nodes downstream of the heating coil represent
the full-load (steady-state) values when the coil is
operating. If the supply air fan is specified to run
continuously (fan ON), then the air mass flow rate remains at
the furnace’s design air mass flow rate. In this case, the air
conditions at nodes downstream of the heating coil are
calculated as the average conditions over the simulation time
step (i.e., the weighted average of full-load conditions when
the coil is operating and inlet air conditions when the coil
is OFF).
For the case where the furnace is scheduled to operate with
continuous supply air fan operation, but no heating load is
required to meet the setpoint temperature in the control zone,
the supply air fan model is still called to determine the fan
exiting air conditions. The heating coil model is also called,
but for the case with no heating load the heating coil model
simply passes the inlet air conditions and mass flow rate from
its inlet node to its outlet node. The air exiting the heating
coil is then sent to the direct air units for distribution to
each zone served by the furnace, where the zone heat balance
is performed to determine the resulting zone air conditions.
The furnace exiting air conditions and energy consumption are
calculated and reported by the individual component models
(fan and heating coil).
The HeatCool configuration consists of an on/off or
constant volume fan, a DX cooling coil, and an electric or gas
heating coil. For the cases where a heating load is calculated
for the control zone or no heating/cooling load is calculated
for the control zone, the model follows nearly identical
computational steps as described in the HeatOnly Configuration
section above. The only difference is the air mass flow rate
during no cooling/heating operation with continuous supply air
fan operation can be different from the air mass flow rate
during heater operation for the HeatCool configuration. If a
cooling load is calculated by EnergyPlus for the control zone,
the solution methodology is also virtually identical and is
described here for completeness.
If EnergyPlus determines that the furnace must supply
cooling to the control zone to meet the zone air temperature
setpoint, then the model computes the total sensible cooling
load to be met by the furnace based on the control zone
sensible cooling load and the fraction of the furnace air flow
that goes through the control zone.
If the supply air fan operating mode schedule requests
cycling fan operation, the model first checks for the presence
of an ecomomizer in the outside air system serving the
furnace’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an
outside air system is not present or if an air-side economizer
is not used, the furnace’s compressor is used to meet the
furnace cooling load. If an air-side economizer is used and is
active (i.e., economizer controls indicate that conditions are
favorable to increase the outside air flow rate), the furnace
will try to meet the cooling load by operating only the supply
air fan. If the fan is able to satisfy the furnace cooling
load, the compressor remains off for the entire simulation
time step. If the operation of the fan alone is unable to meet
the entire cooling load, then the compressor is enabled and
additional calculations are performed to determine the
compressor’s part-load ratio.
The model then calculates the furnace’s sensible cooling
energy rate delivered to the zones being served when the
system runs at full-load conditions and when the DX cooling
coil is OFF. If the supply air fan cycles with the compressor,
then the sensible cooling energy rate is zero when the cooling
coil is OFF. However if the fan is configured to run
continuously regardless of coil operation, then the sensible
cooling energy rate will probably not be zero when the cooling
coil is OFF. Calculating the sensible cooling energy rate
involves modeling the supply air fan (and associated fan
heat), the DX cooling coil, and the heating coil (simply to
pass the air properties and mass flow rate from its inlet node
to its outlet node). For each of these cases (full load and DX
cooling coil OFF), the sensible cooling energy rate delivered
by the furnace is calculated as follows:
With the calculated sensible cooling energy rates and the
total sensible cooling load to be met by the system, the
part-load ratio for the furnace is estimated.
Since the part-load performance of the DX cooling coil is
frequently non-linear (Ref: DX Cooling Coil Model), and the
supply air fan heat varies based on cooling coil operation for
the case of cycling fan/cycling coil (AUTO fan), the final
part-load ratio for the cooling coil compressor and fan are
determined through iterative calculations (successive modeling
of the cooling coil and fan) until the furnace’s cooling
output matches the cooling load to be met within the
convergence tolerance. The convergence tolerance is fixed at
0.001 and is calculated based on the difference between the
load to be met and the furnace’s cooling output divided by the
load to be met.
If the furnace has been specified with cycling fan/cycling
coil (AUTO fan) and high humidity control has not
been specified, then the furnace’s operating supply air mass
flow rate is multiplied by PartLoadRatio to determine the
average air mass flow rate for the system simulation time
step. The air conditions at nodes downstream of the cooling
coil represent the full-load (steady-state) values when the
coil is operating. If a cycling fan is used and high humidity
control has been specified, the calculation of
average air mass flow rate is based on the greater of the
heating or cooling part-load ratio (see following section on
high humidity control). When the heating part-load ratio is
greater than the cooling part-load ratio, the air conditions
at nodes downstream of the cooling coil represent the weighted
average of full-load conditions when the cooling coil is
operating and inlet air conditions when the cooling coil is
off (i.e., the fan continues to operate due to a heating
requirement where the heating PLR is greater than the cooling
PLR). If the supply air fan is specified to run continuously
(fan ON), then the air mass flow rate continues to operate at
the user-specified supply air mass flow rate when no cooling
or heating is required. In this case, the air conditions at
nodes downstream of the cooling coil are calculated as the
average conditions over the simulation time step (i.e., the
weighted average of full-load conditions when the coil is
operating and inlet air conditions when the coil is OFF). The
furnace exiting air conditions and energy consumption are
calculated and reported by the individual component models
(fan and DX cooling coil).
High
Humidity Control with HeatCool Configuration[LINK]
An optional reheat coil can be specified with the HeatCool
configuration to allow the furnace to control high zone
humidity levels. The specific configuration of the HeatCool
Furnace with high humidity control option is shown in Figure
222. The figure below shows the fan placement when a blow
through fan is specified. If a draw through fan is specified,
the fan is located between the heating coil and the reheat
coil. The system is controlled to keep the relative humidity
in the control zone from exceeding the setpoint specified in
the object ZoneControl:Humidistat.
This option is available when the supply air fan operates
continuously (i.e., the supply air fan operating mode schedule
values are never equal to 0) or the supply air fan cycles with
the compressor. For the case of cycling fan mode when the high
humidity control is specified as CoolReheat and the
heating part-load ratio is greater than the compressor
part-load ratio, the air conditions at nodes downstream of the
cooling coil are calculated as the average conditions during
the duration of fan operation (i.e., the weighted average of
full load conditions when the coil is operating and inlet air
conditions when the coil is off and the fan continues to
operate to meet the heating load). For the case where cycling
fan mode is used and the heating part-load ratio is
less than the compressor part-load ratio, the air conditions
at the nodes downstream of the cooling coil are simply the
full load (steady-state) values when the coil is operating. In
addition, when high humidity control is specified and the
compressor operates, the furnace operates at the cooling air
flow rate when a zone heating load is present as determined by
the zone thermostat.
High humidity control is specified as either None,
MultiMode, or CoolReheat in the Dehumidification Control Type
input field. MultiMode is specified when a heat exchanger is
used to improve the dehumidification performance of the
cooling coil. The heat exchanger will be activated when the
sensible part-load ratio is insufficient to meet the zone
latent load. CoolReheat is specified when a DX cooling coil is
used to over-cool the supply air stream in order to meet the
zone latent load. In this case, a reheat coil will ensure the
zone temperature does not fall below the zone heating
temperature set point. When a heat exchanger is used in
conjunction with a DX cooling coil and CoolReheat is specified
as the Dehumidification Control Type, the heat exchanger is
“locked on” to meet either the sensible or latent cooling
load. If the dehumidification control type is selected as None
and a heat exchanger assisted cooling coil is used, the heat
exchanger is “locked on” and the air conditioner runs only to
meet the sensible cooling load. Although a reheat coil is
required when CoolReheat is specified in the Dehumidification
Control Type input field, this reheat coil may optionally be
present for the other Dehumidification Control Types (e.g.,
None and Multimode). If the reheat coil is present and the
dehumidification control type input is not specified as
CoolReheat, the reheat coil will not be active. This allows
changing the dehumidification control option without requiring
a change in the unit’s coil configuration.
The model first calculates the PartLoadRatio required to
meet the sensible cooling load as described above (see Eqn. )
to maintain the dry-bulb temperature setpoint in the control
zone. If a moisture (latent) load exists because the control
zone humidity has exceeded the setpoint, the total moisture
load to be met by the HeatCool furnace (SystemMoistureLoad) is
calculated based on the control zone moisture load and the
control zone air flow fraction. The model then calculates the
LatentPartLoadRatio required to meet the humidistat
setpoint.
FullLatentOutput = the furnace’s latent cooling
energy rate at full-load conditions, W
NoLatentOutput = the furnace’s latent cooling
energy rate with the cooling coil OFF, W
MinPLR= the minimum part-load ratio, which is
usually 0.0. For the case when the latent capacity degradation
model is used (Ref: DX Cooling Coil Model), this value is the
minimum part-load ratio at which the cooling coil will
dehumidify the air.
The model uses the greater of the two part-load ratios,
PartLoadRatio or LatentPartLoadRatio, to determine the
operating part-load ratio of the furnace’s DX cooling coil. As
previously described, iterations are performed to converge on
the solution within the convergence tolerance.
Schematic for Blow Through
Furnace with High Humidity Control
If the model determines that the LatentPartLoadRatio is to
be used as the operating part-load ratio of the furnace’s
cooling coil, the reheat coil is used to offset the excess
sensible capacity provided by the unit. The model first checks
the sensible load that exists for the current simulation time
step (predicted zone temperature with no HVAC operation
compared to the thermostat setpoint temperatures). If a
sensible cooling load or no sensible cooling or heating load
exists (Figure 223), the model calculates the difference
between the sensible heating load required to reach or
maintain the heating dry-bulb temperature setpoint and the
actual sensible cooling energy rate delivered by the unit
(with LatentPartLoadRatio). In this case, the reheat coil is
used to offset the excess sensible cooling energy provided by
the DX cooling coil (if any) that could have caused an
overshoot of the heating dry-bulb temperature setpoint. Note
that when a humidistat is used and high humidity control is
required, the zone dry-bulb temperature will typically move
toward the heating temperature setpoint when a high moisture
(latent) load exists. If a heating load exists (Figure 224),
the reheat coil is used to offset the entire sensible cooling
energy rate of the DX cooling coil (to meet the humidistat
setpoint) and the heating coil is used to meet the entire
heating load as described in the HeatOnly configuration
section above. Note that when a heating load exists and high
humidity control is required, the furnace operates at the
user-specified cooling air flow rate for the entire simulation
time step. As with the fan, DX cooling coil, and heating coil,
report variables associated with reheat coil performance
(e.g., heating coil energy, heating coil rate, heating coil
gas or electric consumption, heating coil runtime fraction,
etc.) are managed in the reheat (heating) coil object.
Reheat Coil Load when Predicted
Zone Temperature is Above Heating SetpointReheat Coil Load when Predicted
Zone Temperature is Below Heating Setpoint
The input objects AirLoopHVAC:UnitaryHeatCool
and AirLoopHVAC:UnitaryHeatOnly
provides models that are identical to the Furnace and Central
Air models described above. Please reference the previous
section for details.
Unitary
System with Changeover-Bypass-Variable Air Volume[LINK]
The input object AirLoopHVAC:UnitaryHeatCool:VAVChangeoverBypass
provides a model for a changeover-bypass variable air volume
(CBVAV) unitary system that is a compound object made up of
other components. Each CBVAV system consists of an outside air
mixer, direct expansion (DX) cooling coil, heating coil, and a
supply air fan as shown in the figures below. Zone
thermostats and terminal units are required in each zone
served by this system. The terminal units are specific to this
system type and are either AirTerminal:SingleDuct:VAV:HeatAndCool:Reheat
or AirTerminal:SingleDuct:VAV:HeatAndCool:NoReheat.
A zone humidistat and single zone max humidity setpoint
manager may also be specified to help control high humidity
levels. These individual components are described elsewhere in
this document. The CBVAV unitary system object coordinates the
operation of these components and is modeled as a type of air
loop equipment (Ref. AirLoopHVAC).
Schematic of a Changeover
Bypass VAV Unitary System with Draw Through FanSchematic of Changeover Bypass
VAV Unitary System with Blow Through Fan
The CBVAV unitary system conditions one or more zones and
is controlled by thermostats located in each zone (the use of
a single humidistat is also allowed when using multi-mode DX
cooling coils). The CBVAV system operates to meet the zone
sensible cooling or sensible heating requirements as dictated
by the thermostat schedule(s). The priority control input
determines the mode of operation and is specified as Cooling
Priority, Heating Priority, or Zone
Priority. If Cooling Priority is specified, the system
operates to meet the cooling load when any zone served by this
system (air loop) requires cooling. If Heating Priority is
specified, the system operates to meet the heating load when
any zone requires heating. If Zone
Priority is specified, the system operates based on the
maximum number of zones requiring either heating or
cooling.
Once the operating mode is determined, the CBVAV model
calculates a target supply air temperature required to operate
a single terminal unit at its maximum air flow rate. The
remaining terminal units will modulate as required to maintain
the dry-bulb temperature in the zone they are serving
according to the thermostat schedule for their respective
zone. The system air flow rate (through the supply air fan,
cooling coil and heat coil) remains constant during cooling
operation, heating operation, and no cooling/heating mode as
specified by the user. Therefore, as the zone terminal units
modulate to reduce zone air flow rates, the excess system air
flow is “bypassed” from the bypass duct splitter node back to
the bypass duct mixer node of the CBVAV system (see figures
above).
The CBVAV system is able to model supply air fan operation
in two modes: cycling fan - cycling coil (i.e., AUTO fan) and
continuous fan - cycling coil (i.e., fan ON). A Fan:OnOff
or Fan:ConstantVolume
is used in either case. Since the excess system air flow is
bypassed while the zone terminal units modulate, the supply
air fan operates the entire simulation time step when heating
or cooling is required. For this reason, AUTO fan only allows
the supply air fan to turn off when no cooling or heating is
required. If fan ON is specified, the supply air fan runs the
entire time the system is scheduled to operate (via its
availability schedule). The mode of operation for the supply
air fan is specified through a fan operating mode schedule
where a value of 0 in the schedule indicates cycling fan mode
and a value greater than 0 indicates continuous fan mode. If
the schedule is not provided, the supply air fan operating
mode is considered to be continuous (fan ON).
Output variables reported for the CBVAV system include the
supply air fan part-load ratio, the compressor part-load
ratio, and the electric consumption of the CBVAV system.
Additional output variables report the total heating rate and
total cooling rate provided by the CBVAV system. The sensible
and latent components for total system cooling and heating are
also available as output variables. Reporting of other
variables of interest for the CBVAV system (DX coil cooling
rate, heating rate, crankcase electric power and energy,
supply air fan electric power, etc.) is done by the individual
system components (fan, DX cooling coil, and heating
coil).
As described previously, the CBVAV system conditions one or
more zones and is controlled by zone thermostats (Ref.
ZoneControl:Thermostat). For each simulation time step,
EnergyPlus performs a zone air heat balance to determine if
cooling or heating is required to meet the zone thermostat
setpoints, excluding any impacts from CBVAV system operation.
CBVAV system performance is then modeled with all
heating/cooling coils off but with the supply air fan
operating according to the user specified supply air fan
operating mode schedule. If the zone air heat balance plus the
impact of CBVAV system operation with coils off results in no
requirement for heating or cooling by the CBVAV coils, or if
the CBVAV system is scheduled off (via its availability
schedule), then the CBVAV coils do not operate and the
compressor part-load ratio output variable is set to 0. If the
model determines that cooling or heating is required and the
CBVAV system is scheduled to operate, the model calculates a
target supply air temperature required to maintain a single
terminal unit at it’s maximum air flow rate, the amount of
bypass air returning to the bypass duct mixer node, and the
part-load ratio of the cooling or heating coils in order to
meet the target supply air temperature.
When high humidity control is desired, a ZoneControl:Humidistat
input object and a SetpointManager:SingleZone:Humidity:Maximum,SetpointManager:MultiZone:MaximumHumidity:Average
or SetpointManager:MultiZone:Humidity:Maximum
object are required. The air outlet node of the CBVAV system
is used as the control node for the setpoint manager. For this
reason, only a single humidistat should be specified for one
of the zones being served by this system. If
humidistat/setpoint manager objects are specified for more
than one zone served by this system, only the last of the SetpointManager:SingleZone:Humidity:Maximum
objects is used (the setpoint manager objects are read in
order of occurrence in the input file). Since the outlet node
of the CBVAV system is always used as the control node, the
setpoints calculated by the previous setpoint managers are
overwritten by the last setpoint manager in the input. When a
heat exchanger is used to improve the dehumidification
performance of the cooling coil
(i.e. CoilSystem:Cooling:DX:HeatExchangerAssisted), the heat
exchanger is always active and can not be turned on and off
based on zone humidity levels.
The remainder of this section describes the calculations
performed when cooling or heating coil operation is required.
For any HVAC simulation time step, the CBVAV system can only
cool or heat the air, not both. Because the CBVAV system
bypasses system air flow back to the inlet of the CBVAV unit,
the system operates for the entire simulation time step. If
the user specifies continuous fan operation, then the supply
air fan continues to operate at a user-specified flow rate
even during periods when the coils cycle off. If the user
specifies AUTO fan operation, then the supply air fan cycles
off for the entire simulation time step only when no cooling
or heating is required.
The first step in modeling a CBVAV system is to obtain the
cooling or heating load for each zone as calculated by
EnergyPlus based on the zone thermostat setpoint
temperature(s). The calculated loads for each zone are used to
determine the total cooling and heating requirements for all
zones served by this system. In addition to summing the zone
cooling and heating loads, the number of zones in cooling and
the number of zones in heating are totalized. The priority
control mode specified by the user is then used to determine
the operating mode for this simulation time step.
If Cooling Priority is specified and the total cooling
requirement in all zones is not equal to zero, then cooling is
selected as the operating mode. If the total cooling
requirement is equal to zero and the total heating requirement
is not equal to zero, then heating is selected as the
operating mode. If the total cooling requirement and total
heating requirement are equal to zero then the zones are
allowed to float (no heating or cooling provided).
If Heating Priority is specified and the total heating
requirement in all zones is not equal to zero, then heating is
selected as the operating mode. If the total heating
requirement is equal to zero and the total cooling requirement
is not equal to zero, then cooling is selected as the
operating mode. If the total cooling requirement and total
heating requirement are equal to zero then the zones are
allowed to float (no heating or cooling provided).
If Zone
Priority is specified and the total number of zones requiring
cooling is greater than the total number of zones requiring
heating, then cooling is selected as the operating mode. If
the total number of zones requiring heating is greater than
the total number of zones requiring cooling, then heating is
selected as the operating mode. If the total number of zones
requiring cooling is equal to the total number of zones
requiring heating, then the magnitude of the total cooling and
heating requirements for all zones sets the operating mode. In
this case, if the magnitudes of the cooling and heating
requirements are zero, then the zones are allowed to float (no
heating or cooing provided). If the magnitudes of the cooling
and heating requirements are non-zero and identical, then
cooling is selected as the operating mode.
Calculation
of Bypass Duct Mixer Node Conditions[LINK]
The operation of this system is unique in that it uses
constant-air-volume equipment to provide variable air volume
to the conditioned zones. This is accomplished with the use of
a bypass duct (shown in the figures above) which shunts excess
system air flow from the bypass duct splitter node at the
system’s outlet back to the bypass duct mixer node at the
system’s inlet. The air conditions at the bypass duct mixer
node are based on the inlet air to the CBVAV system, the
system outlet air conditions required to meet the zone loads,
and the fraction of bypassed air. The following calculations
are performed each simulation time step.
If the model determines that the CBVAV system must supply
cooling to the zones, the model first calculates a target
outlet air dry-bulb temperature required to operate a single
terminal unit at its maximum air flow rate. The minimum target
temperature for all zones is used to control the CBVAV system
in cooling mode.
\(T_{target}^i\) = Target
supply air temperature for zone i, °C
\(T_{zone}^i\) = Air
temperature in zone i, °C
\(Q_{zone}^i\) = Cooling
or heating load for zone i (cooling loads are
negative values, heating loads are positive values), W
\(Cp\) = Specific heat of
supply air with coils off, J/kg-K
\(\dot m_{zone,max}^i\) =
Maximum terminal unit mass flow rate in zone i,
kg/s
\(T_{target}\) = Target
supply (outlet) air temperature for the CBVAV system, °C
The model then calculates the part-load ratio of the DX
compressor required to meet the target supply (outlet) air
temperature. Since the part-load performance of the DX cooling
coil is frequently non-linear (Ref: Coil:Cooling:DX:SingleSpeed
model), the actual part-load ratio for the cooling coil
compressor is determined through iterative calculations
(successive modeling of the DX cooling coil model) until the
CBVAV system’s outlet air temperature (including on/off
cycling effects of the DX coil) matches the target supply
(outlet) air temperature within a small temperature
convergence tolerance (1E-5 ˚C).
Since the supply air fan operates continuously for each
simulation time step (or is OFF for the entire HVAC system
time step), the air conditions at nodes downstream of the
cooling coil are calculated as the average conditions over the
simulation time step (i.e., the weighted average of coil’s
outlet node conditions when the coil is operating and the
coil’s inlet node conditions when the coil is OFF).
Modeling the CBVAV system’s DX heating coil is identical to
the calculations described above for cooling operation except
that the maximum target supply air temperature for all zones
is used to control the CBVAV system in heating mode.
Iterative calculations (successive modeling of the DX
heating coil model) are used to determine the final heating
coil part-load ratio to account for the non-linear performance
of the DX heating coil at part-load conditions.
When a gas or electric heating coil is used instead of a DX
heating coil, the amount of heat required by the coil is
calculated based on the target supply (outlet) air temperature
and the coil inlet air temperature as follows:
When the zone thermostats determine that there is no
cooling or heating requirement in any zone, the CBVAV coils
are OFF and the zone temperatures are allowed to float.
However, a special case exists where the user specifies
continuous supply air fan operation and no cooling or heating
requirements exist in any zone. In this case, the outlet air
temperature of the CBVAV system (with fan ON and coils OFF) is
compared to the target outlet air temperatures required to
maintain the zone’s cooling and heating setpoint temperatures.
If the outlet air temperature with the supply fan ON and coils
OFF is below the target outlet air temperature required to
maintain the heating setpoint, then heating mode is enabled to
avoid overshooting the zone heating setpoint temperature.
Conversely, if the outlet air temperature with the supply fan
ON and coils OFF is above the target outlet air temperature
required to maintain the cooling setpoint, then cooling mode
is enabled to avoid overshooting the zone cooling setpoint
temperature. This special case is handled at any time a no
load condition is reported by the thermostats and overshooting
the zone air temperature setpoint is possible regardless of
the priority control mode selected by the user.
Minimum
and Maximum Outlet Air Temperature in Cooling/Heating
Operation[LINK]
The user also specifies a minimum outlet air temperature
during cooling operation and a maximum outlet air temperature
during heating operation. The target outlet air temperature,
as calculated above, is compared to each of these limits
during each simulation time step. The resulting target outlet
air temperature is used to control the heating and cooling
coils.
The changeover-bypass VAV system operates based on
user-specified (or autosized) air flow rates. The CBVAV system
air flow rate (i.e., air flow through the supply air fan and
heating/cooling coils) during cooling operation may be
different than the system air flow rate during heating
operation. In addition, the system air flow rate when no
cooling or heating is required but the supply air fan remains
ON can be different than the air flow rates when cooling or
heating is required. The outside air flow rates can likewise
be different in these various operating modes. The model takes
these different air flow rates into account when simulating
the performance of the CBVAV system. The system air flow rate
for each simulation time step is based on the current
operating mode (cooling, heating, or no cooling/heating) and
is reported on the inlet/outlet air nodes of the various CBVAV
components (e.g. fan, cooling coil, and heating coil). The
supply air flow rate delivered to the individual zones is
calculated based on the sum of the air flow rates through each
terminal unit and is reported at the air inlet and outlet
nodes of the CBVAV system each simulation time step. The
difference between the system air mass flow rate and the
supply air mass flow rate delivered to all zones is equal to
the bypass air mass flow rate which is also reported each
simulation time step.
The system and outside air flow rates when a system coil is
ON (e.g., system air volumetric flow rate during cooling
operation, system air volumetric flow rate during heating
operation, outside air volumetric air flow rate during cooling
operation, and outside air volumetric air flow rate during
heating operation) or the system coils are OFF and the fan
operates continuously (e.g., system air volumetric flow rate
when no cooling or heating is needed and outside air
volumetric air flow rate when no cooling or heating is needed)
are specified by the user, or can be autosized, and are
converted from volumetric flow rate to mass flow rate at
standard conditions. If the user has specified cycling fan
operation, then the system air and outside air mass flow rates
when the system coils are OFF the entire time step are zero.
If the user has specified constant fan operation, then the air
flow rates when no cooling or heating is needed are used when
the system coils are OFF the entire time step.
There is one special case. If the user has specified
constant fan operation and they specify that the system air
volumetric flow rate when no cooling or heating is needed is
zero (or if the field is left blank), then the model assumes
that the system air mass flow rate when the system coils are
OFF the entire time step is equal to the corresponding air
mass flow rate when any system coil was last operating (ON).
This model handles the zero (or blank) entry for outside air
volumetric flow rate when no cooling or heating is needed in
an analogous fashion.
\(\rho air,std\) =
standard air density (1.204 kg/m3) adjusted for the
local barometric pressure (standard barometric pressure
corrected for altitude, ASHRAE 1997 HOF pg. 6.1),
kg/m3
\({\dot V_{mode}}\) =
User-specified system volumetric flow rate in cooling,
heating, or no cooling or heating mode, m3/s
\({\dot m_{system,OA}}\) =
Outdoor air mass flow rate introduced through the CBVAV
system, kg/s
\({\dot V_{mode,OA}}\) =
User-specified outdoor air volumetric flow rate in cooling,
heating, or no cooling or heating mode, m3/s
Calculation
of System Heating and Cooling Rates[LINK]
At the end of each HVAC simulation time step, this object
reports the heating or cooling rate and energy delivered by
the system, as well as the electric power and consumption by
the system. In terms of thermal energy delivered by the
system, the sensible, latent and total energy transfer rates
for the system are calculated as follows:
\({\dot Q_{total}}\) =
total energy transfer rate by the system, W
\({\dot Q_{sensible}}\) =
sensible energy transfer rate by the system, W
\({\dot Q_{latent}}\) =
latent energy transfer rate by the system, W
hinlet = enthalpy of the air entering
the unit at its inlet node, J/kg
houtlet = enthalpy of the air leaving
the unit at its outlet node, J/kg
\(H{R_{min}}\) = minimum
of the inlet air and outlet air humidity ratio, kg/kg
Since each of these energy transfer rates can be calculated
as positive or negative values, individual reporting variables
are established for cooling and heating and only positive
values are reported. The following calculations are
representative of what is done for each of the energy transfer
rates:
\({\dot
Q_{total,cooling}}\) = output variable ‘Unitary System
Total Cooling Rate, W’
\({\dot
Q_{total,heating}}\) = output variable ‘Unitary System
Total Heating Rate, W’
In addition to heating and cooling rates, the heating and
cooling energy supplied by the system are also calculated for
the time step being reported. The following example for total
zone cooling energy is representative of what is done for the
sensible and latent energy as well as the heating
counterparts.
The changeover-bypass VAV system is modeled as an air loop
component and is sized according to the methodology described
elsewhere in this document (Ref. System Design Loads and Air
Flow Rates). The following volumetric air flow rates may be
autosized:
system air volumetric flow rate during cooling
operation
system air volumetric flow rate during heating
operation
system air volumetric flow rate when no cooling or heating
is needed
outside air volumetric air flow rate during cooling
operation
outside air volumetric air flow rate during heating
operation
outside air volumetric air flow rate when no cooling or
heating is needed
The input object AirLoopHVAC:UnitaryHeatPump:AirToAir
provides a model for an air-to-air heat pump that is a
“virtual” component that consists of an on/off or constant
volume fan component, a DX cooling coil, a DX heating coil,
and a gas or electric supplemental heating coil. The specific
configuration of the blow through heat pump is shown in the
following figure. For a draw through heat pump, the fan is
located between the DX heating coil and the supplemental
heating coil.
Schematic of a Blow Through
Air-to-Air Heat Pump
While the heat pump may be configured to serve multiple
zones, system operation is controlled by a thermostat located
in a single “control” zone. One of the key parameters for the
heat pump component is the fraction of the total system
airflow that goes through the control zone. This fraction is
calculated as the ratio of the maximum air mass flow rate for
the air loop’s supply inlet node for the control zone (e.g.,
AirTerminal:SingleDuct:Uncontrolled,
field = Maximum Air Flow Rate, converted to mass flow) to the
sum of the maximum air mass flow rates for the air loop’s
supply inlet nodes for all zones served by this air loop. The
heat pump module scales the calculated load for the control
zone upward based on this fraction to determine the total load
to be met by the heat pump. The module then proceeds to
calculate the required part-load ratio for the system coil and
the supply air fan to meet this total load. The heating or
cooling capacity delivered by the heat pump is distributed to
all of the zones served by this system via the direct air
units that supply air to each zone. The supply air fraction
that goes though the control zone is calculated as
follows:
\[Control Zone Air
Flow\,Fraction = \frac{{{{\dot
m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones}
{{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot
m_{TUMax\,ControlledZone}}\) =maximum air mass flow
rate for the air loop’s supply inlet node (terminal unit) for
the control zone (kg/s)
\({\dot
m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for
the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of
zones, or number of air loop supply air inlet nodes for all
zones served by the air loop (-)
The heat pump component is able to model supply air fan
operation in two modes: cycling fan - cycling coil (i.e., AUTO
fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff
must be used to model AUTO fan, while Fan:OnOff
or Fan:ConstantVolume
can be used to model fan ON. The fan operation mode is
specified using a supply air fan operating mode schedule where
schedule values of 0 denote cycling fan operation and schedule
values other than 0 (a 1 is usually used) denote continuous
fan operation. Using this schedule, the furnace fan may be
cycled with cooling or heating coil operation or operated
continuously based on time of day (e.g. cycling fan operation
at night and continuous fan operation during the day). If the
fan operating mode schedule name field is left blank in the
heat pump object, the heat pump assumes cycling or AUTO fan
mode operation throughout the simulation.
The output variables reported by the heat pump object are
fan part-load ratio and compressor part-load ratio. Fan
part-load ratio is defined as the actual air mass flow rate
through the system for the time step divided by the operating
supply air mass flow rate specified for the heat pump (\(\dot{m}_{actual} /
\dot{m}_{ON}\)). The operating supply air mass flow
rate may be different for cooling, heating, and when no
cooling or heating is required and the fan operates
continuously. Compressor part-load ratio is the actual load
for the time step divided by the full-load sensible capacity
(see Eqn. or Eqn.). Reporting of other variables of interest
for the heat pump (heating rate, cooling rate, energy
consumption, etc.) is done by the individual system components
(fan, DX cooling coil, DX heating coil, and supplemental
heating coil).
As described previously, the heat pump is a “virtual”
component consisting of a fan, DX cooling coil, DX heating
coil and a supplemental heating coil. The sole purpose of the
heat pump model is to properly coordinate the operation of the
various system components. The following sections describe the
flow of information within the model, as well as the
differences between cycling and continuous supply air fan
operation.
If EnergyPlus determines that the heat pump must supply
cooling to the control zone to meet the zone air temperature
setpoint, then the heat pump model computes the total sensible
cooling load to be delivered to the zones being served based
on the control zone sensible cooling load and the fraction of
the heat pump air flow that goes through the control zone.
If the supply air fan operating mode schedule requests
cycling fan operation, the model first checks for the presence
of an ecomomizer in the outside air system serving the heat
pump’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an
outside air system is not present or if an air-side economizer
is not used, the heat pump’s compressor is used to meet the
heat pump cooling load. If an air-side economizer is used and
is active (i.e., economizer controls indicate that conditions
are favorable to increase the outside air flow rate), the heat
pump will try to meet the cooling load by operating only the
supply air fan. If the fan is able to satisfy the heat pump
cooling load, the compressor remains off for the entire
simulation time step. If the operation of the fan alone is
unable to meet the entire cooling load, then the compressor is
enabled and additional calculations are performed to determine
the compressor’s part-load ratio.
The model then calculates the heat pump’s sensible cooling
energy rate delivered to the zones being served when the
system runs at full-load conditions and when the DX cooling
coil is OFF. If the supply air fan cycles with the compressor,
then the sensible cooling energy rate is zero when the cooling
coil is OFF. However if the fan is scheduled to run
continuously regardless of coil operation, then the sensible
cooling energy rate will not be zero when the cooling coil is
OFF. Calculating the sensible cooling energy rate involves
modeling the supply air fan (and associated fan heat) and the
DX cooling coil. The DX heating coil and the supplemental
heating coil are also modeled, but only to pass the air
properties and mass flow rate from their inlet nodes to their
outlet nodes. For each of these cases (full load and DX
cooling coil OFF), the sensible cooling energy rate delivered
by the heat pump is calculated as follows:
With the calculated sensible cooling energy rates and the
total sensible cooling load to be met by the system, the
part-load ratio for the heat pump is estimated.
Since the part-load performance of the DX cooling coil is
frequently non-linear, and the supply air fan heat varies
based on cooling coil operation for the case of cycling
fan/cycling coil (AUTO fan), the final part-load ratio for the
cooling coil compressor and fan are determined through
iterative calculations (successive modeling of the cooling
coil and fan) until the heat pump’s cooling output matches the
cooling load to be met within the convergence tolerance. The
convergence tolerance is fixed at 0.001 and is calculated
based on the difference between the load to be met and the
heat pump’s cooling output divided by the load to be met.
If the heat pump has been specified with cycling
fan/cycling coil (AUTO fan), then the heat pump’s operating
supply air mass flow rate is multiplied by PartLoadRatio to
determine the average air mass flow rate for the system
simulation time step. In this case, the air conditions at
nodes downstream of the cooling coil represent the full-load
(steady-state) values when the coil is operating.
If the fan operates continuously (i.e., when the supply air
fan operating mode schedule values are NOT equal to 0), the
operating air mass flow rate through the heat pump is
calculated as the average of the user-specified air flow rate
when the cooling coil is ON and the user-specified air flow
rate when the cooling coil is OFF (user-specified supply air
volumetric flow rates converted to dry air mass flow
rates).
\(\mathop m\limits^
\bullet CoolCoilON\) = air mass flow rate through heat
pump when the cooling coil is ON (kg/s)
\(\mathop m\limits^
\bullet CoilOFF\) = air mass flow rate through heat
pump when no cooling or heating is needed (kg/s)
In this case, the air conditions at nodes downstream of the
cooling coil are calculated as the average conditions over the
simulation time step (i.e., the weighted average of full-load
conditions when the coil is operating and inlet air conditions
when the coil is OFF).
Heating Operation
Calculations for heating operation are similar to those for
cooling operation in most respects. However, due to the
inclusion of a supplemental heating coil, additional
calculations are necessary to properly meet the total heating
load for the zones being served.
If EnergyPlus determines that the heat pump must supply
heating to the control zone to meet the zone air temperature
setpoint, then the heat pump model computes the total sensible
heating load to be delivered to the zones being served based
on the control zone sensible heating load and the control zone
airflow fraction.
The model then calculates the heat pump’s sensible heating
energy rate delivered to the zones being served when the
system runs at full-load conditions and when the DX heating
coil is OFF (without supplemental heater operation in either
case). If the supply air fan cycles with the compressor, then
the sensible heating energy rate is zero when the compressor
is OFF. However if the fan is scheduled to run continuously
regardless of coil operation, then the sensible heating energy
rate will not be zero when the compressor is OFF. Calculating
the sensible heating energy rate involves modeling the supply
air fan (and associated fan heat), the DX cooling coil (simply
to pass the air properties and mass flow rate from its inlet
node to its outlet node), the DX heating coil, and the
supplemental heating coil (simply to pass the air properties
and mass flow rate from its inlet node to its outlet node).
For each of these cases (full load and DX heating coil OFF,
without supplemental heater operation in either case), the
sensible heating energy rate delivered by the heat pump is
calculated as follows:
With the calculated sensible heating energy rates and the
total sensible heating load to be met by the system, the
part-load ratio for the heat pump is estimated.
Since the part-load performance of the DX heating coil is
frequently non-linear (Ref: Single-Speed Electric Heat Pump DX
Air Heating Coil), and the supply air fan heat varies based on
heating coil operation for the case of cycling fan/cycling
coil (AUTO fan), the final part-load ratio for the heating
coil compressor and fan are determined through iterative
calculations (successive modeling of the heating coil and fan)
until the heat pump’s heating output matches the heating load
to be met within the convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the heat pump’s
heating output divided by the load to be met.
If the heat pump’s DX heating coil output at full load is
insufficient to meet the entire heating load, PartLoadRatio is
set equal to 1.0 (compressor and fan are not cycling) and the
remaining heating load is passed to the supplemental heating
coil. If the heat pump model determines that the outdoor air
temperature is below the minimum outdoor air temperature for
compressor operation, the compressor is turned off and the
entire heating load is passed to the supplemental gas or
electric heating coil. The heat pump exiting air conditions
and energy consumption are calculated and reported by the
individual component models (fan, DX heating coil, and
supplemental gas or electric heating coil).
If the heat pump has been specified with cycling
fan/cycling coil (AUTO fan), then the heat pump’s operating
supply air mass flow rate is multiplied by PartLoadRatio to
determine the average air mass flow rate for the system
simulation time step. The air conditions at nodes downstream
of the heating coils represent the full-load (steady-state)
values when the coils are operating. If the fan operates
continuously (i.e., when the supply air fan operating mode
schedule values are NOT equal to 0), the operating air mass
flow rate through the heat pump is calculated as the average
of the user-specified air flow rate when the heat pump heating
coil is ON and the user-specified air flow rate when the heat
pump heating coil is OFF (user-specified supply air volumetric
flow rates converted to dry air mass flow rates).
\(\mathop m\limits^
\bullet HeatCoilON\) = air mass flow rate through heat
pump when the heating coil is ON (kg/s)
\(\mathop m\limits^
\bullet CoilOFF\) = air mass flow rate through heat
pump when no heating or cooling is needed (kg/s)
In this case, the air conditions at nodes downstream of the
heating coils are calculated as the average conditions over
the simulation time step (i.e., the weighted average of
full-load conditions when the coils are operating and inlet
air conditions when the coils are OFF).
High
Humidity Control with AirToAir HeatPump Model[LINK]
The specific configuration of the AirToAir HeatPump with
supplemental heating coil is shown above (see Figure 227).
This figure shows the fan placement when a blow through fan is
specified. If a draw through fan is specified, the fan is
located between the heating coil and the supplemental heating
coil. The system is controlled to keep the high relative
humidity in the control zone from exceeding the setpoint
specified in the object ZoneControl:Humidistat.
This option is available when the supply air fan operates
continuously (i.e., the supply air fan operating mode schedule
values are never equal to 0) or the supply air fan cycles with
the compressor. In addition, when high humidity control is
specified and the compressor operates, the heatpump operates
at the cooling air flow rate when a zone heating load is
present as determined by the zone thermostat. High humidity
control is specified as either None, MultiMode, or CoolReheat
in the Dehumidification Control Type input field. MultiMode is
specified when a heat exchanger is used to improve the
dehumidification performance of the cooling coil. The heat
exchanger will be activated when the sensible part-load ratio
is insufficient to meet the zone latent load. CoolReheat is
specified when a DX cooling coil is used to over-cool the
supply air stream in order to meet the zone latent load. In
this case, a supplemental heating coil will ensure the zone
temperature does not fall below the zone heating temperature
set point. When a heat exchanger is used in conjunction with a
DX cooling coil and CoolReheat is specified as the
Dehumidification Control Type, the heat exchanger is “locked
on” to meet either the sensible or latent cooling load. If the
dehumidification control type is selected as None and a heat
exchanger assisted cooling coil is used, the heat exchanger is
“locked on” and the air conditioner runs only to meet the
sensible cooling load. A supplemental heating coil is required
for all dehumidification control types.
The model first calculates the PartLoadRatio
required meeting the sensible cooling load. The heatpump’s
sensible cooling load is determined from the control zone
sensible cooling load to the cooling setpoint and the control
zone air flow fraction to maintain the dry-bulb temperature
setpoint in the control zone.:
The heatpump’s sensible cooling load to be met and the full
load cooling output are used to calculate the sensible the
part-load ratio iteratively based on user specified
convergence criterion.
When the heat pump’s sensible cooling capacity meets the
system sensible cooling load at a given sensible part load
ratio, then the Heat pump meets the controlled zone cooling
setpoint temperature. If a moisture (latent) load exists
because the control zone humidity has exceeded the setpoint,
the total moisture load to be met by the heat pumps
(HeatPumpMoistureLoad) is calculated based on the control zone
moisture load and the control zone air flow fraction.
The model uses the greater of the two part-load ratios,
PartLoadRatio or LatentPartLoadRatio, to
determine the operating part-load ratio of the Heat Pump’s DX
cooling coil.
As previously described, iterations are performed to
converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\)
= the control zone sensible cooling load to the cooling
setpoint, (W).
\(ControlZoneMoistureLoad\) = the
control zone moisture load to the dehumidifying relative
humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) =
the supply air fraction that goes though the control zone,
(-).
FullLatentOutput =the Heat Pump’s latent cooling
energy rate at full-load conditions, W
NoLatentOutput =the Heat Pump’s latent cooling
energy rate with cooling coil OFF, W
\(PartLoadRatio\) =the
heat pump’s part-load-ratio required to meet system sensible
load, (-).
\(LatentPartLoadRatio\)
=the heat pump’s part-load-ratio required to meet system
moisture load, (-).
\(PL{R_{MIN}}\) = the
minimum part-load ratio, which is usually 0.0. For the case
when the latent capacity degradation model is used (Ref: DX
Cooling Coil Model), this value is the minimum part-load ratio
at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the
heating setpoint and if there is a dehumidification load, the
supplemental heating coil load is required to offset the
excess cooling as shown in Figure 228. If the model determines
that the LatentPartLoadRatio is to be used as the operating
part-load ratio of the heatpump’s cooling coil, the
supplemental heating coil is used to offset the excess
sensible capacity provided by the heat pump DX cooling coil.
The model first checks the sensible load that exists for the
current simulation time step (predicted zone temperature with
no HVAC operation compared to the thermostat setpoint
temperatures). If a sensible cooling load or no sensible
cooling or heating load exists (see Figure 2), the model
calculates the difference between the sensible heating load
required to reach or maintain the heating dry-bulb temperature
setpoint and the actual sensible cooling energy rate delivered
by the unit (with LatentPartLoadRatio). In this case, the
supplemental heating coil is used to offset the excess
sensible cooling energy provided by the DX cooling coil (if
any) that could have caused an overshoot of the heating
dry-bulb temperature setpoint. Note that when a humidistat is
used and high humidity control is required, the zone dry-bulb
temperature will typically move toward the heating temperature
setpoint when a high moisture (latent) load exists.
Supplemental heating coil load
when predicted zone air temperature is above the heating
Setpoint
If a heating load exists (Figure 229), the supplemental
heating coil is used to meet the heating coil load and at the
same time offset the entire sensible cooling energy rate of
the DX cooling coil (to meet the humidistat setpoint). Note
that when a heating load exists and high humidity control is
required, the heat pump operates at the user-specified cooling
air flow rate for the entire simulation time step. As with the
fan, and DX cooling coil, report variables associated with
supplemental heating coil performance (e.g., heating coil
energy, heating coil rate, heating coil gas or electric
energy, heating coil runtime fraction, etc.) are managed in
the supplemental (heating) coil object.
Supplemental heating coil load
when predicted zone air temperature is below the heating
setpoint
The input object AirLoopHVAC:UnitaryHeatPump:AirToAir:MultiSpeed
provides a model for a multispeed air-to-air heat pump that is
a “virtual” component that consists of an on/off or constant
volume fan component, a multispeed DX cooling coil, a
multispeed DX heating coil, and a gas or electric supplemental
heating coil. The main difference between this heat pump
object and other EnergyPlus heat pump objects is that this
object allows from two to four discrete compressor speeds for
heating and cooling operation (instead of a single speed for
each mode). The specific configuration of the blow through
heat pump is shown in the following figure. For a draw through
heat pump, the fan is located between the DX heating coil and
the supplemental heating coil.
Schematic of a Multispeed
Air-to-Air Heat Pump (Blow-through Configuration)
While the heat pump may be configured to serve multiple
zones, system operation is controlled by a thermostat located
in a single “control” zone. One of the key parameters for the
heat pump component is the fraction of the total system
airflow that goes through the control zone. This fraction is
calculated as the ratio of the maximum air mass flow rate for
the air loop’s supply inlet node for the control zone (e.g.,
AirTerminal:SingleDuct:Uncontrolled,
field = Maximum Air Flow Rate, converted to mass flow) to the
sum of the maximum air mass flow rates for the air loop’s
supply inlet nodes for all zones served by this air loop. The
heat pump module scales the calculated load for the control
zone upward based on this fraction to determine the total load
to be met by the heat pump. The module then proceeds to
calculate the required cycling ratio, speed ratio and speed
number for the system coil and determines the supply air mass
flow rate to meet this total load based on the speed number.
The cycling ratio is the ratio of the sensible load (heating
or cooling) to the steady-state capacity of the multispeed
heat pump’s DX heating or cooling coil at Speed 1 for the
entire system time step. It is equivalent to the part load
ratio for a single speed DX coil. The value is between 0.0 and
1.0 when the system operates at its lowest speed (Speed 1) and
1.0 when the multispeed heat pump operates at speeds above 1.
The speed ratio is the ratio of time in a system time step
that the compressor is at rated speed between two consecutive
speed numbers ([Compressor Speed - Compressor speed at Speed
i-1] / [Compressor speed at Speed i - Compressor speed at
Speed i-1]). The compressor speed ratio is between 0.0 and 1.0
when the speed number is above 1 and is 0.0 during Speed 1
operation. The speed number is the lowest index number whose
corresponding full-load sensible capacity at the given air
mass flow rate is greater than or equal to the sensible load
(heating or cooling) in a system time step. The heating or
cooling capacity delivered by the heat pump is distributed to
all of the zones served by this system via the direct air
units that supply air to each zone.
The heat pump component is able to model supply air fan
operation in two modes: cycling fan - cycling coil (i.e., AUTO
fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff
must be used to model AUTO fan, while Fan:OnOff
or Fan:ConstantVolume
can be used to model fan ON. The fan operation mode is
specified using a supply air fan operating mode schedule where
schedule values of 0 denote cycling fan operation and schedule
values other than 0 (a 1 is usually used) denote continuous
fan operation. Using this schedule, the supply air fan may be
cycled with cooling or heating coil operation or operated
continuously based on time of day (e.g. cycling fan operation
at night and continuous fan operation during the day).
Several output variables are reported by the heat pump
object including fan part-load ratio, compressor part-load
ratio, cycling ratio, speed ratio and speed number. Fan
part-load ratio is defined as the actual air mass flow rate
through the system for the time step divided by the operating
supply air mass flow rate specified for the heat pump (\(\dot{m}_{actual} /
\dot{m}_{ON}\)) at speed 1. Fan part-load ratio is set
to 1.0 when the heat pump operates at speeds above 1. The
operating supply air mass flow rate may be different for
cooling, heating, and when no cooling or heating is required.
Compressor part-load ratio is the actual load for the time
step divided by the full-load sensible capacity (see Eqn. or
Eqn.). If the defrost strategy is reverse cycle for a DX
heating coil, the compressor part-load ratio is the sum of the
actual load and the defrost load divided by the full-load
sensible capacity. Therefore, the compressor part load ratio
for the DX heating coil may be greater than the cycling ratio.
This heat pump object also reports the sensible, latent and
total cooling and heating rate, as well as the electricity
consumption for the unit with separate accounting of auxiliary
electric consumption. Furthermore, five report variables
related to waste heat recovery are available if the user
chooses to model this option.
As described previously, the heat pump is a “virtual”
component consisting of a fan, multispeed DX cooling coil,
multispeed DX heating coil and supplemental heating coil. The
sole purpose of the heat pump model is to properly coordinate
the operation of the various system components. The following
sections describe the flow of information within the model, as
well as the differences between cycling and continuous supply
air fan operation.
The description of heat pump cooling operation is divided
in two sections: sensible capacity and average supply air flow
rate. Actually, the determinations of capacity and supply air
flow rate are related, so these calculations are performed in
unison.
If EnergyPlus determines that the heat pump must supply
cooling to the control zone to meet the zone air temperature
setpoint, then the heat pump model computes the total sensible
cooling load (negative) to be delivered to the zones being
served based on the control zone sensible cooling load and the
fraction of the heat pump air flow that goes through the
control zone.
The model then calculates the heat pump’s sensible cooling
energy rate delivered to the zones being served when the
system runs at full-load conditions at the highest speed and
when the DX cooling coil is OFF. If the supply air fan cycles
with the compressor, then the sensible cooling energy rate is
zero when the cooling coil is OFF. However if the fan is
scheduled to run continuously regardless of coil operation,
then the sensible cooling energy rate will not be zero when
the cooling coil is OFF. Calculating the sensible cooling
energy rate involves modeling the supply air fan (and
associated fan heat) and the multispeed DX cooling coil. The
multispeed DX heating coil and the supplemental heating coil
are also modeled, but only to pass the air properties and mass
flow rate from their inlet nodes to their outlet nodes. For
each of these cases (full load at highest cooling speed and DX
cooling coil OFF), the sensible cooling energy rate delivered
by the heat pump is calculated as follows:
If the heat pump’s sensible cooling rate at the highest
speed (full load, no cycling) is insufficient to meet the
entire cooling load, the controlled zone conditions will not
be met. The reported cycling rate and speed ratio are 1, and
the speed number is set to the highest index number. If the
total sensible cooling load to be met by the system is less
than the sensible cooling rate at the highest speed, then the
following steps are performed.
Calculate the sensible cooling energy rate at Speed 1
If the sensible cooling energy rate delivered by the heat
pump at Speed 1 is greater or equal to the sensible load, the
cycling ratio (part-load ratio) for the heat pump is
estimated.
AddedFanHeat= generated supply air fan heat, which is a
function of part load ratio and as internal component cooling
load [W].
AddedFanHeatSpeed1= generated supply air fan
heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX cooling coil is
frequently non-linear,and the supply air fan heat varies based
on cooling coil operation for the case of cycling fan/cycling
coil (AUTO fan), the final part-load ratio for the cooling
coil compressor and fan are determined through iterative
calculations (successive modeling of the cooling coil and fan)
until the heat pump’s cooling output matches the cooling load
to be met within the convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the heat pump’s
cooling output divided by the load to be met.
\({\dot
m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply
inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the
required cooling load, the speed ratio is set to zero and
speed number is equal to 1.
If the heat pump’s cooling output at full load for Speed 1
is insufficient to meet the entire cooling load, the Cycling
ratio is set equal to 1.0 (compressor and fan are not
cycling). Then the cooling speed is increased and the
delivered sensible capacity is calculated. If the full load
sensible capacity at Speed n is greater than or equal to the
sensible load, the speed ratio for the heat pump is
estimated:
\(Speed{\kern 1pt} Ratio =
\frac{{ABS(Heat{\kern 1pt} Pump{\kern 1pt} Cooling{\kern 1pt}
Load - AddeFanHeat - Full{\kern 1pt} Cool{\kern 1pt}
Outpu{t_{Speed{\kern 1pt} n - 1}})}}{{ABS(Full{\kern 1pt}
CoolOutpu{t_{Speed{\kern 1pt} n}} - Full{\kern 1pt}
CoolOutpu{t_{Speed{\kern 1pt} n - 1}})}}\) Although a
linear relationship is assumed by applying the speed ratio to
obtain the effective capacity and mass flow rate between speed
n and n-1, the outlet air node conditions are dependent on the
combined outputs and may not be linear. In addition, the
supply air fan heat varies with the speed ratio due to
different supply mass flow rates between speed n and n-1 .
Therefore, the final speed ratio for the cooling coil
compressor and fan are determined through iterative
calculations (successive modeling of the cooling coil and fan)
until the heat pump’s cooling output matches the cooling load
to be met within the convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the heat pump’s
cooling output divided by the load to be met.
If the heat pump has been specified with cycling
fan/cycling coil (AUTO fan), then the heat pump’s operating
supply air mass flow rate is determined by the cycling ratio
(PartLoadRatio) for Speed 1. The supply air mass flow rate is
multiplied by the cycling ratio to determine the average air
mass flow rate for the system simulation time step. The air
conditions at nodes downstream of the cooling coils represent
the full-load (steady-state) values when the coil is
operating.
If the fan operates continuously (i.e., when the supply air
fan operating mode schedule values are NOT equal to 0), the
operating air mass flow rate through the heat pump is
calculated as the average of the user-specified air flow rate
when the heat pump cooling coil is ON at Speed 1 and the
user-specified air flow rate when the heat pump cooling coil
is OFF (user-specified supply air volumetric flow rates
converted to dry air mass flow rates).
\({\dot m_{HeatPump}}\) =
average air mass flow rate through heat pump [kg/s]
\({\dot m_{Speed1}}\) =
air mass flow rate through heat pump when cooling coil is ON
at Speed 1 [kg/s]
\({\dot m_{CoilOff}}\) =
air mass flow rate through heat pump when no heating or
cooling is needed [kg/s]
In this case, the air conditions at nodes downstream of the
cooling coils are calculated as the average conditions over
the simulation time step (i.e., the weighted average of
full-load conditions when the coil is operating and inlet air
conditions when the coil is OFF).
When the heat pump operates at higher speeds to meet the
required cooling load, the supply air mass flow rate is
linearly interpolated between two consecutive speeds:
\({\dot m_{HeatPump}}\) =
average air mass flow rate through the heat pump for the time
step [kg/s]
\({\dot m_{Speed\;n}}\) =
air mass flow rate through heat pump when cooling coil is ON
at Speed n [kg/s]
\({\dot m_{Speed\;n -
1}}\) = air mass flow rate through heat pump when
cooling coil is ON at Speed n-1 [kg/s]
For this case of higher speed operation, the air conditions
at nodes downstream of the cooling coils are determined by the
delivered cooling capacity and supply air mass flow rates
between two consecutive speeds.
Although the above sections present the capacity and air
mass flow rate calculation separately, they are dependent and
change every iteration until convergence is reached for the
time step being simulated.
The description of heat pump heating operation is divided
in two sections: total (sensible) capacity and average supply
air flow rate. Actually, the determinations of capacity and
supply air flow rate are related, so these calculation are
performed in unison.
If EnergyPlus determines that the heat pump must supply
heating to the control zone to meet the zone air temperature
setpoint, then the heat pump model computes the total sensible
heating load (positive) to be delivered to the zones being
served based on the control zone sensible heating load and the
fraction of the heat pump air flow that goes through the
control zone.
The model then calculates the heat pump’s sensible heating
energy rate delivered to the zones being served when the
system runs at full-load conditions at the highest speed and
when the DX heating coil is OFF (without supplemental heater
operation in either case). If the supply air fan cycles with
the compressor, then the sensible heating energy rate is zero
when the compressor is OFF. However if the fan is scheduled to
run continuously regardless of coil operation, then the
sensible heating energy rate will not be zero when the
compressor is OFF. Calculating the sensible heating energy
rate involves modeling the supply air fan (and associated fan
heat), the DX cooling coil (simply to pass the air properties
and mass flow rate from its inlet node to its outlet node),
the DX heating coil, and the supplemental heating coil (simply
to pass the air properties and mass flow rate from its inlet
node to its outlet node). For each of these cases (full load
and DX heating coil OFF, without supplemental heater operation
in either case), the sensible heating energy rate delivered by
the heat pump is calculated as follows:
If the heat pump’s DX heating coil output full load at the
highest speed is insufficient to meet the entire heating load,
the remaining heating load is passed to the supplemental
heating coil. If the heat pump model determines that the
outdoor air temperature is below the minimum outdoor air
temperature for compressor operation (specified by the user),
the compressor is turned off and the entire heating load is
passed to the supplemental gas or electric heating coil. The
heat pump exiting air conditions and energy consumption are
calculated and reported by the individual component models
(fan, DX heating coil, and supplemental gas or electric
heating coil).
If the total heating load to be met by the system is less
than the sensible heating rate at the highest speed, then the
following steps are performed.
Calculate the sensible heating energy rate at Speed 1
If the sensible heating energy rate delivered by the heat
pump at Speed 1 is greater or equal to the sensible load, the
cycling ratio (part-load ratio) for the heat pump is
estimated.
AddedFanHeat = generated supply air fan heat, which is a
function of part load ratio and as internal component heating
load [W].
AddedFanHeatSpeed1 = generated supply air fan
heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX heating coil is
frequently non-linear (Ref: Single-Speed Electric Heat Pump DX
Air Heating Coil), and the supply air fan heat varies based on
heating coil operation for the case of cycling fan/cycling
coil (AUTO fan), the final part-load ratio for the heating
coil compressor and fan are determined through iterative
calculations (successive modeling of the heating coil and fan)
until the heat pump’s heating output matches the heating load
to be met within the convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the heat pump’s
heating output divided by the load to be met.
\({\dot
m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply
inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the
required heating load, the speed ratio is set to zero and
speed number is equal to 1.
If the heat pump’s heating output at full load for Speed 1
is insufficient to meet the entire heatling load, the Cycling
ratio (PartLoadRatio) is set equal to 1.0 (compressor and fan
are not cycling). Then the heating speed is increased and the
delivered sensible capacity is calculated. If the full load
sensible capacity at Speed n is greater than or equal to the
sensible load, the speed ratio for the heat pump is
estimated:
Although a linear relationship is assumed by applying the
speed ratio to obtain the effective capacity and air mass flow
rate between speed n and n-1, the outlet node conditions are
dependent on the combined outputs and may not be linear. In
addition, the supply air fan heat varies based on heating coil
operation for the case of cycling fan/cycling coil (AUTO fan).
Therefore, the final speed ratio for the heating coil
compressor and fan are determined through iterative
calculations (successive modeling of the heating coil and fan)
until the heat pump’s heating output matches the heating load
to be met within the convergence tolerance. The convergence
tolerance is fixed at 0.001 and is calculated based on the
difference between the load to be met and the heat pump’s
heating output divided by the load to be met.
Supply air fan placement impacts the iteration strategy.
When the fan placement type is blow through, the air mass flow
rate and coil part load factor (PLF) affect the fan outlet
conditions. Since the fan is upstream of the coil components
with this fan placement, the fan outlet conditions are
calculated without knowing the next component’s performance at
the beginning of each iteration. DX coil performance is
strongly dependent on the inlet conditions, so without correct
inlet conditions the DX coil components may not be simulated
correctly. Therefore, the heat pump components are called
twice for each iteration when fan placement is ‘blow through’.
The correct part load factor for the fan component is obtained
after the first call, so that the more realistic fan outlet
conditions are used to simulate the coil performance in the
second call. This extra call to the heat pump components is
not required for the draw through fan since the supply air fan
is located downstream of the DX coils with this fan
placement.
When the heat recovery is active (the value of the Design
Heat Recovery Water Flow Rate field is greater than 0), the
outlet node temperature of heat recovery is calculated based
on the recoverable waste heat generated by its child objects
(Coil:Cooling:DX:MultiSpeed and
Coil:Heating:DX:MultiSpeed):
Toutlet = outlet node temperature of heat
recovery, C
Tinlet = inlet node temperature of heat
recovery, C
QWasteHeat = recoverable waste heat generated by
its child objects, W
Cp = inlet node temperature of heat recovery,
C
\({\dot m_{hr}}\) = mass
flow rate of heat recovery, kg/s
If the outlet node temperature is above the value of the
Maximum Temp for Heat Recovery field, the outlet node
temperature is reset to the value of Maximum Temp for Heat
Recovery.
The DX cooling package subsystem model provides a “virtual”
component that consists of a DX air cooling coil component as
shown in the figure below. The CoilSystem:Cooling:DX
input object provides a container component that controls the
associated DX cooling coil which is specified in a separate
object. This coil can be specified anywhere in the air loop
simulation and is controlled by the setpoint(s) on the control
node. Optional dehumidification controls may also be
specified. CoilSystem:Cooling:DX
assumes continuous fan operation for any given time step,
because it is not able to control cycling fan operation in the
way that other AirLoopHVAC:Unitary* systems can.
This system does not need any plant specification and will
provide the electric consumption necessary to operate the
compressor and the condenser fan.
Schematic of Packaged DX
Cooling Subsystem in Air Loop for a Blow-Thru
Application
The system calculates the current sensible load using the
temperature of the inlet node and the System Node Setpoint
Temp on the control node. If the control node is not the
outlet node, the desired outlet node temperature is adjusted
for the current temperature difference between the outlet node
and the control node. Likewise, the current latent load is
calculated using the humidity ratio of the inlet node and the
System Node Humidity Ratio Max on the control node. The
controls determine the required coil run-time fraction and
dehumidification mode (if applicable) using the steps outlined
below.
The controls first attempt to meet the sensible
requirement. The specified DX coil model is called with a
part-load ratio (PLR) of 1.0 to determine the full-load output
of the coil. This is compared with the desired outlet node
temperature and a sensible PLR is calculated. If the PLR is
<1.0, a Regula-Falsi iteration routine is called to
determine the coil run-time fraction which results in the
desired outlet node temperature. For a variable-speed DX
cooling coil, if the load is smaller than the sensible
capacity at the lowest speed, the coil run-time fraction is
determined in the same way as a single-speed DX cooling coil.
Otherwise, its speed level and speed ratio between two
neighboring speeds are selected to match the load.
If the cooling coil type is specified as
CoilSystem:Cooling:DX:CoolingHeatExchanganerAssisted and the
dehumidification control type is specified as CoolReheat, the
heat exchanger is active during this attempt to meet the
sensible requirement.
If dehumidification controls are active, the leaving
humidity ratio resulting from operation to meet the sensible
load (Step 1 above) is compared with the desired outlet node
humidity ratio. If the humidity requirement is already met,
then no further control action is taken. If the humidity
requirement has not been met, then the coil is re-simulated
depending on the type of humidity control.
If the humidity control type is MultiMode, then the coil’s
enhanced dehumidification mode is activated when the coil type
is Coil:Cooling:DX:TwoStageWithHumidityControlMode
or the heat exchanger is activated when the coil type is
CoilSystem:Cooling:DX:CoolingHeatExchangerAssisted and Step 1
above is repeated to meet the sensible load using the coil
performance resulting from the enhanced dehumidificaiton mode.
This is a semi-passive approach to dehumidification which may
fall short or may exceed the dehumidification requirement. If
the user has specified Run on Latent Load = Yes in the CoilSystem:Cooling:DX
object, and there is no sensible load to be met, then the
system will try to meet the entire dehumidification load. If
dehumidification mode should not be active when there is no
sensible load, then choose Run on Latent Load = No.
If the humidity control type is CoolReheat, the coil is
re-simulated to achieve the desired outlet node humidity
ratio. This option is valid for all cooling coil types. When
the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode,
only the cooling performance mode is used for this step and
enhanced dehumidification mode is not activated.
The DX heating package subsystem model provides a “virtual”
component that consists of a DX air-to-air heating coil
component and associated controls. The CoilSystem:Heating:DX
input object provides a container component that controls the
associated DX heating coil which is specified in a separate
object. See the entry called Single-Speed and Variable-Speed
Electric Heat Pump DX Air Heating Coil for details of the coil
model itself. This coil can be specified anywhere in the air
loop simulation and is controlled by the setpoint on the
heating coil’s outlet node. This model is analogous to the
model for CoilSystem:Cooling:DX
which is similar but for cooling. The model assumes continuous
fan operation for any given time step, because it is not able
to control cycling fan operation in the way that other
AirLoopHVAC:Unitary* systems can.
This system does not need any plant specification and will
provide the electric consumption necessary to operate the
compressor and the condenser fan.
The DX heating package system calculates how the coil
should operate to meet current sensible load using the
temperature of the inlet node and the System Node Setpoint
Temp on the outlet node. The controls determine the required
coil run-time fraction to meet the sensible requirement. The
Single-Speed Electric Heat Pump DX Air Heating Coil model is
called with a part-load ratio (PLR) of 1.0 to determine the
full-load output of the coil. If the PLR is <1.0, a
Regula-Falsi iteration routine is called to determine the coil
run-time fraction which results in the desired outlet node
temperature. For a variable-speed DX heating coil, if the load
is smaller than the heating capacity at the lowest speed, the
coil run-time fraction is determined in the same way as a
single-speed DX heating coil. Otherwise, its speed level and
speed ratio between two neighboring speeds are selected to
match the load.
The input object Dehumidifier:Desiccant:System
provides a model that packages components for a
desiccant-based subsystem that dehumidifies an air stream,
normally called the process air stream. A second heated air
stream, called the regeneration air stream, is used to remove
the collected moisture from the desiccant heat exchanger and
this moisture-laden air is then usually exhausted from the
building. This Dehumidifier:Desiccant:System
object is similar to the Dehumidifier:Desiccant:NoFans
object but has some additional modeling capabilities.
The Dehumidifier:Desiccant:System
desiccant dehumidifier object in EnergyPlus is a compound
object that can be placed anywhere in an air loop. Common
locations for this object are in an AirLoopHVAC:OutdoorAirSystem
or in the main air loop downstream of a cooling coil
(postcooling desiccant dehumidifier). This compound object
coordinates the operation of several ‘children’ objects: a
desiccant heat exchanger, a regeneration air fan, and an
optional regeneration air heater. If this dehumidifier is
placed in the main air loop immediately downstream of a direct
expansion (DX) cooling coil, then the dehumidifier’s operation
can be coordinated with the operation of the companion DX coil
and it is also possible to specify that the DX system’s
condenser waste heat can be used to help regenerate the
desiccant heat exchanger. For the case of condenser waste heat
regeneration, an optional exhaust fan can also be modeled by
this desiccant dehumidifier compound object to help maintain a
setpoint temperature for air entering the regeneration side of
the desiccant heat exchanger. Refer to the EnergyPlus Input
Output Reference for the specific input syntax for this
desiccant dehumidifier object.
Schematic of a Desiccant
Dehumidifier with Draw Through Regeneration Fan
PlacementSchematic of a Desiccant
Dehumidifier in Blow Through Regeneration Fan
Placement
The model first decides if the dehumidifier can operate for
the simulation time step, based on its availability schedule
and if there is air flow detected on the process air inlet
node. If available to operate, then the target humidity ratio
for the process outlet air is determined based on the maximum
humidity ratio setpoint on the control node (System Node
Setpoint Humidity Ratio Max). If the control node is not the
process air outlet node, the target humidity ratio is adjusted
for the current humidity ratio difference between the process
air outlet node and the control node. If the humidity ratio of
the process inlet air is greater than the target humidity
ratio for the process outlet air, then the dehumidifier
operates to meet the target to the extent possible.
Once it is determined that the dehumidifier should operate,
the components upstream of the desiccant heat exchanger’s
regeneration inlet are modeled. The actual components that are
modeled depend on the configuration specified by the user.
If the waste heat from the companion cooling coil is being
used to heat the regeneration air, then this model determines
the temperature of the air leaving the cooling coil condenser.
The user may also specify a setpoint temperature for the
regeneration air entering the desiccant heat exchanger and an
optional exhaust fan, which can impact the condenser leaving
air temperature. For this case, the exhaust fan is used to
control the condenser leaving air temperature by boosting the
air flow rate through the condenser to meet the setpoint
temperature (minus regeneration fan heat if blow through fan
placement).
Note: If the desiccant dehumidifier is OFF for a simulation
time step but its companion cooling coil is operating and is
specified to provide regeneration air heating, then the
exhaust fan operates at the maximum air flow rate (i.e., this
fan serves at the condenser fan for the companion cooling coil
system when regeneration air heating is specified, so the
inputs for the companion cooling coil object should not
include the condenser fan energy since the condenser fan
energy is modeled by the
Dehumidifier:Desiccant:SystemDesiccant Dehumidifier
object).
\(PL{R_{exhaust}}\) = part
load ratio of the exhaust fan
\({\mathop {\rm{V}}\limits^
\bullet _{exhaust,\,max}}\) = exhaust fan maximum
volumetric flow rate, user input (m3/s)
\({\rho _{Std}}\) =
density of air at standard temperature and pressure [dry air
at 20°C] (m3/kg)
\({P_{exhaust,\,max}}\) =
exhaust fan maximum power, user input (W)
\(ExhFanModFac\) = exhaust
fan power modifier curve evaluated at PLRexhaust.
If modifier curve not provided by the user, then this factor
is assumed to be 1.0.
\(PL{R_{companion\,coil}}\) = part
load ratio of the companion cooling coil
\({P_{exhaust}}\) = output
variable ‘Dehumidifier Exhaust Fan Electric Power, W’
The exhaust fan electric consumption is then calculated
as:
\({E_{exhaust}}\) = output
variable ‘Dehumidifier Exhaust Fan Electric Energy, J’
\(TimeStepSys\) = HVAC
system simulation time step, hr
Once the outlet conditions from the companion coil
condenser are determined (if present), then the regeneration
air fan (if blow through configuration) and regeneration air
heater (if present) are simulated. To the extent possible
(e.g., if the heater is available to operate based on its
availability schedule and it has sufficient heating capacity),
the regeneration air heater operates to raise its outlet air
temperature to the specified regeneration inlet air setpoint
temperature.
With the inlet air conditions to the regeneration and
process sides of the desiccant heat exchanger now known, the
performance of the desiccant heat exchanger is modeled. If the
desiccant dehumidifier is specified with a companion cooling
coil upstream of the heat exchanger’s process inlet, then the
model assumes that the dehumidifier operates at the same time
as the companion coil (same part-load ratio). If not, then the
desiccant dehumidifier model calculates the fraction of time
it must operate to meet the process outlet air maximum
humidity target (setpoint) using the following equation:
\(\,DDPartLoadRatio\) =
output variable ‘Dehumidifier Part Load Ratio’
\({w_{Proc,\,\,in}}\) =
process inlet air humidity ratio (kg/kg)
\({w_{max, set\,point}}\)
= target humidity ratio (setpoint) for the process outlet air
(kg/kg)
\({w_{Proc,\,\,out,HXon}}\) =
process outlet air humidity ratio when the desiccant heat
exchanger operates (kg/kg)
After all of the desiccant dehumidifier components are
modeled at the appropriate part load ratio, the water removal
rate and water removed are calculated.
ASHRAE. 2004. Chapter 22: Desiccant Dehumidification and
Pressure-Drying Equipment. 2004 ASHRAE HVAC Systems and
Equipment Handbook. Atlanta, GA: American Society of Heating,
Refrigerating and Air-Conditioning Engineers,
Inc. http://www.ashrae.org
Kosar, D. 2006. Dehumidification Enhancements, ASHRAE
Journal, Vol. 48, No. 2, February 2006.
http://www.ashrae.org
Kosar, D. et al. 2006. Dehumidification Enhancement of
Direct Expansion Systems Through Component Augmentation of the
Cooling Coil. 15th Symposium on Improving Building
Systems in Hot and Humid Climates, July 24-26, 2006.
http://www.hothumidsymposium.org/
The input object AirLoopHVAC:UnitaryHeatPump:WaterToAir
provides a model for a water-to-Air heat pump that is a
“virtual” component that consists of an on/off fan component,
a water-to-air heat pump cooling coil, a water-to-air heat
pump heating coil, and a gas or electric supplemental heating
coil. The specific configuration of the blowthru heat pump is
shown in the following figure. For a drawthru heat pump, the
fan is located between the water-to-air heat pump heating coil
and the supplemental heating coil. The configuration of the
water-to-air heat pump in the air loop is similar to an
air-to-air heat pump. In addition, a water-to-air heat pump
has a water loop connection on its source side. The water loop
can be served by a condenser loop (like GHE for Ground source
systems), or by a cooling tower/ boiler plant loop (for water
loop systems).
Source Side and Load Side
Configuration of a BlowThru WateroToAir Heat Pump
There are two different models for water-to-air heat pump
cooling and heating coils. Cooling and heating coils are
modeled using a Single Speed or Variable Speed Equation Fit
model or a Parameter Estimation model. The parameter
estimation procedure is quite detailed and the equation fit
model is designed to simplify the user inputs. Each model is
discussed in short in the following sections. The
Variable-Speed Equation Fit model is described in a separate
section, as Coil:Cooling:WaterToAirHeatPump:VariableSpeedEquationFit
and Coil:Heating:WaterToAirHeatPump:VariableSpeedEquationFit.
This section describes the equation-fit model for
Water-to-Air heat pump (Object names: Coil:Cooling:WaterToAirHeatPump:EquationFit
and Coil:Heating:WaterToAirHeatPump:EquationFit).
This documentation is derived from the M.S. dissertation of
Tang (2005) which is available on the Oklahoma State
University web site http://www.hvac.okstate.edu/. The model
uses five non-dimensional equations or curves to predict the
heat pump performance in cooling and heating mode. The
methodology involved using the generalized least square method
to generate a set of performance coefficients from the catalog
data at indicated reference conditions. Then the respective
coefficients and indicated reference conditions are used in
the model to simulate the heat pump performance. The variables
or inlet conditions that influenced the water-to-air heat pump
performance are load side inlet water temperature, source side
inlet temperature, source side water flow rate and load side
water flow rate. The governing equations for the cooling and
heating mode are as following:
Assuming no losses, the source side heat transfer rate for
cooling and heating mode is calculated as following;
\[{Q_{source,c}} = {Q_{total}} +
Powe{r_c}\]
\[{Q_{source,h}} = {Q_h} -
Powe{r_h}\]
where:
\(A1 - F5\) = Equation fit
coefficients for the cooling and heating mode
\({T_{ref}}\) = 283K
\({T_{w,in}}\) = Entering
water temperature, K
\({T_{db}}\) = Entering
air dry-bulb temperature, K
\({T_{wb}}\) = Entering
air wet-bulb temperature, K
\({\dot V_{air}}\) = Load
side air volumetric flow rate, m3/s
\({\dot V_w}\) = Source
side water volumetric flow rate, m3/s
\({Q_{total}}\) = Total
cooling capacity, W
\({Q_{sens}}\) = Sensible
cooling capacity, W
\(Powe{r_c}\) = Power
consumption (cooling mode), W
\({Q_{source,c}}\) =
Source side heat transfer rate (cooling mode), W
\({Q_h}\) = Total heating
capacity, W
\(Powe{r_h}\) = Power
consumption (heating mode), W
\({Q_{source,h}}\) =
Source side heat transfer rate (heating mode), W
The inlet conditions or variables are divided by the
reference conditions. This formulation allows the coefficients
to fall into smaller range of values. Moreover, the value of
the coefficient indirectly represents the sensitivity of the
output to that particular inlet variable. The reference
conditions used when generating the performance coefficients
must be the same as the reference conditions used later in the
model. The reference temperature \({T_{ref}}\) is fixed at 283K.
Temperature unit of Kelvin is used instead of Celsius to keep
the ratio of the water inlet temperature and reference
temperature positive value should the water inlet temperature
drop below the freezing point.
For cooling mode, the reference conditions; reference load
side air volumetric flow rate \(\left( {{{\dot V}_{air,ref}}}
\right)\) ,reference source side water volumetric flow
rate \(\left( {{{\dot V}_{w,ref}}}
\right)\) ,reference sensible capacity \(\left( {{Q_{sens,ref}}} \right)\)
and reference power input \(\left(
{Powe{r_{c,ref}}} \right)\) are the conditions when the
heat pump is operating at the highest cooling capacity or
reference cooling capacity \(\left(
{{Q_{total,ref}}} \right)\) indicated in the
manufacturer’s catalog. Note that the reference conditions for
heating mode might differ from the reference conditions
specified for the cooling mode.
The generalized least square method is used to generate the
coefficients. This method utilizes an optimization method
which calculates the coefficients that will give the least
amount of differences between the model outputs and the
catalog data. A set of coefficients for the cooling mode is
generated which includes A1-A5 for total cooling capacity,
B1-B6 for sensible cooling capacity, and C1-C5 for power
consumption. The same procedure is repeated for the heating
mode to generate the coefficients E1-E5 and F1-F5. An
information flow chart showing the inputs, reference
conditions, performance coefficients and outputs are shown in
the figure below:
Information Flow Chart for
Water-to-Air Heat Pump Equation Fit Model (Tang
2005)
High
Humidity Control with WaterToAir HeatPump Equation Fit
model[LINK]
The specific configuration of the WaterToAir HeatPump with
supplemental heating coil is shown above (see Figure 234).
This figure shows the fan placement when a blow through fan is
specified. If a draw through fan is specified, the fan is
located between the heating coil and the reheat coil. The
system is controlled to keep the high relative humidity in the
control zone from exceeding the setpoint specified in the
object ZoneControl:Humidistat.
When high humidity control is specified and the compressor
operates, the heatpump always operates at the cooling air flow
rate when a zone heating load is present as determined by the
zone thermostat. High humidity control is specified as either
None, or CoolReheat in the Dehumidification Control Type input
field. CoolReheat is specified when a DX cooling coil is used
to over-cool the supply air stream in order to meet the zone
latent load. In this case, a supplemental heating coil will
ensure the zone temperature does not fall below the zone
heating temperature set point. If the dehumidification control
type is selected as None, the WaterToAir HeatPump uns only to
meet the sensible cooling load. A supplemental heating coil is
required for all dehumidification control types.
The model first calculates the PartLoadRatio
required meeting the sensible cooling load. The heatpump’s
sensible cooling load is determined from the control zone
sensible cooling load to the cooling setpoint and the control
zone air flow fraction to maintain the dry-bulb temperature
setpoint in the control zone:
The heatpump’s sensible cooling load to be met and the full
load cooling output are used to calculate the sensible the
part-load ratio iteratively based on user specified
convergence criterion.
When the heat pumps sensible cooling capacity meets the
system sensible cooling load at a given sensible part load
ratio, then the Heat pump meets the controlled zone cooling
setpoint temperature. If a moisture (latent) load exists
because the control zone humidity has exceeded the setpoint,
the total moisture load to be met by the heat pumps
(HeatPumpMoistureLoad) is calculated based on the control zone
moisture load and the control zone air flow fraction.
The model uses the greater of the two part-load ratios,
PartLoadRatio or LatentPartLoadRatio, to
determine the operating part-load ratio of the Heat Pump’s DX
cooling coil.
As previously described, iterations are performed to
converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\)
= the control zone sensible cooling load to the cooling
setpoint, (W).
\(ControlZoneMoistureLoad\) = the
control zone moisture load to the dehumidifying relative
humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) =
the supply air fraction that goes though the control zone,
(-).
FullLatentOutput =the Heat Pump’s latent cooling
energy rate at full-load conditions, W
NoLatentOutput =the Heat Pump’s latent cooling
energy rate with cooling coil OFF, W
\(PartLoadRatio\) =the
heat pump’s part-load-ratio required to meet system sensible
load, (-).
\(LatentPartLoadRatio\)
=the heat pump’s part-load-ratio required to meet system
moisture load, (-).
\(PL{R_{MIN}}\)=the
minimum part-load ratio, which is usually 0.0. For the case
when the latent capacity degradation model is used (Ref: DX
Cooling Coil Model), this value is the minimum part-load ratio
at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the
heating setpoint and if there is a dehumidification load, the
supplemental heating coil load is required to offset the
excess cooling as shown in Figure 236. If the model determines
that the LatentPartLoadRatio is to be used as the operating
part-load ratio of the heatpump’s cooling coil, the
supplemental coil is used to offset the excess sensible
capacity provided by the unit. The model first checks the
sensible load that exists for the current simulation time step
(predicted zone temperature with no HVAC operation compared to
the thermostat setpoint temperatures). If a sensible cooling
load or no sensible cooling or heating load exists (see Figure
236), the model calculates the difference between the sensible
heating load required to reach or maintain the heating
dry-bulb temperature setpoint and the actual sensible cooling
energy rate delivered by the heat pump (with
LatentPartLoadRatio). In this case, the supplemental heating
coil is used to offset the excess sensible cooling energy
provided by the DX cooling coil (if any) that could have
caused an overshoot of the heating dry-bulb temperature
setpoint. Note that when a humidistat is used and high
humidity control is required, the zone dry-bulb temperature
will typically move toward the heating temperature setpoint
when a high moisture (latent) load exists.
Supplemental heating coil load
when predicted zone air temperature is above the heating
Setpoint
If a heating load exists (Figure 237), the supplemental
heating coil is used to meet the heating coil load and at the
same time offset the entire sensible cooling energy rate of
the DX cooling coil (to meet the humidistat setpoint). Note
that when a heating load exists and high humidity control is
required, the heat pump operates at the user-specified cooling
air flow rate for the entire simulation time step. As with the
fan, and DX cooling coil, report variables associated with
supplemental heating coil performance (e.g., heating coil
energy, heating coil rate, heating coil gas or electric
energy, heating coil runtime fraction, etc.) are managed in
the supplemental (heating) coil object.
Supplemental heating coil load
when predicted zone air temperature is below the heating
setpoint
The steady state simulation model (Object:
AirLoopHVAC:UnitaryHeatPump:WaterToAir) for a water-to-air
vapor compression heat pump is described in this section. The
model is implemented under the air-loop manager similar to the
algorithm discussed under AirLoopHVAC:UnitaryHeatPump. The
heat pump ‘coil’ objects
(Coil:Cooling:WaterToAirHeatPump:ParameterEstimation
andCoil:Heating:WaterToAirHeatPump:ParameterEstimation)
actually consist of a steady state simulation of the unitary
heat pump in cooling or heating mode respectively. This
documentation is derived from the Ph.D. dissertation of Hui
Jin which is available on the Oklahoma State University web
site http://www.hvac.okstate.edu/. The model parameters,
solution technique and solution algorithm are all identical to
that of the water to water heat pump. The only difference
between the two models is in the modeling of the water to air
heat exchanger.
The effectiveness of this heat exchanger is given by
UA for the source side and the load side are two of the
parameters estimated in the parameter estimation
procedure.
Additional model details and a discussion of the parameters
and parameter estimation technique are described in the
following section on Water to Water Heat Pumps.
There are two water-water heat pump models available in
EnergyPlus which are parameter estimation based
model and equation-fit model.
Detailed descriptions of the model are available in the
references Tang and Jin
This section describes the equation-fit model for
water-to-water heat pump. (Object names: HeatPump:WaterToWater:EquationFit:Cooling
& HeatPump:WaterToWater:EquationFit:Heating). This
documentation is derived from the M.S. dissertation of Tang
(2005) which is available on the Oklahoma State University web
site http://www.hvac.okstate.edu/. The model uses four
non-dimensional equations or curves to predict the heat pump
performance in cooling and heating mode. The methodology
involved using the generalized least square method to generate
a set of performance coefficients from the catalog data at
indicated reference conditions. Then the respective
coefficients and indicated reference conditions are used in
the model to simulate the heat pump performance. The variables
that influenced the water-to-water heat pump performance are
load side inlet water temperature, source side inlet
temperature, source side water flow rate and load side water
flow rate. The governing equations for the cooling and heating
mode are as following:
Assuming no losses, the source side heat transfer rate for
cooling and heating mode is calculated as following;
\[{Q_{source,c}} = {Q_c} +
Powe{r_c}\]
\[{Q_{source,h}} = {Q_h} -
Powe{r_h}\]
Where:
A1 – B5 = Equation fit coefficients for the cooling and
heating mode
\({T_{ref}}\) =
283.15K
\({T_{L,in}}\) = Entering
load side water temperature, K
\({T_{S,in}}\) = Entering
source side water temperature, K
\({\dot V_L}\) = Load side
volumetric flow rate, m3/s
\({\dot V_S}\) = Source
side volumetric flow rate, m3/s
\({Q_c}\) = Load side heat
transfer rate (cooling mode), W
\(Powe{r_c}\) = Power
consumption (cooling mode), W
\({Q_{source,c}}\) =
Source side heat transfer rate (cooling mode), W
\({Q_h}\) = Load side heat
transfer rate (heating mode), W
\(Powe{r_h}\) = Power
consumption (heating mode), W
\({Q_{source,h}}\) =
Source side heat transfer rate (heating mode), W
COPc = Cooling coefficient of
performance, W/W
COPh = Heating coefficient of
performance, W/W
If the load side heat transfer rate (Qc
or Qh) or power consumption
(Powerc or Powerh) are
less than or equal to zero, then the heat pump is turned off
for that simulation time step, a warning is issued, and the
simulation continues.
The inlet conditions or variables are divided by the
reference conditions. This formulation allows the coefficients
to fall into smaller range of values. Moreover, the value of
the coefficient indirectly represents the sensitivity of the
output to that particular inlet variable. The reference
conditions used when generating the performance coefficients
must be the same as the reference conditions used later in the
model. The reference temperature \({T_{ref}}\) is fixed at 283K.
Temperature unit of Kelvin is used instead of Celsius to keep
the ratio of the water inlet temperature and reference
temperature positive value should the water inlet temperature
drop below the freezing point.
For cooling mode, the reference conditions; reference load
side volumetric flow rate, \({\dot
V_{L,ref}}\) , reference source side volumetric flow
rate, \({\dot V_{S,ref}}\) ,
\(Powe{r_{c,ref}}\) and
reference source side heat transfer rate, \({Q_{source,c,ref}}\) are the
conditions when the heat pump is operating at the highest
cooling capacity or reference cooling capacity, \({Q_{c,ref}}\) indicated in the
manufacturer’s catalog. Note that the reference conditions for
heating mode might differ from the reference conditions
specified for the cooling mode.
The generalized least square method is used to generate the
coefficients. This method utilizes an optimization method
which calculates for the coefficients that will give the least
amount of differences between the model outputs and the
catalog data. A set of coefficients for the cooling mode is
generated which includes A1-A5 for load side heat transfer.
The same procedure is repeated for the heating mode to
generate the coefficients B1-B5. An information flow chart
showing the inputs, reference conditions, performance
coefficients and outputs are shown in the figure below:
Information Flow Chart for
Water-To-Water Heat Pump Equation Fit (Tang 2005)
A steady state simulation model for a water-to-water
reciprocating vapor compression heat pump (Object names: HeatPump:WaterToWater:ParameterEstimation:Cooling
& HeatPump:WaterToWater:ParameterEstimation:Heating) is
described in this section. This documentation is derived from
the Ph.D. dissertation of Hui Jin which is available on the
Oklahoma State University web site
http://www.hvac.okstate.edu/. The model incorporates a
multivariable unconstrained optimization algorithm to estimate
several unspecific parameters. The aim of the model is to
describe the detailed physical geometry and operation of each
component and replicate the performance of the actual unit in
operation. Assuming the thermodynamic process in the expansion
device and the pressure drop at the suction and discharge
valves to be isenthalpic the heat balance equation is given
by
\[{\dot Q_s} = \dot W + {\dot
Q_{_L}}\]
Where:
\({\dot Q_s}\) = Source
side heat transfer rate
\({\dot Q_L}\) = Load side
heat transfer rate
\(\dot W\) = Compressor
power input
The compressor model is based on an isentropic process
shown in Figure 239 governed by
\(P{V^\gamma }\) =
Constant
Where:
P = Pressure
v = Specific volume
Schematic indicator diagram for
a reciprocating Compressor(Jin 2002)
Since the refrigerant vapor in the clearance volume as
shown in the previous figure goes through a re-expansion
procedure, the mass flow rate of the compressor refrigerant is
a decreasing function of the pressure ratio.
A set of parameters for the cooling mode is defined on the
basis of the equations used in the model. An information
flowchart indicating the parameters, inputs to the model and
the resulting outputs acquired are shown in Figure 240. The
estimation of parameters is conducted using the catalog
data.
The parameter definition include:
Piston displacement, PD
Clearance factor, C
Pressure drop across the suction and discharge valves,
\({\rm{\Delta P}}\)
Loss factor used to define the electromechanical losses
supposed to be proportional to the theoretical power, \({\rm{\eta }}\)
Superheat in οC or F, \({\rm{\Delta
T}}{}_{{\rm{sh}}}\)
Constant part of the electromechanical losses, \({\rm{W}}{}_{{\rm{loss}}}\)
Source side heat transfer coefficient,
(UA)S
Load side heat transfer coefficient, (UA)L
Information Flowchart for
Water-To-Water Heat Pump Parameter Estimation Mmodel
implementation (Jin 2002)
Where:
TWiL = Entering water Load side temperature
TWiS = Entering water Source side temperature
\(\mathop {\rm{m}}\limits^
\bullet {}_{{\rm{WiL}}}\) = Entering water Load side
mass flow rate
\(\mathop {\rm{m}}\limits^
\bullet {}_{{\rm{WiS}}}\) = Entering water Source side
mass flow rate
S = Thermostatic Signal
The parameter estimation procedure incorporates an
objective function that computes the difference between the
model outputs and the catalog outputs. The objective function
is then minimized by using a multi variable unconstrained
multi modal Nelder Mead optimization algorithm. As the
objective function value lowers after each iteration, the
model outputs approach the catalog outputs consequently
leading to convergence and the correct parameters are
estimated for the respective model. The inputs to the model
include the entering water temperatures and mass flow rates on
the load side and the source side. The calculation of the
objective function is shown in the form of a formula flowchart
in Figure 241. The square of the sum of the errors (SSQE) for
a given set of parameter values that will be minimized is
given by
\({\rm{W}}{}_{{\rm{cat}}}\) =
Catalog power consumption
\({\rm{W}}{}_{}\) = Model
power consumption
\({\rm{QL}}{}_{{\rm{cat}}}\) =
Catalog load side heat transfer
\({\rm{QL}}{}_{}\) = Model
load side heat transfer
Extrapolation beyond the catalog data grants the parameter
estimation model an upper hand in comparison with the equation
fit and deterministic models. However, the detailed model is
computationally more intensive. Moreover, when the model is
implemented within a transient system simulation program, it
may come across figures that are random and unplanned by the
manufacturer such as low water flow rates or extreme
temperatures. This oddity may result in unrealistic set of
results.
Flow diagram of EnergyPlus
Water to Water HeatPump implementation
Both water-to-water heat pump models; parameter estimation
based model and curve-fit model use the “cycle time control
logic” developed by Murugappan (2002).
This strategy keeps the heat pump from short-cycling
whereby the heat pump will stay on or off for the specified
cycle time after switching states. The control logic is
identical to the operation of a physical heat pump whereby the
heat pump does not switch between on and off instantly. Refer
to Muraggapan (2002) for the further details on the control
strategy.
Jin, Hui. 2002. Parameter Estimation Based Models of Water
Source Heat Pumps. Phd. Thesis, Department of Mechanical and
Aerospace Engineering, Oklahoma State University.
(downloadable from http://www.hvac.okstate.edu/)
Tang,C. C. 2005. Modeling Packaged Heat Pumps in
Quasi-Steady State Energy Simulation Program. M.S. Thesis.
Department of Mechanical and Aerospace Engineering, Oklahoma
State University. (downloadable from
http://www.hvac.okstate.edu/)
Murugappan, Arun. 2002. Implementing Ground Source Heat
Pump and Ground Loop Heat Exchanger Models in the EnergyPlus
Simulation Environment, M.S. Thesis, Department of Mechanical
and Aerospace Engineering, Oklahoma State University
(downloadable from http://www.hvac.okstate.edu/)
Air System Compound Component Groups[LINK]
Unitary Systems[LINK]
Overview[LINK]
The input object AirLoopHVAC:UnitarySystem provide a “virtual” component that collect and control a set of components: fan, heating coil, cooling coil, and/or reheat coil. Reheat coil is modeled for controlling high zone humidity levels. The unit may be configured to have either a blow through or draw through fan. In a blow through configuration, fan is generally the fist component upstream of heating ro cooling coil. In a draw through fan configuration, fan is placed directly after the heating coil and before reheat coil.
Model Description[LINK]
As described previously, the unitary system is a “virtual” component consisting of a fan, heating coil, cooling coil and reheat coil. The sole purpose of the unitary system model is to properly coordinate the operation of the various system components. The following sections describe the flow of information within the model, as well as the differences between cycling and continuous supply air fan operation.
Controls[LINK]
There are two types of control types allowed to be specified in the unitary system which are setpoint based and load based. Each control type is described in detail below.
Setpoint based control:
The unitary system calculates the current sensible load using the temperature of the inlet node and the System Node Setpoint Temp on the control node. If the control node is not the outlet node, the desired outlet node temperature is adjusted for the current temperature difference between the outlet node and the control node. Likewise, the current latent load is calculated using the humidity ratio of the inlet node and the System Node Humidity Ratio Max on the control node. The controls determine the required coil run-time fraction and dehumidification mode (if applicable) using the steps outlined below.
Step 1 - Meet Sensible Load Requirement[LINK]
The controls first attempt to meet the sensible requirement. The specified coil model is called with a part-load ratio (PLR) of 1.0 to determine the full-load output of the coil. This is compared with the desired outlet node temperature and a sensible PLR is calculated. If the PLR is <1.0, a Regula-Falsi iteration routine is called to determine the coil run-time fraction which results in the desired outlet node temperature. For a variable-speed DX cooling coil, if the load is smaller than the sensible capacity at the lowest speed, the coil run-time fraction is determined in the same way as a single-speed DX cooling coil. Otherwise, its speed number and speed ratio between two neighboring speeds are selected to match the load.
Step 2 - Meet Latent Load Requirement (if activated)[LINK]
If dehumidification controls are active, the leaving humidity ratio resulting from operation to meet the sensible load (Step 1 above) is compared with the desired outlet node humidity ratio. If the humidity requirement is already met, then no further control action is taken. If the humidity requirement has not been met, then the coil is re-simulated depending on the type of humidity control.
Step 2a - Humidity Control = MultiMode[LINK]
If the humidity control type is MultiMode, then the coil’s enhanced dehumidification mode is activated when the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode and Step 1 above is repeated to meet the sensible load using the coil performance resulting from the enhanced dehumidificaiton mode. This is a semi-passive approach to dehumidification which may fall short or may exceed the dehumidification requirement.
Step 2b - Humidity Control = CoolReheat[LINK]
If the humidity control type is CoolReheat, the coil is re-simulated to achieve the desired outlet node humidity ratio. This option is valid for all cooling coil types. When the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode, only the cooling performance mode is used for this step and enhanced dehumidification mode is not activated.
Load based control:
While the unitary system may be configured to serve multiple zones, system operation is controlled by a thermostat located in a single “control” zone. One of the key parameters for the unitary system component is the fraction of the total system air flow that goes through the control zone. This fraction is calculated as the ratio of the maximum air mass flow rate for the air loop’s supply inlet node for the control zone (e.g., AirTerminal:SingleDuct:Uncontrolled, field = Maximum Air Flow Rate, converted to mass flow) to the sum of the maximum air mass flow rates for the air loop’s supply inlet nodes for all zones served by this air loop. The unitary system module scales the calculated load for the control zone upward based on this fraction to determine the total load to be met by the unitary system. The module then proceeds to calculate the required part-load ratio for the system coil and the supply air fan to meet this total load. The heating or cooling capacity delivered by the unitary system is distributed to all of the zones served by this system via the terminal units that supply air to each zone. The supply air fraction that goes though the control zone is calculated as follows:
\[Control Zone Air Flow\,Fraction = \frac{{{{\dot m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones} {{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot m_{TUMax\,ControlledZone}}\) =maximum air mass flow rate for the air loop’s supply inlet node (terminal unit) for the control zone (kg/s)
\({\dot m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of zones, or number of air loop supply air inlet nodes for all zones served by the air loop (-)
The unitary system component is able to model supply air fan operation in two modes: cycling fan - cycling coil (i.e., AUTO fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff must be used to model AUTO fan, while Fan:OnOff or Fan:ConstantVolume can be used to model fan ON. The fan operation mode is specified using a supply air fan operating mode schedule where schedule values of 0 denote cycling fan operation and schedule values other than 0 (a 1 is usually used) denote continuous fan operation. Using this schedule, the unitary system fan may be cycled with cooling or heating coil operation or operated continuously based on time of day (e.g., cycling fan operation at night and continuous fan operation during the daytime). If the fan operating mode schedule name field is left blank in the unitary system object, the unitary system assumes cycling or AUTO fan mode operation throughout the simulation.
The unitary system operates based on the user-specified (or autosized) design supply air flow rate(s). The ‘design’ supply air mass flow rate may be different for cooling, heating, and when no cooling or heating is required and the fan operates continuously based on user-specified inputs.
Cooling Operation
If EnergyPlus determines that the unitary system must supply cooling to the control zone to meet the zone air temperature setpoint, then the model computes the total sensible cooling load to be met by the unitary system based on the control zone sensible cooling load and the fraction of the unitary system air flow that goes through the control zone.
\[UnitarySystemCoolingLoad = \frac{{ControlZoneCoolingLoad}}{{ControlZoneAirFlowFraction}}\]
If the supply air fan operating mode schedule requests cycling fan operation, the model first checks for the presence of an ecomomizer in the outside air system serving the unitary system’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an outside air system is not present or if an air-side economizer is not used, the unitary system’s compressor is used to meet the unitary system cooling load. If an air-side economizer is used and is active (i.e., economizer controls indicate that conditions are favorable to increase the outside air flow rate), the unitary system will try to meet the cooling load by operating only the supply air fan. If the fan is able to satisfy the unitary system cooling load, the compressor remains off for the entire simulation time step. If the operation of the fan alone is unable to meet the entire cooling load, then the compressor is enabled and additional calculations are performed to determine the compressor’s part-load ratio.
The model then calculates the unitary system’s sensible cooling energy rate delivered to the zones being served when the system runs at full-load conditions and when the cooling coil is OFF. If the supply air fan cycles with the compressor, then the sensible cooling energy rate is zero when the cooling coil is OFF. However if the fan is configured to run continuously regardless of coil operation, then the sensible cooling energy rate will probably not be zero when the cooling coil is OFF. Calculating the sensible cooling energy rate involves modeling the supply air fan (and associated fan heat), the cooling coil, and the heating and reheat coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and cooling coil OFF), the sensible cooling energy rate delivered by the unitary system is calculated as follows:
\[Full\;Cool\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Cool\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(Mass Flow Rate_{full load}\) = air mass flow rate through unitary system at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the unitary system at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air in the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the unitary system exiting air or the air in the control zone
\(Mass Flow Rate_{coil off}\) = air mass flow rate through the unitary system with the cooling coil OFF, kg/s
\(h_{out, coil off}\) = enthalpy of air exiting the unitary system with the cooling coil OFF, J/kg
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{coil\;off}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible cooling energy rates and the total sensible cooling load to be met by the system, the part-load ratio for the unitary system is estimated.
\[PartLoadRatio = MAX\left( {0.0,\frac{{\left( {UnitarySystemCoolingLoad - NoCoolOutput} \right)}}{{\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
Since the part-load performance of the cooling coil is frequently non-linear, and the supply air fan heat varies based on cooling coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the unitary system’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemCoolingLoad - {Q_{UnitarySystem}}} \right)}}{{UnitarySystemCoolingLoad}}\]
where:
\({Q_{UnitarySystem}}\) = Unitary system delivered sensible capacity (W)
If the unitary system has been specified with cycling fan/cycling coil (AUTO fan), then the unitary system’s operating supply air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. In this case, the air conditions at nodes downstream of the cooling coil represent the full-load (steady-state) values when the coil is operating.
If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the unitary system is calculated as the average of the user-specified air flow rate when the cooling coil is ON and the user-specified air flow rate when the cooling coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[{\mathop m\limits^ \bullet _{UnitarySystem}} = PartLoadRatio\left( {{{\mathop m\limits^ \bullet }_{CoolCoilON}}} \right) + \left( {1 - PartLoadRatio} \right)\left( {{{\mathop m\limits^ \bullet }_{CoilOFF}}} \right)\]
where:
\(\mathop m\limits^ \bullet CoolCoilON\) = air mass flow rate through unitary system when the cooling coil is ON (kg/s)
\(\mathop m\limits^ \bullet CoilOFF\) = air mass flow rate through unitary system when no cooling or heating is needed (kg/s)
In this case, the air conditions at nodes downstream of the cooling coil are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF).
Cooling Operation (multi or variable speed coils)
After the unitary system cooling load is determined as described in Eq. above, the multi or variable speed cooling coil models calculations are described in this section.
The model calculates the unitary system’s sensible cooling energy rate delivered to the zones being served when the system runs at full-load conditions at the highest speed and when the DX cooling coil is OFF. If the supply air fan cycles with the compressor, then the sensible cooling energy rate is zero when the cooling coil is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible cooling energy rate will not be zero when the cooling coil is OFF. Calculating the sensible cooling energy rate involves modeling the supply air fan (and associated fan heat) and the multi/variable speed DX cooling coil. The multi/variable speed DX heating coil and the supplemental heating coil are also modeled, but only to pass the air properties and mass flow rate from their inlet nodes to their outlet nodes. For each of these cases (full load at highest cooling speed and DX cooling coil OFF), the sensible cooling energy rate delivered by the unitary system is calculated as follows:
\(FullCoolOutpu{t_{Highest\;Speed}} = ({\dot m_{HighestSpeed}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;HighestSpeed}}\) \(NoCoolOutput = ({\dot m_{CoilOff}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\)
where:
\({\dot m_{HighestSpeed}}\) = air mass flow rate through unitary system at the highest cooling speed [kg/s]
\(h_{out,full\;load}\) = enthalpy of air exiting the unitary system at full-load conditions [J/kg]
\(h_{control\;zone}\) = enthalpy of air leaving the control zone (where thermostat is located) [J/kg]
HRmin = the minimum humidity ratio of the unitary system exiting air or the air leaving the control zone [kg/kg]
\({\dot m_{CoilOff}}\) = air mass flow rate through the unitary system with the cooling coil OFF [kg/s]
\(h_{out,coil\;off}\) = enthalpy of air exiting the unitary system with the cooling coil OFF [J/kg]
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;HighestSpeed}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad \quad + \left( {{{\dot m}_{_{HighestSpeed}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the cooling coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{coil\;off}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the unitary system’s sensible cooling rate at the highest speed (full load, no cycling) is insufficient to meet the entire cooling load, the controlled zone conditions will not be met. The reported cycling rate and speed ratio are 1, and the speed number is set to the highest index number. If the total sensible cooling load to be met by the system is less than the sensible cooling rate at the highest speed, then the following steps are performed.
Calculate the sensible cooling energy rate at Speed 1
\[FullCoolOutpu{t_{Speed1}} = ({\dot m_{Speed1}}){({h_{out,fullload}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;Speed1}}\]
where
\({\dot m_{Speed1}}\) = air mass flow rate through unitary system at Speed 1 [kg/s]
\(\Delta_{sen, Speed1}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions at Speed 1
\[\begin{array}{l}{\Delta _{sen,\;Speed1}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{Speed1}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the sensible cooling energy rate delivered by the unitary system at Speed 1 is greater or equal to the sensible load, the cycling ratio (part-load ratio) for the unitary system is estimated.
\[\begin{array}{l}CyclingRatio = \frac{{\left( {ABS(CoolingCoilSensibleLoad)} \right)}}{{FullCoolingCoilCapacity}}\\ = MAX\left( {0.0,\frac{{\left( {UnitarySystemCoolingLoad - AddedFanHeat} \right)}}{{\left( {FullCoolOutpu{t_{speed1}} - AddedFanHea{t_{speed1}}} \right)}}} \right)\end{array}\]
where
AddedFanHeat = generated supply air fan heat, which is a function of part load ratio and as internal component cooling load [W].
AddedFanHeatSpeed1 = generated supply air fan heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX cooling coil is frequently non-linear,and the supply air fan heat varies based on cooling coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the unitary system’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemOutpu{t_{cycling}} - {Q_{UnitarySystem}}} \right)}}{{UnitarySystemCoolingLoad}}\]
where:
Unitary systemOutputCycling = unitary system delivered sensible capacity for Speed 1 operating at a specific cycling ratio (W)
\[UnitarySystemOutpu{t_{cycling}} = {\mathop m\limits^ \bullet _{UnitarySystem}}{\left( {{h_{out}} - {h_{ControlZone}}} \right)_{HR\min }} - {\Delta _{cycling}}\]
where
\({\mathop m\limits^ \bullet _{UnitarySystem}}\) = average air mass flow rate defined in the next section [kg/s]
hout, = enthalpy of air exiting the unitary system at part load conditions [J/kg]
Δcycling = average sensible load difference between the system output node and the zone inlet node
\[{\Delta _{cycling}} = \frac{{{{\mathop m\limits^ \bullet }_{ZoneInlet}}}}{{frac}}\left( {{h_{ZoneInlet}} - {h_{ControlZone}}} \right) + \left( {{{\mathop m\limits^ \bullet }_{UnitarySystem}} - \frac{{{{\mathop m\limits^ \bullet }_{ZoneInlet}}}}{{frac}}} \right)\left( {{h_{Out}} - {h_{ControlZone}}} \right)\]
\({\dot m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the required cooling load, the speed ratio is set to zero and speed number is equal to 1.
If the unitary system’s cooling output at full load for Speed 1 is insufficient to meet the entire cooling load, the Cycling ratio is set equal to 1.0 (compressor and fan are not cycling). Then the cooling speed is increased and the delivered sensible capacity is calculated. If the full load sensible capacity at Speed n is greater than or equal to the sensible load, the speed ratio for the unitary system is estimated:
\[SpeedRatio = \frac{{ABS\left( {UnitarySystemCoolingLoad - AddedFanHeat - FullCoolOutpu{t_{Speedn - 1}}} \right)}}{{ABS\left( {FullCoolOutpu{t_{Speedn}} - FullCoolOutpu{t_{Speedn - 1}}} \right)}}\]
Although a linear relationship is assumed by applying the speed ratio to obtain the effective capacity and mass flow rate between speed n and n-1, the outlet air node conditions are dependent on the combined outputs and may not be linear. In addition, the supply air fan heat varies with the speed ratio due to different supply mass flow rates between speed n and n-1 . Therefore, the final speed ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the unitary system’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemCoolingLoad - UnitarySystemOutpu{t_{SpeedRatio}}} \right)}}{{UnitarySystemCoolingLoad}}\]
where:
Unitary systemOutputSpeed,n= unitary system delivered sensible capacity between two consecutive speeds at a specific speed ratio (W)
\[\begin{array}{l}UnitarySystemOutpu{t_{SpeedRatio}} = (SpeedRatio)FullCoolOutpu{t_{speedn}} + \\ (1 - SpeedRatio)FullCoolOutpu{t_{speedn - 1}} - AddedFanHea{t_{SpeedRatio}}\end{array}\]
Where
AddedFanHeatSpeedRatio= generated supply air fan heat at a specific speed ratio [W]
In this case, the reported cycling ratio is 1 and speed number is equal to n.
Air Mass Flow Rate Calculation[LINK]
Speed 1 operation
If the unitary system has been specified with cycling fan/cycling coil (AUTO fan), then the unitary system’s operating supply air mass flow rate is determined by the cycling ratio (PartLoadRatio) for Speed 1. The supply air mass flow rate is multiplied by the cycling ratio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the cooling coils represent the full-load (steady-state) values when the coil is operating.
\[{\mathop m\limits^ \bullet _{UnitarySystem}} = \left( {CyclingRatio} \right){\mathop m\limits^ \bullet _{speed1}}\]
If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the unitary system is calculated as the average of the user-specified air flow rate when the unitary system cooling coil is ON at Speed 1 and the user-specified air flow rate when the unitary system cooling coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[{\mathop m\limits^ \bullet _{UnitarySystem}} = \left( {CyclingRatio} \right){\mathop m\limits^ \bullet _{speed1}} + \left( {1 - CyclingRatio} \right){\mathop m\limits^ \bullet _{coiloff}}\]
where:
\({\mathop m\limits^ \bullet _{UnitarySystem}}\) = average air mass flow rate through unitary system [kg/s]
\({\dot m_{Speed1}}\) = air mass flow rate through unitary system when cooling coil is ON at Speed 1 [kg/s]
\({\dot m_{CoilOff}}\) = air mass flow rate through unitary system when no heating or cooling is needed [kg/s]
In this case, the air conditions at nodes downstream of the cooling coils are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF).
Higher Speed Operation[LINK]
When the unitary system operates at higher speeds to meet the required cooling load, the supply air mass flow rate is linearly interpolated between two consecutive speeds:
\[{\mathop m\limits^ \bullet _{UnitarySystem}} = \left( {SpeedRatio} \right){\mathop m\limits^ \bullet _{Speedn}} + \left( {1 - SpeedRatio} \right){\mathop m\limits^ \bullet _{Speedn - 1}}\]
where:
\({\mathop m\limits^ \bullet _{UnitarySystem}}\) = average air mass flow rate through the unitary system for the time step [kg/s]
\({\dot m_{Speed\;n}}\) = air mass flow rate through unitary system when cooling coil is ON at Speed n [kg/s]
\({\dot m_{Speed\;n - 1}}\) = air mass flow rate through unitary system when cooling coil is ON at Speed n-1 [kg/s]
For this case of higher speed operation, the air conditions at nodes downstream of the cooling coils are determined by the delivered cooling capacity and supply air mass flow rates between two consecutive speeds.
Although the above sections present the capacity and air mass flow rate calculation separately, they are dependent and change every iteration until convergence is reached for the time step being simulated.
Heating Operation
Calculations for heating operation are similar to those for cooling operation in most respects. However, due to the inclusion of a supplemental heating coil, additional calculations are necessary to properly meet the total heating load for the zones being served.
If EnergyPlus determines that the unitary system must supply heating to the control zone to meet the zone air temperature setpoint, then the unitary system model computes the total sensible heating load to be delivered to the zones being served based on the control zone sensible heating load and the control zone airflow fraction.
\[UnitarySystemHeatingLoad = \frac{{ControlZoneHeatingLoad}}{{ControlZoneAirFlowFraction}}\]
The model then calculates the unitary system’s sensible heating energy rate delivered to the zones being served when the system runs at full-load conditions and when the heating coil is OFF (without supplemental heater operation in either case). If the supply air fan cycles with the compressor, then the sensible heating energy rate is zero when the compressor is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible heating energy rate will not be zero when the compressor is OFF. Calculating the sensible heating energy rate involves modeling the supply air fan (and associated fan heat), the cooling coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node), the heating coil, and the supplemental heating coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and heating coil OFF, without supplemental heater operation in either case), the sensible heating energy rate delivered by the unitary system is calculated as follows:
\[Full\;Heat\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Heat\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(\rm{Mass Flow Rate}_{\rm{full load}}\) = air mass flow rate through unitary system at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the unitary system at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the unitary system exiting air or the air leaving the control zone
\(\rm{Mass Flow Rate}_{coil off}\) = air mass flow rate through the unitary system with the heating coil OFF, kg/s
\(h_{out, coil off}\) = enthalpy of air exiting the unitary system with the heating coil OFF, J/kg
\(\Delta_{sen, full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen, coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{coil\;off}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible heating energy rates and the total sensible heating load to be met by the system, the part-load ratio for the unitary system is estimated.
\[PartLoadRatio = MAX\left( {0.0,\frac{{\left( {UnitarySystemHeatingLoad - NoHeatOutput} \right)}}{{\left( {FullHeatOutput - NoHeatOutput} \right)}}} \right)\]
Since the part-load performance of the heating coil is frequently non-linear, and the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the unitary system’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemHeatingLoad - {Q_{UnitarySystem}}} \right)}}{{UnitarySystemHeatingLoad}}\]
where:
\({Q_{UnitarySystem}}\) = Unitary system delivered sensible capacity (W)
If the unitary system’s heating coil output at full load is insufficient to meet the entire heating load, PartLoadRatio is set equal to 1.0 (compressor and fan are not cycling) and the remaining heating load is passed to the supplemental heating coil. If the unitary system model determines that the outdoor air temperature is below the minimum outdoor air temperature for compressor operation, the compressor is turned off and the entire heating load is passed to the supplemental gas or electric heating coil. The unitary system exiting air conditions and energy consumption are calculated and reported by the individual component models (fan, heating coil, and supplemental gas or electric heating coil).
If the unitary system has been specified with cycling fan/cycling coil (AUTO fan), then the unitary system’s operating supply air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the heating coils represent the full-load (steady-state) values when the coils are operating. If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the unitary system is calculated as the average of the user-specified air flow rate when the unitary system heating coil is ON and the user-specified air flow rate when the unitary system heating coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[{\mathop m\limits^ \bullet _{UnitarySystem}} = PartLoadRatio\left( {{{\mathop m\limits^ \bullet }_{HeatCoilON}}} \right) + \left( {1 - PartLoadRatio} \right)\left( {{{\mathop m\limits^ \bullet }_{CoilOFF}}} \right)\]
where:
\(\mathop m\limits^ \bullet HeatCoilON\) = air mass flow rate through unitary system when the heating coil is ON (kg/s)
\(\mathop m\limits^ \bullet CoilOFF\) = air mass flow rate through unitary system when no heating or cooling is needed (kg/s)
In this case, the air conditions at nodes downstream of the heating coils are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coils are operating and inlet air conditions when the coils are OFF).
Heating Operation (multi or variable speed coils )[LINK]
After the unitary system heating load is determined as described in Eq. above, the multi or variable speed heating coil models calculation are described in this section.
The model calculates the unitary system’s sensible heating energy rate delivered to the zones being served when the system runs at full-load conditions at the highest speed and when the DX heating coil is OFF (without supplemental heater operation in either case). If the supply air fan cycles with the compressor, then the sensible heating energy rate is zero when the compressor is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible heating energy rate will not be zero when the compressor is OFF. Calculating the sensible heating energy rate involves modeling the supply air fan (and associated fan heat), the DX cooling coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node), the DX heating coil, and the supplemental heating coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and DX heating coil OFF, without supplemental heater operation in either case), the sensible heating energy rate delivered by the unitary system is calculated as follows:
\[FullHeatOutpu{t_{Highest\;Speed}} = ({\dot m_{HighestSpeed}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;HighestSpeed}}\]
\[NoHeatOutput = ({\dot m_{CoilOff}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\({\dot m_{HighestSpeed}}\) = air mass flow rate through unitary system at the highest heating speed [kg/s]
\(h_{out, full load}\) = enthalpy of air exiting the unitary system at full-load conditions [J/kg]
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located) [J/kg]
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the unitary system exiting air or the air leaving the control zone
\({\dot m_{CoilOff}}\) = air mass flow rate through the unitary system with the heating coil OFF [kg/s]
\(h_{out,coil off}\) = enthalpy of air exiting the unitary system with the heating coil OFF [J/kg]
\(\Delta_{sen, full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;HighestSpeed}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad \quad + \left( {{{\dot m}_{_{HighestSpeed}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen, coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{coil\;off}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the unitary system’s DX heating coil output full load at the highest speed is insufficient to meet the entire heating load, the remaining heating load is passed to the supplemental heating coil. If the unitary system model determines that the outdoor air temperature is below the minimum outdoor air temperature for compressor operation (specified by the user), the compressor is turned off and the entire heating load is passed to the supplemental gas or electric heating coil. The unitary system exiting air conditions and energy consumption are calculated and reported by the individual component models (fan, DX heating coil, and supplemental gas or electric heating coil).
If the total heating load to be met by the system is less than the sensible heating rate at the highest speed, then the following steps are performed.
Calculate the sensible heating energy rate at Speed 1
\[FullHeatOutpu{t_{Speed1}} = ({\dot m_{Speed1}}){({h_{out,fullload}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;Speed1}}\]
where:
\({\dot m_{Speed1}}\) = air mass flow rate through unitary system at Speed 1 [kg/s]
\(\Delta_{sen, Speed1}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions at Speed 1
\[\begin{array}{l}{\Delta _{sen,\;Speed1}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{Speed1}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the sensible heating energy rate delivered by the unitary system at Speed 1 is greater or equal to the sensible load, the cycling ratio (part-load ratio) for the unitary system is estimated.
\[\begin{array}{l}CyclingRatio = \frac{{\left( {ABS(HeatingCoilSensibleLoad)} \right)}}{{FullHeatingCoilCapacity}} \\ = MAX\left( {0.0,\frac{{\left( {UnitarySystemHeatingLoad - AddedFanHeat} \right)}}{{\left( {FullHeatOutpu{t_{speed1}} - AddedFanHea{t_{speed1}}} \right)}}} \right)\end{array}\]
where
AddedFanHeat= generated supply air fan heat, which is a function of part load ratio and as internal component heating load [W].
AddedFanHeatSpeed1= generated supply air fan heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX heating coil is frequently non-linear, and the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the unitary system’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemHeatingLoad - UnitarySystemOutpu{t_{cycling}}} \right)}}{{UnitarySystemHeatingLoad}}\]
where:
Unitary systemOutputCycling= unitary system delivered sensible capacity for Speed 1 operating at a specific cycling ratio (W)
\[UnitarySystemOutpu{t_{cycling}} = {\mathop m\limits^ \bullet _{UnitarySystem}}{\left( {{h_{out}} - {h_{ControlZone}}} \right)_{HR\min }} - {\Delta _{cycling}}\]
where
\({\mathop m\limits^ \bullet _{UnitarySystem}}\) = average air mass flow rate defined in the next section [kg/s]
hout, = enthalpy of air exiting the unitary system at part load conditions [J/kg]
Δcycling = average sensible load difference between the system output node and the zone inlet node
\[{\Delta _{cycling}} = \frac{{{{\mathop m\limits^ \bullet }_{ZoneInlet}}}}{{frac}}\left( {{h_{ZoneInlet}} - {h_{ControlZone}}} \right) + \left( {{{\mathop m\limits^ \bullet }_{UnitarySystem}} - \frac{{{{\mathop m\limits^ \bullet }_{ZoneInlet}}}}{{frac}}} \right)\left( {{h_{Out}} - {h_{ControlZone}}} \right)\]
\({\dot m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the required heating load, the speed ratio is set to zero and speed number is equal to 1.
If the unitary system’s heating output at full load for Speed 1 is insufficient to meet the entire heatling load, the Cycling ratio (PartLoadRatio) is set equal to 1.0 (compressor and fan are not cycling). Then the heating speed is increased and the delivered sensible capacity is calculated. If the full load sensible capacity at Speed n is greater than or equal to the sensible load, the speed ratio for the unitary system is estimated:
\[SpeedRatio = \frac{{ABS\left( {UnitarySystemHeatingLoad - AddedFanHeat - FullHeatOutpu{t_{Speedn - 1}}} \right)}}{{ABS\left( {FullHeatOutpu{t_{Speedn}} - FullHeatOutpu{t_{Speedn - 1}}} \right)}}\]
Although a linear relationship is assumed by applying the speed ratio to obtain the effective capacity and air mass flow rate between speed n and n-1, the outlet node conditions are dependent on the combined outputs and may not be linear. In addition, the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan). Therefore, the final speed ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the unitary system’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the unitary system’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {UnitarySystemHeatingLoad - UnitarySystemOutpu{t_{SpeedRatio}}} \right)}}{{UnitarySystemHeatingLoad}}\]
where:
UnitarySystemOutputSpeedRatio= unitary system delivered sensible capacity between two consecutive speeds at a specific ratio [W]
\[\begin{array}{l}UnitarySystemOutpu{t_{SpeedRatio}} = (SpeedRatio)FullHeatOutpu{t_{speedn}} + \\ (1 - SpeedRatio)FullHeatOutpu{t_{speedn - 1}} - AddedFanHea{t_{SpeedRatio}}\end{array}\]
Where
AddedFanHeatSpeedRatio= generated supply air fan heat at a specific speed ratio [W]
In this case, the reported cycling ratio is 1 and speed number is equal to n.
Air Mass Flow Rate Calculation[LINK]
The air mass flow rate calculations during heating operation are the same as those described above for cooling operation for multi/variable speed.
High Humidity Control[LINK]
The specific configuration of the unitary system with supplemental heating coil is shown above (see Figure 227). This figure shows the fan placement when a blow through fan is specified. If a draw through fan is specified, the fan is located between the heating coil and the supplemental heating coil. The system is controlled to keep the high relative humidity in the control zone from exceeding the setpoint specified in the object ZoneControl:Humidistat. This option is available when the supply air fan operates continuously (i.e., the supply air fan operating mode schedule values are never equal to 0) or the supply air fan cycles with the compressor. In addition, when high humidity control is specified and the compressor operates, the unitary system operates at the cooling air flow rate when a zone heating load is present as determined by the zone thermostat. High humidity control is specified as either None, MultiMode, or CoolReheat in the Dehumidification Control Type input field. MultiMode is specified when a heat exchanger is used to improve the dehumidification performance of the cooling coil. The heat exchanger will be activated when the sensible part-load ratio is insufficient to meet the zone latent load. CoolReheat is specified when a cooling coil is used to over-cool the supply air stream in order to meet the zone latent load. In this case, a supplemental heating coil will ensure the zone temperature does not fall below the zone heating temperature set point. When a heat exchanger is used in conjunction with a cooling coil and CoolReheat is specified as the Dehumidification Control Type, the heat exchanger is “locked on” to meet either the sensible or latent cooling load. If the dehumidification control type is selected as None and a heat exchanger assisted cooling coil is used, the heat exchanger is “locked on” and the air conditioner runs only to meet the sensible cooling load. A supplemental heating coil is required for all dehumidification control types.
The model first calculates the PartLoadRatio required to meet the sensible cooling load. The unitary system’s sensible cooling load is determined from the control zone sensible cooling load to the cooling setpoint and the control zone air flow fraction to maintain the dry-bulb temperature setpoint in the control zone.:
\[UnitarySystemCoolingLoad = \frac{{ControlZoneCoolingLoad}}{{ControlZoneAirFlowFraction}}\]
The unitary system’s sensible cooling load to be met and the full load cooling output are used to calculate the sensible the part-load ratio iteratively based on user specified convergence criterion.
\[PartLoadRatio = MAX\left( {0.0,\frac{{\left( {UnitarySystemCoolingLoad - NoCoolOutput} \right)}}{{\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
hen the unitary system’s sensible cooling capacity meets the system sensible cooling load at a given sensible part load ratio, then the Unitary system meets the controlled zone cooling setpoint temperature. If a moisture (latent) load exists because the control zone humidity has exceeded the setpoint, the total moisture load to be met by the unitary systems (Unitary systemMoistureLoad) is calculated based on the control zone moisture load and the control zone air flow fraction.
\[UnitarySystemMoistureLoad = \frac{{ControlZoneMoistureLoad}}{{ControlZoneAirFlowFraction}}\]
Then the LatentPartLoadRatio required to meet the high humidity setpoint is calculated as follows:
\(LatentPartLoadRatio = MIN\left( {PL{R_{Min}},\frac{{\left( {UnitarySystemMoistureLoad - NoLatentOutput} \right)}}{{\left( {FullLatentOutput - NoLatentOutput} \right)}}} \right)\) The model uses the greater of the two part-load ratios, PartLoadRatio or LatentPartLoadRatio, to determine the operating part-load ratio of the Unitary system’s DX cooling coil.
\[LatentPartLoadRatio = MAX\left( {PartLoadRatio,LatentPartLoadRatio} \right)\]
As previously described, iterations are performed to converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\) = the control zone sensible cooling load to the cooling setpoint, (W).
\(ControlZoneMoistureLoad\) = the control zone moisture load to the dehumidifying relative humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) = the supply air fraction that goes though the control zone, (-).
\(FullLatentOutput\) = the Unitary system’s latent cooling energy rate at full-load conditions, W
\(NoLatentOutput\) = the Unitary system’s latent cooling energy rate with cooling coil OFF, W
\(PartLoadRatio\) = the unitary system’s part-load-ratio required to meet system sensible load, (-).
\(LatentPartLoadRatio\) = the unitary system’s part-load-ratio required to meet system moisture load, (-).
\(PL{R_{Min}}\) = the minimum part-load ratio, which is usually 0.0. For the case when the latent capacity degradation model is used (Ref: DX Cooling Coil Model), this value is the minimum part-load ratio at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the heating setpoint and if there is a dehumidification load, the supplemental heating coil load is required to offset the excess cooling as shown in Figure 228. If the model determines that the LatentPartLoadRatio is to be used as the operating part-load ratio of the unitary system’s cooling coil, the supplemental heating coil is used to offset the excess sensible capacity provided by the unitary system cooling coil. The model first checks the sensible load that exists for the current simulation time step (predicted zone temperature with no HVAC operation compared to the thermostat setpoint temperatures). If a sensible cooling load or no sensible cooling or heating load exists, the model calculates the difference between the sensible heating load required to reach or maintain the heating dry-bulb temperature setpoint and the actual sensible cooling energy rate delivered by the unit (with LatentPartLoadRatio). In this case, the supplemental heating coil is used to offset the excess sensible cooling energy provided by the cooling coil (if any) that could have caused an overshoot of the heating dry-bulb temperature setpoint. Note that when a humidistat is used and high humidity control is required, the zone dry-bulb temperature will typically move toward the heating temperature setpoint when a high moisture (latent) load exists.
If a heating load exists (Figure 229), the supplemental heating coil is used to meet the heating coil load and at the same time offset the entire sensible cooling energy rate of the cooling coil (to meet the humidistat setpoint). Note that when a heating load exists and high humidity control is required, the unitary system operates at the user-specified cooling air flow rate for the entire simulation time step. As with the fan, and cooling coil, report variables associated with supplemental heating coil performance (e.g., heating coil energy, heating coil rate, heating coil gas or electric energy, heating coil runtime fraction, etc.) are managed in the supplemental (heating) coil object.
Waste Heat Calculation[LINK]
Waste heat calculations are done when the multi speed cooling and heating coils are specified in the unitary system and the heat recovery is active (the value of the Design Heat Recovery Water Flow Rate field is greater than 0), the outlet node temperature of heat recovery is calculated based on the recoverable waste heat generated by the child objects Coil:Cooling:DX:MultiSpeed and Coil:Heating:DX:MultiSpeed:
\[{T_{outlet}} = {T_{inlet}} + \frac{{{Q_{WasteHeat}}}}{{{C_p}{{\dot m}_{hr}}}}\]
where
Toutlet = outlet node temperature of heat recovery, C
Tinlet = inlet node temperature of heat recovery, C
QWasteHeat = recoverable waste heat generated by its child objects, W
Cp = inlet node temperature of heat recovery, C
\({\dot m_{hr}}\) = mass flow rate of heat recovery, kg/s
If the outlet node temperature is above the value of the Maximum Temp for Heat Recovery field, the outlet node temperature is reset to the value of Maximum Temp for Heat Recovery.
Forced-Air Furnace and Central Air Conditioning[LINK]
Overview[LINK]
The input objects AirLoopHVAC:Unitary:Furnace:HeatOnly and AirLoopHVAC:Unitary:Furnace:HeatCool provide a “virtual” component that collect and control a set of components: an on/off or constant volume fan component and a gas or electric heating coil component. If the HeatCool version is selected, then a DX cooling coil is also modeled as part of the system as shown in Figure 221 below. For the HeatCool version, an optional reheat coil may also be modeled for controlling high zone humidity levels and the furnace’s configuration when specifying this option is shown in Figure 222 below. The unit may be configured to have either a blow through or draw through fan. If a blow through fan configuration is specified, the furnace fan is placed before the heating coil for the HeatOnly version, or before the cooling coil for the HeatCool version as shown in the figure below. If a draw through fan configuration is specified, the fan is placed directly after the heating coil.
While the furnace may be configured to serve multiple zones, system operation is controlled by a thermostat located in a single “control” zone. One of the key parameters for the furnace component is the fraction of the total system air flow that goes through the control zone. This fraction is calculated as the ratio of the maximum air mass flow rate for the air loop’s supply inlet node for the control zone (e.g., AirTerminal:SingleDuct:Uncontrolled, field = Maximum Air Flow Rate, converted to mass flow) to the sum of the maximum air mass flow rates for the air loop’s supply inlet nodes for all zones served by this air loop. The furnace module scales the calculated load for the control zone upward based on this fraction to determine the total load to be met by the furnace. The module then proceeds to calculate the required part-load ratio for the system coil and the supply air fan to meet this total load. The heating or cooling capacity delivered by the furnace is distributed to all of the zones served by this system via the terminal units that supply air to each zone. The supply air fraction that goes though the control zone is calculated as follows:
\[Control Zone Air Flow\,Fraction = \frac{{{{\dot m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones} {{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot m_{TUMax\,ControlledZone}}\) =maximum air mass flow rate for the air loop’s supply inlet node (terminal unit) for the control zone (kg/s)
\({\dot m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of zones, or number of air loop supply air inlet nodes for all zones served by the air loop (-)
The furnace component is able to model supply air fan operation in two modes: cycling fan - cycling coil (i.e., AUTO fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff must be used to model AUTO fan, while Fan:OnOff or Fan:ConstantVolume can be used to model fan ON. The fan operation mode is specified using a supply air fan operating mode schedule where schedule values of 0 denote cycling fan operation and schedule values other than 0 (a 1 is usually used) denote continuous fan operation. Using this schedule, the furnace fan may be cycled with cooling or heating coil operation or operated continuously based on time of day (e.g., cycling fan operation at night and continuous fan operation during the daytime). If the fan operating mode schedule name field is left blank in the furnace object, the furnace assumes cycling or AUTO fan mode operation throughout the simulation.
The only output variables reported by the furnace object are the fan part-load ratio and the compressor part-load ratio (HeatCool only). The fan part-load ratio is defined as the actual air mass flow rate through the system for the time step divided by the design supply air mass flow rate specified for the furnace (\(\dot{m}_{actual} / \dot{m}_{design}\)). The furnace operates based on the user-specified (or autosized) design supply air flow rate(s). The ‘design’ supply air mass flow rate may be different for cooling, heating, and when no cooling or heating is required and the fan operates continuously based on user-specified inputs (HeatCool only). For the HeatCool version, If alternate air flow rates are specified for cooling, heating, and when no cooling or heating is required, the design supply air mass flow rate is the maximum of these specified values. Also for the HeatCool version, the compressor part-load ratio is reported as the ratio of the actual cooling load to the full-load sensible capacity (see Eqn. ). Reporting of other variables of interest for the furnace (heating rate, cooling rate, energy consumption, etc.) is done by the individual system components (fan, heating coil and DX cooling coil).
Model Description[LINK]
As described previously, the furnace is a “virtual” component consisting of a fan, heating coil and, for the HeatCool version, a cooling coil with an optional reheat coil. The sole purpose of the furnace model is to properly coordinate the operation of the various system components. The following sections describe the flow of information within the model for both the HeatOnly and HeatCool configurations, as well as the differences between cycling and continuous supply air fan operation. The last section describes the optional control of high zone humidity with a reheat coil for the HeatCool configuration.
HeatOnly Configuration[LINK]
The HeatOnly configuration consists of an on/off or constant volume fan and an electric or gas heating coil. When the model is first called during an EnergyPlus simulation, all of the input data specified for each furnace in the input data file are read into data structures for use throughout the remainder of the simulation.
For each simulation time step when the performance of a heat-only furnace is being modeled, the first step is to retrieve the heating load required to meet the thermostat setpoint for the “control” zone (see Figure 221. Schematic of the EnergyPlus Furnace). See the section “Summary of Predictor-Corrector Procedure” elsewhere in this document for more details regarding load calculations. Since the furnace may be specified to serve several zones but controlled based on the load calculated for the “control” zone, the total heating load to be met by the furnace is determined from the following equation:
\[Furnace\,Heating\,Load\, = \frac{{Control\,Zone\,Heating\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
The model then calculates the furnace’s sensible heating energy rate delivered to the zones being served when the system runs at full-load conditions and when the heating coil is OFF. If the supply air fan cycles on and off with the heater, then the sensible heating energy rate is zero when the heating coil is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible heating energy rate will not be zero when the heating coil is OFF. Calculating the sensible heating energy rate involves modeling the supply air fan (and associated fan heat) and the heating coil. For each of these cases (full load and heating coil OFF), the sensible heating energy rate delivered by the furnace is calculated as follows:
\[Full\;Heat\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Heat\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(Mass Flow Rate_{full load}\) = air mass flow rate through furnace at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the furnace at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air in the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the furnace exiting air or the air in the control zone
\(Mass Flow Rate_{coil off}\) = air mass flow rate through the furnace with the heating coil OFF, kg/s
\(h_{out, coil off}\) = enthalpy of air exiting the furnace with the heating coil OFF, J/kg
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{_{Out,\;full\;load}}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{Zone\;Inlet}}}}{{Frac}}{\left( {{h_{Out,coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \; + \left( {Mass\;Flow\;Rat{e_{coil\;off}} - \frac{{Mass\;Flow\;Rat{e_{Zone\;Inlet}}}}{{Frac}}} \right){\left( {{h_{Out,coil\;off}} - {h_{Control\;Zone}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible heating energy rates and the total sensible heating load to be met by the system, the part-load ratio for the furnace is estimated.
\[PartLoadRatio\, = \,MAX\left( {0.0,MIN\left( {1.0,\frac{{ABS\left( {FurnaceHeatingLoad - NoHeatOutput} \right)}}{{ABS(FullHeatOutput - NoHeatOutput)}}} \right)} \right)\]
The part-load ratio calculated above is used to determine the required heating coil capacity as \(Qheating\,coil = Qdesign\,*PartLoadRatio\) where Qdesign is the nominal heating coil capacity as specified in the heating coil object. If the fan cycles on and off with the heating coil (i.e., when the supply air fan operating mode schedule values are equal to 0), then this part-load ratio is also used to determine the operating mass flow rate of the furnace as
\[{\dot m_{furnace}} = {\dot m_{design}}*PartLoadRatio\]
If the fan operates continuously (i.e. fan ON), the operating mass flow rate is specified as \({\dot m_{design}}\) . The furnace’s fan and heating coil are then re-simulated to determine the furnace’s delivered sensible heating capacity at the above calculated part-load ratio.
\[{Q_{furnace}} = \left( {{{\dot m}_{furnace}}} \right){\left( {{h_{out,actual}} - {h_{control\;zone}}} \right)_{HR\min }} - {\Delta _{sen,\;actual}}\]
where:
\(Qfurnace\) = sensible heating capacity delivered by the furnace (W)
\({\dot m_{furnace}}\) = air mass flow rate through the furnace (kg/s)
\(h_{\rm{out,actual}}\) = enthalpy of air exiting the furnace (J/kg)
\(h_{\rm{out,control zone}}\) = enthalpy of air in the control zone (J/kg)
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the furnace exiting air or the air in the control zone
\(\Delta_{\rm{sen,actual}}\) = Sensible load difference between the system output node and the zone inlet node at the above calculated part-load ratio.
\[\begin{array}{l}{\Delta _{sen,\;actual}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;actual}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{furnace}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;actual}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
Since the part-load performance of the heating coil can be non-linear, and the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the heating coil and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the furnace’s heating output matches the heating load to be met within the heating convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the furnace’s heating output divided by the load to be met.
\[Tolerance = \frac{FurnaceHeatingLoad - Q_{furnace}}{FurnaceHeatingLoad} = 0.001\]
If the furnace has been specified with cycling fan/cycling coil (AUTO fan), then the furnace’s design air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the heating coil represent the full-load (steady-state) values when the coil is operating. If the supply air fan is specified to run continuously (fan ON), then the air mass flow rate remains at the furnace’s design air mass flow rate. In this case, the air conditions at nodes downstream of the heating coil are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF).
For the case where the furnace is scheduled to operate with continuous supply air fan operation, but no heating load is required to meet the setpoint temperature in the control zone, the supply air fan model is still called to determine the fan exiting air conditions. The heating coil model is also called, but for the case with no heating load the heating coil model simply passes the inlet air conditions and mass flow rate from its inlet node to its outlet node. The air exiting the heating coil is then sent to the direct air units for distribution to each zone served by the furnace, where the zone heat balance is performed to determine the resulting zone air conditions. The furnace exiting air conditions and energy consumption are calculated and reported by the individual component models (fan and heating coil).
HeatCool Configuration[LINK]
The HeatCool configuration consists of an on/off or constant volume fan, a DX cooling coil, and an electric or gas heating coil. For the cases where a heating load is calculated for the control zone or no heating/cooling load is calculated for the control zone, the model follows nearly identical computational steps as described in the HeatOnly Configuration section above. The only difference is the air mass flow rate during no cooling/heating operation with continuous supply air fan operation can be different from the air mass flow rate during heater operation for the HeatCool configuration. If a cooling load is calculated by EnergyPlus for the control zone, the solution methodology is also virtually identical and is described here for completeness.
If EnergyPlus determines that the furnace must supply cooling to the control zone to meet the zone air temperature setpoint, then the model computes the total sensible cooling load to be met by the furnace based on the control zone sensible cooling load and the fraction of the furnace air flow that goes through the control zone.
\[Furnace\,Cooling\,Load\, = \frac{{Control\,Zone\,Cooling\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
If the supply air fan operating mode schedule requests cycling fan operation, the model first checks for the presence of an ecomomizer in the outside air system serving the furnace’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an outside air system is not present or if an air-side economizer is not used, the furnace’s compressor is used to meet the furnace cooling load. If an air-side economizer is used and is active (i.e., economizer controls indicate that conditions are favorable to increase the outside air flow rate), the furnace will try to meet the cooling load by operating only the supply air fan. If the fan is able to satisfy the furnace cooling load, the compressor remains off for the entire simulation time step. If the operation of the fan alone is unable to meet the entire cooling load, then the compressor is enabled and additional calculations are performed to determine the compressor’s part-load ratio.
The model then calculates the furnace’s sensible cooling energy rate delivered to the zones being served when the system runs at full-load conditions and when the DX cooling coil is OFF. If the supply air fan cycles with the compressor, then the sensible cooling energy rate is zero when the cooling coil is OFF. However if the fan is configured to run continuously regardless of coil operation, then the sensible cooling energy rate will probably not be zero when the cooling coil is OFF. Calculating the sensible cooling energy rate involves modeling the supply air fan (and associated fan heat), the DX cooling coil, and the heating coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and DX cooling coil OFF), the sensible cooling energy rate delivered by the furnace is calculated as follows:
\[Full\;Cool\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Cool\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(Mass Flow Rate_{full load}\) = air mass flow rate through furnace at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the furnace at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air in the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the furnace exiting air or the air in the control zone
\(Mass Flow Rate_{coil off}\) = air mass flow rate through the furnace with the cooling coil OFF, kg/s
\(h_{out, coil off}\) = enthalpy of air exiting the furnace with the cooling coil OFF, J/kg
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{coil\;off}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible cooling energy rates and the total sensible cooling load to be met by the system, the part-load ratio for the furnace is estimated.
\[PartLoadRatio\, = \,MAX\left( {0.0,\frac{{ABS\left( {Furnace\,Cooling\,Load - NoCoolOutput} \right)}}{{ABS\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
Since the part-load performance of the DX cooling coil is frequently non-linear (Ref: DX Cooling Coil Model), and the supply air fan heat varies based on cooling coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the furnace’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the furnace’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{FurnaceCoolingLoad - Q_{furnace}}{FurnaceCoolingLoad}\]
where:
\(Qfurnace\) = Furnace delivered sensible capacity (W)
If the furnace has been specified with cycling fan/cycling coil (AUTO fan) and high humidity control has not been specified, then the furnace’s operating supply air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the cooling coil represent the full-load (steady-state) values when the coil is operating. If a cycling fan is used and high humidity control has been specified, the calculation of average air mass flow rate is based on the greater of the heating or cooling part-load ratio (see following section on high humidity control). When the heating part-load ratio is greater than the cooling part-load ratio, the air conditions at nodes downstream of the cooling coil represent the weighted average of full-load conditions when the cooling coil is operating and inlet air conditions when the cooling coil is off (i.e., the fan continues to operate due to a heating requirement where the heating PLR is greater than the cooling PLR). If the supply air fan is specified to run continuously (fan ON), then the air mass flow rate continues to operate at the user-specified supply air mass flow rate when no cooling or heating is required. In this case, the air conditions at nodes downstream of the cooling coil are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF). The furnace exiting air conditions and energy consumption are calculated and reported by the individual component models (fan and DX cooling coil).
High Humidity Control with HeatCool Configuration[LINK]
An optional reheat coil can be specified with the HeatCool configuration to allow the furnace to control high zone humidity levels. The specific configuration of the HeatCool Furnace with high humidity control option is shown in Figure 222. The figure below shows the fan placement when a blow through fan is specified. If a draw through fan is specified, the fan is located between the heating coil and the reheat coil. The system is controlled to keep the relative humidity in the control zone from exceeding the setpoint specified in the object ZoneControl:Humidistat. This option is available when the supply air fan operates continuously (i.e., the supply air fan operating mode schedule values are never equal to 0) or the supply air fan cycles with the compressor. For the case of cycling fan mode when the high humidity control is specified as CoolReheat and the heating part-load ratio is greater than the compressor part-load ratio, the air conditions at nodes downstream of the cooling coil are calculated as the average conditions during the duration of fan operation (i.e., the weighted average of full load conditions when the coil is operating and inlet air conditions when the coil is off and the fan continues to operate to meet the heating load). For the case where cycling fan mode is used and the heating part-load ratio is less than the compressor part-load ratio, the air conditions at the nodes downstream of the cooling coil are simply the full load (steady-state) values when the coil is operating. In addition, when high humidity control is specified and the compressor operates, the furnace operates at the cooling air flow rate when a zone heating load is present as determined by the zone thermostat.
High humidity control is specified as either None, MultiMode, or CoolReheat in the Dehumidification Control Type input field. MultiMode is specified when a heat exchanger is used to improve the dehumidification performance of the cooling coil. The heat exchanger will be activated when the sensible part-load ratio is insufficient to meet the zone latent load. CoolReheat is specified when a DX cooling coil is used to over-cool the supply air stream in order to meet the zone latent load. In this case, a reheat coil will ensure the zone temperature does not fall below the zone heating temperature set point. When a heat exchanger is used in conjunction with a DX cooling coil and CoolReheat is specified as the Dehumidification Control Type, the heat exchanger is “locked on” to meet either the sensible or latent cooling load. If the dehumidification control type is selected as None and a heat exchanger assisted cooling coil is used, the heat exchanger is “locked on” and the air conditioner runs only to meet the sensible cooling load. Although a reheat coil is required when CoolReheat is specified in the Dehumidification Control Type input field, this reheat coil may optionally be present for the other Dehumidification Control Types (e.g., None and Multimode). If the reheat coil is present and the dehumidification control type input is not specified as CoolReheat, the reheat coil will not be active. This allows changing the dehumidification control option without requiring a change in the unit’s coil configuration.
The model first calculates the PartLoadRatio required to meet the sensible cooling load as described above (see Eqn. ) to maintain the dry-bulb temperature setpoint in the control zone. If a moisture (latent) load exists because the control zone humidity has exceeded the setpoint, the total moisture load to be met by the HeatCool furnace (SystemMoistureLoad) is calculated based on the control zone moisture load and the control zone air flow fraction. The model then calculates the LatentPartLoadRatio required to meet the humidistat setpoint.
\[SystemMoistureLoad\, = \frac{{Control\,Zone\,Moisture\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
\[LatentPartLoadRatio\, = \,MAX\left( {MinPLR,\frac{{ABS\left( {SystemMoistureLoad - NoLatentOutput} \right)}}{{ABS\left( {FullLatentOutput - NoLatentOutput} \right)}}} \right)\]
where:
FullLatentOutput = the furnace’s latent cooling energy rate at full-load conditions, W
NoLatentOutput = the furnace’s latent cooling energy rate with the cooling coil OFF, W
MinPLR= the minimum part-load ratio, which is usually 0.0. For the case when the latent capacity degradation model is used (Ref: DX Cooling Coil Model), this value is the minimum part-load ratio at which the cooling coil will dehumidify the air.
The model uses the greater of the two part-load ratios, PartLoadRatio or LatentPartLoadRatio, to determine the operating part-load ratio of the furnace’s DX cooling coil. As previously described, iterations are performed to converge on the solution within the convergence tolerance.
If the model determines that the LatentPartLoadRatio is to be used as the operating part-load ratio of the furnace’s cooling coil, the reheat coil is used to offset the excess sensible capacity provided by the unit. The model first checks the sensible load that exists for the current simulation time step (predicted zone temperature with no HVAC operation compared to the thermostat setpoint temperatures). If a sensible cooling load or no sensible cooling or heating load exists (Figure 223), the model calculates the difference between the sensible heating load required to reach or maintain the heating dry-bulb temperature setpoint and the actual sensible cooling energy rate delivered by the unit (with LatentPartLoadRatio). In this case, the reheat coil is used to offset the excess sensible cooling energy provided by the DX cooling coil (if any) that could have caused an overshoot of the heating dry-bulb temperature setpoint. Note that when a humidistat is used and high humidity control is required, the zone dry-bulb temperature will typically move toward the heating temperature setpoint when a high moisture (latent) load exists. If a heating load exists (Figure 224), the reheat coil is used to offset the entire sensible cooling energy rate of the DX cooling coil (to meet the humidistat setpoint) and the heating coil is used to meet the entire heating load as described in the HeatOnly configuration section above. Note that when a heating load exists and high humidity control is required, the furnace operates at the user-specified cooling air flow rate for the entire simulation time step. As with the fan, DX cooling coil, and heating coil, report variables associated with reheat coil performance (e.g., heating coil energy, heating coil rate, heating coil gas or electric consumption, heating coil runtime fraction, etc.) are managed in the reheat (heating) coil object.
Unitary Systems[LINK]
The input objects AirLoopHVAC:UnitaryHeatCool and AirLoopHVAC:UnitaryHeatOnly provides models that are identical to the Furnace and Central Air models described above. Please reference the previous section for details.
Unitary System with Changeover-Bypass-Variable Air Volume[LINK]
Overview[LINK]
The input object AirLoopHVAC:UnitaryHeatCool:VAVChangeoverBypass provides a model for a changeover-bypass variable air volume (CBVAV) unitary system that is a compound object made up of other components. Each CBVAV system consists of an outside air mixer, direct expansion (DX) cooling coil, heating coil, and a supply air fan as shown in the figures below. Zone thermostats and terminal units are required in each zone served by this system. The terminal units are specific to this system type and are either AirTerminal:SingleDuct:VAV:HeatAndCool:Reheat or AirTerminal:SingleDuct:VAV:HeatAndCool:NoReheat. A zone humidistat and single zone max humidity setpoint manager may also be specified to help control high humidity levels. These individual components are described elsewhere in this document. The CBVAV unitary system object coordinates the operation of these components and is modeled as a type of air loop equipment (Ref. AirLoopHVAC).
The CBVAV unitary system conditions one or more zones and is controlled by thermostats located in each zone (the use of a single humidistat is also allowed when using multi-mode DX cooling coils). The CBVAV system operates to meet the zone sensible cooling or sensible heating requirements as dictated by the thermostat schedule(s). The priority control input determines the mode of operation and is specified as Cooling Priority, Heating Priority, or Zone Priority. If Cooling Priority is specified, the system operates to meet the cooling load when any zone served by this system (air loop) requires cooling. If Heating Priority is specified, the system operates to meet the heating load when any zone requires heating. If Zone Priority is specified, the system operates based on the maximum number of zones requiring either heating or cooling.
Once the operating mode is determined, the CBVAV model calculates a target supply air temperature required to operate a single terminal unit at its maximum air flow rate. The remaining terminal units will modulate as required to maintain the dry-bulb temperature in the zone they are serving according to the thermostat schedule for their respective zone. The system air flow rate (through the supply air fan, cooling coil and heat coil) remains constant during cooling operation, heating operation, and no cooling/heating mode as specified by the user. Therefore, as the zone terminal units modulate to reduce zone air flow rates, the excess system air flow is “bypassed” from the bypass duct splitter node back to the bypass duct mixer node of the CBVAV system (see figures above).
The CBVAV system is able to model supply air fan operation in two modes: cycling fan - cycling coil (i.e., AUTO fan) and continuous fan - cycling coil (i.e., fan ON). A Fan:OnOff or Fan:ConstantVolume is used in either case. Since the excess system air flow is bypassed while the zone terminal units modulate, the supply air fan operates the entire simulation time step when heating or cooling is required. For this reason, AUTO fan only allows the supply air fan to turn off when no cooling or heating is required. If fan ON is specified, the supply air fan runs the entire time the system is scheduled to operate (via its availability schedule). The mode of operation for the supply air fan is specified through a fan operating mode schedule where a value of 0 in the schedule indicates cycling fan mode and a value greater than 0 indicates continuous fan mode. If the schedule is not provided, the supply air fan operating mode is considered to be continuous (fan ON).
Output variables reported for the CBVAV system include the supply air fan part-load ratio, the compressor part-load ratio, and the electric consumption of the CBVAV system. Additional output variables report the total heating rate and total cooling rate provided by the CBVAV system. The sensible and latent components for total system cooling and heating are also available as output variables. Reporting of other variables of interest for the CBVAV system (DX coil cooling rate, heating rate, crankcase electric power and energy, supply air fan electric power, etc.) is done by the individual system components (fan, DX cooling coil, and heating coil).
Model Description[LINK]
As described previously, the CBVAV system conditions one or more zones and is controlled by zone thermostats (Ref. ZoneControl:Thermostat). For each simulation time step, EnergyPlus performs a zone air heat balance to determine if cooling or heating is required to meet the zone thermostat setpoints, excluding any impacts from CBVAV system operation. CBVAV system performance is then modeled with all heating/cooling coils off but with the supply air fan operating according to the user specified supply air fan operating mode schedule. If the zone air heat balance plus the impact of CBVAV system operation with coils off results in no requirement for heating or cooling by the CBVAV coils, or if the CBVAV system is scheduled off (via its availability schedule), then the CBVAV coils do not operate and the compressor part-load ratio output variable is set to 0. If the model determines that cooling or heating is required and the CBVAV system is scheduled to operate, the model calculates a target supply air temperature required to maintain a single terminal unit at it’s maximum air flow rate, the amount of bypass air returning to the bypass duct mixer node, and the part-load ratio of the cooling or heating coils in order to meet the target supply air temperature.
When high humidity control is desired, a ZoneControl:Humidistat input object and a SetpointManager:SingleZone:Humidity:Maximum, SetpointManager:MultiZone:MaximumHumidity:Average or SetpointManager:MultiZone:Humidity:Maximum object are required. The air outlet node of the CBVAV system is used as the control node for the setpoint manager. For this reason, only a single humidistat should be specified for one of the zones being served by this system. If humidistat/setpoint manager objects are specified for more than one zone served by this system, only the last of the SetpointManager:SingleZone:Humidity:Maximum objects is used (the setpoint manager objects are read in order of occurrence in the input file). Since the outlet node of the CBVAV system is always used as the control node, the setpoints calculated by the previous setpoint managers are overwritten by the last setpoint manager in the input. When a heat exchanger is used to improve the dehumidification performance of the cooling coil (i.e. CoilSystem:Cooling:DX:HeatExchangerAssisted), the heat exchanger is always active and can not be turned on and off based on zone humidity levels.
The remainder of this section describes the calculations performed when cooling or heating coil operation is required. For any HVAC simulation time step, the CBVAV system can only cool or heat the air, not both. Because the CBVAV system bypasses system air flow back to the inlet of the CBVAV unit, the system operates for the entire simulation time step. If the user specifies continuous fan operation, then the supply air fan continues to operate at a user-specified flow rate even during periods when the coils cycle off. If the user specifies AUTO fan operation, then the supply air fan cycles off for the entire simulation time step only when no cooling or heating is required.
Operating Mode[LINK]
The first step in modeling a CBVAV system is to obtain the cooling or heating load for each zone as calculated by EnergyPlus based on the zone thermostat setpoint temperature(s). The calculated loads for each zone are used to determine the total cooling and heating requirements for all zones served by this system. In addition to summing the zone cooling and heating loads, the number of zones in cooling and the number of zones in heating are totalized. The priority control mode specified by the user is then used to determine the operating mode for this simulation time step.
If Cooling Priority is specified and the total cooling requirement in all zones is not equal to zero, then cooling is selected as the operating mode. If the total cooling requirement is equal to zero and the total heating requirement is not equal to zero, then heating is selected as the operating mode. If the total cooling requirement and total heating requirement are equal to zero then the zones are allowed to float (no heating or cooling provided).
If Heating Priority is specified and the total heating requirement in all zones is not equal to zero, then heating is selected as the operating mode. If the total heating requirement is equal to zero and the total cooling requirement is not equal to zero, then cooling is selected as the operating mode. If the total cooling requirement and total heating requirement are equal to zero then the zones are allowed to float (no heating or cooling provided).
If Zone Priority is specified and the total number of zones requiring cooling is greater than the total number of zones requiring heating, then cooling is selected as the operating mode. If the total number of zones requiring heating is greater than the total number of zones requiring cooling, then heating is selected as the operating mode. If the total number of zones requiring cooling is equal to the total number of zones requiring heating, then the magnitude of the total cooling and heating requirements for all zones sets the operating mode. In this case, if the magnitudes of the cooling and heating requirements are zero, then the zones are allowed to float (no heating or cooing provided). If the magnitudes of the cooling and heating requirements are non-zero and identical, then cooling is selected as the operating mode.
Calculation of Bypass Duct Mixer Node Conditions[LINK]
The operation of this system is unique in that it uses constant-air-volume equipment to provide variable air volume to the conditioned zones. This is accomplished with the use of a bypass duct (shown in the figures above) which shunts excess system air flow from the bypass duct splitter node at the system’s outlet back to the bypass duct mixer node at the system’s inlet. The air conditions at the bypass duct mixer node are based on the inlet air to the CBVAV system, the system outlet air conditions required to meet the zone loads, and the fraction of bypassed air. The following calculations are performed each simulation time step.
\[BypassFrac = 1.0 - \left( {\frac{{{{\dot m}_{supply}}}}{{{{\dot m}_{system}}}}} \right)\]
\[{T_{bypassductmixernode}} = \left( {1 - BypassFrac} \right){T_{inlet}} + \left( {BypassFrac} \right){T_{outlet}}\]
\[{\omega _{bypassductmixernode}} = \left( {1 - BypassFrac} \right){\omega _{inlet}} + \left( {BypassFrac} \right){\omega _{outlet}}\]
\[{h_{bypassductmixernode}} = PsyHFnTdbW\left( {{T_{mixerinlet}},{\omega _{mixerinlet}}} \right)\]
where:
\(BypassFrac\) = fraction of system air directed to the bypass duct mixer node
\({\dot m_{supply}}\) = Air mass flow rate at the system’s air outlet node, kg/s
\({\dot m_{system}}\) = Air mass flow rate through CBVAV system (coils and supply air fan), kg/s
\({T_{bypassductmixernode}}\) = Air temperature at the bypass duct mixer node, °C
\({T_{inlet}}\) = Air inlet node temperature, °C
\({T_{outlet}}\) = Air outlet node temperature, °C
\({\omega _{bypassductmixernode}}\) = Air humidity ratio at the bypass duct mixer node, kg/kg
\({\omega _{inlet}}\) = Air inlet node humidity ratio, kg/kg
\({\omega _{outlet}}\) = Air outlet node humidity ratio, kg/kg
\({h_{bypassductmixernode}}\) = Air enthalpy at the bypass duct mixer node, J/kg
\(PsyHFnTdbW\) = Psychrometric function calculating enthalpy given dry-bulb temperature and humidity ratio
Cooling Operation[LINK]
If the model determines that the CBVAV system must supply cooling to the zones, the model first calculates a target outlet air dry-bulb temperature required to operate a single terminal unit at its maximum air flow rate. The minimum target temperature for all zones is used to control the CBVAV system in cooling mode.
\[T_{target}^i = T_{Zone}^i + \left( \frac{Q^i_{Zone}}{\dot{m}^i_{zone,max} * C_p} \right) ; i = 1,n\]
\[{T_{target}} = MIN\left( {T_{target}^i} \right);\,\,i = 1,n\]
where:
\(T_{target}^i\) = Target supply air temperature for zone i, °C
\(T_{zone}^i\) = Air temperature in zone i, °C
\(Q_{zone}^i\) = Cooling or heating load for zone i (cooling loads are negative values, heating loads are positive values), W
\(Cp\) = Specific heat of supply air with coils off, J/kg-K
\(\dot m_{zone,max}^i\) = Maximum terminal unit mass flow rate in zone i, kg/s
\(T_{target}\) = Target supply (outlet) air temperature for the CBVAV system, °C
The model then calculates the part-load ratio of the DX compressor required to meet the target supply (outlet) air temperature. Since the part-load performance of the DX cooling coil is frequently non-linear (Ref: Coil:Cooling:DX:SingleSpeed model), the actual part-load ratio for the cooling coil compressor is determined through iterative calculations (successive modeling of the DX cooling coil model) until the CBVAV system’s outlet air temperature (including on/off cycling effects of the DX coil) matches the target supply (outlet) air temperature within a small temperature convergence tolerance (1E-5 ˚C).
Since the supply air fan operates continuously for each simulation time step (or is OFF for the entire HVAC system time step), the air conditions at nodes downstream of the cooling coil are calculated as the average conditions over the simulation time step (i.e., the weighted average of coil’s outlet node conditions when the coil is operating and the coil’s inlet node conditions when the coil is OFF).
Heating Operation[LINK]
Modeling the CBVAV system’s DX heating coil is identical to the calculations described above for cooling operation except that the maximum target supply air temperature for all zones is used to control the CBVAV system in heating mode.
\[{T_{target}} = MAX\left( {T_{target}^i} \right);\,\,i = 1,n\]
Iterative calculations (successive modeling of the DX heating coil model) are used to determine the final heating coil part-load ratio to account for the non-linear performance of the DX heating coil at part-load conditions.
When a gas or electric heating coil is used instead of a DX heating coil, the amount of heat required by the coil is calculated based on the target supply (outlet) air temperature and the coil inlet air temperature as follows:
\[{Q_{heating}} = {\dot m_{system}}{C_p}({T_{target}} - {T_{inlet,heatcoil}})\]
where:
\({Q_{heating}}\) = Heating coil load, W
\({C_p}\) = Specific heat of heating coil inlet air, J/kg-K
\({T_{inlet,heatcoil}}\) = Heating coil inlet air temperature, °C
Floating Operation (no cooling or heating)[LINK]
When the zone thermostats determine that there is no cooling or heating requirement in any zone, the CBVAV coils are OFF and the zone temperatures are allowed to float. However, a special case exists where the user specifies continuous supply air fan operation and no cooling or heating requirements exist in any zone. In this case, the outlet air temperature of the CBVAV system (with fan ON and coils OFF) is compared to the target outlet air temperatures required to maintain the zone’s cooling and heating setpoint temperatures. If the outlet air temperature with the supply fan ON and coils OFF is below the target outlet air temperature required to maintain the heating setpoint, then heating mode is enabled to avoid overshooting the zone heating setpoint temperature. Conversely, if the outlet air temperature with the supply fan ON and coils OFF is above the target outlet air temperature required to maintain the cooling setpoint, then cooling mode is enabled to avoid overshooting the zone cooling setpoint temperature. This special case is handled at any time a no load condition is reported by the thermostats and overshooting the zone air temperature setpoint is possible regardless of the priority control mode selected by the user.
Minimum and Maximum Outlet Air Temperature in Cooling/Heating Operation[LINK]
The user also specifies a minimum outlet air temperature during cooling operation and a maximum outlet air temperature during heating operation. The target outlet air temperature, as calculated above, is compared to each of these limits during each simulation time step. The resulting target outlet air temperature is used to control the heating and cooling coils.
\[{T_{target}} = MAX\left( {{T_{target}},\,\,{T_{min,cooling}}} \right)\]
\[{T_{target}} = MIN\left( {{T_{target}},\,\,{T_{max,heating}}} \right)\]
where:
\({T_{min,cooling}}\) = Minimum outlet air temperature during cooling operation, °C
\({T_{max,heating}}\) = Maximum outlet air temperature during heating operation, °C
Air Flow Calculations[LINK]
The changeover-bypass VAV system operates based on user-specified (or autosized) air flow rates. The CBVAV system air flow rate (i.e., air flow through the supply air fan and heating/cooling coils) during cooling operation may be different than the system air flow rate during heating operation. In addition, the system air flow rate when no cooling or heating is required but the supply air fan remains ON can be different than the air flow rates when cooling or heating is required. The outside air flow rates can likewise be different in these various operating modes. The model takes these different air flow rates into account when simulating the performance of the CBVAV system. The system air flow rate for each simulation time step is based on the current operating mode (cooling, heating, or no cooling/heating) and is reported on the inlet/outlet air nodes of the various CBVAV components (e.g. fan, cooling coil, and heating coil). The supply air flow rate delivered to the individual zones is calculated based on the sum of the air flow rates through each terminal unit and is reported at the air inlet and outlet nodes of the CBVAV system each simulation time step. The difference between the system air mass flow rate and the supply air mass flow rate delivered to all zones is equal to the bypass air mass flow rate which is also reported each simulation time step.
The system and outside air flow rates when a system coil is ON (e.g., system air volumetric flow rate during cooling operation, system air volumetric flow rate during heating operation, outside air volumetric air flow rate during cooling operation, and outside air volumetric air flow rate during heating operation) or the system coils are OFF and the fan operates continuously (e.g., system air volumetric flow rate when no cooling or heating is needed and outside air volumetric air flow rate when no cooling or heating is needed) are specified by the user, or can be autosized, and are converted from volumetric flow rate to mass flow rate at standard conditions. If the user has specified cycling fan operation, then the system air and outside air mass flow rates when the system coils are OFF the entire time step are zero. If the user has specified constant fan operation, then the air flow rates when no cooling or heating is needed are used when the system coils are OFF the entire time step.
There is one special case. If the user has specified constant fan operation and they specify that the system air volumetric flow rate when no cooling or heating is needed is zero (or if the field is left blank), then the model assumes that the system air mass flow rate when the system coils are OFF the entire time step is equal to the corresponding air mass flow rate when any system coil was last operating (ON). This model handles the zero (or blank) entry for outside air volumetric flow rate when no cooling or heating is needed in an analogous fashion.
\[{\dot m_{system}} = {\rho _{air,std}}*{\dot V_{mode}}\]
\[{\dot m_{system,OA}} = {\rho _{air,std}}*{\dot V_{mode,OA}}\]
\[{\dot m_{supply}} = \sum\limits_{i = 1}^n {{{\dot m}_{zone}}}\]
\[{\dot m_{bypass}} = {\dot m_{system}} - {\dot m_{supply}}\]
where:
\(\rho air,std\) = standard air density (1.204 kg/m3) adjusted for the local barometric pressure (standard barometric pressure corrected for altitude, ASHRAE 1997 HOF pg. 6.1), kg/m3
\({\dot V_{mode}}\) = User-specified system volumetric flow rate in cooling, heating, or no cooling or heating mode, m3/s
\({\dot m_{system,OA}}\) = Outdoor air mass flow rate introduced through the CBVAV system, kg/s
\({\dot V_{mode,OA}}\) = User-specified outdoor air volumetric flow rate in cooling, heating, or no cooling or heating mode, m3/s
Calculation of System Heating and Cooling Rates[LINK]
At the end of each HVAC simulation time step, this object reports the heating or cooling rate and energy delivered by the system, as well as the electric power and consumption by the system. In terms of thermal energy delivered by the system, the sensible, latent and total energy transfer rates for the system are calculated as follows:
\[{\dot Q_{total}} = ({\dot m_{supply}})({h_{outlet}} - {h_{inlet}})\]
\[{\dot Q_{sensible}} = ({\dot m_{supply}}){({h_{outlet}} - {h_{inlet}})_{HRmin}}\]
\[{\dot Q_{latent}} = {\dot Q_{total}} - {\dot Q_{sensible}}\]
where:
\({\dot Q_{total}}\) = total energy transfer rate by the system, W
\({\dot Q_{sensible}}\) = sensible energy transfer rate by the system, W
\({\dot Q_{latent}}\) = latent energy transfer rate by the system, W
hinlet = enthalpy of the air entering the unit at its inlet node, J/kg
houtlet = enthalpy of the air leaving the unit at its outlet node, J/kg
\(H{R_{min}}\) = minimum of the inlet air and outlet air humidity ratio, kg/kg
Since each of these energy transfer rates can be calculated as positive or negative values, individual reporting variables are established for cooling and heating and only positive values are reported. The following calculations are representative of what is done for each of the energy transfer rates:
\[\begin{array}{l}If\;({{\dot Q}_{total}} < 0.0)\;Then \\ \quad {{\dot Q}_{total,cooling}} = ABS({{\dot Q}_{total}}) \\ \quad {{\dot Q}_{total,heating}} = 0.0 \\ Else \\ \quad {{\dot Q}_{total,cooling}} = 0.0 \\ \quad {{\dot Q}_{total,heating}} = {{\dot Q}_{total}} \\ Endif\end{array}\]
where:
\({\dot Q_{total,cooling}}\) = output variable ‘Unitary System Total Cooling Rate, W’
\({\dot Q_{total,heating}}\) = output variable ‘Unitary System Total Heating Rate, W’
In addition to heating and cooling rates, the heating and cooling energy supplied by the system are also calculated for the time step being reported. The following example for total zone cooling energy is representative of what is done for the sensible and latent energy as well as the heating counterparts.
\[{Q_{total,cooling}} = {\dot Q_{total,cooling}}*TimeStepSys*3600\]
where:
\({Q_{total,cooling}}\) = output variable ‘Unitary System Total Cooling Energy, J’
TimeStepSys= HVAC system simulation time step, hr
3600= conversion factor, sec/hr
Changeover-bypass VAV Unitary System Sizing[LINK]
The changeover-bypass VAV system is modeled as an air loop component and is sized according to the methodology described elsewhere in this document (Ref. System Design Loads and Air Flow Rates). The following volumetric air flow rates may be autosized:
Unitary Air-To-Air Heat Pump[LINK]
Overview[LINK]
The input object AirLoopHVAC:UnitaryHeatPump:AirToAir provides a model for an air-to-air heat pump that is a “virtual” component that consists of an on/off or constant volume fan component, a DX cooling coil, a DX heating coil, and a gas or electric supplemental heating coil. The specific configuration of the blow through heat pump is shown in the following figure. For a draw through heat pump, the fan is located between the DX heating coil and the supplemental heating coil.
While the heat pump may be configured to serve multiple zones, system operation is controlled by a thermostat located in a single “control” zone. One of the key parameters for the heat pump component is the fraction of the total system airflow that goes through the control zone. This fraction is calculated as the ratio of the maximum air mass flow rate for the air loop’s supply inlet node for the control zone (e.g., AirTerminal:SingleDuct:Uncontrolled, field = Maximum Air Flow Rate, converted to mass flow) to the sum of the maximum air mass flow rates for the air loop’s supply inlet nodes for all zones served by this air loop. The heat pump module scales the calculated load for the control zone upward based on this fraction to determine the total load to be met by the heat pump. The module then proceeds to calculate the required part-load ratio for the system coil and the supply air fan to meet this total load. The heating or cooling capacity delivered by the heat pump is distributed to all of the zones served by this system via the direct air units that supply air to each zone. The supply air fraction that goes though the control zone is calculated as follows:
\[Control Zone Air Flow\,Fraction = \frac{{{{\dot m}_{TUMax\,ControlZone}}}}{{\sum\limits_{j = 1}^{NumOfZones} {{{\dot m}_{TUMax\,Zone\,j}}} }}\]
where:
\({\dot m_{TUMax\,ControlledZone}}\) =maximum air mass flow rate for the air loop’s supply inlet node (terminal unit) for the control zone (kg/s)
\({\dot m_{TUMax\,Zone\,j}}\) =maximum air mass flow rate for the air loop’s supply inlet node for the jth zone (kg/s)
\(NumOfZones\) =number of zones, or number of air loop supply air inlet nodes for all zones served by the air loop (-)
The heat pump component is able to model supply air fan operation in two modes: cycling fan - cycling coil (i.e., AUTO fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff must be used to model AUTO fan, while Fan:OnOff or Fan:ConstantVolume can be used to model fan ON. The fan operation mode is specified using a supply air fan operating mode schedule where schedule values of 0 denote cycling fan operation and schedule values other than 0 (a 1 is usually used) denote continuous fan operation. Using this schedule, the furnace fan may be cycled with cooling or heating coil operation or operated continuously based on time of day (e.g. cycling fan operation at night and continuous fan operation during the day). If the fan operating mode schedule name field is left blank in the heat pump object, the heat pump assumes cycling or AUTO fan mode operation throughout the simulation.
The output variables reported by the heat pump object are fan part-load ratio and compressor part-load ratio. Fan part-load ratio is defined as the actual air mass flow rate through the system for the time step divided by the operating supply air mass flow rate specified for the heat pump (\(\dot{m}_{actual} / \dot{m}_{ON}\)). The operating supply air mass flow rate may be different for cooling, heating, and when no cooling or heating is required and the fan operates continuously. Compressor part-load ratio is the actual load for the time step divided by the full-load sensible capacity (see Eqn. or Eqn.). Reporting of other variables of interest for the heat pump (heating rate, cooling rate, energy consumption, etc.) is done by the individual system components (fan, DX cooling coil, DX heating coil, and supplemental heating coil).
Model Description[LINK]
As described previously, the heat pump is a “virtual” component consisting of a fan, DX cooling coil, DX heating coil and a supplemental heating coil. The sole purpose of the heat pump model is to properly coordinate the operation of the various system components. The following sections describe the flow of information within the model, as well as the differences between cycling and continuous supply air fan operation.
Cooling Operation[LINK]
If EnergyPlus determines that the heat pump must supply cooling to the control zone to meet the zone air temperature setpoint, then the heat pump model computes the total sensible cooling load to be delivered to the zones being served based on the control zone sensible cooling load and the fraction of the heat pump air flow that goes through the control zone.
\[Heat\,Pump\,Cooling\,Load\, = \frac{{Control\,Zone\,Cooling\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
If the supply air fan operating mode schedule requests cycling fan operation, the model first checks for the presence of an ecomomizer in the outside air system serving the heat pump’s air loop (Ref. AirLoopHVAC:OutdoorAirSystem). If an outside air system is not present or if an air-side economizer is not used, the heat pump’s compressor is used to meet the heat pump cooling load. If an air-side economizer is used and is active (i.e., economizer controls indicate that conditions are favorable to increase the outside air flow rate), the heat pump will try to meet the cooling load by operating only the supply air fan. If the fan is able to satisfy the heat pump cooling load, the compressor remains off for the entire simulation time step. If the operation of the fan alone is unable to meet the entire cooling load, then the compressor is enabled and additional calculations are performed to determine the compressor’s part-load ratio.
The model then calculates the heat pump’s sensible cooling energy rate delivered to the zones being served when the system runs at full-load conditions and when the DX cooling coil is OFF. If the supply air fan cycles with the compressor, then the sensible cooling energy rate is zero when the cooling coil is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible cooling energy rate will not be zero when the cooling coil is OFF. Calculating the sensible cooling energy rate involves modeling the supply air fan (and associated fan heat) and the DX cooling coil. The DX heating coil and the supplemental heating coil are also modeled, but only to pass the air properties and mass flow rate from their inlet nodes to their outlet nodes. For each of these cases (full load and DX cooling coil OFF), the sensible cooling energy rate delivered by the heat pump is calculated as follows:
\[Full\;Cool\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Cool\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(Mass Flow Rate_{full load}\) = air mass flow rate through heat pump at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the heat pump at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the heat pump exiting air or the air leaving the control zone
\(Mass Flow Rate_{coil off}\) = air mass flow rate through the heat pump with the cooling coil OFF, kg/s
\(h_{out,coil off}\) = enthalpy of air exiting the heat pump with the cooling coil OFF, J/kg
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{coil\;off}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible cooling energy rates and the total sensible cooling load to be met by the system, the part-load ratio for the heat pump is estimated.
\[PartLoadRatio\, = \,MAX\left( {0.0,\frac{{ABS\left( {Heat\,Pump\,Cooling\,Load - NoCoolOutput} \right)}}{{ABS\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
Since the part-load performance of the DX cooling coil is frequently non-linear, and the supply air fan heat varies based on cooling coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the heat pump’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{HeatPumpCoolingLoad - Q_{HeatPump}}{HeatPumpCoolingLoad}\]
where:
\(QHeatPump\) = Heat pump delivered sensible capacity (W)
If the heat pump has been specified with cycling fan/cycling coil (AUTO fan), then the heat pump’s operating supply air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. In this case, the air conditions at nodes downstream of the cooling coil represent the full-load (steady-state) values when the coil is operating.
If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the heat pump is calculated as the average of the user-specified air flow rate when the cooling coil is ON and the user-specified air flow rate when the cooling coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[\mathop m\limits^ \bullet furnace = PartLoadRatio\left( {\mathop m\limits^ \bullet CoolCoilON} \right) + \left( {1 - PartLoadRatio} \right)\left( {\mathop m\limits^ \bullet CoilOFF} \right)\]
where:
\(\mathop m\limits^ \bullet CoolCoilON\) = air mass flow rate through heat pump when the cooling coil is ON (kg/s)
\(\mathop m\limits^ \bullet CoilOFF\) = air mass flow rate through heat pump when no cooling or heating is needed (kg/s)
In this case, the air conditions at nodes downstream of the cooling coil are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF).
Heating Operation
Calculations for heating operation are similar to those for cooling operation in most respects. However, due to the inclusion of a supplemental heating coil, additional calculations are necessary to properly meet the total heating load for the zones being served.
If EnergyPlus determines that the heat pump must supply heating to the control zone to meet the zone air temperature setpoint, then the heat pump model computes the total sensible heating load to be delivered to the zones being served based on the control zone sensible heating load and the control zone airflow fraction.
\[Heat\,Pump\,Heating\,Load\, = \frac{{Control\,Zone\,Heating\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
The model then calculates the heat pump’s sensible heating energy rate delivered to the zones being served when the system runs at full-load conditions and when the DX heating coil is OFF (without supplemental heater operation in either case). If the supply air fan cycles with the compressor, then the sensible heating energy rate is zero when the compressor is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible heating energy rate will not be zero when the compressor is OFF. Calculating the sensible heating energy rate involves modeling the supply air fan (and associated fan heat), the DX cooling coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node), the DX heating coil, and the supplemental heating coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and DX heating coil OFF, without supplemental heater operation in either case), the sensible heating energy rate delivered by the heat pump is calculated as follows:
\[Full\;Heat\;Output = (Mass\;Flow\;Rat{e_{ful\;load}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;full\;load}}\]
\[No\;Heat\;Output = (Mass\;Flow\;Rat{e_{coil\;off}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\(Mass Flow Rate_{full load}\) = air mass flow rate through heat pump at full-load conditions, kg/s
\(h_{out, full load}\) = enthalpy of air exiting the heat pump at full-load conditions, J/kg
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located), J/kg
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the heat pump exiting air or the air leaving the control zone
\(Mass Flow Rate_{coil off}\) = air mass flow rate through the heat pump with the heating coil OFF, kg/s
\(h_{out, coil off}\) = enthalpy of air exiting the heat pump with the heating coil OFF, J/kg
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;full\;load}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{full\;load}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad + \left( {Mass\;Flow\;Rat{e_{_{coil\;off}}} - \frac{{Mass\;Flow\;Rat{e_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
With the calculated sensible heating energy rates and the total sensible heating load to be met by the system, the part-load ratio for the heat pump is estimated.
\[PartLoadRatio\, = \,MAX\left( {0.0,\frac{{ABS\left( {Heat\,Pump\,Heating\,Load - NoHeatOutput} \right)}}{{ABS\left( {FullHeatOutput - NoHeatOutput} \right)}}} \right)\]
Since the part-load performance of the DX heating coil is frequently non-linear (Ref: Single-Speed Electric Heat Pump DX Air Heating Coil), and the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the heat pump’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{HeatPumpHeatingLoad - Q_{HeatPump}}{HeatPumpHeatingLoad}\]
where:
\(Q_{HeatPump}\) = Heat pump delivered sensible capacity (W)
If the heat pump’s DX heating coil output at full load is insufficient to meet the entire heating load, PartLoadRatio is set equal to 1.0 (compressor and fan are not cycling) and the remaining heating load is passed to the supplemental heating coil. If the heat pump model determines that the outdoor air temperature is below the minimum outdoor air temperature for compressor operation, the compressor is turned off and the entire heating load is passed to the supplemental gas or electric heating coil. The heat pump exiting air conditions and energy consumption are calculated and reported by the individual component models (fan, DX heating coil, and supplemental gas or electric heating coil).
If the heat pump has been specified with cycling fan/cycling coil (AUTO fan), then the heat pump’s operating supply air mass flow rate is multiplied by PartLoadRatio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the heating coils represent the full-load (steady-state) values when the coils are operating. If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the heat pump is calculated as the average of the user-specified air flow rate when the heat pump heating coil is ON and the user-specified air flow rate when the heat pump heating coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[\mathop m\limits^ \bullet HeatPump = PartLoadRatio\left( {\mathop m\limits^ \bullet HeatCoilON} \right) + \left( {1 - PartLoadRatio} \right)\left( {\mathop m\limits^ \bullet CoilOFF} \right)\]
where:
\(\mathop m\limits^ \bullet HeatCoilON\) = air mass flow rate through heat pump when the heating coil is ON (kg/s)
\(\mathop m\limits^ \bullet CoilOFF\) = air mass flow rate through heat pump when no heating or cooling is needed (kg/s)
In this case, the air conditions at nodes downstream of the heating coils are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coils are operating and inlet air conditions when the coils are OFF).
High Humidity Control with AirToAir HeatPump Model[LINK]
The specific configuration of the AirToAir HeatPump with supplemental heating coil is shown above (see Figure 227). This figure shows the fan placement when a blow through fan is specified. If a draw through fan is specified, the fan is located between the heating coil and the supplemental heating coil. The system is controlled to keep the high relative humidity in the control zone from exceeding the setpoint specified in the object ZoneControl:Humidistat. This option is available when the supply air fan operates continuously (i.e., the supply air fan operating mode schedule values are never equal to 0) or the supply air fan cycles with the compressor. In addition, when high humidity control is specified and the compressor operates, the heatpump operates at the cooling air flow rate when a zone heating load is present as determined by the zone thermostat. High humidity control is specified as either None, MultiMode, or CoolReheat in the Dehumidification Control Type input field. MultiMode is specified when a heat exchanger is used to improve the dehumidification performance of the cooling coil. The heat exchanger will be activated when the sensible part-load ratio is insufficient to meet the zone latent load. CoolReheat is specified when a DX cooling coil is used to over-cool the supply air stream in order to meet the zone latent load. In this case, a supplemental heating coil will ensure the zone temperature does not fall below the zone heating temperature set point. When a heat exchanger is used in conjunction with a DX cooling coil and CoolReheat is specified as the Dehumidification Control Type, the heat exchanger is “locked on” to meet either the sensible or latent cooling load. If the dehumidification control type is selected as None and a heat exchanger assisted cooling coil is used, the heat exchanger is “locked on” and the air conditioner runs only to meet the sensible cooling load. A supplemental heating coil is required for all dehumidification control types.
The model first calculates the PartLoadRatio required meeting the sensible cooling load. The heatpump’s sensible cooling load is determined from the control zone sensible cooling load to the cooling setpoint and the control zone air flow fraction to maintain the dry-bulb temperature setpoint in the control zone.:
\[HeatPumpCoolingLoad = \,\frac{{ControlZoneCoolingLoad}}{{ControlZoneAirFlowFraction}}\]
The heatpump’s sensible cooling load to be met and the full load cooling output are used to calculate the sensible the part-load ratio iteratively based on user specified convergence criterion.
\[PartLoadRatio = MAX\left( {0.0,\,\frac{{ABS\left( {HeatPumpCoolingLoad - NoCoolOutput} \right)}}{{ABS\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
When the heat pump’s sensible cooling capacity meets the system sensible cooling load at a given sensible part load ratio, then the Heat pump meets the controlled zone cooling setpoint temperature. If a moisture (latent) load exists because the control zone humidity has exceeded the setpoint, the total moisture load to be met by the heat pumps (HeatPumpMoistureLoad) is calculated based on the control zone moisture load and the control zone air flow fraction.
\[HeatPumpMoistureLoad = \,\frac{{ControlZoneMoitureLoad}}{{ControlZoneAirFlowFraction}}\]
Then the LatentPartLoadRatio required to meet the high humidity setpoint is calculated as follows:
\[LatentPartLoadRatio = MIN\left( {PL{R_{Min}},\,\frac{{ABS\left( {HeatPumpMoistureLoad - NoLatentOutput} \right)}}{{ABS\left( {FullLatentOutput - NoLatentOutput} \right)}}} \right)\]
The model uses the greater of the two part-load ratios, PartLoadRatio or LatentPartLoadRatio, to determine the operating part-load ratio of the Heat Pump’s DX cooling coil.
\[LatentPartLoadRatio = MAX\left( {PartLoadRatio,\,LatentPartLoadRatio} \right)\]
As previously described, iterations are performed to converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\) = the control zone sensible cooling load to the cooling setpoint, (W).
\(ControlZoneMoistureLoad\) = the control zone moisture load to the dehumidifying relative humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) = the supply air fraction that goes though the control zone, (-).
FullLatentOutput =the Heat Pump’s latent cooling energy rate at full-load conditions, W
NoLatentOutput =the Heat Pump’s latent cooling energy rate with cooling coil OFF, W
\(PartLoadRatio\) =the heat pump’s part-load-ratio required to meet system sensible load, (-).
\(LatentPartLoadRatio\) =the heat pump’s part-load-ratio required to meet system moisture load, (-).
\(PL{R_{MIN}}\) = the minimum part-load ratio, which is usually 0.0. For the case when the latent capacity degradation model is used (Ref: DX Cooling Coil Model), this value is the minimum part-load ratio at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the heating setpoint and if there is a dehumidification load, the supplemental heating coil load is required to offset the excess cooling as shown in Figure 228. If the model determines that the LatentPartLoadRatio is to be used as the operating part-load ratio of the heatpump’s cooling coil, the supplemental heating coil is used to offset the excess sensible capacity provided by the heat pump DX cooling coil. The model first checks the sensible load that exists for the current simulation time step (predicted zone temperature with no HVAC operation compared to the thermostat setpoint temperatures). If a sensible cooling load or no sensible cooling or heating load exists (see Figure 2), the model calculates the difference between the sensible heating load required to reach or maintain the heating dry-bulb temperature setpoint and the actual sensible cooling energy rate delivered by the unit (with LatentPartLoadRatio). In this case, the supplemental heating coil is used to offset the excess sensible cooling energy provided by the DX cooling coil (if any) that could have caused an overshoot of the heating dry-bulb temperature setpoint. Note that when a humidistat is used and high humidity control is required, the zone dry-bulb temperature will typically move toward the heating temperature setpoint when a high moisture (latent) load exists.
If a heating load exists (Figure 229), the supplemental heating coil is used to meet the heating coil load and at the same time offset the entire sensible cooling energy rate of the DX cooling coil (to meet the humidistat setpoint). Note that when a heating load exists and high humidity control is required, the heat pump operates at the user-specified cooling air flow rate for the entire simulation time step. As with the fan, and DX cooling coil, report variables associated with supplemental heating coil performance (e.g., heating coil energy, heating coil rate, heating coil gas or electric energy, heating coil runtime fraction, etc.) are managed in the supplemental (heating) coil object.
Unitary Multi-Speed Air-To-Air Heat Pump[LINK]
Overview[LINK]
The input object AirLoopHVAC:UnitaryHeatPump:AirToAir:MultiSpeed provides a model for a multispeed air-to-air heat pump that is a “virtual” component that consists of an on/off or constant volume fan component, a multispeed DX cooling coil, a multispeed DX heating coil, and a gas or electric supplemental heating coil. The main difference between this heat pump object and other EnergyPlus heat pump objects is that this object allows from two to four discrete compressor speeds for heating and cooling operation (instead of a single speed for each mode). The specific configuration of the blow through heat pump is shown in the following figure. For a draw through heat pump, the fan is located between the DX heating coil and the supplemental heating coil.
While the heat pump may be configured to serve multiple zones, system operation is controlled by a thermostat located in a single “control” zone. One of the key parameters for the heat pump component is the fraction of the total system airflow that goes through the control zone. This fraction is calculated as the ratio of the maximum air mass flow rate for the air loop’s supply inlet node for the control zone (e.g., AirTerminal:SingleDuct:Uncontrolled, field = Maximum Air Flow Rate, converted to mass flow) to the sum of the maximum air mass flow rates for the air loop’s supply inlet nodes for all zones served by this air loop. The heat pump module scales the calculated load for the control zone upward based on this fraction to determine the total load to be met by the heat pump. The module then proceeds to calculate the required cycling ratio, speed ratio and speed number for the system coil and determines the supply air mass flow rate to meet this total load based on the speed number. The cycling ratio is the ratio of the sensible load (heating or cooling) to the steady-state capacity of the multispeed heat pump’s DX heating or cooling coil at Speed 1 for the entire system time step. It is equivalent to the part load ratio for a single speed DX coil. The value is between 0.0 and 1.0 when the system operates at its lowest speed (Speed 1) and 1.0 when the multispeed heat pump operates at speeds above 1. The speed ratio is the ratio of time in a system time step that the compressor is at rated speed between two consecutive speed numbers ([Compressor Speed - Compressor speed at Speed i-1] / [Compressor speed at Speed i - Compressor speed at Speed i-1]). The compressor speed ratio is between 0.0 and 1.0 when the speed number is above 1 and is 0.0 during Speed 1 operation. The speed number is the lowest index number whose corresponding full-load sensible capacity at the given air mass flow rate is greater than or equal to the sensible load (heating or cooling) in a system time step. The heating or cooling capacity delivered by the heat pump is distributed to all of the zones served by this system via the direct air units that supply air to each zone.
The heat pump component is able to model supply air fan operation in two modes: cycling fan - cycling coil (i.e., AUTO fan) and continuous fan - cycling coil (i.e., fan ON). Fan:OnOff must be used to model AUTO fan, while Fan:OnOff or Fan:ConstantVolume can be used to model fan ON. The fan operation mode is specified using a supply air fan operating mode schedule where schedule values of 0 denote cycling fan operation and schedule values other than 0 (a 1 is usually used) denote continuous fan operation. Using this schedule, the supply air fan may be cycled with cooling or heating coil operation or operated continuously based on time of day (e.g. cycling fan operation at night and continuous fan operation during the day).
Several output variables are reported by the heat pump object including fan part-load ratio, compressor part-load ratio, cycling ratio, speed ratio and speed number. Fan part-load ratio is defined as the actual air mass flow rate through the system for the time step divided by the operating supply air mass flow rate specified for the heat pump (\(\dot{m}_{actual} / \dot{m}_{ON}\)) at speed 1. Fan part-load ratio is set to 1.0 when the heat pump operates at speeds above 1. The operating supply air mass flow rate may be different for cooling, heating, and when no cooling or heating is required. Compressor part-load ratio is the actual load for the time step divided by the full-load sensible capacity (see Eqn. or Eqn.). If the defrost strategy is reverse cycle for a DX heating coil, the compressor part-load ratio is the sum of the actual load and the defrost load divided by the full-load sensible capacity. Therefore, the compressor part load ratio for the DX heating coil may be greater than the cycling ratio. This heat pump object also reports the sensible, latent and total cooling and heating rate, as well as the electricity consumption for the unit with separate accounting of auxiliary electric consumption. Furthermore, five report variables related to waste heat recovery are available if the user chooses to model this option.
Model Description[LINK]
As described previously, the heat pump is a “virtual” component consisting of a fan, multispeed DX cooling coil, multispeed DX heating coil and supplemental heating coil. The sole purpose of the heat pump model is to properly coordinate the operation of the various system components. The following sections describe the flow of information within the model, as well as the differences between cycling and continuous supply air fan operation.
Cooling Operation[LINK]
The description of heat pump cooling operation is divided in two sections: sensible capacity and average supply air flow rate. Actually, the determinations of capacity and supply air flow rate are related, so these calculations are performed in unison.
Capacity calculation[LINK]
If EnergyPlus determines that the heat pump must supply cooling to the control zone to meet the zone air temperature setpoint, then the heat pump model computes the total sensible cooling load (negative) to be delivered to the zones being served based on the control zone sensible cooling load and the fraction of the heat pump air flow that goes through the control zone.
\[Heat\,Pump\,Cooling\,Load\, = \frac{{Control\,Zone\,Cooling\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
The model then calculates the heat pump’s sensible cooling energy rate delivered to the zones being served when the system runs at full-load conditions at the highest speed and when the DX cooling coil is OFF. If the supply air fan cycles with the compressor, then the sensible cooling energy rate is zero when the cooling coil is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible cooling energy rate will not be zero when the cooling coil is OFF. Calculating the sensible cooling energy rate involves modeling the supply air fan (and associated fan heat) and the multispeed DX cooling coil. The multispeed DX heating coil and the supplemental heating coil are also modeled, but only to pass the air properties and mass flow rate from their inlet nodes to their outlet nodes. For each of these cases (full load at highest cooling speed and DX cooling coil OFF), the sensible cooling energy rate delivered by the heat pump is calculated as follows:
\(FullCoolOutpu{t_{Highest\;Speed}} = ({\dot m_{HighestSpeed}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;HighestSpeed}}\) \(NoCoolOutput = ({\dot m_{CoilOff}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\)
where:
\({\dot m_{HighestSpeed}}\) = air mass flow rate through heat pump at the highest cooling speed [kg/s]
\(h_{out, full load}\) = enthalpy of air exiting the heat pump at full-load conditions [J/kg]
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located) [J/kg]
HRmin = the minimum humidity ratio of the heat pump exiting air or the air leaving the control zone [kg/kg]
\({\dot m_{CoilOff}}\) = air mass flow rate through the heat pump with the cooling coil OFF [kg/s]
\(h_{out,coil off}\) = enthalpy of air exiting the heat pump with the cooling coil OFF [J/kg]
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;HighestSpeed}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }} \\ \quad \quad \quad \quad \quad + \left( {{{\dot m}_{_{HighestSpeed}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the cooling coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{coil\;off}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the heat pump’s sensible cooling rate at the highest speed (full load, no cycling) is insufficient to meet the entire cooling load, the controlled zone conditions will not be met. The reported cycling rate and speed ratio are 1, and the speed number is set to the highest index number. If the total sensible cooling load to be met by the system is less than the sensible cooling rate at the highest speed, then the following steps are performed.
Calculate the sensible cooling energy rate at Speed 1
\[FullCoolOutpu{t_{Speed1}} = ({\dot m_{Speed1}}){({h_{out,fullload}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;Speed1}}\]
where
\({\dot m_{Speed1}}\) = air mass flow rate through heat pump at Speed 1 [kg/s]
\(\Delta_{sen,Speed1}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions at Speed 1
\[\begin{array}{l}{\Delta _{sen,\;Speed1}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{Speed1}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the sensible cooling energy rate delivered by the heat pump at Speed 1 is greater or equal to the sensible load, the cycling ratio (part-load ratio) for the heat pump is estimated.
\[\begin{array}{l}CyclingRatio = \frac{{ABS(HeatingCoilSensibleLoad)}}{{FullHeatingCoilCapacity}}\\ \;\;\;\;\;\;\;\; = MAX\left( {0.0,\frac{{ABS(Heat\;Pump\;Heating\;Load - AddedFanHeat)}}{{ABS(FullHeatOutpu{t_{Speed1}} - AddedFanHea{t_{Speed1}})}}} \right)\end{array}\]
where
AddedFanHeat= generated supply air fan heat, which is a function of part load ratio and as internal component cooling load [W].
AddedFanHeatSpeed1= generated supply air fan heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX cooling coil is frequently non-linear,and the supply air fan heat varies based on cooling coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the heat pump’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{\left( {Heat\,Pump\,Cooling\,Load - HeatPumpOutpu{t_{Cycling}}} \right)}}{{Heat\,Pump\,Cooling\,Load}}\]
where:
HeatPumpOutputCycling = heat pump delivered sensible capacity for Speed 1 operating at a specific cycling ratio (W)
\[HeatPumpOutpu{t_{cycling}} = {\dot m_{_{HeatPump}}}{\left( {{h_{out}} - {h_{Control\;Zone}}} \right)_{HR\min }} - {\Delta _{cycling}}\]
where
\({\dot m_{HeatPump}}\) = average air mass flow rate defined in the next section [kg/s]
hout = enthalpy of air exiting the heat pump at part load conditions [J/kg]
Δcycling = average sensible load difference between the system output node and the zone inlet node
\[\begin{array}{l}\;{\Delta _{cycling}} = \frac{{{{\dot m}_{_{ZoneInlet}}}}}{{frac}}\left( {{h_{ZoneInlet}} - {h_{Control\;Zone}}} \right) + \left( {{{\dot m}_{_{HeatPump}}} - \frac{{{{\dot m}_{_{ZoneInlet}}}}}{{frac}}} \right)\left( {{h_{Out}} - {h_{Control\;Zone}}} \right)\\ \;\end{array}\]
\({\dot m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the required cooling load, the speed ratio is set to zero and speed number is equal to 1.
If the heat pump’s cooling output at full load for Speed 1 is insufficient to meet the entire cooling load, the Cycling ratio is set equal to 1.0 (compressor and fan are not cycling). Then the cooling speed is increased and the delivered sensible capacity is calculated. If the full load sensible capacity at Speed n is greater than or equal to the sensible load, the speed ratio for the heat pump is estimated:
\(Speed{\kern 1pt} Ratio = \frac{{ABS(Heat{\kern 1pt} Pump{\kern 1pt} Cooling{\kern 1pt} Load - AddeFanHeat - Full{\kern 1pt} Cool{\kern 1pt} Outpu{t_{Speed{\kern 1pt} n - 1}})}}{{ABS(Full{\kern 1pt} CoolOutpu{t_{Speed{\kern 1pt} n}} - Full{\kern 1pt} CoolOutpu{t_{Speed{\kern 1pt} n - 1}})}}\) Although a linear relationship is assumed by applying the speed ratio to obtain the effective capacity and mass flow rate between speed n and n-1, the outlet air node conditions are dependent on the combined outputs and may not be linear. In addition, the supply air fan heat varies with the speed ratio due to different supply mass flow rates between speed n and n-1 . Therefore, the final speed ratio for the cooling coil compressor and fan are determined through iterative calculations (successive modeling of the cooling coil and fan) until the heat pump’s cooling output matches the cooling load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s cooling output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{Heat\,Pump\,Cooling\,Load - HeatPumpOutpu{t_{SpeedRatio}}}}{{Heat\,Pump\,Cooling\,Load}}\]
where:
HeatPumpOutputSpeed,n= heat pump delivered sensible capacity between two consecutive speeds at a specific speed ratio (W)
\[\begin{array}{l}HeatPumpOutpu{t_{SpeedRatio}} = (SpeedRatio)FullCoolOutpu{t_{Speed\;n}}\\;\;\;\;\;\;\; = (1 - SpeedRatio)FullCoolOutpu{t_{Speed\;n - 1}} - AddedFanHea{t_{SpeedRatio}}\end{array}\]
Where
AddedFanHeatSpeedRatio= generated supply air fan heat at a specific speed ratio [W]
In this case, the reported cycling ratio is 1 and speed number is equal to n.
Air Mass Flow Rate Calculation[LINK]
Speed 1 operation
If the heat pump has been specified with cycling fan/cycling coil (AUTO fan), then the heat pump’s operating supply air mass flow rate is determined by the cycling ratio (PartLoadRatio) for Speed 1. The supply air mass flow rate is multiplied by the cycling ratio to determine the average air mass flow rate for the system simulation time step. The air conditions at nodes downstream of the cooling coils represent the full-load (steady-state) values when the coil is operating.
\[{\dot m_{HeatPump}} = (CyclingRatio){\dot m_{Speed1}}\]
If the fan operates continuously (i.e., when the supply air fan operating mode schedule values are NOT equal to 0), the operating air mass flow rate through the heat pump is calculated as the average of the user-specified air flow rate when the heat pump cooling coil is ON at Speed 1 and the user-specified air flow rate when the heat pump cooling coil is OFF (user-specified supply air volumetric flow rates converted to dry air mass flow rates).
\[{\dot m_{HeatPump}} = (CyclingRatio){\dot m_{Speed1}} + (1.0 - CyclingRatio){\dot m_{CoilOff}}\]
where:
\({\dot m_{HeatPump}}\) = average air mass flow rate through heat pump [kg/s]
\({\dot m_{Speed1}}\) = air mass flow rate through heat pump when cooling coil is ON at Speed 1 [kg/s]
\({\dot m_{CoilOff}}\) = air mass flow rate through heat pump when no heating or cooling is needed [kg/s]
In this case, the air conditions at nodes downstream of the cooling coils are calculated as the average conditions over the simulation time step (i.e., the weighted average of full-load conditions when the coil is operating and inlet air conditions when the coil is OFF).
Higher Speed Operation[LINK]
When the heat pump operates at higher speeds to meet the required cooling load, the supply air mass flow rate is linearly interpolated between two consecutive speeds:
\[{\mathop m\limits^ \bullet _{HeatPump}} = (SpeedRatio)\mathop m\limits^ \bullet {{\kern 1pt} _{Speed{\kern 1pt} n}} + (1.0 - SpeedRatio)\mathop m\limits^ \bullet {{\kern 1pt} _{Speed{\kern 1pt} n - 1}}\]
where:
\({\dot m_{HeatPump}}\) = average air mass flow rate through the heat pump for the time step [kg/s]
\({\dot m_{Speed\;n}}\) = air mass flow rate through heat pump when cooling coil is ON at Speed n [kg/s]
\({\dot m_{Speed\;n - 1}}\) = air mass flow rate through heat pump when cooling coil is ON at Speed n-1 [kg/s]
For this case of higher speed operation, the air conditions at nodes downstream of the cooling coils are determined by the delivered cooling capacity and supply air mass flow rates between two consecutive speeds.
Although the above sections present the capacity and air mass flow rate calculation separately, they are dependent and change every iteration until convergence is reached for the time step being simulated.
Heating Operation[LINK]
The description of heat pump heating operation is divided in two sections: total (sensible) capacity and average supply air flow rate. Actually, the determinations of capacity and supply air flow rate are related, so these calculation are performed in unison.
Capacity calculation[LINK]
If EnergyPlus determines that the heat pump must supply heating to the control zone to meet the zone air temperature setpoint, then the heat pump model computes the total sensible heating load (positive) to be delivered to the zones being served based on the control zone sensible heating load and the fraction of the heat pump air flow that goes through the control zone.
\[Heat\,Pump\,Heating\,Load\, = \frac{{Control\,Zone\,Heating\,Load}}{{Control\,Zone\,Air\,Flow\,Fraction}}\]
The model then calculates the heat pump’s sensible heating energy rate delivered to the zones being served when the system runs at full-load conditions at the highest speed and when the DX heating coil is OFF (without supplemental heater operation in either case). If the supply air fan cycles with the compressor, then the sensible heating energy rate is zero when the compressor is OFF. However if the fan is scheduled to run continuously regardless of coil operation, then the sensible heating energy rate will not be zero when the compressor is OFF. Calculating the sensible heating energy rate involves modeling the supply air fan (and associated fan heat), the DX cooling coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node), the DX heating coil, and the supplemental heating coil (simply to pass the air properties and mass flow rate from its inlet node to its outlet node). For each of these cases (full load and DX heating coil OFF, without supplemental heater operation in either case), the sensible heating energy rate delivered by the heat pump is calculated as follows:
\[FullHeatOutpu{t_{Highest\;Speed}} = ({\dot m_{HighestSpeed}}){({h_{out,full\;load}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;HighestSpeed}}\]
\[NoHeatOutput = ({\dot m_{CoilOff}}){({h_{out,\;coil\;off}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;coil\;off}}\]
where:
\({\dot m_{HighestSpeed}}\) = air mass flow rate through heat pump at the highest heating speed [kg/s]
\(h_{out, full load}\) = enthalpy of air exiting the heat pump at full-load conditions [J/kg]
\(h_{control zone}\) = enthalpy of air leaving the control zone (where thermostat is located) [J/kg]
HRmin = enthalpies evaluated at a constant humidity ratio, the minimum humidity ratio of the heat pump exiting air or the air leaving the control zone
\({\dot m_{CoilOff}}\) = air mass flow rate through the heat pump with the heating coil OFF [kg/s]
\(h_{out,coil\;off}\) = enthalpy of air exiting the heat pump with the heating coil OFF [J/kg]
\(\Delta_{sen,full load}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions
\[\begin{array}{l}{\Delta _{sen,\;HighestSpeed}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad \quad + \left( {{{\dot m}_{_{HighestSpeed}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
where:
Frac = Control zone air fraction with respect to the system mass flow rate
\(\Delta_{sen,coil off}\) = Sensible load difference between the system output node and the zone inlet node with the heating coil OFF conditions
\[\begin{array}{l}{\Delta _{sen,\;coil\;off}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;coil\;off}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{coil\;off}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;coil\;off}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the heat pump’s DX heating coil output full load at the highest speed is insufficient to meet the entire heating load, the remaining heating load is passed to the supplemental heating coil. If the heat pump model determines that the outdoor air temperature is below the minimum outdoor air temperature for compressor operation (specified by the user), the compressor is turned off and the entire heating load is passed to the supplemental gas or electric heating coil. The heat pump exiting air conditions and energy consumption are calculated and reported by the individual component models (fan, DX heating coil, and supplemental gas or electric heating coil).
If the total heating load to be met by the system is less than the sensible heating rate at the highest speed, then the following steps are performed.
Calculate the sensible heating energy rate at Speed 1
\[FullHeatOutpu{t_{Speed1}} = ({\dot m_{Speed1}}){({h_{out,fullload}} - {h_{control\;zone}})_{HR\min }} - {\Delta _{sen,\;Speed1}}\]
where:
\({\dot m_{Speed1}}\) = air mass flow rate through heat pump at Speed 1 [kg/s]
\(\Delta_{sen,Speed1}\) = Sensible load difference between the system output node and the zone inlet node at full-load conditions at Speed 1
\[\begin{array}{l}{\Delta _{sen,\;Speed1}} = \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}{\left( {{h_{Out,\;full\;load}} - {h_{Zone\;Inlet}}} \right)_{HR\min }}\\ \quad \quad \quad \quad + \left( {{{\dot m}_{_{Speed1}}} - \frac{{{{\dot m}_{_{Zone\;Inlet}}}}}{{Frac}}} \right){\left( {{h_{Out,\;full\;load}} - {h_{_{Control\;Zone}}}} \right)_{HR\min }}\end{array}\]
If the sensible heating energy rate delivered by the heat pump at Speed 1 is greater or equal to the sensible load, the cycling ratio (part-load ratio) for the heat pump is estimated.
\[\begin{array}{l}CyclingRatio = \frac{{ABS(HeatingCoilSensibleLoad)}}{{FullHeatingCoilCapacity}}\\ \;\;\;\;\;\;\; = MAX\left( {0.0,\frac{{ABS(Heat\;Pump\;Heating\;Load - AddedFanHeat)}}{{ABS(FullHeatOutpu{t_{Speed1}} - AddedFanHea{t_{Speed1}})}}} \right)\end{array}\]
where
AddedFanHeat = generated supply air fan heat, which is a function of part load ratio and as internal component heating load [W].
AddedFanHeatSpeed1 = generated supply air fan heat at Speed 1 (part load ratio=1) [W].
Since the part-load performance of the DX heating coil is frequently non-linear (Ref: Single-Speed Electric Heat Pump DX Air Heating Coil), and the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan), the final part-load ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the heat pump’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{Heat\,Pump\,Heating\,Load - HeatPumpOutpu{t_{Cycling}}}}{{Heat\,Pump\,Heating\,Load}}\]
where:
HeatPumpOutputCycling= heat pump delivered sensible capacity for Speed 1 operating at a specific cycling ratio (W)
\[HeatPumpOutpu{t_{cycling}} = {\dot m_{_{HeatPump}}}{\left( {{h_{out}} - {h_{Control\;Zone}}} \right)_{HR\min }} - {\Delta _{cycling}}\]
where
\({\dot m_{HeatPump}}\) = average air mass flow rate defined in the next section [kg/s]
hout = enthalpy of air exiting the heat pump at part load conditions [J/kg]
Δcycling = average sensible load difference between the system output node and the zone inlet node
\[\begin{array}{l}\;{\Delta _{cycling}} = \frac{{{{\dot m}_{_{ZoneInlet}}}}}{{frac}}\left( {{h_{ZoneInlet}} - {h_{Control\;Zone}}} \right) + \left( {{{\dot m}_{_{HeatPump}}} - \frac{{{{\dot m}_{_{ZoneInlet}}}}}{{frac}}} \right)\left( {{h_{Out}} - {h_{Control\;Zone}}} \right)\\ \;\end{array}\]
\({\dot m_{_{ZoneInlet}}}\) = Air mass flow rate in the supply inlet node in the controlled zone [kg/s]
For this case where speed 1 operation was able to meet the required heating load, the speed ratio is set to zero and speed number is equal to 1.
If the heat pump’s heating output at full load for Speed 1 is insufficient to meet the entire heatling load, the Cycling ratio (PartLoadRatio) is set equal to 1.0 (compressor and fan are not cycling). Then the heating speed is increased and the delivered sensible capacity is calculated. If the full load sensible capacity at Speed n is greater than or equal to the sensible load, the speed ratio for the heat pump is estimated:
\[Speed{\kern 1pt} Ratio = \frac{{ABS(Heat{\kern 1pt} Pump{\kern 1pt} Heating{\kern 1pt} Load - AddeFanHeat - Full{\kern 1pt} Heat{\kern 1pt} Outpu{t_{Speed{\kern 1pt} \;n - 1}})}}{{ABS(Full{\kern 1pt} HeatOutpu{t_{Speed\;n}} - Full{\kern 1pt} HeatOutpu{t_{Speed\;n - 1}})}}\]
Although a linear relationship is assumed by applying the speed ratio to obtain the effective capacity and air mass flow rate between speed n and n-1, the outlet node conditions are dependent on the combined outputs and may not be linear. In addition, the supply air fan heat varies based on heating coil operation for the case of cycling fan/cycling coil (AUTO fan). Therefore, the final speed ratio for the heating coil compressor and fan are determined through iterative calculations (successive modeling of the heating coil and fan) until the heat pump’s heating output matches the heating load to be met within the convergence tolerance. The convergence tolerance is fixed at 0.001 and is calculated based on the difference between the load to be met and the heat pump’s heating output divided by the load to be met.
\[Tolerance = 0.001 \ge \frac{{Heat\,Pump\,Heating\,Load - HeatPumpOutpu{t_{SpeedRatio}}}}{{Heat\,Pump\,Heating\,Load}}\]
where:
HeatPumpOutputSpeedRatio = heat pump delivered sensible capacity between two consecutive speeds at a specific ratio [W]
\[\begin{array}{l}HeatPumpOutpu{t_{SpeedRatio}} = (SpeedRatio)FullHeatOutpu{t_{Speed\;n}}\\ \;\;\;\;\;\;\; = (1 - SpeedRatio)FullHeatOutpu{t_{Speed\;n - 1}} - AddedFanHea{t_{SpeedRatio}}\end{array}\]
Where
AddedFanHeatSpeedRatio = generated supply air fan heat at a specific speed ratio [W]
In this case, the reported cycling ratio is 1 and speed number is equal to n.
Air Mass Flow Rate Calculation[LINK]
The air mass flow rate calculations during heating operation are the same as those described above for cooling operation.
Fan Placement[LINK]
Supply air fan placement impacts the iteration strategy. When the fan placement type is blow through, the air mass flow rate and coil part load factor (PLF) affect the fan outlet conditions. Since the fan is upstream of the coil components with this fan placement, the fan outlet conditions are calculated without knowing the next component’s performance at the beginning of each iteration. DX coil performance is strongly dependent on the inlet conditions, so without correct inlet conditions the DX coil components may not be simulated correctly. Therefore, the heat pump components are called twice for each iteration when fan placement is ‘blow through’. The correct part load factor for the fan component is obtained after the first call, so that the more realistic fan outlet conditions are used to simulate the coil performance in the second call. This extra call to the heat pump components is not required for the draw through fan since the supply air fan is located downstream of the DX coils with this fan placement.
Waste Heat Calculation[LINK]
When the heat recovery is active (the value of the Design Heat Recovery Water Flow Rate field is greater than 0), the outlet node temperature of heat recovery is calculated based on the recoverable waste heat generated by its child objects (Coil:Cooling:DX:MultiSpeed and Coil:Heating:DX:MultiSpeed):
\[{T_{outlet}} = {T_{inlet}} + \frac{{{Q_{WasteHeat}}}}{{{C_p}{{\dot m}_{hr}}}}\]
where
Toutlet = outlet node temperature of heat recovery, C
Tinlet = inlet node temperature of heat recovery, C
QWasteHeat = recoverable waste heat generated by its child objects, W
Cp = inlet node temperature of heat recovery, C
\({\dot m_{hr}}\) = mass flow rate of heat recovery, kg/s
If the outlet node temperature is above the value of the Maximum Temp for Heat Recovery field, the outlet node temperature is reset to the value of Maximum Temp for Heat Recovery.
DX Cooling Package[LINK]
Overview[LINK]
The DX cooling package subsystem model provides a “virtual” component that consists of a DX air cooling coil component as shown in the figure below. The CoilSystem:Cooling:DX input object provides a container component that controls the associated DX cooling coil which is specified in a separate object. This coil can be specified anywhere in the air loop simulation and is controlled by the setpoint(s) on the control node. Optional dehumidification controls may also be specified. CoilSystem:Cooling:DX assumes continuous fan operation for any given time step, because it is not able to control cycling fan operation in the way that other AirLoopHVAC:Unitary* systems can.
This system does not need any plant specification and will provide the electric consumption necessary to operate the compressor and the condenser fan.
Controls[LINK]
The system calculates the current sensible load using the temperature of the inlet node and the System Node Setpoint Temp on the control node. If the control node is not the outlet node, the desired outlet node temperature is adjusted for the current temperature difference between the outlet node and the control node. Likewise, the current latent load is calculated using the humidity ratio of the inlet node and the System Node Humidity Ratio Max on the control node. The controls determine the required coil run-time fraction and dehumidification mode (if applicable) using the steps outlined below.
Step 1 - Meet Sensible Load Requirement[LINK]
The controls first attempt to meet the sensible requirement. The specified DX coil model is called with a part-load ratio (PLR) of 1.0 to determine the full-load output of the coil. This is compared with the desired outlet node temperature and a sensible PLR is calculated. If the PLR is <1.0, a Regula-Falsi iteration routine is called to determine the coil run-time fraction which results in the desired outlet node temperature. For a variable-speed DX cooling coil, if the load is smaller than the sensible capacity at the lowest speed, the coil run-time fraction is determined in the same way as a single-speed DX cooling coil. Otherwise, its speed level and speed ratio between two neighboring speeds are selected to match the load.
Step 2 - Meet Latent Load Requirement (if activated)[LINK]
If dehumidification controls are active, the leaving humidity ratio resulting from operation to meet the sensible load (Step 1 above) is compared with the desired outlet node humidity ratio. If the humidity requirement is already met, then no further control action is taken. If the humidity requirement has not been met, then the coil is re-simulated depending on the type of humidity control.
Step 2a - Humidity Control = MultiMode[LINK]
If the humidity control type is MultiMode, then the coil’s enhanced dehumidification mode is activated when the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode or the heat exchanger is activated when the coil type is CoilSystem:Cooling:DX:CoolingHeatExchangerAssisted and Step 1 above is repeated to meet the sensible load using the coil performance resulting from the enhanced dehumidificaiton mode. This is a semi-passive approach to dehumidification which may fall short or may exceed the dehumidification requirement. If the user has specified Run on Latent Load = Yes in the CoilSystem:Cooling:DX object, and there is no sensible load to be met, then the system will try to meet the entire dehumidification load. If dehumidification mode should not be active when there is no sensible load, then choose Run on Latent Load = No.
Step 2b - Humidity Control = CoolReheat[LINK]
If the humidity control type is CoolReheat, the coil is re-simulated to achieve the desired outlet node humidity ratio. This option is valid for all cooling coil types. When the coil type is Coil:Cooling:DX:TwoStageWithHumidityControlMode, only the cooling performance mode is used for this step and enhanced dehumidification mode is not activated.
DX Heating Package[LINK]
Overview[LINK]
The DX heating package subsystem model provides a “virtual” component that consists of a DX air-to-air heating coil component and associated controls. The CoilSystem:Heating:DX input object provides a container component that controls the associated DX heating coil which is specified in a separate object. See the entry called Single-Speed and Variable-Speed Electric Heat Pump DX Air Heating Coil for details of the coil model itself. This coil can be specified anywhere in the air loop simulation and is controlled by the setpoint on the heating coil’s outlet node. This model is analogous to the model for CoilSystem:Cooling:DX which is similar but for cooling. The model assumes continuous fan operation for any given time step, because it is not able to control cycling fan operation in the way that other AirLoopHVAC:Unitary* systems can.
This system does not need any plant specification and will provide the electric consumption necessary to operate the compressor and the condenser fan.
Controls[LINK]
The DX heating package system calculates how the coil should operate to meet current sensible load using the temperature of the inlet node and the System Node Setpoint Temp on the outlet node. The controls determine the required coil run-time fraction to meet the sensible requirement. The Single-Speed Electric Heat Pump DX Air Heating Coil model is called with a part-load ratio (PLR) of 1.0 to determine the full-load output of the coil. If the PLR is <1.0, a Regula-Falsi iteration routine is called to determine the coil run-time fraction which results in the desired outlet node temperature. For a variable-speed DX heating coil, if the load is smaller than the heating capacity at the lowest speed, the coil run-time fraction is determined in the same way as a single-speed DX heating coil. Otherwise, its speed level and speed ratio between two neighboring speeds are selected to match the load.
Desiccant Dehumidifier Package[LINK]
Overview[LINK]
The input object Dehumidifier:Desiccant:System provides a model that packages components for a desiccant-based subsystem that dehumidifies an air stream, normally called the process air stream. A second heated air stream, called the regeneration air stream, is used to remove the collected moisture from the desiccant heat exchanger and this moisture-laden air is then usually exhausted from the building. This Dehumidifier:Desiccant:System object is similar to the Dehumidifier:Desiccant:NoFans object but has some additional modeling capabilities.
The Dehumidifier:Desiccant:System desiccant dehumidifier object in EnergyPlus is a compound object that can be placed anywhere in an air loop. Common locations for this object are in an AirLoopHVAC:OutdoorAirSystem or in the main air loop downstream of a cooling coil (postcooling desiccant dehumidifier). This compound object coordinates the operation of several ‘children’ objects: a desiccant heat exchanger, a regeneration air fan, and an optional regeneration air heater. If this dehumidifier is placed in the main air loop immediately downstream of a direct expansion (DX) cooling coil, then the dehumidifier’s operation can be coordinated with the operation of the companion DX coil and it is also possible to specify that the DX system’s condenser waste heat can be used to help regenerate the desiccant heat exchanger. For the case of condenser waste heat regeneration, an optional exhaust fan can also be modeled by this desiccant dehumidifier compound object to help maintain a setpoint temperature for air entering the regeneration side of the desiccant heat exchanger. Refer to the EnergyPlus Input Output Reference for the specific input syntax for this desiccant dehumidifier object.
Control Logic[LINK]
The model first decides if the dehumidifier can operate for the simulation time step, based on its availability schedule and if there is air flow detected on the process air inlet node. If available to operate, then the target humidity ratio for the process outlet air is determined based on the maximum humidity ratio setpoint on the control node (System Node Setpoint Humidity Ratio Max). If the control node is not the process air outlet node, the target humidity ratio is adjusted for the current humidity ratio difference between the process air outlet node and the control node. If the humidity ratio of the process inlet air is greater than the target humidity ratio for the process outlet air, then the dehumidifier operates to meet the target to the extent possible.
Once it is determined that the dehumidifier should operate, the components upstream of the desiccant heat exchanger’s regeneration inlet are modeled. The actual components that are modeled depend on the configuration specified by the user.
If the waste heat from the companion cooling coil is being used to heat the regeneration air, then this model determines the temperature of the air leaving the cooling coil condenser. The user may also specify a setpoint temperature for the regeneration air entering the desiccant heat exchanger and an optional exhaust fan, which can impact the condenser leaving air temperature. For this case, the exhaust fan is used to control the condenser leaving air temperature by boosting the air flow rate through the condenser to meet the setpoint temperature (minus regeneration fan heat if blow through fan placement).
The exhaust fan power is determined as follows:
\[\begin{array}{l}If\,dehumidifier\,is\,operating:\\ \,\,\,PL{R_{exhaust}} = \,\frac{{{{\mathop m\limits^ \bullet }_{exhaust}}}}{{\left( {{\rho _{Std}} * {{\mathop {\rm{V}}\limits^ \bullet }_{exhaust,\,max}}} \right)}}\\ \,\,\,{P_{exhaust}} = \,{P_{exhaust,\,max}} * \,ExhFanModFac \\ If\,dehumidifier\,\,is\,\,not\,\,operating\,\,but\,\,companion\,\,coil\,\,is\,\,operating:\\ \,\,\,{P_{exhaust}} = \,{P_{exhaust,\,max}} * \,PL{R_{companion\,coil}}\end{array}\]
where:
\(PL{R_{exhaust}}\) = part load ratio of the exhaust fan
\({\mathop {\rm{V}}\limits^ \bullet _{exhaust,\,max}}\) = exhaust fan maximum volumetric flow rate, user input (m3/s)
\({\rho _{Std}}\) = density of air at standard temperature and pressure [dry air at 20°C] (m3/kg)
\({P_{exhaust,\,max}}\) = exhaust fan maximum power, user input (W)
\(ExhFanModFac\) = exhaust fan power modifier curve evaluated at PLRexhaust. If modifier curve not provided by the user, then this factor is assumed to be 1.0.
\(PL{R_{companion\,coil}}\) = part load ratio of the companion cooling coil
\({P_{exhaust}}\) = output variable ‘Dehumidifier Exhaust Fan Electric Power, W’
The exhaust fan electric consumption is then calculated as:
\[{E_{exhaust}} = {P_{exhaust}}*\,\,TimeStepSys\,\,*\,\,3600.\]
where:
\({E_{exhaust}}\) = output variable ‘Dehumidifier Exhaust Fan Electric Energy, J’
\(TimeStepSys\) = HVAC system simulation time step, hr
Once the outlet conditions from the companion coil condenser are determined (if present), then the regeneration air fan (if blow through configuration) and regeneration air heater (if present) are simulated. To the extent possible (e.g., if the heater is available to operate based on its availability schedule and it has sufficient heating capacity), the regeneration air heater operates to raise its outlet air temperature to the specified regeneration inlet air setpoint temperature.
With the inlet air conditions to the regeneration and process sides of the desiccant heat exchanger now known, the performance of the desiccant heat exchanger is modeled. If the desiccant dehumidifier is specified with a companion cooling coil upstream of the heat exchanger’s process inlet, then the model assumes that the dehumidifier operates at the same time as the companion coil (same part-load ratio). If not, then the desiccant dehumidifier model calculates the fraction of time it must operate to meet the process outlet air maximum humidity target (setpoint) using the following equation:
\[\begin{array}{l}\,DDPartLoadRatio = \,\frac{{\left( {{w_{Proc,\,\,in}} - {w_{max, set\,point}}} \right)}}{{\left( {{w_{Proc,\,\,in}} - {w_{Proc,\,\,out,HXon}}} \right)}} \\ DDPartLoadRatio = MAX\left( {0.0,DDPartLoadRatio} \right) \\ DDPartLoadRatio = MIN\,\left( {1.0,DDPartLoadRatio} \right)\end{array}\]
where:
\(\,DDPartLoadRatio\) = output variable ‘Dehumidifier Part Load Ratio’
\({w_{Proc,\,\,in}}\) = process inlet air humidity ratio (kg/kg)
\({w_{max, set\,point}}\) = target humidity ratio (setpoint) for the process outlet air (kg/kg)
\({w_{Proc,\,\,out,HXon}}\) = process outlet air humidity ratio when the desiccant heat exchanger operates (kg/kg)
After all of the desiccant dehumidifier components are modeled at the appropriate part load ratio, the water removal rate and water removed are calculated.
\[\begin{array}{l}{\mathop m\limits^ \bullet _{water\_removed,Proc}} = \,{\mathop m\limits^ \bullet _{Proc,in}}\left( {{w_{Proc,\,\,in}} - {w_{Proc,\,\,out}}} \right) \\ {m_{water\_removed,Proc}} = {\mathop m\limits^ \bullet _{water\_removed,Proc}}*\,\,TimeStepSys\,\,*\,\,3600.\end{array}\]
where:
\({\mathop m\limits^ \bullet _{water\_removed,Proc}}\) = output variable ‘Dehumidifier Removed Water Mass Flow Rate, kg/s’
\({\mathop m\limits^ \bullet _{Proc,in}}\) = air mass flow rate at the process air inlet node (kg/s)
\({w_{Proc,\,\,out}}\) = process outlet air humidity ratio (kg/kg)
\({m_{water\_removed,Proc}}\) = output variable ‘Dehumidifier Removed Water Mass, kg’
References[LINK]
ASHRAE. 2004. Chapter 22: Desiccant Dehumidification and Pressure-Drying Equipment. 2004 ASHRAE HVAC Systems and Equipment Handbook. Atlanta, GA: American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc. http://www.ashrae.org
Kosar, D. 2006. Dehumidification Enhancements, ASHRAE Journal, Vol. 48, No. 2, February 2006. http://www.ashrae.org
Kosar, D. et al. 2006. Dehumidification Enhancement of Direct Expansion Systems Through Component Augmentation of the Cooling Coil. 15th Symposium on Improving Building Systems in Hot and Humid Climates, July 24-26, 2006. http://www.hothumidsymposium.org/
Unitary Water-To-Air Heat Pump[LINK]
Overview[LINK]
The input object AirLoopHVAC:UnitaryHeatPump:WaterToAir provides a model for a water-to-Air heat pump that is a “virtual” component that consists of an on/off fan component, a water-to-air heat pump cooling coil, a water-to-air heat pump heating coil, and a gas or electric supplemental heating coil. The specific configuration of the blowthru heat pump is shown in the following figure. For a drawthru heat pump, the fan is located between the water-to-air heat pump heating coil and the supplemental heating coil. The configuration of the water-to-air heat pump in the air loop is similar to an air-to-air heat pump. In addition, a water-to-air heat pump has a water loop connection on its source side. The water loop can be served by a condenser loop (like GHE for Ground source systems), or by a cooling tower/ boiler plant loop (for water loop systems).
There are two different models for water-to-air heat pump cooling and heating coils. Cooling and heating coils are modeled using a Single Speed or Variable Speed Equation Fit model or a Parameter Estimation model. The parameter estimation procedure is quite detailed and the equation fit model is designed to simplify the user inputs. Each model is discussed in short in the following sections. The Variable-Speed Equation Fit model is described in a separate section, as Coil:Cooling:WaterToAirHeatPump:VariableSpeedEquationFit and Coil:Heating:WaterToAirHeatPump:VariableSpeedEquationFit.
Single Speed Equation-Fit Model:[LINK]
This section describes the equation-fit model for Water-to-Air heat pump (Object names: Coil:Cooling:WaterToAirHeatPump:EquationFit and Coil:Heating:WaterToAirHeatPump:EquationFit). This documentation is derived from the M.S. dissertation of Tang (2005) which is available on the Oklahoma State University web site http://www.hvac.okstate.edu/. The model uses five non-dimensional equations or curves to predict the heat pump performance in cooling and heating mode. The methodology involved using the generalized least square method to generate a set of performance coefficients from the catalog data at indicated reference conditions. Then the respective coefficients and indicated reference conditions are used in the model to simulate the heat pump performance. The variables or inlet conditions that influenced the water-to-air heat pump performance are load side inlet water temperature, source side inlet temperature, source side water flow rate and load side water flow rate. The governing equations for the cooling and heating mode are as following:
Cooling Mode:
\[\frac{{Q{}_{total}}}{{Q{}_{total,ref}}} = A1 + A2\left[ {\frac{{{T_{wb}}}}{{{T_{ref}}}}} \right] + A3\left[ {\frac{{T{}_{w,in}}}{{T{}_{ref}}}} \right] + A4\left[ {\frac{{{{\dot V}_{air}}}}{{{{\dot V}_{air,ref}}}}} \right] + A5\left[ {\frac{{{{\dot V}_w}}}{{{{\dot V}_{w,ref}}}}} \right]\]
\[\frac{{{Q_{sens}}}}{{{Q_{sens,ref}}}} = B1 + B2\left[ {\frac{{T{}_{db}}}{{T{}_{ref}}}} \right] + B3\left[ {\frac{{T{}_{wb}}}{{T{}_{ref}}}} \right] + B4\left[ {\frac{{T{}_{w,in}}}{{T{}_{ref}}}} \right] + B5\left[ {\frac{{{{\dot V}_{air}}}}{{{{\dot V}_{air,ref}}}}} \right] + B6\left[ {\frac{{\dot V{}_w}}{{\dot V{}_{w,ref}}}} \right]\]
\[\frac{{Power{}_c}}{{Power{}_{c,ref}}} = C1 + C2\left[ {\frac{{{T_{wb}}}}{{{T_{ref}}}}} \right] + C3\left[ {\frac{{T{}_{w,in}}}{{T{}_{ref}}}} \right] + C4\left[ {\frac{{{{\dot V}_{air}}}}{{{{\dot V}_{air,ref}}}}} \right] + C5\left[ {\frac{{{{\dot V}_w}}}{{{{\dot V}_{w,ref}}}}} \right]\]
Heating Mode:
\[\frac{{{Q_h}}}{{Q{}_{h,ref}}} = E1 + E2\left[ {\frac{{{T_{db}}}}{{{T_{ref}}}}} \right] + E3\left[ {\frac{{T{}_{w,in}}}{{T{}_{ref}}}} \right] + E4\left[ {\frac{{{{\dot V}_{air}}}}{{{{\dot V}_{air,ref}}}}} \right] + E5\left[ {\frac{{{{\dot V}_w}}}{{{{\dot V}_{w,ref}}}}} \right]\]
\[\frac{{Powe{r_h}}}{{Power{}_{h,ref}}} = F1 + F2\left[ {\frac{{{T_{db}}}}{{{T_{ref}}}}} \right] + F3\left[ {\frac{{T{}_{w,in}}}{{T{}_{ref}}}} \right] + F4\left[ {\frac{{{{\dot V}_{air}}}}{{{{\dot V}_{air,ref}}}}} \right] + F5\left[ {\frac{{{{\dot V}_w}}}{{{{\dot V}_{w,ref}}}}} \right]\]
Assuming no losses, the source side heat transfer rate for cooling and heating mode is calculated as following;
\[{Q_{source,c}} = {Q_{total}} + Powe{r_c}\]
\[{Q_{source,h}} = {Q_h} - Powe{r_h}\]
where:
\(A1 - F5\) = Equation fit coefficients for the cooling and heating mode
\({T_{ref}}\) = 283K
\({T_{w,in}}\) = Entering water temperature, K
\({T_{db}}\) = Entering air dry-bulb temperature, K
\({T_{wb}}\) = Entering air wet-bulb temperature, K
\({\dot V_{air}}\) = Load side air volumetric flow rate, m3/s
\({\dot V_w}\) = Source side water volumetric flow rate, m3/s
\({Q_{total}}\) = Total cooling capacity, W
\({Q_{sens}}\) = Sensible cooling capacity, W
\(Powe{r_c}\) = Power consumption (cooling mode), W
\({Q_{source,c}}\) = Source side heat transfer rate (cooling mode), W
\({Q_h}\) = Total heating capacity, W
\(Powe{r_h}\) = Power consumption (heating mode), W
\({Q_{source,h}}\) = Source side heat transfer rate (heating mode), W
The inlet conditions or variables are divided by the reference conditions. This formulation allows the coefficients to fall into smaller range of values. Moreover, the value of the coefficient indirectly represents the sensitivity of the output to that particular inlet variable. The reference conditions used when generating the performance coefficients must be the same as the reference conditions used later in the model. The reference temperature \({T_{ref}}\) is fixed at 283K. Temperature unit of Kelvin is used instead of Celsius to keep the ratio of the water inlet temperature and reference temperature positive value should the water inlet temperature drop below the freezing point.
For cooling mode, the reference conditions; reference load side air volumetric flow rate \(\left( {{{\dot V}_{air,ref}}} \right)\) ,reference source side water volumetric flow rate \(\left( {{{\dot V}_{w,ref}}} \right)\) ,reference sensible capacity \(\left( {{Q_{sens,ref}}} \right)\) and reference power input \(\left( {Powe{r_{c,ref}}} \right)\) are the conditions when the heat pump is operating at the highest cooling capacity or reference cooling capacity \(\left( {{Q_{total,ref}}} \right)\) indicated in the manufacturer’s catalog. Note that the reference conditions for heating mode might differ from the reference conditions specified for the cooling mode.
Coefficient estimation procedure:[LINK]
The generalized least square method is used to generate the coefficients. This method utilizes an optimization method which calculates the coefficients that will give the least amount of differences between the model outputs and the catalog data. A set of coefficients for the cooling mode is generated which includes A1-A5 for total cooling capacity, B1-B6 for sensible cooling capacity, and C1-C5 for power consumption. The same procedure is repeated for the heating mode to generate the coefficients E1-E5 and F1-F5. An information flow chart showing the inputs, reference conditions, performance coefficients and outputs are shown in the figure below:
High Humidity Control with WaterToAir HeatPump Equation Fit model[LINK]
The specific configuration of the WaterToAir HeatPump with supplemental heating coil is shown above (see Figure 234). This figure shows the fan placement when a blow through fan is specified. If a draw through fan is specified, the fan is located between the heating coil and the reheat coil. The system is controlled to keep the high relative humidity in the control zone from exceeding the setpoint specified in the object ZoneControl:Humidistat. When high humidity control is specified and the compressor operates, the heatpump always operates at the cooling air flow rate when a zone heating load is present as determined by the zone thermostat. High humidity control is specified as either None, or CoolReheat in the Dehumidification Control Type input field. CoolReheat is specified when a DX cooling coil is used to over-cool the supply air stream in order to meet the zone latent load. In this case, a supplemental heating coil will ensure the zone temperature does not fall below the zone heating temperature set point. If the dehumidification control type is selected as None, the WaterToAir HeatPump uns only to meet the sensible cooling load. A supplemental heating coil is required for all dehumidification control types.
The model first calculates the PartLoadRatio required meeting the sensible cooling load. The heatpump’s sensible cooling load is determined from the control zone sensible cooling load to the cooling setpoint and the control zone air flow fraction to maintain the dry-bulb temperature setpoint in the control zone:
\[HeatPumpCoolingLoad = \,\frac{{ControlZoneCoolingLoad}}{{ControlZoneAirFlowFraction}}\]
The heatpump’s sensible cooling load to be met and the full load cooling output are used to calculate the sensible the part-load ratio iteratively based on user specified convergence criterion.
\[PartLoadRatio = MAX\left( {0.0,\,\frac{{ABS\left( {HeatPumpCoolingLoad - NoCoolOutput} \right)}}{{ABS\left( {FullCoolOutput - NoCoolOutput} \right)}}} \right)\]
When the heat pumps sensible cooling capacity meets the system sensible cooling load at a given sensible part load ratio, then the Heat pump meets the controlled zone cooling setpoint temperature. If a moisture (latent) load exists because the control zone humidity has exceeded the setpoint, the total moisture load to be met by the heat pumps (HeatPumpMoistureLoad) is calculated based on the control zone moisture load and the control zone air flow fraction.
\[HeatPumpMoistureLoad = \,\frac{{ControlZoneMoitureLoad}}{{ControlZoneAirFlowFraction}}\]
Then the LatentPartLoadRatio required to meet the high humidity setpoint is calculated as follows:
\[LatentPartLoadRatio = MIN\left( {PL{R_{Min}},\,\frac{{ABS\left( {HeatPumpMoistureLoad - NoLatentOutput} \right)}}{{ABS\left( {FullLatentOutput - NoLatentOutput} \right)}}} \right)\]
The model uses the greater of the two part-load ratios, PartLoadRatio or LatentPartLoadRatio, to determine the operating part-load ratio of the Heat Pump’s DX cooling coil.
\[LatentPartLoadRatio = MAX\left( {PartLoadRatio,\,LatentPartLoadRatio} \right)\]
As previously described, iterations are performed to converge on the solution within the convergence tolerance.
Where,
\(ControlZoneCoolingLoad\) = the control zone sensible cooling load to the cooling setpoint, (W).
\(ControlZoneMoistureLoad\) = the control zone moisture load to the dehumidifying relative humidity setpoint, (W).
\(ControlZoneAirFlowFraction\) = the supply air fraction that goes though the control zone, (-).
FullLatentOutput =the Heat Pump’s latent cooling energy rate at full-load conditions, W
NoLatentOutput =the Heat Pump’s latent cooling energy rate with cooling coil OFF, W
\(PartLoadRatio\) =the heat pump’s part-load-ratio required to meet system sensible load, (-).
\(LatentPartLoadRatio\) =the heat pump’s part-load-ratio required to meet system moisture load, (-).
\(PL{R_{MIN}}\) =the minimum part-load ratio, which is usually 0.0. For the case when the latent capacity degradation model is used (Ref: DX Cooling Coil Model), this value is the minimum part-load ratio at which the cooling coil will dehumidify the air.
When the predicted zone air temperature is above the heating setpoint and if there is a dehumidification load, the supplemental heating coil load is required to offset the excess cooling as shown in Figure 236. If the model determines that the LatentPartLoadRatio is to be used as the operating part-load ratio of the heatpump’s cooling coil, the supplemental coil is used to offset the excess sensible capacity provided by the unit. The model first checks the sensible load that exists for the current simulation time step (predicted zone temperature with no HVAC operation compared to the thermostat setpoint temperatures). If a sensible cooling load or no sensible cooling or heating load exists (see Figure 236), the model calculates the difference between the sensible heating load required to reach or maintain the heating dry-bulb temperature setpoint and the actual sensible cooling energy rate delivered by the heat pump (with LatentPartLoadRatio). In this case, the supplemental heating coil is used to offset the excess sensible cooling energy provided by the DX cooling coil (if any) that could have caused an overshoot of the heating dry-bulb temperature setpoint. Note that when a humidistat is used and high humidity control is required, the zone dry-bulb temperature will typically move toward the heating temperature setpoint when a high moisture (latent) load exists.
If a heating load exists (Figure 237), the supplemental heating coil is used to meet the heating coil load and at the same time offset the entire sensible cooling energy rate of the DX cooling coil (to meet the humidistat setpoint). Note that when a heating load exists and high humidity control is required, the heat pump operates at the user-specified cooling air flow rate for the entire simulation time step. As with the fan, and DX cooling coil, report variables associated with supplemental heating coil performance (e.g., heating coil energy, heating coil rate, heating coil gas or electric energy, heating coil runtime fraction, etc.) are managed in the supplemental (heating) coil object.
Parameter Estimation Model[LINK]
The steady state simulation model (Object: AirLoopHVAC:UnitaryHeatPump:WaterToAir) for a water-to-air vapor compression heat pump is described in this section. The model is implemented under the air-loop manager similar to the algorithm discussed under AirLoopHVAC:UnitaryHeatPump. The heat pump ‘coil’ objects (Coil:Cooling:WaterToAirHeatPump:ParameterEstimation andCoil:Heating:WaterToAirHeatPump:ParameterEstimation) actually consist of a steady state simulation of the unitary heat pump in cooling or heating mode respectively. This documentation is derived from the Ph.D. dissertation of Hui Jin which is available on the Oklahoma State University web site http://www.hvac.okstate.edu/. The model parameters, solution technique and solution algorithm are all identical to that of the water to water heat pump. The only difference between the two models is in the modeling of the water to air heat exchanger.
The effectiveness of this heat exchanger is given by
\[\varepsilon = 1 - {e^{ - NTU}}\]
Where NTU is defined by
\[NTU = \frac{{UA}}{{(\dot mC{}_p){}_{water/air}}}\]
UA for the source side and the load side are two of the parameters estimated in the parameter estimation procedure.
Additional model details and a discussion of the parameters and parameter estimation technique are described in the following section on Water to Water Heat Pumps.
Water To Water Heat Pumps[LINK]
There are two water-water heat pump models available in EnergyPlus which are parameter estimation based model and equation-fit model. Detailed descriptions of the model are available in the references Tang and Jin
Equation Fit Water To Water Heat Pump Model[LINK]
This section describes the equation-fit model for water-to-water heat pump. (Object names: HeatPump:WaterToWater:EquationFit:Cooling & HeatPump:WaterToWater:EquationFit:Heating). This documentation is derived from the M.S. dissertation of Tang (2005) which is available on the Oklahoma State University web site http://www.hvac.okstate.edu/. The model uses four non-dimensional equations or curves to predict the heat pump performance in cooling and heating mode. The methodology involved using the generalized least square method to generate a set of performance coefficients from the catalog data at indicated reference conditions. Then the respective coefficients and indicated reference conditions are used in the model to simulate the heat pump performance. The variables that influenced the water-to-water heat pump performance are load side inlet water temperature, source side inlet temperature, source side water flow rate and load side water flow rate. The governing equations for the cooling and heating mode are as following:
Cooling Mode:
\[\frac{{Q{}_c}}{{Q{}_{c,ref}}} = A1 + A2\left[ {\frac{{T{}_{L,in}}}{{T{}_{ref}}}} \right] + A3\left[ {\frac{{T{}_{S,in}}}{{T{}_{ref}}}} \right] + A4\left[ {\frac{{{{\dot V}_L}}}{{{{\dot V}_{L,ref}}}}} \right] + A5\left[ {\frac{{{{\dot V}_S}}}{{{{\dot V}_{S,ref}}}}} \right]\]
\[Power_c = \frac{Q_c}{COP_c}\]
Heating Mode:
\[\frac{{{Q_h}}}{{Q{}_{h,ref}}} = C1 + C2\left[ {\frac{{T{}_{L,in}}}{{T{}_{ref}}}} \right] + C3\left[ {\frac{{T{}_{S,in}}}{{T{}_{ref}}}} \right] + C4\left[ {\frac{{{{\dot V}_L}}}{{{{\dot V}_{L,ref}}}}} \right] + C5\left[ {\frac{{{{\dot V}_S}}}{{{{\dot V}_{S,ref}}}}} \right]\]
\[Power_h = \frac{Q_h}{COP_h}\]
Assuming no losses, the source side heat transfer rate for cooling and heating mode is calculated as following;
\[{Q_{source,c}} = {Q_c} + Powe{r_c}\]
\[{Q_{source,h}} = {Q_h} - Powe{r_h}\]
Where:
A1 – B5 = Equation fit coefficients for the cooling and heating mode
\({T_{ref}}\) = 283.15K
\({T_{L,in}}\) = Entering load side water temperature, K
\({T_{S,in}}\) = Entering source side water temperature, K
\({\dot V_L}\) = Load side volumetric flow rate, m3/s
\({\dot V_S}\) = Source side volumetric flow rate, m3/s
\({Q_c}\) = Load side heat transfer rate (cooling mode), W
\(Powe{r_c}\) = Power consumption (cooling mode), W
\({Q_{source,c}}\) = Source side heat transfer rate (cooling mode), W
\({Q_h}\) = Load side heat transfer rate (heating mode), W
\(Powe{r_h}\) = Power consumption (heating mode), W
\({Q_{source,h}}\) = Source side heat transfer rate (heating mode), W
COPc = Cooling coefficient of performance, W/W
COPh = Heating coefficient of performance, W/W
If the load side heat transfer rate (Qc or Qh) or power consumption (Powerc or Powerh) are less than or equal to zero, then the heat pump is turned off for that simulation time step, a warning is issued, and the simulation continues.
The inlet conditions or variables are divided by the reference conditions. This formulation allows the coefficients to fall into smaller range of values. Moreover, the value of the coefficient indirectly represents the sensitivity of the output to that particular inlet variable. The reference conditions used when generating the performance coefficients must be the same as the reference conditions used later in the model. The reference temperature \({T_{ref}}\) is fixed at 283K. Temperature unit of Kelvin is used instead of Celsius to keep the ratio of the water inlet temperature and reference temperature positive value should the water inlet temperature drop below the freezing point.
For cooling mode, the reference conditions; reference load side volumetric flow rate, \({\dot V_{L,ref}}\) , reference source side volumetric flow rate, \({\dot V_{S,ref}}\) , \(Powe{r_{c,ref}}\) and reference source side heat transfer rate, \({Q_{source,c,ref}}\) are the conditions when the heat pump is operating at the highest cooling capacity or reference cooling capacity, \({Q_{c,ref}}\) indicated in the manufacturer’s catalog. Note that the reference conditions for heating mode might differ from the reference conditions specified for the cooling mode.
Coefficient estimation procedure:[LINK]
The generalized least square method is used to generate the coefficients. This method utilizes an optimization method which calculates for the coefficients that will give the least amount of differences between the model outputs and the catalog data. A set of coefficients for the cooling mode is generated which includes A1-A5 for load side heat transfer. The same procedure is repeated for the heating mode to generate the coefficients B1-B5. An information flow chart showing the inputs, reference conditions, performance coefficients and outputs are shown in the figure below:
Parameter Estimation Water-To-Water Heat Pump Model[LINK]
A steady state simulation model for a water-to-water reciprocating vapor compression heat pump (Object names: HeatPump:WaterToWater:ParameterEstimation:Cooling & HeatPump:WaterToWater:ParameterEstimation:Heating) is described in this section. This documentation is derived from the Ph.D. dissertation of Hui Jin which is available on the Oklahoma State University web site http://www.hvac.okstate.edu/. The model incorporates a multivariable unconstrained optimization algorithm to estimate several unspecific parameters. The aim of the model is to describe the detailed physical geometry and operation of each component and replicate the performance of the actual unit in operation. Assuming the thermodynamic process in the expansion device and the pressure drop at the suction and discharge valves to be isenthalpic the heat balance equation is given by
\[{\dot Q_s} = \dot W + {\dot Q_{_L}}\]
Where:
\({\dot Q_s}\) = Source side heat transfer rate
\({\dot Q_L}\) = Load side heat transfer rate
\(\dot W\) = Compressor power input
The compressor model is based on an isentropic process shown in Figure 239 governed by
\(P{V^\gamma }\) = Constant
Where:
P = Pressure
v = Specific volume
Since the refrigerant vapor in the clearance volume as shown in the previous figure goes through a re-expansion procedure, the mass flow rate of the compressor refrigerant is a decreasing function of the pressure ratio.
\[\mathop m\limits^ \bullet = \frac{{PD}}{{\nu {}_{suc}}}(1 + C - C{(\frac{{P{}_{dis}}}{{P{}_{suc}}})^{\frac{1}{\gamma }}}\]
Where:
\(\mathop m\limits^ \bullet\) = refrigerant mass flow rate
PD = Piston displacement
C = Clearance factor
\(P{}_{dis}\) = discharge pressure
\(P{}_{suc}\) = Suction pressure
\(\gamma\) = Isentropic exponent
Parameter estimation procedure:[LINK]
A set of parameters for the cooling mode is defined on the basis of the equations used in the model. An information flowchart indicating the parameters, inputs to the model and the resulting outputs acquired are shown in Figure 240. The estimation of parameters is conducted using the catalog data.
The parameter definition include:
Where:
TWiL = Entering water Load side temperature
TWiS = Entering water Source side temperature
\(\mathop {\rm{m}}\limits^ \bullet {}_{{\rm{WiL}}}\) = Entering water Load side mass flow rate
\(\mathop {\rm{m}}\limits^ \bullet {}_{{\rm{WiS}}}\) = Entering water Source side mass flow rate
S = Thermostatic Signal
The parameter estimation procedure incorporates an objective function that computes the difference between the model outputs and the catalog outputs. The objective function is then minimized by using a multi variable unconstrained multi modal Nelder Mead optimization algorithm. As the objective function value lowers after each iteration, the model outputs approach the catalog outputs consequently leading to convergence and the correct parameters are estimated for the respective model. The inputs to the model include the entering water temperatures and mass flow rates on the load side and the source side. The calculation of the objective function is shown in the form of a formula flowchart in Figure 241. The square of the sum of the errors (SSQE) for a given set of parameter values that will be minimized is given by
\[SSQE = \sum\limits_{i = 1} {{{\left( {\frac{{\left( {\mathop {W{}_{cat}}\limits^{} } \right) - \left( {\mathop W\limits^{} } \right){}_i}}{{\left( {\mathop {W{}_{cat}}\limits^{} } \right)}}} \right)}^2}} + \left( {\frac{{\left( {\mathop {QL{}_{cat}}\limits^{} } \right) - \left( {\mathop {QL}\limits^{} } \right){}_i}}{{\left( {\mathop {QL{}_{cat}}\limits^{} } \right)}}} \right)\]
Where
\({\rm{W}}{}_{{\rm{cat}}}\) = Catalog power consumption
\({\rm{W}}{}_{}\) = Model power consumption
\({\rm{QL}}{}_{{\rm{cat}}}\) = Catalog load side heat transfer
\({\rm{QL}}{}_{}\) = Model load side heat transfer
Extrapolation beyond the catalog data grants the parameter estimation model an upper hand in comparison with the equation fit and deterministic models. However, the detailed model is computationally more intensive. Moreover, when the model is implemented within a transient system simulation program, it may come across figures that are random and unplanned by the manufacturer such as low water flow rates or extreme temperatures. This oddity may result in unrealistic set of results.
Control Strategy:[LINK]
Both water-to-water heat pump models; parameter estimation based model and curve-fit model use the “cycle time control logic” developed by Murugappan (2002).
This strategy keeps the heat pump from short-cycling whereby the heat pump will stay on or off for the specified cycle time after switching states. The control logic is identical to the operation of a physical heat pump whereby the heat pump does not switch between on and off instantly. Refer to Muraggapan (2002) for the further details on the control strategy.
References[LINK]
Jin, Hui. 2002. Parameter Estimation Based Models of Water Source Heat Pumps. Phd. Thesis, Department of Mechanical and Aerospace Engineering, Oklahoma State University. (downloadable from http://www.hvac.okstate.edu/)
Tang,C. C. 2005. Modeling Packaged Heat Pumps in Quasi-Steady State Energy Simulation Program. M.S. Thesis. Department of Mechanical and Aerospace Engineering, Oklahoma State University. (downloadable from http://www.hvac.okstate.edu/)
Murugappan, Arun. 2002. Implementing Ground Source Heat Pump and Ground Loop Heat Exchanger Models in the EnergyPlus Simulation Environment, M.S. Thesis, Department of Mechanical and Aerospace Engineering, Oklahoma State University (downloadable from http://www.hvac.okstate.edu/)
Documentation content copyright © 1996-2026 The Board of Trustees of the University of Illinois and the Regents of the University of California through the Ernest Orlando Lawrence Berkeley National Laboratory. All rights reserved. EnergyPlus is a trademark of the US Department of Energy.
This documentation is made available under the EnergyPlus Open Source License v1.0.