Absorption Chiller[LINK]
The input object Chiller:Absorption provides a model for absorption chillers that is an empirical model of a standard absorption refrigeration cycle. The condenser and evaporator are similar to that of a standard chiller, which are both watertowater heat exchangers. The assembly of a generator and absorber provides the compression operation. Lowpressure vapor from the evaporator is absorbed by the liquid solution in the absorber. A pump receives lowpressure liquid from the absorber, elevates the pressure of the liquid, and delivers the liquid to the generator. In the generator, heat from a high temperature source (hot water or steam) drives off the vapor that has been absorbed by the solution. The liquid solution returns to the absorber through a throttling valve whose purpose is to provide a pressure drop to maintain the pressure difference between the generator and absorber. The heat supplied to the absorber can be waste heat from a diesel jacket, or the exhaust heat from diesel, gas, and steam turbines. For more information on absorption chillers, see the Input/Output Reference Document (Object: Chiller:Absorption).
The partload ratio of the absoprtion chiller’s evaporator is simply the actual cooling effect produced by the chiller divided by the maximum cooling effect available.
PLR=˙Qevap˙Qevap,rated
where
PLR = partload ratio of chiller evaporator
˙Qevap = chiller evaporator load [W]
˙Qevap,rated = rated chiller evaporator capacity [W]
This absorption chiller model is based on a polynomial fit of absorber performance data. The Generator Heat Input Part Load Ratio Curve is a quadratic equation that determines the ratio of the generator heat input to the demand on the chiller’s evaporator (Q_{evap}).
GeneratorHeatInputRatio=C1PLR+C2+C3(PLR)
The Pump Electric Use Part Load Ratio Curve is a quadratic equation that determines the ratio of the actual absorber pumping power to the nominal pumping power.
ElectricInputRatio=C1+C2∗PLR+C3∗PLR2
Thus, the coefficient sets establish the ratio of heat power intocooling effect produced as a function of part load ratio. The ratio of heatpowerin to coolingeffectproduced is the inverse of the coefficient of performance.
If the operating partload ratio is greater than the minimum partload ratio, the chiller will run the entire time step and cycling will not occur (i.e. CyclingFrac = 1). If the operating partload ratio is less than the minimum partload ratio, the chiller will be on for a fraction of the time step equal to CyclingFrac. Steam (or hot water) and pump electrical energy use are also calculated using the chiller partload cycling fraction.
CyclingFrac=MIN(1,PLRPLRmin)
˙Qgenerator=GeneratorHeatInputRatio(˙Qevap)(CyclingFrac)
˙Qpump=ElectricInputRatio(Ppump)(CyclingFrac)
where
CyclingFrac = chiller partload cycling fraction
PLRmin = chiller minimum partload ratio
˙Qgenerator = generator input power [W]
˙Qpump = absorbtion chiller pumping power [W]
The evaporator water mass flow rate is calculated based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mevap=˙mevap,max
Variable Flow Chillers:
ΔTevap=Tevap,in−Tevap,SP
˙mevap=˙QevapCp,evap(ΔT)
where
˙mevap = chiller evaporator water mass flow rate (kg/s)
˙mevap,max = chiller design evaporator water mass flow rate (kg/s)
ΔTevap = chiller evaporator water temperature difference (ºC)
Tevap,in = chiller evaporator inlet water temperature (ºC)
Tevap,SP = chiller evaporator outlet water setpoint temperature (ºC)
Cp = specific heat of water entering evaporator (J/kg•ºC)
The evaporator outlet water temperature is then calculated based on the cooling effect produced and the evaporator entering water temperature.
Tevap,out=Tevap,in+˙QevapCp,evap(˙mevap)
where
Tevap,out = chiller evaporator outlet water temperature [ºC]
Tevap,in = chiller evaporator inlet water temperature [ºC]
Cp,evap = specific heat of chiller evaporator inlet water [J/kg/ºC]
˙mevap = chiller evaporator water mass flow rate [kg/s]
The condenser heat transfer and condenser leaving water temperature are also calculated.
˙Qcond=˙Qevap+˙Qgenerator+˙Qpump
Tcond,out=Tcond,in+˙QcondCp,cond(˙mcond)
where
˙Qcond = chiller condenser heat transfer rate [W]
Tcond,out = chiller condenser outlet water temperature [ºC]
Tcond,in = chiller condenser inlet water temperature [ºC]
Cp,cond = specific heat of chiller condenser inlet water [J/kg/ºC]
˙mcond = chiller condenser water mass flow rate [kg/s]
The absorption chiller can model the impact of steam or hot water entering the generator, although the connection of the steam (hot water) nodes to a plant is not actually required. The calculations specific to the generator depend on the type of fluid used and are described here in further detail.
Steam Loop Calculations[LINK]
When a steam loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a steam loop), the generator outlet node steam mass flow rate and temperature are calculated based on the generator input power, latent heat of steam, the specific heat of water, and the amount of subcooling in the steam generator. The model assumes dry saturated steam enters the absorption chiller’s generator and exits the generator as a subcooled liquid. The temperature leaving the generator is calculated based on the user entered amount of liquid subcooling in the generator. The effect of subcooling of the liquid (condensate) in the pipe returning to the boiler is not modeled.
˙msteam=˙Qgeneratorhfg+cp,water×ΔTsc
Tgenerator,out=Tgenerator,in−ΔTsc
where
˙msteam = chiller steam mass flow rate [kg/s]
hfg = latent heat of steam [J/kg]
cp,water = specific heat of saturated water in the generator [J/Kg ºK]
ΔTsc = amount of subcooling in steam generator [ºC]
Tgenerator,out = generator steam outlet node temperature [ºC]
Tgenerator,in = generator steam inlet node temperature [ºC]
Hot Water Loop Calculations[LINK]
When a hot water loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a hot water loop), the generator outlet node temperature is calculated based on the generator input power, mass flow rate of water, and the specific heat of water entering the hot water generator. The calculations are based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mgenerator=˙mgenerator,max
Variable Flow Chillers:
˙mgenerator=˙QgeneratorCp,water(ΔTgenerator)
Tgenerator,out=Tgenerator,in−˙Qgenerator˙mgenerator(Cp,water)
where
˙mgenerator = generator hot water mass flow rate [kg/s]
˙mgenerator,max = generator design hot water mass flow rate (kg/s)
ΔTgenerator = generator design hot water temperature difference (ºC)
Indirect Absorption Chiller[LINK]
The Chiller:Absorption:Indirect object is an enhanced version of the absorption chiller model found in the Building Loads and System Thermodynamics (BLAST) program. This enhanced model is nearly identical to the existing absorption chiller model (Ref. Chiller:Absorption) with the exceptions that: 1) the enhanced indirect absorption chiller model provides more flexible performance curves and 2) chiller performance now includes the impact of varying evaporator, condenser, and generator temperatures. Since these absorption chiller models are nearly identical (i.e., the performance curves of the enhanced model can be manipulated to produce similar results to the previous model), it is quite probable that the Chiller:Absorption model will be deprecated in a future release of EnergyPlus.
The indirect absorption chiller’s condenser and evaporator are similar to that of a standard chiller, which are both watertowater heat exchangers. The assembly of a generator and absorber provides the compression operation. A schematic of a singlestage absorption chiller is shown in the figure below. Lowpressure vapor from the evaporator is absorbed by the liquid solution in the absorber. A pump receives lowpressure liquid from the absorber, elevates the pressure of the liquid, and delivers the liquid to the generator. In the generator, heat from a high temperature source (hot water or steam) drives off the vapor that has been absorbed by the solution. The liquid solution returns to the absorber through a throttling valve whose purpose is to provide a pressure drop to maintain the pressure difference between the generator and absorber. The heat supplied to the generator can be either hot water or steam, however, connection to an actual plant loop is not required. For more information on indirect absorption chillers, see the Input/Output Reference Document (Object: Chiller:Absorption:Indirect).
The chiller cooling effect (capacity) will change with a change in condenser water temperature. Similarly, the chiller cooling effect will change as the temperature of the evaporator water changes. The chiller cooling effect will also change with a change in or generator inlet water temperature and only applies when Hot Water is used as the generator heat source. A quadratic or cubic equation is used to modify the rated chiller capacity as a function of both the condenser and generator inlet water temperatures and the evaporator outlet water temperature. If any or all of the capacity correction factor curves are not used, the correction factors are assumed to be 1.
CAPFTevaporator=a+b(Tevaporator)+c(Tevaporator)2+d(Tevaporator)3
CAPFTcondenser=e+f(Tcondenser)+g(Tcondenser)2+h(Tcondenser)3
CAPFTgenerator=i+j(Tgenerator)+k(Tgenerator)2+l(Tgenerator)3 (Hot Water only)
where
CAPFTevaporator = Capacity correction (function of evaporator temperature) factor
CAPFTcondenser= = Capacity correction (function of condenser temperature) factor
CAPFTgenerator = Capacity correction (function of generator temperature) factor
Tevaporator = evaporator outet water temperature [C]
Tcondenser = condenser inlet water temperature [C]
Tgenerator = generator inlet water temperature [C]
˙Qevap,max = maximum chiller capacity [W]
˙Qevap,rated = rated chiller capacity [W]
The partload ratio of the indirect absoprtion chiller’s evaporator is simply the actual cooling effect required (load) divided by the maximum cooling effect available.
PLR=˙Qevap˙Qevap,max
where
PLR = partload ratio of chiller evaporator
˙Qevap = chiller evaporator operating capacity [W]
The generator’s heat input is also a function of several parameters. The primary input for determining the heat input requirements is the Generator Heat Input function of PartLoad Ratio Curve. The curve is a quadratic or cubic equation that determines the ratio of the generator heat input to the chiller’s maximum capacity (Q~evap, max~) and is soley a function of partload ratio. Typical generator heat input ratios at full load (i.e., PLR=1) are between 1 and 2. Two additional curves are available to modifiy the heat input requirement based on the generator inlet water temperature and the evaporator outlet water temperature.
GeneratorHIR=a+b(PLR)+c(PLR)2+d(PLR)3
GenfCondT=e+f(Tgenerator)+g(Tgenerator)2+h(Tgenerator)3
GenfEvapT=i+j(Tevaporator)+k(Tevaporator)2+l(Tevaporator)3
where
GeneratorHIR = ratio of generator heat input to chiller operating capacity
GenfCondT = heat input modifier based on generator inlet water temperature
GenfEvapT = heat input modifier based on evaporator outlet water temperature
The Pump Electric Use function of PartLoad Ratio Curve is a quadratic or cubic equation that determines the ratio of the actual absorber pumping power to the nominal pumping power.
ElectricInputRatio=a+b(PLR)+c(PLR)2+d(PLR)3
If the chiller operating partload ratio is greater than the minimum partload ratio, the chiller will run the entire time step and cycling will not occur (i.e. CyclingFrac = 1). If the operating partload ratio is less than the minimum partload ratio, the chiller will be on for a fraction of the time step equal to CyclingFrac. Generator heat input and pump electrical energy use are also calculated using the chiller partload cycling fraction.
CyclingFrac=MIN(1.PLRPLRmin)
˙Qgenerator=GeneratorHIR(˙Qevap,max)(GenfCondT)(GenfEvapT)(CyclingFrac)
˙Qgenerator=ElectricInputRatio(Ppump)(CyclingFrac)
where
CyclingFrac = chiller partload cycling fraction
PLRmin = chiller minimum partload ratio
˙Qgenerator = generator heat input [W]
˙Qpump = chiller pumping power [W]
The evaporator water mass flow rate is calculated based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mevap=˙mevap,max
Variable Flow Chillers:
ΔTevap=Tevap,in−Tevap,SP
˙mevap=˙QevapCp,evap(ΔTevap)
where
˙mevap = chiller evaporator water mass flow rate (kg/s)
˙mevap,max = chiller design evaporator water mass flow rate (kg/s)
ΔTevap = chiller evaporator water temperature difference (ºC)
Tevap,in = chiller evaporator inlet water temperature (ºC)
Tevap,SP = chiller evaporator outlet water setpoint temperature (ºC)
Cp,evap = specific heat of water entering evaporator (J/kg ºC)
The evaporator outlet water temperature is then calculated based on the cooling effect produced and the evaporator entering water temperature.
Tevap,out=Tevap,in+˙QevapCp,evap(˙mevap)
where
Tevap,out = chiller evaporator outlet water temperature [ºC]
Tevap,in = chiller evaporator inlet water temperature [ºC]
Cp,evap = specific heat of chiller evaporator inlet water [J/kg/ºC]
˙mevap = chiller evaporator water mass flow rate [kg/s]
The condenser heat transfer and condenser leaving water temperature are also calculated.
˙Qcond=˙Qevap+˙Qgenerator+˙Qpump
Tcond,out=Tcond,in+˙QcondCp,cond(˙mcond)
where
˙Qcond = chiller condenser heat transfer rate [W]
Tcond,out = chiller condenser outlet water temperature [ºC]
Tcond,in = chiller condenser inlet water temperature [ºC]
Cp,cond = specific heat of chiller condenser inlet water [J/kg/ºC]
˙mcond = chiller condenser water mass flow rate [kg/s]
The absorption chiller can model the impact of steam or hot water entering the generator, although the connection of the steam (hot water) nodes to a plant is not actually required. The calculations specific to the generator depend on the type of fluid used and are described here in further detail.
Steam Loop Calculations[LINK]
When a steam loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a steam loop), the generator outlet node steam mass flow rate and temperature are calculated based on the generator heat input, latent heat of steam, the specific heat of water, and the amount of subcooling in the steam generator. The model assumes dry saturated steam enters the generator and exits the generator as a subcooled liquid. The temperature leaving the generator is calculated based on the user entered amount of liquid subcooling in the generator. The effect of subcooling of the liquid (condensate) in the pipe returning to the boiler is also modeled using the user entered abount of steam condensate loop subcooling.
˙msteam=˙Qgeneratorhfg+cp,water×ΔTsc
Tgenerator,out=Tgenerator,in−ΔTsc
Tloop,out=Tgenerator,out−ΔTsc,loop
where
˙msteam = chiller steam mass flow rate [kg/s]
hfg = latent heat of steam [J/kg]
cp,water = specific heat of water [J/Kg ºC]
ΔTsc = amount of subcooling in steam generator [ºC]
ΔTsc,loop = amount of condensate subcooling in steam loop [ºC]
Tgenerator,out = generator steam outlet node temperature [ºC]
Tgenerator,in = generator steam inlet node temperature [ºC]
Hot Water Loop Calculations[LINK]
When a hot water loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a hot water loop), the generator outlet node temperature is calculated based on the generator heat input, mass flow rate of water, and the specific heat of water entering the hot water generator. The calculations are based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mgenerator=˙mgenerator,max
Variable Flow Chillers:
˙mgenerator=˙QgeneratorCp,water(ΔTgenerator)
Tgenerator,out=Tgenerator,in−˙Qgenerator˙mgenerator(Cp,water)
where
˙mgenerator = generator hot water mass flow rate [kg/s]
˙mgenerator,max = generator design hot water mass flow rate (kg/s)
ΔTgenerator = generator design hot water temperature difference (ºC)
Combustion Turbine Chiller[LINK]
The input object Chiller:CombustionTurbine provides a chiller model that is the empirical model from the Building Loads and System Thermodynamics (BLAST) program. Fitting catalog data to a third order polynomial equations generates the chiller performance curves. Three sets of coefficients are required to model the open centrifugal chiller as discussed in the section, titled, ‘Electric Chiller Based on BLAST Centrifugal Chiller Model’.
The gas turbinedriven chiller is an open centrifugal chiller driven directly by a gas turbine. The BLAST model of an open centrifugal chiller is modeled as standard vapor compression refrigeration cycle with a centrifugal compressor driven by a shaft power from an engine. The centrifugal compressor has the incoming fluid entering at the eye of a spinning impeller that throws the fluid by centrifugal force to the periphery of the impeller. After leaving the compressor, the refrigerant is condensed to liquid in a refrigerant to water condenser. The heat from the condenser is rejected to a cooling tower, evaporative condenser, or well water condenser depending on which one is selected by the user based on the physical parameters of the plant. The refrigerant pressure is then dropped through a throttling valve so that fluid can evaporate at a low pressure that provides cooling to the evaporator. The evaporator can chill water that is pumped to chilled water coils in the building. For more information, see the Input/Output Reference Document.
This chiller is modeled like the electric chiller with the same numerical curve fits and then some additional curve fits to model the turbine drive. Shown below are the definitions of the curves that describe this model.
The chiller’s temperature rise coefficient which is defined as the ratio of the required change in condenser water temperature to a given change in chilled water temperature, which maintains the capacity at the nominal value. This is calculated as the following ratio:
TCEntrequired−TCEntratedTELvrequired−TELvrated
Where:
TCEnt_{required} = Required entering condenser air or water temperature to maintain rated capacity.
TCEnt_{rated} = Rated entering condenser air or water temperature at rated capacity.
TELv_{required} = Required leaving evaporator water outlet temperature to maintain rated capacity.
TELv_{rated} = Rated leaving evaporator water outlet temperature at rated capacity.
The Capacity Ratio Curve is a quadratic equation that determines the Ratio of Available Capacity to Nominal Capacity. The defining equation is:
AvailToNominalCapacityRatio=C1+C2Δtemp+C3Δ2temp
Where the Delta Temperature is defined as:
ΔTemp=TempCondIn−TempCondInDesignTempRiseCoefficient−(TempEvapOut−TempEvapOutDesign)
TempCondIn = Temperature entering the condenser (water or air temperature depending on condenser type).
TempCondInDesign = Temp Design Condenser Inlet from User input above.
TempEvapOut = Temperature leaving the evaporator.
TempEvapOutDesign = Temp Design Evaporator Outlet from User input above.
TempRiseCoefficient = User Input from above.
The following three fields contain the coefficients for the quadratic equation.
The Power Ratio Curve is a quadratic equation that determines the Ratio of Full Load to Power. The defining equation is:
FullLoadtoPowerRatio=C1+C2AvailToNominalCapRatio+C3AvailToNominalCapRatio2
The Full Load Ratio Curve is a quadratic equation that determines the fraction of full load power. The defining equation is:
FracFullLoadPower=C1+C2PartLoadRatio+C3PartLoadRatio2
The Fuel Input Curve is a polynomial equation that determines the Ratio of Fuel Input to Energy Output. The equation combines both the Fuel Input Curve Coefficients and the Temperature Based Fuel Input Curve Coefficients. The defining equation is:
FuelEnergyInput=PLoad∗(FIC1+FIC2RLoad+FIC3RLoad2)∗(TBFIC1+TBFIC2ATair+TBFIC3AT2air)
Where FIC represents the Fuel Input Curve Coefficients, TBFIC represents the Temperature Based Fuel Input Curve Coefficients, Rload is the Ratio of Load to Combustion Turbine Engine Capacity, and AT_{air}is the difference between the current ambient and design ambient temperatures.
The Exhaust Flow Curve is a quadratic equation that determines the Ratio of Exhaust Gas Flow Rate to Engine Capacity. The defining equation is:

ExhaustFlowRate=GTCapacity∗(C1+C2ATair+C3AT2air) * **
Where GTCapacity is the Combustion Turbine Engine Capacity, and AT_{air} is the difference between the current ambient and design ambient temperatures.
The Exhaust Gas Temperature Curve is a polynomial equation that determines the Exhaust Gas Temperature. The equation combines both the Exhaust Gas Temperature Curve Coefficients (Based on the Part Load Ratio) and the (Ambient) Temperature Based Exhaust Gas Temperature Curve Coefficients. The defining equation is:
ExhaustTemperature=(C1+C2RLoad+C3RLoad2)∗(TBC1+TBC2ATair+TBC3AT2air)−273.15
Where C represents the Exhaust Gas Temperature Curve Coefficients, TBC are the Temperature Based Exhaust Gas Temperature Curve Coefficients, RLoad is the Ratio of Load to Combustion Turbine Engine Capacity, and AT_{air} is the difference between the actual ambient and design ambient temperatures.
The Recovery Lubricant Heat Curve is a quadratic equation that determines the recovery lube energy. The defining equation is:
RecoveryLubeEnergy=PLoad∗(C1+C2RL+C3RL2)
Where Pload is the engine load and RL is the Ratio of Load to Combustion Turbine Engine Capacity
The UA is an equation that determines the overall heat transfer coefficient for the exhaust gasses with the stack. The heat transfer coefficient ultimately helps determine the exhaust stack temperature. The defining equation is:
UAToCapacityRatio=C1GasTurbineEngineCapacityC2
Chiller Basin Heater[LINK]
This chiller’s basin heater (for evaporativelycooled condenser type) operates in the same manner as the Engine driven chiller’s basin heater. The calculations for the chiller basin heater are described in detail at the end of the engine driven chiller description (Ref. Engine Driven Chiller).
ChillerHeater:Absorption:DirectFired[LINK]
This model (object name ChillerHeater:Absorption:DirectFired) simulates the performance of a direct fired twostage absorption chiller with optional heating capability. The model is based on the direct fired absorption chiller model (ABSORGCHLR) in the DOE2.1 building energy simulation program. The EnergyPlus model contains all of the features of the DOE2.1 chiller model, plus some additional capabilities.
This model simulates the thermal performance of the chiller and the fuel consumption of the burner(s). This model does not simulate the thermal performance or the power consumption of associated pumps or cooling towers. This auxiliary equipment must be modeled using other EnergyPlus models (e.g. Cooling Tower:Single Speed).
Model Description[LINK]
The chiller model uses usersupplied performance information at design conditions along with five performance curves (curve objects) for cooling capacity and efficiency to determine chiller operation at offdesign conditions. Two additional performance curves for heating capacity and efficiency are used when the chiller is operating in a heating only mode or simultaneous cooling and heating mode.
The following nomenclature is used in the cooling equations:
AvailCoolCap=available fullload cooling capacity at current conditions [W]
CEIR=user input “Electric Input to Cooling Output Ratio”
CEIRfPLR=electric input to cooling output factor, equal to 1 at full load, user input “Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CEIRfT=electric input to cooling output factor, equal to 1 at design conditions, user input “Electric Input to Cooling Output Ratio Function of Temperature Curve Name”
CFIR=user input “Fuel Input to Cooling Output Ratio”
CFIRfPLR=fuel input to cooling output factor, equal to 1 at full load, user input “Fuel Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CFIRfT=fuel input to cooling output factor, equal to 1 at design conditions, user input “Fuel Input to Cooling Output Ratio Function of Temperature Curve Name”
CondenserLoad=condenser heat rejection load [W]
CoolCapfT=cooling capacity factor, equal to 1 at design conditions, user input “Cooling Capacity Function of Temperature Curve Name”
CoolElectricPower=cooling electricity input [W]
CoolFuelInput=cooling fuel input [W]
CoolingLoad=current cooling load on the chiller [W]
CPLR=cooling partload ratio = CoolingLoad / AvailCoolCap
HeatingLoad=current heating load on the chiller heater [W]
HFIR=user input “Fuel Input to Heating Output Ratio”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
T_{cond}=entering or leaving condenser fluid temperature [C]. For a watercooled condenser this will be the water temperature returning from the condenser loop (e.g., leaving the cooling tower) if the entering condenser fluid temperature option is used. For air or evapcooled condensers this will be the entering outdoor air drybulb or wetbulb temperature, respectively, if the entering condenser fluid temperature option is used.
T_{cw,l}=leaving chilled water temperature [C]
Five performance curves are used in the calculation of cooling capacity and efficiency:
Cooling Capacity Function of Temperature Curve
Fuel Input to Cooling Output Ratio Function of Temperature Curve
Fuel Input to Cooling Output Ratio Function of Part Load Ratio Curve
Electric Input to Cooling Output Ratio Function of Temperature Curve
Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve
The cooling capacity function of temperature (CoolCapfT) curve represents the fraction of the cooling capacity of the chiller as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature. The output of this curve is multiplied by the nominal cooling capacity to give the fullload cooling capacity at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CoolCapfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The available cooling capacity of the chiller is then computed as follows:
AvailCoolCap=NomCoolCap⋅CoolCapfT(Tcw,l,Tcond)
The fuel input to cooling output ratio function of temperature (CFIRfT) curve represents the fraction of the fuel input to the chiller at full load as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature. The output of this curve is multiplied by the nominal fuel input to cooling output ratio (CFIR) to give the fullload fuel input to cooling capacity ratio at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CFIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The fuel input to cooling output ratio function of part load ratio (CFIRfPLR) curve represents the fraction of the fuel input to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CFIRfPLR=a+b⋅CPLR+c⋅CPLR2
The fraction of the time step during which the chiller heater is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLR)/MinPLR)
The cooling fuel input to the chiller is then computed as follows:
CoolFuelInput=AvailCoolCap⋅RunFrac⋅CFIR⋅CFIRfT(Tcw,l,Tcond)⋅CFIRfPLR(CPLR)
The electric input to cooling output ratio as function of temperature (CEIRfT) curve represents the fraction of electricity to the chiller at full load as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature.
CEIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The electric input to cooling output ratio function of part load ratio (CEIRfPLR) curve represents the fraction of electricity to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CEIRfPLR=a+b⋅CPLR+c⋅CPLR2
The cooling electric input to the chiller is computed as follows:
CoolElectricPower=NomCoolCap⋅RunFrac⋅CEIR⋅CEIRfT(Tcw,l,Tcond)⋅CEIRfPLR(CPLR)
All five of these cooling performance curves are accessed through EnergyPlus’ builtin performance curve equation manager (objects Curve:Linear, Curve:Quadratic and Curve:Biquadratic). It is not imperative that the user utilize all coefficients in the performance curve equations if their performance equation has fewer terms (e.g., if the user’s CFIRfPLR performance curve is linear instead of quadratic, simply enter the values for a and b, and set coefficient c equal to zero).
The condenser load is computed as follows:
CondenserLoad=CoolingLoad+CoolFuelInputHFIR+CoolElectricPower
The following nomenclature is used in the heating equations:
AvailHeatCap=available fullload heating capacity at current conditions [W]
CPLRh=cooling partload ratio for heating curve = CoolingLoad / NomCoolCap
HeatCapfCPLR=heating capacity factor as a function of cooling part load ratio, equal to 1 at zero cooling load, user input “Heating Capacity Function of Cooling Capacity Curve Name”
HeatCoolCapRatio=user input “Heating to Cooling Capacity Ratio”
HeatElectricPower=heating electricity input [W]
HeatFuelInput=heating fuel input [W]
HeatingLoad=current heating load on the chiller [W]
HEIR=user input “Electric Input to Heating Output Ratio”
HFIR=user input “Fuel Input to Heating Output Ratio”
HFIRfHPLR=fuel input to heating output factor, equal to 1 at full load, user input “Fuel Input to Heat Output Ratio During Heating Only Operation Curve Name”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
TotalElectricPower=total electricity input [W]
TotalFuelInput=total fuel input [W]
Cooling is the primary purpose of the Direct Fired Absorption Chiller so that function is satisfied first and if energy is available for providing heating that is provided next.
The two performance curves for heating capacity and efficiency are:
Heating Capacity Function of Cooling Capacity Curve
FuelInputto Heat Output Ratio Function
The heating capacity function of cooling capacity curve (HeatCapfCool) determines how the heating capacity of the chiller varies with cooling capacity when the chiller is simultaneously heating and cooling. The curve is normalized so an input of 1.0 represents the nominal cooling capacity and an output of 1.0 represents the full heating capacity. An output of 1.0 should occur when the input is 0.0.
HeatCapfCPLR=a+b⋅CPLRh+c⋅CPLRh2
The available heating capacity is then computed as follows:
AvailHeatCap=NomCoolCap⋅HeatCoolCapRatio⋅HeatCapfCPLR(CPLRh)
The fuel input to heat output ratio curve (HFIRfHPLR) function is used to represent the fraction of fuel used as the heating load varies as a function of heating part load ratio. It is normalized so that a value of 1.0 is the full available heating capacity. The curve is usually linear or quadratic and will probably be similar to a boiler curve for most chillers.
HFIRfHPLR=a+b⋅HPLR+c⋅HPLR2
 The fuel use rate when heating is computed as follows:
HeatFuelInput=AvailHeatCap⋅HFIR⋅HFIRfHPLR(HPLR)
The fraction of the time step during which the chiller is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLRh)/MinPLR)
The heating electric input to the chiller is computed as follows:
HeatElectricPower=NomCoolCap⋅HeatCoolCapRatio⋅HEIR⋅RunFrac
If the chiller is delivering heating and cooling simultaneously, the parasitic electric load will be doublecounted, so the following logic is applied:
IF(HeatElectricPower≤CoolElectricPower)THENHeatElectricPower=0.0ELSEHeatElectricPower=HeatElectricPower−CoolElectricPowerENDIF
The total fuel and electric power input to the chiller is computed as shown below:
TotalElectricPower=HeatElectricPower+CoolElectricPowerTotalFuelInput=HeatFuelInput+CoolFuelInput
ChillerHeater:Absorption:DoubleEffect[LINK]
This model (object name ChillerHeater:Absorption:DoubleEffect) simulates the performance of an exhaust fired twostage (double effect) absorption chiller with optional heating capability. The model is based on the direct fired absorption chiller model (ABSORGCHLR) in the DOE2.1 building energy simulation program. The EnergyPlus model contains all of the features of the DOE2.1 chiller model, plus some additional capabilities. The model uses the exhaust gas output from Microturbine.
This model simulates the thermal performance of the chiller and the thermal energy input to the chiller. This model does not simulate the thermal performance or the power consumption of associated pumps or cooling towers. This auxiliary equipment must be modeled using other EnergyPlus models (e.g. Cooling Tower:Single Speed).
Model Description[LINK]
The chiller model uses usersupplied performance information at design conditions along with five performance curves (curve objects) for cooling capacity and efficiency to determine chiller operation at offdesign conditions. Two additional performance curves for heating capacity and efficiency are used when the chiller is operating in a heating only mode or simultaneous cooling and heating mode.
The following nomenclature is used in the cooling equations:
AvailCoolCap=available fullload cooling capacity at current conditions [W]
CEIR=user input “Electric Input to Cooling Output Ratio”
CEIRfPLR=electric input to cooling output factor, equal to 1 at full load, user input “Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CEIRfT=electric input to cooling output factor, equal to 1 at design conditions, user input “Electric Input to Cooling Output Ratio Function of Temperature Curve Name”
TeFIR=user input “Thermal Energy Input to Cooling Output Ratio”
TeFIRfPLR=thermal energy input to cooling output factor, equal to 1 at full load, user input “Thermal Energy Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
TeFIRfT=thermal energy input to cooling output factor, equal to 1 at design conditions, user input “Thermal Energy Input to Cooling Output Ratio Function of Temperature Curve Name”
CondenserLoad=condenser heat rejection load [W]
CoolCapfT=cooling capacity factor, equal to 1 at design conditions, user input “Cooling Capacity Function of Temperature Curve Name”
CoolElectricPower=cooling electricity input [W]
CoolThermalEnergyInput=cooling thermal energy input [W]
CoolingLoad=current cooling load on the chiller [W]
CPLR=cooling partload ratio = CoolingLoad / AvailCoolCap
HeatingLoad=current heating load on the chiller heater [W]
HFIR=user input “Thermal Energy Input to Heating Output Ratio”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
˙mExhAir = exhaust air mass flow rate from microturbine (kg/s)
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
Ta,o = exhaust air outlet temperature from microturbine entering the chiller (^{o}C)
Tabs,gen,o = Temperature of exhaust leaving the chiller (the generator component of the absorption chiller)
T_{cond} = entering condenser fluid temperature [°C]. For a watercooled condenser this will be the water temperature returning from the condenser loop (e.g., leaving the cooling tower). For air or evapcooled condensers this will be the entering outdoor air drybulb or wetbulb temperature, respectively.
T_{cw,l} = leaving chilled water temperature [°C]
The selection of entering or leaving condense fluid temperature can be made through the optional fieldTemperature Curve Input Variable.
Five performance curves are used in the calculation of cooling capacity and efficiency:
Cooling Capacity Function of Temperature Curve
Thermal Energy Input to Cooling Output Ratio Function of Temperature Curve
Thermal Energy Input to Cooling Output Ratio Function of Part Load Ratio Curve
Electric Input to Cooling Output Ratio Function of Temperature Curve
Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve
The cooling capacity function of temperature (CoolCapfT) curve represents the fraction of the cooling capacity of the chiller as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and the entering condenser fluid temperature. The output of this curve is multiplied by the nominal cooling capacity to give the fullload cooling capacity at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CoolCapfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The available cooling capacity of the chiller is then computed as follows:
AvailCoolCap=NomCoolCap⋅CoolCapfT(Tcw,l−Tcond)
The thermal energy input to cooling output ratio function of temperature (TeFIRfT) curve represents the fraction of the thermal energy input to the chiller at full load as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and the entering condenser fluid temperature. The output of this curve is multiplied by the nominal thermal energy input to cooling output ratio (TeFIR) to give the fullload thermal energy input to cooling capacity ratio at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
TeFIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The thermal energy input to cooling output ratio function of part load ratio (TeFIRfPLR) curve represents the fraction of the thermal energy input to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
TeFIRfPLR=a+b⋅CPLR+c⋅CPLR2
The fraction of the time step during which the chiller heater is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLR)/MinPLR)
The cooling thermal energy input to the chiller is then computed as follows:
CoolThermalEnergyInput=AvailCoolCap⋅RunFrac⋅TeFIR⋅TeFIRfT(Tcw,l,Tcond)⋅TeFIRfPLR(CPLR)
To make sure that the exhaust mass flow rate and temperature from microturbine are sufficient to drive the chiller, the heat recovery potential is compared with the cooling thermal energy input to the chiller (CoolThermalEergyInput). The heat recovery potential should be greater than the CoolThermalEnergyInput. Heat recovery potential is calculated as:
QRecovery=˙mExhAir⋅CpAir⋅(Ta,o−TAbs,gen,o)
T_{abs,gen,o}is the minimum temperature required for the proper operation of the doubleeffect chiller. It will be defaulted to 176°C.
The electric input to cooling output ratio as function of temperature (CEIRfT) curve represents the fraction of electricity to the chiller at full load as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature.
CEIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The electric input to cooling output ratio function of part load ratio (CEIRfPLR) curve represents the fraction of electricity to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CEIRfPLR=a+b⋅CPLR+c⋅CPLR2
The cooling electric input to the chiller is computed as follows:
CoolElectricPower=NomCoolCap⋅RunFrac⋅CEIR⋅CEIRfT(Tcw,l,Tcond)⋅CEIRfPLR(CPLR)
All five of these cooling performance curves are accessed through EnergyPlus’ builtin performance curve equation manager (objects Curve:Linear, Curve:Quadratic and Curve:Biquadratic). It is not imperative that the user utilize all coefficients in the performance curve equations if their performance equation has fewer terms (e.g., if the user’s TeFIRfPLR performance curve is linear instead of quadratic, simply enter the values for a and b, and set coefficient c equal to zero). A set of curves derived from manufacturer’s data are also provided in the dataset (ExhaustFiredChiller.idf) is provided with E+ installation.
The condenser load is computed as follows:
CondenserLoad=CoolingLoad+CoolThermalEnergyInput/HFIR+CoolElectricPower
The following nomenclature is used in the heating equations:
AvailHeatCap=available fullload heating capacity at current conditions [W]
CPLRh=cooling partload ratio for heating curve = CoolingLoad / NomCoolCap
HeatCapfCPLR=heating capacity factor as a function of cooling part load ratio, equal to 1 at zero cooling load, user input “Heating Capacity Function of Cooling Capacity Curve Name”
HeatCoolCapRatio=user input “Heating to Cooling Capacity Ratio”
HeatElectricPower=heating electricity input [W]
HeatThermalEnergyInput= heating thermal energy input [W]
HeatingLoad=current heating load on the chiller [W]
HEIR=user input “Electric Input to Heating Output Ratio”
HFIR=user input “Thermal Energy Input to Heating Output Ratio”
HFIRfHPLR=thermal energy input to heating output factor, equal to 1 at full load, user input “Thermal Energy Input to Heat Output Ratio During Heating Only Operation Curve Name”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
TotalElectricPower=total electricity input [W]
TotalThermalEnergyInput=total thermal energy input [W]
Cooling is the primary purpose of the Exhaust Fired Absorption Chiller so that function is satisfied first and if energy is available for providing heating that is provided next.
The two performance curves for heating capacity and efficiency are:
Heating Capacity Function of Cooling Capacity Curve
ThermalEnergyInputto Heat Output Ratio Function
The heating capacity function of cooling capacity curve (HeatCapfCPLR) determines how the heating capacity of the chiller varies with cooling capacity when the chiller is simultaneously heating and cooling. The curve is normalized so an input of 1.0 represents the nominal cooling capacity and an output of 1.0 represents the full heating capacity. An output of 1.0 should occur when the input is 0.0.
HeatCapfCPLR=a+b⋅CPLRh+c⋅CPLRh2
The available heating capacity is then computed as follows:
AvailHeatCap=NomCoolCap⋅HeatCoolCapRatio⋅HeatCapfCPLR(CPLRh)
The thermal energy input to heat output ratio curve (HFIRfHPLR) function is used to represent the fraction of thermal energy used as the heating load varies as a function of heating part load ratio. It is normalized so that a value of 1.0 is the full available heating capacity. The curve is usually linear or quadratic and will probably be similar to a boiler curve for most chillers.
HFIRfHPLR=a+b⋅HPLR+c⋅HPLR2
 The thermal energy use rate when heating is computed as follows:
HeatThermalEnergyInput=AvailHeatCap.HFIR.HFIRfHPLR(HPLR)
The fraction of the time step during which the chiller is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLRh)/MinPLR)
The heating electric input to the chiller is computed as follows:
HeatElectricPower=NomCoolCap⋅HeatCoolCapRatio⋅HEIR.RunFrac
If the chiller is delivering heating and cooling simultaneously, the parasitic electric load would be doublecounted, so the following logic is applied:
IF(HeatElectricPower≤CoolElectricPower)THENHeatElectricPower=0.0ELSEHeatElectricPower=HeatElectricPower−CoolElectricPowerENDIF
The total thermal energy and electric power input to the chiller is computed as shown below:
TotalElectricPower=HeatElectricPower+CoolElectricPower
TotalThermalEnergyInput=HeatThermalEnergyInput+CoolThermalEnergyInput
Personal communications with various absorption chiller manufacturers, March 2011.
Absorption Chillers and Heat Pumps, Keith Herold, Reinhard Radermacher and Sanford A. Klein (Mar 18, 1996).
Absorption systems for combined heat and power: The problem of partload operation, ASHRAE Transactions, 2003, Vol 109, Part1.
Constant COP Chiller[LINK]
The input object Chiller:ConstantCOP provides a chiller model that is based on a simple, constant COP simulation of the chiller. In this case, performance does not vary with chilled water temperature or condenser conditions. The nominal capacity of the chiller and the COP are user specified along with the connections to the plant and condenser loop and mass flow rates. Such a model is useful when the user does not have access to detailed performance data.
The chiller power is calculated from the load divided by the COP. This chiller will meet the load as long as it does not exceed the nominal capacity specified by the user.
QEvaporator = Load
Power = Load / ConstCOPChiller(ChillNum)%COP
Then the evaporator temperatures are calculated from the load
EvapDeltaTemp = QEvaporator/EvapMassFlowRate/CPwater
EvapOutletTemp = Node(EvapInletNode)%Temp  EvapDeltaTemp
The condenser load and temperatures are calculated from the evaporator load and the power to the chiller.
QCondenser = Power + QEvaporator
IF (ConstCOPChiller(ChillNum)%CondenserType == WaterCooled) THEN
IF (CondMassFlowRate > WaterMassFlowTol) THEN
CondOutletTemp = QCondenser/CondMassFlowRate/CPCW(CondInletTemp) + CondInletTemp
ELSE
CALL ShowSevereError('CalcConstCOPChillerModel: Condenser flow = 0, for CONST COP Chiller='// &
TRIM(ConstCOPChiller(ChillNum)%Name))
CALL ShowContinueErrorTimeStamp(' ')
CALL ShowFatalError('Program Terminates due to previous error condition.')
END IF
ELSE ! Air Cooled or Evap Cooled
! Set condenser outlet temp to condenser inlet temp for Air Cooled or Evap Cooled
! since there is no CondMassFlowRate and would divide by zero
CondOutletTemp = CondInletTemp
END IF
See the InputOutput Reference for additional information.
Chiller Basin Heater[LINK]
This chiller’s basin heater (for evaporativelycooled condenser type) operates in the same manner as the Engine driven chiller’s basin heater. The calculations for the chiller basin heater are described in detail at the end of the engine driven chiller description (Ref. Engine Driven Chiller).
Hot Water Heat Recovery from Chillers[LINK]
The electric chillers (e.g., Chiller:Electric, Chiller:EngineDriven, Chiller:CombustionTurbine, Chiller:Electric:EIR, and Chiller:Electric:ReformulatedEIR) all have the option of connecting a third plant loop for heating hot water at the same time the chiller cools the chilled water. The engine and combustion turbine chillers models include curves for heat recovery from oil and or jacket coolers. The other three chillers can model heat recovery where part of its condenser section is connected to a heat recovery loop for what is commonly known as a double bundled chiller, or single condenser with split bundles. The heat recovery chiller is simulated as a standard vapor compression refrigeration cycle with a double bundled condenser. A double bundle condenser involves two separate flow paths through a split condenser. One of these paths is condenser water typically connected to a standard cooling tower; the other path is hot water connected to a heat recovery loop. After leaving the compressor, the refrigerant is condensed to liquid in a refrigerant to water condenser. In a split bundle, the chiller’s internal controls will direct a part of the refrigerant to heat recovery condenser bundle and/or to the tower water condenser bundle depending on the chilled water load, the condenser inlet temperatures and internal chiller controls (and possibly a leaving hot water temperature setpoint). The refrigerant pressure is then dropped through a throttling valve so that fluid can evaporate at a low pressure that provides cooling to the evaporator.
The algorithm for the heat recovery portion of the chiller needs to be determined from relatively simple inputs to estimate the amount of the heat that is recovered and then send the rest of the heat to the cooling tower. For the chiller models associated with the object Chiller:Electric, air or evaporativelycooled condensers are allowed to be used with heat recovery and, when used, the condenser specific heat, mass flow rate, and temperatures shown below refer to outdoor air. A condenser air volume flow rate must be specified when using heat recovery with air or evaporativelycooled chillers.
The basic energy balance for the condenser section of a heat recovery chiller is
˙Qtot=˙QEvap+˙QElec=˙QCond+˙QHR
In practice, if the entering temperature of the heat recovery hot fluid is too high, the chiller’s internal controls will redirect refrigerant away from the heat recovery bundle. A user input is available for declaring the inlet high temperature limit, and if it is exceeded, the chiller will shut down heat recovery and request no flow and will not reject any condenser heat to that fluid.
The heat recovery condenser bundle is often physically smaller than the tower water condenser bundle and therefore may have limited heat transfer capacity. User input for the relative capacity of the heat recovery bundle, FHR,Cap, is used to define a maximum rate of heat recovery heat transfer using
˙QHR,Max=FHR,Cap⎛⎝˙QEvap,Ref+˙QEvap,RefCOPRef⎞⎠
This capacity factor is also used to autosize the heat recovery design fluid flow rate when it is set to autosize. The design heat recover flow rate is calculated by multiplying FHR,Cap by the condenser tower water design flow rate. If no capacity factor is input, it is assumed to be 1.0.
A heat recovery chiller may control the temperature of heat recovery fluid leaving the device by modulating the flow of refrigerant to the heat recovery condenser bundle. There are two different algorithms used depending on if the input has declared a leaving setpoint node.
If no control setpoint node was named, then the model developed by Liesen and Chillar (2004) is used to approximate the relative distribution of refrigerant flow and condenser heat transfer between the bundles. This model approximates the heat transfer situation by using average temperatures in and out of the condenser section.
QTot=(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)∗(TAvgOut−TAvgIn)
Then the inlet temperature is flowweighted to determine lumped inlet and outlet conditions.
TAvgIn=(˙mHeatRec∗CpHeatRec∗THeatRecIn+˙mCond∗CpCond∗TCondIn)(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)
TAvgOut=QTot(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)+TAvgIn
The lumped outlet temperature is then used for an approximate method of determining the heat recovery rate
˙QHR=˙mHRcpHR(TAvg,out−THR,in)
This rate is then limited by the physical size of the heat recovery bundle.
˙QHR=Min(˙QHR,˙QHR,max)
If user input for the leaving temperature setpoint is available, then a second model is used to distribute refrigerant flow and condenser heat transfer between the bundles that attempts to meet the heat recovery load implied by the leaving setpoint. When setpoint control is used, the desired rate of heat recovery heat transfer is:
˙QHR,Setpoint=˙mHRcpHR(THR,set−THR,in)
˙QHR,Setpoint=Max(˙QHR,Setpoint,0.0)
Then the heat recovery rate is simply modeled as the lower of the three different heat flow rates: the desired capacity, the maximum capacity, and the current total heat rejection rate.
˙QHR=Min(˙QHR,Setpoint,˙QHR,max,˙QTot)
For both models, the condenser heat transfer rate is then
˙QCond=˙QTot−˙QHR
The outlet temperatures are then calculated using
THR,out=THR,in+˙QHR˙mHRcpHR
TCond,out=TCond,in+˙QCond˙mCondcpcond
A heat recovery chiller may need to work harder because the refrigeration system faces a higher lift owing to an elevated effective temperature for heat rejection. With heat recovery, the condenser temperature used with the chiller’s performance curves is determined using one of the following heatflowweighted methods. The first is used for the chiller model for the objects Chiller:Electric, and Chiller:Electric:EIR which use the condensing entering temperature for performance.
TCond,in,Avg=(˙QHRTHR,in+˙QCondTCond,in)(˙QHR+
Chillers[LINK]
Absorption Chiller[LINK]
The input object Chiller:Absorption provides a model for absorption chillers that is an empirical model of a standard absorption refrigeration cycle. The condenser and evaporator are similar to that of a standard chiller, which are both watertowater heat exchangers. The assembly of a generator and absorber provides the compression operation. Lowpressure vapor from the evaporator is absorbed by the liquid solution in the absorber. A pump receives lowpressure liquid from the absorber, elevates the pressure of the liquid, and delivers the liquid to the generator. In the generator, heat from a high temperature source (hot water or steam) drives off the vapor that has been absorbed by the solution. The liquid solution returns to the absorber through a throttling valve whose purpose is to provide a pressure drop to maintain the pressure difference between the generator and absorber. The heat supplied to the absorber can be waste heat from a diesel jacket, or the exhaust heat from diesel, gas, and steam turbines. For more information on absorption chillers, see the Input/Output Reference Document (Object: Chiller:Absorption).
The partload ratio of the absoprtion chiller’s evaporator is simply the actual cooling effect produced by the chiller divided by the maximum cooling effect available.
PLR=˙Qevap˙Qevap,rated
where
PLR = partload ratio of chiller evaporator
˙Qevap = chiller evaporator load [W]
˙Qevap,rated = rated chiller evaporator capacity [W]
This absorption chiller model is based on a polynomial fit of absorber performance data. The Generator Heat Input Part Load Ratio Curve is a quadratic equation that determines the ratio of the generator heat input to the demand on the chiller’s evaporator (Q_{evap}).
GeneratorHeatInputRatio=C1PLR+C2+C3(PLR)
The Pump Electric Use Part Load Ratio Curve is a quadratic equation that determines the ratio of the actual absorber pumping power to the nominal pumping power.
ElectricInputRatio=C1+C2∗PLR+C3∗PLR2
Thus, the coefficient sets establish the ratio of heat power intocooling effect produced as a function of part load ratio. The ratio of heatpowerin to coolingeffectproduced is the inverse of the coefficient of performance.
If the operating partload ratio is greater than the minimum partload ratio, the chiller will run the entire time step and cycling will not occur (i.e. CyclingFrac = 1). If the operating partload ratio is less than the minimum partload ratio, the chiller will be on for a fraction of the time step equal to CyclingFrac. Steam (or hot water) and pump electrical energy use are also calculated using the chiller partload cycling fraction.
CyclingFrac=MIN(1,PLRPLRmin)
˙Qgenerator=GeneratorHeatInputRatio(˙Qevap)(CyclingFrac)
˙Qpump=ElectricInputRatio(Ppump)(CyclingFrac)
where
CyclingFrac = chiller partload cycling fraction
PLRmin = chiller minimum partload ratio
˙Qgenerator = generator input power [W]
˙Qpump = absorbtion chiller pumping power [W]
The evaporator water mass flow rate is calculated based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mevap=˙mevap,max
Variable Flow Chillers:
ΔTevap=Tevap,in−Tevap,SP
˙mevap=˙QevapCp,evap(ΔT)
where
˙mevap = chiller evaporator water mass flow rate (kg/s)
˙mevap,max = chiller design evaporator water mass flow rate (kg/s)
ΔTevap = chiller evaporator water temperature difference (ºC)
Tevap,in = chiller evaporator inlet water temperature (ºC)
Tevap,SP = chiller evaporator outlet water setpoint temperature (ºC)
Cp = specific heat of water entering evaporator (J/kg•ºC)
The evaporator outlet water temperature is then calculated based on the cooling effect produced and the evaporator entering water temperature.
Tevap,out=Tevap,in+˙QevapCp,evap(˙mevap)
where
Tevap,out = chiller evaporator outlet water temperature [ºC]
Tevap,in = chiller evaporator inlet water temperature [ºC]
Cp,evap = specific heat of chiller evaporator inlet water [J/kg/ºC]
˙mevap = chiller evaporator water mass flow rate [kg/s]
The condenser heat transfer and condenser leaving water temperature are also calculated.
˙Qcond=˙Qevap+˙Qgenerator+˙Qpump
Tcond,out=Tcond,in+˙QcondCp,cond(˙mcond)
where
˙Qcond = chiller condenser heat transfer rate [W]
Tcond,out = chiller condenser outlet water temperature [ºC]
Tcond,in = chiller condenser inlet water temperature [ºC]
Cp,cond = specific heat of chiller condenser inlet water [J/kg/ºC]
˙mcond = chiller condenser water mass flow rate [kg/s]
The absorption chiller can model the impact of steam or hot water entering the generator, although the connection of the steam (hot water) nodes to a plant is not actually required. The calculations specific to the generator depend on the type of fluid used and are described here in further detail.
Steam Loop Calculations[LINK]
When a steam loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a steam loop), the generator outlet node steam mass flow rate and temperature are calculated based on the generator input power, latent heat of steam, the specific heat of water, and the amount of subcooling in the steam generator. The model assumes dry saturated steam enters the absorption chiller’s generator and exits the generator as a subcooled liquid. The temperature leaving the generator is calculated based on the user entered amount of liquid subcooling in the generator. The effect of subcooling of the liquid (condensate) in the pipe returning to the boiler is not modeled.
˙msteam=˙Qgeneratorhfg+cp,water×ΔTsc
Tgenerator,out=Tgenerator,in−ΔTsc
where
˙msteam = chiller steam mass flow rate [kg/s]
hfg = latent heat of steam [J/kg]
cp,water = specific heat of saturated water in the generator [J/Kg ºK]
ΔTsc = amount of subcooling in steam generator [ºC]
Tgenerator,out = generator steam outlet node temperature [ºC]
Tgenerator,in = generator steam inlet node temperature [ºC]
Hot Water Loop Calculations[LINK]
When a hot water loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a hot water loop), the generator outlet node temperature is calculated based on the generator input power, mass flow rate of water, and the specific heat of water entering the hot water generator. The calculations are based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mgenerator=˙mgenerator,max
Variable Flow Chillers:
˙mgenerator=˙QgeneratorCp,water(ΔTgenerator)
Tgenerator,out=Tgenerator,in−˙Qgenerator˙mgenerator(Cp,water)
where
˙mgenerator = generator hot water mass flow rate [kg/s]
˙mgenerator,max = generator design hot water mass flow rate (kg/s)
ΔTgenerator = generator design hot water temperature difference (ºC)
Indirect Absorption Chiller[LINK]
The Chiller:Absorption:Indirect object is an enhanced version of the absorption chiller model found in the Building Loads and System Thermodynamics (BLAST) program. This enhanced model is nearly identical to the existing absorption chiller model (Ref. Chiller:Absorption) with the exceptions that: 1) the enhanced indirect absorption chiller model provides more flexible performance curves and 2) chiller performance now includes the impact of varying evaporator, condenser, and generator temperatures. Since these absorption chiller models are nearly identical (i.e., the performance curves of the enhanced model can be manipulated to produce similar results to the previous model), it is quite probable that the Chiller:Absorption model will be deprecated in a future release of EnergyPlus.
The indirect absorption chiller’s condenser and evaporator are similar to that of a standard chiller, which are both watertowater heat exchangers. The assembly of a generator and absorber provides the compression operation. A schematic of a singlestage absorption chiller is shown in the figure below. Lowpressure vapor from the evaporator is absorbed by the liquid solution in the absorber. A pump receives lowpressure liquid from the absorber, elevates the pressure of the liquid, and delivers the liquid to the generator. In the generator, heat from a high temperature source (hot water or steam) drives off the vapor that has been absorbed by the solution. The liquid solution returns to the absorber through a throttling valve whose purpose is to provide a pressure drop to maintain the pressure difference between the generator and absorber. The heat supplied to the generator can be either hot water or steam, however, connection to an actual plant loop is not required. For more information on indirect absorption chillers, see the Input/Output Reference Document (Object: Chiller:Absorption:Indirect).
Schematic Diagram of a SingleStage Absorption Chiller
The chiller cooling effect (capacity) will change with a change in condenser water temperature. Similarly, the chiller cooling effect will change as the temperature of the evaporator water changes. The chiller cooling effect will also change with a change in or generator inlet water temperature and only applies when Hot Water is used as the generator heat source. A quadratic or cubic equation is used to modify the rated chiller capacity as a function of both the condenser and generator inlet water temperatures and the evaporator outlet water temperature. If any or all of the capacity correction factor curves are not used, the correction factors are assumed to be 1.
CAPFTevaporator=a+b(Tevaporator)+c(Tevaporator)2+d(Tevaporator)3
CAPFTcondenser=e+f(Tcondenser)+g(Tcondenser)2+h(Tcondenser)3
CAPFTgenerator=i+j(Tgenerator)+k(Tgenerator)2+l(Tgenerator)3 (Hot Water only)
where
CAPFTevaporator = Capacity correction (function of evaporator temperature) factor
CAPFTcondenser= = Capacity correction (function of condenser temperature) factor
CAPFTgenerator = Capacity correction (function of generator temperature) factor
Tevaporator = evaporator outet water temperature [C]
Tcondenser = condenser inlet water temperature [C]
Tgenerator = generator inlet water temperature [C]
˙Qevap,max = maximum chiller capacity [W]
˙Qevap,rated = rated chiller capacity [W]
The partload ratio of the indirect absoprtion chiller’s evaporator is simply the actual cooling effect required (load) divided by the maximum cooling effect available.
PLR=˙Qevap˙Qevap,max
where
PLR = partload ratio of chiller evaporator
˙Qevap = chiller evaporator operating capacity [W]
The generator’s heat input is also a function of several parameters. The primary input for determining the heat input requirements is the Generator Heat Input function of PartLoad Ratio Curve. The curve is a quadratic or cubic equation that determines the ratio of the generator heat input to the chiller’s maximum capacity (Q~evap, max~) and is soley a function of partload ratio. Typical generator heat input ratios at full load (i.e., PLR=1) are between 1 and 2. Two additional curves are available to modifiy the heat input requirement based on the generator inlet water temperature and the evaporator outlet water temperature.
GeneratorHIR=a+b(PLR)+c(PLR)2+d(PLR)3
GenfCondT=e+f(Tgenerator)+g(Tgenerator)2+h(Tgenerator)3
GenfEvapT=i+j(Tevaporator)+k(Tevaporator)2+l(Tevaporator)3
where
GeneratorHIR = ratio of generator heat input to chiller operating capacity
GenfCondT = heat input modifier based on generator inlet water temperature
GenfEvapT = heat input modifier based on evaporator outlet water temperature
The Pump Electric Use function of PartLoad Ratio Curve is a quadratic or cubic equation that determines the ratio of the actual absorber pumping power to the nominal pumping power.
ElectricInputRatio=a+b(PLR)+c(PLR)2+d(PLR)3
If the chiller operating partload ratio is greater than the minimum partload ratio, the chiller will run the entire time step and cycling will not occur (i.e. CyclingFrac = 1). If the operating partload ratio is less than the minimum partload ratio, the chiller will be on for a fraction of the time step equal to CyclingFrac. Generator heat input and pump electrical energy use are also calculated using the chiller partload cycling fraction.
CyclingFrac=MIN(1.PLRPLRmin)
˙Qgenerator=GeneratorHIR(˙Qevap,max)(GenfCondT)(GenfEvapT)(CyclingFrac)
˙Qgenerator=ElectricInputRatio(Ppump)(CyclingFrac)
where
CyclingFrac = chiller partload cycling fraction
PLRmin = chiller minimum partload ratio
˙Qgenerator = generator heat input [W]
˙Qpump = chiller pumping power [W]
The evaporator water mass flow rate is calculated based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mevap=˙mevap,max
Variable Flow Chillers:
ΔTevap=Tevap,in−Tevap,SP
˙mevap=˙QevapCp,evap(ΔTevap)
where
˙mevap = chiller evaporator water mass flow rate (kg/s)
˙mevap,max = chiller design evaporator water mass flow rate (kg/s)
ΔTevap = chiller evaporator water temperature difference (ºC)
Tevap,in = chiller evaporator inlet water temperature (ºC)
Tevap,SP = chiller evaporator outlet water setpoint temperature (ºC)
Cp,evap = specific heat of water entering evaporator (J/kg ºC)
The evaporator outlet water temperature is then calculated based on the cooling effect produced and the evaporator entering water temperature.
Tevap,out=Tevap,in+˙QevapCp,evap(˙mevap)
where
Tevap,out = chiller evaporator outlet water temperature [ºC]
Tevap,in = chiller evaporator inlet water temperature [ºC]
Cp,evap = specific heat of chiller evaporator inlet water [J/kg/ºC]
˙mevap = chiller evaporator water mass flow rate [kg/s]
The condenser heat transfer and condenser leaving water temperature are also calculated.
˙Qcond=˙Qevap+˙Qgenerator+˙Qpump
Tcond,out=Tcond,in+˙QcondCp,cond(˙mcond)
where
˙Qcond = chiller condenser heat transfer rate [W]
Tcond,out = chiller condenser outlet water temperature [ºC]
Tcond,in = chiller condenser inlet water temperature [ºC]
Cp,cond = specific heat of chiller condenser inlet water [J/kg/ºC]
˙mcond = chiller condenser water mass flow rate [kg/s]
The absorption chiller can model the impact of steam or hot water entering the generator, although the connection of the steam (hot water) nodes to a plant is not actually required. The calculations specific to the generator depend on the type of fluid used and are described here in further detail.
Steam Loop Calculations[LINK]
When a steam loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a steam loop), the generator outlet node steam mass flow rate and temperature are calculated based on the generator heat input, latent heat of steam, the specific heat of water, and the amount of subcooling in the steam generator. The model assumes dry saturated steam enters the generator and exits the generator as a subcooled liquid. The temperature leaving the generator is calculated based on the user entered amount of liquid subcooling in the generator. The effect of subcooling of the liquid (condensate) in the pipe returning to the boiler is also modeled using the user entered abount of steam condensate loop subcooling.
˙msteam=˙Qgeneratorhfg+cp,water×ΔTsc
Tgenerator,out=Tgenerator,in−ΔTsc
Tloop,out=Tgenerator,out−ΔTsc,loop
where
˙msteam = chiller steam mass flow rate [kg/s]
hfg = latent heat of steam [J/kg]
cp,water = specific heat of water [J/Kg ºC]
ΔTsc = amount of subcooling in steam generator [ºC]
ΔTsc,loop = amount of condensate subcooling in steam loop [ºC]
Tgenerator,out = generator steam outlet node temperature [ºC]
Tgenerator,in = generator steam inlet node temperature [ºC]
Hot Water Loop Calculations[LINK]
When a hot water loop is used and the inlet and outlet node names are specified (i.e. the nodes are connected to a hot water loop), the generator outlet node temperature is calculated based on the generator heat input, mass flow rate of water, and the specific heat of water entering the hot water generator. The calculations are based on the Chiller Flow Mode as follows.
Constant Flow Chillers:
˙mgenerator=˙mgenerator,max
Variable Flow Chillers:
˙mgenerator=˙QgeneratorCp,water(ΔTgenerator)
Tgenerator,out=Tgenerator,in−˙Qgenerator˙mgenerator(Cp,water)
where
˙mgenerator = generator hot water mass flow rate [kg/s]
˙mgenerator,max = generator design hot water mass flow rate (kg/s)
ΔTgenerator = generator design hot water temperature difference (ºC)
Combustion Turbine Chiller[LINK]
The input object Chiller:CombustionTurbine provides a chiller model that is the empirical model from the Building Loads and System Thermodynamics (BLAST) program. Fitting catalog data to a third order polynomial equations generates the chiller performance curves. Three sets of coefficients are required to model the open centrifugal chiller as discussed in the section, titled, ‘Electric Chiller Based on BLAST Centrifugal Chiller Model’.
The gas turbinedriven chiller is an open centrifugal chiller driven directly by a gas turbine. The BLAST model of an open centrifugal chiller is modeled as standard vapor compression refrigeration cycle with a centrifugal compressor driven by a shaft power from an engine. The centrifugal compressor has the incoming fluid entering at the eye of a spinning impeller that throws the fluid by centrifugal force to the periphery of the impeller. After leaving the compressor, the refrigerant is condensed to liquid in a refrigerant to water condenser. The heat from the condenser is rejected to a cooling tower, evaporative condenser, or well water condenser depending on which one is selected by the user based on the physical parameters of the plant. The refrigerant pressure is then dropped through a throttling valve so that fluid can evaporate at a low pressure that provides cooling to the evaporator. The evaporator can chill water that is pumped to chilled water coils in the building. For more information, see the Input/Output Reference Document.
This chiller is modeled like the electric chiller with the same numerical curve fits and then some additional curve fits to model the turbine drive. Shown below are the definitions of the curves that describe this model.
The chiller’s temperature rise coefficient which is defined as the ratio of the required change in condenser water temperature to a given change in chilled water temperature, which maintains the capacity at the nominal value. This is calculated as the following ratio:
TCEntrequired−TCEntratedTELvrequired−TELvrated
Where:
TCEnt_{required} = Required entering condenser air or water temperature to maintain rated capacity.
TCEnt_{rated} = Rated entering condenser air or water temperature at rated capacity.
TELv_{required} = Required leaving evaporator water outlet temperature to maintain rated capacity.
TELv_{rated} = Rated leaving evaporator water outlet temperature at rated capacity.
The Capacity Ratio Curve is a quadratic equation that determines the Ratio of Available Capacity to Nominal Capacity. The defining equation is:
AvailToNominalCapacityRatio=C1+C2Δtemp+C3Δ2temp
Where the Delta Temperature is defined as:
ΔTemp=TempCondIn−TempCondInDesignTempRiseCoefficient−(TempEvapOut−TempEvapOutDesign)
TempCondIn = Temperature entering the condenser (water or air temperature depending on condenser type).
TempCondInDesign = Temp Design Condenser Inlet from User input above.
TempEvapOut = Temperature leaving the evaporator.
TempEvapOutDesign = Temp Design Evaporator Outlet from User input above.
TempRiseCoefficient = User Input from above.
The following three fields contain the coefficients for the quadratic equation.
The Power Ratio Curve is a quadratic equation that determines the Ratio of Full Load to Power. The defining equation is:
FullLoadtoPowerRatio=C1+C2AvailToNominalCapRatio+C3AvailToNominalCapRatio2
The Full Load Ratio Curve is a quadratic equation that determines the fraction of full load power. The defining equation is:
FracFullLoadPower=C1+C2PartLoadRatio+C3PartLoadRatio2
The Fuel Input Curve is a polynomial equation that determines the Ratio of Fuel Input to Energy Output. The equation combines both the Fuel Input Curve Coefficients and the Temperature Based Fuel Input Curve Coefficients. The defining equation is:
FuelEnergyInput=PLoad∗(FIC1+FIC2RLoad+FIC3RLoad2)∗(TBFIC1+TBFIC2ATair+TBFIC3AT2air)
Where FIC represents the Fuel Input Curve Coefficients, TBFIC represents the Temperature Based Fuel Input Curve Coefficients, Rload is the Ratio of Load to Combustion Turbine Engine Capacity, and AT_{air}is the difference between the current ambient and design ambient temperatures.
The Exhaust Flow Curve is a quadratic equation that determines the Ratio of Exhaust Gas Flow Rate to Engine Capacity. The defining equation is:
Where GTCapacity is the Combustion Turbine Engine Capacity, and AT_{air} is the difference between the current ambient and design ambient temperatures.
The Exhaust Gas Temperature Curve is a polynomial equation that determines the Exhaust Gas Temperature. The equation combines both the Exhaust Gas Temperature Curve Coefficients (Based on the Part Load Ratio) and the (Ambient) Temperature Based Exhaust Gas Temperature Curve Coefficients. The defining equation is:
ExhaustTemperature=(C1+C2RLoad+C3RLoad2)∗(TBC1+TBC2ATair+TBC3AT2air)−273.15
Where C represents the Exhaust Gas Temperature Curve Coefficients, TBC are the Temperature Based Exhaust Gas Temperature Curve Coefficients, RLoad is the Ratio of Load to Combustion Turbine Engine Capacity, and AT_{air} is the difference between the actual ambient and design ambient temperatures.
The Recovery Lubricant Heat Curve is a quadratic equation that determines the recovery lube energy. The defining equation is:
RecoveryLubeEnergy=PLoad∗(C1+C2RL+C3RL2)
Where Pload is the engine load and RL is the Ratio of Load to Combustion Turbine Engine Capacity
The UA is an equation that determines the overall heat transfer coefficient for the exhaust gasses with the stack. The heat transfer coefficient ultimately helps determine the exhaust stack temperature. The defining equation is:
UAToCapacityRatio=C1GasTurbineEngineCapacityC2
Chiller Basin Heater[LINK]
This chiller’s basin heater (for evaporativelycooled condenser type) operates in the same manner as the Engine driven chiller’s basin heater. The calculations for the chiller basin heater are described in detail at the end of the engine driven chiller description (Ref. Engine Driven Chiller).
ChillerHeater:Absorption:DirectFired[LINK]
Overview[LINK]
This model (object name ChillerHeater:Absorption:DirectFired) simulates the performance of a direct fired twostage absorption chiller with optional heating capability. The model is based on the direct fired absorption chiller model (ABSORGCHLR) in the DOE2.1 building energy simulation program. The EnergyPlus model contains all of the features of the DOE2.1 chiller model, plus some additional capabilities.
This model simulates the thermal performance of the chiller and the fuel consumption of the burner(s). This model does not simulate the thermal performance or the power consumption of associated pumps or cooling towers. This auxiliary equipment must be modeled using other EnergyPlus models (e.g. Cooling Tower:Single Speed).
Model Description[LINK]
The chiller model uses usersupplied performance information at design conditions along with five performance curves (curve objects) for cooling capacity and efficiency to determine chiller operation at offdesign conditions. Two additional performance curves for heating capacity and efficiency are used when the chiller is operating in a heating only mode or simultaneous cooling and heating mode.
Cooling[LINK]
The following nomenclature is used in the cooling equations:
AvailCoolCap=available fullload cooling capacity at current conditions [W]
CEIR=user input “Electric Input to Cooling Output Ratio”
CEIRfPLR=electric input to cooling output factor, equal to 1 at full load, user input “Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CEIRfT=electric input to cooling output factor, equal to 1 at design conditions, user input “Electric Input to Cooling Output Ratio Function of Temperature Curve Name”
CFIR=user input “Fuel Input to Cooling Output Ratio”
CFIRfPLR=fuel input to cooling output factor, equal to 1 at full load, user input “Fuel Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CFIRfT=fuel input to cooling output factor, equal to 1 at design conditions, user input “Fuel Input to Cooling Output Ratio Function of Temperature Curve Name”
CondenserLoad=condenser heat rejection load [W]
CoolCapfT=cooling capacity factor, equal to 1 at design conditions, user input “Cooling Capacity Function of Temperature Curve Name”
CoolElectricPower=cooling electricity input [W]
CoolFuelInput=cooling fuel input [W]
CoolingLoad=current cooling load on the chiller [W]
CPLR=cooling partload ratio = CoolingLoad / AvailCoolCap
HeatingLoad=current heating load on the chiller heater [W]
HFIR=user input “Fuel Input to Heating Output Ratio”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
T_{cond}=entering or leaving condenser fluid temperature [C]. For a watercooled condenser this will be the water temperature returning from the condenser loop (e.g., leaving the cooling tower) if the entering condenser fluid temperature option is used. For air or evapcooled condensers this will be the entering outdoor air drybulb or wetbulb temperature, respectively, if the entering condenser fluid temperature option is used.
T_{cw,l}=leaving chilled water temperature [C]
Five performance curves are used in the calculation of cooling capacity and efficiency:
Cooling Capacity Function of Temperature Curve
Fuel Input to Cooling Output Ratio Function of Temperature Curve
Fuel Input to Cooling Output Ratio Function of Part Load Ratio Curve
Electric Input to Cooling Output Ratio Function of Temperature Curve
Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve
The cooling capacity function of temperature (CoolCapfT) curve represents the fraction of the cooling capacity of the chiller as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature. The output of this curve is multiplied by the nominal cooling capacity to give the fullload cooling capacity at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CoolCapfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The available cooling capacity of the chiller is then computed as follows:
AvailCoolCap=NomCoolCap⋅CoolCapfT(Tcw,l,Tcond)
The fuel input to cooling output ratio function of temperature (CFIRfT) curve represents the fraction of the fuel input to the chiller at full load as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature. The output of this curve is multiplied by the nominal fuel input to cooling output ratio (CFIR) to give the fullload fuel input to cooling capacity ratio at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CFIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The fuel input to cooling output ratio function of part load ratio (CFIRfPLR) curve represents the fraction of the fuel input to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CFIRfPLR=a+b⋅CPLR+c⋅CPLR2
The fraction of the time step during which the chiller heater is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLR)/MinPLR)
The cooling fuel input to the chiller is then computed as follows:
CoolFuelInput=AvailCoolCap⋅RunFrac⋅CFIR⋅CFIRfT(Tcw,l,Tcond)⋅CFIRfPLR(CPLR)
The electric input to cooling output ratio as function of temperature (CEIRfT) curve represents the fraction of electricity to the chiller at full load as it varies by temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature.
CEIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The electric input to cooling output ratio function of part load ratio (CEIRfPLR) curve represents the fraction of electricity to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CEIRfPLR=a+b⋅CPLR+c⋅CPLR2
The cooling electric input to the chiller is computed as follows:
CoolElectricPower=NomCoolCap⋅RunFrac⋅CEIR⋅CEIRfT(Tcw,l,Tcond)⋅CEIRfPLR(CPLR)
All five of these cooling performance curves are accessed through EnergyPlus’ builtin performance curve equation manager (objects Curve:Linear, Curve:Quadratic and Curve:Biquadratic). It is not imperative that the user utilize all coefficients in the performance curve equations if their performance equation has fewer terms (e.g., if the user’s CFIRfPLR performance curve is linear instead of quadratic, simply enter the values for a and b, and set coefficient c equal to zero).
The condenser load is computed as follows:
CondenserLoad=CoolingLoad+CoolFuelInputHFIR+CoolElectricPower
Heating[LINK]
The following nomenclature is used in the heating equations:
AvailHeatCap=available fullload heating capacity at current conditions [W]
CPLRh=cooling partload ratio for heating curve = CoolingLoad / NomCoolCap
HeatCapfCPLR=heating capacity factor as a function of cooling part load ratio, equal to 1 at zero cooling load, user input “Heating Capacity Function of Cooling Capacity Curve Name”
HeatCoolCapRatio=user input “Heating to Cooling Capacity Ratio”
HeatElectricPower=heating electricity input [W]
HeatFuelInput=heating fuel input [W]
HeatingLoad=current heating load on the chiller [W]
HEIR=user input “Electric Input to Heating Output Ratio”
HFIR=user input “Fuel Input to Heating Output Ratio”
HFIRfHPLR=fuel input to heating output factor, equal to 1 at full load, user input “Fuel Input to Heat Output Ratio During Heating Only Operation Curve Name”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
TotalElectricPower=total electricity input [W]
TotalFuelInput=total fuel input [W]
Cooling is the primary purpose of the Direct Fired Absorption Chiller so that function is satisfied first and if energy is available for providing heating that is provided next.
The two performance curves for heating capacity and efficiency are:
Heating Capacity Function of Cooling Capacity Curve
FuelInputto Heat Output Ratio Function
The heating capacity function of cooling capacity curve (HeatCapfCool) determines how the heating capacity of the chiller varies with cooling capacity when the chiller is simultaneously heating and cooling. The curve is normalized so an input of 1.0 represents the nominal cooling capacity and an output of 1.0 represents the full heating capacity. An output of 1.0 should occur when the input is 0.0.
HeatCapfCPLR=a+b⋅CPLRh+c⋅CPLRh2
The available heating capacity is then computed as follows:
AvailHeatCap=NomCoolCap⋅HeatCoolCapRatio⋅HeatCapfCPLR(CPLRh)
The fuel input to heat output ratio curve (HFIRfHPLR) function is used to represent the fraction of fuel used as the heating load varies as a function of heating part load ratio. It is normalized so that a value of 1.0 is the full available heating capacity. The curve is usually linear or quadratic and will probably be similar to a boiler curve for most chillers.
HFIRfHPLR=a+b⋅HPLR+c⋅HPLR2
HeatFuelInput=AvailHeatCap⋅HFIR⋅HFIRfHPLR(HPLR)
The fraction of the time step during which the chiller is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLRh)/MinPLR)
The heating electric input to the chiller is computed as follows:
HeatElectricPower=NomCoolCap⋅HeatCoolCapRatio⋅HEIR⋅RunFrac
If the chiller is delivering heating and cooling simultaneously, the parasitic electric load will be doublecounted, so the following logic is applied:
IF(HeatElectricPower≤CoolElectricPower)THENHeatElectricPower=0.0ELSEHeatElectricPower=HeatElectricPower−CoolElectricPowerENDIF
The total fuel and electric power input to the chiller is computed as shown below:
TotalElectricPower=HeatElectricPower+CoolElectricPowerTotalFuelInput=HeatFuelInput+CoolFuelInput
ChillerHeater:Absorption:DoubleEffect[LINK]
Overview[LINK]
This model (object name ChillerHeater:Absorption:DoubleEffect) simulates the performance of an exhaust fired twostage (double effect) absorption chiller with optional heating capability. The model is based on the direct fired absorption chiller model (ABSORGCHLR) in the DOE2.1 building energy simulation program. The EnergyPlus model contains all of the features of the DOE2.1 chiller model, plus some additional capabilities. The model uses the exhaust gas output from Microturbine.
This model simulates the thermal performance of the chiller and the thermal energy input to the chiller. This model does not simulate the thermal performance or the power consumption of associated pumps or cooling towers. This auxiliary equipment must be modeled using other EnergyPlus models (e.g. Cooling Tower:Single Speed).
Model Description[LINK]
The chiller model uses usersupplied performance information at design conditions along with five performance curves (curve objects) for cooling capacity and efficiency to determine chiller operation at offdesign conditions. Two additional performance curves for heating capacity and efficiency are used when the chiller is operating in a heating only mode or simultaneous cooling and heating mode.
Cooling[LINK]
The following nomenclature is used in the cooling equations:
AvailCoolCap=available fullload cooling capacity at current conditions [W]
CEIR=user input “Electric Input to Cooling Output Ratio”
CEIRfPLR=electric input to cooling output factor, equal to 1 at full load, user input “Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
CEIRfT=electric input to cooling output factor, equal to 1 at design conditions, user input “Electric Input to Cooling Output Ratio Function of Temperature Curve Name”
TeFIR=user input “Thermal Energy Input to Cooling Output Ratio”
TeFIRfPLR=thermal energy input to cooling output factor, equal to 1 at full load, user input “Thermal Energy Input to Cooling Output Ratio Function of Part Load Ratio Curve Name”
TeFIRfT=thermal energy input to cooling output factor, equal to 1 at design conditions, user input “Thermal Energy Input to Cooling Output Ratio Function of Temperature Curve Name”
CondenserLoad=condenser heat rejection load [W]
CoolCapfT=cooling capacity factor, equal to 1 at design conditions, user input “Cooling Capacity Function of Temperature Curve Name”
CoolElectricPower=cooling electricity input [W]
CoolThermalEnergyInput=cooling thermal energy input [W]
CoolingLoad=current cooling load on the chiller [W]
CPLR=cooling partload ratio = CoolingLoad / AvailCoolCap
HeatingLoad=current heating load on the chiller heater [W]
HFIR=user input “Thermal Energy Input to Heating Output Ratio”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
˙mExhAir = exhaust air mass flow rate from microturbine (kg/s)
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
Ta,o = exhaust air outlet temperature from microturbine entering the chiller (^{o}C)
Tabs,gen,o = Temperature of exhaust leaving the chiller (the generator component of the absorption chiller)
T_{cond} = entering condenser fluid temperature [°C]. For a watercooled condenser this will be the water temperature returning from the condenser loop (e.g., leaving the cooling tower). For air or evapcooled condensers this will be the entering outdoor air drybulb or wetbulb temperature, respectively.
T_{cw,l} = leaving chilled water temperature [°C]
The selection of entering or leaving condense fluid temperature can be made through the optional fieldTemperature Curve Input Variable.
Five performance curves are used in the calculation of cooling capacity and efficiency:
Cooling Capacity Function of Temperature Curve
Thermal Energy Input to Cooling Output Ratio Function of Temperature Curve
Thermal Energy Input to Cooling Output Ratio Function of Part Load Ratio Curve
Electric Input to Cooling Output Ratio Function of Temperature Curve
Electric Input to Cooling Output Ratio Function of Part Load Ratio Curve
The cooling capacity function of temperature (CoolCapfT) curve represents the fraction of the cooling capacity of the chiller as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and the entering condenser fluid temperature. The output of this curve is multiplied by the nominal cooling capacity to give the fullload cooling capacity at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
CoolCapfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The available cooling capacity of the chiller is then computed as follows:
AvailCoolCap=NomCoolCap⋅CoolCapfT(Tcw,l−Tcond)
The thermal energy input to cooling output ratio function of temperature (TeFIRfT) curve represents the fraction of the thermal energy input to the chiller at full load as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and the entering condenser fluid temperature. The output of this curve is multiplied by the nominal thermal energy input to cooling output ratio (TeFIR) to give the fullload thermal energy input to cooling capacity ratio at specific temperature operating conditions (i.e., at temperatures different from the design temperatures). The curve should have a value of 1.0 at the design temperatures and flow rates specified in the input data file by the user. The biquadratic curve should be valid for the range of water temperatures anticipated for the simulation.
TeFIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The thermal energy input to cooling output ratio function of part load ratio (TeFIRfPLR) curve represents the fraction of the thermal energy input to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
TeFIRfPLR=a+b⋅CPLR+c⋅CPLR2
The fraction of the time step during which the chiller heater is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLR)/MinPLR)
The cooling thermal energy input to the chiller is then computed as follows:
CoolThermalEnergyInput=AvailCoolCap⋅RunFrac⋅TeFIR⋅TeFIRfT(Tcw,l,Tcond)⋅TeFIRfPLR(CPLR)
To make sure that the exhaust mass flow rate and temperature from microturbine are sufficient to drive the chiller, the heat recovery potential is compared with the cooling thermal energy input to the chiller (CoolThermalEergyInput). The heat recovery potential should be greater than the CoolThermalEnergyInput. Heat recovery potential is calculated as:
QRecovery=˙mExhAir⋅CpAir⋅(Ta,o−TAbs,gen,o)
T_{abs,gen,o}is the minimum temperature required for the proper operation of the doubleeffect chiller. It will be defaulted to 176°C.
The electric input to cooling output ratio as function of temperature (CEIRfT) curve represents the fraction of electricity to the chiller at full load as it varies with temperature. This a biquadratic curve with the input variables being the leaving chilled water temperature and either the entering or leaving condenser fluid temperature.
CEIRfT=a+bTcw,l+cT2cw,l+dTcond+eT2cond+fTcw,lTcond
The electric input to cooling output ratio function of part load ratio (CEIRfPLR) curve represents the fraction of electricity to the chiller as the load on the chiller varies at a given set of operating temperatures. The curve is normalized so that at full load the value of the curve should be 1.0. The curve is usually linear or quadratic.
CEIRfPLR=a+b⋅CPLR+c⋅CPLR2
The cooling electric input to the chiller is computed as follows:
CoolElectricPower=NomCoolCap⋅RunFrac⋅CEIR⋅CEIRfT(Tcw,l,Tcond)⋅CEIRfPLR(CPLR)
All five of these cooling performance curves are accessed through EnergyPlus’ builtin performance curve equation manager (objects Curve:Linear, Curve:Quadratic and Curve:Biquadratic). It is not imperative that the user utilize all coefficients in the performance curve equations if their performance equation has fewer terms (e.g., if the user’s TeFIRfPLR performance curve is linear instead of quadratic, simply enter the values for a and b, and set coefficient c equal to zero). A set of curves derived from manufacturer’s data are also provided in the dataset (ExhaustFiredChiller.idf) is provided with E+ installation.
The condenser load is computed as follows:
CondenserLoad=CoolingLoad+CoolThermalEnergyInput/HFIR+CoolElectricPower
Heating[LINK]
The following nomenclature is used in the heating equations:
AvailHeatCap=available fullload heating capacity at current conditions [W]
CPLRh=cooling partload ratio for heating curve = CoolingLoad / NomCoolCap
HeatCapfCPLR=heating capacity factor as a function of cooling part load ratio, equal to 1 at zero cooling load, user input “Heating Capacity Function of Cooling Capacity Curve Name”
HeatCoolCapRatio=user input “Heating to Cooling Capacity Ratio”
HeatElectricPower=heating electricity input [W]
HeatThermalEnergyInput= heating thermal energy input [W]
HeatingLoad=current heating load on the chiller [W]
HEIR=user input “Electric Input to Heating Output Ratio”
HFIR=user input “Thermal Energy Input to Heating Output Ratio”
HFIRfHPLR=thermal energy input to heating output factor, equal to 1 at full load, user input “Thermal Energy Input to Heat Output Ratio During Heating Only Operation Curve Name”
HPLR=heating partload ratio = HeatingLoad / AvailHeatCap
MinPLR=user input “Minimum Part Load Ratio”
NomCoolCap=user input “Nominal Cooling Capacity” [W]
RunFrac=fraction of time step which the chiller is running
TotalElectricPower=total electricity input [W]
TotalThermalEnergyInput=total thermal energy input [W]
Cooling is the primary purpose of the Exhaust Fired Absorption Chiller so that function is satisfied first and if energy is available for providing heating that is provided next.
The two performance curves for heating capacity and efficiency are:
Heating Capacity Function of Cooling Capacity Curve
ThermalEnergyInputto Heat Output Ratio Function
The heating capacity function of cooling capacity curve (HeatCapfCPLR) determines how the heating capacity of the chiller varies with cooling capacity when the chiller is simultaneously heating and cooling. The curve is normalized so an input of 1.0 represents the nominal cooling capacity and an output of 1.0 represents the full heating capacity. An output of 1.0 should occur when the input is 0.0.
HeatCapfCPLR=a+b⋅CPLRh+c⋅CPLRh2
The available heating capacity is then computed as follows:
AvailHeatCap=NomCoolCap⋅HeatCoolCapRatio⋅HeatCapfCPLR(CPLRh)
The thermal energy input to heat output ratio curve (HFIRfHPLR) function is used to represent the fraction of thermal energy used as the heating load varies as a function of heating part load ratio. It is normalized so that a value of 1.0 is the full available heating capacity. The curve is usually linear or quadratic and will probably be similar to a boiler curve for most chillers.
HFIRfHPLR=a+b⋅HPLR+c⋅HPLR2
HeatThermalEnergyInput=AvailHeatCap.HFIR.HFIRfHPLR(HPLR)
The fraction of the time step during which the chiller is operating is computed as a function of the cooling and heating partload ratios and the userinput minimum partload ratio:
RunFrac=MIN(1.0,MAX(HPLR,CPLRh)/MinPLR)
The heating electric input to the chiller is computed as follows:
HeatElectricPower=NomCoolCap⋅HeatCoolCapRatio⋅HEIR.RunFrac
If the chiller is delivering heating and cooling simultaneously, the parasitic electric load would be doublecounted, so the following logic is applied:
IF(HeatElectricPower≤CoolElectricPower)THENHeatElectricPower=0.0ELSEHeatElectricPower=HeatElectricPower−CoolElectricPowerENDIF
The total thermal energy and electric power input to the chiller is computed as shown below:
TotalElectricPower=HeatElectricPower+CoolElectricPower
TotalThermalEnergyInput=HeatThermalEnergyInput+CoolThermalEnergyInput
References[LINK]
Personal communications with various absorption chiller manufacturers, March 2011.
Absorption Chillers and Heat Pumps, Keith Herold, Reinhard Radermacher and Sanford A. Klein (Mar 18, 1996).
Absorption systems for combined heat and power: The problem of partload operation, ASHRAE Transactions, 2003, Vol 109, Part1.
Constant COP Chiller[LINK]
The input object Chiller:ConstantCOP provides a chiller model that is based on a simple, constant COP simulation of the chiller. In this case, performance does not vary with chilled water temperature or condenser conditions. The nominal capacity of the chiller and the COP are user specified along with the connections to the plant and condenser loop and mass flow rates. Such a model is useful when the user does not have access to detailed performance data.
The chiller power is calculated from the load divided by the COP. This chiller will meet the load as long as it does not exceed the nominal capacity specified by the user.
Then the evaporator temperatures are calculated from the load
The condenser load and temperatures are calculated from the evaporator load and the power to the chiller.
See the InputOutput Reference for additional information.
Chiller Basin Heater[LINK]
This chiller’s basin heater (for evaporativelycooled condenser type) operates in the same manner as the Engine driven chiller’s basin heater. The calculations for the chiller basin heater are described in detail at the end of the engine driven chiller description (Ref. Engine Driven Chiller).
Hot Water Heat Recovery from Chillers[LINK]
The electric chillers (e.g., Chiller:Electric, Chiller:EngineDriven, Chiller:CombustionTurbine, Chiller:Electric:EIR, and Chiller:Electric:ReformulatedEIR) all have the option of connecting a third plant loop for heating hot water at the same time the chiller cools the chilled water. The engine and combustion turbine chillers models include curves for heat recovery from oil and or jacket coolers. The other three chillers can model heat recovery where part of its condenser section is connected to a heat recovery loop for what is commonly known as a double bundled chiller, or single condenser with split bundles. The heat recovery chiller is simulated as a standard vapor compression refrigeration cycle with a double bundled condenser. A double bundle condenser involves two separate flow paths through a split condenser. One of these paths is condenser water typically connected to a standard cooling tower; the other path is hot water connected to a heat recovery loop. After leaving the compressor, the refrigerant is condensed to liquid in a refrigerant to water condenser. In a split bundle, the chiller’s internal controls will direct a part of the refrigerant to heat recovery condenser bundle and/or to the tower water condenser bundle depending on the chilled water load, the condenser inlet temperatures and internal chiller controls (and possibly a leaving hot water temperature setpoint). The refrigerant pressure is then dropped through a throttling valve so that fluid can evaporate at a low pressure that provides cooling to the evaporator.
Diagram of Chiller:Electric with Heat Recovery
The algorithm for the heat recovery portion of the chiller needs to be determined from relatively simple inputs to estimate the amount of the heat that is recovered and then send the rest of the heat to the cooling tower. For the chiller models associated with the object Chiller:Electric, air or evaporativelycooled condensers are allowed to be used with heat recovery and, when used, the condenser specific heat, mass flow rate, and temperatures shown below refer to outdoor air. A condenser air volume flow rate must be specified when using heat recovery with air or evaporativelycooled chillers.
The basic energy balance for the condenser section of a heat recovery chiller is
˙Qtot=˙QEvap+˙QElec=˙QCond+˙QHR
In practice, if the entering temperature of the heat recovery hot fluid is too high, the chiller’s internal controls will redirect refrigerant away from the heat recovery bundle. A user input is available for declaring the inlet high temperature limit, and if it is exceeded, the chiller will shut down heat recovery and request no flow and will not reject any condenser heat to that fluid.
The heat recovery condenser bundle is often physically smaller than the tower water condenser bundle and therefore may have limited heat transfer capacity. User input for the relative capacity of the heat recovery bundle, FHR,Cap, is used to define a maximum rate of heat recovery heat transfer using
˙QHR,Max=FHR,Cap⎛⎝˙QEvap,Ref+˙QEvap,RefCOPRef⎞⎠
This capacity factor is also used to autosize the heat recovery design fluid flow rate when it is set to autosize. The design heat recover flow rate is calculated by multiplying FHR,Cap by the condenser tower water design flow rate. If no capacity factor is input, it is assumed to be 1.0.
A heat recovery chiller may control the temperature of heat recovery fluid leaving the device by modulating the flow of refrigerant to the heat recovery condenser bundle. There are two different algorithms used depending on if the input has declared a leaving setpoint node.
If no control setpoint node was named, then the model developed by Liesen and Chillar (2004) is used to approximate the relative distribution of refrigerant flow and condenser heat transfer between the bundles. This model approximates the heat transfer situation by using average temperatures in and out of the condenser section.
QTot=(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)∗(TAvgOut−TAvgIn)
Then the inlet temperature is flowweighted to determine lumped inlet and outlet conditions.
TAvgIn=(˙mHeatRec∗CpHeatRec∗THeatRecIn+˙mCond∗CpCond∗TCondIn)(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)
TAvgOut=QTot(˙mHeatRec∗CpHeatRec+˙mCond∗CpCond)+TAvgIn
The lumped outlet temperature is then used for an approximate method of determining the heat recovery rate
˙QHR=˙mHRcpHR(TAvg,out−THR,in)
This rate is then limited by the physical size of the heat recovery bundle.
˙QHR=Min(˙QHR,˙QHR,max)
If user input for the leaving temperature setpoint is available, then a second model is used to distribute refrigerant flow and condenser heat transfer between the bundles that attempts to meet the heat recovery load implied by the leaving setpoint. When setpoint control is used, the desired rate of heat recovery heat transfer is:
˙QHR,Setpoint=˙mHRcpHR(THR,set−THR,in)
˙QHR,Setpoint=Max(˙QHR,Setpoint,0.0)
Then the heat recovery rate is simply modeled as the lower of the three different heat flow rates: the desired capacity, the maximum capacity, and the current total heat rejection rate.
˙QHR=Min(˙QHR,Setpoint,˙QHR,max,˙QTot)
For both models, the condenser heat transfer rate is then
˙QCond=˙QTot−˙QHR
The outlet temperatures are then calculated using
THR,out=THR,in+˙QHR˙mHRcpHR
TCond,out=TCond,in+˙QCond˙mCondcpcond
A heat recovery chiller may need to work harder because the refrigeration system faces a higher lift owing to an elevated effective temperature for heat rejection. With heat recovery, the condenser temperature used with the chiller’s performance curves is determined using one of the following heatflowweighted methods. The first is used for the chiller model for the objects Chiller:Electric, and Chiller:Electric:EIR which use the condensing entering temperature for performance.
TCond,in,Avg=(˙QHRTHR,in+˙QCondTCond,in)(˙QHR+