ChilledWaterBased Air Cooling Coil[LINK]
The input object Coil:Cooling:Water is simpler than the detailed geometry model. The simple model provides a good prediction of the air and water outlet conditions without requiring the detailed geometric input required for the detailed model. A greatly simplified schematic of enthalpy and temperature conditions in a counter flow cooling/dehumidifying coil is shown in the schematic Figure 1. The input required to model the coil includes only a set of thermodynamic design inputs, which require no specific manufacturer’s data. The coil simulation model is essentially a modification of one presented by Elmahdy and Mitalas (1977), TRNSYS, 1990 and Threlkeld, J.L. 1970. The model calculates the UA values required for a Dry, Wet and Part Wet & Part Dry Coil and iterates between the Dry and Wet Coil to output the fraction wet. There are two modes of flow operation for this model: CrossFlow or CounterFlow. The default mode is CounterFlow. In addition the coil has two modes of analysis: Simple Analysis and Detailed Analysis. The Simple analysis mode operates the coil as either wet or dry while the detailed mode simulates the coil as part wet partdry. While the detailed mode provides more accurate results, it is significantly slower than the simple model. The simple mode gives good results for an annual simulation but will not be adequate for a time step performance analysis.
Heat Transfer and Energy Balance[LINK]
The cooling coil may be completely dry, completely wet with condensation, or it may have wet and dry sections. The actual condition of the coil surface depends on the humidity and temperature of the air passing over the coil and the coil surface temperature. The partdry partwet case represents the most general scenario for the coil surface conditions. There are subroutines present in the model for both the dry and wet regions of the coil, and a subroutine that iterates between the dry and wet subroutines to calculate the fraction of the coil surface that is wet. For each region the heat transfer rate from air to water may be defined by the rate of enthalpy change in the air and in the water. The rates must balance between each medium for energy to be conserved.
Model Description[LINK]
The Model has two blocks: 1st = Design Block with the Design Inputs. This block calculates the Design UFactor Times Area Value (UA) values required by the model. Using these UA values the model simulates the operating conditions. The operating block is the one containing the operating conditions, the conditions at which the coil operates. Following is the list of Design and Operating inputs and subsequently the Design and Operating variables used in the model.
Operating Conditions (From Nodes – not user inputs)
InletWaterMassFlowRate 
Entering Water Mass Flow Rate at operating condition 
InletWaterTemp 
Inlet Water Temperature at operating condition 
InletAirMassFlowRate 
Entering Air Mass Flow Rate at operating condition 
InletAirTemp 
Inlet Air Temperature at operating condition 
InletAirHumRat 
Entering air humidity ratio at operating conditions 
The various UFactor Times Area values (UA) required by this model are calculated from the above inputs, which are explained later in the document. The various UA are:
UA Descriptions of Model
CoilUATotal 
Overall heat transfer coefficient (W/∘C) 
CoilUAInternal 
Overall internal UA (W/∘C) 
CoilUAExternal 
Overall external UA (W/∘C) 
CoilUInternal 
Internal overall heat transfer coefficient (W/m∘C) 
CoilUWetExternal 
Wet part external overall heat transfer coefficient (W/m∘C) 
CoilUDryExternal 
Dry part external overall heat transfer coefficient (W/m∘C) 
The UA values are calculated assuming a wet coil at the design conditions. Following are a few important calculations to understand the working of the model. The model is basically divided into two blocks: the Design Block and the Operating Block.
The Design Block is a one time calculation. The aim of the Design Block is to calculate the Coil UA for use in the operating Block.
Design Block Calculations[LINK]
The design block has the code for calculating the six Coil UA values required by the operating block. Reasonable assumptions have been made in the calculations to maintain the simplicity of the model.
Heat transfer in a wet coil model is based on enthalpy rather than temperature to take into account latent effects. While heat transfer rates are commonly expressed as the product of an overall heat transfer coefficient, UA, and a temperature difference, the use of enthalpybased heat transfer calculations requires an enthalpybased heat transfer coefficient which we denote as DesUACoilTotalEnth and hence the equation.
Q=DesUACoilTotalEnth∗(Hair,mean−Hwater,mean)
The value of Q is calculated using product of air mass flow rate and difference in inlet and outlet air enthalpies at design conditions.
The relation between the enthalpybased UA and the temperaturebased UA is:
DesUACoilTotalEnth=CoilUA/Cp
where CoilUA is the conventional heat transfer coefficient and Cp is the specific heat of the air.
We need the following quantities for our design calculations. The Psy functions are the EnergyPlus builtin psychrometric functions.
˙mair=ρair˙Vair
hair,in=PsyHFnTdbW(Tair,in,wair,in)
hair,out=PsyHFnTdbW(Tair,out,wair,out)
hw,sat,in=PsyHFnTdbW(Tw,in,PsyWFnTdpPb(Tw,in,Patm))
˙Qcoil=˙mair(hair,in−hair,out)
Tw,out=Tw,in+˙Qcoil/(˙mw,maxCp,w)
hw,sat,out=PsyHFnTdbW(Tw,out,PsyWFnTdpPb(Tw,out,Patm))
We now calculate the design coil bypass factor. The bypass factor is not used in subsequent calculations. It is calculated solely to use as check on the reasonableness of the userinput design inlet and outlet conditions. First we make an initial estimate of the apparatus dew point temperature:
Tair,dp,app=PsyTdpFnWPb(wair,out,Patm)
We also need the “slope” of temperature versus humidity ratio on the psych chart between the inlet and outlet air conditions:
ST,w=(Tair,in−Tair,out)/(wair,in−wair,out)
We now obtain the actual design apparatus dewpoint temperature by iterating over the following two equations:
wair,dp,app=PsyWFnTdpPb(Tair,dp,app,Patm)
Tair,dp,app=Tair,in−ST,w(wair,in−wair,dp,app)
The apparatus dewpoint enthalpy is then:
hair,dp,app=PsyHFnTdbW(Tair,dp,app,wair,dp,app)
and the coil bypass factor is:
Fcoilbypass=(hair,out−hair,dp,app)/(hair,in−hair,dp,app)
If the iterative procedure doesn’t converge, or the coil bypass factor is too large (greater than 0.5), or the apparatus dewpoint enthalpy is less than the saturated air enthalpy at the water inlet temperature, the design outlet air conditions are reset to 90% relative humidity at the same outlet enthalpy. The above design calculations are then repeated.
We are now ready to calculate the design coil UA. This will be accomplished by inverting the simple coil calculation routine CoolingCoil using the root solver method. First we make an initial estimate of the coil UA.
Δhlmd=(hair,in−hw,sat,out)−(hair,out−hw,sat,in)log(hair,in−hw,sat,outhair,out−hw,sat,in)
UAcoil,enthalpy−based=˙Qcoil/Δhlmd
UAcoil,ext=Cp,airUAcoil,enthalpy−based
We set the internal UA to 3.3 times the external UA (as a typical value for a coil). Then the total UA is:
UAcoil,tot=1(1/UAcoil,int+1/UAcoil,ext)
The next step is to estimate the coil external heat transfer surface area. This is done in the function EstimateHEXSurfaceArea:
Areacoil,ext=EstimateHEXSurfaceArea
using the following assumptions:
Tube inside diameter = 0.0122 (m)
Tube side water velocity = 2.0 (m/s)
Inside to outside coil surface area ratio (Ai/Ao) = 0.07 ()
Fins overall efficiency = 0.92 ()
Aluminum fins, 12 fins per inch with fins to total outside surface area ratio of 90%.
Airside combined heat and mass transfer coefficient = 140 (W/m2∘C)
Interior and exterior U values (really UA’s per unit exterior surface area) are calculated by dividing the above UA’s by the area. The resulting Ucoil,ext is assumed to be Ucoil,ext,wet; Ucoil,ext,dry is set equal to Ucoil,ext,wet. We now have all the starting values needed for inverting the simple coil model using the chosen root solver iterative method. Once the iteration is completed, we have coil UA’s and U’s that yield the design outlet air and water enthalpies given the inlet design conditions and flow rates. Note that the simple coil model can not exactly match the specified design outlet air temperature and humidity ratio. It can only match the design air outlet enthalpy. Generally the simple coil model will yield outlet conditions near the saturation curve if any dehumidification is occuring. Typical outlet relative humidities are around 95%.
The above calculations yield coil UA’s for the design inlet conditions and air and water flow rates. As the flow rates vary during the time step calculations, the UA’s need to be adjusted, since coil UA’s are a rather strong function of air and water side flow rates. Each time step the coil UA’s are modified using the same formulas as are used in the hot water coil model. Refer to that model for the flow dependences.
Operating Block Calculations:[LINK]
There are two modes of coil analysis in the operating block. They are the Simple analysis mode and the detailed analysis mode. The simple analysis mode assumes the coil to be either all wet or either all dry and execute the model , on the other hand the detailed mode checks for part wet part dry mode of operation and reports surface area wet fraction of coil, however the program execution time in detailed mode is noticeably higher.
The operating block for Detailed Mode Analysis of this coil model is divided into three modes of coil performance. The modes being:
Coil is completely dry: There is no moisture condensation on the coil surface and the coil is a dry coil. This is an extreme condition when the entering air has very low humidity ratio or is dry air.
Coil is completely wet: The entire coil is wet due to complete condensation on the surface of the coil.
Part Wet Part Dry Mode: This is the usual/frequent mode of operation of coil where part of the coil at entry of air is dry and as air cools condensation occurs and part of the coil becomes wet.
The Part Wet Part Dry Mode of operation is essentially a function the Coil Completely Dry and Coil Completely Wet mode. This subroutine iterates between the Dry Coil and the Wet Coil to give outputs, a detailed explanation is given later in the document. The operating block requires 5 inputs, which are mentioned earlier in the document. These inputs are automatically generated from the node connections in Energy Plus. The user does not have to input any information to run this coil model.
The option to identify which mode of operation the coil should perform ie, for a given set of inputs would the coil be Dry, Wet or Part Wet Part Dry, is decided by set of conditions described below.
IF (Temperature Dewpoint Air < Water Inlet Temperature) THEN the coil is Dry and we call the Subroutine Coil Completely Dry. In this case outlet temperature of air would be higher than the air dewpoint and hence there would be no condensation.
IF (Temperature Dewpoint Air > Water Inlet Temperature) THEN the coil is completely wet, call subroutine Coil Completely Wet, it is assumed that moisture condensation occurs over completely surface of the coil. However we go ahead and check for the coil being partially wet with the following condition.
IF (AirDewPointTemp < AirInletCoilSurfTemp) THEN the coil is Partially Wet because there is possibility that air temperature will go below its dewpoint and moisture will condense on latter part of the cooling coil.
The Operating Block for Simple Mode Analysis is divided into two modes of coil performance, the two modes being:
Coil is completely dry: There is no moisture condensation on the coil surface and the coil is a dry coil.
Coil is completely wet: The entire coil is wet due to complete condensation on the surface of the coil.
The option to identify which mode of operation the Simple mode analysis should perform ie, for a given set of inputs would the coil be Dry or Wet is decided by set of conditions described below.
IF (Temperature Dewpoint Air < Water Inlet Temperature) THEN the coil is Dry and we call the Subroutine Coil Completely Dry. In this case outlet temperature of air would be higher than the air dewpoint and hence there would be no condensation.
IF (Temperature Dewpoint Air > Water Inlet Temperature) THEN the coil is completely wet, call subroutine Coil Completely Wet, it is assumed that moisture condensation occurs over completely surface of the coil. However we go ahead and check for the coil being partially wet with the following condition.
The above is a simple mode of analysis and the results are very slightly different from the detailed mode of analysis. The algorithms used in Simple mode and the Detailed mode are identically similar. The surface area wet fraction in the coil is reported as 1.0 or 0.0 for wet or dry coil respectively. The program defaults to simple mode of analysis for enabling higher execution speed.
Effectiveness Equations[LINK]
There are two modes of flow for the coil, CounterFlow or CrossFlow. The default mode is CounterFlow. According to the mode of flow the following NTU  Effectiveness relationships are used to calculate coil effectiveness, which is used later by all the three modes (Dry, Wet, Part Wet) for calculating air outlet conditions and heat transfer.
Following are the relations used for calculating effectiveness equation for the heat exchangers.
Counter Flow Heat Exchanger Effectiveness Equation:
ηCounterFlow=(1−Exp(−NTU×(1−RatioStreamCapacity)))1−RatioStreamCapacity×Exp(−NTU×(1−RatioStreamCapacity))
In Equation [eq:CounterFlowHeatExchangerEffectiveness], the variable RatioStreamCapacity is defined as below:
RatioStreamCapacity=MinCapacityStreamMaxCapacityStream
In Equation [eq:RatioStreamCapacity], the capacities of stream are defined as below in Equation [eq:MinMaxCapacityStream]:
(Min,Max)CapacityStream=(MassFlowRate×Cp)air,water
NTU as shown in Equation [eq:CounterFlowHeatExchangerEffectiveness] is defined as the Number of Transfer Units and is a function of Coil UA and the Minimum Capacity of Stream. The Coil UA is a variable in this equation and depends on which mode of the coil operation (Dry, Wet, Part Wet) is calling upon Equation [eq:CounterFlowHeatExchangerEffectiveness], i.e., if it is Coil Completely Dry calling upon the effectiveness equation with the value of Dry UA total, which in our case is defined as CoilUA_total. Equation [eq:NTUCounterFlowHeatExchanger] gives definition for NTU.
NTU=CoilUAMinStreamCapacity
Cross Flow Heat Exchanger Effectiveness Equation:
ηCrossFlow=1−EXP{Exp(−NTU×RatioStreamCapacity×NTU−0.22)−1RatioStreamCapacity×NTU−0.22}
The variables in the above equation have already been defined earlier. Depending on the mode of operation of the coil model, the CrossFlow or CounterFlow equations are used to calculate the effectiveness.
Coil Outlet Conditions[LINK]
Calculating the Outlet Stream Conditions using the effectiveness value from Equation [eq:CounterFlowHeatExchangerEffectiveness] or [eq:EtaCrossFlow] depending on the mode of flow. The energy difference between the outlet and inlet stream conditions gives the amount of heat transfer that has actually take place. The temperature of air and water at the outlet of the coil are given by the following equations:
TempAirOut=TempAirinlet−ηcross,counter×MaxHeatTransferStreamCapacityAir
TempWaterOut=TempWaterInlet+ηCross,counter×MaxHeatTransferStreamCapacityWater
In Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp] above, the maximum heat transfer is calculated as shown in the following equation:
MaxHeatTransfer=MinStreamCapacity×(TempAirInlet−TempWaterInlet)
Coil Completely Dry Calculations (operating block)[LINK]
Since the coil is dry, the sensible load is equal to total load and the same with the humidity ratios at inlet and outlet, as in Equations [eq:HeatExchangerQSensibleDryCoil] and [eq:HeatExchangerHumRatioDryCoil].
QSensibleDryCoil=QTotalDryCoil
HumRatioInlet=HumRatioOutlet
Total Heat Transfer in dry coil is as follows:
QTotalDryCoil=CapacityAir×(AirTempIn−AirTempOutlet)
The variables in the above equation are calculated earlier in Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp] to give the total cooling load on the coil.
Coil Completely Wet Calculations (operating block)[LINK]
In wet coil we need to account for latent heat transfer, hence calculations are done using enthalpy of air and water instead of stream temperatures Hence we need to define coil UA for the wet coil based on enthalpy of the operating streams and not design streams.
Similar to Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp], we calculate the air outlet enthalpy and water outlet enthalpy, i.e. by replacing temperature with enthalpy for the respective streams. The input variable for Coil UA in Equation [eq:NTUCounterFlowHeatExchanger] for calculating NTU, in this case it would be enthalpy based and is given as shown in Equation [eq:CoilUAEnthalpyBased]:
CoilUAEnthalpyBased=1(CpSatIntermediateCoilUAInternal+CpAirCoilUAExternal)
Total Coil Load in the case of a Wet Coil is the product of mass flow rate of air and enthalpy difference between the inlet and outlet streams as given in the following equation:
QTotal=˙mair×(EnthAirInlet−EnthAirOutlet)
Once the enthalpy is known the outlet temperatures and outlet humidity ratios of the wet coil are calculated as in equations below.
IF (TempCondensation < PsyTdpFnWPb(InletAirHumRat ,Patm)) THEN
AirTempOut=AirTempinlet−(AirTempinlet−CondensationTemp)×η
and
OutletAirHumdityRatio=PsyWFnTdbH(OutletAirTemp,EnthAirOutlet)
ELSE
There is no condensation. Thus, the inlet and outlet humidity ratios are equal, and the outlet temperature is a function of the outlet air enthalpy as shown below:
OutletAirTemp=PsyTdbFnHW(EnthalpyAirOutlet,OutletAirHumRat)
and
OutletAirHumRat=InletAirHumRat
ENDIF
Effectiveness η used in Equation [eq:AirTempOutWithCondensation] is defined in Equation [eq:EtaWithCondensation] and the condensation temperature is calculated using a psychrometric function as in Equation [eq:CondensationTemp].
η=1−Exp{−CoilUAExternalCapacitanceAir}
CondensationTemp=PsyTsatFnHPb(EnthAirCondensateTemp,Patm)
EnthAirCondensateTemp=EnthAirInlet−(EnthAirInlet−EnthAirOutlet)η
Once the air outlet temperature are known, then the sensible load is calculated as a product of the capacitance of air and the temperature difference at the inlet and outlet, as in Equation [eq:HeatExchangerQSensible]:
QSensible=CapacitanceAir×(AirTempInlet−AirTempOutlet)
Coil Part Wet Part Dry Calculations (operating block)[LINK]
The Coil would perform under part wet part dry conditions when Air Dewpoint Temperature is less than Coil surface temperature at inlet to air. In this case part of the coil used value of Dry UA for heat transfer and part the coil used Wet UA value for heat transfer.
This problem is solved utilizing the fact that the Exit conditions from the Dry Part of the Coil would become the inlet conditions to the wet part of the coil (see Figure 1) and the coil model determines by iteration what fraction of the coil is wet and based on that it calculates the areas and subsequently the UA values of that dry and wet part, based on the area of the dry and wet part respectively. Explained below are the steps followed for estimating the wet dry behavior of the coil.
First, iterate between the Dry Coil and the Wet Coil. First calculate Coil Completely Dry performance by estimating the wet dry interface water temperature using equation and inputting this variable as the water inlet temperature to dry Coil.
WetDryInterfaceWaterTemp=WaterTempInlet+AreaWetFraction∗(WaterTempOutlet−WaterTempInlet)
The value of Surface Area Wet fraction is estimated initially as follows:
AreaWetFractionEstimate=AirDewPtTemp−InletWaterTempOutletWaterTemp−InletWaterTemp
For the above mentioned iteration the value of Coil UA for Wet and Dry part need to be varied according to the new respective area of the wet and dry parts. This estimate of Wet and Dry area is a product of the estimated Surface Area Fraction and total coil external area, which keeps varying as will be explained further in the document.
UA value for Dry part of the Coil is estimated as below.
CoilUADryExternal=SurfAreaDry1CoilUDryExternal+1CoilUInternal
where Surface Area Dry = (Total Coil Area – Wet Part Area), where the Wet part area is the product of Surface fraction Wet and Total Coil Area.
UA value for the Wet part of the Coil requires Wet UA external and Wet UA Internal, which are calculated as below.
WetPartUAExternal=CoilUWetExternal×SurfaceAreaWet
WetPartUAInternal=CoilUInternal×SurfaceAreaWet
It is essential to remember that the mode of calculation for the coils remains the same as in completely wet and completely dry mode, only the UA values and water, air outlet and inlet values change.
Now iterate between the Dry Coil and wet Coil with the above respective UA, and usual operating inputs except the variable water inlet temperature for dry Coil is replaced with Wet Dry Interface Water temperature, and in the Wet Coil the Outlet Air Temperature from dry Coil is the inlet air temperature to Wet Coil. The iteration proceeds till the Outlet Water Temperature from Wet Coil equals the Wet Dry Interface Water Temp, which is the input to Dry Coil.
Dry Part Inputs, Iteration Case 1: Explained In Programming Fashion
CALL CoilCompletelyDry(WetDryInterfcWaterTemp, InletAirTemp, DryCoilUA, OutletWaterTemp, WetDryInterfcAirTemp, WetDryInterfcHumRat, DryCoilHeatTranfer)
Input the calculated values calculated by Dry Coil above into Wet Coil below:
CALL CoilCompletelyWet(InletWaterTemp, WetDryInterfcAirTemp, WetDryInterfcHumRat, WetPartUAInternal, WetPartUAExternal, EstimateWetDryInterfcWaterTemp, OutletAirTemp, OutletAirHumRat, WetCoilTotalHeatTransfer, WetCoilSensibleHeatTransfer, EstimateSurfAreaWetFraction, WetDryInterfcSurfTemp)
Iterate Between the above two Wet and Dry Coil calls until WetDryInterfcWaterTemp = EstimateWetDryInterfcWaterTemp. The key is to have the difference between the variables (WetDryInterfcWaterTemp  OutletWaterTemp) in the Dry Coil equal to (InletWaterTemp EstimatedWetDryInterfcWaterTemp) in the Wet Coil. This equality quantized the relative part of coil that is dry and the part that is wet on the basis of the heat transfer that has occurred.
After the above convergence check for the coil being dry, iterate to calculate surface fraction area wet.
IF
{(AreaFractionWet≤0.0).AND.(WetDryInterfaceSurfTemp>AirDewPt)}
THEN CoilCompletelyDry
If Equation [eq:WetDryCoilConvergenceCheck] is satisfied, then the coil is dry and simply output the value for Dry Coil calculated else the coil is partially wet and then iterate to find the surface fraction area wet. Start with the initial guess value of surface area fraction (Equation [eq:AreaWetFractionEstimate]) wet and iterate on the entire loop starting from Equation [eq:AreaWetFractionEstimate] until the Wet Dry Interface Temperature equals the Air Dewpoint Temperature. The value of Surface Area fraction wet at which the interface air temperature equals is dewpoint is the transition point from wet to dry and gives the % of coil that is dry and % that is wet.
Graphs Showing the Performance of the coil model at optimum operating conditions are shown below. All values of variable used have been normalized.
IBPSA BuildSim2004. 2004. Colarado Boulder: An Improvement of Ashrae Secondary HVAC toolkit Simple Cooling Coil Model for Building Simulation, Rahul J Chillar, Richard J Liesen M&IE ,UIUC.
Stoecker, W.F. <dates unspecified> Design of Thermal Systems,: ME 423 Class Notes , M& IE Dept UIUC.
Brandemeuhl, M. J. 1993. HVAC2 Toolkit: Algorithms and Subroutines for Secondary HVAC Systems Energy Calculations, ASHRAE.
Elmahdy, A.H. and Mitalas, G.P. 1977. “A Simple Model for Cooling and Dehumidifying Coils for Use In Calculating Energy Requirements for Buildings ASHRAE Transactions, Vol.83 Part 2, pp. 103117.
Threlkeld, J.L. 1970. Thermal Environmental Engineering, 2nd Edition, Englewood Cliffs: PrenticeHall,Inc. pp. 254270.
ASHRAE Secondary HVAC Toolkit TRNSYS. 1990. A Transient System Simulation Program: Reference Manual. Solar Energy Laboratory, Univ. WisconsinMadison, pp. 4.6.81  4.6.812.
Kays, W.M. and A.L. London. 1964. Compact Heat Exchangers, 2nd Edition, New York: McGrawHill.
Clark, D.R.. 1985. HVACSIM+ Building Systems and Equipment Simulation Program Reference Manual, Pub. No. NBSIR 842996, National Bureau of Standards, U.S. Department of Commerce, January, 1985
Elmahdy, A.H. 1975. Analytical and Experimental MultiRow FinnedTube Heat Exchanger Performance During Cooling and Dehumidifying Processes, Ph.D. Thesis, Carleton University, Ottawa, Canada, December, 1975.
Elmahdy, A.H., and Mitalas, G.P. 1977. “A Simple Model for Cooling and Dehumidifying Coils for Use in Calculating Energy Requirements for Buildings,” ASHRAE Transactions, Vol. 83, Part 2, pp. 103117.
ChilledWaterBased Detailed Geometry Air Cooling Coil[LINK]
The input object Coil:Cooling:Water:DetailedGeometry provides a coil model that predicts changes in air and water flow variables across the coil based on the coil geometry. A greatly simplified schematic of enthalpy and temperature conditions in a counterflow cooling/dehumidifying coil is shown in the following schematic figure. In addition, the variables required to model a cooling/dehumidifying coils and their definitions are extensively listed in “Table 4. Coil Geometry and Flow Variables for Coils”. The input required to model the coil includes a complete geometric description that, in most cases, should be derivable from specific manufacturer’s data. The coil simulation model is essentially the one presented by Elmahdy and Mitalas (1977) and implemented in HVACSIM+ (Clark 1985), a modular program also designed for energy analysis of building systems. The model solves the equations for the dry and wet sections of the coil using log mean temperature and log mean enthalpy differences between the liquid and the air streams. Elmahdy and Mitalas state that crossflow counterflow coils with at four rows or more are approximated well by this model. This does not constitute a major limitation since cooling and dehumidifying coils typically have more than four rows.
Heat Transfer and Energy Balance[LINK]
The cooling coil may be completely dry, completely wet with condensation, or it may have wet and dry sections. The actual condition of the coil surface depends on the humidity and temperature of the air passing over the coil and the coil surface temperature. The partly wetpartly dry case represents the most general scenario for the coil surface conditions. The all dry and all wet cases can be considered as limiting solutions of the wet or dry areas respectively going to zero. In the general case, equations are written for both the dry and wet regions of the coil. For each region the heat transfer rate from air to water may be defined by the rate of enthalpy change in the air and in the water. The rates must balance between each medium for energy to be conserved. Equations [eq:QdDotmCpdT] through [eq:QwDotmdH] express the energy balance between the water and the air for the case of dry and wet coils respectively. Equations [eq:QwDotmCpdT] and [eq:QwDotUALMHD] represent the heat transfer rate between water and air based on the actual performance of the coil. The UA parameter can be calculated from the parameters in the following table.
Coil Geometry and Flow Variables for Coils
A 
area 
LMHD 
log mean enthalpy difference 
A 
air, air side 
LMTD 
log mean temperature difference 
aa, bb 
coeff. in enthalpy approximation 
˙m 
mass flow rate 
C1, C2 
coeff. in air side film coeff. 
mf 
metal and fouling 
Cp

specific heat 
μ 
viscosity 
D 
diameter, effective diameter 
o 
outside (air side) 
Dhdr 
hydraulic diameter on air side 
Pr 
Prandtl number 
D 
dry region 
˙Q 
heat transfer rate 
δ 
thickness 
R 
overall thermal resistance 
Δ 
spacing 
Re 
Reynolds number 
F 
heat transfer film coefficient 
ρ 
ratio of diameters 
fai 
variable in fin eff. calculation 
s 
surface, outside of metal 
fin, fins 
air side fin geometry 
St 
Stanton number 
H 
enthalpy 
T 
temperature 
η 
efficiency 
tube 
water tube 
I0() 
mod Bessel fn, 1st kind, ord 0 
UAdry 
dry heat xfer coeff. * dry area 
I1() 
mod Bessel fn, 1st kind, ord 1 
UcAw 
wet heat xfer coeff. * wet area 
K0() 
mod Bessel fn, 2nd kind, ord 0 
ub, ue 
variables in fin eff. calculation 
K1() 
mod Bessel fn, 2nd kind, ord 1 
V 
average velocity 
I 
inside (water side) 
w 
water, water side, or wet region 
K1 
variable in sol’n form of eq. 
wa 
humidity ratio 
K 
thermal conductivity 
Z 
variables in sol’n form of eq. 
L 
length 
1, 2, 3 
positions (see diagram) 
Equations [eq:QdDotmCpdT] through [eq:QwDotUALMHD] represent two sets of three equations with 7 unknowns: ˙Qd, Ta,1, Ta,2, Tw,2, Tw,3, ˙ma, ˙mw. However, normally at least four of these variables are specified, for example: inlet water temperature, outlet air temperature, water flow rate, air flow rate, so that the system of equations is effectively closed.
˙Qd=˙maCp,a(Ta,1−Ta,2)
˙Qd=˙mwCp,w(Tw,3−Tw,2)
˙Qd=(UAdry)(LMTD)
˙Qw=˙ma(Ha,2−Ha,3)
˙Qw=˙mwCp,w(Tw,2−Tw,1)
˙Qw=(UcAw)(LMHD)
In order to manipulate these equations, the log mean temperature and enthalpy differences are expanded as shown in Equations [eq:CoilLMTD] and [eq:CoilLMHD]. Finally, a linear approximation of the enthalpy of saturated air over the range of surface temperature is made using Equation [eq:CoilHw]. Note that in Equation [eq:CoilLMHD] Hw refers to the enthalpy of saturated air at the water temperature.
LMTD=(Ta,1−Tw,3)−(Ta,2−Tw,2)lnTa,1−Tw,3Ta,2−Tw,2
LMHD=(Ha,2−Hw,2)−(Ha,3−Hw,1)lnHa,2−Hw,2Ha,3−Hw,1
Hw=aa+bbTw
Equation [eq:CoilTw2Equation] is derived from the above equations and is used to solve for the coil conditions when all of the inlet conditions are given as input. Operating in this manner, the coil does not have a controlled outlet air temperature.
Tw,2=(1−Z)(Ha,1−aa−K1Cp,aTa,1)+ZTw,1(bb−mwCp,wma)bb−ZmwCp,wma−(1−Z)K1Cp,a
An alternative solution method is to define the coil leaving air temperature as an input with a variable water flow rate. In this case Equations [eq:CoilTw2419] and [eq:CoilTw2420] are more convenient. Equations [eq:CoilZ421] through [eq:CoilZd423] define terms that are used to simplify Equations [eq:CoilTw2Equation], [eq:CoilTw2419] and [eq:CoilTw2420].
Tw,2=(1−Z)(Ha,3−aa)+Tw,1(mwCp,wma−bbZ)mwCp,wma−bb
Tw,2=(Zd−1)Ta1Cp,a+Tw,3(Cp,a−ZdmwCp,wma)Zd(Cp,a−mwCp,wma)
Z=exp(UcAw(1ma−bbmwCp,w))
K1=Zd−1Zd−maCp,amwCp,w
Zd=exp(UcAdry(1maCp,a−1mwCp,w))
Underlying Correlations, Properties, and Assumptions[LINK]
Overall heat transfer coefficients are calculated from the specified coil geometry and by using empirical correlations from fluid mechanics and heat transfer. For the water side, Equation [eq:Coilfi] gives the film heat transfer coefficient in SI units:
fi=1.429(1+0.0146Tw)V0.8wD−0.2i
This is valid for Reynolds numbers greater than 3100 based on water flow velocity and pipe inside diameter and is given in Elmahdy and Mitalas(1977) as recommended in the standard issued by the AirConditioning and Refrigeration Institute (1972) for aircooling coils. The definition of overall inside thermal resistance follows directly as shown in Equation [eq:CoilRi].
Ri=1fiAi
Equation [eq:Coilfo] gives the film coefficient for the air side. Another form of the same equation is Equation [eq:CoilC1Rea], which is familiar from the data presented in Kays and London (1984). For coil sections that have a wet surface due to condensation, the air side film coefficient is modified according to Equation [eq:Coilfow]. The correction term, a function of air Reynolds number, is valid for Reynolds numbers between 400 and 1500. The coefficients in Equations [eq:Coilfo] and [eq:CoilC1Rea] are calculated by Equations [eq:CoilC1] and [eq:CoilC2] that are functions of the coil geometry. Elmahdy (1977) explains the modifier for the wet surface and coefficients for the film coefficient. Equations [eq:CoilDhdr] through [eq:Coilmua] show definitions and values of common parameters and properties.
fo=C1ReC2amaAa,minflowCp,aPr2/3a
C1ReC2a=StaPr2/3a
fo,w=fo(1.425−5.1×10−4Rea+2.63×10−7Re2a)
C1=0.159(δfinDhdr)−0.065(δfinLfin)0.141
C2=−0.323(ΔfinsLfin)0.049(DfinΔtuberows)0.549(δfinΔfins)−0.028
Dhdr=4Aa,minflowδcoilAs,total
Rea=4δcoil(1+wa)maAs,totalμa
Pra=0.733
μa=1.846×10−5
The film coefficients above act on the extended surface of the air side, that is the area of the fins and the tubes. Therefore, the fin efficiency must also be considered in calculating the overall thermal resistance on the outside. Gardner (1945) gives the derivation of Equation [eq:Coiletafin], used as a curve fit to find the fin efficiency as a function of film coefficient. This equation is based on circular fins of constant thickness. To model a coil with flat fins, an effective diameter – that of circular fins with the same fin area – is used. Equations [eq:Coilfai] through [eq:Coilub] define variables used in Equation [eq:Coiletafin]. The overall efficiency of the surface is shown by Equation [eq:Coiletao]. Note that the efficiency is found by the same equations for the wet surface using the wet surface film coefficient.
ηfin=−2ρfai(1+ρ)[I1(ub)K1(ue)−K1(ub)I1(ue)I0(ub)K1(ue)+K0(ub)I1(ue)]
fai=(Dfin−Dtube)2√2fokfinδfin
ρ=DtubeDfin
ue=fai1−ρ
ub=ueρ
ηo=1−(1−ηfin)AfinsAs,total
The definition of overall outside thermal resistance is given in Equation [eq:CoilRo441] as a function of fin efficiency and film coefficient. For a wet coil surface the resistance must be defined differently because the heat transfer equations are based on enthalpy rather than temperature differences, as shown in Equation [eq:CoilRow442].
Ro=1foηoAs,total
Ro,w=Cp,a/bbfo,wηo,wAs,total
Equation [eq:CoilRmf] gives the last two overall components of thermal resistance. They represent the metal tube wall and internal fouling. The fouling factor, due to deposits of dirt and corrosion of the tube inside surfaces, is assumed to be 5x10−5 m2K/W. All components of thermal resistance are added in series to produce the overall heat transfer coefficients shown in Equations [eq:CoilUAdry] and [eq:CoilUcAw].
Rmf=δtubektubeAi+FlAi
UAdry=AdryAs,total[1Ri+Rmf+Ro]
UcAw=AwAs,total[1/1bbbbRi+Rmf+Ro,w]
Solution Method of Model[LINK]
The complicated equations derived above were implemented in a successive substitution solution procedure to calculate the coil performance based on the input parameters. The MODSIM implementation of a cooling coil, the TYPE12 subroutine, was the motivation for this approach; the method used there has been retained with modifications for the uncontrolled coil model. Clark (1985) contains notes about the MODSIM routine.
In the general case, the cooling coil is only partially wet. For an uncontrolled coil, Equation [eq:CoilTw2Equation] is used to find the water temperature at the boundary. Several simple equations in the loop adjust the boundary point until the dry surface temperature at the boundary is equal to the dewpoint of the inlet air. For the controlled coil, Equations [eq:CoilTw2419] and [eq:CoilTw2420] give two calculations of the boundary temperature, and the water flow rate and boundary position are adjusted until the two equations agree.
Special cases occur when the coil is all wet or all dry. The coil is solved as if it were all wet before the general case is attempted. If the wet surface temperatures at the coil inlet and outlet are both below the dewpoint, no further solution is required. However, to ensure a continuous solution as flow variables are changed, when the surface is all dry or when it is wet with only the dry surface equations yielding a surface temperature below the dewpoint at the water outlet, the general solution is used to calculate the unknowns. In the solution of the controlled coil the outlet air enthalpy, given some resulting dehumidification, must correspond to the enthalpy at the specified outlet air temperature.
Application of Cooling Coil Model to Heating Coils[LINK]
The implementation of detailed heating coil models in IBLAST was another important aspect of the system/plant integration. The same kind of loops exist to provide hot water to the heating coils from the boilers as exist to supply the cooling coils with chilled water from the chillers. Some simplifications can be made, however, since the enthalpy change of the air flowing over a heating coil is entirely sensible. There is no condensation in a heating coil. In order to allow heating and cooling coils to be specified using the same geometric parameters, a heating coil simulation was developed from the cooling coil model described above by eliminating the wet surface analysis.
In addition, it was concluded that, since much simpler and less computationally expensive heating coil simulations are possible, an option was provided in IBLAST for a heating coil design using only the UA value of the coil, the product of heat transfer coefficient and coil area. This model was largely based on the TYPE10 subroutine implemented in MODSIM. The equations used to model the performance of the TYPE10 heating coil are as follows:
Ta,out=Ta,in+(Tw,in−Ta,in)ε(min(Cp,a˙ma,Cp,w˙mw)Cp,a˙ma)Tw,out=Tw,in−(Ta,out−Ta,in)(Cp,a˙maCp,w˙mw)
where the coil effectiveness is given by:
ε=1−exp⎛⎜
⎜
⎜
⎜⎝{exp[−(min{Cp,a˙ma,Cp,w˙mw}max{Cp,a˙ma,Cp,w˙mw}){NTU}0.78]−1}(min{Cp,a˙ma,Cp,w˙mw}max{Cp,a˙ma,Cp,w˙mw}){NTU}−.22⎞⎟
⎟
⎟
⎟⎠
The parameter NTU is the number of transfer units and is defined as a function of the UA value of the coil as follows:
NTU=UAmin(Cp,a˙ma,Cp,w˙mw)
HotWaterBased Air Heating Coil[LINK]
The input object Coil:Heating:Water provides a model that uses an NTU–effectiveness model of a static heat exchanger. The model is an inlet – outlet model: given the inlet conditions and flow rates and the UA, the effectiveness is calculated using the formula for the effectiveness of a crossflow heat exchanger with both fluid streams unmixed. The effectiveness then allows the calculation of the outlet conditions from the inlet conditions.
The inputs to the model are: (1) the current inlet temperatures and flow rates of the air and water fluid streams and (2) the UA of the coil. Note that the UA is fixed in this model and is not a function of the flow rates.
There are 2 alternative user inputs for the component: the user may input the design water volumetric flow rate and the UA directly; or the user may choose to input the more familiar design heating capacity plus design inlet & outlet temperatures and let the program calculate the design UA. These alternative user inputs are fully described in the EnergyPlus Input Output Reference document.
Model Description[LINK]
The air and water capacitance flows are defined as:
˙Cair=cp,air⋅˙mair
˙Cwater=cp,water⋅˙mwater
The minimum and maximum capacity flows are then:
˙Cmin=min(˙Cair,˙Cwater)
˙Cmax=max(˙Cair,˙Cwater)
The capacitance flow ratio is defined as:
Z=˙Cmin/˙Cmax
The number of transfer units (NTU) is:
NTU=UA/˙Cmin
The effectiveness is:
ε=1−exp(e−NTU⋅Z⋅η−1Z⋅η)
where η=NTU−0.22.
The outlet conditions are then:
Tair,out=Tair,in+ε⋅˙Cmin⋅(Twater,in−Tair,in)/˙Cair
Twater,out=Twater,in−˙Cair⋅(Tair,out−Tair,in)/˙Cwater
The output of the coil in watts is:
˙Qcoil=˙Cwater⋅(Twater,in−Twater,out)
The UA value is recalculated for each timestep. A nominal UA, UA0, at the rating point is calculated by the program using the input for rated conditions and a search routine called root solver.
User input for the ratio of convective heat transfers at the nominal or rated operating point, “r,” is used in the model. This ratio is defined as:
r=ηf(hA)air(hA)water
where:
ηf is the fin efficiency, (dimensionless)
h is the surface convection heat transfer coefficient
A is the surface area.
The value calculated for UA0 is used with the input for r to characterize the convective heat transfer on the water sides at the nominal rating operation point using:
((hA)w)0=UA0(r+1r)
and on the air side at the nominal rating point using:
(ηf(hA)a)0=r(hA)w,0
Then, the following equations are used to calculate a new UA as a function of the flow rates and inlet temperatures at each timestep.
xa=1+4.769⋅10−3(Tair,in−Tair,in,0)
ηf(hA)a=xa(˙ma˙ma,0)0.8(ηf(hA)a)0
xw=1+(0.0141+0.014Twater,in,0)(Twater,in−
Coils[LINK]
ChilledWaterBased Air Cooling Coil[LINK]
The input object Coil:Cooling:Water is simpler than the detailed geometry model. The simple model provides a good prediction of the air and water outlet conditions without requiring the detailed geometric input required for the detailed model. A greatly simplified schematic of enthalpy and temperature conditions in a counter flow cooling/dehumidifying coil is shown in the schematic Figure 1. The input required to model the coil includes only a set of thermodynamic design inputs, which require no specific manufacturer’s data. The coil simulation model is essentially a modification of one presented by Elmahdy and Mitalas (1977), TRNSYS, 1990 and Threlkeld, J.L. 1970. The model calculates the UA values required for a Dry, Wet and Part Wet & Part Dry Coil and iterates between the Dry and Wet Coil to output the fraction wet. There are two modes of flow operation for this model: CrossFlow or CounterFlow. The default mode is CounterFlow. In addition the coil has two modes of analysis: Simple Analysis and Detailed Analysis. The Simple analysis mode operates the coil as either wet or dry while the detailed mode simulates the coil as part wet partdry. While the detailed mode provides more accurate results, it is significantly slower than the simple model. The simple mode gives good results for an annual simulation but will not be adequate for a time step performance analysis.
Simplified Schematic of Cooling/Dehumidifying Coil [fig:simplifiedschematicofcoolingdehumidifying]
Heat Transfer and Energy Balance[LINK]
The cooling coil may be completely dry, completely wet with condensation, or it may have wet and dry sections. The actual condition of the coil surface depends on the humidity and temperature of the air passing over the coil and the coil surface temperature. The partdry partwet case represents the most general scenario for the coil surface conditions. There are subroutines present in the model for both the dry and wet regions of the coil, and a subroutine that iterates between the dry and wet subroutines to calculate the fraction of the coil surface that is wet. For each region the heat transfer rate from air to water may be defined by the rate of enthalpy change in the air and in the water. The rates must balance between each medium for energy to be conserved.
Model Description[LINK]
The Model has two blocks: 1st = Design Block with the Design Inputs. This block calculates the Design UFactor Times Area Value (UA) values required by the model. Using these UA values the model simulates the operating conditions. The operating block is the one containing the operating conditions, the conditions at which the coil operates. Following is the list of Design and Operating inputs and subsequently the Design and Operating variables used in the model.
Intermediate calculated UFactor Times Area Values: The Crux of the Model[LINK]
The various UFactor Times Area values (UA) required by this model are calculated from the above inputs, which are explained later in the document. The various UA are:
The UA values are calculated assuming a wet coil at the design conditions. Following are a few important calculations to understand the working of the model. The model is basically divided into two blocks: the Design Block and the Operating Block.
The Design Block is a one time calculation. The aim of the Design Block is to calculate the Coil UA for use in the operating Block.
Design Block Calculations[LINK]
The design block has the code for calculating the six Coil UA values required by the operating block. Reasonable assumptions have been made in the calculations to maintain the simplicity of the model.
Heat transfer in a wet coil model is based on enthalpy rather than temperature to take into account latent effects. While heat transfer rates are commonly expressed as the product of an overall heat transfer coefficient, UA, and a temperature difference, the use of enthalpybased heat transfer calculations requires an enthalpybased heat transfer coefficient which we denote as DesUACoilTotalEnth and hence the equation.
Q=DesUACoilTotalEnth∗(Hair,mean−Hwater,mean)
The value of Q is calculated using product of air mass flow rate and difference in inlet and outlet air enthalpies at design conditions.
The relation between the enthalpybased UA and the temperaturebased UA is:
DesUACoilTotalEnth=CoilUA/Cp
where CoilUA is the conventional heat transfer coefficient and Cp is the specific heat of the air.
We need the following quantities for our design calculations. The Psy functions are the EnergyPlus builtin psychrometric functions.
˙mair=ρair˙Vair
hair,in=PsyHFnTdbW(Tair,in,wair,in)
hair,out=PsyHFnTdbW(Tair,out,wair,out)
hw,sat,in=PsyHFnTdbW(Tw,in,PsyWFnTdpPb(Tw,in,Patm))
˙Qcoil=˙mair(hair,in−hair,out)
Tw,out=Tw,in+˙Qcoil/(˙mw,maxCp,w)
hw,sat,out=PsyHFnTdbW(Tw,out,PsyWFnTdpPb(Tw,out,Patm))
We now calculate the design coil bypass factor. The bypass factor is not used in subsequent calculations. It is calculated solely to use as check on the reasonableness of the userinput design inlet and outlet conditions. First we make an initial estimate of the apparatus dew point temperature:
Tair,dp,app=PsyTdpFnWPb(wair,out,Patm)
We also need the “slope” of temperature versus humidity ratio on the psych chart between the inlet and outlet air conditions:
ST,w=(Tair,in−Tair,out)/(wair,in−wair,out)
We now obtain the actual design apparatus dewpoint temperature by iterating over the following two equations:
wair,dp,app=PsyWFnTdpPb(Tair,dp,app,Patm)
Tair,dp,app=Tair,in−ST,w(wair,in−wair,dp,app)
The apparatus dewpoint enthalpy is then:
hair,dp,app=PsyHFnTdbW(Tair,dp,app,wair,dp,app)
and the coil bypass factor is:
Fcoilbypass=(hair,out−hair,dp,app)/(hair,in−hair,dp,app)
If the iterative procedure doesn’t converge, or the coil bypass factor is too large (greater than 0.5), or the apparatus dewpoint enthalpy is less than the saturated air enthalpy at the water inlet temperature, the design outlet air conditions are reset to 90% relative humidity at the same outlet enthalpy. The above design calculations are then repeated.
We are now ready to calculate the design coil UA. This will be accomplished by inverting the simple coil calculation routine CoolingCoil using the root solver method. First we make an initial estimate of the coil UA.
Δhlmd=(hair,in−hw,sat,out)−(hair,out−hw,sat,in)log(hair,in−hw,sat,outhair,out−hw,sat,in)
UAcoil,enthalpy−based=˙Qcoil/Δhlmd
UAcoil,ext=Cp,airUAcoil,enthalpy−based
We set the internal UA to 3.3 times the external UA (as a typical value for a coil). Then the total UA is:
UAcoil,tot=1(1/UAcoil,int+1/UAcoil,ext)
The next step is to estimate the coil external heat transfer surface area. This is done in the function EstimateHEXSurfaceArea:
Areacoil,ext=EstimateHEXSurfaceArea
using the following assumptions:
Tube inside diameter = 0.0122 (m)
Tube side water velocity = 2.0 (m/s)
Inside to outside coil surface area ratio (Ai/Ao) = 0.07 ()
Fins overall efficiency = 0.92 ()
Aluminum fins, 12 fins per inch with fins to total outside surface area ratio of 90%.
Airside combined heat and mass transfer coefficient = 140 (W/m2∘C)
Interior and exterior U values (really UA’s per unit exterior surface area) are calculated by dividing the above UA’s by the area. The resulting Ucoil,ext is assumed to be Ucoil,ext,wet; Ucoil,ext,dry is set equal to Ucoil,ext,wet. We now have all the starting values needed for inverting the simple coil model using the chosen root solver iterative method. Once the iteration is completed, we have coil UA’s and U’s that yield the design outlet air and water enthalpies given the inlet design conditions and flow rates. Note that the simple coil model can not exactly match the specified design outlet air temperature and humidity ratio. It can only match the design air outlet enthalpy. Generally the simple coil model will yield outlet conditions near the saturation curve if any dehumidification is occuring. Typical outlet relative humidities are around 95%.
Variable UA[LINK]
The above calculations yield coil UA’s for the design inlet conditions and air and water flow rates. As the flow rates vary during the time step calculations, the UA’s need to be adjusted, since coil UA’s are a rather strong function of air and water side flow rates. Each time step the coil UA’s are modified using the same formulas as are used in the hot water coil model. Refer to that model for the flow dependences.
Operating Block Calculations:[LINK]
There are two modes of coil analysis in the operating block. They are the Simple analysis mode and the detailed analysis mode. The simple analysis mode assumes the coil to be either all wet or either all dry and execute the model , on the other hand the detailed mode checks for part wet part dry mode of operation and reports surface area wet fraction of coil, however the program execution time in detailed mode is noticeably higher.
The operating block for Detailed Mode Analysis of this coil model is divided into three modes of coil performance. The modes being:
Coil is completely dry: There is no moisture condensation on the coil surface and the coil is a dry coil. This is an extreme condition when the entering air has very low humidity ratio or is dry air.
Coil is completely wet: The entire coil is wet due to complete condensation on the surface of the coil.
Part Wet Part Dry Mode: This is the usual/frequent mode of operation of coil where part of the coil at entry of air is dry and as air cools condensation occurs and part of the coil becomes wet.
The Part Wet Part Dry Mode of operation is essentially a function the Coil Completely Dry and Coil Completely Wet mode. This subroutine iterates between the Dry Coil and the Wet Coil to give outputs, a detailed explanation is given later in the document. The operating block requires 5 inputs, which are mentioned earlier in the document. These inputs are automatically generated from the node connections in Energy Plus. The user does not have to input any information to run this coil model.
The option to identify which mode of operation the coil should perform ie, for a given set of inputs would the coil be Dry, Wet or Part Wet Part Dry, is decided by set of conditions described below.
IF (Temperature Dewpoint Air < Water Inlet Temperature) THEN the coil is Dry and we call the Subroutine Coil Completely Dry. In this case outlet temperature of air would be higher than the air dewpoint and hence there would be no condensation.
IF (Temperature Dewpoint Air > Water Inlet Temperature) THEN the coil is completely wet, call subroutine Coil Completely Wet, it is assumed that moisture condensation occurs over completely surface of the coil. However we go ahead and check for the coil being partially wet with the following condition.
IF (AirDewPointTemp < AirInletCoilSurfTemp) THEN the coil is Partially Wet because there is possibility that air temperature will go below its dewpoint and moisture will condense on latter part of the cooling coil.
The Operating Block for Simple Mode Analysis is divided into two modes of coil performance, the two modes being:
Coil is completely dry: There is no moisture condensation on the coil surface and the coil is a dry coil.
Coil is completely wet: The entire coil is wet due to complete condensation on the surface of the coil.
The option to identify which mode of operation the Simple mode analysis should perform ie, for a given set of inputs would the coil be Dry or Wet is decided by set of conditions described below.
IF (Temperature Dewpoint Air < Water Inlet Temperature) THEN the coil is Dry and we call the Subroutine Coil Completely Dry. In this case outlet temperature of air would be higher than the air dewpoint and hence there would be no condensation.
IF (Temperature Dewpoint Air > Water Inlet Temperature) THEN the coil is completely wet, call subroutine Coil Completely Wet, it is assumed that moisture condensation occurs over completely surface of the coil. However we go ahead and check for the coil being partially wet with the following condition.
The above is a simple mode of analysis and the results are very slightly different from the detailed mode of analysis. The algorithms used in Simple mode and the Detailed mode are identically similar. The surface area wet fraction in the coil is reported as 1.0 or 0.0 for wet or dry coil respectively. The program defaults to simple mode of analysis for enabling higher execution speed.
Effectiveness Equations[LINK]
There are two modes of flow for the coil, CounterFlow or CrossFlow. The default mode is CounterFlow. According to the mode of flow the following NTU  Effectiveness relationships are used to calculate coil effectiveness, which is used later by all the three modes (Dry, Wet, Part Wet) for calculating air outlet conditions and heat transfer.
Following are the relations used for calculating effectiveness equation for the heat exchangers.
Counter Flow Heat Exchanger Effectiveness Equation:
ηCounterFlow=(1−Exp(−NTU×(1−RatioStreamCapacity)))1−RatioStreamCapacity×Exp(−NTU×(1−RatioStreamCapacity))
In Equation [eq:CounterFlowHeatExchangerEffectiveness], the variable RatioStreamCapacity is defined as below:
RatioStreamCapacity=MinCapacityStreamMaxCapacityStream
In Equation [eq:RatioStreamCapacity], the capacities of stream are defined as below in Equation [eq:MinMaxCapacityStream]:
(Min,Max)CapacityStream=(MassFlowRate×Cp)air,water
NTU as shown in Equation [eq:CounterFlowHeatExchangerEffectiveness] is defined as the Number of Transfer Units and is a function of Coil UA and the Minimum Capacity of Stream. The Coil UA is a variable in this equation and depends on which mode of the coil operation (Dry, Wet, Part Wet) is calling upon Equation [eq:CounterFlowHeatExchangerEffectiveness], i.e., if it is Coil Completely Dry calling upon the effectiveness equation with the value of Dry UA total, which in our case is defined as CoilUA_total. Equation [eq:NTUCounterFlowHeatExchanger] gives definition for NTU.
NTU=CoilUAMinStreamCapacity
Cross Flow Heat Exchanger Effectiveness Equation:
ηCrossFlow=1−EXP{Exp(−NTU×RatioStreamCapacity×NTU−0.22)−1RatioStreamCapacity×NTU−0.22}
The variables in the above equation have already been defined earlier. Depending on the mode of operation of the coil model, the CrossFlow or CounterFlow equations are used to calculate the effectiveness.
Coil Outlet Conditions[LINK]
Calculating the Outlet Stream Conditions using the effectiveness value from Equation [eq:CounterFlowHeatExchangerEffectiveness] or [eq:EtaCrossFlow] depending on the mode of flow. The energy difference between the outlet and inlet stream conditions gives the amount of heat transfer that has actually take place. The temperature of air and water at the outlet of the coil are given by the following equations:
TempAirOut=TempAirinlet−ηcross,counter×MaxHeatTransferStreamCapacityAir
TempWaterOut=TempWaterInlet+ηCross,counter×MaxHeatTransferStreamCapacityWater
In Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp] above, the maximum heat transfer is calculated as shown in the following equation:
MaxHeatTransfer=MinStreamCapacity×(TempAirInlet−TempWaterInlet)
Coil Completely Dry Calculations (operating block)[LINK]
Since the coil is dry, the sensible load is equal to total load and the same with the humidity ratios at inlet and outlet, as in Equations [eq:HeatExchangerQSensibleDryCoil] and [eq:HeatExchangerHumRatioDryCoil].
QSensibleDryCoil=QTotalDryCoil
HumRatioInlet=HumRatioOutlet
Total Heat Transfer in dry coil is as follows:
QTotalDryCoil=CapacityAir×(AirTempIn−AirTempOutlet)
The variables in the above equation are calculated earlier in Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp] to give the total cooling load on the coil.
Coil Completely Wet Calculations (operating block)[LINK]
In wet coil we need to account for latent heat transfer, hence calculations are done using enthalpy of air and water instead of stream temperatures Hence we need to define coil UA for the wet coil based on enthalpy of the operating streams and not design streams.
Similar to Equations [eq:HeatExchangerOutAirTemp] and [eq:HeatExchangerOutWaterTemp], we calculate the air outlet enthalpy and water outlet enthalpy, i.e. by replacing temperature with enthalpy for the respective streams. The input variable for Coil UA in Equation [eq:NTUCounterFlowHeatExchanger] for calculating NTU, in this case it would be enthalpy based and is given as shown in Equation [eq:CoilUAEnthalpyBased]:
CoilUAEnthalpyBased=1(CpSatIntermediateCoilUAInternal+CpAirCoilUAExternal)
Total Coil Load in the case of a Wet Coil is the product of mass flow rate of air and enthalpy difference between the inlet and outlet streams as given in the following equation:
QTotal=˙mair×(EnthAirInlet−EnthAirOutlet)
Once the enthalpy is known the outlet temperatures and outlet humidity ratios of the wet coil are calculated as in equations below.
IF (TempCondensation < PsyTdpFnWPb(InletAirHumRat ,Patm)) THEN
AirTempOut=AirTempinlet−(AirTempinlet−CondensationTemp)×η
and
OutletAirHumdityRatio=PsyWFnTdbH(OutletAirTemp,EnthAirOutlet)
ELSE
There is no condensation. Thus, the inlet and outlet humidity ratios are equal, and the outlet temperature is a function of the outlet air enthalpy as shown below:
OutletAirTemp=PsyTdbFnHW(EnthalpyAirOutlet,OutletAirHumRat)
and
OutletAirHumRat=InletAirHumRat
ENDIF
Effectiveness η used in Equation [eq:AirTempOutWithCondensation] is defined in Equation [eq:EtaWithCondensation] and the condensation temperature is calculated using a psychrometric function as in Equation [eq:CondensationTemp].
η=1−Exp{−CoilUAExternalCapacitanceAir}
CondensationTemp=PsyTsatFnHPb(EnthAirCondensateTemp,Patm)
EnthAirCondensateTemp=EnthAirInlet−(EnthAirInlet−EnthAirOutlet)η
Once the air outlet temperature are known, then the sensible load is calculated as a product of the capacitance of air and the temperature difference at the inlet and outlet, as in Equation [eq:HeatExchangerQSensible]:
QSensible=CapacitanceAir×(AirTempInlet−AirTempOutlet)
Coil Part Wet Part Dry Calculations (operating block)[LINK]
The Coil would perform under part wet part dry conditions when Air Dewpoint Temperature is less than Coil surface temperature at inlet to air. In this case part of the coil used value of Dry UA for heat transfer and part the coil used Wet UA value for heat transfer.
This problem is solved utilizing the fact that the Exit conditions from the Dry Part of the Coil would become the inlet conditions to the wet part of the coil (see Figure 1) and the coil model determines by iteration what fraction of the coil is wet and based on that it calculates the areas and subsequently the UA values of that dry and wet part, based on the area of the dry and wet part respectively. Explained below are the steps followed for estimating the wet dry behavior of the coil.
First, iterate between the Dry Coil and the Wet Coil. First calculate Coil Completely Dry performance by estimating the wet dry interface water temperature using equation and inputting this variable as the water inlet temperature to dry Coil.
WetDryInterfaceWaterTemp=WaterTempInlet+AreaWetFraction∗(WaterTempOutlet−WaterTempInlet)
The value of Surface Area Wet fraction is estimated initially as follows:
AreaWetFractionEstimate=AirDewPtTemp−InletWaterTempOutletWaterTemp−InletWaterTemp
For the above mentioned iteration the value of Coil UA for Wet and Dry part need to be varied according to the new respective area of the wet and dry parts. This estimate of Wet and Dry area is a product of the estimated Surface Area Fraction and total coil external area, which keeps varying as will be explained further in the document.
UA value for Dry part of the Coil is estimated as below.
CoilUADryExternal=SurfAreaDry1CoilUDryExternal+1CoilUInternal
where Surface Area Dry = (Total Coil Area – Wet Part Area), where the Wet part area is the product of Surface fraction Wet and Total Coil Area.
UA value for the Wet part of the Coil requires Wet UA external and Wet UA Internal, which are calculated as below.
WetPartUAExternal=CoilUWetExternal×SurfaceAreaWet
WetPartUAInternal=CoilUInternal×SurfaceAreaWet
It is essential to remember that the mode of calculation for the coils remains the same as in completely wet and completely dry mode, only the UA values and water, air outlet and inlet values change.
Now iterate between the Dry Coil and wet Coil with the above respective UA, and usual operating inputs except the variable water inlet temperature for dry Coil is replaced with Wet Dry Interface Water temperature, and in the Wet Coil the Outlet Air Temperature from dry Coil is the inlet air temperature to Wet Coil. The iteration proceeds till the Outlet Water Temperature from Wet Coil equals the Wet Dry Interface Water Temp, which is the input to Dry Coil.
Dry Part Inputs, Iteration Case 1: Explained In Programming Fashion
CALL CoilCompletelyDry(WetDryInterfcWaterTemp, InletAirTemp, DryCoilUA, OutletWaterTemp, WetDryInterfcAirTemp, WetDryInterfcHumRat, DryCoilHeatTranfer)
Input the calculated values calculated by Dry Coil above into Wet Coil below:
CALL CoilCompletelyWet(InletWaterTemp, WetDryInterfcAirTemp, WetDryInterfcHumRat, WetPartUAInternal, WetPartUAExternal, EstimateWetDryInterfcWaterTemp, OutletAirTemp, OutletAirHumRat, WetCoilTotalHeatTransfer, WetCoilSensibleHeatTransfer, EstimateSurfAreaWetFraction, WetDryInterfcSurfTemp)
Iterate Between the above two Wet and Dry Coil calls until WetDryInterfcWaterTemp = EstimateWetDryInterfcWaterTemp. The key is to have the difference between the variables (WetDryInterfcWaterTemp  OutletWaterTemp) in the Dry Coil equal to (InletWaterTemp EstimatedWetDryInterfcWaterTemp) in the Wet Coil. This equality quantized the relative part of coil that is dry and the part that is wet on the basis of the heat transfer that has occurred.
After the above convergence check for the coil being dry, iterate to calculate surface fraction area wet.
IF
{(AreaFractionWet≤0.0).AND.(WetDryInterfaceSurfTemp>AirDewPt)}
THEN CoilCompletelyDry
If Equation [eq:WetDryCoilConvergenceCheck] is satisfied, then the coil is dry and simply output the value for Dry Coil calculated else the coil is partially wet and then iterate to find the surface fraction area wet. Start with the initial guess value of surface area fraction (Equation [eq:AreaWetFractionEstimate]) wet and iterate on the entire loop starting from Equation [eq:AreaWetFractionEstimate] until the Wet Dry Interface Temperature equals the Air Dewpoint Temperature. The value of Surface Area fraction wet at which the interface air temperature equals is dewpoint is the transition point from wet to dry and gives the % of coil that is dry and % that is wet.
Graphs Showing the Performance of the coil model at optimum operating conditions are shown below. All values of variable used have been normalized.
Air Outlet Temperature Vs. Air Mass Flow Rate [fig:airoutlettemperaturevsairmassflowrate]
Sensible Load Variations Vs. Air mass Flow Rate [fig:sensibleloadvariationsvsairmassflow]
Total and Sensible Load Variations Vs. Air Mass Flow Rate [fig:totalandsensibleloadvariationsvsair]
Surface Area Fraction Wet Vs Air Mass Flow Rate [fig:surfaceareafractionwetvsairmassflow]
References[LINK]
IBPSA BuildSim2004. 2004. Colarado Boulder: An Improvement of Ashrae Secondary HVAC toolkit Simple Cooling Coil Model for Building Simulation, Rahul J Chillar, Richard J Liesen M&IE ,UIUC.
Stoecker, W.F. <dates unspecified> Design of Thermal Systems,: ME 423 Class Notes , M& IE Dept UIUC.
Brandemeuhl, M. J. 1993. HVAC2 Toolkit: Algorithms and Subroutines for Secondary HVAC Systems Energy Calculations, ASHRAE.
Elmahdy, A.H. and Mitalas, G.P. 1977. “A Simple Model for Cooling and Dehumidifying Coils for Use In Calculating Energy Requirements for Buildings ASHRAE Transactions, Vol.83 Part 2, pp. 103117.
Threlkeld, J.L. 1970. Thermal Environmental Engineering, 2nd Edition, Englewood Cliffs: PrenticeHall,Inc. pp. 254270.
ASHRAE Secondary HVAC Toolkit TRNSYS. 1990. A Transient System Simulation Program: Reference Manual. Solar Energy Laboratory, Univ. WisconsinMadison, pp. 4.6.81  4.6.812.
Kays, W.M. and A.L. London. 1964. Compact Heat Exchangers, 2nd Edition, New York: McGrawHill.
Clark, D.R.. 1985. HVACSIM+ Building Systems and Equipment Simulation Program Reference Manual, Pub. No. NBSIR 842996, National Bureau of Standards, U.S. Department of Commerce, January, 1985
Elmahdy, A.H. 1975. Analytical and Experimental MultiRow FinnedTube Heat Exchanger Performance During Cooling and Dehumidifying Processes, Ph.D. Thesis, Carleton University, Ottawa, Canada, December, 1975.
Elmahdy, A.H., and Mitalas, G.P. 1977. “A Simple Model for Cooling and Dehumidifying Coils for Use in Calculating Energy Requirements for Buildings,” ASHRAE Transactions, Vol. 83, Part 2, pp. 103117.
ChilledWaterBased Detailed Geometry Air Cooling Coil[LINK]
The input object Coil:Cooling:Water:DetailedGeometry provides a coil model that predicts changes in air and water flow variables across the coil based on the coil geometry. A greatly simplified schematic of enthalpy and temperature conditions in a counterflow cooling/dehumidifying coil is shown in the following schematic figure. In addition, the variables required to model a cooling/dehumidifying coils and their definitions are extensively listed in “Table 4. Coil Geometry and Flow Variables for Coils”. The input required to model the coil includes a complete geometric description that, in most cases, should be derivable from specific manufacturer’s data. The coil simulation model is essentially the one presented by Elmahdy and Mitalas (1977) and implemented in HVACSIM+ (Clark 1985), a modular program also designed for energy analysis of building systems. The model solves the equations for the dry and wet sections of the coil using log mean temperature and log mean enthalpy differences between the liquid and the air streams. Elmahdy and Mitalas state that crossflow counterflow coils with at four rows or more are approximated well by this model. This does not constitute a major limitation since cooling and dehumidifying coils typically have more than four rows.
Simplified Schematic of Cooling/Dehumidifying Coil [fig:simplifiedschematicofcoolingdehumidifying001]
Heat Transfer and Energy Balance[LINK]
The cooling coil may be completely dry, completely wet with condensation, or it may have wet and dry sections. The actual condition of the coil surface depends on the humidity and temperature of the air passing over the coil and the coil surface temperature. The partly wetpartly dry case represents the most general scenario for the coil surface conditions. The all dry and all wet cases can be considered as limiting solutions of the wet or dry areas respectively going to zero. In the general case, equations are written for both the dry and wet regions of the coil. For each region the heat transfer rate from air to water may be defined by the rate of enthalpy change in the air and in the water. The rates must balance between each medium for energy to be conserved. Equations [eq:QdDotmCpdT] through [eq:QwDotmdH] express the energy balance between the water and the air for the case of dry and wet coils respectively. Equations [eq:QwDotmCpdT] and [eq:QwDotUALMHD] represent the heat transfer rate between water and air based on the actual performance of the coil. The UA parameter can be calculated from the parameters in the following table.
Equations [eq:QdDotmCpdT] through [eq:QwDotUALMHD] represent two sets of three equations with 7 unknowns: ˙Qd, Ta,1, Ta,2, Tw,2, Tw,3, ˙ma, ˙mw. However, normally at least four of these variables are specified, for example: inlet water temperature, outlet air temperature, water flow rate, air flow rate, so that the system of equations is effectively closed.
˙Qd=˙maCp,a(Ta,1−Ta,2)
˙Qd=˙mwCp,w(Tw,3−Tw,2)
˙Qd=(UAdry)(LMTD)
˙Qw=˙ma(Ha,2−Ha,3)
˙Qw=˙mwCp,w(Tw,2−Tw,1)
˙Qw=(UcAw)(LMHD)
In order to manipulate these equations, the log mean temperature and enthalpy differences are expanded as shown in Equations [eq:CoilLMTD] and [eq:CoilLMHD]. Finally, a linear approximation of the enthalpy of saturated air over the range of surface temperature is made using Equation [eq:CoilHw]. Note that in Equation [eq:CoilLMHD] Hw refers to the enthalpy of saturated air at the water temperature.
LMTD=(Ta,1−Tw,3)−(Ta,2−Tw,2)lnTa,1−Tw,3Ta,2−Tw,2
LMHD=(Ha,2−Hw,2)−(Ha,3−Hw,1)lnHa,2−Hw,2Ha,3−Hw,1
Hw=aa+bbTw
Equation [eq:CoilTw2Equation] is derived from the above equations and is used to solve for the coil conditions when all of the inlet conditions are given as input. Operating in this manner, the coil does not have a controlled outlet air temperature.
Tw,2=(1−Z)(Ha,1−aa−K1Cp,aTa,1)+ZTw,1(bb−mwCp,wma)bb−ZmwCp,wma−(1−Z)K1Cp,a
An alternative solution method is to define the coil leaving air temperature as an input with a variable water flow rate. In this case Equations [eq:CoilTw2419] and [eq:CoilTw2420] are more convenient. Equations [eq:CoilZ421] through [eq:CoilZd423] define terms that are used to simplify Equations [eq:CoilTw2Equation], [eq:CoilTw2419] and [eq:CoilTw2420].
Tw,2=(1−Z)(Ha,3−aa)+Tw,1(mwCp,wma−bbZ)mwCp,wma−bb
Tw,2=(Zd−1)Ta1Cp,a+Tw,3(Cp,a−ZdmwCp,wma)Zd(Cp,a−mwCp,wma)
Z=exp(UcAw(1ma−bbmwCp,w))
K1=Zd−1Zd−maCp,amwCp,w
Zd=exp(UcAdry(1maCp,a−1mwCp,w))
Underlying Correlations, Properties, and Assumptions[LINK]
Overall heat transfer coefficients are calculated from the specified coil geometry and by using empirical correlations from fluid mechanics and heat transfer. For the water side, Equation [eq:Coilfi] gives the film heat transfer coefficient in SI units:
fi=1.429(1+0.0146Tw)V0.8wD−0.2i
This is valid for Reynolds numbers greater than 3100 based on water flow velocity and pipe inside diameter and is given in Elmahdy and Mitalas(1977) as recommended in the standard issued by the AirConditioning and Refrigeration Institute (1972) for aircooling coils. The definition of overall inside thermal resistance follows directly as shown in Equation [eq:CoilRi].
Ri=1fiAi
Equation [eq:Coilfo] gives the film coefficient for the air side. Another form of the same equation is Equation [eq:CoilC1Rea], which is familiar from the data presented in Kays and London (1984). For coil sections that have a wet surface due to condensation, the air side film coefficient is modified according to Equation [eq:Coilfow]. The correction term, a function of air Reynolds number, is valid for Reynolds numbers between 400 and 1500. The coefficients in Equations [eq:Coilfo] and [eq:CoilC1Rea] are calculated by Equations [eq:CoilC1] and [eq:CoilC2] that are functions of the coil geometry. Elmahdy (1977) explains the modifier for the wet surface and coefficients for the film coefficient. Equations [eq:CoilDhdr] through [eq:Coilmua] show definitions and values of common parameters and properties.
fo=C1ReC2amaAa,minflowCp,aPr2/3a
C1ReC2a=StaPr2/3a
fo,w=fo(1.425−5.1×10−4Rea+2.63×10−7Re2a)
C1=0.159(δfinDhdr)−0.065(δfinLfin)0.141
C2=−0.323(ΔfinsLfin)0.049(DfinΔtuberows)0.549(δfinΔfins)−0.028
Dhdr=4Aa,minflowδcoilAs,total
Rea=4δcoil(1+wa)maAs,totalμa
Pra=0.733
μa=1.846×10−5
The film coefficients above act on the extended surface of the air side, that is the area of the fins and the tubes. Therefore, the fin efficiency must also be considered in calculating the overall thermal resistance on the outside. Gardner (1945) gives the derivation of Equation [eq:Coiletafin], used as a curve fit to find the fin efficiency as a function of film coefficient. This equation is based on circular fins of constant thickness. To model a coil with flat fins, an effective diameter – that of circular fins with the same fin area – is used. Equations [eq:Coilfai] through [eq:Coilub] define variables used in Equation [eq:Coiletafin]. The overall efficiency of the surface is shown by Equation [eq:Coiletao]. Note that the efficiency is found by the same equations for the wet surface using the wet surface film coefficient.
ηfin=−2ρfai(1+ρ)[I1(ub)K1(ue)−K1(ub)I1(ue)I0(ub)K1(ue)+K0(ub)I1(ue)]
fai=(Dfin−Dtube)2√2fokfinδfin
ρ=DtubeDfin
ue=fai1−ρ
ub=ueρ
ηo=1−(1−ηfin)AfinsAs,total
The definition of overall outside thermal resistance is given in Equation [eq:CoilRo441] as a function of fin efficiency and film coefficient. For a wet coil surface the resistance must be defined differently because the heat transfer equations are based on enthalpy rather than temperature differences, as shown in Equation [eq:CoilRow442].
Ro=1foηoAs,total
Ro,w=Cp,a/bbfo,wηo,wAs,total
Equation [eq:CoilRmf] gives the last two overall components of thermal resistance. They represent the metal tube wall and internal fouling. The fouling factor, due to deposits of dirt and corrosion of the tube inside surfaces, is assumed to be 5x10−5 m2K/W. All components of thermal resistance are added in series to produce the overall heat transfer coefficients shown in Equations [eq:CoilUAdry] and [eq:CoilUcAw].
Rmf=δtubektubeAi+FlAi
UAdry=AdryAs,total[1Ri+Rmf+Ro]
UcAw=AwAs,total[1/1bbbbRi+Rmf+Ro,w]
Solution Method of Model[LINK]
The complicated equations derived above were implemented in a successive substitution solution procedure to calculate the coil performance based on the input parameters. The MODSIM implementation of a cooling coil, the TYPE12 subroutine, was the motivation for this approach; the method used there has been retained with modifications for the uncontrolled coil model. Clark (1985) contains notes about the MODSIM routine.
In the general case, the cooling coil is only partially wet. For an uncontrolled coil, Equation [eq:CoilTw2Equation] is used to find the water temperature at the boundary. Several simple equations in the loop adjust the boundary point until the dry surface temperature at the boundary is equal to the dewpoint of the inlet air. For the controlled coil, Equations [eq:CoilTw2419] and [eq:CoilTw2420] give two calculations of the boundary temperature, and the water flow rate and boundary position are adjusted until the two equations agree.
Special cases occur when the coil is all wet or all dry. The coil is solved as if it were all wet before the general case is attempted. If the wet surface temperatures at the coil inlet and outlet are both below the dewpoint, no further solution is required. However, to ensure a continuous solution as flow variables are changed, when the surface is all dry or when it is wet with only the dry surface equations yielding a surface temperature below the dewpoint at the water outlet, the general solution is used to calculate the unknowns. In the solution of the controlled coil the outlet air enthalpy, given some resulting dehumidification, must correspond to the enthalpy at the specified outlet air temperature.
Application of Cooling Coil Model to Heating Coils[LINK]
The implementation of detailed heating coil models in IBLAST was another important aspect of the system/plant integration. The same kind of loops exist to provide hot water to the heating coils from the boilers as exist to supply the cooling coils with chilled water from the chillers. Some simplifications can be made, however, since the enthalpy change of the air flowing over a heating coil is entirely sensible. There is no condensation in a heating coil. In order to allow heating and cooling coils to be specified using the same geometric parameters, a heating coil simulation was developed from the cooling coil model described above by eliminating the wet surface analysis.
In addition, it was concluded that, since much simpler and less computationally expensive heating coil simulations are possible, an option was provided in IBLAST for a heating coil design using only the UA value of the coil, the product of heat transfer coefficient and coil area. This model was largely based on the TYPE10 subroutine implemented in MODSIM. The equations used to model the performance of the TYPE10 heating coil are as follows:
Ta,out=Ta,in+(Tw,in−Ta,in)ε(min(Cp,a˙ma,Cp,w˙mw)Cp,a˙ma)Tw,out=Tw,in−(Ta,out−Ta,in)(Cp,a˙maCp,w˙mw)
where the coil effectiveness is given by:
ε=1−exp⎛⎜ ⎜ ⎜ ⎜⎝{exp[−(min{Cp,a˙ma,Cp,w˙mw}max{Cp,a˙ma,Cp,w˙mw}){NTU}0.78]−1}(min{Cp,a˙ma,Cp,w˙mw}max{Cp,a˙ma,Cp,w˙mw}){NTU}−.22⎞⎟ ⎟ ⎟ ⎟⎠
The parameter NTU is the number of transfer units and is defined as a function of the UA value of the coil as follows:
NTU=UAmin(Cp,a˙ma,Cp,w˙mw)
HotWaterBased Air Heating Coil[LINK]
Overview[LINK]
The input object Coil:Heating:Water provides a model that uses an NTU–effectiveness model of a static heat exchanger. The model is an inlet – outlet model: given the inlet conditions and flow rates and the UA, the effectiveness is calculated using the formula for the effectiveness of a crossflow heat exchanger with both fluid streams unmixed. The effectiveness then allows the calculation of the outlet conditions from the inlet conditions.
The inputs to the model are: (1) the current inlet temperatures and flow rates of the air and water fluid streams and (2) the UA of the coil. Note that the UA is fixed in this model and is not a function of the flow rates.
There are 2 alternative user inputs for the component: the user may input the design water volumetric flow rate and the UA directly; or the user may choose to input the more familiar design heating capacity plus design inlet & outlet temperatures and let the program calculate the design UA. These alternative user inputs are fully described in the EnergyPlus Input Output Reference document.
Model Description[LINK]
The air and water capacitance flows are defined as:
˙Cair=cp,air⋅˙mair
˙Cwater=cp,water⋅˙mwater
The minimum and maximum capacity flows are then:
˙Cmin=min(˙Cair,˙Cwater)
˙Cmax=max(˙Cair,˙Cwater)
The capacitance flow ratio is defined as:
Z=˙Cmin/˙Cmax
The number of transfer units (NTU) is:
NTU=UA/˙Cmin
The effectiveness is:
ε=1−exp(e−NTU⋅Z⋅η−1Z⋅η)
where η=NTU−0.22.
The outlet conditions are then:
Tair,out=Tair,in+ε⋅˙Cmin⋅(Twater,in−Tair,in)/˙Cair
Twater,out=Twater,in−˙Cair⋅(Tair,out−Tair,in)/˙Cwater
The output of the coil in watts is:
˙Qcoil=˙Cwater⋅(Twater,in−Twater,out)
The UA value is recalculated for each timestep. A nominal UA, UA0, at the rating point is calculated by the program using the input for rated conditions and a search routine called root solver.
User input for the ratio of convective heat transfers at the nominal or rated operating point, “r,” is used in the model. This ratio is defined as:
r=ηf(hA)air(hA)water
where:
ηf is the fin efficiency, (dimensionless)
h is the surface convection heat transfer coefficient
A is the surface area.
The value calculated for UA0 is used with the input for r to characterize the convective heat transfer on the water sides at the nominal rating operation point using:
((hA)w)0=UA0(r+1r)
and on the air side at the nominal rating point using:
(ηf(hA)a)0=r(hA)w,0
Then, the following equations are used to calculate a new UA as a function of the flow rates and inlet temperatures at each timestep.
xa=1+4.769⋅10−3(Tair,in−Tair,in,0)
ηf(hA)a=xa(˙ma˙ma,0)0.8(ηf(hA)a)0
xw=1+(0.0141+0.014Twater,in,0)(Twater,in−