### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 1 of 10 

## Ap **pendix IM**  **AC 2**  **- F**  **: Calculations for the bench test**  **Data acquisition and reduction** All data were taken with a Hewlett - Packard data acquisition system HP75000 and data acquisition software. The data acquisition program was written using HPVEE. All data we re monitored via graphic windows and transferred to an Excel data sheet. Data stored in Excel were then transferred to Engineering Equation Solver (EES). The performance of the system was calculated in this EES program and converted again to an Excel data sheet for drawing graphs of the results as a form of COP, capacity, flow rate, torque, etc. The following is the calculation model in EES code used to calculate the system performance for the bench test. The code includes comments and explanations of the calculation being made. The variable names refer to Appendix C

. These templates were based on SAE ARCRP Pahse I and II with the improvements made during the ARCRP program. **C alculation model**  **-- EES template**  {================================================ ======================== This program is for SAE IMAC R134 asystem developed based on SAE ARCRP Phase I and Phase II for refrigerant R134a in Jan 05 ========================================================================= } { ----------------------------- -------------------------- Procedure AirFlowRate -----------------------------------------

----------------------------------------------------------------------------------------------------------------------------- ----- This procedure calculates air flow rates and velocities through the nozzles.

------------------------------------------------------------------------------------------------------------------ ------- -------- Calls: none Called by: main program

----------------------------------------------- --------------------------------------- ------- ------------------------------------ Inputs: CDguess nozzle discharge coefficient guess D nozzle throat diameter, [m] Tn nozzle temperature, [C] Pn nozzle entrance pressure, [kPa] DPn pressure drop across n ozzle, [Pa] Wn hum idity ratio at nozzle Outputs: Ma_wet wet air mass flow rate, [kg/s] Ma_dr y dry

air mass flow rate, [kg/s] Q_m3 volumetric flow rate, [m^3/s] Q_scfm volumetric flow rate, [scfm] Vel air velocity through nozzle, [m/s] Vn specific v olume of air at nozzle, [m^3/kg] Re Reynolds Number at nozzle CDnew discharge coefficient corresponding to Reynolds Number

-------------------------------------------------------------------------------------------------------------------------- ------ } P rocedure AirFlowRate (Nozzle$, CDguess, D, Tn, Pn, DPn, Wn : Ma_wet, Ma_dry, Q_m3, Q_scfm, Vel, Vn, Re, CDold)

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 2 of 10 $Common ENN IF (Nozzle$ = 'e1') AND (ENN < 1.5) THEN "e1 -- evap nozzle No.1, ENN=2 for high low load while ENN=1for low load" Ma_wet = 0 Ma_dr y = 0 Q_m3 = 0 Q_scfm = 0 Vel = 0 Vn = 0 Re = 0 CDold = 0 ELSE An = pi * D^2/4 " nozzle throat area, [m^2] " Vn = VOLUME(AirH2O,T=Tn,P=Pn,w= Wn )/(1+ Wn ) " air specific volume at exit of nozzle" rho = 1/Vn " air density at nozzle, [kg/m^3] " mu = VISCOSITY(AirH2O, T = Tn, P=Pn, w= Wn ) " air viscosity at nozzle, [kg/m - sec] " CDnew = CDguess repeat " iterate to find proper discharge coefficient " CDold=CDnew Q_m3 = CDold * An * (2 * DPn * Vn)^0.5 Vel = Q_m3/An Re = rho * Vel * D/mu CDnew = .9986 - 7.006/Re^.5 + 134.6/Re " discharge coefficient correlation " until (abs(CDold - CDnew) < .001) Q_scfm = Q_m3/(1.2 * Vn) * convert(m^3/s, ft^3/min) Ma_wet = Q_m3/Vn Ma_dr y = Ma_wet/(1+ Wn ) ENDIF END { -------------------------------------------- Procedure ChillerCapacity ---------------------------------------- This procedure calculates glycol chiller capacity using the EES BrineProp library.

------------------------------------------------------- ------------------------------------------------------------------- Calls: BrineProp Called by: OutdoorChamberBalance

-------------------------------------------------------------------------------------------------------------------------- Inputs: Mg gl yc ol m ass flow rate, [g/s] Conc glycol concentration, [mass %] Tgi glycol inlet temperature, [C] Tgo glycol outlet temperature, [C] Outputs: Q_glycol glycol chiller capacity, [kW ]

-------------------------------------------------------------------- ------------------------------------------------------ } Procedure ChillerCapacity (Mg, Conc, Tgi, Tgo : Q_glycol) Call BrineProp ('SpecHeat', 'EG', Conc, Tgi : Cpgi) Call BrineProp ('SpecHeat', 'EG', Conc, Tgo : Cpgo) Cpg_avg = (Cpgi + Cpgo)/2 Q_glycol = Mg/1000 * Cpg_avg * (Tgo - Tgi) End

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 3 of 10 { ------------------------------------------ Procedure SteamCapacity -----------------------------------------

--------------------------------------------------------------------------------------------------------- ----------------- This procedure calculates steam capacity.

-------------------------------------------------------------------------------------------------------------------------- Calls: none Called by: IndoorChamberBalance

----------------------------- --------------------------------------------------------------------------------------------- Inputs: Mg glycol mass flow rate, [g/s] Conc glycol concentration, [mass %] Tgi glycol inlet temperature, [C] Tgo glycol outlet temperature, [C] Output s: Q_glycol glycol chiller capacity, [kW ]

-------------------------------------------------------------------------------------------------------------------------- } Procedure SteamCapacity (Mw_kgps, Patm, Ts, Tw : Q_steam) hs = ENTHA LPY(Steam_NBS, T = T s, x = 1) " saturated steam inlet enthalpy, [kJ/kg] " hw = ENTHALP Y( Steam_NBS, T = Tw, P = Patm) " condensate exit enthalpy, [kJ/kg] " Q_steam = Mw_kgps * (hs - hw) End { ------------------------------------- Procedure ChamberLosses ------------------- --------------------------

-------------------------------------------------------------------------------------------------------------------------- This procedure calculates the transmission losses through the corresponding chamber walls.

--------------- ----------------------------------------------------------------------------------------------------------- Calls: none Called by: main program

---------------------------------------------------------------------------------------------------------------- ---------- Inputs: chamber num ber telling which chamber equation to use: 1 - >outdoor, 2 - >indoor Tic ceiling temperature inside chamber, [C] Toc ceiling temperature outside chamber, [C] Tiw wall temperature inside chamber, [C] Tow wall temperature o utside chamber, [C] Tif floor temperature inside chamber, [C] To f floor temperature outside chamber, [C] Outputs: Q_trans transmission losses to chamber walls, [kW ]

------------------------------------------------------------------------------------- ------------------------------------- } Procedure ChamberLosses (chamber, Tic, Toc, Tiw, Tow, Tif, Tof : Q_trans) " Outdoor Chamber " If (chamber = 1) Then Q_trans = (0.6571 * 7.576 * (Tif - Tof) + 0.2197 * 7.576 * (Tic - Toc)

+ 0.073 * (8.701 + 5.230) * (Tiw - Tow))/1000 EndIf " Indoor Chamber " If (chamber = 2) Then Q_trans = (0.6571 * 6.493 * (Tif - Tof) + 0.2197 * 6.493 * (Tic - Toc)

+ 0.073 * (8.701 + 4.483) * (Tiw - Tow))/1000 EndIf End { ------------------------------------------- Procedure OutdoorChamberBalance -------- - -------------------

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 4 of 10 ----------------------------------------------------------------------------------------------------------------------- --- This procedure calculates the heat exchanger heat transfer rate using chamber calorimetry for the outdoor chamber.

-------------------------------------------------------------------------------------------------------------------------- Calls: none Ca lled by: main program

-------------------------------------------------------------------------------------------------------------------------- Inputs: Mg glycol mass flow rate, [g/s] Conc glycol concentration, [mass %] Tgi glycol inlet temperature, [C] Tgo glycol outlet temperature, [C] Tic ceiling temperature inside chamber, [C] Toc ceiling temperature outside chamber, [C] Tiw wall temperature inside chamber, [C] Tow wall temperature outside chamber, [C] Tif floor temperature insid e chamber, [C] To f floor temperature outside chamber, [C] W chamber electrical power 1, [W] W2 chamber electrical power 2, [W] Outputs: Q_hx heat exchanger heat transfer, [kW ]

-------------------------------------------------------------------- ------------------------------------------------------ } Procedure OutdoorChamberBalance (Mg, Conc, Tgi, Tgo, Tic, Toc, Tiw, Tow, Tif, Tof, W, W 2 : Q_hx) chamber = 1 Call ChillerCapacity (Mg, Conc, Tgi, Tgo : Q_glycol) Call ChamberLosses (chamber, Tic, T oc, Tiw, Tow, Tif, Tof : Q_trans) Q_hx = Q_glycol + Q_trans - (W + W 2)/1000 End { ----------------------------------------------- Procedure IndoorChamberBalance --------------------------

------------------------------------------------------------------ -------------------------------------------------------- This procedure calculates the heat exchanger heat transfer rate for the indoor chamber.

--------------------------------------------------------------------------------------------------------------- ----------- Calls: none Called by: main program

-------------------------------------------------------------------------------------------------------------------------- Inputs: Mw_kgps condensate rate, [kg/s] P_atm atmospheric pressure, [kPa] Ts st eam inlet temperature, [C] Tw condensate exit temperature, [C] Tic ceiling temperature inside chamber, [C] Toc ceiling temperature outside chamber, [C] Tiw wall temperature inside chamber, [C] Tow wall temperature outside chamber, [C] Tif f loor temperature inside chamber, [C] To f floor temperature outside chamber, [C] W chamber electrical power, [W ] Outputs: Q_hx heat exchanger heat transfer, [kW ]

-------------------------------------------------------------------------------------- ------------------------------------ } Procedure IndoorChamberBalance (Mw_kgps, Patm, Ts, Tw, Tic, Toc, Tiw, Tow, Tif, Tof, W : Q_hx, Mw_kgps2)

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 5 of 10 $common Dslope2 chamber = 2 Call SteamCapacit y (Mw_kgps, Patm, Ts, Tw : Q_steam) Call ChamberLosses (chamber, Tic, Toc, Tiw, Tow, Tif, Tof : Q_trans) Mw_kgps2 = Ds lope2 * convert(lbm/s, kg/s) " condensation rate2, [kg/s] " Q_steam2= Mw_kgps2*(ENTHALPY(Steam_NBS, T = Ts, x = 1)

- ENTHALPY(Steam_NBS, T = Ts, x = 0)) Q_hx = Q_steam+Q_steam2 + W/ 1000 - Q_trans End { ----------------------------------------------- Procedure Efficiency ---------------------------------------------

------------------------ -------------------------------------------------------------------------------------------------- This procedure calculates the various compressor efficiencies.

---------------------------------------------------------------------------------------------- ---------------------------- Calls: none Called by: main program

-------------------------------------------------------------------------------------------------------------------------- Inputs: Mr refrigerant mass flow rate in compressor, [g/s] Tri refrigerant inlet temperature, [C] Pri refrigerant inlet pressure, [kPa] Tro refrigerant outlet temperature, [C] Pro refrigerant outlet pressure, [kPa] W_com p com pressor work, [kW ] Vc com pressor speed, [rpm] V_disp com pressor suctio n volume, [cc] Outputs: h_in inlet refrigerant enthalpy, [kJ/kg] h_out outlet refrigerant enthalpy, [kJ/kg] eta_c com pression efficiency eta_v volumetric efficiency

------------------------------------------------------------------------------ -------------------------------------------- } Procedure Efficiency (Mr, Tri, Pri, Tro, Pro, W _com p, Vc, V_suc : h_in, h_out, eta_isen, eta_mech, eta_comp, eta_v) h_in = ENTHALPY(R134a, T = Tri, P = Pri) s_in = ENTROPY (R134a, T = Tri, P = Pri) " inlet refrigerant entropy, [kJ/kg - K] " h_out_isen = ENT HALPY(R134a, P = Pro, s = s_in) " isentropic outlet refrigerant enthalpy, [kJ/kg] " h_out = ENTHALPY(R134a, T = Tro, P = Pro) " outlet refrigerant entropy, [kJ/kg - K] " eta_isen = (Mr/1000) * (h_out_isen - h_in)/W _comp " Isentropic efficiency " eta_mech= (Mr/1000) * (h_out - h_in)/W _com p " Mechanical efficiency " eta_comp= (h_out_isen - h_in)/(h_out - h_in) " Compression (or indicated) efficiency " v_in = VOLUME(R134a, T = Tri, P = Pri) " inlet refrigerant specific volume, [m^3/kg] " Vdot_c = Mr * v_ in " refrigerant displacement rate, [L/s] " eta_v = (Vdot_c/1000)/(V_suc/1e6 * Vc/60) " Volumetric Efficiency " End {******************************************************************************************************** ********** Main Program Section Begins Here *******************************************************************************************************************}

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 6 of 10 VersionDate = 031113 " Date of Revision " {These variables may need to be updated depend ing on the current system status } V_disp =160 "compressor suction volume, [cc] " Xoil=0.0 "assumed oil circulation rate" { ------------------------------------------ Outdoor Chamber Calculations ------- ------------------------------------------- } " Chamber Humidity " Wc i = Hum Rat(AirH2O, P =Patm, T=24, R=0.4) "estimated Rh=40%" Rhci =RELHUM(AirH2O, T=Tcai, P=Patm, w=W ci) " relative humidity at inlet " " Air Flow Rate Param eters " Pcn = Patm - DPcd/1000 - DPcn/1000 "air pressure at nozzle exit, [kPa] " CDc = 0.98 " discharge coefficient guess value " D_c1 =0.1778 { 0.17792 original value, 7" } " nozzle 1 diameter, [m] " D_c2 = 0.1778 {0.17792, 7" } " nozzle 2 diameter, [m] " Tcn = (Tcn1 + Tcn2)/2 " average nozzle temperature, [C] " " Air Flow Rate Through Nozzles " Call AirFlowRate('c1', CDc, D_c1, Tcn1, Pcn, DPcn, W ci : ma_wet_c1, ma_dry_c1, AFR_m3_c1 , AFR_scfm_c1, Vel_c1, Vn_c1, Re_c1, CDc1) Call AirFlowRate('c2', CDc, D_c2, Tcn2, Pcn, DPcn, W ci : ma_wet_c2, ma_dry_c2, AFR_m3_c2, AFR_scfm_c2, Vel_c2, Vn_c2, Re_c2, CDc2) " Total Air Flow Rates " Ma_outdoor_dr y = m a_dry_c1 + ma_dry_c2 " dry air mass flow rate, [kg(dry air)/s] " Ma_outdoor = ma_wet_c1 + ma_wet_c2 " air mass flow rate, [kg/s] " AFR_m3_ou tdoor = AFR_m3_c1 + AFR_m3_c2 " volum etric air flow rate, [m^3/s] " AFR_scfm_outdo or = AFR_scfm_c1 + AFR_scfm_c2 " volumetric air flow rate, [scfm] " " Air- Side Energy Balance " hcai = ENTHALPY(AirH2O, T = Tcai, P = Patm, W = W ci) " m oist inlet air enthalpy, [kJ/kg] " hcan = ENT HALPY(AirH2O, T = Tcn, P = Pcn, W = W ci) " m oist nozzle air enthalpy, [kJ/kg] " Qoutdoor_air = Ma_outdoor_dry* (hcan - hcai) " Refrigerant - Side Energy Balance " Pcri = Pcro + DPcr " inlet pressure (absolute), kPa " hcri = ENTHAL PY(R134a, T = Tcri, P = Pcri) " refrigerant inlet enthalpy, [kJ/kg] , single phase - gas" hcro = ENTHALPY(R1 34a, T = Tcro, P = P cro) “ refrigerant exit enthalpy, [kJ/kg], single phase - subcooled liquid " Qoutdoor_ref = Mr*(1 - Xoil) * (hcri - hcro)/1000

+ Mr*Xoil/1000*(2.0499*(Tcri - Tcro)+2.261e - 3/2*(Tcri^2 - Tcro^2)) Tcro_sat = TEMPERATURE(R13 4a, P = Pcro, x = 0.5) DTsubcool=Tcro_sat - Tcro " Chamber Energy Balance " Call BRINEPROP ('Density', 'EG', Conc, Tgi : Deng*1000) Call OutdoorChamberBalance (Mg, Conc, Tgi, Tgo, Tcic, Tcoc, Tciw, Tcow, Tcif, Tcof, Wc , W c2 : Qoutdoor_chamber) " Average Energy Balance based on Air- side and chamber balances" Qoutdoor_avg=0.5*(Qoutdoor_air+Qoutdoor_chamber) " Error Calculations "

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 7 of 10 ErrOutdoor_air = (Qoutdoor_air - Qoutdoor_chamber)/Qoutdoor_chamber * 100 E rrOutdoor_ref = (Qoutdoor_ref - Qoutdoor_chamber)/Qoutdoor_chamber * 100 { -------------------------------------- Indoor Chamber Calculations -------------------------------------------------------- } " For R134a/R152, the first row of thermocouple grid is out of main stream. " Teao2 = (Teao21+Teao22+Teao23+Teao24)/4 Teao3 = (Teao31+Teao32+Teao33+Teao34)/4 Teao4 = (Teao41+Teao42+Teao43+Teao44)/4 Teao_avg = (Teao2+Teao3+Teao4)/3 " Chamber Humidity " Rhei = RELHUM(AirH2O, T = Teai, P = Patm, D = Tdpei) " inle t relative humidity " Rhen = RELHUM(AirH2O, T = Ten, P = Pen, D = Tdpen) " relative humidity after nozzle " We i = HUMRAT(AirH2O, T = Teai, P = Patm, D = Tdpei) " inlet humidity ratio " We n = HUMRAT(AirH2O, T = Ten, P = Pen, D = Tdpen) " hum idit y ratio a fter nozzle " " Air Flow Rate Parameters " Pen = Patm - DPea/1000 - DPen/1000 " air pressure at nozzle entrance, [kPa] " CDe = 0.975 " discharge coefficient guess value " D_e1 = 0.06342 {0.0635, 2.5", measured value} " nozzle 1 (North Side, air flow direction) diameter, [m] " D_e2 = 0.06348 {0.0635, 2.5", measured value} " nozzle 2 (South Side, airflow direction) diameter, [m] " Ten = If(ENN, 2, Ten2, (Ten1 + Ten2)/2,0) " average nozzle temperature, [C] " " Ai r Flow Rates Through Nozzles " Call AirFlowRate('e1', CDe, D_e1, Ten1, Pen, DPen, W en : m a_wet_e1, ma_dry_e1, AFR_m3_e1, AFR_scfm_e1, Vel_e1, Vn_e1, Re_e1, CDe1) Call AirFlowRate('e2', CDe, D_e2, Ten2, Pen, DPen, W en : m a_wet_e2, ma_dry_e2, AFR_m3_e2, AFR_scfm_e2, Vel_e2, Vn_e2, Re_e2, CDe2) " Total Air Flow Rates " Ma_indoo r_dr y = m a_dry_e1 + ma_dry_e2 " total dry air mass flow rate, [kg/s] " Ma_indoor_wet = ma_wet_e1 + ma_wet_e2 " total wet air mass flow rate, [kg/s] " AFR_m3_indoor = AFR_m3_e1 + AFR_m 3_e2 " total volumetric air flow rate, [m^3/s] " AFR_scfm_indoor = AFR_scfm _e1 + AFR_scfm_e2 " total volumetric air flow rate, [scfm] " " Total Air- Side Heat Transfer " heai = ENTHALPY(AirH2O, T = Teai, P = Patm, W = W ei) " moist inlet air enthalpy, [ kJ/kg] " hean = ENTHALPY(AirH2O, T = T en, P = Pen, W = W en) " m oist nozzle air enthalpy, [kJ/kg] " Qindoor_air = Ma_indoor_dry * (heai - hean)+Qleak_duct - Ma_indoor_dr y*(W ei We n)*ENTHALPY(Steam_NBS,T=Ten,x=0) " heat leak through the duct is added to t he air side energy balance" Qleak_duct=4.8*(Teai - (Ten+Teao_avg)/2)/1000 " heat leak through the duct. 4.8 is the measured UA value" " Sensible Air- Side Heat Transfer " heai_encondition = ENTHALPY(AirH2O, T = Teai, P = Patm, W = W en) Qindoor_sensible_ps yc h = Ma_indoor_dr y * (heai_encondition - hean) Qindoor_latent_ps yc h = Qindoor_air - Qindoor_sensible_psych - Qleak_duct " Latent Air- Side Heat Transfer " Mw_kgps_calcu=(W ei -We n)*Ma_indoor_dry Mw_kgps = D slope * convert(lbm/s, kg/s) " condensation rate, [kg/s] " Mw_gps = Mw_kgps * 1000 " condensation rate, [g/s] "

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 8 of 10 Pv_ei=PRESSURE(Steam_NBS,T=Tdpei,x=1) Pv_en=PRESSURE(Steam_NBS,T=Tdpen,x=1) hvapour_in=ENTHALPY(Steam_NBS, T =Teai, P=Pv_ei) hvapour_out = ENTHALPY(Steam_NBS, T = Ten, x=0 ) h_fg= hvapour_in - hvapour_out Qindoor_latent_cond = Mw_kgps * h_fg Qindoor_sensible_cond = Qindoor_air - Qindoor_latent_cond - Qleak_duct " Refrigerant - Side Energy Balance " {Pero, DPer, Tero are measured variables} Peri = Pero + DPer " inlet pres sure (absolute), kPa " Teri_sat=TEMPERATURE(R134a, P = Peri, x = 0.5) "2 phase inlet" Tero_sat= TEMPERAT URE(R134a, P = Pero, x = 0.5) " 2 - phase saturation temperature on Pero, [C] " DTsuperheat=Tero - Tero_sat hxri = ENTHALPY(R 134a, T = Txri, P = Pxri) " refrigerant inlet enthalpy, [kJ/kg], single phase - subcooled liquid " heri = hxri hero=ENTHALPY(R134a, T = Tero, P = Pero) Qindoor_ref = Mr*(1 - Xoil) * (hero - heri)/1000

+ Mr*Xoil/1000*(2.0499*( Tero - Teri_sat)+2.261e - 3/2*(Tero^2 - Teri_sat^2)) " Refrigerator Qualities " h_liq_in = ENTHALPY(R134a, P = Peri, x = 0) " saturated liquid enthalpy, [kJ/kg] " h_vap_in = ENTHALPY(R134a, P = Peri, x = 1) " saturated vapor enthalpy, [kJ/kg] " x_in = (heri - h_liq_in)/(h_vap_in - h_liq_in) " inlet quality " h_liq_out = ENTHALPY(R134a, P = Pero, x = 0) " saturated liquid enthalpy, [kJ/kg] " h_vap_out = ENTHALPY(R134a, P = Pero, x = 1) " saturated vapor enthalpy, [kJ/kg] " x_out = (hero - h_liq_out)/(h_vap_out - h_liq_out) " exit quality " " Chamber Energy Balance " Call IndoorChamberBalance (Mw_kgps, Patm, Ts, Tw, Teic, Teoc, Teiw, Teow, Teif, Teof, W e : Qindoor_chamber,Mw_kgps2) " Average Energy Balance based on Air- side and chamber balances" Qindoor_avg=0.5*(Qindoor_air+Qindoor_chamber) " Error Calculations " ErrIndoor_air = (Qindoor_air - Qindoor_chamber)/Qindoor_chamber * 100 ErrInd oor_ref = (Qindoor_ref - Qindoor_chamber)/Qindoor_chamber * 100 { ---------------------------------------------- Com pressor Calculations --------------------------------------------------- } Prcpo = Pxri + DPhr P_ratio = Prcpo/Prcpi " compression ratio " " Efficiency Calculations " Call Efficiency(Mr*(1 - Xoil), Trcpi, Prcpi, Trcpo, Prcpo, W_com p, Vc,

V_disp : h_compin, h_compout, eta_isen, eta_mech, eta_comp, eta_v) " Com pressor Shaft Wo rk" W_com p = (Fc * convert(lbf- in, N - m)) * (Vc * convert(rev/min, rad/s))/1000

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 9 of 10 DT_sup_cp_in=Trcpi - TEMPERATURE(R134a,P=Prcp i,x=0.5) "compressor inlet superheat" DT_sup_cp_out=Trcpo - TE MPERATURE(R134a ,P=Prcpo,x=0.5) "compressor inlet superheat" { ------------------------------- -------------------------- System Performance ------------------------------------ } DPsl=Pero - Prcpi COP_indoor_air = Qindoor_air/W _com p COP_indoor_ref = Qindoor_ref/ W_com p COP_indoor_chamber = Qindoor_chamber/ W_com p COP_indoor_avg=Qindoor_avg/W _com p { --- -------------------- ------------- Measured parameters from Excel data file ------------------------------------- } " Excel Data " Pcro= xxxx DPcr= xxxx DPca= xxxx DPcn= xxxx Wc = xxxx Wc 2= xxxx Mr= xxxx Denr= xxxx Mg= xxxx Deng= xxxx Vc= xxxx Fc= xxxx Tdpe i= xxxx Tdpen= xxxx DPcd= xxxx DPer= xxxx DPea= xxxx DPen= xxxx We = xxxx Patm = xxxx G= xxxx G2= xxxx Pero= xxxx count= xxxx Dslope= xxxx Dslope2= xxxx EXV= xxxx Pxri= xxxx DPhr= xxxx Prcpi= xxxx DPlr= xxxx Tcic= xxxx Tciw= xxxx Tci f= xxxx Tcoc= xxxx Tc ow= xxxx Tco f= xxxx Tcri= xxxx Tcro= xxxx Tcai= xxxx Tcao= xxxx

### IMAC Team 2 - Improved Efficiency Final Report December 2006

Appendix F: Calculation for Bench Test Page 10 of 10 Tcn1= xxxx Tcn2= xxxx Tgi= xxxx Tgo= xxxx Trcpi= xxxx Trcpo= xxxx Teic= xxxx Teiw= xxxx Teif= xxxx Teoc= xxxx Teow= xxxx Teof= xxxx Tcph= xxxx Tero= xxxx Teai= xxxx Ten1= xxxx Ten2= xxxx T s= xxxx Tw = xxxx Txri= xxxx Teri= xxxx Tcro_2= xxxx Teao21= xxxx Teao22= xxxx Teao23= xxxx Teao24= xxxx Teao31= xxxx Teao32= xxxx Teao33= xxxx Teao34= xxxx Teao41= xxxx Teao42= xxxx Teao43= xxxx Teao44= xxxx ENN= xxxx outdoor= xxxx indoor= xxxx a1File$=' xxxxxxxxxxx ' a2Time$=' xxxxxxxxxx '