Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Low-GWP Alternative Refrigerants Evaluation Program (Low-GWP AREP) TEST REPORT #6 System Drop-in Tests of R-22 Alternative Fluids (ARM-32a, DR-7, L-20, LTR4X, LTR6A, and D52Y) in a 5-RT Air-Cooled Water Chiller (Cooling Mode) Ken Schultz Steve Kujak Trane / Ingersoll Rand 3600 Pammel Creek Rd La Crosse, WI 54601 January 25, 2013 This report has been made available to the public as part of the author company s participation in the AHRI s Low-GWP AREP.
List of Tested Refrigerants Compositions (Mass%) ARM-32a R-32/R-125//R-134a/R-1234yf (25/30/25/20) DR-7 R-32/R-1234yf (36/64) L-20 R-32/R-152a/R-1234ze(E) (45/20/35) LTR4X R-32/R-125/R-134a/R-1234ze(E) (28/25/16/31) LTR6A R-32/R-744/R-1234ze(E) (30/7/63) D52Y R-32/R-125/R-1234yf (15/25/60)
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 2 of 13 INTRODUCTION This report documents tests run on a small air cooled water chiller / heat pump in Trane s La Crosse, Wisconsin, Laboratory. Tests were run only in cooling mode; the facility we ended up using did/could not control ambient humidity. The refrigerants tested are listed below: name order begin testing end testing number of runs DR 7 1 01 Aug 2012 08 Aug 2012 21 ARM 32a 2 20 Aug 2012 22 Aug 2012 16 L 20 3 27 Aug 2012 30 Aug 2012 18 LTR4X 4 04 Sep 2012 11 Sep 2012 18 LTR6A 5 11 Sep 2012 19 Sep 2012 16 R22 6 26 Sep 2012 27 Sep 2012 13 D52Y 7 28 Sep 2012 03 Oct 2012 21 This same equipment and facility were used for the tests reported earlier on R410A alternate refrigerants. 1 The only changes involved replacing the compressor and TXV with components sized for R22. TEST SETUP The equipment being tested is a Koolman air cooled water chiller / heat pump, model CGAR 0605. It has a nominal design cooling capacity of 4.4 RT (15.6 kw). The product is designed to provide chilled or hot water to apartments, offices, or small retail stores. In cooling mode, the evaporator is a brazed plate heat exchanger (BPHE); the condenser is a copper tube/aluminum fin coil (RTPF coil). The production design employs R22 or R407C as the refrigerant (depending on country of use). 2 Following completion of testing with alternate refrigerants proposed as replacements for R410A, the compressor and TXV were replaced with standard production R22 components and testing continued with alternate refrigerants projected to be closer to R22. The unit came to us containing a POE 160SZ oil. This oil will be used when testing all refrigerants. The mineral oil contained in the replacement R22 compressor was drained prior to installation and replaced with a POE 160SZ oil. See Figure 1 for photos of the Koolman unit set up in the laboratory. A schematic diagram of the system with locations of instrumentation is shown in Figure 2. Key measurements include chilled water flow rate along with inlet and outlet temperatures (RTD s) and pressures, mixed air temperature, and power input to the compressor and total power to the unit. Pressure sensors are mounted along the refrigerant circuit; thermocouples are surface mounted at corresponding locations. A list of instrumentation along with sensor accuracies is attached as Appendix A. METHOD OF TEST The method of test is consistent with Appendix C of AHRI Standard 550/590 2011 with operating conditions generally held within tighter tolerances. Performance is reported here as measured; no adjustments are made for fouling allowance or elevation. The cooling capacities reported are computed from the measured chilled 1 TEST REPORT #SD001, SYSTEM DROP IN TEST OF R410A ALTERNATIVE FLUIDS (ARM 32, ARM 70, DR 5, HPR1D, L 41a, L 41b, and R32) IN A 5 RT AIR COOLED WATER CHILLER (COOLING MODE), 20 Aug 2012, AHRI Low GWP Alternative Refrigerants Evaluation Program. 2 Catalogs were not readily available for making a direct comparison of performance with R407C and R22. TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 3 of 13 water flow rate and the difference between the entering and leaving chilled water enthalpies. The enthalpies are computed from the measured water temperatures and pressures. Therefore, the capacity reported here corresponds to the gross refrigerating capacity defined in AHRI Standard 550/590 2011. Thermodynamic properties of water are computed using Trane s internal code, which is consistent with the 550/590 equations to well within experimental accuracy. Tests in cooling mode consist of: 1. Refrigerant charge sweep at nominal operating (boundary) conditions of: leaving chilled water temperature = 45 ±0.1 chilled water flow rate = 14.0 gpm ±0.1 gpm ambient air temperature = 95 ±0.15 compressor suction superheat ~ 10 12 (TXV adjusted as needed) The charge for further testing was selected at maximum EER (0.5 lbm resolution). 2. Variation in leaving chilled water temperature while holding air temperature fixed at 95: 41 TChWo 47 3. Variation in ambient air temperature while holding leaving water temperature fixed at 45: 75 Tair 115 (unless limited by high pressure cutout switch set at 415 psia) This test matrix produces several measurements at the nominal operating condition to check repeatability. The Koolman product is designed for international markets and is rated at the following conditions in cooling mode: ambient air temperature = 35 C = 95 leaving chilled water temperature = 7 C = 44.6 entering chilled water temperature = 12 C = 53.6 chilled water temperature change = 5 C = 9 These conditions are slightly different than those listed in AHRI Standard 550/590 2011. To expedite execution of the test matrix, several simplifications to the operating conditions were made. First, the rating point leaving water temperature (7 C) was rounded up to an integer value (45). Second, the chilled water flow rate was set at a fixed value of 14 gpm which produced a 7.1 change in chilled water temperature for the baseline R22 runs (same flow rate as used for the R410A tests). Adjusting chilled water flow rate for a fixed temperature change is an iterative process and can become time consuming in the laboratory. Although a fixed flow rate, variable entering water temperature can affect the potential refrigerant superheat leaving the evaporator 3, a fixed water flow rate does maintain a nearly constant water side heat transfer coefficient in the heat exchanger. These simplifications were considered to be minor compromises to maintaining conditions per a formal rating standard and are expected to have negligible impact on the ultimate comparisons of the alternate refrigerants to the baseline. RESULTS Overall performance results (capacity and EER), along with the key state points obtained at the nominal operating condition using the charge that maximizes EER are attached as Appendix B for each refrigerant tested. This information is also compiled in a companion Excel file. A summary of the capacities, EER s, and refrigerant charges relative to performance with the baseline R22 are shown in Figure 3, Figure 4, and Figure 5, respectively. The refrigerants are listed in the order that they were run. Also shown are values for the capacity and EER (COP) predicted by a simple thermodynamic cycle model. The simple model ignores line pressure drops and so assumes the evaporator pressure equals the compressor 3 The refrigerant superheat leaving the evaporator is relatively small here roughly only half of the compressor suction superheat maintained by the TXV. The second portion of the compressor suction superheat is added by heat transfer in the four way mode switching valve TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 4 of 13 suction pressure and the condenser pressure equals the compressor discharge pressure. The model inputs (compressor suction pressure evaporator saturation temperature, compressor suction superheat, compressor discharge pressure condenser saturation temperature, condenser subcooling, and compressor adiabatic efficiency) were set to match those for the R22 baseline experimental data. The switching valve for cooling or heating model is assumed to behave as a heat exchanger with a temperature effectiveness of 5% (from the R410A test data). Measured capacities ranged from 10% higher (DR 7) to 5.5% lower (D52Y) than with R22. The capacities with DR 7 and D52Y were about 5.5% higher than predicted by the simple model; ARM 32a was up about 2%. The capacity with LTR6A was ~10% lower than predicted; as discussed further below, LTR6A has a very large glide of 25+d. All of the alternate refrigerants had measured EER s significantly lower than with R22, ranging from 5% for L 20 to 20% for LTR6A. Measured EER s ranged from 2 5% lower than predicted, except the measured EER for LTR6A was nearly 18% lower than predicted. Refrigerant charges ranged from a nearly 10% reduction with L 20 to a 14% increase for LTR6A, with most of the others requiring a small 5% increase in charge. Figure 6 shows the superheats measured at the evaporator outlet and at the compressor suction (the difference is caused by heat transfer in the four way mode switching valve). Most tests were held within the 10 12d target band, although the LTR4X and LTR6A superheats proved a bit difficult to adjust and maintain. The condenser exit subcooling obtained at the nominal operating condition with optimum charge is shown in Figure 7. Subcooling generally ranged between 9 14d. The R22 alternate subcoolings are slightly smaller than for the R410A alternates. Determining the approach temperatures between the water and refrigerant in the evaporator (BPHE) is somewhat problematic. The water and refrigerant are in counter flow. On the refrigerant side, restrictions internal to the heat exchanger create a large pressure drop between the evaporator inlet pressure measurement point and the heat exchanger channels (to promote uniform flow rates through the channels). Therefore, the true pressure of the refrigerant entering the heat exchanger channels is unknown. It is estimated here by assuming that 85% of the total pressure drop across the BPHE occurs across the entrance restrictions (same assumption used for R410A data analysis). The resulting evaporator approach temperatures are shown in Figure 8. The Twtr,lvg Tsat,ent approach temperatures measured during the R22 alternate testing are 5 8d higher than in the R410A testing. 4 The approach temperatures between the entering water and leaving refrigerant are shown by the second and third columns in Figure 8. The difference between these two columns is the evaporator exit superheat. These two approach temperatures are similar between the R22 and R410A testing. Figure 9 compares the water and refrigerant temperature glides for each of the refrigerants tested. As with the HPR1D in the R410A testing, the excessively large glide associated with LTR6A is likely having a negative impact on performance. The refrigerant glides associated with the R22 alternates are somewhat larger than for the R410A alternates. Figure 10 provides measures of condenser performance. The entering refrigerant dew point temperatures (an indication of the excess pressure needed to achieve the condenser heat rejection) of all the alternate refrigerants are slightly higher than the baseline R22 case. The significantly higher entering dew point for LTR6A is again likely attributable to its large glide and might contribute to the degraded performance relative to the simple model prediction. 4 The fractional pressure drop across the BPHE entering orifice has to be dropped to ~50% to make the Twtr,lvg Tsat,ent s for the R22 tests match the R410A tests at 85%. However, this would result in a large negative glide for R22 because of the relatively large pressure drop across the refrigerant channels. TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 5 of 13 The pressure drops along the evaporator to compressor suction and compressor discharge to condenser lines are shown in Figure 11. The line pressure drops range from slightly higher to somewhat lower for the alternate refrigerants compared with the R22 baseline. The pressure drops correlate with the refrigerant mass flow rates shown in Figure 12 (computed from the measured evaporator water side heat transfer rate, the refrigerant enthalpy leaving the evaporator as determined from the measured temperature and pressure, and the refrigerant enthalpy entering the evaporator as determined from the measured temperature and pressure at the condenser outlet assuming adiabatic flow through the expansion device). Figure 13 shows the compressor adiabatic efficiencies computed from the suction and discharge measurements and the fluid properties as provided by the refrigerant suppliers. Some of variation can be attributed to uncertainties in fluid properties, in particular, the ideal gas specific heat (likely estimated, not measured for most blends). Some of the variation can be attributed to the pressure ratios seen by the compressor; see Figure 14. For example, the low compressor efficiency seen for LTR6A might be a consequence of significantly higher pressure ratio experienced. Figure 15 shows the compressor discharge temperatures reached for each refrigerant. The experimental results match the predictions reasonably well the measured discharge temperatures range from 0 (R22) to 8d (DR 7) higher than modeled, with LTR4X ( 12d) and LTR6A ( 16d) being exceptions. Finally, Figure 16 shows the ratio of refrigerant volume flow rate to the swept volume of the compressor stated by the manufacturer. The refrigerant volume flow rate is computed from the mass flow rate as computed above (Figure 12) and the refrigerant specific volume as determined from the measured temperature and pressure entering the compressor. The ratios vary from 2% (LTR6A) to 3% (DR 7) relative to R22. The variation could come from the range of compression ratios experienced, along with any errors/uncertainties there might be in the gas region PVT equations of state. REMARKS In general, the test results were similar between the R410A like and R22 like refrigerants. The short fall in EER of the R22 refrigerants is greater than for the R410A refrigerants. The discrepancies between the measured results and the simple model predictions were a little larger for the R22 alternates than the R410A alternates. It appears that the majority of the candidates considered here could successfully be used in high pressure HVAC&R equipment with varying levels of design modifications. It also appears that large refrigerant glide can negatively impact performance, at least for the equipment and operating conditions tested here. TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 6 of 13 NOMENCLATURE BPHE Brazed Plate Heat Exchanger CAP Capacity [RT or Btu/hr or W] Chrg refrigerant charge [lbm or kg] CiDP Condenser inlet Dew Point (dew point temperature of refrigerant entering condenser) CoBP Condenser outlet Bubble Point (bubble point temperature of refrigerant leaving condenser) COP Coefficient of Performance [ ] dpent ratio of the refrigerant pressure drop across the distributor entering the evaporator channels to the total pressure drop across the evaporator EER Energy Efficiency Ratio = cooling capacity measured from water side of evaporator divided by electrical power input [Btu/W hr] EERc EER based on power input to compressor only EERt EER based on total power input (compressor, fans, and controls) RT Refrigeration Tons RTPF Tair TCo Tdew,lvg Tref,lvg Tsat,ent Twi Two Twtr,ent Twtr,lvg Round Tube Plate Fin heat exchanger (condenser coil ) temperature of the ambient air entering the condenser subcooled refrigerant temperature leaving condenser saturation temperature (dew point) at the refrigerant pressure leaving the evaporator temperature of the superheat refrigerant vapor leaving the evaporator saturation temperature of the refrigerant entering the evaporator channels (after the inlet distributor ) temperature of the chilled water entering the evaporator temperature of the chilled water leaving the evaporator temperature of the chilled water entering the evaporator temperature of the chilled water leaving the evaporator TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Low GWP AREP High Pressure Test Summary Final Report (Cooling Mode) created: 19 November 2012 last edited: 19 November 2012 page 8 of 13 cooling: evaporator inlet (check Tsat) heating: condenser outlet (subcooling) T cooling: evaporator inlet P heating: condenser outlet cooling: evaporator outlet P T cooling: evaporator outlet (superheat) heating: condenser inlet heating: condenser inlet (superheat) T P Koolman Chiller/Heat Pump Test of Alternate Refrigerants LO 42807 Instrumentation Refrigerant Circuit (v1) HP LP HP LP 1 EVAP TFi filter or P F city water TFo expansion tank T 13 2 LP 12 HP 11 "T" "Tsat(P)" Flow T P accum Flow 10 control panel variable control discharge superheat control box Tdischarge 6 COOLING MODE liquid injection for discharge superheat control Twell (empty) P T P T cooling: condenser outlet (subcooling) heating: evaporator inlet (check Tsat) cooling: condenser inlet (superheat) heating: evaporator outlet (superheat) 8 9 COND TC's Measure T's at outlet of each circuit to check for maldistribution? (cmpr discharge) T 5 4 3 T air (cmpr discharge) P Schrader valves Phi cut-out switch CMPR Plo cut-out switch T (cmpr suction) 7 P (compressor power) W (cmpr suction) (unit power) W Figure 2. Schematic diagram of Koolman system showing locations of measurement points. printed 6 Jul, 2012 Drawing1 Page-1 TraneHP_Report#3_121119.docx Ken Schultz Thermal Systems Group
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix A: Instrumentation List ID # ** Description Units Stated Sensor Accuracy Measurement Accuracy 1 BPHX Water Flow GPM SI: m³/h ± 0.5% of Rdg ± 0.5% of Rdg 2 BPHX Waterside Delta P psid SI: kpa diff 0.2% of Span ± 0.054 PSID 3 Ent BPHX Water Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 4 Lvg BPHX Water Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 5 Entering BPHX Water Temp SI: C ± 0.1 F 6 Leaving BPHX Water Temp SI: C ± 0.1 F 7 Outdoor Air DB Temp SI: C ± 0.1 F 8 Outdoor Air WB Temp SI: C ± 0.5 F 9 Barometric Pressure psia SI: kpa abs 0.1% of FS ± 0.0157 PSIA 10 Compressor Discharge Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 11 RTPF Vapor Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 12 RTPF Liquid Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 13 Entering TXV Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 14 BPHX Liquid Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 15 BPHX Vapor Refr Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 16 Compressor Suction Pressure psia SI: kpa abs 0.05% of FS ± 0.375 PSIA 20 Compressor Discharge Refr Temp SI: C ± 1.0 F 21 RTPF Vapor Refr Temp SI: C ± 1.0 F 22 RTPF Liquid Refr Temp SI: C ± 1.0 F 23 Entering TXV Refr Temp SI: C ± 1.0 F 24 BPHX Liquid Refr Temp SI: C ± 1.0 F 25 BPHX Vapor Refr Temp SI: C ± 1.0 F 26 Compressor Suction Temp SI: C ± 1.0 F 30 Ent RTPF Circuit Temp #1 (cooling) SI: C ± 1.0 F 31 Ent RTPF Circuit Temp #2 (cooling) SI: C ± 1.0 F 32 Ent RTPF Circuit Temp #3 (cooling) SI: C ± 1.0 F 33 Ent RTPF Circuit Temp #4 (cooling) SI: C ± 1.0 F 34 Ent RTPF Circuit Temp #5 (cooling) SI: C ± 1.0 F 35 Ent RTPF Circuit Temp #6 (cooling) SI: C ± 1.0 F 36 Ent RTPF Circuit Temp #7 (cooling) SI: C ± 1.0 F 37 Ent RTPF Circuit Temp #8 (cooling) SI: C ± 1.0 F 40 Lvg RTPF Circuit Temp #1 (cooling) SI: C ± 1.0 F 41 Lvg RTPF Circuit Temp #2 (cooling) SI: C ± 1.0 F 42 Lvg RTPF Circuit Temp #3 (cooling) SI: C ± 1.0 F 43 Lvg RTPF Circuit Temp #4 (cooling) SI: C ± 1.0 F 44 Lvg RTPF Circuit Temp #5 (cooling) SI: C ± 1.0 F 45 Lvg RTPF Circuit Temp #6 (cooling) SI: C ± 1.0 F 46 Lvg RTPF Circuit Temp #7 (cooling) SI: C ± 1.0 F 47 Lvg RTPF Circuit Temp #8 (cooling) SI: C ± 1.0 F 50 Liquid Refrigerant Flow GPM SI: m³/h ± 0.5% of Rdg ± 0.5% of Rdg 51 Compressor Liquid Injection Flow GPM SI: m³/h ± 0.5% of Rdg ± 0.5% of Rdg 60 Compressor Voltage AB V SI: V 0.2% of Rdg + ± 0.1% of Range 61 Compressor Voltage BC V SI: V 0.2% of Rdg + ± 0.1% of Range 62 Compressor Voltage AC V SI: V 0.2% of Rdg + ± 0.1% of Range 63 Compressor Current A A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 64 Compressor Current B A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 65 Compressor Current C A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 66 Compressor Power W SI: W 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 70 Total Unit Voltage AN V SI: V 0.2% of Rdg + ± 0.1% of Range 71 Total Unit Voltage BN V SI: V 0.2% of Rdg + ± 0.1% of Range 72 Total Unit Voltage AN V SI: V 0.2% of Rdg + ± 0.1% of Range 73 Total Unit Current A A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 74 Total Unit Current B A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 75 Total Unit Current C A SI: A 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 76 Total Unit Power W SI: W 0.2% of Rdg + ± 0.1% of Rang ~0.5% of Rdg w/ CTs 90 Ent RTPF Air Temp #1 SI: C ± 1.0 F 91 Ent RTPF Air Temp #2 SI: C ± 1.0 F 92 Ent RTPF Air Temp #3 SI: C ± 1.0 F 93 Ent RTPF Air Temp #4 SI: C ± 1.0 F 94 Ent RTPF Air Temp #5 SI: C ± 1.0 F 95 Ent RTPF Air Temp #6 SI: C ± 1.0 F 96 Ent RTPF Air Temp #7 SI: C ± 1.0 F 97 Ent RTPF Air Temp #8 SI: C ± 1.0 F 98 Ent RTPF Air Temp #9 SI: C ± 1.0 F 99 Ent RTPF Air Temp #10 SI: C ± 1.0 F 100 Ent RTPF Air Temp #11 SI: C ± 1.0 F 101 Ent RTPF Air Temp #12 SI: C ± 1.0 F 102 Ent RTPF Air Temp #13 SI: C ± 1.0 F 103 Ent RTPF Air Temp #14 SI: C ± 1.0 F 104 Ent RTPF Air Temp #15 SI: C ± 1.0 F
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 12 Oct 2012 Alternative Refrigerant DR 7 DuPont Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 4.99 kg 10.5 11.0 lbm 1.048 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 16,203 W 50,329 55,287 Btu/hr 1.099 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 6,961 W 5,700 6,961 W 1.221 Power to Compressor 5,369 6,623 W 5,369 6,623 W 1.233 COP or EER (total) 2.59 2.33 [] 8.83 7.94 Btu/W hr 0.900 COP or EER (compressor only) 2.75 2.45 [] 9.37 8.35 Btu/W hr 0.891 Refrigerant Mass Flow Rate 345 402 kg/hr 761 887 lbm/hr 1.165 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF DR 7
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 12 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: DR 7 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 53.1 L/hr 14.0 14.0 gpm 0.999 T entering 11.2 11.5 C 52.2 52.8 0.6 T leaving 7.2 7.2 C 45.0 44.9 0.1 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.0 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 8.5 587 42.8 71.4 47.3 85.2 discharge 92.9 1982 87.4 2501 199.2 287.4 189.3 362.8 suction SH 6.3 6.3 11.4 11.3 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 82.3 2,487 185.7 285.0 180.2 360.7 outlet 43.8 1,941 42.0 2,458 110.8 281.5 107.6 356.5 outlet subcooling 6.2 8.0 11.1 14.4 Expansion Device (TXV) inlet 43.2 1,924 41.7 2,439 109.7 279.1 107.1 353.7 inlet subcooling 6.4 7.9 11.6 14.3 Evaporator (water to refrig BPHE) inlet 7.4 607 6.2 747 45.4 88.0 43.2 108.3 outlet 4.7 505 6.9 604 40.4 73.3 44.4 87.6 outlet superheat 4.2 3.8 7.6 6.9 Refrigerant Reversing Valve LP inlet 4.7 505 6.9 604 40.4 73.3 44.4 87.6 LP outlet 6.0 492 8.5 587 42.8 71.4 47.3 85.2 HP inlet 92.9 1,982 87.4 2,501 199.2 287.4 189.3 362.8 HP outlet 85.4 1,965 82.3 2,487 185.7 285.0 180.2 360.7 DR 7
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 12 Oct 2012 Alternative Refrigerant ARM 32a Arkema Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 4.99 kg 10.5 11.0 lbm 1.048 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 15,612 W 50,329 53,269 Btu/hr 1.058 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 6,775 W 5,700 6,775 W 1.189 Power to Compressor 5,369 6,431 W 5,369 6,431 W 1.198 COP or EER (total) 2.59 2.30 [] 8.83 7.86 Btu/W hr 0.891 COP or EER (compressor only) 2.75 2.43 [] 9.37 8.28 Btu/W hr 0.884 Refrigerant Mass Flow Rate 345 405 kg/hr 761 894 lbm/hr 1.174 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF ARM 32a
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 12 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: ARM 32a Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 52.9 L/hr 14.0 14.0 gpm 0.996 T entering 11.2 11.4 C 52.2 52.5 0.4 T leaving 7.2 7.2 C 45.0 45.0 0.1 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.1 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 7.9 565 42.8 71.4 46.2 81.9 discharge 92.9 1982 85.1 2430 199.2 287.4 185.1 352.5 suction SH 6.3 5.8 11.4 10.5 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 80.0 2,415 185.7 285.0 176.0 350.2 outlet 43.8 1,941 43.2 2,386 110.8 281.5 109.7 346.0 outlet subcooling 6.2 6.6 11.1 11.8 Expansion Device (TXV) inlet 43.2 1,924 42.8 2,366 109.7 279.1 109.0 343.2 inlet subcooling 6.4 6.6 11.6 11.8 Evaporator (water to refrig BPHE) inlet 7.4 607 7.3 740 45.4 88.0 45.1 107.3 outlet 4.7 505 6.1 583 40.4 73.3 43.0 84.5 outlet superheat 4.2 3.1 7.6 5.7 Refrigerant Reversing Valve LP inlet 4.7 505 6.1 583 40.4 73.3 43.0 84.5 LP outlet 6.0 492 7.9 565 42.8 71.4 46.2 81.9 HP inlet 92.9 1,982 85.1 2,430 199.2 287.4 185.1 352.5 HP outlet 85.4 1,965 80.0 2,415 185.7 285.0 176.0 350.2 ARM 32a
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 12 Oct 2012 Alternative Refrigerant L 20 Honeywell Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 4.31 kg 10.5 9.5 lbm 0.905 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 14,857 W 50,329 50,695 Btu/hr 1.007 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 6,052 W 5,700 6,052 W 1.062 Power to Compressor 5,369 5,718 W 5,369 5,718 W 1.065 COP or EER (total) 2.59 2.46 [] 8.83 8.38 Btu/W hr 0.949 COP or EER (compressor only) 2.75 2.60 [] 9.37 8.87 Btu/W hr 0.946 Refrigerant Mass Flow Rate 345 268 kg/hr 761 591 lbm/hr 0.777 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF L 20
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 12 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: L 20 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 52.7 L/hr 14.0 13.9 gpm 0.992 T entering 11.2 11.2 C 52.2 52.2 0.0 T leaving 7.2 7.2 C 45.0 44.9 0.1 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.1 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 9.8 490 42.8 71.4 49.6 71.0 discharge 92.9 1982 98.0 2142 199.2 287.4 208.4 310.7 suction SH 6.3 6.5 11.4 11.8 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 90.6 2,133 185.7 285.0 195.1 309.4 outlet 43.8 1,941 42.5 2,114 110.8 281.5 108.5 306.7 outlet subcooling 6.2 5.3 11.1 9.5 Expansion Device (TXV) inlet 43.2 1,924 42.0 2,104 109.7 279.1 107.5 305.2 inlet subcooling 6.4 5.6 11.6 10.2 Evaporator (water to refrig BPHE) inlet 7.4 607 2.8 581 45.4 88.0 37.0 84.3 outlet 4.7 505 7.5 500 40.4 73.3 45.6 72.5 outlet superheat 4.2 3.7 7.6 6.6 Refrigerant Reversing Valve LP inlet 4.7 505 7.5 500 40.4 73.3 45.6 72.5 LP outlet 6.0 492 9.8 490 42.8 71.4 49.6 71.0 HP inlet 92.9 1,982 98.0 2,142 199.2 287.4 208.4 310.7 HP outlet 85.4 1,965 90.6 2,133 185.7 285.0 195.1 309.4 L 20
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 12 Oct 2012 Alternative Refrigerant LTR4X Mexichem Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 4.76 kg 10.5 10.5 lbm 1.000 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 14,790 W 50,329 50,464 Btu/hr 1.003 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 6,297 W 5,700 6,297 W 1.105 Power to Compressor 5,369 5,955 W 5,369 5,955 W 1.109 COP or EER (total) 2.59 2.35 [] 8.83 8.01 Btu/W hr 0.908 COP or EER (compressor only) 2.75 2.48 [] 9.37 8.47 Btu/W hr 0.904 Refrigerant Mass Flow Rate 345 349 kg/hr 761 769 lbm/hr 1.011 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF LTR4X
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 12 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: LTR4X Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 53.4 L/hr 14.0 14.1 gpm 1.004 T entering 11.2 11.2 C 52.2 52.1 0.0 T leaving 7.2 7.2 C 45.0 45.0 0.0 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.1 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 10.8 500 42.8 71.4 51.5 72.6 discharge 92.9 1982 90.4 2245 199.2 287.4 194.7 325.7 suction SH 6.3 8.6 11.4 15.4 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 84.4 2,237 185.7 285.0 184.0 324.4 outlet 43.8 1,941 41.2 2,212 110.8 281.5 106.2 320.9 outlet subcooling 6.2 6.7 11.1 12.1 Expansion Device (TXV) inlet 43.2 1,924 40.8 2,197 109.7 279.1 105.5 318.7 inlet subcooling 6.4 6.8 11.6 12.3 Evaporator (water to refrig BPHE) inlet 7.4 607 4.5 635 45.4 88.0 40.1 92.1 outlet 4.7 505 7.3 514 40.4 73.3 45.1 74.6 outlet superheat 4.2 4.2 7.6 7.6 Refrigerant Reversing Valve LP inlet 4.7 505 7.3 514 40.4 73.3 45.1 74.6 LP outlet 6.0 492 10.8 500 42.8 71.4 51.5 72.6 HP inlet 92.9 1,982 90.4 2,245 199.2 287.4 194.7 325.7 HP outlet 85.4 1,965 84.4 2,237 185.7 285.0 184.0 324.4 LTR4X
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 12 Oct 2012 Alternative Refrigerant LTR6A Mexichem Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 5.44 kg 10.5 12.0 lbm 1.143 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 14,971 W 50,329 51,082 Btu/hr 1.015 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 7,112 W 5,700 7,112 W 1.248 Power to Compressor 5,369 6,765 W 5,369 6,765 W 1.260 COP or EER (total) 2.59 2.11 [] 8.83 7.18 Btu/W hr 0.813 COP or EER (compressor only) 2.75 2.21 [] 9.37 7.55 Btu/W hr 0.806 Refrigerant Mass Flow Rate 345 317 kg/hr 761 698 lbm/hr 0.917 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF LTR6A
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 12 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: LTR6A Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 53.3 L/hr 14.0 14.1 gpm 1.003 T entering 11.2 11.2 C 52.2 52.2 0.0 T leaving 7.2 7.2 C 45.0 45.0 0.0 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.0 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 10.1 519 42.8 71.4 50.2 75.3 discharge 92.9 1982 102.5 2561 199.2 287.4 216.5 371.4 suction SH 6.3 4.1 11.4 7.4 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 95.0 2,549 185.7 285.0 203.0 369.6 outlet 43.8 1,941 40.7 2,531 110.8 281.5 105.2 367.1 outlet subcooling 6.2 5.1 11.1 9.2 Expansion Device (TXV) inlet 43.2 1,924 40.3 2,518 109.7 279.1 104.6 365.3 inlet subcooling 6.4 5.3 11.6 9.5 Evaporator (water to refrig BPHE) inlet 7.4 607 0.2 644 45.4 88.0 32.3 93.3 outlet 4.7 505 9.5 532 40.4 73.3 49.1 77.1 outlet superheat 4.2 2.8 7.6 5.1 Refrigerant Reversing Valve LP inlet 4.7 505 9.5 532 40.4 73.3 49.1 77.1 LP outlet 6.0 492 10.1 519 42.8 71.4 50.2 75.3 HP inlet 92.9 1,982 102.5 2,561 199.2 287.4 216.5 371.4 HP outlet 85.4 1,965 95.0 2,549 185.7 285.0 203.0 369.6 LTR6A
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 1 Manufacturer: Basic Information Trane 15 Oct 2012 Alternative Refrigerant D52Y Daikin Alternative Lubricant Type and ISO Viscosity POE 160SZ Baseline Refrigerant R22 Baseline Lubricant Type and ISO Viscosity POE 160SZ Make and Model of System Koolman CGAR 0605 Air Cooled Water Chiller / Heat Pump Nominal Capacity and Type of System 15.6 kw cooling / 17.7 kw heating (4.4 tons / 5.0 tons) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) cooling Compressor Type scroll compressor (Copeland ZR81KC TFD 50 Hz, 3φ, 380V) Compressor Displacement 18.7 m³/hr 662 ft³/hr Nominal Motor Size not listed by Copeland kw not listed by Copeland hp Motor Speed (50 Hz) not listed by Copeland Hz Expansion Device Type TXV (Danfoss, TDEX6, 068H4103) Lubricant Charge 1.8 L 1.9 qt Refrigerant Charge 4.76 4.99 kg 10.5 11.0 lbm 1.048 Composition (at Cmpr Suct) Chilled Leaving Temp 7.2 C 45 Water Flow rate 53.0 L/min 14.0 gpm Outdoor Dry Bulb 35 C 95 Air Wet Bulb n/a C n/a Total Capacity 14,750 13,954 W 50,329 47,612 Btu/hr 0.946 Sensible Capacity n/a n/a W n/a n/a Btu/hr n/a Total System Power Input 5,700 5,926 W 5,700 5,926 W 1.040 Power to Compressor 5,369 5,597 W 5,369 5,597 W 1.042 COP or EER (total) 2.59 2.35 [] 8.83 8.03 Btu/W hr 0.910 COP or EER (compressor only) 2.75 2.49 [] 9.37 8.51 Btu/W hr 0.908 Refrigerant Mass Flow Rate 345 423 kg/hr 761 933 lbm/hr 1.225 Other System Changes The unit tested was returned to original production by replacing the compressor and TXV with original equipment. The evaporator remains the one used during R410A testing. System Data Base Alt. Ratio Degradation Coefficient Seasonal Energy Efficiency Ration SEER Heating Seasonal Performance Factor HSPF D52Y
Trane Koolman Tests of "HP" Alternate Refrigerants Appendix B: Experimental Results at Nominal Operating Condition Low GWP AREP SYSTEM DROP IN TEST DATA FORM page 2 15 Oct 2012 Type of System: Koolman CGAR 0605 Alternate Refrigerant: D52Y Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio Diff Evaporator (BPHE) fluid flow rate water 53.1 53.1 L/hr 14.0 14.0 gpm 0.999 T entering 11.2 11.0 C 52.2 51.7 0.4 T leaving 7.2 7.2 C 45.0 45.0 0.1 Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd gpm T entering C 95.1 95.0 0.1 T leaving not msrd C not msrd Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction 6.0 492 8.3 514 42.8 71.4 46.9 74.5 discharge 92.9 1982 74.7 2113 199.2 287.4 166.4 306.5 suction SH 6.3 5.4 11.4 9.8 Condenser (refrig to air fin & tube coil) inlet 85.4 1,965 70.2 2,095 185.7 285.0 158.3 303.9 outlet 43.8 1,941 42.4 2,065 110.8 281.5 108.4 299.4 outlet subcooling 6.2 5.2 11.1 9.4 Expansion Device (TXV) inlet 43.2 1,924 42.1 2,042 109.7 279.1 107.8 296.2 inlet subcooling 6.4 5.2 11.6 9.4 Evaporator (water to refrig BPHE) inlet 7.4 607 8.9 706 45.4 88.0 48.1 102.4 outlet 4.7 505 7.4 533 40.4 73.3 45.4 77.3 outlet superheat 4.2 3.5 7.6 6.3 Refrigerant Reversing Valve LP inlet 4.7 505 7.4 533 40.4 73.3 45.4 77.3 LP outlet 6.0 492 8.3 514 42.8 71.4 46.9 74.5 HP inlet 92.9 1,982 74.7 2,113 199.2 287.4 166.4 306.5 HP outlet 85.4 1,965 70.2 2,095 185.7 285.0 158.3 303.9 D52Y