TEST REPORT #63. Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Low-GWP Alternative Refrigerants Evaluation Program (Low-GWP AREP)

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1 Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Low-GWP Alternative Refrigerants Evaluation Program (Low-GWP AREP) TEST REPORT #63 System Soft-optimization Tests of Refrigerant R-32, DR-5A, and DR-55 in a R-410A 4-ton Unitary Rooftop Heat Pump-Heating Mode Performance Ken Schultz Marcos Perez-Blanco Steve Kujak Ingersoll Rand 3600 Pammel Creek Road La Crosse, WI January 18, 2016 This report has been made available to the public as part of the author company s participation in the AHRI s Low-GWP AREP.

2 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 2 of 12 INTRODUCTION This report documents tests performed on a 4 RT (14 kw) rooftop heat pump, to evaluate the performance of lower GWP refrigerants as alternatives to R410A in unitary air-conditioning and heat pump equipment. Compositions and GWPs are listed below in Table 1. The unit was run at the rating conditions specified in AHRI Standard 210/240 for heating mode performance. Tests were run using R410A (baseline), DR-55, R32, and DR-5A with performance of the three alternatives compared to the baseline R410A. The tests were performed in controlled ambient chambers at Ingersoll Rand/Trane s La Crosse Development Laboratory in La Crosse, Wisconsin, from late-may through early-august Table 1. Refrigerants tested, with compositions and global warming potentials (GWPs). Name composition (%wt) GWP (AR4) GWP (AR5) R410A 50% R32 / 50% R DR-55 67% R32 / 7% R125 / 26% R1234yf R32 100% R DR-5A 68.9% R32 / 31.1% R1234yf The thermodynamic properties of R410A and R32 are based on NIST s REFPROP v The thermodynamic properties of DR-55 and DR-5A are based on REFPROP v9.1 using mixing parameters for the R32/R1234yf and R125/R1234yf pairs provided Chemours (formerly DuPont). DETAILS OF TEST SETUP Description of Baseline System A Precedent model WSC048E3ROA1J rooftop unit, manufactured by Trane, was chosen for refrigerant testing purposes. The unit is rated at a net heating capacity of 44,000 BTU/hr (12.9 kw) heating capacity and 3.40 COP, with a catalog refrigerant charge of 9.0 lbm (4.1 kg) of R410A. The unit is driven by an Alliance model SXA044B2BPA fixed speed scroll compressor with a displacement of ft³/rev (2.56 in³/rev or L/rev) lubricated with Emkarate RL32H POE oil. The compressor runs at 3500 RPM at 60 Hz input frequency for a displacement of 311 ft³/hr (8.82 m³/hr). The indoor and outdoor heat exchangers are of aluminum-fin/copper-tube construction with fixed speed fans. Description of Modifications to System The original factory-installed fixed TXVs for cooling and heating were both replaced with adjustable TXVs of the same size. Additionally the compressor was fitted with a variable frequency drive (VFD, Trane TR200 P5K5), which allowed the compressor speed (volumetric capacity) to be varied so that all the refrigerants could be tested at the same thermodynamic capacity. Measure- 1 The descriptions of R410A and R32 have not changed from REFPROP v8.1 to the current v9.1. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

3 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 3 of 12 ment of input power was made upstream of the VFD, however, the efficiency of the AFD is essentially constant (cataloged at 0.97) over the range of power and speed tested, so it has no effect on the comparisons between refrigerants. Description of Tests Conducted The method of test was consistent with Appendix M of AHRI Standard 210/240 with Addenda 1 and 2 (2008/2012), with operating conditions generally held within tighter tolerances. The indoor (ID) airflow rate was fixed at the catalog value of 1600 scfm for all tests. Figure 1 shows a diagram of the Precedent unit. In this diagram, the reversing valve is in the heating mode position. The points in the cycle at which measurements such as pressure and temperature were taken are indicated on the diagram. The accuracies of the various instrument types are listed in Table 2. Table 2. Instrumentation accuracies. measurement accuracy thermocouples (uncalibrated) ±1 RTD sensors (calibrated) ±0.1 air-side pressure differences (calibrated) Rosemount 1151DP3S12 (30 inh 2 O full scale) ±0.075% of span pressure transducers (calibrated) Honeywell DS-750 (750 psi full scale) ±0.1% full scale refrigerant turbine meter (calibrated) Flow Technology FT4-8NE00-LEAH4 ±0.5% of reading electrical power (calibrated) YEW WT230 (6 kw full scale) ± (0.1% of reading + 0.1% of range) The reported heating capacities were calculated from airside flow rate and temperature (dry bulb and wet bulb) measurements. For confirmation, capacity was also calculated from refrigerant side flow rate and enthalpy measurements around the indoor coil, providing a check on energy balance. Internal property codes, consistent with ASHRAE and NIST REFPROP descriptions, were used for calculation of air and refrigerant thermodynamic properties. Tests were carried out at the rating points called out in AHRI Standard 210/240 for heating performance, listed in Table 3. The H2 conditions produce frosting on the outdoor evaporator coil, resulting in cyclic heat/defrost operation. The capacity and efficiency values reported here are integrated averages over a number of heat/defrost cycles acquired after several heat/defrost cycles had occurred and periodic steady-state had been established. Although the H3 conditions also result in frosting of the outdoor coil, the build-up rate is slow enough to allow essentially steady-state behavior. Performance at the H3 conditions was determined by averaging capacity and power consumption for 30 minute period following the termination of a defrost cycle. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

4 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 4 of 12 Table 3. Conditions for the H1, H2, and H3 heating mode rating tests. test indoor Tdb indoor Twb outdoor Tdb outdoor Twb H1 70 / 21.1 C 60 / 15.6 C 47 / 8.3 C 43 / 6.1 C H2 70 / 21.1 C 60 / 15.6 C 35 / 1.7 C 33 / 0.6 C H3 70 / 21.1 C 60 / 15.6 C 17 / 8.3 C 15 / 9.4 C Refrigerant charge and compressor speed were taken from the A cooling condition as described in the previous report 2 and summarized in Table 4. A charge sweep run with R410A in heating mode at the H1 conditions showed a peak in COP at the same 9.0 lbm (4.1 kg) charge determined from the cooling mode tests. The heating mode TXV was adjusted at the H1 conditions with each alternative refrigerant to deliver the same compressor suction superheat as obtained with R410A (~10/5.6 C). RESULTS Table 4 shows the refrigerant charge, TXV setting, and compressor speed used for each refrigerant. Also shown is the heating mode capacity and COP measured at the H1 rating point. Air-side capacities relative to the average of the R410A test points are shown in Figure 2. Capacity was very repeatable within ±1.5% for each refrigerant at the H1 point. Unit capacity was very similar with all refrigerants being within 2.5% of R410A. COP data are shown in Figure 3. COP was also very repeatable at the H1 point, generally within ±0.5% to ±1% for each refrigerant. DR-55 and DR-5A provided COPs ~1.5% better than R410A; R32 s COP was ~3% higher. Table 4. Refrigerant charge, TXV position, and compressor speed selected for each refrigerant, along with the average capacity and COP obtained at the H1 point for each. Refrig # of Charge TXV AFD wrt wrt CAP COP runs (lbm) (turns) (Hz) R410A R410A R410A , DR CW 60 45, % % R CW 55 45, % % DR-5A ½ CW 61 45, % % CW is clockwise (in/closed), CAP is Air-side Capacity in BTU/hr. The air-side heating capacities and COPs (as integrated averages over a number of heating/defrost cycles) taken under the H2 conditions are shown in Figure 4 and Figure 5, respectively. Significant variability in performance was observed during the H2 tests, especially with R410A. This can be attributed to several potential causes, one being variability in the frost build process and the (in)ability of the facility to hold chamber conditions perfectly as the unit switches between operating modes. 2 TEST REPORT #56, SOFT-OPTIMIZED SYSTEM TEST OF R410A, DR-55, R32, AND DR-5A IN A 4-TON UNITARY ROOFTOP HEAT PUMP, Schultz, Perez-Blanco, and Kujak, submitted to AHRI Low GWP AREP 29-Sep IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

5 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 5 of 12 Under the H2 defrost conditions, DR-55 provided about 10% additional capacity over R410A and R32 15% to 20% more capacity along with significantly higher efficiencies. Figure 6 shows time traces of heat pump status and compressor power draw during operating under H2 conditions for each refrigerant. As shown in Figure 7, the fraction of time spent in defrost mode with R32 was shorter than for the other refrigerants. The defrost period for R32 ranged from 2.5 to 3 minutes while being 5 to 10 minutes for the other refrigerants. Heating periods ranged from 35 to 50 minutes for all refrigerants. The differences in defrost periods appear to be driven by differences in controls response. Defrost mode is supposed to terminate when the outdoor coil sensor (attached to the inlet to the bottom circuit) reading (OCT) is a specified offset above the outdoor air temperature. With R32 in the unit, defrost periods terminated when OCT was slightly above the setpoint. With R410A and DR-5A, the OCT reading was 20d to 30d beyond the setpoint before defrost ended. With DR-55, the OCT reading was 10d to 20d higher than the setpoint when defrost stopped. Although this phenomenon was generally repeatable, it is not understood how or why the controls response should be dependent on the refrigerant present. 3 Given the similarities in properties of these four refrigerants, it would be expected that similar levels of performance should be obtained if defrost occurred at common initiation and termination temperatures. (This also suggests that the level of performance obtained with R32 should be approachable with the other refrigerants.) Heating capacities and COPs relative to R410A at the H3 conditions are shown in Figure 11. At this colder outdoor condition, all refrigerants produced slightly lower capacities, ranging from R32 being 1% lower to DR-55 being 4% lower than R410A. COPs were equal to 1% lower with DR-5A and DR-55 and up by 4% with R32. The compressor discharge temperatures (CDTs) measured are shown in Figure 9 for the H1 tests and in Figure 10 for the H3 tests. R32 ran about 20d higher than the baseline R410A. DR-5A ran about 10d to 14d higher and DR-55 ran only 8d higher. Similar results were obtained during the heating segments of the H2 tests. All CDTs were well below the maximum operating temperature limit of 250. Heating mode cyclic degradation coefficients (C Dh ), calculated from the H1C (cyclic) tests with each refrigerant, are shown in Figure 11, along with percent differences relative to R410A. All the C Dh values are quite small, so the differences between them are of little significance. SUMMARY Performance tests have been run on a standard production rooftop unit of nominal 44,000 BTU/hr heating capacity and 3.40 COP with R410A, serving as the baseline, and alternative refrigerants DR-55, R32, and DR-5A. No alterations were made to the unit other than replacing the fixed TXVs with adjustable TXVs to allow keeping the superheats with the low GWP refrigerants consistent with the R410A baseline, and installing a VFD on the compressor to match the baseline capacity. 3 The OCT values used here are readings from a thermocouple attached to the OCT sensor well. The OCT thermocouple readings closely matched readings from another thermocouple attached to the same circuit approximately 3 inches upstream. Although there might have been an offset between the OCT sensor and thermocouple readings, it would be expected to be a fixed value not dependent on the refrigerant being used. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

6 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 6 of 12 At the H1 and H3 (continuous run) heating points, all three alternative refrigerants showed a small (1% to 4%) decrease in capacity. All three alternatives showed small improvements in COP at the H1 point (1% to 2%). DR-55 showed a small decrease (~1%) at the H3 point while R32 showed a small increase (~4%). At the H2 cyclic defrost test condition, there was a modest increase in capacity with DR-55 (~10%) and a significant increase (~20%) with R32. There was a large improvement in COP at the H2 condition when running with DR-55 (10% to 15%) and R32 (~25%). This was driven mainly by the shorter defrost periods with DR-55 and especially so with R32. This appears to have been driven by the controller tripping the end of defrost at quite different temperatures between the refrigerants. It is unclear at this time why this happened. It is expected that differences in performance under frosting conditions between the refrigerants would be much smaller with consistent trip points. Compressor discharge temperatures (CDTs) were slightly higher when running with DR-55 and DR-5A, typically 5 d to 10 d (3 Cd to 6 Cd). As expected, the highest discharge temperatures were measured with R32, being roughly 20 d higher than with R410A. Figure 1. Precedent unit test setup indicating measurement locations. Heating mode flow directions are shown. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

7 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 7 of 12 Figure 2. Air-side heating capacity at the H1 conditions relative to the average of the R410A baseline points. Figure 3. Heating COP at the H1 conditions relative to the average of the R410A baseline points. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

8 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 8 of 12 Figure 4. Air-side heating capacity (as an integrated average over a number of heating/defrost cycles) at the H2 conditions relative to the average of the R410A baseline points. Note the order of runs, starting with R410A, progressing with DR-55, R32, and DR-5A through Run 127. Additional runs were then collected with R410A, R32, and DR-55 (in that order). Figure 5. Heating COP (as an integrated average over a number of heating/defrost cycles) at the H2 conditions relative to the average of the R410A baseline points. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

9 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 9 of 12 R410A R32 DR-55 DR-5A Figure 6. Traces with time (in minutes) of compressor power (in kw on left axis) and heat pump status (right axis, 0 = defrost mode, 500 = heating mode) while operating at the H2 conditions. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

10 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 10 of 12 Figure 7. Fraction of time that unit spent in heating mode (bottom segment of the columns) and defrost mode (upper segment of the columns) during H2 tests. Figure 8. Performance under H3 conditions. Left) Air-side capacity relative to R410A. Right) Heating COP relative to R410A. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

11 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 11 of 12 Figure 9. Compressor discharge temperatures measured during operation at the H1 test conditions. Figure 10. Compressor discharge temperatures measured during operation at the H3 test conditions. Figure 11. Left: Cyclic degradation coefficients determined by the H1C test. Right: Percent difference of cyclic degradation coefficients relative to R410A. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

12 Soft-Optimized Tests of a 4-RT Unitary Rooftop Heat Pump with R410A, DR-55, R32, and DR-5A Heating Mode Performance page 12 of 12 DATA TABLES Tables of data recorded for the H1 and H3 test points from selected runs for each refrigerant follow. Note: The value for the compressor/unit lubricant charge is unknown (not listed on any of the unit labels nor in the catalog). The standard production lubricant charged was used for both the cooling and heating tests. IRUnitaryHeatPumpTestReport_Htg_v5b.docx Marcos E. Perez-Blanco & Ken Schultz Technology Validation Group Modeling & Simulation NoE

13 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H1 Basic Information Alternative Refrigerant DR 55 Run #70 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #12 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 1.00 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.91 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 47 Air Wet Bulb 6.1 C 43 EB = Qrefrig/Qair % % Air side Capacity kw 46,590 45,640 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

14 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H1 Baseline Refrig: R410A Run #12 Alternate Refrig: DR 55 Run #70 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet

15 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H3 Basic Information Alternative Refrigerant DR 55 Run #145 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #29 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 1.00 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.91 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 17 Air Wet Bulb 9.4 C 15 EB = Qrefrig/Qair % % Air side Capacity kw 25,270 24,230 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

16 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H3 Baseline Refrig: R410A Run #29 Alternate Refrig: DR 55 Run #145 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet

17 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H1 Basic Information Alternative Refrigerant R32 Run #102 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #12 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 0.92 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.81 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 47 Air Wet Bulb 6.1 C 43 EB = Qrefrig/Qair % % Air side Capacity kw 46,590 45,360 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

18 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H1 Baseline Refrig: R410A Run #12 Alternate Refrig: R32 Run #102 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet

19 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H3 Basic Information Alternative Refrigerant R32 Run #100 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #29 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 0.92 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.81 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 17 Air Wet Bulb 9.4 C 15 EB = Qrefrig/Qair % % Air side Capacity kw 25,270 25,010 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

20 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H3 Baseline Refrig: R410A Run #29 Alternate Refrig: R32 Run #100 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet

21 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H1 Basic Information Alternative Refrigerant DR 5A Run #125 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #12 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 1.02 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.91 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 47 Air Wet Bulb 6.1 C 43 EB = Qrefrig/Qair % % Air side Capacity kw 46,590 45,800 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

22 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H1 Baseline Refrig: R410A Run #12 Alternate Refrig: DR 5A Run #125 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet

23 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 1 04/Nov/2015 Manufacturer: Trane Test Point: H3 Basic Information Alternative Refrigerant DR 5A Run #128 Alternative Lubricant Type and ISO Viscosity POE Emkarate RL32H Baseline Refrigerant R410A Run #29 Baseline Lubricant Type and ISO Viscosity POE Emkarate RL32H Make and Model of System Precedent Rooftop Heat Pump, WSC048E3 Nominal Capacity and Type of System 48,500 Btu/hr cooling (A) / 44,000 Btu/hr heating (H1) Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio Mode (heating/cooling) heating Compressor Type scroll, Alliance model SXA044B2BPA Compressor Displacement 8.82 m³/hr 311 ft³/hr Nominal Motor Size 2.83 kw 3.8 hp Motor Speed (w/60 Hz input) 3500 Hz Hz 1.02 Expansion Device Type TXV (Emerson: cooling = AACE4 ZW195, heating = AAE3 ZW195) Lubricant Charge? L? qt Refrigerant Charge kg lbm 0.91 Indoor Entering DBT 21.1 C 70 Air Entering WBT 15.6 C 60 Target Flow rate (mixed) 45.3 m³/min 1600 scfm Outdoor Dry Bulb 8.3 C 17 Air Wet Bulb 9.4 C 15 EB = Qrefrig/Qair % % Air side Capacity kw 25,270 24,530 Btu/hr Sensible Capacity n/a n/a kw n/a n/a Btu/hr n/a Total System Power Input kw kw Power to Compressor kw kw COP or EER (total) [] [] COP or EER (compressor only) [] [] Refrigerant Mass Flow Rate kg/hr lbm/hr Other System Changes The unit tested was modified from original production by replacing fixed TXVs with adjustable TXVs of the same size and installing a VFD on the compressor to allow matching baseline capacity. Compressor speed was set by matching cooling capacity at the "A" conditions. Refrigerant charge was chosen to maximize EER at the "A" conditions (essentially the same as matching the baseline condenser exit subcooling). continued on next page

24 Low GWP AREP SOFT OPTIMIZED SYSTEM TEST DATA FORM page 2 04/Nov/2015 Type of System: Precedent RTU HP Test Point: H3 Baseline Refrig: R410A Run #29 Alternate Refrig: DR 5A Run #128 Water/Air Side Data Base Alt. SI Units Base Alt. IP Units Ratio barametric pressure kpa psia Evaporator (fin &tube coil) fluid flow rate air L/hr scfm entering DBT C d entering WBT C d entering DPT C d leaving DBT C d leaving WBT C d leaving DPT C d Condenser (fin & tube coil) fluid air flow rate not msrd L/hr not msrd scfm entering DBT C d entering DPT C d entering w kgw/kgda lbmw/lbmda Refrigerant Side Base Alt. Base Alt. T ( C) P (kpa) T ( C) P (kpa) T () P (psia) T () P (psia) Compressor (scroll) suction discharge suction SH Condenser (refrig to air fin & tube coil) inlet outlet outlet subcooling Expansion Device (TXV) inlet inlet subcooling Evaporator (refrig to air fin & tube coil) inlet (header) outlet outlet superheat Refrigerant Reversing Valve LP inlet LP outlet HP inlet HP outlet