THERMAL PUMP REFRIGERANTS

Abstract

A refrigerant consisting or consisting essentially of: a) a nonflammable high volatility component consisting of carbon dioxide, and b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) optionally a component selected from the group consisting of HFC227ea, HFC152a, HFC32 and mixtures thereof.

Claims

1. A refrigerant consisting essentially of: a) a nonflammable high volatility component consisting of carbon dioxide, and b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) optionally a component selected from the group consisting of HFC227ea, HFC152a, HFC32 and mixtures thereof.

2. A refrigerant as claimed in claim 1 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) optionally an HFC selected from the group consisting of HFC32, HFC227ea and R152a or mixtures thereof; wherein the amount of the high volatility component is in the range from 5 wt % to 85 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 80 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 90 wt %; wherein the amount of HFC32 when present is in the range from 2 wt % to 59 wt %; wherein the amount of HFC227ea when present is in the range from 1 wt % to 12.4 wt %; wherein the amount of HFC152ea when present is in the range from 2 wt % -10 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

3. A refrigerant as claimed in claim 2 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) and an HFC selected from the group consisting of HFC32, HFC227ea and mixtures thereof; wherein the amount of the high volatility component is in the range from 5 wt % to 60 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 65 wt %; wherein the amount of HFC32 when present is in the range from 2 wt % to 59 wt %; wherein the amount of HFC227ea when present is in the range from 1 wt % to 12.4 wt %; wherein the amount of HFC152ea when present is in the range from −2 wt % -10 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

4. A refrigerant as claimed in claim 3 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) an HFC selected from the group consisting of HFC32, HFC152a and HFC227ea and mixtures thereof; wherein the amount of the high volatility component is in the range from 5 wt % to 30 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 65 wt %; wherein the amount of HFC32 when present is in the range from 22.2 wt % to 59 wt %; wherein the amount of HFC227ea when present is in the range from 4.7 wt % to 12.4 wt %; wherein the amount of HFC152ea when present is in the range from 3 wt %-] 8 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

5. A refrigerant as claimed in claim 3 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) and an HFC selected from the group consisting of HFC32, HFC152a, HFC227ea and mixtures thereof; wherein the amount of the high volatility component is in the range from 5 wt % to 30 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 65 wt %; wherein the amount of HFC32 when present is in the range from 2 wt % to 22 wt %; wherein the amount of HFC227ea when present is in the range from 1 wt % to 4.7 wt %; wherein the amount of HFC152ea when present is in the range from 3 wt %-5 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

6. A refrigerant as claimed in claim 5 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32; wherein the amount of the high volatility component is in the range from 5 wt % to 30 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 60 wt %; wherein the amount of HFC32 is in the range from 2 wt % to 22 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

7. A refrigerant as claimed in claim 6 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO-1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32; wherein the amount of the high volatility component is in the range from 6 wt % to 25 wt %; wherein the amount of the low volatility component is in the range from 7 wt % to 30 wt %; wherein the amount of the intermediate volatility component is in the range from 40 wt % to 60 wt %; wherein the amount of HFC32 is in the range from 10 wt % to 21.5 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

8. A refrigerant as claimed in claim 5 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO-1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32; wherein the amount of the high volatility component is in the range from 5 wt % to 15 wt %; wherein the amount of the low volatility component is in the range from 6 wt % to 35 wt %; wherein the amount of the intermediate volatility component is in the range from 46 wt % to 55 wt %; wherein the amount of HFC32 is in the range from 15 wt % to 21.5 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

9. A refrigerant as claimed in claim 5 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC227ea; wherein the amount of the high volatility component is in the range from 5 wt % to 30 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 65 wt %; wherein the amount of HFC227ea is in the range from 2 wt % to 4.7 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %

10. A refrigerant as claimed in claim 2 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 5 wt % to 90 wt %; wherein the amount of the low volatility component is in the range from 2 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 15 wt % to 60 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

11. A refrigerant as claimed in claim 10 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 5 wt % to 80 wt %; wherein the amount of the low volatility component is in the range from 2 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 15 wt % to 60 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

12. A refrigerant as claimed in claim 11 consisting or consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) optionally an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 50 wt % to 75 wt %; wherein the amount of the low volatility component is in the range from 2 wt % to 25 wt %; wherein the amount of the intermediate volatility component is in the range from 15 wt % to 35 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

13. A refrigerant as claimed in claim 12 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) optionally an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; wherein the amount of the high volatility component is in the range from 60 wt % to 75 wt %; wherein the amount of the low volatility component is in the range from 2 wt % to 20 wt %; wherein the amount of the intermediate volatility component is in the range from 15 wt % to 30 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

14. A refrigerant as claimed in claim 2 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) optionally an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 5 wt % to 60 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 10 wt % to 75 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

15. A refrigerant as claimed in claim 14 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 10 wt % to 50 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 35 wt %; wherein the amount of the intermediate volatility component is in the range from 12 wt % to 70 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

16. A refrigerant as claimed in claim 15 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 10 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 15wt % to 55 wt %; wherein the amount of the low volatility component is in the range from 7 wt % to 25 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

17. A refrigerant as claimed in claim 16 consisting essentially of: a) a nonflammable, high volatility component CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO-1225ye(Z), HFO1243zf and mixtures thereof; and wherein the amount of the high volatility component is in the range from 20 wt % to 40 wt %; wherein the amount of the intermediate volatility component is in the range from 30 wt % to 55 wt %; wherein the amount of the low volatility component is in the range from 7 wt % to 25 wt %; and wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %.

18. A refrigerant as claimed in claim 4 for use in new equipment and for retrofitting for use in existing equipment consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO-1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32; wherein the amount of the high volatility component is in the range from 8 wt % to 19 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 8 wt %; wherein the amount of the intermediate volatility component is in the range from 39 wt % to 51 wt %; wherein the amount of HFC32 is in the range from 35 wt % to 44 wt %; wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %; and wherein the bubble point vapour pressure of the blend at 40° C. does not exceed 30 bara.

19. A refrigerant as claimed in claim 3 consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO-1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32, HFC227ea or mixtures thereof, wherein the amount of the high volatility component is in the range from 10 wt % to 35 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 20 wt %; wherein the amount of the intermediate volatility component is in the range from 40 wt % to 80 wt %; wherein the amount of HFC32 when present is in the range from 18 wt % to 22 wt %; wherein the amount of HFC227ea when present is in the range from 2wt % to 4.5 wt %; wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt % and wherein the bubble point vapour pressure of the blend at 35° C. does not exceed 30 bara.

20. A refrigerant consisting essentially of: a) a nonflammable, high volatility component consisting of CO.sub.2; b) a nonflammable low volatility component selected from the group consisting of: HFO1224yd(Z), HFO1224yd(E), HFO1233zd(E), HFO1233zd(Z), HFO1233xf, HFO1336mzz(E), HFO1336mzz(Z), 2-bromo-3,3,3-trifluoroprop-1-ene and mixtures thereof; c) an intermediate volatility component selected from the group consisting of: HFO1234yf, HFO1234ze(E), HFO1225ye(Z), HFO1243zf and mixtures thereof; and d) HFC32, HFC227ea or mixtures thereof, wherein the amount of the high volatility component is in the range from 8 wt % to 25 wt %; wherein the amount of the low volatility component is in the range from 5 wt % to 20 wt %; wherein the amount of the intermediate volatility component is in the range from 35 wt % to 70 wt %; wherein the amount of HFC32 when present is in the range from 18 wt % to 22 wt %; wherein the amount of HFC227ea when present is in the range from 2 wt % to 5 wt %; wherein the amounts of the ingredients are selected from the ranges recited to total 100 wt %; and wherein the bubble point vapour pressure of the blend at 35° C. does not exceed 35 bara.

Description

EXAMPLE 1

[0334] A comparative calculation was made for R410A used in a typical split air conditioning system represented by FIG. 1, comprising an hermetic compressor 2, driven by electric motor 1, both components being enclosed in pressure casing 12, an air cooled condenser 3, an electronic expansion valve 4, an air heated evaporator 5, and an accumulator 6. The condenser exit temperature of the liquid refrigerant was 40° C. with 5 K subcooling. The exit temperature of the vapour from the evaporator was 12° C. with 5 K superheat. The unit was controlled by microprocessor 8, which received temperature values for the refrigerant exiting the evaporator from temperature sensor 7 via data line 11, and from a room thermostat 13 via data line 14. 8 controlled the system to maintain the room temperature at the required level in response to the input data by adjusting 4 via signal line 10, and the speed of 1, and thus the compressor capacity, by signal line 9.

The values of key parameters demonstrating the refrigerant performance are shown in Table 1.

[0335] Example 2

[0336] A comparative calculation was made for R404A used in a typical freezer chest, also represented by FIG. 1, comprising an hermetic compressor 2, driven by electric motor 1, both components being enclosed in pressure casing 12, an air cooled condenser 3, an electronic expansion valve 4, an air heated evaporator 5, and an accumulator 6. The condenser exit temperature of the liquid refrigerant was 30° C. with 5 K subcooling. The exit temperature of the vapour from the evaporator was −30° C. with 5 K superheat. The unit was controlled by microprocessor 8, which received temperature values for the refrigerant exiting the evaporator from temperature sensor 7 via data line 10, and from a thermostat 13 located inside the freezer chest via data line 14. 8 controlled the system to maintain the freezer chest in the range −18 to −23° C. in response to the input data by adjusting 4 via signal line 10, and the speed of 1, and thus the compressor capacity, by signal line 9.

[0337] The values of key parameters demonstrating the refrigerant performance are shown in Table 2.

EXAMPLE 3

[0338] Calculations were performed for non-flammable blends with GWPs below 400 in a split air conditioning system (as shown in FIG. 2) comprising an accumulator 14, an hermetic compressor 1, a condenser 4, an internal heat exchanger 5 transferring heat from the higher temperature, higher pressure refrigerant stream to the lower temperature, lower pressure refrigerant stream, an electronic expansion valve 6 and an evaporator 10. The refrigerant flow in the circuit was controlled by pressure and temperature sensors in the discharge line immediately after the compressor. The compressor was driven by a variable-speed electric motor 12 and cooled by the removal of heat using a heat pipe 13.

[0339] The unit was controlled by a micro-processor 9, programmed with the thermodynamic properties of the refrigerant. The microprocessor received input data from a temperature sensor 2, via data line 8, and a pressure sensor 3, via data line 7, the sensors being located on the discharge line close to the compressor. The microprocessor transmitted output signals that varied the motor speed, via signal line 15, and the degree of opening of the expansion valve, via signal line 11, so the performance of the unit was matched to the required room temperature. In particular, the microprocessor ensured that the superheat of the refrigerant entering the discharge line was at least 5 K to avoid potentially damaging wet compression.

[0340] To provide proper comparison with R410A in Example 1, the refrigerant temperature at the condenser exit temperature was 40° C.; the evaporator entry temperature was 7° C.; the compressor isentropic efficiency was 0.7; and the electric motor efficiency was 0.9. A pressure drop was applied across the evaporator to provide an actual temperature glide of 11K.

[0341] The values of key parameters demonstrating the refrigerant performance of blends 1 to 12 are shown in Tables 3a and 3b.

EXAMPLE 4

[0342] Calculations were performed for non-flammable blends with GWPs below 400 in a refrigeration system (as shown in FIG. 3) comprising an accumulator 14, an hermetic compressor 1, a condenser 4, an internal heat exchanger 5 transferring heat from the higher temperature, higher pressure refrigerant stream to the lower temperature, lower pressure refrigerant stream, an electronic expansion valve 6 and an evaporator 10. The refrigerant flow in the circuit was controlled by pressure and temperature sensors in the discharge line immediately after the compressor. The compressor was driven by a variable-speed electric motor 12 and cooled by the removal of heat by pumping liquid refrigerant into heat exchanger 13 in contact with the compressor head using an injector pump or liquid turbopump 16 drawing liquid refrigerant from the liquid line just before the expansion valve 6. The unit was controlled by a micro-processor 9, programmed with the thermodynamic properties of the refrigerant. The microprocessor received input data from a temperature sensor 2, via data line 8, and a pressure sensor 3, via data line 7, the sensors being located on the discharge line close to the compressor. The microprocessor transmitted output signals that varied the motor speed, via signal line 15, and the degree of opening of the expansion valve, via signal line 11, so the performance of the unit was matched to the required room temperature. In particular, the microprocessor ensured that the superheat of the refrigerant entering the discharge line was at least 5 K to avoid potentially damaging wet compression.

[0343] To provide proper comparison with R404A in Example 2, the refrigerant temperature at the condenser exit temperature was 30° C.; the evaporator entry temperature was −35° C.; the compressor isentropic efficiency was 0.7; and the electric motor efficiency was 0.9. A pressure drop was applied across the evaporator to provide an actual temperature glide of 5K.

[0344] The values of key parameters for blends 13 to 24 are shown in Tables 4a and 4b.

EXAMPLE 5

[0345] Calculations were performed for a non-flammable blend (25) with a GWP of 2 consisting of 5% R1224yd(Z), 69% CO.sub.2 and 26% R1234ze(E) in a split air conditioning system (FIG. 4) comprising an accumulator 13; a two-stage, integrated hermetic compressor comprising a variable speed electric motor 4, a lower pressure first stage 1 and a higher pressure second stage 2; a condenser 5; an internal heat exchanger (IHX) 6 transferring heat from the higher temperature, higher pressure refrigerant stream to the lower temperature, lower pressure refrigerant stream; an electronic expansion valve 7 and an evaporator 8. The refrigerant flow in the circuit was controlled by pressure and temperature sensors, 10 and 11, in the suction line immediately after the IHX 6.

[0346] Gas discharged from the first compression stage was passed through an external heat exchanger, called an intercooler 3, where it was cooled by ambient air before to entering the gas volume within the compressor casing surrounding the electric motor and the 2-stage compressor. The gas cooled the motor and then entered the suction port of the second compression stage, where it was further compressed and then discharged to the condenser.

[0347] The unit was controlled by a micro-processor 9, programmed with the thermodynamic properties of the refrigerant. The microprocessor received input data from the temperature sensor 11, the pressure sensor 10 and the temperature sensor 14 that measured the room temperature. The microprocessor transmitted output signals that varied the motor speed, via signal line 15, and the degree of opening of the expansion valve, via signal line 12, so the performance of the unit was optimised and matched to the required room temperature. In particular, the microprocessor ensured that the superheat of the refrigerant entering the compressor was at least 2 K and preferably 5 K to avoid potentially damaging wet compression.

[0348] To provide proper comparison with R410A in Example 1, the refrigerant temperature at the condenser exit temperature was 40° C.; the evaporator entry temperature was 7° C.; the compressor isentropic efficiency was 0.7; and the electric motor efficiency was 0.9. A pressure drop was applied across the evaporator to provide an actual temperature glide of 11K.

[0349] The values of key parameters demonstrating the refrigerant performance for a blend consisting of 5% R1224yd(Z), 69% CO.sub.2 and 26% R1234ze(E) are shown in Table 5. This blend is superior to R410A for air conditioning because it combines a GWP of only 2 with a suction volumetric capacity of 107808 kJ/kg (R410A: 5832 kJ/kg) but with a comparable energy efficiency. The blend is superior to CO.sub.2, because it operates at a maximum pressure of ˜60 bar (CO.sub.2: typically 130 bar), which reduces back leakage of vapour in the compressor and provides operation on a subcritical cycle thus allowing efficient condensing heat transfer to ambient.

EXAMPLE 6

[0350] Calculations were performed for a non-flammable blend 26 with a GWP of 2 consisting of 10% R1224yd(Z), 67% CO.sub.2 and 23% R1234yf in a split air conditioning system (as shown in FIG. 4), operating under similar conditions to Example 5. The values of key parameters demonstrating the refrigerant performance are shown in Table 5. This blend is superior to R410A for air conditioning because it combines a GWP of only 2 with a suction volumetric capacity of 11156 kJ/kg (R410A: 5832 kJ/kg) but with a comparable energy efficiency. The blend is superior to CO.sub.2, because it operates at a maximum pressure of ˜60 bar (CO.sub.2: typically 130 bar) which reduces back leakage of vapour in the compressor and operates on a subcritical cycle which allows efficient condensing heat transfer to ambient.

EXAMPLE 7

[0351] Calculations were performed for a non-flammable blend 27 with a GWP of 2 consisting of 8% R1224yd(Z), 70% CO.sub.2 and 22% R1234ze(E) in the air conditioning system of an electrically powered vehicle (FIG. 5) comprising a single-stage hermetic compressor driven by a variable speed electric motor 2; a condenser 3; an internal heat exchanger (IHX) 4 transferring heat from the higher temperature, higher pressure refrigerant stream to the lower temperature, lower pressure refrigerant stream; an electronic expansion valve 5; an evaporator 6; and an accumulator 13 The refrigerant flow in the circuit included pressure and temperature sensors , 7 and 8, in the suction line immediately after the IHX 4.

[0352] The unit was controlled by a micro-processor 9, programmed with the thermodynamic properties of the refrigerant. The microprocessor received input data from the temperature sensor 11 via data line 10, the pressure sensor 10 via data line 11, and the temperature sensor 16 via data line 15 that measured the vehicle cabin temperature. The microprocessor transmitted output signals that varied the motor speed, via signal line 14, and the degree of opening of the expansion valve, via signal line 12, so the performance of the unit was optimised and matched to the required cabin temperature. In particular, the microprocessor ensured that the superheat of the refrigerant entering the compressor was at least 2 K and preferably 5 K to avoid potentially damaging wet compression.

[0353] The values of key parameters demonstrating the refrigerant performance for a blend consisting of 8% R1224yd(Z), 70% CO.sub.2 and 22% R1234ze(E) are shown in Table 6. This blend (nonflammable and GWP 2) is superior to both R134a (nonflammable but having a high GWP 1300) and its replacement R1234yf (very low GWP (2) but flammable) for vehicle air conditioning. It also benefits from a much higher suction specific volumetric capacity than these refrigerants. The blend is also superior to CO.sub.2, because it operates at a maximum pressure of ˜66 bar (CO.sub.2: 130 bar) which reduces back leakage of vapour in the compressor and operates on a subcritical cycle which allows efficient condensing heat transfer to ambient.

[0354] Table 7 also provides performance data for Blend 28 in an automobile air conditioning system.

EXAMPLE 8

[0355] The performances of blends 29 to 37 (Tables 7a and 7b) containing HFC152a in a low temperature refrigeration unit described in Example 4 were calculated. The results are shown in Table 7.

EXAMPLE 9

[0356] The performances of blends 38 to 42 retrofitted for HFC32 in an existing split air conditioner were calculate and compared with HFC32 (43 in Table 8b). The results are shown in Tables 8a and 8b. These blends provide acceptable energy efficiencies and suction cooling capacities compared to HFC32 with GWPs less than half that of HFC32, thus reducing the direct contribution of split airconditioner to global warming.

EXAMPLE 10

[0357] The performances of blends 44 to 45 (Table 9) in a refrigeration unit similar to that described in Example 4 were calculated. The results, shown in Table 9, show that good suction cooling capacities and efficiencies were obtained. The blends have GWPs less than 150, a value that is being mandated as the regulatory upper limit by some governments to force the phase-out of high GWP refrigerants, for such as R404A and R507A.

EXAMPLE 11

[0358] The performances of blends 48 to 51 (Table 10)) in a split air conditioning unit similar to that described in Example 3 were calculated. The results, shown in Table 10, show that good suction cooling capacities and efficiencies were obtained that comare favourably with existing refrigerant R410A and HFC32 that are presently used in this application. The blends have GWPs less than 150, a value that is being mandated as the regulatory upper limit by some governments to force the phase-out of high GWP refrigerants, for such as R410A and HFC32.

TABLE-US-00002 TABLE 1 Input R410A Cooling duty kW 1 Condenser Bubble point C. 40 Subcool K 5 Evaporator Dew point C. 7 Superheat K 5 Compressor Isentropic efficiency 0.7 Electric motor efficiency 0.9 Output Condenser Condenser midpoint C. 45.1 Condenser glide K 0.1 Evaporator Evaporator midpoint C. 7 Evaporator entry temperature C. 7 Evaporator glide K 0.1 Flow rate kg/(kWc) 0.00613 Compressor Discharge temperature C. 76.4 Discharge pressure bara 27.3 System COP 3.91 Suction capacity kJ/m{circumflex over ( )}3 5832

TABLE-US-00003 TABLE 2 Input R404A Cooling duty kW 1 Condenser Bubble point C. 35 Subcool K 5 Evaporator Dew point C. −35 Superheat K 5 Compressor Isentropic efficiency 0.7 Electric motor efficiency 0.9 Output Condenser Condenser midpoint C. 35.2 Condenser glide K 0.4 Evaporator Evaporator midpoint C. −35.2 Evaporator entry temperature C. −35.5 Evaporator glide K 0.5 Flow rate kg/(s.kW) 0.00937 Compressor Discharge temperature C. 77.8 Discharge pressure bara 16.2 System COP 1.49 Suction capacity kJ/m{circumflex over ( )}3 855

TABLE-US-00004 TABLE 3a Composition (mass fraction) Blend: 1 2 3 4 5 6 HFO1224yd(Z) 0.08 0.08 0.12 0.12 0.08 0.08 carbon dioxide 0.35 0.4 0.4 0.3 0.24 0.22 HFO1234yf 0.36 0.36 0.37 0.43 0.53 0.58 HFC227ea 0 0 0 0 0 0 HFC1234ze(E) 0.15 0.1 0.05 0.05 0.1 0.05 HFC32 0 0 0 0.1 0.05 0.07 HFO1336mzzz 0 0 0 0 0 0 HFO1234zez 0 0 0 0 0 0 HFO1233zd(E) 0.06 0.06 0.06 0 0 0 GWP 1 1 1 69 35 48 Input Condenser Exit temperature C. 40 40 40 40 40 40 Exit quality m/m 0 0 0 0 0 0 IHX high pressure condensation Liquid exit/suction entry difference kJ/kg 5 5 5 5 5 5 Evaporator Entry temperature C. 7 7 7 7 7 7 Exit temperature C. 18 18 18 18 18 18 Exit quality m/m 0.9 0.9 0.9 0.9 0.9 0.9 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 0.9 0.9 Enthalpy removed by heat pipe 0.1436 0.1436 0.1446 0.1398 0.1338 0.1351 Output Condenser Pressure bara 44.09 48.1 48.47 41.18 35.71 34.36 Dew point C. 75.2 73.4 75.5 68.5 69.6 68.2 Mid point C. 57.6 56.7 57.8 54.3 54.8 54.1 Glide K 35.2 33.4 35.5 28.5 29.6 28.2 Enthalpy loss kW 1.26 1.262 1.285 1.189 1.181 1.164 IHX high pressure side Enthalpy transferred from suction line kJ/kWc 0.115 0.115 0.114 0.117 0.192 0.185 Bubble point C. 40 40 40 40 40 40 Exit temperature C. 31.3 31.7 31.8 31 23 23.8 Evaporator Entry pressure bara 19.44 21.68 21.96 18.01 16.12 15.28 Midpoint C. 12.5 12.5 12.5 12.5 12.5 12.5 Glide C. 11 11 11 11 11 11 Exit pressure bara 10.25 11.85 11.31 11.59 9.73 9.71 Enthalpy gain kWc 1 1 1 1 1 1 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 0.115 0.115 0.114 0.117 0.192 0.185 Exit temperature C. 21.4 21.7 21.9 21.2 26 24.8 Dew point C. 24.3 25.2 26 23.4 21.6 21.4 Compressor Entry temperature to compressor C. 21.4 21.7 21.9 21.2 26 24.8 Discharge temperature C. 81.9 82.3 84.7 73.6 81.1 77.2 Compression ratio P/P 4.3 4.06 4.29 3.55 3.67 3.54 System Suction specific volume kJ/m{circumflex over ( )}3 5017 5558 5265 5821 5248 5270 Electrical energy input kJ/kWc 0.234 0.236 0.256 0.17 0.163 0.148 COP cooling 4.28 4.24 3.9 5.88 6.14 6.77 Mass flow rate kg/kWc 0.00718 0.00718 0.00723 0.00699 0.00669 0.00676

TABLE-US-00005 TABLE 3b Composition (mass fraction) Blend: 7 8 9 10 11 12 HFO1224yd(Z) 0.08 0.08 0 0.08 0.08 0.1 carbon dioxide 0.35 0.19 0.19 0.05 0.1 0.12 HFO1234yf 0.36 0.41 0.46 0.25 0.42 0.42 HFC227ea 0 0 0 0 0.05 0 HFC1234ze(E) 0 0.1 0 0.11 0.05 0.05 HFC32 0.15 0.16 0.21 0.45 0.3 0.25 HFO1336mzzz 0 0 0 0 0 0 HFO1234zez 0 0 0 0 0 0 HFO1233zd(E) 0.06 0.06 0.14 0.06 0 0.06 GWP 102 109 143 305 364 170 Input Condenser Exit temperature C. 40 40 40 40 40 40 Exit quality m/m 0 0 0 0 0 0 IHX high pressure condensation Liquid exit/suction entry difference kJ/kg 5 5 5 5 5 5 Evaporator Entry temperature C. 7 7 7 7 7 7 Exit temperature C. 18 18 18 18 18 18 Exit quality m/m 0.9 0.9 0.9 0.9 0.9 0.9 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 0.9 0.9 Enthalpy removed by heat pipe 0.0646 0.131 0.1273 0.0543 0.1218 0.1243 Output Condenser Pressure bara 45.12 32.31 32.95 23.58 26.58 27.4 Dew point C. 66.6 67.8 66.7 54 56.4 63.1 Mid point C. 53.3 53.9 53.3 47 48.2 51.5 Glide K 26.6 27.8 26.7 14 16.4 23.1 Enthalpy loss kW 1.218 1.164 1.161 1.089 1.074 1.123 IHX high pressure side Enthalpy transferred from suction line kJ/kWc 0.144 0.144 0.139 0.158 0.176 0.157 Bubble point C. 40 40 40 40 40 40 Exit temperature C. 28.8 27.2 27.6 23 23 24.9 Evaporator Entry pressure bara 20.46 13.81 14.16 9.83 11.31 11.61 Midpoint C. 12.5 12.5 12.5 12.5 12.5 12.5 Glide K 11 11 11 11 11 11 Exit pressure bara 13.48 9.07 9.64 9.4 10 8.64 Enthalpy gain kWc 1 1 1 1 1 1 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 0.144 0.144 0.139 0.158 0.176 0.157 Exit temperature C. 22.9 21.8 22.2 23.5 25.6 22.2 Dew point C. 25 22.7 23.7 21.5 20.8 22.5 Compressor Entry temperature to compressor C. 22.9 21.8 22.2 23.5 25.6 22.2 Discharge temperature C. 82 72.9 72.5 62.7 62.9 68.1 Compression ratio P/P 3.35 3.56 3.42 2.51 2.66 3.17 System Suction specific volume kJ/m{circumflex over ( )}3 6893 5048 5326 6117 5932 5086 Electrical energy input kJ/kWc 0.254 0.148 0.145 0.129 0.067 0.11 COP cooling 3.94 6.77 6.9 7.78 14.97 9.06 Mass flow rate kg/kWc 0.00646 0.00655 0.00637 0.00543 0.00609 0.00621

TABLE-US-00006 TABLE 4a Composition (mass fraction) 13 14 15 16 17 18 HFO1224ydz 0 0.25 0.11 0.13 0 0.1 carbon dioxide 0.4 0.4 0.35 0.3 0.21 0.3 HFO1234yf 0.6 0 0.18 0.03 0.12 0.14 HFC227ea 0 0 0 0 0 0 HFC1234ze(E) 0 0.35 0.23 0.28 0.28 0.12 HFC32 0 0 0 0.1 0.13 0.08 HFO1336mzzz 0 0 0.13 0.16 0.16 0.16 HFO1233zd(E) 0 0 0 0 0.1 0.1 Cooling Duty kW 1 1 1 1 1 1 GWP 1 1 1 69 89 55 Input Condenser Exit temperature C. 30 30 30 30 30 30 Exit quality m/m 0 0 0 0 0 0 IHX high pressure condensation Liquid exit/suction entry difference K 5 5 5 5 5 5 Evaporator Entry temperature C. −35 −35 −35 −35 −35 −35 Exit temperature C. −30 −30 −30 −30 −30 −30 Exit quality m/m 0.8 0.7 0.7 0.7 0.6 0.6 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 0.9 0.9 Discharge temperature—dew point diff K 5 5 5 5 5 5 Heat removed from compressor kJ/kWc 0.262 0.318 0.323 0.302 0.284 0.289 Refrigerant flow cooling compressor × 10.sup.3 kg/kWc 8.74 9.09 9.24 8.63 9.47 9.64 Output Condenser Pressure bara 40.72 39.70 37.02 33.63 27.38 34.27 Entry quality kg/kg 0.492 0.395 0.390 0.387 0.345 0.345 Mid point C. 37.6 38.9 39.4 39.2 38.5 38.6 Glide K 15.2 17.8 18.8 18.3 17.0 17.2 Enthalpy loss kW 1.66 1.73 1.76 1.64 1.80 1.83 IHX high pressure side Enthalpy transferred from suction line kJ/kWc 0.658 1.056 1.138 1.055 1.389 1.509 Exit temperature C. 9.0 −5.2 −8.6 −8.5 −18.5 −21.1 Evaporator Entry pressure bara 6.28 6.63 6.29 5.37 4.42 6.15 Midpoint C. −32.5 −32.5 −32.5 −32.5 −32.5 −32.5 Glide K 5 5 5 5 5 5 Exit pressure bara 3.34 2.79 2.59 2.32 2.26 3.41 Enthalpy gain kWc 1.000 1.000 1.000 1.000 1.000 1.000 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 0.658 1.056 1.138 1.055 1.389 1.509 Exit temperature −5.4 −1.6 11.4 5.7 11.2 19.2 Dew point −22.8 −4.3 0.3 0.8 2.3 13.1 Compressor Entry temperature to compressor C. −5.4 −1.6 11.4 5.7 11.2 19.2 Discharge temperature C. 79.5 80.9 85.3 82.9 81.1 88.4 Compression ratio P/P 12.17 14.25 14.27 14.50 12.12 10.04 System Suction specific volume kJ/m{circumflex over ( )}3 1391 1123 1043 994 914 1269 Electrical energy input kJ/kWc 0.595 0.596 0.589 0.561 0.560 0.553 COP cooling 1.68 1.68 1.70 1.78 1.79 1.81 Mass flow rate × 10.sup.3 kg/kWc 8.74 9.09 9.24 8.63 9.47 9.64

TABLE-US-00007 TABLE 4b Composition (mass fraction) 19 20 21 22 23 24 HFO1224yd(Z) 0.05 0.15 0 0.15 0 0.17 carbon dioxide 0.14 0.1 0.11 0.1 0.1 0.08 HFO1234yf 0.1 0.22 0.25 0.35 0.19 0.15 HFC227ea 0 0 0 0 0.1 0.03 HFO1234ze(E) 0.31 0.32 0.22 0 0.2 0.13 HFC32 0.22 0.21 0.2 0.4 0.2 0.3 HFO1336mzzz 0.08 0 0.12 0 0.11 0.04 HFO1233zd(E) 0.1 0 0.1 0 0.1 0.1 Cooling Duty kW 1 1 1 1 1 1 GWP 150 143 136 271 456 300 Input Condenser Exit temperature C. 30 30 30 30 30 30 Exit quality m/m 0.1 0 0 0 0 0 IHX high pressure condensation Liquid exit/suction entry difference K 5 5 5 5 5 5 Evaporator Entry temperature C. −35 −35 −35 −35 −35 −35 Exit temperature C. −30 −30 −30 −30 −30 −30 Exit quality m/m 0.6 0.7 0.6 0.6 0.7 0.7 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 0.9 0.9 Discharge temperature—dew point diff K 5 5 5 5 5 5 Heat removed from compressor kJ/kWc 0.248 0.174 0.169 0.150 0.119 0.111 Refrigerant flow cooling compressor × 10.sup.3 kg/kWc 4.14 1.39 4.23 3.74 1.59 1.48 Output Condenser Pressure bara 21.20 19.82 20.62 22.18 20.00 19.31 Entry quality kg/kg 0.604 0.880 0.567 0.642 0.841 0.840 Mid point C. 39.9 41.7 40.2 35.7 44.7 43.1 Glide K 19.8 23.4 20.5 11.4 29.3 26.3 Enthalpy loss kW 1.57 1.32 1.61 1.42 1.51 1.41 IHX high pressure side Enthalpy transferred from suction line kJ/kWc 1.175 0.649 1.016 0.891 0.630 0.583 Exit temperature C. −23.4 −23.2 −25.0 −20.7 −15.5 −14.7 Evaporator Entry pressure bara 3.47 2.84 3.13 3.08 2.72 2.54 Midpoint C. −32.5 −32.5 −32.5 −32.5 −32.5 −32.5 Glide C. 5 5 5 5 5 5 Exit pressure bara 1.97 1.57 1.80 2.55 1.41 1.53 Enthalpy gain kWc 1.000 1.000 1.000 1.000 1.000 1.000 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 1.175 0.649 1.016 0.891 0.630 0.583 Exit temperature 7.6 −11.9 −6.4 −16.1 −13.9 −14.5 Dew point −5.5 −18.4 −5.0 −15.7 −9.8 −10.2 Compressor Entry temperature to compressor C. 7.6 −11.9 −6.4 −16.1 −13.9 −14.5 Discharge temperature C. 68.2 61.0 70.3 67.5 69.6 66.6 Compression ratio P/P 10.78 12.61 11.48 8.69 14.17 12.63 System Suction specific volume kJ/m{circumflex over ( )}3 925 971 890 1274 796 883 Electrical energy input kJ/kWc 0.439 0.395 0.521 0.466 0.559 0.525 COP cooling 2.28 2.53 1.92 2.14 1.79 1.90 Mass flow rate × 10.sup.3 kg/kWc 8.28 6.96 8.45 7.48 7.97 7.41

TABLE-US-00008 TABLE 5 Composition (mass fraction) 25 26 HFO1224yd(Z) 0.05 0.1 carbon dioxide 0.69 0.67 HFO1234yf 0 0.23 HFO1234ze(E) 0.26 0 Condenser Exit temperature C. 35 35 Exit quality m/m 0.0618 0.0618 IHX high pressure condensation Liquid exit/suction entry kJ/kg 5.00 5.00 difference Evaporator Entry temperature C. 10 10 Exit temperature C. 18 18 Exit quality m/m 0.900 0.900 Compressor Isentropic efficiency 0.7 0.7 Electric motor efficiency 0.9 0.9 Output Condenser Pressure bara 60.42 60.67 Dew point C. 53.27 52.95 Mid point C. 44.13 43.97 Glide K 18.3 17.9 Enthalpy loss kW 1.346 1.333 Exit quality 0.062 0.062 IHX high pressure side Enthalpy transferred from kJ/kWc 0.223 0.237 suction line Bubble point C. 34.5 34.5 Exit temperature C. 23.0 22.6 Evaporator Entry pressure bara 35.12 35.45 Midpoint C. 14 14 Glide C. 8 8 Exit pressure bara 24.82 26.62 Enthalpy gain kWc 1.000 1.000 IHX low pressure side Enthalpy transferred to liquid kW/kWc 0.223 0.237 line Exit temperature 30.0 31.4 Dew point 25.0 26.6 Compressor Entry temperature to compressor C. 30.0 31.4 Discharge temperature C. 108.9 103.6 Compression ratio P/P 2.43 2.28 System Suction specific volume kJ/m{circumflex over ( )}3 10780 11156 Electrical energy input kJ/kWc 0.311 0.297 COP cooling 3.21 3.37 Mass flow rate kg/kWc 0.00587 0.00623

TABLE-US-00009 TABLE 6 Composition (mass fraction) HFO1224ydz 0.08 0.1 carbon dioxide 0.7 0.7 HFO1234yf 0 0.2 HFO1234zee 0.22 0 GWP 2 2 Cooling duty kW 1 1 Input Condenser Exit temperature C. 35 35 Exit quality m/m 0.0228 0.0605 IHX high pressure condensation Liquid exit/suction entry kJ/kg 5.00 5.00 difference Evaporator Entry temperature C. 10 10 Exit temperature C. 18 18 Exit quality m/m 0.923 0.923 Compressor Isentropic efficiency 0.7 0.7 Electric motor efficiency 0.9 0.9 Output Condenser Pressure bara 61 61 Dew point C. 53.04 51.32 Mid point C. 44.02 43.16 Glide K 18.0 16.3 Enthalpy loss kW 1.363 1.349 Exit quality 0.023 0.061 IHX high pressure side Enthalpy transferred from kJ/kWc 0.184 0.193 suction line Bubble point C. 34.8 34.5 Exit temperature C. 24.0 26.0 Evaporator Entry pressure bara 35.26 35.17 Midpoint C. 14 14 Glide C. 8 8 Exit pressure bara 24.01 25.63 Enthalpy gain kWc 1.000 1.000 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 0.184 0.193 Exit temperature 29.4 29.6 Dew point 24.4 24.4 Compressor Entry temperature to compressor C. 29.4 29.6 Discharge temperature C. 113.2 106.4 Compression ratio P/P 2.55 2.38 System Suction specific volume kJ/m{circumflex over ( )}3 10484 10753 Electrical energy input kJ/kWc 0.327 0.314 COP cooling 3.06 3.19 Mass flow rate kg/kWc 0.00578 0.00613

TABLE-US-00010 TABLE 7a Composition (mass fraction) 29 30 31 32 33 carbon dioxide 0.4 0.4 0.4 0.38 0.38 HFO1224ydz 0.1 0.1 0.08 0.08 0.08 HFO1234yf 0.42 0.4 0.38 0.37 0.37 HFC1234zee 0.05 0.08 0.12 0.12 0.12 HFC152a 0.03 0.02 0.02 0.05 0.025 HFC227ea 0 0 0 0 0.045 HFC32 0 0 0 0 0 Output kW 1 1 1 1 1 GWP 7 6 6 10 150 Input Condenser Exit temperature C. 30 30 30 30 30 Exit quality m/m 0 0 0 0 0 ICEX high pressure condensation Liquid exit/suction entry difference kJ/kg 5 5 5 5 5 Evaporator Entry temperature C. −35 −35 −35 −35 −35 Exit temperature C. −30 −30 −30 −30 −30 Exit quality m/m 1 1 1 1 1 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 0.9 Enthalpy removed from compressor kW/kWc 0.417 0.418 0.416 0.409 0.425 Output Condenser Pressure bara 40.13 40.14 39.91 38.22 38.36 Dew point C. 63.7 63.8 62.8 63.3 63.7 Mid point C. 46.8 46.9 46.4 46.6 46.8 Glide K 33.7 33.8 32.8 33.3 33.7 Enthalpy loss kW 1.673 1.675 1.634 1.613 1.605 Exit quality 0.000 0.000 0.000 0.000 0.000 IHX high pressure side Enthalpy transferred to suction line kJ/kWc 0.028 0.028 0.028 0.028 0.028 Bubble point C. 30.0 30.0 30.0 30.0 30.0 Exit temperature C. 27.9 27.9 27.9 27.8 27.8 Evaporator Entry pressure bara 5.00 4.99 4.90 4.48 4.48 Midpoint C. −32.5 −32.5 −32.5 −32.5 −32.5 Glide C. 5 5 5 5 5 Exit pressure bara 1.54 1.53 1.63 1.55 1.52 Enthalpy gain kWc 1.000 1.000 1.000 1.000 1.000 Exit quality 1.000 1.000 1.000 1.000 1.000 IHX low pressure side Enthalpy transferred from liquid line kW/kWc 0.028 0.028 0.028 0.028 0.028 Exit temperature C. −25.0 −25.0 −25.0 −25.0 −25.0 Dew point C. −30.0 −30.0 −30.0 −30.0 −30.0 Compressor Entry temperature to casing C. −25.0 −25.0 −25.0 −25.0 −25.0 Discharge temperature C. 111.7 111.8 106.7 104.6 101.3 Compression ratio P/P 26.01 26.32 24.51 24.62 25.30 Compressor cooling kW/kWc 0.4165 0.4180 0.4161 0.4093 0.4253 System Suction specific volume kJ/m{circumflex over ( )}3 733 725 779 760 736 Electrical energy input kJ/kWc 0.606 0.608 0.570 0.551 0.545 COP cooling 1.65 1.65 1.75 1.81 1.84 Mass flow rate kg/kWc 0.00694 0.00697 0.00693 0.00682 0.00709

TABLE-US-00011 TABLE 7b Composition (mass fraction) 34 35 36 37 carbon dioxide 0.405 0.385 0.39 0.39 HFO1224ydz 0.08 0.07 0.07 0.07 HFO1234yf 0.37 0.37 0.32 0.28 HFO1234zee 0.12 0.15 0.22 0.22 HFC152a 0.025 0.025 0 0.04 HFC227ea 0.045 0.035 0.03 0.03 HFC32 0.05 0.08 0.075 0.06 Output kW 1 1 1 1 GWP 184 173 150 145 Input Condenser Exit temperature C. 30 30 30 30 Exit quality m/m 0 0 0 0 ICEX high pressure condensation Liquid exit/suction entry difference kJ/kg 5 5 5 5 Evaporator Entry temperature C. −35 −35 −35 −35 Exit temperature C. −30 −30 −30 −30 Exit quality m/m 1 1 1 1 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 Enthalpy removed from compressor kW/kWc 0.412 0.407 0.410 0.398 Output Condenser Pressure bara 38.39 36.79 37.27 36.97 Dew point C. 61.3 60.3 60.6 61.2 Mid point C. 45.6 45.1 45.3 45.6 Glide K 31.3 30.3 30.6 31.2 Enthalpy loss kW 1.595 1.546 1.562 1.577 Exit quality 0.000 0.000 0.000 0.000 IHX high pressure side Enthalpy transferred to suction line kJ/kWc 0.028 0.028 0.028 0.027 Bubble point C. 30.0 30.0 30.0 30.0 Exit temperature C. 27.9 27.8 27.8 27.8 Evaporator Entry pressure bara 4.62 4.30 4.38 4.28 Midpoint C. −32.5 −32.5 −32.5 −32.5 Glide C. 5 5 5 5 Exit pressure bara 1.63 1.67 1.63 1.59 Enthalpy gain kWc 1.000 1.000 1.000 1.000 Exit quality 1.000 1.000 1.000 1.000 IHX low pressure side Enthalpy transferred from kW/kWc 0.028 0.028 0.028 0.027 liquid line Exit temperature C. −25.0 −25.0 −25.0 −25.0 Dew point C. −30.0 −30.0 −30.0 −30.0 Compressor Entry temperature to casing C. −25.0 −25.0 −25.0 −25.0 Discharge C. 102.7 96.8 98.9 102.5 temperature Compression ratio 23.51 22.07 22.80 23.29 P/P Compressor cooling kW/kWc 0.4120 0.4072 0.4095 0.3985 System Suction specific kJ/m{circumflex over ( )}3 796 829 810 797 volume Electrical energy kJ/kWc 0.536 0.492 0.506 0.519 input COP cooling 1.87 2.03 1.98 1.93 Mass flow rate kg/kWc 0.00687 0.00679 0.00683 0.00664

TABLE-US-00012 TABLE 8a Composition mass % 38 39 40 carbon dioxide 12 11 8 HFO1234yf 45 40 45 HFC32 38 44 42 HFO1224ydz 5 5 5 GWP 259 300 286 Input Cooling duty kW 1 1 1 Condenser Bubble point C. 45 45 45 Subcool kJ/kg 5 5 5 Evaporator Dew point C. 13 13 13 Superheat C. 5 5 5 Compressor Isentropic efficiency 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 Output Condenser Pressure bara 32.3 32.1 29.3 Dew point C. 57.3 55.8 55.0 Bubble point C. 45 45 45 Mid point C. 51.1 50.4 50.0 Glide K 12.3 10.8 10.0 Exit temperature C. 40 40 40 Heat out kW −1.36 −1.34 −1.33 Evaporator Pressure bara 9.76 10.13 9.43 Entry temperature C. 1.51 2.77 3.50 Dew point C. 13 13 13 Mid point C. 7.3 7.9 8.2 Glide K 11.5 10.2 9.5 Exit temperature C. 18 18 18 Heat in kW 1 1 1 Compressor Entry temperature to casing C. 18 18 18 Entry temperature to compressor C. 23.74 23.59 23.29 Discharge temperature C. 100.5 99.6 95.2 Compression ratio 3.31 3.17 3.11 Total power input kW 0.32 0.31 0.29 Swept volume m{circumflex over ( )}3/h 0.66 0.63 0.66 System Suction specific volume kJ/m{circumflex over ( )}3 5451 5732 5421 COP cooling 3.13 3.28 3.41 Mass flow rate kg/s 0.00585 0.00563 0.00578

TABLE-US-00013 TABLE 8b Composition mass % 41 42 43 carbon dioxide 16 8 100 HFO1234yf 39 50 0 HFC32 40 40 0 HFO1224ydz 5 2 0 GWP 273 273 677 Input Cooling duty kW 1 1 1 Condenser Bubble point C. 45 45 45 Subcool kJ/kg 5 5 5 Evaporator Dew point C. 13 13 7 Superheat C. 5 5 5 Compressor Isentropic efficiency 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 Output Condenser Pressure bara 35.8 29.2 27.9 Dew point C. 57.8 54.2 45 Bubble point C. 45 45 45 Mid point C. 51.4 49.6 45 Glide K 12.8 9.2 0 Exit temperature C. 40 40 40 Heat out kW −1.37 −1.31 −1.28 Evaporator Pressure bara 10.69 9.78 10.12 Entry temperature C. 0.71 4.78 7 Dew point C. 13 13 7 Mid point C. 6.9 8.9 7 Glide K 12.3 8.2 0 Exit temperature C. 18 18 12 Heat in kW 1 1 1 Compressor Entry temperature to casing C. 18 18 12 Entry temperature to compressor C. 24.08 22.90 17.69 Discharge temperature C. 105.6 91.3 99.4 Compression ratio 3.35 2.99 2.76 Total power input kW 0.33 0.28 0.25 Swept volume m{circumflex over ( )}3/h 0.62 0.64 0.57 System Suction specific volume kJ/m{circumflex over ( )}3 5848 5608 6345 COP cooling 3.00 3.54 3.99 Mass flow rate kg/s 0.00568 0.00592 0.00404

TABLE-US-00014 TABLE 9 Composition (mass fraction) 44 45 46 47 carbon dioxide 0.15 0.2 0.13 0.25 HFO1224ydz 0.14 0.14 0.14 0.1 HFC32 0.21 0.21 0.21 0.21 HFO1234ze(E) 0.5 0.45 0.52 0.44 Cooling duty kW 1 1 1 1 GWP 146 145 146 145 Cooling duty kW 1 1 1 1 Input Condenser Exit temperature C. 30 30 30 30 Exit quality m/m 0.1 0.1 0.1 0.2 ICEX high pressure condensation Liquid exit/suction entry difference kJ/kg 5 5 5 5 Evaporator Entry temperature C. −35 −35 −35 −35 Exit temperature C. −30 −30 −30 −30 Exit quality m/m 0.8 0.8 0.8 0.8 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 Enthalpy removed from compressor kW/kWc 0.166 0.193 0.201 0.209 Output Condenser Pressure bara 21.33 24.85 19.91 26.51 Dew point C. 57.2 58.7 56.3 55.3 Mid point C. 43.6 44.4 43.2 42.6 Glide K 27.2 28.7 26.3 25.3 Enthalpy loss kW 1.666 1.650 1.590 1.708 Exit quality 0.100 0.100 0.100 0.200 IHX high pressure side Enthalpy transferred to suction line kJ/kWc 0.455 0.464 0.451 0.516 Bubble point C. 26.8 27.1 26.8 24.5 Exit temperature C. −4.4 −5.8 −3.8 5.0 Evaporator Entry pressure bara 2.88 3.59 2.60 3.87 Midpoint C. −32.5 −32.5 −32.5 −32.5 Glide C. 5 5 5 5 Exit pressure bara 1.37 1.63 1.28 2.00 Enthalpy gain kWc 1.000 1.000 1.000 1.000 Exit quality 0.800 0.800 0.800 0.800 ICEX low pressure side Enthalpy transferred from liquid line kW/kWc 0.455 0.464 0.451 0.516 Exit temperature C. −16.8 −15.3 −17.4 −15.2 Dew point C. −21.8 −20.3 −22.4 −20.2 Compressor Entry temperature to casing C. −16.8 −15.3 −17.4 −15.2 Discharge temperature C. 114.5 118.1 101.5 118.2 Compression ratio P/P 15.56 15.26 15.53 13.28 Compressor cooling kW/kWc 0.1660 0.1930 0.2019 0.2097 System Suction specific volume kJ/m{circumflex over ( )}3 744 861 708 922 Electrical energy input kJ/kWc 0.600 0.585 0.531 0.637 COP cooling 1.67 1.71 1.88 1.57 Mass flow rate kg/kWc 0.00664 0.00643 0.00673 0.00699

TABLE-US-00015 TABLE 10 Composition (mass fraction) carbon dioxide 0.17 0.17 0.17 0.19 HFO1234yf 0.57 0.52 0.47 0.48 HFC32 0.21 0.21 0.21 0.18 HFO1234yd(Z) 0.05 0.01 0.15 0.15 GWP 145 145 145 124 Cooling duty kW Input Condenser Exit temperature C. 40 40 40 40 Exit quality m/m 0.05 0.05 0.05 0.05 Evaporator Entry temperature C. 1 1 3 3 Exit temperature C. 16 16 16 16 Exit quality m/m 1 1 1 1 Compressor Isentropic efficiency 0.7 0.7 0.7 0.7 Electric motor efficiency 0.9 0.9 0.9 0.9 Enthalpy removed from compressor kW/kWc 0.031 0.030 0.030 0.030 Output Condenser Pressure bara 31.83 32.75 33.76 35.30 Dew point C. 56.1 55.9 55.6 57.1 Mid point C. 48.1 48.0 47.8 48.5 Glide K 16.1 15.9 15.6 17.1 Enthalpy loss kW 1.283 1.284 1.285 1.303 Exit quality 0.050 0.050 0.050 0.050 IHX high pressure side Enthalpy transferred from suction line kJ/kWc 0.123 0.121 0.120 0.122 Bubble point C. 38.9 39.0 39.0 39.0 Exit temperature C. 32.8 33.0 33.1 33.0 Evaporator Entry pressure bara 11.07 11.46 12.67 13.35 Midpoint C. 8.5 8.5 9.5 9.5 Glide C. 15 15 13 13 Exit pressure bara 11.03 11.43 11.88 11.94 Pressure drop bar 0.04 0.03 0.79 1.41 Enthalpy gain kWc 1.000 1.000 1.000 1.000 Exit quality 1.000 1.000 1.000 1.000 IHX low pressure side Enthalpy transferred to liquid line kW/kWc 0.123 0.121 0.120 0.122 Exit temperature C. 34.9 34.8 34.6 34.8 Dew point C. 16.0 16.0 16.0 16.0 Compressor Entry temperature to compressor C. 34.9 34.8 34.6 34.8 Discharge temperature C. 98.9 99.6 100.4 103.3 Compression ratio P/P 2.88 2.87 2.84 2.96 Compressor cooling kW/kWc 0.0306 0.0303 0.0300 0.0304 System Suction specific volume kJ/m{circumflex over ( )}3 5785 5952 6142 6077 Electrical energy input kJ/kWc 0.255 0.256 0.257 0.273 COP cooling 3.93 3.91 3.90 3.67 Mass flow rate kg/kWc 0.00613 0.00607 0.00600 0.00608