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2205, Page 5 temperature glide of refrigerant is smaller than water temperature difference in the heat exchanger inlet and outlet. On the other hand, the calculation of type B is that temperature glide of refrigerant is larger as shown in Figure 4(b). The condensation and evaporation pressure is decided so that pinch points (temperature difference between refrigerant and water) become 0 K. 4. EXPERIMENTAL AND ANALYSIS RESULTS 4.1 Coefficient of performance (COP) Figure 5 shows coefficient of performance for heating mode 1 and heating mode 2 in the experiment, where blue, red, green, purple and orange represent the results obtained for ternary 300, ternary 200, binary 300, binary 200 and R410A, respectively. The refrigerant charge is varied to find the maximum COP during the experiment. The optimized charge is determined as the refrigerant amount exhibits the highest COP at the most of conditions for each test refrigerant. The series of experimental data are obtained at that optimized refrigerant charge. For the heating mode 1, the COP of ternary300 and binery300 are comparable to that of R410A. The COP of ternary 200 and binary 200 are lower than that of R410A. For the heating mode 2, the COP trend due to differences in refrigerant is the same as that of heating mode 1. The difference in COP due to difference in refrigerant of heating mode 2 is, Figure 5: COP in the experiment Figure 6: COP in the analysis (a) Experimental result (b) Analysis result Figure 7: Irreversible loss in condenser Ternary300 Ternary200 Binary300 Binary200 R410A Water Heating mode1 340 330 320 310 300 0 0.5 1 1.5 2 QCOND [kW] (a) heating mode 1 340 330 320 310 300 0 0.5 1 1.5 2 QCOND [kW] (b) heating mode 2 Figure 8: Temperature distribution in condenser in experiment Ternary300 Ternary200 Binary300 Binary200 R410A Water Heating mode2 International Refrigeration and Air Conditioning Conference at Purdue, July 16-19, 2012 T [K] T [K]PDF Image | Experimental Assessment on Performance of a Heat Pump Cycle
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