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Heat Output Compressor Work Input Run (kW) 1 10.975 2 10.968 3 11.136 4 11.171 5 11.443 6 11.549 7 11.699 8 11.740 9 11.780 10 11.795 11 11.688 12 11.789 13 11.686 14 1.115 (kW) COPhp 2.958 3.71 2.952 3.72 2.964 3.76 2.964 3.77 3.018 3.79 3.026 3.82 2.992 3.91 2.998 3.92 3.004 3.92 2.998 3.93 2.99 3.91 3.022 3.90 3.022 3.87 1.666 0.669 Figure 4: T-S diagram of the average output values at full charge. After reducing the amount of charge, the output of the system as seen in table 2 and 3 (run 14) was inferior to the other outputs. In fact its COP was less than 1 meaning that the heat gained is less than the amount of power used. This is a very undesirable and unrealistic output which defies the basic advantage of using a heat pump in the first place. A further analysis of the system shows that the system underwent a complete cycle in the superheated state. Figure 5 presents the cycle in a T- S diagram as drawn by the simulating software. The fact that the refrigerant in this cycle didn’t undergo any phase change also contributes to its inefficiency. The evaporator in the system under study was designed considering the properties of a wet vapor. When a superheated fluid is passed through it, definitely its efficiency will greatly reduce and thus the output. The same applies to the throttle valve and other system 323PDF Image | TYPICAL INITIAL OUTPUT OF A CO2 HEAT PUMP
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