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2 1 0 7400 7500 7600 7700 7800 7900 8000 8100 8200 8300 8400 8500 Discharge Pressure (kPa) Figure B.4 Evaporating temperature (at inlet to evaporator) To get an idea of the effectiveness of the suction accumulator, we can look at the estimated ratio of heat transfer in the suction line heat exchanger from the high pressure side to the low pressure side. Since the refrigerant on the low-pressure side is assumed to be vapor, a change of phase of liquid in the suction line heat exchanger will reduce the calculated heat transfer and result in a ration greater than one. Figure B.5 shows the ratio of high- pressure side to low-pressure side heat transfer in the suction accumulator. The results from the re-orientated/no suction accumulator adjustment are very close to one indicating that very little phase change occurred within the suction line heat exchanger and that the system was optimally charged. Except for the lowest and highest discharge pressure points in the re-orientated/suction accumulator adjusted data, which were both taken after additional charge was added to the system, there appears to be slightly less of a dependence on the discharge pressure as compared to the results compared with R410A. This indicates that the exit quality from the suction accumulator is more consistent since the vapor line/liquid line intersection was relocated. Also, to note, during the re-orientated coil/suction accumulator adjusted testing, to prevent surging (spikes in the refrigerant mass flow rate), the suction accumulator bypass valve (Appendix A, section 2.8) was open 1⁄4 of a turn more than in previous tests. This valve may not have been adjusted optimally during these runs. For reference, in earlier tests the valve was open 1/8 of a turn from fully closed. Comparison with R410A results Re-orientated indoor coil/No suct. acc. adjust. Re-orientated indoor coil/Suct. acc. adjust. 62 Evaporating Temperature (C)PDF Image | Comparison of R744 and R410A
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