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1. Based on heat transferred by coil (outdoor=ht from envir.; indoor= ht from envir+comp pwr) 2. Most conservative (i.e. lowest calculated heat transfer coefficient) as compared to CO2 specific correlations (Pitla et al., 1998) 3. Based on results from Kirkwood et al. (1999) 4. RAC2 simulation results (Yin, 2000) 5. Calculated values from Radermacher-Hwang range from 7500-22,600 for operating condition 6. Calculated from Chang-Wang correlation 7. Experimental R410A baseline results 4.2 Compressor assumptions 4.2.1 Isentropic and volumetric efficiency To incorporate the effect of a real compressor into the cycle analysis a linear fit to compressor data is used for volumetric and isenetropic efficiencies. The type of compressor selected for each refrigerant is: a commercially available hermetic scroll compressor for R410A and a semi-hermetic prototype reciprocating compressor for R744. The isentropic efficiency model for the R410A compressor is based on manufacturer’s data for a 3 ton compressor, and this fit is compared with the measured performance of a similar compressor by Stott (1999) in Figure 4.1. The R744 fit is based on measured results of a 50 Hz prototype reciprocating compressor (Neksa, 1999). In Figure 4.2 its isentropic efficiency is compared with data from a very similar prototype compressor used in the RAC1 experimental results, which included losses of unknown magnitude attributable to a frequency converter. Experimental results from two open automotive compressors are also shown. In the cycle analysis it is assumed that no heat is rejected from the compressor to the surroundings. 1.0 0.9 0.8 0.7 0.6 0.5 0.4 0.3 0.2 0.1 0.0 Figure 4.1 R410A compressor efficiency 2 ton scroll, measured (Stott, 1998) Best fit, 3 ton compressor 1234567 Compression Ratio 24 Isentropic EfficiencyPDF Image | Comparison of R744 and R410A
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