CHAPTER 5 SUMMARY AND CONCLUSIONS
5.2 Conclusion for modeling study
On the modeling side, a single tube model is first developed using a thermodynamic approach to take account of the thermodynamic and transport properties of refrigerant-oil mixture and their impact on boiling heat transfer and pressure drop characteristics. Then a two tube model which is assembled by two single tube model is used to demonstrate how oil affects the flow resistance of each tube, and thus, affect distribution. After that, a heat exchanger model only considering lubricant effect among parallel microchannel tubes is developed and it have been shown that 1) high viscosity is detrimental for refrigerant distribution; 2) as OCR increases, distribution becomes worse but at very high OCR, distribution becomes better.
In order to improve the model by taking account of lubricant effects in the inlet header, attempts have been made to calculate refrigerant distribution inside of microchannel tubes reversely from the infrared image of the heat exchangers. As a result, a non-intrusive and low cost distribution quantification method has been developed correlating the liquid refrigerant distribution with evaporator air inlet temperature (measured by thermocouple) and evaporator wall temperature (measured by infrared camera). This method has been validated against wide range of experimental datas and it can be applied for different types of heat exchangers and various heat exchange designs.
The newly proposed distribution quantification method can serve the same role as a quality distribution function in a mircochannel heat exchanger model (If used as a distribution function, it cannot perform prediction because it comes from the infrared image taken in the experiment.
So this method is mainly used as a quantification tool for refrigerant distribution), by this means the lubricant effect in the inlet header is taken into account. Combining the distribution function reversely calculated from the infrared image with the parallel tubes model introduced earlier, a complete heat exchanger model is formed fully incorporating lubricant effects. This model is validated against the experimental data (shown in appendix) and better prediction of performance has been confirmed over pure refrigerant models especially at high OCR’s.
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APPENDIX
Experimental results
Table A-1 Experimental results of R134a and PAG46 pair in HX1
OCR Qe Qair Qref Wc isen COPave COPair COPref mtotal xin
Table A-2 Experimental results of R134a and PAG46 pair in HX2
OCR Qe Qair Qref Wc isen COPave COPair COPref mtotal xin
Table A-3 Experimental results of R134a and PAG100 pair in HX2
OCR Qe Qair Qref Wc isen COPave COPair COPref mtotal xin
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Table A-4 Experimental results of R134a and PAG150 pair in HX2
OCR Qe Qair Qref Wc isen COPave COPair COPref mtotal xin 0.1% 2.271 2.300 2.241 1.256 0.414 1.807 1.830 1.784 14.28 0.253 0.5% 2.324 2.352 2.295 1.218 0.460 1.908 1.931 1.885 14.83 0.252 2.8% 2.346 2.357 2.335 1.109 0.574 2.116 2.126 2.106 15.83 0.244 6.2% 2.183 2.168 2.197 1.092 0.582 1.999 1.986 2.012 16.09 0.246 7.8% 2.180 2.167 2.194 1.081 0.592 2.017 2.005 2.030 16.27 0.245
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