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Performance of a Combined Organic Rankine Cycle

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Performance of a Combined Organic Rankine Cycle ( performance-combined-organic-rankine-cycle )

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scale range), or ±1.7 kPa. The mass flow rates for both the power and cooling sides were measured by turbine flow meters made by AW Company (model TRG-11.300-5) with an accuracy of ±1% of the actual measured flow. The expander power output was measured by a Futek torque sensor (model TRS 605) with rated torque capacity of 10 N-m. It had an accuracy of ±0.3% of the full scale range, or ±0.03 N-m. The uncertainty analysis was focused on the bias errors introduced by the instruments, as the random errors during the experiments were minimal and averaged out. According to the theory of error propagation, the root-sum-square method such as proposed by Kline and McClintock [40] was used to combine individual errors. The resulting uncertainties for the quantities of interest are listed in Table 2 (Refer to Appendix for detailed equations). Table 2: Uncertainties for Interested Parameters Quantity ηexp ηp ηp,II εrecp Qevap COPc COPs Uncertainty 2.5% 2.5% 2.5% 2.8% 2.2% 2.5% 3.5% 5. Performance Analysis and Discussions A series laboratory tests were conducted to assess the prototype system performance over a range of conditions. Due to facility limitations, the system has not yet been tested under its design conditions with outdoor condenser air temperature of 48.9 °C and indoor evaporator air temperature of 32 °C. Rather, the system was tested indoors with air temperature at approximately 22 °C. Because of internal leaks asso ciated with the custom made microchannel boiler and recuperator, two standard plate-type heat exchangers were used during the system tests. Figures 13 and 14 show a typical pressure-enthalpy (P-h) diagram for the power and cooling cycle, respectively. The graphs provide in visual form the cycle conversion performance. As the boiling takes place from state point 3 to point 4 in Fig. 13, the corresponding distance on the horizontal axis (enthalpy) indicates the amount of heat input in the boiler. In contrast, the work generated by the expander is projected on the horizontal axis between state points 4 and 5. The ratio of these two is the power cycle conversion efficiency. For a given heat input to the boiler, as the length of the projection on the horizontal axis increases, the better the energy conversion efficiency. Also, from a second law point of view, less entropy is generated in the process as the slope between state points 4 and 5 decreases. Similarly in Fig. 14, the horizontal distance from state point 11 to point 8 represents the heat absorbed in the evaporator, while the horizontal distance from points 8 to 9 represents the work consumed by the compressor. The ratio of these two quantities gives the coefficient of performance for the cooling cycle. 19

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