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Variable T̄ T̄ M ̇ a rp M ̇ f Nrot Tev Tcd Description First hot air source mean temperature Second hot air source mean temperature Air mass flow rate Pressure ratio Mass flow rate Expander rotating speed Evaporating temperature Condensing temperature Heat transfer at the evaporator Shaft power Net power Expander effectiveness Cycle efficiency Second-law cycle efficiency Partial pressure of non- condensable gases Improved test rig 110 - 130°C 110 - 134°C 71-126 g/s 2.42 - 7.44 49 - 78 g/s 1855 - 3125 rpm 84.3 - 102.1 °C 26.5 - 56.5 °C 14 - 24 kW 180.5 - 2164 W -224 - 1709 W 16.9 - 71.1 % -1.4 - 7.3 % -4.1 - 20.2% 0.53 - 0.69 bar Former results 53.4 - 86.4 °C 101 - 163.2 °C 71 - 90 g/s 2.7 - 5.4 45 - 86 g/s 1771 - 2660 rpm 83.9 - 116.2 33.6 - 50.2 °C 11.6 - 22.35 kW 382 - 1820 W -0.9 - 1421 W 42 - 68 % 0 - 6.6 % 0 - 16.5 % 0.5 - 1.48 bar ev II part , air , cd Chapter 3: Experimental setups hf1 hf2 Q ̇ W ̇ exp W ̇ net εs ,exp ηcycle η p Table 7: Operating parameters and reached performance on the two experimental setups 4 Expander test rig 4.1 Description of the test rig A “vapor cycle” test rig was built to test the performance of the expander with fluid HFC-245fa. This rig (simpler, less bulky and cheaper to build than the entire Rankine cycle system) is mainly made up of a scroll compressor, a scroll expander, a water-cooled heat exchanger and a by-pass valve. A simplified representation of the cycle described by the working fluid is given in Figure 24: the fluid, in vapor phase, is successively compressed (1-2), expanded (2-3) and cooled-down (3-1). A heat exchanger could have been integrated at the outlet of the compressor to adjust the expander inlet temperature. 18PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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