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126 Table β5-2: Design Input Parameters [238]. Parameter Fluid Inletstagnation temperature Inlet stagnation pressure Exit static pressure Rotational speed Mass flow rate Value Unit Argon - 1083.3 K 91 kPa 56.52 kPa 38,500 rpm 0.277 Kg/s The results of both cases are presented in Table β5-3, which clearly shows that the results of the current model are in good agreement with the test case (Glassmanβs model). In terms of turbine size, the current model overestimates the size, with 3.63% increase compared to the test case. The deviation in the turbine performance between the two models is 2.3%, indicating the overestimation of the current model. This result can be justified by the fact that the input parameters (π, πΉ) in the current study are optimised for higher turbine performance. The next paragraphs show that the flow coefficient π plays a vital role in the performance of the turbine. The maximum deviation between the two models in the prediction of the rotor exit tip radius π5π‘is 5.38%. The results in Table β5-3 indicate that the results in the current model are in good agreement with the test case. Importantly, the model can optimise any existing turbine. It is worth mentioning that the test case is just a theoretical study and no experiment has been done to validate it. Table β5-3: Comparsion between the Current Model and Glassmanβs Model. Parameter Stator inlet radius ππ Stator exit radius ππ Absolute flow angle πΆπ Number of nozzle vanes π΅π Rotor inlet radius ππ Rotor exit hub radius πππ Rotor exit tip radius πππ Absolute flow angle πΆπ Unit Glassman mm 97.75 mm 79.38 deg 72 - 16 mm 78.74 mm 19.36 mm 55.42 deg 71.92 Current Model 101.3 82.6 73.7 16 76 18.7 58.4 72.5 Deviation % 3.63 4.06 2.36 0.00 3.48 3.41 5.38 0.81PDF Image | Automotive Radial Turbine Expander Design WHR
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