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127 Relative flow angle π·π deg β31.5 β33 4.76 Relative flow angle π·π deg β70.69 β72 1.85 Number of rotor blades π΅π - 12 12 0.00 Stage total to static efficiency % 83 85.3 2.3 πΌππ 5.6.2 ORC Turbines When the proposed methodology is validated, an efficient radial-inflow turbine can be designed based on the conditions provided in Table β4-1. Prior to running the OC, a parametric study that uses the DoEC is performed to explore the effects of input parameters on the performance and geometry of the turbine. 5.6.2.1 Parametric Study Using DOEC Adopting a non-zero blade angle π½πππππ ,4 at the rotor inlet without considering the bending stresses as in conventional turbines is possible because the operating temperature of the model is less than 200 Β°C. Figure β5-5 presents a schematic comparison between radial and non-radial blades. The increase in the inlet blade angle results in a hightangential velocity at the rotor leading edge πΆπ4 and, hence, higher specific work. However, a further increase in π½πππππ ,4 will result in excessive blade curvature and, hence, higher secondary losses. Therefore, efficiency deteriorates with any further increase in the blade angle. Figure β5-5: (a) Shape of radial and non-radial blades and (b) effecct of non-zero blade angle π½πππππ ,4 on the efficiency of the turbine.PDF Image | Automotive Radial Turbine Expander Design WHR
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