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116 reduction of the total pressure from the stator trailing edge and rotor leading edge is 1.45%, which is sufficiently small to validate a constant total pressure in the interspace. Watanabe et al. [243]proposed a correlation to estimate a suitable clearance gap between the stator exit and the rotor inlet, as shown in equation (β5-34). The maximum turbine efficiency can be achieved by placing a value of 2 for π. π β π = π π π π π πΌ 3 + πΌ 4 , ( β5 - 3 4 ) 2 where π3 is the stator blade height calculated using equation (β5-35). ππ₯ and ππare the axialand radial tip clearances, as shown in Figure β4-2, and they are calculated using equation (β5-36)[234]. 343 π3 = π4 + ππ₯ ππ₯ = ππ =0.04π5 5.3.4 Stator Modelling (β5-35) (β5-36) To reduce incidence loss, the nozzle vanes must be set at an appropriate blade angle to enable a smooth swirl flow at the rotor leading edge. The design procedure of the nozzle vanes are performed iteratively, as shown in the flowcharts inFigure β5-3 and Figure β5-4. Li et al. [244] stated that the conservation of angular momentum can be applied in the vaneless space because the swirl coefficient (SC) between the stator exit and the rotor inlet is close to unity. Therefore, the tangential component of the velocity at the stator exit πΆπ3 can be calculated, as shown in equation(β5-37). πΆβπ πΆπ3=π4 4 To construct the velocity triangle at the stator exit, the absolute velocity πΆ3 is calculated iteratively with a first assumption of πΆ3 = πΆπ3. Subsequently, the static enthalpy π3 is calculated from the total enthalpy and the kinetic energy, as shown in equation(β5-38). π 3 (β5-37)PDF Image | Automotive Radial Turbine Expander Design WHR
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