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98 The required diameter should by identified to obtain the specific diameter, π·π , as expressed by equation (β4-9). However, the exact value of the rotor diameter is not given by the industrial partner. Rather, the maximum allowable diameter is specified as shown in Table β4-1. Therefore, π·π is calculated for the minimum and maximum values of rotor diameter. π βπ0.25 π·π =4 πππ‘ π (β4-9) The second type of parameters, π πππ Ρ°, requires velocity values at the inlet and exit of the turbine, which are not available at the early stage of the project. However, Dixon and Hall [197] presented useful relationships between the two types of parameters, as shown in equations (β4-10)and (β4-11). π= 1 (π π·3) (β4-10) Ρ°=1 (β4-11) π π (π2π·2) π π The results of both pairs of parameters are depicted in Figure β4-13. The ππ values are 0.52 (SI system) and 68 (US system). π·π is plotted at two diameter and its values are 1.96 and 2.68. The second pair of parameters is calculated using equations (β4-10) and (β4-11). The results show that π = 0.254 πππ Ρ° = 0.957, which indicate that the intersection of the two parameters lies in the optimum turbine performance area. However, the utilised charts are presented for air turbines only. Therefore, the developed guide, presented in Section β2.3.3,is also applied to confirm the final decision on the expanderβs type using organic expansion machines as depicted in Figure β4-14. Along with the advantages mentioned in βChapter 2, Figure β4-13andFigure β4-14(red dotted lines) nominate the radial-inflow turbine as the optimum expansion machine for the current application.PDF Image | Automotive Radial Turbine Expander Design WHR
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