Automotive Radial Turbine Expander Design WHR

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Automotive Radial Turbine Expander Design WHR ( automotive-radial-turbine-expander-design-whr )

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109 given pressure ratio. Therefore, the isentropic enthalpy 𝑕5𝑠 can be found using EoS, as shown in equation (β€Ž5-5). 5.3.2 𝑇,𝑃 =πΈπ‘œπ‘†πœŒ,𝑆,π‘Ž,𝑓𝑙𝑒𝑖𝑑 01 01 01 01 01 𝑃=𝑃,𝑠=𝑠 =πΈπ‘œπ‘†π‘•,𝑓𝑙𝑒𝑖𝑑 5𝑠 55𝑠 01 5𝑠 (β€Ž5-4) (β€Ž5-5) Subsequently, the isentropic βˆ†π‘•π‘–π‘  and actual βˆ†π‘•π‘Žπ‘π‘‘ enthalpies drops, and the turbine power output π‘Šπ‘œπ‘’π‘‘ can be obtained using the following equations: βˆ†π‘•π‘–π‘  = π‘•π‘œ1 βˆ’ 𝑕5𝑠 βˆ†π‘•π‘Žπ‘π‘‘ = ɳ𝑑𝑠 βˆ†π‘•π‘–π‘  = 𝑕01 βˆ’ 𝑕05 π‘Š =π‘šβˆ†π‘• π‘œπ‘’π‘‘ π‘Žπ‘π‘‘ Rotor Modelling (β€Ž5-6) (β€Ž5-7) (β€Ž5-8) Rotor is the most significant component in the turbine stage because work transfer occurs in this region. Therefore, this component will be analysed first. In the DPC, the designer has the option to select either specific speed approach, or loading Ρ°and flow πœ‘ coefficients approach. 5.3.2.1 Mean-line Based on Specific Speed, 𝑡𝒔 In this approach, 𝑁𝑠 is defined by the user, the rotational speed 𝑁 is calculated using equation(β€Ž2-3)and 𝑁 is specified by the user in the second approach, which will be shown in the next section. Once 𝑣𝑠 is calculated, rotor tip speed π‘ˆ4 , tangential speed πΆπœƒ4 and absolute flow angle 𝛼4 are calculated using equations (β€Ž5-9), (β€Ž5-10)and(β€Ž5-11), respectively [234]. It is worth mentioning that equation (β€Ž5-11) is used in ideal gases. Therefore, the velocity triangle at the rotor inlet (Figure β€Ž5-2) is completed using trigonometry rules. Figure β€Ž5-3 presents the flowchart of the design point using 𝑁𝑠 correlation. π‘ˆ4=𝑣𝑠 2βˆ†π‘•π‘–π‘  (β€Ž5-9)

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