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Energies 2020, 13, 2118 7 of 18 If the Reynolds number is not 105, the loss coefficient (ζ2) corrected by the Reynolds number can be obtained through Equations (18)–(20). where 105 1/4 ζ2=Re ζ1 (18) Re = ρ2C2Dh/μ (19) Dh = 2sHcosα2/(scosα2 +H) (20) The deviation angle model of the blade can be expressed as Equations (21)–(24) with reference to Aungier [27]. where −1 (o/s) 1+(1−o/s) βg/90 sinβg = o/s 2 −βg (22) (23) (24) δ ,M≤0.5 0 exit δ= (21) δ0 1−10X3 +15X4 −6X5 ,Mexit > 0.5 δ0 = sin X = 2Mexit − 1 3. Validation of the Preliminary Design Program 3.1. Design Condition For validation of the preliminary design program, a radial outflow turbine was designed. The design condition was referenced by the studies of Kim [2] and Sauret et al. [28], and the main design variables are shown in Table 1. In consideration of manufacturability, the thickness–chord ratio (tmax/c) of the nozzle blade and rotor blade was selected to be 0.25 and 0.10, respectively. Table 1. Design values of a radial outflow turbine. Variables Unit Working fluid - . W kW P01 MPa 5.0 T01 K ηtt % 90.0 413.0 P3 MPa 3.4 ηts % 85.0 3.2. Results of Preliminary Design As the preliminary design result for the design conditions in Table 1, the RPM range that satisfies the high accuracy required and design conditions was 7100–7300 RPM. Table 2 shows the main specifications of the radial outflow turbine according to RPM. Excluding the number of nozzle blades and rotor blades, there is no significant difference in turbine shape according to RPM. Meanwhile, the local power grid generally uses a frequency of 60 Hz. In this study, 7200 RPM, which is easy to convert to frequency, was determined as the RPM of the turbine. Values R143a 400.0PDF Image | Off-Design Analysis of a Radial Outflow Turbine for ORC
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