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3-3 Turbine Model 27 ratio D3h/D3s should be greater than 0.4 in order to reduce the secondary flow and avoid flow blockage caused by closely spaced vanes. Hence the minimum value of 0.4 has been considered. The diameter ratio D3s/D2 should not be more than 0.7 in order to avoid excessive shroud curvature [45]. This ratio is assumed to be 0.5. The turbine exit velocity is assumed to be 60 m/s [28]. Table 3-5 summarizes the important parameters discussed above. The details of the calculation procedure has been described in appendix B. Table 3-5: Input parameters for the model[1][43] Parameter Value Degree of Reaction, R [-] 0.15 Exit Velocity Ratio, φ [-] 0.25 Spouting Velocity Ratio, ψ [-] 0.7 Isentropic Efficiency of Nozzle, ηnozzle[%] 0.95 Inlet Velocity, c1 [m/s] 0 Exit Velocity, c4 [m/s] 60 Exit hub to shroud diameter ratio, D3h/D3s [-] 0.4 Diameter ratio, D3s/D2 [-] 0.5 Solidity, [-] 6 Efficiency calculation The final step in the turbine model is to compute the isentropic efficiency using the calculated values of fluid properties, angles and dimensions. The performance of turbomachines can be easily evaluated by using nsds diagram [46] as shown in Figure 3-10. Figure 3-10: nsds diagram (from Balje [46]) The nsds diagram does not include the losses in the nozzle and rotor. In addition, the need to integrate the model into a continuous procedure makes it difficult to use this chart. Dixon [17] presents an expression for nominal isentropic efficiency in the absence of a diffuser Master of Science Thesis Akshay HattiangadiPDF Image | Working Fluid Design for Organic Rankine Cycle
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