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Energies 2020, 13, 2118 9 of 18 (413.0 K). The exit boundary condition was given static pressure (3.4 MPa). The rotational speed of the rotor domain was 7200 RPM, the same as the preliminary design condition. The interface between the nozzle domain and the rotor domain set the frozen rotor model. Figure 6. One-passage geometry of the radial outflow turbine. 3.4. Results of CFD Analysis Table 3 compares the CFD analysis results to the preliminary design results. CFD validation . results were generally satisfactory but showed about 5% error in turbine power (W). This is because the working fluid is not sufficiently accelerated at the nozzle blade, and the tangential absolute velocity of the nozzle exit (C2θ) is somewhat lower compared to the preliminary design result. Table 3. Comparison of results between preliminary design and CFD. Variables . W [kW] ηts [%] PRts [-] C2θ [m/s] C3θ [m/s] 4. Optimization of Velocity Triangles 4.1. Optimization Procedure Preliminary Design CFD 400.0 85.0 84.66 1.47 1.43 91.5 87.9 0.0 0.7 379.87 As turbines have a significant impact on the overall efficiency of the cycle, ORC developers have generally provided clear targets of turbine power and efficiency. If the performance of the actual turbine is better or worse than that required by the developer, the cycle efficiency may deteriorate as the operating conditions of the evaporator, condenser, and pump move away from the design condition. Hence, the designed turbine must meet the targets exactly. In this study, optimization wasPDF Image | Off-Design Analysis of a Radial Outflow Turbine for ORC
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