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turbine configuration for low-power organic Rankine cycle

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turbine configuration for low-power organic Rankine cycle ( turbine-configuration-low-power-organic-rankine-cycle )

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Parameters Value Parameters β4 (degree) β5 (degree) Znozzle (-) Zrotor (-) Nozzle chord(m) Rotor chord (m) Radial Clearance (m) Nozzle trailing edge thickness (m) Rotor trailing edge thickness (m) Value 31.8 -57.40 19 16 0.0229 0.0457 0.23 ×10-3 0.51 ×10-3 0.76 ×10-3 ACCEPTED MANUSCRIPT performance parameters (i.e. turbine efficiency and power) are in good agreement with the Glassman cases and the maximum variation are within the acceptable margin as demonstrated in Fig. 9 for all working fluids. Due to the lack of availability in the experimental data for small-scale ORC turbines, verification of the present 3D CFD model for each turbine configuration is made against the PD results at nominal operating conditions (i.e. Table 5), as shown in Fig. 9a and b. The turbine efficiency and power are evaluated for five turbine configurations with working fluid R245fa. The comparison results exhibited that the maximum variation between the PD and CFD results was 3.28%, 3.56%, 3.85%, 3.65% and 4.12% for single-stage AFT, RIT, ROT and two-stage AFT and ROT respectively. The variance between the PD and CFD is mostly because of the characteristic of the 1D mean-line design, which is not able to provide all 3D flow characteristics. Eventually, there was better agreement between these results than can be seen in Fiaschi et al. (2016) and Russell et al. (2016), in which there was a 6-9% deviation in terms of the turbine isentropic efficiency. Furthermore, the 3D CFD results of the single-stage RIT and two-stage AFT turbines are compared with experimental data available in Jones (1996) and Kofskey and Nusbaum (1968), as shown in Figs. 10 and 11 respectively. To allow a fair comparison, most of the range/values of dimensions and operating conditions are taken from the above-mentioned references, as shown in Table 8 for radial inflow turbine and Table 9 for axial flow turbine respectively. The comparison results showed that the maximum difference in efficiency was about 4.29% with single-stage RIT configuration as shown in Fig. 10, compared to 3.57% with two-stage AFT as shown in Fig.11. This difference could also be attributed to the complex phenomena that can be accurately handled by 3D CFD modelling. Table 8 Details of the radial-inflow turbine geometry of a real case (Jones case (Jones, 1996)). r2 (m) r3 (m) r4 (m) r5tip (m) r5hup (m) b4 (m) b5 (m) α3 (degree) α4 (degree) α5 (degree) 0.074 0.0635 0.0582 0.0368 0.0152 0.00618 0.00635 77.80 76.8 -0.03 19

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turbine configuration for low-power organic Rankine cycle

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