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ACCEPTED MANUSCRIPT π π»ππ’π‘ = πππ’π‘πππ’π‘cos (π΅π·π΄)π·ππ’π‘π (18) 3.3 Radial-inflow turbine (RIT) design Fig. 4 shows the basic geometry of the RIT and rotor geometry that are implemented according to the methodology offered by Whitfield and Baines (1990) and Moustapha et al. (2003). To obtain the best turbine isentropic efficiency, the dimensionless parameters, i.e. the flow and loading coefficients (Ο, Ο) are essential and given with an inlet blade angle (Ξ²4) of 70Β° (Whitfield and Baines, 1990). The current losses model of the RIT combines: the incidence, disk friction, friction, secondary, tip clearance, windage, exit energy, nozzle friction and volute losses model, as tabulated in Table 4. The details of the dimensions of the RIT stage calculations are explained in Glassman (1976) and Whitfield and Baines (1990). The total-to-total turbine isentropic efficiency and total-to-static turbine isentropic efficiency are presented in equation (19) as following (Ventura et al., 2012): Ξ·= β βhactual + Type of losses Incidence loss Disk friction loss Friction loss Secondary loss Tip clearance loss Windage loss Exit energy loss Nozzle friction loss Volute loss (19) Ref. Ventura et al. (2012) Whitfield and Baines (1990) Suhrmann et al. (2010) Suhrmann et al. (2010) Japikse and Baines π .π .πΆ .πΆ π₯(19π94π₯) π) Moustapha et al. (2003), Ventura et al. (2012) Suhrmann et al. (2010) Whitfield and Baines (1990) Whitfield and Baines (1990) βhactual (βh ) total losses Correlation Table 4 RIT losses modeling. π€2 π4 βhπππππππππ = 2 βhπππ π πππππ‘πππ = ππππ34π24 4π π€4 + (π€5π‘ππ + π€5hπ’π) βhπππππ‘πππ = πππ’ππ£π[ πΆ24.π4 βhπ ππππππππ¦ = ππππ‘ππ.ππ 2 2 πhπ¦π ] πhπ¦π π34.ππππ‘ππ βhπ‘ππ ππππππππ = 8π π.π43.π24 (0.4.ππ₯.πΆπ₯ + 0.75.ππ.πΆπ β 0.3 βhπ€ππππππ = ππ2.π.π€2 5 βhππ₯ππ‘ = 0.5πΆ25 πhπ¦π βhπππππ‘πππ = 4.ππππ§π§ππ.πΆπhπ¦π πΎπ£πππ’π‘ππΆ2 βhπ£πππ’π‘π πππ π = 2 12PDF Image | turbine configuration for low-power organic Rankine cycle
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