WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES

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WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES ( working-fluid-selection-and-design-small-scale-waste-heat-re )

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36 3 Numerical methods operate with high pressure ratios over a single turbine stage. In addition, radial turbines have been proven successful in small-scale high speed ORC turbogenerator prototypes, designed and tested at LUT. The turbine inlet and the outlet conditions were obtained as a result from the process design, presented more in detail in the previous section. The preliminary evaluation of the turbine rotational speed, n is carried out by using the nondi- mensional parameter, turbine specific speed Ns defined as ωqv,out0.5 Ns = ∆hs 0.75 (3.15) where the ω is the angular speed. The angular speed is defined as, ω = 2πn. (3.16) According to the performance diagram for radial turbines operating with compressible fluids, presented by Balje (1981), the highest efficiencies are obtained with a specific speed in the range from 0.4 to 0.8. Another nondimensional design parameter, specific diameter Ds, defined as D∆hs1/4 Ds = qv,out0.5 (3.17) , was used in evaluating the turbine rotor diameter. According to the diagram by Balje (1981), the highest efficiencies are obtained with a specific diameter in the range from 2 to 6. The input parameters used in the turbine design are presented in Table 3.4. The ratio of Table 3.4: Input parameters used in the turbine design. total inlet pressure total inlet temperature working fluid mass flow rate static pressure at stator outlet total pressure at rotor outlet ratio of rotor diameters ratio of rotor outlet diameters stator efficiency prediction turbine efficiency prediction stator exit flow angle or blade height specific speed or turbine rotational speed ptot,in Ttot,in qm,wf pst,out prot,out D2,t /D1 D2,h /D2,t ηst ηt α1ort1 Nsorn diameters at the rotor inlet and rotor outlet D2t/D1, the ratio of the blade tip and hub diameters D2h/D2tip at the rotor outlet, as well as the suitable stator exit flow angle α1 were determined by following the design guidelines presented by Rohlik (1975) and by monitoring the velocity triangles and blade heights at the inlet and at the outlet of the

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