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3.2 Turbine design methods 39 the velocity at the rotor inlet is as presented in Figure 3.4b and the angle of relative veloc- ity β1 >0, curved blades can be considered at the rotor inlet to prevent flow separation at the rotor inlet caused by the high incidence angle. Examples of straight and curved rotor blades are presented in Figure 3.6a and Figure 3.6b. (a) (b) Figure 3.6: Examples of turbine inlet (a) with straight blades and (b) with curved blades. A suitable static pressure at the stator outlet was selected by using the definition of the degree of reaction, which can be defined by dividing the isentropic enthalpy change in the turbine rotor by the total isentropic enthalpy change in the turbine r = ∆hs,rot . (3.19) ∆hs,tot The absolute flow velocity c1 at the stator outlet was solved from the estimated enthalpy change between the stator inlet and stator outlet by using the equation √ c1 = 2(htot,in − h1,st). (3.20) The stator outlet enthalpy, h1,st was solved by using the turbine inlet enthalpy and the estimated total-to-static state efficiency of the stator h1,st = htot,in − ηst(htot,in − h1s,st). (3.21) The turbine power was determined from the velocity triangles based on the Euler’s equa- tion Pt = qm(cu1u1 − cu2u2). (3.22) The turbines were designed to have the rotor outlet flow exiting in the axial direction, and thus, the velocity vector cu2 = 0. The peripheral velocity u1 was calculated by using the equation u1 = ∆ht/cu1. (3.23) The turbine diameter can be solved when the peripheral velocity and the rotational speed of the turbine are known by using the equation D1 = u1/(πn). (3.24)PDF Image | WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES
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