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Chapter 3 Pm [MW] Din [m] Hmin [mm] R b [mm] ηTχ=0.5 ηTχ=0.5,C F D δmax [◦] 30 Dout [m] 0.98 1.27 0.2 8.2 0.47 30 0.87 Mmax 1.16 0.86 Mmax,CFD 0.99 Hmax [mm] 147 BDA [◦] 66 Table 3.3: Main results for the 6-stage 1 MWM transonic turbine. M =0.93 st W3 M =0.93 C2 M =0.40 U2 1 rot nd 2 rot rd 3 rot th 4 rot th 5 rot th 6 rot M =0.56 C3 0.49 M =0.58 W2 M =0.44 U3 0.56 0.95 0.51 0.42 0.94 0.92 0.90 0.94 0.91 1.10 0.92 0.70 0.89 0.85 0.91 1.00 0.95 1.16 0.40 0.52 0.65 0.90 0.79 0.36 0.38 0.45 0.36 0.40 0.48 th 6 rot th 5 rot th 4 rot 3rd rot nd 2 rot st 1 rot Rotational axis 23 200 400 ROT radius [mm] 200 100 0 -100 -200 0 (a) (b) Figure 3.5: Design results for the 6-stage transonic 1 MWM turbine, following the repeating- stage assumption, adopting the boundary conditions reported in Tab. 3.1, and the Craig & Cox loss estimation method [15]. Fig. 3.5a shows the velocity triangles, in black those referring to the rotor inlet section, in grey to the rotor outlet. The Mach numbers corresponding to the different velocity components are also detailed. The meridional section is depicted in Fig. 3.5b. ing, expressed by the work coefficient Ψ, does not imply a direct decrease of w, as shown in 2 Fig. 3.6a. In fact, by assuming the definition typical of axial turbines, i.e. Ψ = wstg/2U , with U = (Uin + Uout)stg/2, can be noted how Ψ can lower throughout the expander, notwithstanding the fact that ∆hTT, stg, i.e. the specific work extracted, increases. This results in the initial stages be- ing characterized by a lower specific work, but larger blade deflections and aerodynamic loadings, which cause the profile losses to increase. The trend is thus strictly correlated to the constraints imposed on the geometry. The loss-estimation method of Craig & Cox [15] predicts a significant variation of the losses 72 H [mm]PDF Image | New Concepts FOR Organic Rankine Cycle Power Systems
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