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are given by. T=T 2 ∗ 061+γ Tγ ∗ γ−1 06 (A.103) (A.104) (A.105) (A.106) p∗ = p06 T ρ∗ = p∗ T∗ R a∗ =T∗Rγ The equation (A.103) is derived from the following equation when the mach number is set to unity. Equation (A.107) can be found derived in for example [1]. T0 =1+γ−1M2 (A.107) T2 There are some constraints regarding the calculation of the setting angle, δ6. If the calculated setting angle is found to be below five degrees the analysis will be terminated and a message box shown making the user observant to this fault. Another message box will be shown and the analysis will be terminated if the nozzle inlet to outlet radius ratio exceed the following interval, 1.1 ≤ r4/r6 ≤ 1.7. The blade angle distribution can be determined using the following relationships. r cos δ = r6 cos δ6 (A.108) β=δ−χ (A.109) We are now at the point where the blade angle distribution and most of the geometry is designed. The numerical algorithms for the complete design and for the case when only the default values are calculated are the same up until now. The only difference being that when the default values are desirable all of the variable in table A.1 except the number of blades are determined by the algorithm and not by the user which is the case when the design analysis is run. The default values are set according to. r6 r7 θ a/c t4 /c t6 /c tmax /c d/c s6 /c = 1 + 2b7 sin α7 r7 = 0◦ = 0.5 = 0.025 = 0.012 = 0.06 = 0.4 = 0.75 91 (A.110) (A.111) (A.112) (A.113) (A.114) (A.115) (A.116) (A.117)PDF Image | A Detailed Analysis of Radial Turbines
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