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This stress can be approximated by the following equation: S = 0.01625 N Vtipb The rotor tip speed (V . 1 can be approximated by substituting the spouting velocity k*i ) from the turbine performance calcu- lations. Thebladeheighf(b)intheaboveequationiscomputed from the equation given in the section on Turbine Efficiency vs. ReynoldsNumber. Generally,thestressequationwillbecomethe controlling factor whenever the volumetric flow rate of the steam at the exit of the turbine becomes very large. This occurs at low condensing temperatures and/or very high power output. It should be noted that the above stress equation is applicable only to ETI's turbine design. Radial outflow turbines built by other manufacturers are not likely to possess the tip speed capa- bility which has been engineered into ETI's design. Other ROF turbine builders generally utilize counter-rotating turbine bh9e rowstoachievecomparablerelativetipspeeds. Thisisamuch more costly approach and one of the main reasons why this type of turbine design has not seen very wide application in this country. TUEWINEEFFICIENCYAS AFUNCTION OF NUMBER OF STAGES Turbine efficiency can be related to four basic overall parameters: 1. 2, 3 , 4. Blade.jet speed ratio Speed-work parameter Specific diameter Specific speed. Where a particular type of velocity diagram is used, as dictated by the turbine geometry selected, only one of the above parameters isneededtocorrelateefficiency. ThisisdiscussedinReference1. The speed-work parameter was selected to analyze the effect of varying the nwnber of stage!; in a fixed pressure ratio design. The speed-work parameter (A) af an individual stage is defined as: a= p2 Optimum stage performance occurs when A= 1. The overall speed-work parameter (XI for the completion tur- bine is defined ds: lJ* x=aq Figure 11 shows overall total-to-static turbine efficiency as 8 function of the overall speed-work parameter and the number of 9PDF Image | Radial Outflow Turbine for Solar Steam Rankine Engines
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