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The final design was a selection of inlet geometry that could be modified between tests to observe the characteristics of various inlet angle changes. Figure 16 shows the predicted axial velocity profile at two stations for a 60 ° inlet angle. As the flow passes through the inducer, the axial velocity at the tip becomes more uniform. When the blade extends to the hub and the fluid is completely 'captured' between blade passages and the contour, the blade angle can be decreased more rapidly. Until this axial station is reached, the blade angle can be decreased only to the point where the inducer-free fluid pressure can support the flow field at the larger radii. To maintain hydrodynamic similarity between the hubless inducer and the conventional inducer, the solidity at the mean radius was made identical. This resulted in higher tip and lower hub solidities when compared to the conventional inducer. The blade angles of the hubless inducer are equal to those of the conventional inducer from approximately 70% of axial length to the discharge. The tip contour is converging from the inlet to the discharge along a conical line. The convergence ratio, discharge to inlet, is 0.946. The hub contour from the connection of the blade to the discharge is als0 a conical section. This conical hub contour approximates the contour of the conventional inducer over that portion of the inducer. This design concept made the discharge of the hubless inducer nearly identical to that of the conventional so that both would provide similar flow into the transition (aft) section. 2. Aft Section The aft section is common to both inducers and is aptly called the transition section. The function of the transition section is to 'straighten' the flow coming from the front section and provide more nearly uniform axial flow and radial head to the rotor. By dividing the inducer into two sections, the blading of the rear portion could be twisted enough to accomplish these favorable conditions. An inducer with a continuous blade with comparable twist would not only be difficult to manufacture but would have higher centrifugal stresses because of its forward lean. The selected blade form of the transition section was double circular arcs because of their characteristic sharp leading edges (which is necessary for good cavitation performance), and abundance of cascade data. The incidence angles were set at near-zero values after accounting for the flow deviation from the forward section. This was done to account for any uncertainties in relative flow angles. The deviation angles were established from data in Ref 6 and corrected to account for rotation effects, tip leakage and radial flow shifts, based on correlations of this data and existing axial flow pump blade element performance data. 25PDF Image | HUBLESS INDUCER FLOW HYDRAULIC TURBINE INDUCER BOOST PUMP
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