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This was caused by the decrease in head produced by the hubless inducer compared to the conventional. This has the effect of decreasing the available NPSH to the rotor causing complete cavitation breakdown and consequently zero delivered head. 3. High Frequency A comparison of the boost pump suction and discharge pressure oscillations with the conventional and with the 45° hubless inducer during transient operation is shown on Figure 68. The 45° hubless inducer had the highest peak-to-peak pressure oscillations during steady-state operation (Section VII.B.3.b.). In most cases there appeared to be some resonance between 1 and 3 seconds. This could have been caused by 'ringing' of the flow loop. All frequencies with significant peak-to-peak pressure magnitude were between 5 and 30 Hertz with 20 being the predominant frequency. In all cases except one, hubless inducer discharge pressure at 80% flow coefficient, peak-to-peak pressure returned to the minimal steady-state value after 4 seconds. The suction peak-to-peak oscillations in transient are approximately three times those measured in steady-state (see Figure 55 for comparison). Xhe discharge peak-to-peak pressure oscillations, however, are approximately the same during transient and steady-state (see Figure 56 for comparison). D. MODIFIED ROTOR Upon completion of the contract-required test program, the rotor was modified in an attempt to improve its cavitation performance. The modification consisted of reducing the maximum blade thickness by approximately one-half at mid cord from hub to tip on the suction side. From mid cord to 20% and 80% cord the material removal was reduced to zero. Since the blade was a double circular arc with little camber, the radius of curvature on the pressure side was extremely large, consequently the modification had the effect of making suction and pressure surfaces parallel from 20% cord to 80% cord. In addition the leading edge was reduced from 0.030 in. (0.00076 m) to 0.007 in. (0.00018 m). The thickness increased from the leading edge linearly to the 20% cord station. Figure 69 shows the head coefficient and efficiency vs. flow coefficient for the maximum test speed. The head coefficient is less than the design but 16% higher than the original head coefficient. The efficiency appears to peak at a higher than design flow coefficient and is 13 percentage points less than design and 7 percentage points less than the origianl. Stall is not evident down to 70% flow coefficient. The original rotor stalled at approximately 85% flow coefficient. At 120% flow coefficient the modified rotor has a 23% higher head coefficient, indicating that decreasing the thickness kept the rotor from choking at the higher flow. The modified rotor head coefficient at four radial stations vs. flow coefficient is shown in Figure 70. This should be compared to Figure 42, which is the same data for the original rotor. The stall at the hub in the 92 riiTPDF Image | HUBLESS INDUCER FLOW HYDRAULIC TURBINE INDUCER BOOST PUMP
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