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5. Rotor The rotor cavitation performance at three flow coefficients is shownin Figure 57. The NPSHat the rotor was computedby adding the NPSH of the inducer to the total head rise of the inducer and does not account for fluid temperature increase in the inducer or fluid prewhirl at the rotor inlet. The maximumsuction specific speed at 2%head loss was 6600 (2.4) at the design flow coefficient. This compareswith the design point value of 7420 (2.7) at 2%head loss. The off-design cavitation performance was 6000 (2.2) for the 78%flow and 5200 (1.9) for the 108%flow at 2%head loss. In all cases the head loss increased uniformly as the suction specific speedwas increased over the test range. Data was taken until approximately 10%head loss occurred, which was equivalent to 30%loss in the overall boost pumphead rise. 6. Overall Performance The overall boost pump cavitation performance is shown in Figure 58 at three different flows. Essentially all the head loss shown is due to the rotor cavitation. The inducer is operating at a maximum of 20,000 (7.3) which, as can be seen on Figure 49, represents negligible head loss. If the rotor would have had less than 2% head loss at 7420 (2.7) suction specific speed then the boost pump would have operated with negligible loss to 92,000 (33.6). This represents a 12% increase in the suction specific speed perform- ance of the rotor. The value of the 92,000 (33.6) is equal to 43,000 (15.7) inducer suction specific speed times the shaft speed ratio and is the maximum obtainable boost pump suction performance. C. TRANSIENT PERFORMANCE The transient tests were conducted in both cavitating and non- cavitating conditions, using a GN2 powered turbine to drive the boost pump. The flow loop flow control valve was preset to the desired steady-state flow coefficient and the manually operated GN 2 power valve was opened to the desired rate. This method produced start transients with a minimum of 1.5 sec elapsed time from zero to design speed; there was no limit to the maximum start time. The shutdowns were not controlled and were accomplished simply by closing the GN2 power valve through the emergency override system. i. Conventional Inducer Figure 59 shows the start transient of the boost pump with the conventional inducer at the design steady-state flow and non-cavitation conditions. This transient acceleration represents the 'fastest' start possible within drive limitations. The suction pressure was set to a level which pre- cluded cavitation within the boost pump. As indicated by Curve 7, the inducer - turbine are essentially locked to the rotor after 1.5 sec of elapsed time. The boost pump does not operate along a specific speed line as it would if the start was infinitely long. This can be seen by Curves 8 and 9, which are directly proportional to their respective flow coefficients. Curve 8 shows that the 79PDF Image | HUBLESS INDUCER FLOW HYDRAULIC TURBINE INDUCER BOOST PUMP
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