Centrifugal Pumps, Edition: 3rd by H. H. Anderson (Auth.)

By H. H. Anderson (Auth.)

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61 STATISTICAL ANALYSIS OF PUMP PERFORMANCE a E E z Minus 6 4 Plus Fig 16 First test efficiency % compared to quoted efficiency. Quoting Level Below average of all test Minus 03 — Θ 02 Fig 01 17 Proportion O Above average of all test 100 — 0Ί 02 of variable losses. 03 Plus 62 STATISTICAL ANALYSIS OF PUMP PERFORMANCE The probability of meeting any particular efficiency is shown in Fig 17, plotted against quoting level. 2 l/s)"0,32 since this is the true basis of the scatter of Fig 15, and omits the tolerance of ISO 3555.

1927 'Steam and Gas Turbines' (McGraw-Hill). 5. PFLEIDERER, C. 1932. 'Die Kreiselpumpen', second edition (Springer, Berlin). 6. , 'Centrifugal Pumps, An Alternative Theory'. Proc. IME 1947 Vol 157 We 27. 7. , 'The Flow in Volutes and its Effect on Centrifugal Pump Performance', Proc. E. 1963 Vol 177 No 31. 8. STEPANOFF, A. , 'Centrifugal and Axial Flow Pumps' (Wiley) 1957. 9. ANDERSON, H. , 'Hydraulic Design of Centrifugal Pumps and Water Turbines', 1961. ASME 61 WA 320. 44 7. Type Number, Flou; and Efficiency THE PRECEDING chapters considered, in a very preliminary way, the re­ lationship between the dimensions of a pump and its performance.

D. tan β Throat area If the test data had been based upon tan β instead of sin β the test points would have agreed more closely w i t h Worster's theoretical lines. BC Area ratio = y = — AC AB = 2 u 2g (see Fig 12). THEORY OF CENTRIFUGAL PUMPS 42 The contention of earlier investigators that the outlet angle is the major arbiter of pump performance arose through consideration of impeller only. It is certainly a fact that, for the same impeller width and casing throat, a larger angle would produce a higher head, but this higher head is due to the increase of impeller outlet area or of area ratio.

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