By H.H. Anderson

This ebook could be of important curiosity to all engineers and architects inquisitive about centrifugal pumps and generators. together with statistical info derived from 20000 pumps and seven hundred generators with capacities of 5gpm to 5000000gpm, this booklet deals the widest diversity and scope of knowledge at the moment on hand. Statistical analyses recommend sensible tools of accelerating pump functionality and supply invaluable information for brand spanking new layout points.

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Extra resources for Centrifugal Pumps and Allied Machinery

Sample text

5 shows ratios of outlet diameter to eye diameter plotted against shape number for various pumps. CENTRIFUGAL PUMPS 60 .. =: Good suction layouts, showing pipes rising all the _ .. = way to the pump. : .... - Bad suction layouts, which will cause air pockets and =failure to pump. 4 - Suction layouts to give optimum inlet conditions. Pumps drawing from overhead vessels at saturation pressure should similarly have inlet piping falling progressively from vessel to pump with no vapour pockets. A vapour bubble release pipe (a quarter the diameter of the inlet pipe) should rise progressively from the top of the inlet passage near the impeller to the saturation vessel above the liquid level.

4%, the deviation from formula efficiency being comparable to the tolerance of Class A measurement, which also appears on the chart. All the machines in the survey are assumed to have the same absolute surface finish so that every machine is a model of every other machine of the same shape number. 32 C/). :t > -e m Z c (%) Correction. 29 10 gal/min / ",-,"',"""'""" ~ .!? ~ ... 32-log,0 - 1000 ~ rev/minVTiSiC ns:l metres head 3/" O··~~ 10,000 '' ''' ''' #~. ~...... __ .... --- .... ~~ . :::IQ. ~ 10 100 Cubic m/sec > Z tJ m ~ n m z n ~ 'u ...

Euler equated the rate of change of angular momentum to the torque on the pump shaft and thereby obtained the equation: Head equals uw/g where u is the peripheral velocity of the impeller, w is the velocity of whirl and g is the acceleration due to gravity. Busemann (Ref 3), Stodola (Ref 4) and Pfleiderer (Ref 5), suggested that firstly, the THEORY OF CENTRIFUGAL PUMPS 33 impeller outlet angle and secondly, the number of vanes, controlled pump performance; but these investigators apparently concentrated on the impeller alone and ignored the effect of the casing in controlling flow at best efficiency point.

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