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Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)

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184 <strong>Centrifugal</strong> <strong>Pumps</strong>: <strong>Design</strong> <strong>and</strong> <strong>Application</strong><br />

the diameter, while flow or throughput is proportional to the cross-sectional<br />

area <strong>and</strong> so is proportional to the square of the diameter. Small<br />

pipes thus experience relatively higher flow loss than do large pipes. In<br />

fact, pipe friction data provide excellent corollary with the N s —^ data for<br />

pumps in that pipe diameters commonly appear as parameters on a dimensionless<br />

plot of friction factor versus Reynolds Number.<br />

With specific spe<strong>ed</strong> as well as head <strong>and</strong> flow expressions having been<br />

defin<strong>ed</strong> for P.E. pumps, convenient expressions for impeller <strong>and</strong> throat<br />

size may be deriv<strong>ed</strong><br />

The concentric bowl pump has been unjustly criticiz<strong>ed</strong> as having only<br />

low efficiency potential, probably because this pump type is frequently<br />

design<strong>ed</strong> for very low specific spe<strong>ed</strong> where only low efficiency potential<br />

exists. Barske states that efficiency was of secondary importance in his<br />

development efforts, yet reports an efficiency isl<strong>and</strong> of 57% in the vicinity<br />

of H = 1,000, Q = 40, N = 28,000 (N, = 1,000). This is seen to<br />

be representative of good pump performance as indicat<strong>ed</strong> by the general<br />

pump population data discuss<strong>ed</strong> in Chapter 2.<br />

Because partial emission pumps range so widely in spe<strong>ed</strong>, it is sensible<br />

to use impeller diameters for scale or size parameters on N S -T| maps,<br />

rather than the flow parameters widely us<strong>ed</strong> for the higher specific spe<strong>ed</strong><br />

types. Direct comparison of P.E. <strong>and</strong> RE. efficiency potentials from<br />

these data is a little elusive since these maps define explicitly only two of<br />

the four parameters involv<strong>ed</strong> in the specific spe<strong>ed</strong> expression. But by<br />

making the quite reasonable assumption that the low specific spe<strong>ed</strong> data<br />

collect<strong>ed</strong> by Karassik deriv<strong>ed</strong> from pumps at 3,600 RPM, direct comparison<br />

can be made as shown in Figure 11-3. The dott<strong>ed</strong> curves reflect the<br />

Karassik data <strong>and</strong> the solid curves represent P.E. performance at 3,600<br />

RPM. Distinct P.E. efficiency superiority is seen to exist at low specific<br />

spe<strong>ed</strong>s <strong>and</strong> low to m<strong>ed</strong>ium flow rates.

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