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12.5 Dimensionless Parameters and Similarity Laws 669<br />

8<br />

⋅ ⋅<br />

W shaft1 /W shaft2<br />

6<br />

Q 1 /Q 2<br />

4<br />

2<br />

h a1 /h a2<br />

0<br />

0 0.5 1 1.5 2<br />

D 1 /D 2<br />

Pump affinity laws<br />

relate the same<br />

pump at different<br />

speeds or geometrically<br />

similar pumps<br />

at the same speed.<br />

and<br />

W # shaft1<br />

W # shaft2<br />

D5 1<br />

D 5 2<br />

(12.41)<br />

Thus, for a family of geometrically similar pumps operating at a given speed and the same flow<br />

coefficient, the flow varies as the diameter cubed, the head varies as the diameter squared, and the<br />

power varies as the diameter raised to the fifth power. These strong effects of diameter variation<br />

are illustrated in the sketch in the margin. These scaling relationships are based on the condition<br />

that, as the impeller diameter is changed, all other important geometric variables are properly scaled<br />

to maintain geometric similarity. This type of geometric scaling is not always possible due to practical<br />

difficulties associated with manufacturing the pumps. It is common practice for manufacturers<br />

to put impellers of different diameters in the same pump casing. In this case, complete geometric<br />

similarity is not maintained, and the scaling relationships expressed in Eqs. 12.39, 12.40, and 12.41<br />

will not, in general, be valid. However, experience has shown that if the impeller diameter change<br />

is not too large, less than about 20%, these scaling relationships can still be used to estimate the<br />

effect of a change in the impeller diameter. The pump similarity laws expressed by Eqs. 12.36<br />

through 12.41 are sometimes referred to as the pump affinity laws.<br />

The effects of viscosity and surface roughness have been neglected in the foregoing similarity<br />

relationships. However, it has been found that as the pump size decreases these effects more<br />

significantly influence efficiency because of smaller clearances and blade size. An approximate,<br />

empirical relationship to estimate the influence of diminishing size on efficiency is 1Ref. 92<br />

1 h 2<br />

a D 15<br />

1<br />

b<br />

1 h 1 D 2<br />

(12.42)<br />

In general, it is to be expected that the similarity laws will not be very accurate if tests on a model<br />

pump with water are used to predict the performance of a prototype pump with a highly viscous<br />

<strong>fluid</strong>, such as oil, because at the much smaller Reynolds number associated with the oil flow, the<br />

<strong>fluid</strong> physics involved is different from the higher Reynolds number flow associated with water.<br />

12.5.2 Specific Speed<br />

A useful pi term can be obtained by eliminating diameter D between the flow coefficient and the<br />

head rise coefficient. This is accomplished by raising the flow coefficient to an appropriate exponent<br />

1122 and dividing this result by the head coefficient raised to another appropriate exponent<br />

1342 so that<br />

1QvD 3 2 1 2<br />

1gh av 2 D 2 2 3 4 v1Q<br />

1gh a 2 3 4 N s<br />

(12.43)<br />

The dimensionless parameter N s is called the specific speed. Specific speed varies with flow coefficient<br />

just as the other coefficients and efficiency discussed earlier do. However, for any pump it<br />

is customary to specify a value of specific speed at the flow coefficient corresponding to peak efficiency<br />

only. For pumps with low Q and high h a , the specific speed is low compared to a pump<br />

with high Q and low h a . Centrifugal pumps typically are low-capacity, high-head pumps, and therefore<br />

have low specific speeds.<br />

Specific speed as defined by Eq. 12.43 is dimensionless, and therefore independent of the system<br />

of units used in its evaluation as long as a consistent unit system is used. However, in the United<br />

States a modified, dimensional form of specific speed, N sd , is commonly used, where<br />

v1rpm2 1Q1gpm2<br />

N sd <br />

3h a 1ft24 3 4<br />

(12.44)<br />

In this case N sd is said to be expressed in U.S. customary units. Typical values of N sd are in the<br />

range 500 6 N sd 6 4000 for centrifugal pumps. Both N s and N sd have the same physical meaning,<br />

but their magnitudes will differ by a constant conversion factor 1N sd 2733 N s 2 when v in<br />

Eq. 12.43 is expressed in rads.<br />

Each family or class of pumps has a particular range of values of specific speed associated with<br />

it. Thus, pumps that have low-capacity, high-head characteristics will have specific speeds that are

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