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

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

diameter, viscosity, load, spe<strong>ed</strong>, clearance, <strong>and</strong> the Sommerfeld number<br />

that is defin<strong>ed</strong> as:<br />

l*. = lubricant viscosity, Ib-sec/in.<br />

N = rotor spe<strong>ed</strong>, rev/sec<br />

D = bearing diameter, in.<br />

L = bearing length, in.<br />

R = bearing radius, in.<br />

W = bearing load, Ibs<br />

C = radial machin<strong>ed</strong> clearance, in,<br />

The normal proc<strong>ed</strong>ure in a design audit would be to calculate the bearing<br />

characteristics for the range of expect<strong>ed</strong> clearances, preload, <strong>and</strong> oil<br />

temperatures. The maximum clearance, minimum preload, <strong>and</strong> highest<br />

oil temperature usually define the minimum stiffness. The other extreme<br />

is obtain<strong>ed</strong> from the minimum clearance, maximum preload, <strong>and</strong> the<br />

coldest oil temperature. This will typically define the range of expect<strong>ed</strong><br />

stiffness <strong>and</strong> damping coefficients for the bearings.<br />

Preload is a configuration of the bearing clearances to promote a converging<br />

w<strong>ed</strong>ge of oil that increases the oil pressure <strong>and</strong> consequently the<br />

bearing stiffnesses. A preload<strong>ed</strong> bearing has its radius of curvature<br />

greater than the shaft radius plus the clearance.<br />

Seal Effects<br />

The critical spe<strong>ed</strong> map for a eight-stage pump, including the effects of<br />

seal <strong>and</strong> bearing stiffness, is given in Figure 18-15. Even though the<br />

bearings <strong>and</strong> seals add considerable cross-coupling <strong>and</strong> damping, it is<br />

still desirable to generate an undamp<strong>ed</strong> critical spe<strong>ed</strong> map to establish the<br />

range of the undamp<strong>ed</strong> (dry) critical spe<strong>ed</strong>s.<br />

Adequate experimental data exists that documents that the analytical<br />

proc<strong>ed</strong>ures us<strong>ed</strong> for simulating rotor response <strong>and</strong> stability for compressors<br />

<strong>and</strong> turbines can accurately pr<strong>ed</strong>ict critical spe<strong>ed</strong>s <strong>and</strong> potential instabilities<br />

from the design information. This is not true for pumps, especially<br />

for pumps that use groov<strong>ed</strong> seals, labyrinth seals, or screw type<br />

seals with several leads. The accurate pr<strong>ed</strong>iction of the stiffness <strong>and</strong><br />

damping properties of seals for different geometries <strong>and</strong> operating conditions<br />

is a subject of on-going research [22, 27, 28]. The basic theories<br />

present<strong>ed</strong> by Black [29] have been modifi<strong>ed</strong> to account for finite length

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