Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)
Vibration and Noise in Pumps 485 Figure 18-40. Pump shaft vibration orbits. times as long. A cascade plot of the vibration data (Figure 18-41) showed that just before trip of the unit at 21,960 rpm, an instability vibration component occurred near 15,000 cpm. From this and other data, it was determined that the high vibrations were caused by: • A sudden increase in nonsynchronous vibration as the unit approached full speed resulting in shaft bow. « A sudden increase in unbalance due to the shaft bow and as a result, a rapid increase in synchronous vibration levels as the nonsynchronous components disappeared. After the problem source was identified using the above data analysis technique, computer simulation of the rotor led to a solution consisting of bearing modifications. The stability analysis of the pump rotor predicted that the pump had an unstable mode at 15,000 cpm with a negative loga-
486 Centrifugal Pumps: Design and Application Figure 18-41. Nonsynchronous instability vibration of high speed pump. rithmic decrement of 0.01 for a simulated fluid aerodynamic loading of 1,000 Ib/in. at the impellers [36, 47]. The pump rotor with the modified bearings was predicted to have a positive logarithmic decrement of 0.10. The rotor vibrations after the bearing modifications were made are shown in Figure 18-42. The nonsynchronous vibration component was no longer present and the unit has since operated successfully. Appendix Acoustic Velocity of Liquids The acoustic velocity of liquids can be written as a function of the isentropic bulk modulus, K s and the specific gravity: where c = acoustic velocity, ft/sec sp gr = specific gravity K s = isentropic (tangent) bulk modulus, psi
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486 <strong>Centrifugal</strong> <strong>Pumps</strong>: <strong>Design</strong> <strong>and</strong> <strong>Application</strong><br />
Figure 18-41. Nonsynchronous instability vibration of high spe<strong>ed</strong> pump.<br />
rithmic decrement of 0.01 for a simulat<strong>ed</strong> fluid aerodynamic loading of<br />
1,000 Ib/in. at the impellers [36, 47]. The pump rotor with the modifi<strong>ed</strong><br />
bearings was pr<strong>ed</strong>ict<strong>ed</strong> to have a positive logarithmic decrement of 0.10.<br />
The rotor vibrations after the bearing modifications were made are<br />
shown in Figure 18-42. The nonsynchronous vibration component was<br />
no longer present <strong>and</strong> the unit has since operat<strong>ed</strong> successfully.<br />
Appendix<br />
Acoustic Velocity of Liquids<br />
The acoustic velocity of liquids can be written as a function of the isentropic<br />
bulk modulus, K s <strong>and</strong> the specific gravity:<br />
where<br />
c = acoustic velocity, ft/sec<br />
sp gr = specific gravity<br />
K s = isentropic (tangent) bulk modulus, psi