Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)
Vibration and Noise in Pumps 463 cies and mode shapes are generally calculated by the Holzer method or by eigenvalue-eigenvector procedures [401. Either of the methods can give accurate results. A good design practice would be to locate the torsional natural frequencies a minimum margin of 10% from all potential excitation frequencies. An example of the mass-elastic diagram of a torsional system of a 3,600 rpm motor-driven, six-stage pipeline pump is given in Figure 18- 24. The natural frequencies and mode shapes associated with the first four natural frequencies are given in Figure 18-25. The mode shapes can be used to determine the most influential springs and masses in the system. This information is important if a resonance is found near the operating speed and system changes must be made to detune the frequencies. Figure 18-24. Mass-elastic diagram of six-stage pump train.
464 Centrifugal Pumps: Design and Application Parametric variations of the coupling stiffness should be made if changes are necessary, because most torsional problems can be solved by coupling changes. An interference diagram for the six-stage pipeline pump is given in Figure 18-26. In this system, excitation by several orders is possible as the pump is started; however, operation at 3,600 rpm has an adequate margin from the critical speeds. Once the system has been modeled and the natural frequencies have been determined, potential forcing functions should be identified. The forcing functions represent dynamic torques applied at locations in the system that are likely to generate torque varia- Figure 18-25. Torsional resonant mode shapes of six-stage pump train.
- Page 428 and 429: Mechanical Seals 413 Figure 17-51.
- Page 430 and 431: Mechanical Seals 415 Figure 17-53.
- Page 432 and 433: Mechanical Seals 417 Figure 17-55.
- Page 434 and 435: Mechanical Seats 419 Figure 17-58.
- Page 436 and 437: Vibration and Noise in Pumps 421 Re
- Page 438 and 439: Vibration and Noise in Pumps 423 me
- Page 440 and 441: Vibration and Noise in Pumps 425 in
- Page 442 and 443: Vibration and Noise in Pumps 427 pr
- Page 444 and 445: Vibration and Noise in Pumps 429 ot
- Page 446 and 447: Vibration and Noise in Pumps 431 Fi
- Page 448 and 449: Vibration and Noise in Pumps 433 fi
- Page 450 and 451: Vibration and Noise in Pumps 435 pr
- Page 452 and 453: Vibration and Noise in Pumps 437 up
- Page 454 and 455: Vibration and Noise in Pumps 439 Fi
- Page 456 and 457: Vibration and Noise in Pumps 441 na
- Page 458 and 459: Vibration and Noise in Pumps 443 A
- Page 460 and 461: Vibration and Noise in Pumps 445 Fi
- Page 462 and 463: Vibration and Noise in Pumps 447 Fi
- Page 464 and 465: Vibration and Noise in Pumps 449 Fi
- Page 466 and 467: Vibration and Noise in Pumps 451 Fi
- Page 468 and 469: Vibration and Noise in Pumps 453 Re
- Page 470 and 471: Vibration and Noise in Pumps 455 Fi
- Page 472 and 473: Vibration and Noise in Pumps 457 Ac
- Page 474 and 475: Vibration and Noise in Pumps 459 Fi
- Page 476 and 477: Vibration and Noise in Pumps 461 As
- Page 480 and 481: Vibration and Noise in Pumps 465 Fi
- Page 482 and 483: Vibration and Noise in Pumps 467 sp
- Page 484 and 485: Vibration and Noise in Pumps 469 Be
- Page 486 and 487: Vibration and Noise in Pumps 471 Fi
- Page 488 and 489: Vibration and Noise in Pumps 473 Fi
- Page 490 and 491: Vibration and Noise in Pumps 475 Vi
- Page 492 and 493: Vibration and Noise in Pumps 477 Fi
- Page 494 and 495: Vibration and Noise in Pumps 479 Fi
- Page 496 and 497: Vibration and Noise in Pumps 481 Fi
- Page 498 and 499: Vibration and Noise in Pumps 483 Fi
- Page 500 and 501: Vibration and Noise in Pumps 485 Fi
- Page 502 and 503: Vibration and Noise in Pumps 487 Fi
- Page 504 and 505: Vibration and Noise in Pumps 489 pe
- Page 506 and 507: Vibration and Noise in Pumps 491 th
- Page 508 and 509: Vibration and Noise in Pumps 4S3 fo
- Page 510 and 511: Part 4 Extending Pump Life
- Page 512 and 513: 19 by Malcolm G. Murray, Jr. Murray
- Page 514 and 515: Alignment 499 Figure 19-2. Pump dam
- Page 516 and 517: Alignment 501 The best designs fail
- Page 518 and 519: Table 19-1 Vertical Alignment Movem
- Page 520 and 521: Table 19-2 Continued Horizontal Ali
- Page 522 and 523: Alignment 507 bearing motors becaus
- Page 524 and 525: Alignment 509 meet results. It shou
- Page 526 and 527: Alignment 511 Determination of Tole
464 <strong>Centrifugal</strong> <strong>Pumps</strong>: <strong>Design</strong> <strong>and</strong> <strong>Application</strong><br />
Parametric variations of the coupling stiffness should be made if changes<br />
are necessary, because most torsional problems can be solv<strong>ed</strong> by coupling<br />
changes.<br />
An interference diagram for the six-stage pipeline pump is given in<br />
Figure 18-26. In this system, excitation by several orders is possible as<br />
the pump is start<strong>ed</strong>; however, operation at 3,600 rpm has an adequate<br />
margin from the critical spe<strong>ed</strong>s. Once the system has been model<strong>ed</strong> <strong>and</strong><br />
the natural frequencies have been determin<strong>ed</strong>, potential forcing functions<br />
should be identifi<strong>ed</strong>. The forcing functions represent dynamic torques<br />
appli<strong>ed</strong> at locations in the system that are likely to generate torque varia-<br />
Figure 18-25. Torsional resonant mode shapes of six-stage pump train.