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

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Mechanical Seals 403 alignment, parallel misalignment, end play, and radial shaft runout (Figure 17-41). If wear has occurred between seal parts or between seal parts and a shaft sleeve or shaft, the pump should be checked for the type of condition illustrated and corrective measures should be taken. A pump must operate within the pump manufacturer's tolerances. Angular misalignment results when the mating ring is not square with the shaft. As shaft rotation begins, the primary ring will try to follow the surface of the mating ring. This often results in uneven wear of the softer carbon primary ring, possible internal wear of seal parts, fretting of seal hardware or shaft sleeve. Fretting on a shaft or shaft sleeve occurs when the protective oxide coating is removed from the metal by rubbing motion from a secondary seal in a pusher-type seal design. A hard coating on the shaft or shaft sleeve can be used to eliminate this type of wear. A full convolution elastomeric bellows is designed to protect the shaft or shaft sleeve by taking all the movement in the bellows convolution instead of along the shaft. Angular misalignment may also occur from a stuffing box that has been distorted by piping strain developed at operating temperatures. In this case, damage to the wear rings in the pump may also be found if the stuffing box has been distorted. Parallel misalignment results when the stuffing box is not properly aligned with the rest of the pump. Generally, with small amounts of parallel misalignment, the seal will operate properly. However, with a large amount of parallel misalignment, the shaft may strike the inside diameter of the mating ring. If damage has occurred, there will also be damage to any bushing located at the bottom of the stuffing box. The point of damage will be in the same location as that on the mating ring. Excessive axial end play can damage the sealing surfaces and can also cause fretting. If the seal is continually being loaded and unloaded, abrasives can penetrate the seal faces and cause premature wear of the primary and mating rings. Thermal damage in the form of heat checking on the seal faces can result if excessive end play occurs and the seal is operated below its working height. Radial runout in excess of limits established by the pump manufacturer will cause excessive vibration at the seal. This vibration, coupled with small amounts of other types of motion which have been defined, can shorten seal life. Radial runout from a bent shaft can damage the inside diameter of a mating ring through 36X3°. Seal installation begins with a review of the assembly instructions and any seal layout drawings. The proper seal installation dimension or spacing is required to ensure that the seal is at its proper working height (Figure 17-42). The installation reference can be determined by locating the face of the box on the surface of the sleeve and then measuring along the sleeve after it has been removed from the unit. It is not necessary to use
404 Centrifugal Pumps: Design and Application Figure 17-41. Common types of motion that influence seal performance and method of checking the equipment. this procedure if a step in the sleeve or collar has been designed into the sleeve assembly to provide for proper seal setting. Assembly of other parts of the seal will bring the unit to its correct working height. A single seal mounted as shown in Figure 17-42 is the most economical seal installation available to industry. Package seals as shown in Figure 17-26 can be assembled with relative ease because only the bolts on the gland plate and set screws in the collar need to be fastened to the stuffing box and shaft. After the spacer is removed, the pump is ready to operate, provided the piping has been replaced. Because a seal has precision lapped faces and secondary seal surfaces are critical in the assembly, installation should be kept as clean as possible. All lead edges on sleeves and gland plates should have sufficient chamfers to facilitate installation.
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CENTRIFIUGAL PUMPS Design & applica
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CENTRIFUGAL PUMPS Design & Applicat
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Contents Preface —..... —......
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ern Pumps, Mine Dewatering Pumps. W
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Stage Pumps. Single-Suction Single-
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Preface When Val and I decided to c
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CENTRIFUGAL PUMPS Design & applicat
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Part 1 Elements of Pump Design
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1 Introduction System Analysis for
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Introduction 5 Figure 1-2. The syst
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Introduction 7 mate responsibility
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Introduction 9 Figure 1-6. Maximum
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2 Specific Speed and Modeling Laws
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Specific Speed and Modeling Laws 13
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Figyre 2-7, New pump from model pum
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Impeller Design 29 Figure 3-1. Requ
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Impeller Design 31 Figure 3-4. Capa
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Impeller Design 33 Step 8: Estimate
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Impeller Design 35 Figure 3-7. Volu
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impeller Design 37 (2) 5 , as final
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Impeller Design 39 The vane develop
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Impeller Design 41 Figure 3-12. Are
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impeller Design 43 Figure 3-16. Inf
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4 General Pump Design It is not a d
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General Pump Design 4? Figure 4-1.
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General Pump Design 49 designed and
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Volute Design 51 Figure 5-1. Volute
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Volute Design 53 Figure 5-2. Radial
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Volute Design 55
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Volute Design 57 Figure 5-4. Effici
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Volute Design 59 Figure 5-5. Typica
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Volute Design 61 Figure 5-8. Univer
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Volute Design S3 Manufacturing Cons
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6 Design of Multi-Stage Casing Mult
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Design of Multi-Stage Casing 67 How
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Design of Multi-Stage Casing 69 Fig
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Design of Multi-Stage Casing 73 sec
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7 Double-Suction Pumps and Side-Suc
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Double-Suction Pumps 79 two. Experi
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Double-Suction Pumps 81 Figure 7-3.
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Double-Suction Pumps 83 LOCATION AR
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8 NPSH The expressions NPSHR and NP
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NPSH 87 Predicting NPSHR The other
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NPSH 89 Figure 8-4. Pressure loss b
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NPSH 91 SUCTION VELOCITY TRIANGLES
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NPSH 93 Figure 8-8. Performance cur
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NPSH 95 Figure 8-10. Leakage across
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NPSH 97 Figure 8-13. Plate inserts
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NPSH 99 Figure 8-17. Influence of p
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NPSH 101 Figure 8-19. Estimating K
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NPSH 103 Step 3: Determine KI* From
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Figure 8«22. Calculating NPSHA for
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NPSH 107 Figure 8-24. NPSHR cavitat
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NPSH 109 Notation KI Friction and a
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Part 2 Application
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9 by Erik B. Fiske BW/JP Internatio
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Vertical Pumps 115 Figure 9-2. Well
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Vertical Pumps 117 Figure 9-4. Subm
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Vertical Pumps 119 Figure 9-6. Inst
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Vertical Pumps 121 Figure 9-8. Barr
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Vertical Pumps 123 • Loading pump
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Vertical Pumps 125 Wet Pit Pumps Th
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Vertical Pumps 127 • Fresh water
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Vertical Pumps 129 Condensate and H
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Vertical Pumps 131 mally insulate w
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Vertical Pumps 133 Figure 9-15. Imp
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Vertical Pumps 135 checked for corr
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Vertical Pumps 137 crating paramete
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10 Pipeline Pipe line, Waterflood,
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Pipeline, Waterflood and CO 2 Pumps
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Pipeline, Waterfiood and CO 2 Pumps
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Figure 10-11. Performance change wi
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Figure 10-13. Seven-stage pump dest
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Pipeline, Waterflood and COa Pumps
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11 By Edward Gravelle Sundstrand Fl
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High Speed Pumps 175 History and De
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High Speed Pumps 177 Figure 11-2. (
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High Speed Pumps 179 some portion o
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High Speed Pumps 181 This is to say
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High Speed Pumps 183 This expressio
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High Speed Pumps 185 Figure 11-3. P
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High Speed Pumps 187 As an aside, p
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High Speed Pumps 189 Figure 11-5. I
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High Speed Pumps 191 Figure 11-7. I
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High Speed Pumps 193 Figure 11-9. R
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High Speed Pumps 195 Figure 11-10.
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High Speed Pumps 19? Figure 11-11.
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High Speed Pumps 199
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High Speed Pumps 201 Figure 11-13.
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High Speed Pumps 203 nal bearings a
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High Speed Pumps 205 Barske, U, M.,
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Double-Case Pumps 207 jected to ext
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Double-Case Pumps 209 Figure 12-3.
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Double-Case Pumps 213 ally by split
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Double-Case Pumps 215 The throttle
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Figure 12-11. pump for 4,000 psi In
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Double-Case Pumps 219 so that the t
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Doubte-Case Pumps 223 Volute Casing
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Double-Case Pumps 225 5. Survey of
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Slurry Pumps 227 An approximate com
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Slurry Pumps 229 Figure 13-2. Nomog
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Slurry Pumps 231 Table 13-2 Alloys
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Slurry Pumps 233 Figure 13-3. Class
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Figure 13-4, (A) (B) (C)
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Slurry Pumps 237 There is little to
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Figyre 13-7, (courtesy Pumps, Inc.)
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Flgyr« 13-8, with (courtesy Goulds
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Slurry Pumps 243 ing the pump speed
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Slurry Pumps 245 Where there exists
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Hydraulic Power Recovery Turbines 2
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Figure 14-14. Internally adjustable
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14-22, Flow of hydraulic recovery a
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15 by Frederic W. Buse Ingersolf-Ra
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Chemical Pumps Metallic and Nonmeta
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Driver Chemical Pumps Metallic and
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Part3 Mechanical Design
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16 Shaft Design and Axial Thrust Sh
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Shaft Design and Axial Thrust 335 S
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Shaft Design and Axial Thrust 337 W
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Shaft Design and Axial Thrust 339 T
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Shaft Design and Axial Thrust 341 b
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Shaft Design and Axial Thrust 343 K
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Double-Suction Single-Stage Pumps S
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Shaft Design and Axial Thrust 347 F
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Page 368 and 369: D (with subscript) P D P s T T (wit
Page 370 and 371: Mechanical Seals 355 Figure 17-1. M
Page 372 and 373: Mechanical Seats 357 Figure 17-2B.
Page 374 and 375: Mechanical Seals 359 Figure 17-2D.
Page 376 and 377: Mechanical Seals 361 Figure 17-4. H
Page 378 and 379: Mechanical Seals 363 Pressure-Veloc
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Page 388 and 389: Mechanical Seals 373 Classification
Page 390 and 391: Mechanical Seals 375 Double seals m
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Page 396 and 397: Mechanical Seals 381 Table 17-4 Tem
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Page 410 and 411: Mechanical Seals 395 The measured l
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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
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Page 446 and 447: Vibration and Noise in Pumps 431 Fi
Page 448 and 449: Vibration and Noise in Pumps 433 fi
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Page 452 and 453: Vibration and Noise in Pumps 437 up
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Vibration and Noise in Pumps 453 Re
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Vibration and Noise in Pumps 455 Fi
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Vibration and Noise in Pumps 457 Ac
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Vibration and Noise in Pumps 461 As
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Vibration and Noise in Pumps 463 ci
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Vibration and Noise in Pumps 467 sp
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Vibration and Noise in Pumps 469 Be
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Vibration and Noise in Pumps 475 Vi
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Vibration and Noise in Pumps 489 pe
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Vibration and Noise in Pumps 491 th
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Vibration and Noise in Pumps 4S3 fo
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Part 4 Extending Pump Life
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19 by Malcolm G. Murray, Jr. Murray
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Alignment 499 Figure 19-2. Pump dam
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Alignment 501 The best designs fail
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Table 19-1 Vertical Alignment Movem
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Table 19-2 Continued Horizontal Ali
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Alignment 507 bearing motors becaus
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Alignment 509 meet results. It shou
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Alignment 511 Determination of Tole
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Table 19-3 Continued Primary Alignm
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Alignment 515 Figure 19-3 A & B. Tw
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Table 19*4 Continued Methods of Cal
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Alignment 510 parallelism/perpendic
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Alignment 521 Table 19-5 continued
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Alignment 523 3. Essinger, J. N., B
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Rolling Element Bearings and Lubric
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Roiling Element Bearings and Lubric
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Roiling Element Bearings and Lubric
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Failure Analysis Mechanical Seal Re
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Table 21-2 Causes of Seal Failures
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Mechanical Seal Reliability 561 ^mi
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Mechanical Seal Reliability 563 Sea
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Mechanical Seal Reliability 565 run
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Reliability Mechanical Seal Reliabi
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Index A thermal growth, 519-522 ver
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Critical speed analysis. See also V
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Index 573 inlet angle, 37 classific
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Index 575 Shaft design, 333-343 ind
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double, 52-54 velocity ratio, 50-51
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Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)

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