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

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High Speed Pumps 191 Figure 11-7. Inducer family for partial emission pumps (courtesy Sundstrand) blades, razor sharp edges, etc., but rather a useful "optimum" relating reasonable suction performance expectation to the inlet flow coefficient. The Brumfield suction performance can be exceeded with well-designed inducers. Tradeoff or compromise is not always required in performance and cavitation considerations, because modest speed, small inducers, or low specific gravity fluids can result in operating regimes far removed from cavitation concern. Substantial effort has been devoted to inducer development and will undoubtedly continue in the future, since inducers are a key element in extending the frontiers of high-speed pump technol- ogy- A family of inducers for RE. pumps is shown in Figure 11-7 which range from 1.25 to 3.5 inches in diameter and provide coverage from Q/ N = .0005 to .1. Partial Emission Design Evolution Beyond the very substantial NPSHR improvement provided by inducers, improvement of the concentric bowl pump has been pursued in other areas including efficiency, curve shape, and noise reduction. Positive results have been achieved in all three of these areas as summarized below. Areas exist where the concentric bowl pump is wanting by a few efficiency points to be more fully competitive with other pump types. A clue
192 Centrifugal Pumps: Design and Application Figure 11-8. Diagram of concentric bowl static pressures and flows. to a basic hydraulic "fault" in the concentric bowl pump exists in the eyeto-throat flow path described in the section "Terminology." The sketch in Figure 11-8 illustrates a concentric bowl pump, where the dashed line represents a polar plot of static pressure within the bowl. The static pressure is depressed in the vicinity of pump discharge, and this depression increases with increasing flow rate. This indicates unfavorable exchange of static head for velocity head in the area of discharge, which must be reconverted to static head in the diffuser. Furthermore, fluid approaches the discharge throat in the direction indicated by vector c, the vector sum of U2 and v r , detracting from the diffuser recovery potential. These adversities can be eliminated by abandoning the concentric bowl geometry in favor of a volute collector geometry. This modification has been shown to improve efficiency by about 6 points with specific speeds in the range of N s = 800 to 1,000, but this advantage fades to parity with the concentric bowl configuration at specific speeds of about N s = 300 to 400. Radial side load results from standing pressure variations around the impeller periphery. These hydraulically imposed radial loads are proportional to the product of pump head times the projected area of the impeller, and must be reckoned with from the standpoint of bearing loads. Side load trends vary dramatically with the pump design geometry as indicated in Figure 11-9, where magnitudes are shown in the upper plot and vector direction trends are shown by the polar plots within the lower fig-
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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,
Page 156 and 157: Pipeline, Waterflood and CO 2 Pumps
Page 162 and 163: Pipeline, Waterfiood and CO 2 Pumps
Page 164 and 165: Figure 10-11. Performance change wi
Page 166 and 167: Figure 10-13. Seven-stage pump dest
Page 178 and 179: Pipeline, Waterflood and COa Pumps
Page 188 and 189: 11 By Edward Gravelle Sundstrand Fl
Page 190 and 191: High Speed Pumps 175 History and De
Page 192 and 193: High Speed Pumps 177 Figure 11-2. (
Page 194 and 195: High Speed Pumps 179 some portion o
Page 196 and 197: High Speed Pumps 181 This is to say
Page 198 and 199: High Speed Pumps 183 This expressio
Page 200 and 201: High Speed Pumps 185 Figure 11-3. P
Page 202 and 203: High Speed Pumps 187 As an aside, p
Page 204 and 205: High Speed Pumps 189 Figure 11-5. I
Page 208 and 209: High Speed Pumps 193 Figure 11-9. R
Page 210 and 211: High Speed Pumps 195 Figure 11-10.
Page 212 and 213: High Speed Pumps 19? Figure 11-11.
Page 214 and 215: High Speed Pumps 199
Page 216 and 217: High Speed Pumps 201 Figure 11-13.
Page 218 and 219: High Speed Pumps 203 nal bearings a
Page 220 and 221: High Speed Pumps 205 Barske, U, M.,
Page 222 and 223: Double-Case Pumps 207 jected to ext
Page 224 and 225: Double-Case Pumps 209 Figure 12-3.
Page 228 and 229: Double-Case Pumps 213 ally by split
Page 230 and 231: Double-Case Pumps 215 The throttle
Page 232 and 233: Figure 12-11. pump for 4,000 psi In
Page 234 and 235: Double-Case Pumps 219 so that the t
Page 238 and 239: Doubte-Case Pumps 223 Volute Casing
Page 240 and 241: Double-Case Pumps 225 5. Survey of
Page 242 and 243: Slurry Pumps 227 An approximate com
Page 244 and 245: Slurry Pumps 229 Figure 13-2. Nomog
Page 246 and 247: Slurry Pumps 231 Table 13-2 Alloys
Page 248 and 249: Slurry Pumps 233 Figure 13-3. Class
Page 250 and 251: Figure 13-4, (A) (B) (C)
Page 252 and 253: Slurry Pumps 237 There is little to
Page 254 and 255: 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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D (with subscript) P D P s T T (wit
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Mechanical Seals 355 Figure 17-1. M
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Mechanical Seats 357 Figure 17-2B.
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Mechanical Seals 359 Figure 17-2D.
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Mechanical Seals 361 Figure 17-4. H
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Mechanical Seals 363 Pressure-Veloc
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Mechanical Seals 365 The temperatur
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Mechanical Seals 367 Figure 17-7. B
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Mechanical Seals 369 Figure 17-9. P
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Mechanical Seals 371 where C 3 = 53
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Mechanical Seals 373 Classification
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Mechanical Seals 375 Double seals m
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Mechanical Seals 377 less than 100,
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Mechanical Seals 379 Figure 17-19.
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Mechanical Seals 381 Table 17-4 Tem
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Mechanical Seats 385 steam, is to p
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Mechanical Seats 38? rather than a
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Mechanical Seals 389 Mechanical Sea
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Mechanical Seals 391 seal to work i
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Mechanical Seals 395 The measured l
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Mechanical Seals 39? Figure 17-34.
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Mechanical Seals 401 This design is
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Mechanical Seals 403 alignment, par
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Mechanical Seats 419 Figure 17-58.
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Vibration and Noise in Pumps 421 Re
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Vibration and Noise in Pumps 423 me
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Vibration and Noise in Pumps 425 in
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Vibration and Noise in Pumps 427 pr
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Vibration and Noise in Pumps 429 ot
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Vibration and Noise in Pumps 431 Fi
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Vibration and Noise in Pumps 433 fi
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Vibration and Noise in Pumps 435 pr
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Vibration and Noise in Pumps 437 up
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Vibration and Noise in Pumps 441 na
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Vibration and Noise in Pumps 443 A
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Vibration and Noise in Pumps 453 Re
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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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