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

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High Speed Pumps 193 Figure 11-9. Radial load trends. ures along with the letters S, D, and C, indicating shutoff, design, and cutoff flow rates. The concentric bowl side load increases continuously with flow and is always oriented in the general direction of the discharge throat. The volute radial load virtually vanishes at design flow, but undergoes about a 180° reversal in direction over the full flow range. These considerations are significant when fluid film bearings are used and the lube feed spreader groove location must not encroach into the bearing load zones.
194 Centrifugal Pumps: Design and Application Change to a volute collector raises the question of terminology, since fluid exists via the full impeller periphery and it may be asked whether or not the description "partial emission" should be abandoned. On balance, tall radial blade geometry is carried over from the concentric bowl de sign, so the impeller emission area remains much larger than the discharge throat area. Disorderly flow conditions similar to those in concentric bowl design prevail due both to retention of tall blades and the radial inlet geometry. The volute modification perhaps is most accurately viewed as a P.E./F.E. transitional design, but we will choose here to remain with the P.E. classification, in part because this modification stems from the original concentric bowl concept to which the P.E. designation clearly applies. Further efficiency improvement is possible through optimization of the inlet eye diameter. By analytic means, this optimum has been established as: Test experience has shown that optimum eye sizing can improve efficiency by about four points over that attainable with large eye diameters on the order of twice the optimum diameter, which are often used in the interest of minimizing NPSHR. Equation 11-17 shows that eye size influences NPSHR as a fourth power function of diameter, so freedom to exploit the eye size efficiency advantage often does not exist. For inducerless design and ample NPSHA, near-optimum eye sizing should always be used. This situation nearly always exists, for example, in stage 2 of series-staged machines. Curve shape improvement and noise reduction have been achieved through use of high-solidity impellers, i.e., by adding more impeller blades, which increases the ratio of blade cord length to blade spacing. High-solidity impellers tend toward minimizing flow stratification and blade loading because the total power is divided between a larger blade complement. To obtain benefit with high solidity impellers, it is necessary that all blades penetrate equally into the impeller eye. Use of splitter geometry or blades alternating in length as is often done in turbomachines to avoid eye crowding results in dominance of the larger blades and provides no advantage in P.E. pumps. A rising-to-shutoff or stable curve shape can be provided with high solidity radial-bladed impellers as shown by the solid curve in Figure 11 10. This is contrary to the generally held view that backswept blade dasign is essential to providing a stable curve. The reason that improved curve shape results with high-solidity impellers is believed to lie with im-
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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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Page 164 and 165: Figure 10-11. Performance change wi
Page 166 and 167: Figure 10-13. Seven-stage pump dest
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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 206 and 207: High Speed Pumps 191 Figure 11-7. I
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
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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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