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

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Impeller Design 39 The vane development and layout for the back shroud is done in the same manner, taking into account the required hub vane angle. This procedure should result in Point 10 reaching the estimated hub vane diameter. If this diameter is missed by more than ! /4-in., the hub vane angle should be changed and the layout repeated. Complete the vane layout by adding vane thickness (Figure 3-11) and indicating a slight underfile at the vane OD and a thinning at the suction, This underfile will produce higher head and improved efficiency. The vane spacing location of the second vane on the end view will be determined by the number of vanes. At this point it is necessary to check the ratio of the vane area A v to the suction eye area A e . Referring to Figure 3-12, this ratio should be 0.4 to 0,6. The area A v is the area which is shaded on the plan view. If the area ratio falls outside the limits shown, it will be necessary to change the plan view profile and/or vane thickness. Pumps in the higher specific speed range (N s 1,000-5,000) have suction velocity triangles that dictate different suction vane angularity at the impeller hub and impeller eye. This difference in angularity restricts vane removal from the core box, requiring a segmented core and more costly patterns and casting. Hydraulically, it is very necessary, and we must learn to live with it. On low specific speeds however, (N s 500- 1000) a straight vane is acceptable and will not jeopardize hydraulic performance, Design Suggestions The following points should be kept in mind when designing an impeller. • Standardize the relationship between the number of vanes and discharge vane angle. The relationship shown in Figure 3-13 is suggested. Number and angularity of vanes greatly affect H-Q pump performance. Standardization as shown will lead to more accurate perfor mance prediction. • Figure 3-14 shows the effect of the number of impeller vanes in the same casing, on H-Q performance. Please note that with less vanes, the lower is the BEP head and efficiency and steeper is the shape of H-Q curve. » It is possible to maintain same BEP, Q, and efficiency by increasing b 2 where number of vanes and angularity are reduced (Figure 3-15). For best efficiency, the velocity ratio between volute and impeller peripheral must be maintained. Similarly for the same impeller diameter, vane number and discharge angle BEP will change with change in b 2 (Figure 3-16). • Avoid using even number of vanes in double volute pumps.
40 Centrifugal Pumps: Design and Application IMP.DIA MIN. VANE THICKNESS O.D. MIDDLE INLET MIN. SHROUD THICKNESS t, t 2 > 6-11 7/32 5/16 1/8 1/8 3/16 > 11-15 1/4 3/8 3/16 5/32 5/16 > 15-19 9/32 7/16 3/16 3/16 3/8 > 19-23 5/16 1/2 1/4 7/32 7/16 > 23-31 11/32 9/16 1/4 1/4 9/16 > 31-35 3/8 5/8 5/16 5/16 5/8 > 35-39 7/16 11/16 5./16 3/8 11/16 > 39-50 1/2 3/4 3/8 7/16 3/4 Figure 3-11. Recommended minimum impeller vane and shroud thickness for castability (standard cast materials).
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CENTRIFIUGAL PUMPS Design & applica
Page 4 and 5: CENTRIFUGAL PUMPS Design & Applicat
Page 6 and 7: Contents Preface —..... —......
Page 8 and 9: ern Pumps, Mine Dewatering Pumps. W
Page 10 and 11: Stage Pumps. Single-Suction Single-
Page 12 and 13: Preface When Val and I decided to c
Page 14 and 15: CENTRIFUGAL PUMPS Design & applicat
Page 16 and 17: Part 1 Elements of Pump Design
Page 18 and 19: 1 Introduction System Analysis for
Page 20 and 21: Introduction 5 Figure 1-2. The syst
Page 22 and 23: Introduction 7 mate responsibility
Page 24 and 25: Introduction 9 Figure 1-6. Maximum
Page 26 and 27: 2 Specific Speed and Modeling Laws
Page 28 and 29: Specific Speed and Modeling Laws 13
Page 38 and 39: Figyre 2-7, New pump from model pum
Page 44 and 45: Impeller Design 29 Figure 3-1. Requ
Page 46 and 47: Impeller Design 31 Figure 3-4. Capa
Page 48 and 49: Impeller Design 33 Step 8: Estimate
Page 50 and 51: Impeller Design 35 Figure 3-7. Volu
Page 52 and 53: impeller Design 37 (2) 5 , as final
Page 56 and 57: Impeller Design 41 Figure 3-12. Are
Page 58 and 59: impeller Design 43 Figure 3-16. Inf
Page 60 and 61: 4 General Pump Design It is not a d
Page 62 and 63: General Pump Design 4? Figure 4-1.
Page 64 and 65: General Pump Design 49 designed and
Page 66 and 67: Volute Design 51 Figure 5-1. Volute
Page 68 and 69: Volute Design 53 Figure 5-2. Radial
Page 70 and 71: Volute Design 55
Page 72 and 73: Volute Design 57 Figure 5-4. Effici
Page 74 and 75: Volute Design 59 Figure 5-5. Typica
Page 76 and 77: Volute Design 61 Figure 5-8. Univer
Page 78 and 79: Volute Design S3 Manufacturing Cons
Page 80 and 81: 6 Design of Multi-Stage Casing Mult
Page 82 and 83: Design of Multi-Stage Casing 67 How
Page 84 and 85: Design of Multi-Stage Casing 69 Fig
Page 88 and 89: Design of Multi-Stage Casing 73 sec
Page 92 and 93: 7 Double-Suction Pumps and Side-Suc
Page 94 and 95: Double-Suction Pumps 79 two. Experi
Page 96 and 97: Double-Suction Pumps 81 Figure 7-3.
Page 98 and 99: Double-Suction Pumps 83 LOCATION AR
Page 100 and 101: 8 NPSH The expressions NPSHR and NP
Page 102 and 103: 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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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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