Fluid Mechanics and Thermodynamics of Turbomachinery, 5e

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(6.38) after combining with eqn. (6.33), noting that dh02/dr = 0 and that (d/dr)(rc q2) = 0 at all mass flows. From eqn. (6.37), which when substituted into eqn. (6.38) gives After rearranging, Equation (6.39) is immediately integrated in the form Three-dimensional Flows in Axial Turbomachines 193 FIG. 6.7. Design and off-design velocity triangles for a free-vortex turbine stage. (6.39) (6.40) where cx3 = cx3m at r = rm. Equation (6.40) is more conveniently expressed in a nondimensional form by introducing flow coefficients f = cx3/U m, f* = c* x3/U m and f m = cx3m/U m. Thus,
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Fluid Mechanics, Thermodynamics of
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Preface to the Fifth Edition In the
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Preface to the Fourth Edition It is
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Preface to Third Edition Several mo
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List of Symbols A area A2 area of a
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z enthalpy loss coefficient, total
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Contents PREFACE TO THE FIFTH EDITI
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Velocity diagrams of the compressor
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10. Wind Turbines 323 Introduction
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2 Fluid Mechanics, Thermodynamics o
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10 Fluid Mechanics, Thermodynamics
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CHAPTER 2 Basic Thermodynamics, Flu
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CHAPTER 3 Two-dimensional Cascades
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CHAPTER 4 Axial-flow Turbines: Two-
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Page 370: 168 Fluid Mechanics, Thermodynamics
Page 424: Three-dimensional Flows in Axial Tu
Page 428: velocity undergoes an abrupt change
Page 432: adding these to the related radial
Page 444: References Adamczyk, J. J. (2000).
Page 448: and the axial velocity is constant
Page 452: engine turbochargers, chemical plan
Page 456: Centrifugal Pumps, Fans and Compres
Page 460: or since Since I1 = I2 across the i
Page 464: For the inlet geometry shown in Fig
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(Mr1) = mW 2 /(p k p 01 a01 3 ) ·
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(iii) Use of prewhirl at entry to i
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(7.13a) where cq2 is the tangential
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Centrifugal Pumps, Fans and Compres
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(number of blades). He also found t
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Determining the velocities and head
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efficiencies seldom exceeded 80% gi
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Centrifugal Pumps, Fans and Compres
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efficiently converting this energy
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Therefore Hence, The diffuser syste
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Dq (deg) 240 160 80 Centrifugal Pum
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(7.41) If choking occurs in the rot
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Van den Braembussche, R. (1985). De
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Assuming that the hydraulic efficie
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Radial Flow Gas Turbines 247 FIG. 8
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Basic design of the rotor Radial Fl
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Radial Flow Gas Turbines 253 (8.9)
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Thus, the total-to-static efficienc
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Now, Loss coefficients in 90deg IFR
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P S P S c 2 Direction of rotation (
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and, combining this with eqns. (8.2
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(ii) Rewriting eqn. (8.26), (iii) U
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Thus, combining eqns. (8.39) and (8
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U 2/c o 0.8 0.7 0.6 88 Radial Flow
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(a) the static pressure at rotor ex
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(a) (2) (1) w 2 b2 ¢ w 2 ¢ b2, op
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Radial Flow Gas Turbines 273 This e
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Radial Flow Gas Turbines 279 occurs
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(a) f = 0.83 a 0 = q 0 U 0 = -7.18
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Measured performance Radial Flow Ga
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Radial Flow Gas Turbines 287 Whitfi
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Radial Flow Gas Turbines 289 Absolu
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Hydraulic Turbines 291 TABLE 9.1. D
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TABLE 9.3. Operating ranges of hydr
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Hydraulic Turbines 295 ridge splits
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Hydraulic Turbines 297 (9.3) (9.4)
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Hydraulic Turbines 299 FIG. 9.8. Me
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Hydraulic Turbines 301 (9.10) The e
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Neglecting bearing and windage loss
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Hydraulic Turbines 305 Figure 9.12
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Hydraulic Turbines 307 It is of int
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Hydraulic Turbines 309 constant. Th
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(a) (b) Hydraulic Turbines 311 FIG.
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TABLE 9.4. Calculated values of flo
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Hydraulic Turbines 315 gave measure
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Hydraulic Turbines 317 using Thoma
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Avoiding cavitation Hydraulic Turbi
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Hydraulic Turbines 321 nozzles. The
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CHAPTER 10 Wind Turbines Take care
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FIG. 10.2. Tower Windmill, Bidston,
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Brake discs Flexible coupling Build
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Small HAWTs Small wind turbines wit
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(iii) no flow rotation produced by
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It is convenient to define an axial
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Example 10.2. Determine the radii o
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where a - T = 0.3262. Sharpe (1990)
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each element must have an associate
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In the actuator disc analysis the v
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operate in post-stall conditions wh
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Solving the equations The foregoing
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Pitch angle, b (deg) 30 20 10 0 0.2
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TABLE 10.4. Data used for summing t
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F 1.0 0.8 0.6 0.4 0.2 0 0.4 dX = 4
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TABLE 10.5. Summary of results for
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Power coefficient, C P 0.6 0.4 0.2
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C X/(JC L) 0.14 0.12 0.10 0.08 0.06
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The flow angle j at optimum power c
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R 1 2 3 8 3 CP = P ( prR cx )= ( -a
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caused by this increased roughness
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Airfoil S820 S819 r/R 0.95 0.75 pro
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Airfoil S817 S816 r/R 0.95 0.75 NRE
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C C 0.4 0.2 -0 -0.2 -0.4 -0.6 twist
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According to Tangler (2002), some l
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understanding of the complex phenom
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References Wind Turbines 375 Abbott
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Bibliography Cumpsty, N. A. (1989).
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APPENDIX 2 Answers to Problems Chap
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Chapter 8 1. 586 m/s, 73.75 deg. 2.
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Index Terms Links Axial flow compre
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Index Terms Links Cascades, two-dim
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Index Terms Links Coefficient of, c
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Index Terms Links Diffusers (Cont.)
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Index Terms Links Francis turbine 2
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Index Terms Links Illustrative exam
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Index Terms Links Mollier diagram,
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Index Terms Links Pressure head 4 P
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Index Terms Links Rotor configurati
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Index Terms Links Thoma’s coeffic
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Index Terms Links U Units Imperial
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