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Handbook of Turbomachinery Second Edition Revised - Ventech!
Handbook of Turbomachinery Second Edition Revised - Ventech!
Handbook of Turbomachinery Second Edition Revised - Ventech!
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Figure 38 Straddle mounted rotor. (a) Critical speed map, (b) mode shapes.<br />
Copyright © 2003 Marcel Dekker, Inc.
and a 1.00-in. (2.54-cm) outer radius, bearings at 2.0 and 18.0 in. (5.08 and 45.72 cm), a 15.44-lbm (7.00-kg) disk at 5.0 in. (12.70 cm), and a 23.16-lbm (10.51-kg) disk at 15.0in. (38.10cm). The critical speed map <strong>of</strong> Fig. 38(a) shows how the first four synchronous whirl speeds change with bearing support stiffness. The corresponding mode shapes are shown in Fig. 38(b) for a bearing support stiffness <strong>of</strong> 100,000 lbf/in. (17.51 MN/m). The first two critical speeds are support dominated ‘‘rigid-body’’ modes with most <strong>of</strong> the strain energy in the bearing supports. These critical speeds are associated with the ‘‘cylindrical’’ and ‘‘conical’’ modes in which the two ends <strong>of</strong> the rotor whirl in-phase and out-<strong>of</strong>-phase, respectively. The third and fourth critical speeds are associated with ‘‘bending modes’’ with most <strong>of</strong> the strain energy in the rotating assembly. The bending modes are not significantly affected by bearing supports stiffness until the stiffness becomes very large. Note that the node points for the ‘‘bending modes’’ coincide with the disks and their associated relatively large inertias. If the design goal for this configuration is to operate below the first critical speed, the bearings must to be very stiff and the maximum spin-speed must be limited to about 20,000 rpm. Most designs probably do not have a sufficiently large design envelope, i.e., weight and performance freedom, to allow for the placement <strong>of</strong> the first critical speed above the operating range. A combination <strong>of</strong> the three design approaches, listed above, is <strong>of</strong>ten required to develop a practical design with acceptable rotordynamic response characteristics. A machine will typically need to operate above at least one <strong>of</strong> the ‘‘rigid-body’’ critical speeds. Ideally the ‘‘rigid-body’’ critical speed(s) will occur below idle, and the critical speed response will be a brief transient condition as the machine is accelerated to either its idle or operating speed. If the bearings are ‘‘hard-mounted’’ and the rotor operates above the ‘‘rigid-body’’ critical speed(s), large response should be expected as the rotor accelerates through the critical speeds. Assuming that structural damping produces 5% critical damping, the dynamic magnification would be approximately 10 (i.e., 1/2z e). This situation may be acceptable if the rotor has sufficient clearance relative to the structure and the bearings have adequate load capacity for the large response as the rotor accelerates through the critical speed(s). However, a preferred design option is to add damping via a squeeze film damper at one or both <strong>of</strong> the bearings to reduce the response at the critical speed(s). The unbalance response for the ‘‘hard-mounted’’ and ‘‘squeeze filmmounted’’ configurations may be estimated by assuming a mass eccentricity for the two disks [i.e., 1.0 mils ð25:4 mmÞ] and performing an unbalance response analysis. For the ‘‘hard-mounted’’ configuration, an equivalent viscous damping coefficient ðc ¼ 2z ek=oÞ may be calculated based on the Copyright © 2003 Marcel Dekker, Inc.
Figure 38 Straddle mounted rotor. (a) Critical speed map, (b) mode shapes. Copyright © 2003 Marcel Dekker, Inc.
- Page 1 and 2:
D E K K E R Handbook of Turbomachin
- Page 3 and 4:
MECHANICAL ENGINEERING A Series of
- Page 5 and 6:
61 Computer-Aided Simulation in Rai
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127 Designing for Product Sound Qua
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Preface to the Second Edition The o
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Preface to the Second Edition Prefa
- Page 13 and 14:
Contributors Nathan G. Adams The Bo
- Page 15 and 16:
1 Introduction Earl Logan, Jr.*, an
- Page 17 and 18:
HISTORICAL BACKGROUND Earl Logan, J
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MECHANICAL AND THERMAL DESIGN CONSI
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Figure 1 Cross-section showing the
- Page 23 and 24:
Figure 2 Turboprop engine, TPE 331-
- Page 25 and 26:
Figure 4 Auxiliary power unit, APU1
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Durability. The mechanical and ther
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with time during flight. Such a typ
- Page 31 and 32:
experience and existing similar des
- Page 33 and 34:
adverse pressure gradient against w
- Page 35 and 36:
and its attachments. A substantial
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Figure 9 Typical high-pressure turb
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and the measurement of local heat-t
- Page 41 and 42:
due to cyclic operation. In additio
- Page 43 and 44:
the steady and transient conditions
- Page 45 and 46:
Table 3(a) Steps in a Three-Dimensi
- Page 47 and 48:
Figure 16 Schematic Goodman diagram
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occur due to particles of unburned
- Page 51 and 52:
pressures at critical points. These
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1. Ceramics are subject to ‘‘in
- Page 55 and 56:
with Transient Tests and Surface Co
- Page 57 and 58:
Overall engine performance goals tr
- Page 59 and 60:
Much of the complexity of turbomach
- Page 61 and 62:
End-wall boundary layers can also h
- Page 63 and 64:
pressure at the wake centerline. Th
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the same vaneless diffuser and shro
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from internal cooling passages, thr
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Further downstream, the wake was ev
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to its original position. This unst
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cooling film was found to trip the
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shroud static pressure and the exit
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stage in the design process allows
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Flow Physics Modeling Modeling of t
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passage to the next, assuming that
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The next step in modeling accuracy
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tend to be large, due to the necess
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Navier-Stokes equations are time-ma
- Page 89 and 90:
To satisfy these requirements, it i
- Page 91 and 92:
are discussed by a number of author
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source code, and to assign each seg
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selected locations in the flow path
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of the component designers must be
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Trends in Flow Modeling Capabilitie
- Page 101 and 102:
optimize the flow behavior. The eff
- Page 103 and 104:
20. D. Eckardt, ‘‘Flow Field An
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49. K. R. Kirtley, ‘‘An Algebra
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INTRODUCTION 3 Turbine Gas-Path Hea
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Figure 1 Maximum turbine rotor inle
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Figure 2 Intersecting S1 and S2 sur
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determination. Nothing in the simpl
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e well matched with the engine. The
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case different forms of the popular
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volume will be equal to the accumul
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Figure 9 Nusselt number vs. vane su
- Page 123 and 124:
Furthermore, to keep computer time
- Page 125 and 126:
Figure 12 Comparison of three turbu
- Page 127 and 128:
and small and cooled and uncooled t
- Page 129 and 130:
Figure 15 Miniature heat flux gauge
- Page 131 and 132:
Figure 17 Time resolved heat transf
- Page 133 and 134:
Figure 19 Surface pressure changes
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NONUNIFORM INLET FLOW All gas turbi
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Figure 22 Typical distributions of
- Page 139 and 140:
4. Better instrumentation for heat-
- Page 141 and 142:
24. R. H. Ni, ‘‘A Multiple Grid
- Page 143 and 144:
4 Selection of a Gas Turbine Coolin
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Re L ¼ rVL=m—Reynolds number bas
- Page 147 and 148:
(1,300 8F). But modern gas turbines
- Page 149 and 150:
during engine operation are compati
- Page 151 and 152:
Figure 3 Airfoil cooling techniques
- Page 153 and 154:
expected to increase this limit to
- Page 155 and 156:
1. Reduce the effect of main-stream
- Page 157 and 158:
P? is total inlet pressure. Tc=T? i
- Page 159 and 160:
thereby increasing both the skin-fr
- Page 161 and 162:
After four decades of advancement i
- Page 163 and 164:
correspondingly high coolant-side t
- Page 165 and 166:
component. Use of a hot cascade for
- Page 167 and 168:
nozzle vanes is limited by their ox
- Page 169 and 170:
Figure 9 Typical turbine hot sectio
- Page 171 and 172:
important factor to consider for tr
- Page 173 and 174:
Figure 10 Evolution of nozzle geome
- Page 175 and 176:
the exit of the combustor section f
- Page 177 and 178:
Figure 12 Inlet turbulence effect o
- Page 179 and 180:
in heat transfer as the Reynolds nu
- Page 181 and 182:
easonably well using correlations e
- Page 183 and 184:
in the section on blade cooling tha
- Page 185 and 186:
mass flow rate (e.g., M ¼ 1 for a
- Page 187 and 188:
holes. Cooling hole pattern is an i
- Page 189 and 190:
coolant flow with the main stream,
- Page 191 and 192:
above equation assumes a constant f
- Page 193 and 194:
Figure 15 Definition of film-coolin
- Page 195 and 196:
edistribution of the external heat-
- Page 197 and 198:
Three-Dimensional Effects The three
- Page 199 and 200:
In order to achieve the bulk metal
- Page 201 and 202:
coefficient is given by Nud ¼ hd=k
- Page 203 and 204:
Where G ¼ 2:24ðw=tÞ 0:1 ðReeÞ
- Page 205 and 206:
pressure drop. The 608/458 V-shaped
- Page 207 and 208:
Some of the studies have found that
- Page 209 and 210:
of the cooling air and the turning
- Page 211 and 212:
Figure 20 Impingement geometry defi
- Page 213 and 214:
correlated by Nu a d ¼ 0:63ðGd=m
- Page 215 and 216:
tangentially to the inner wall, beh
- Page 217 and 218:
The effectiveness of a suction surf
- Page 219 and 220:
vortex structure. Their studies sho
- Page 221 and 222:
Figure 23 Effect of preswirler pres
- Page 223 and 224:
component to the cooling air that c
- Page 225 and 226:
axial gap. A static pressure variat
- Page 227 and 228:
Weight, cost, and complexity constr
- Page 229 and 230:
Figure 28 Effectiveness of liner co
- Page 231 and 232:
thickness. A problem this poses is
- Page 233 and 234:
portion of the hole has been shown
- Page 235 and 236:
unacceptable engine performance pen
- Page 237 and 238:
analysis, in order to provide accur
- Page 239 and 240:
Figure 30 Application of PSP for fi
- Page 241 and 242:
thermocouple positioned close to th
- Page 243 and 244:
spray-painted black (Hallcrest, BB-
- Page 245 and 246:
Figure 32 Schematics of a hot casca
- Page 247 and 248:
the turbine static temperature (rot
- Page 249 and 250:
Figure 33 Experimental rig for inve
- Page 251 and 252:
their color when exposed to higher
- Page 253 and 254:
margins defined within each discipl
- Page 255 and 256:
them. The larger gas-path divergenc
- Page 257 and 258:
Figure 36 Blade-cooling selection d
- Page 259 and 260:
8. B. Barry, Turbine Blade Cooling:
- Page 261 and 262:
40. A. K. Tolpadi and M. E. Crawfor
- Page 263 and 264:
73. R. S. Abhari, ‘‘Comparison
- Page 265 and 266:
106. J. M. Owen and R. H. Rogers, F
- Page 267 and 268:
138. I. Egorov, G. Kretinin, I. Les
- Page 269 and 270:
integrity (stress levels) will have
- Page 271 and 272:
Figure 1 Instant entropy contours o
- Page 273 and 274:
Aerodynamic Interaction (Unsteady L
- Page 275 and 276:
Figure 3 Pitchwise time-averaged en
- Page 277 and 278:
The above considerations are all fo
- Page 279 and 280:
lades, the wavelength of the distur
- Page 281 and 282:
forcing and damping, and hence the
- Page 283 and 284:
frequency and its higher harmonics
- Page 285 and 286:
The two-cell pattern with a relativ
- Page 287 and 288:
Figure 9 Typical blade flutter boun
- Page 289 and 290:
field is generated to satisfy the t
- Page 291 and 292:
Figure 11 Instant static pressure c
- Page 293 and 294:
Figure 12 Calculated instantaneous
- Page 295 and 296:
Figure 14 Time-space static pressur
- Page 297 and 298:
one period Tp (neglecting change of
- Page 299 and 300:
It should be noted that the effects
- Page 301 and 302:
There are some further points to no
- Page 303 and 304:
Figure 17 Flow around an NACA-65 ai
- Page 305 and 306:
(11) for a simple case]: Where WA
- Page 307 and 308:
Regardless whether loosely coupled
- Page 309 and 310:
Several methods have been developed
- Page 311 and 312:
significant difference is introduce
- Page 313 and 314:
losses, but it may affect to a mini
- Page 315 and 316:
when we refine a mesh in an unstead
- Page 317 and 318:
8. W. S. Barankiewicz and M. D. Hat
- Page 319 and 320:
6 Fundamentals of Compressor Design
- Page 321 and 322:
Figure 3 AlliedSignal 331 turboprop
- Page 323 and 324:
each of the selected radii. The pro
- Page 325 and 326:
components of gas velocity upstream
- Page 327 and 328:
Observe that each of the curves for
- Page 329 and 330:
The conservation of angular momentu
- Page 331 and 332:
allowable static pressure ratio of
- Page 333 and 334:
Figure 7 Boundary layers and wakes
- Page 335 and 336:
component that is perpendicular to
- Page 337 and 338:
Figure 10 (a) Deflection of flow of
- Page 339 and 340:
increase in the downstream pressure
- Page 341 and 342:
Mach number at a compressor outlet
- Page 343 and 344:
Figure 12 Sketch of flow surface an
- Page 345 and 346:
useful shapes and orientations of b
- Page 347 and 348:
where G and oa are constant along a
- Page 349 and 350:
There is a good reason for this sit
- Page 351 and 352:
Projected Shape in Meridional Plane
- Page 353 and 354:
inherent flow range of the impeller
- Page 355 and 356:
compressors. Multistage centrifugal
- Page 357 and 358:
turbines. In these designs the high
- Page 359 and 360:
Corrections for Streamline Curvatur
- Page 361 and 362:
Preparation of Maps Once the losses
- Page 363 and 364:
that circumferential gradients meas
- Page 365 and 366:
Nastran, which was developed by NAS
- Page 367 and 368:
tests. One should take pains to pro
- Page 369 and 370:
e predicted in advance. Total press
- Page 371 and 372:
Cv Coefficient of heat at constant
- Page 373 and 374:
15. S. Lieblein, J. Basic Eng., Tra
- Page 375 and 376:
INTRODUCTION 7 Fundamentals of Turb
- Page 377 and 378:
Figure 1 Cross sections of generic
- Page 379 and 380:
espectively. Radial-inflow turbines
- Page 381 and 382:
Figure 4 Typical rotor blade shapes
- Page 383 and 384:
Figure 6 The expansion process acro
- Page 385 and 386:
the average for the gas flowing thr
- Page 387 and 388:
etween the velocity diagram and the
- Page 389 and 390:
gas dynamics relation p 00 p ¼ T 0
- Page 391 and 392:
Figure 9 Variations in turbine velo
- Page 393 and 394:
pressure, inlet losses are usually
- Page 395 and 396:
diffuser recovery, defined as Rp ¼
- Page 397 and 398:
different turbines easier, dimensio
- Page 399 and 400:
where and y ¼ T 0 in TSTD d ¼ p0
- Page 401 and 402:
sizing exercises where the details
- Page 403 and 404:
where Rth is the Reynolds number ba
- Page 405 and 406:
order to determine the overall turb
- Page 407 and 408:
The classical approach to satisfyin
- Page 409 and 410:
clearance. Since tip clearance repr
- Page 411 and 412:
turbine with an effective diffuser,
- Page 413 and 414:
atio ðp 0 in =pdisÞ is 3. The sta
- Page 415 and 416:
Automation of Calculations and Trad
- Page 417 and 418:
and for the rotor Zrotor ¼ ð0:1Þ
- Page 419 and 420:
the energy extracted and the rotor
- Page 421 and 422:
RADIAL-INFLOW TURBINE SIZING Differ
- Page 423 and 424:
interpolations from existing design
- Page 425 and 426:
Glassman [1], the optimum ratio of
- Page 427 and 428:
design fault in the radial-inflow t
- Page 429 and 430:
[27]. In order to avoid manufacturi
- Page 431 and 432:
The rotor exit critical velocity is
- Page 433 and 434:
The hub-to-tip radius ratio at the
- Page 435 and 436:
REFERENCES 1. A. J. Glassman (ed.),
- Page 437 and 438:
8 Steam Turbines Thomas H. McCloske
- Page 439 and 440:
Figure 3 Reciprocating steam engine
- Page 441 and 442:
This process began in the 1920s, al
- Page 443 and 444:
First Law of Thermodynamics The fir
- Page 445 and 446:
the amount of fuel burned and the p
- Page 447 and 448:
Figure 7 Rankine cycle temperature-
- Page 449 and 450:
The Mollier diagram is quite useful
- Page 451 and 452:
Figure 10 Theoretical Rankine cycle
- Page 453 and 454:
stages of the turbine is at a highe
- Page 455 and 456:
calculate the relevant thermodynami
- Page 457 and 458:
Figure 14 Steam leakage losses for
- Page 459 and 460:
can reveal nozzle and/or blade eros
- Page 461 and 462:
Figure 17 Enlarged portion of the M
- Page 463 and 464:
Traditionally, pressures have been
- Page 465 and 466:
Figure 21 Wetness thermodynamic los
- Page 467 and 468:
Figure 23 Radial steam turbine flow
- Page 469 and 470:
Figure 25 Percentage stage reaction
- Page 471 and 472:
The power output of the stage can b
- Page 473 and 474:
the LP turbines is split into paral
- Page 475 and 476:
Turbine Inlet Two stages in particu
- Page 477 and 478:
of 20%, which would cause excessive
- Page 479 and 480:
Figure 30 Typical low-pressure stea
- Page 481 and 482:
ductility and poor toughness, since
- Page 483 and 484:
‘‘tramp’’ elements to minim
- Page 485 and 486:
End Seals End seals or packing glan
- Page 487 and 488:
Drains Condensate can form during s
- Page 489 and 490:
Figure 32 Steam turbine blade roots
- Page 491 and 492:
Figure 34 Cross-section view of thr
- Page 493 and 494:
Figure 36 Interblade shroud and Tie
- Page 495 and 496:
Where The influence of notch sensit
- Page 497 and 498:
Similarly, LP turbine blades are su
- Page 499 and 500:
those made of steel. Note, however,
- Page 501 and 502:
esult, significant attention must b
- Page 503 and 504:
Figure 38 Centrifugal stresses on a
- Page 505 and 506:
Figure 39 Centrifugal bending stres
- Page 507 and 508:
onto the rotating blade. These can
- Page 509 and 510:
Vortex shedding from blade trailing
- Page 511 and 512:
Figure 42 Torsional coupled vibrati
- Page 513 and 514:
Figure 44 Stall flutter of low-pres
- Page 515 and 516:
Start-Stop Transients/Overspeeds La
- Page 517 and 518:
(4) ellipiticity, such as caused by
- Page 519 and 520:
Figure 47 Campbell diagram (frequen
- Page 521 and 522:
Furthermore, in practice each manuf
- Page 523 and 524:
Figure 49 Modal diameters of a low-
- Page 525 and 526:
Figure 51 Three-dimensional computa
- Page 527 and 528:
Figure 52 Converging wedge and resu
- Page 529 and 530:
value as the operating value of uv/
- Page 531 and 532:
Lubrication Supply System Design De
- Page 533 and 534:
Figure 56 Steam turbine oil system
- Page 535 and 536:
The main oil reservoir is located b
- Page 537 and 538:
Although a light oil does provide a
- Page 539 and 540:
temperatures are suspected as reaso
- Page 541 and 542:
There is no fixed or absolute value
- Page 543 and 544:
pivots incorporated in this bearing
- Page 545 and 546:
covers and doors. Pipe scale, rust,
- Page 547 and 548:
Figure 63 Mechanical hydraulic cont
- Page 549 and 550:
Figure 64 Steam turbine electro-hyd
- Page 551 and 552:
Figure 65 Steam turbine electro-hyd
- Page 553 and 554:
generator rotor moment of inertia h
- Page 555 and 556:
the turbine against overspeed. This
- Page 557 and 558:
an additional electronic overspeed
- Page 559 and 560:
Figure 68 Steam turbine protective
- Page 561 and 562:
3. Need for better understanding of
- Page 563 and 564:
REFERENCES 1. J. C. Zink, ‘‘Ste
- Page 565 and 566:
No. TWDPS-1, The American Society o
- Page 567 and 568:
58. A. V. Sarlashkar and T. C. T. L
- Page 569 and 570:
81. IEEE Guide for Abnormal Frequen
- Page 571 and 572:
Atlanta, GA, Oct. 18-22, 1992, PWR-
- Page 573 and 574:
Performance Enhancement Program, he
- Page 575 and 576:
of the design process toward achiev
- Page 577 and 578:
procedure capable of addressing mul
- Page 579 and 580:
to achieve a specific target pressu
- Page 581 and 582:
objective was to minimize the downs
- Page 583 and 584:
more closely represents the largest
- Page 585 and 586:
temperature by forming a thin film
- Page 587 and 588:
such as the one described here. For
- Page 589 and 590:
k is the thermal conductivity of th
- Page 591 and 592:
through finite differences. Mathema
- Page 593 and 594:
Figure 4 Comparison of blade cross-
- Page 595 and 596:
integration of multiple disciplines
- Page 597 and 598:
17. S. S. Talya, ‘‘Multidiscipl
- Page 599 and 600:
INTRODUCTION 10 Rotordynamic Consid
- Page 601 and 602: Figure 1 (c) AlliedSignal 331 turbo
- Page 603 and 604: Figure 2 Rotor system displacements
- Page 605 and 606: Figure 3 Elliptic lateral whirl. av
- Page 607 and 608: vibration (either forward or backwa
- Page 609 and 610: Figure 6 The Laval-Jeffcott rotor.
- Page 611 and 612: are 1808 out of phase (i.e., the be
- Page 613 and 614: this graph is quite simple; however
- Page 615 and 616: included on these types of graphs b
- Page 617 and 618: on the shaft is zero. Thus, the ste
- Page 619 and 620: are uðtÞ ¼e zeott uo cos ott þ
- Page 621 and 622: satisfies the inequality O < ot 1
- Page 623 and 624: Figure 16 Laval-Jeffcott rotor tran
- Page 625 and 626: Figure 18 Whirl speed map: Laval-Je
- Page 627 and 628: Figure 20 Laval-Jeffcott rotor: ste
- Page 629 and 630: Figure 22 Typical precessional mode
- Page 631 and 632: Figure 24 Examples of flexible disk
- Page 633 and 634: ackward modes, however, involve con
- Page 635 and 636: Figure 29 Steady unbalance response
- Page 637 and 638: assist in attenuating high vibratio
- Page 639 and 640: properly sizing the damper, a highl
- Page 641 and 642: Figure 31 Gas turbine schematic and
- Page 643 and 644: Flexible Disk If the frequency of a
- Page 645 and 646: motion for each subsegment to form
- Page 647 and 648: Figure 35 Whirl speed map—straddl
- Page 649 and 650: Figure 37 Rotor-bearing-support str
- Page 651: DESIGN STRATEGIES AND PROCEDURES Ro
- Page 655 and 656: Figure 39 Unbalance response: strad
- Page 657 and 658: Figure 40 Double overhung rotor—d
- Page 659 and 660: earing supports are reduced. The th
- Page 661 and 662: and also increases the critical spe
- Page 663 and 664: Examples of structure modes couplin
- Page 665 and 666: REFERENCES 1. D. Childs, Turbomachi
- Page 667 and 668: section is intended to place today
- Page 669 and 670: pressure-fed propellant systems. Hi
- Page 671 and 672: normally be considered a very small
- Page 673 and 674: increase of required suction perfor
- Page 675 and 676: displaced by the F-1 oxidizer pump
- Page 677 and 678: exposure may be subjected to imping
- Page 679 and 680: the exhaust duct. Sized to create s
- Page 681 and 682: excess of 6,000 psi for consumption
- Page 683 and 684: lifetime. With very few exceptions,
- Page 685 and 686: using hydrocarbon fuel combustion p
- Page 687 and 688: can yield noticeable savings in req
- Page 689 and 690: Figure 3 Rocket engine system schem
- Page 691 and 692: Figure 6 Staged combustion system,
- Page 693 and 694: each stage. The term C0 represents
- Page 695 and 696: Figure 10 Some representative turbo
- Page 697 and 698: emembered that the second (and any
- Page 699 and 700: the greatest demands on turbopump p
- Page 701 and 702: momentum exchange between working f
- Page 703 and 704:
Figure 13 Arrangement of various tu
- Page 705 and 706:
pressure levels. As long as combust
- Page 707 and 708:
Figure 14 Approxmate values of pump
- Page 709 and 710:
liquid rocket engine systems, and e
- Page 711 and 712:
above becomes a factor. This statem
- Page 713 and 714:
We can then state (correctly) that,
- Page 715 and 716:
Figure 15c Typical 2-D centrifugal
- Page 717 and 718:
have seen that the flow rate throug
- Page 719 and 720:
somewhat smaller magnitude of vecto
- Page 721 and 722:
general indicator. Nss will give us
- Page 723 and 724:
U ¼ rotor tangential velocity. By
- Page 725 and 726:
and pump flow derived from the engi
- Page 727 and 728:
In addition to shaft seals, shaft b
- Page 729 and 730:
should be understood that the optim
- Page 731 and 732:
stable operation is assured. In som
- Page 733 and 734:
From Eq. (16) an impeller radial ou
- Page 735 and 736:
Figure 18 Examples of centrifugal p
- Page 737 and 738:
tional to clearance distance) with
- Page 739 and 740:
I would like to conclude this secti
- Page 741 and 742:
generally result in lower pump hydr
- Page 743 and 744:
Figure 15h Cross-section of a typic
- Page 745 and 746:
solutions of Eq. (7) for both stage
- Page 747 and 748:
Figure 15k H-Q characteristics for
- Page 749 and 750:
Figure 15l Typical inducer configur
- Page 751 and 752:
camber) is proportionally lower. Th
- Page 753 and 754:
Figure 22 Single-stage impulse turb
- Page 755 and 756:
the velocity ratio K, but in somewh
- Page 757 and 758:
~V and ~n ¼ fluid velocity and con
- Page 759 and 760:
Fig. 25. The nature of the flow in
- Page 761 and 762:
Although shrouded centrifugal impel
- Page 763 and 764:
is a parasitic device, whose flow r
- Page 765 and 766:
apidly than does the inducer thrust
- Page 767 and 768:
Figure 30 LH2 turbopump rotor mecha
- Page 769 and 770:
eplacement of a failed bearing with
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shall see, contemporary rocket engi
- Page 773 and 774:
needs of the aircraft gas turbine a
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was increased due to engine upratin
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12 Turbomachinery Performance Testi
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istics. The more accurate the perfo
- Page 781 and 782:
Inlet Distortion Most turbomachiner
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Gas Thermodynamic Properties Turbom
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ought to rest isentropically. Total
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include not only the pressure chang
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The circumferential placement of th
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simply arithmetically averaging the
- Page 793 and 794:
usually mounted in radial immersion
- Page 795 and 796:
Figure 12(b) Radial flow angle prof
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Figure 15 Wake rake total pressure
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Figure 16 Blade-tip pressure traces
- Page 801 and 802:
Figure 18 Typical test rig schemati
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INSTRUMENTATION DESIGN CONSIDERATIO
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Dynamic Pressure. Dynamic pressure
- Page 807 and 808:
thermocouples. With care in constru
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Figure 24 Typical two-dimensional f
- Page 811 and 812:
Thermocouple lead wires should be i
- Page 813 and 814:
Corrected Flow The flow rates used
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pressure ratio [15]. It can be calc
- Page 817 and 818:
SYMBOLS A Cross-section area Cd Dis
- Page 819 and 820:
INTRODUCTION 13 Automotive Supercha
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Figure 2 A Roots-type supercharger
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The supercharger was in routine use
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Table 1 Superchargers Versus Turboc
- Page 827 and 828:
1960s, turbocharging was used by US
- Page 829 and 830:
Roots Blower The Roots-type blower
- Page 831 and 832:
speeds. The sound is caused by the
- Page 833 and 834:
Figure 8b How the Ro-charger operat
- Page 835 and 836:
The vanes in many designs are preve
- Page 837 and 838:
Figure 11a Key components of the G-
- Page 839 and 840:
Figure 11c G-Lader supercharger is
- Page 841 and 842:
Figure 12b Schematic of centrifugal
- Page 843 and 844:
Figure 14b Components of the typica
- Page 845 and 846:
Turbine Design The turbine housing
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inertia of the wheel assembly. Mini
- Page 849 and 850:
Figure 18 (a) Turbocharger compress
- Page 851 and 852:
Theoretically this efficiency is: o
- Page 853 and 854:
The overall turbine efficiency incl
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adjust the spring force to vary the
- Page 857 and 858:
Figure 22b Two vanes are used to pr
- Page 859 and 860:
However, the temperature has to be
- Page 861 and 862:
air can reduce carbon monoxide and
- Page 863 and 864:
Figure 25 (a) Schematic of the COMP
- Page 865 and 866:
this plus the fact that the exhaust
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14 Tesla Turbomachinery Warren Rice
- Page 869 and 870:
press at the time of the invention
- Page 871 and 872:
can be made to simplify the equatio
- Page 873 and 874:
comparison of the results of variou
- Page 875 and 876:
y composing them of nested cones ra
- Page 877 and 878:
26. E. Bakke, ‘‘Theoretical and
- Page 879 and 880:
61. M. Piesche, ‘‘Investigation
- Page 881 and 882:
15 Hydraulic Turbines V. Dakshina M
- Page 883 and 884:
Table 1 Variables of Interest in Tu
- Page 885 and 886:
Figure 1 Variation of impeller shap
- Page 887 and 888:
Figure 2 Flow and velocity componen
- Page 889 and 890:
Figure 3 Schematic diagram of Pelto
- Page 891 and 892:
shown in Fig. 5(see KadambiandPrasa
- Page 893 and 894:
classified according to the directi
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The manufacturers of hydraulic turb
- Page 897 and 898:
The direction of the relative veloc
- Page 899 and 900:
Table 3 Variation of Some Quantitie
- Page 901 and 902:
denoted by hd. Thus the efficiency
- Page 903 and 904:
Figure 14 Draft tube setting. same
- Page 905:
REFERENCES 1. J. J. Fritz, Small an
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