chapter 1 evolution of a successful design

More documents

Recommendations

Info

CLUTCHES AND BRAKES 8.12 MACHINE ELEMENTS THAT ABSORB AND STORE ENERGY FIGURE 8.8 Drum brake. (Chrysler Corporation.) in the friction coefficient cause large changes in brake torque, the brake is unstable. It will tend to grab and squeal if the coefficient of friction increases. But if the coefficient decreases (say, because of a temperature increase), there will be a noticeable drop in capacity. Full disk brakes are used principally for industrial machinery.They are very much like full disk clutches in construction. Indeed, they are found in clutch-brake combination drives where both members of the drive are full disk in construction. Caliper disk brakes (Fig. 8.9) are now familiar components of vehicles, but they find applications in industrial equipment as well. The Chrysler brake shown uses a floating caliper. In this design, an automatic mechanism to adjust for pad wear can be incorporated easily. Generally caliper disk brakes are not self-energizing, although they can be. An advantage of the non-self-energizing disk brake is its great stability; it is relatively insensitive to changes in the coefficient of friction. Brake Actuation. Four principal actuation methods are shown in the classification chart of Fig. 8.7: mechanical, pneumatic (or hydraulic), electric, and automatic. Sometimes the methods are combined. The drum brake of Fig. 8.8 and the disk brake of Fig. 8.9 are both hydraulically operated. Both are intended for vehicles. In industrial applications, air is often the actuating fluid. The air-tube configuration in Fig. 8.10 can be used for a pneumatically operated clutch or brake. Electrically operated brakes most commonly use electromagnetic forces to actuate a full-disk-friction brake. However, a number of other designs are found (see Sec. 8.8). Automatically operated brakes are used for both transportation and industrial equipment. Sometimes manual operation is overridden by automatic actuation. Truck brakes are available with spring actuators that engage if the air pressure is lost. The air brake, as originally conceived by George Westinghouse for railroad applications, was of this fail-safe design. Electrically, hydraulically, and pneumatically operated brakes can all be designed for automatic operation. Antiskid brakes for automobiles and trucks superimpose on the usual manual control an automatic control that releases braking pressure if lockup and skidding are imminent. Downloaded from Digital Engineering Library @ McGraw-Hill (www.digitalengineeringlibrary.com) Copyright © 2004 The McGraw-Hill Companies. All rights reserved. Any use is subject to the Terms of Use as given at the website.
8.1.4 Selecting a Brake CLUTCHES AND BRAKES FIGURE 8.9 Automotive disk brake. (Chrysler Corporation.) CLUTCHES AND BRAKES 8.13 To help narrow the choice of a brake, Table 8.2 has been provided. Some general indicators are given for performance requirements and environmental conditions. Typical applications are listed as well. The brake factor is the ratio of the frictional braking force developed to the actuating force. Note that temperature considerations have been omitted from the environmental conditions in Table 8.2. For high temperatures, the capacity of all brakes listed is limited by the type of friction material. The performance of all brakes listed is con- Downloaded from Digital Engineering Library @ McGraw-Hill (www.digitalengineeringlibrary.com) Copyright © 2004 The McGraw-Hill Companies. All rights reserved. Any use is subject to the Terms of Use as given at the website.
Page 1 and 2:
Source: STANDARD HANDBOOK OF MACHIN
Page 3 and 4:
EVOLUTION OF A SUCCESSFUL DESIGN EV
Page 5 and 6:
Flywheels are an important machine
Page 7 and 8:
EVOLUTION OF A SUCCESSFUL DESIGN sp
Page 9 and 10:
Page 11 and 12:
GLOSSARY OF SYMBOLS CHAPTER 2 A THE
Page 13 and 14:
(a) A THESAURUS OF MECHANISMS 2.5 (
Page 15 and 16:
(c) A THESAURUS OF MECHANISMS A THE
Page 17 and 18:
(g) (l) (c) (e) A THESAURUS OF MECH
Page 19 and 20:
(a) (g) (c) A THESAURUS OF MECHANIS
Page 21 and 22:
(a) (c) (e) A THESAURUS OF MECHANIS
Page 23 and 24:
(e) (a) (i) A THESAURUS OF MECHANIS
Page 25 and 26:
(b) A THESAURUS OF MECHANISMS (d) A
Page 27 and 28:
(a) (f) A THESAURUS OF MECHANISMS A
Page 29 and 30:
(a) A THESAURUS OF MECHANISMS A THE
Page 31 and 32:
(c) (a) A THESAURUS OF MECHANISMS A
Page 33 and 34:
(c) (f) (i) A THESAURUS OF MECHANIS
Page 35 and 36:
A THESAURUS OF MECHANISMS (a) A THE
Page 37 and 38:
(a) (d) (j) (g) A THESAURUS OF MECH
Page 39 and 40:
CHAPTER 3 LINKAGES Richard E. Gusta
Page 41 and 42:
(a) (c) where l = number of links (
Page 43 and 44:
(a) (c) LINKAGES LINKAGES 3.5 FIGUR
Page 45 and 46:
Since both sides of (3.5) can be di
Page 47 and 48:
The driven link d will be at angle
Page 49 and 50:
LINKAGES FIGURE 3.8 Two positions o
Page 51 and 52:
LINKAGES LINKAGES 3.13 FIGURE 3.10
Page 53 and 54:
LINKAGES FIGURE 3.12 Determining th
Page 55 and 56:
of motion. Proper care in selection
Page 57 and 58:
4. With O B as vertex, set off a li
Page 59 and 60:
3. Determine lines S ab(ab) and S a
Page 61 and 62:
LINKAGES LINKAGES 3.23 3.13 John J.
Page 63 and 64:
CHAPTER 4 CAM MECHANISMS Andrzej A.
Page 65 and 66:
FIGURE 4.3 Plate cams with oscillat
Page 67 and 68:
FIGURE 4.6 Types of follower motion
Page 69 and 70:
CAM MECHANISMS CAM MECHANISMS 4.7 F
Page 71 and 72:
CAM MECHANISMS CAM MECHANISMS 4.9 F
Page 73 and 74:
the motion specification for the ri
Page 75 and 76:
CAM MECHANISMS CAM MECHANISMS 4.13
Page 77 and 78:
CAM MECHANISMS 4.15 This is called
Page 79 and 80:
Page 81 and 82:
It is a common rule of thumb to ass
Page 83 and 84:
Page 85 and 86:
Page 87 and 88:
For F23 = 0, roller and cam lose th
Page 89 and 90:
FIGURE 4.20 Programming of cam syst
Page 91 and 92:
Page 93 and 94:
n5 = N2N4 n2 (5.5) N3N5 and the t
Page 95 and 96:
5.3 PLANETARY GEAR TRAINS GEAR TRAI
Page 97 and 98:
GEAR TRAINS 5.7 termini of the velo
Page 99 and 100:
GEAR TRAINS TABLE 5.1 Solution by T
Page 101 and 102:
GEAR TRAINS 5.11 TABLE 5.2 Characte
Page 103 and 104:
FIGURE 5.9 (a) Planetary train; (b)
Page 105 and 106:
GEAR TRAINS GEAR TRAINS 5.15 (a) (b
Page 107 and 108:
Page 109 and 110:
Page 111 and 112:
SPRINGS SPRINGS 6.5 close-wound: wo
Page 113 and 114:
6.3.2 Heat Treatment of Springs Hea
Page 115 and 116:
SPRINGS 6.9 Downloaded from Digital
Page 117 and 118:
SPRINGS 6.11 Downloaded from Digita
Page 119 and 120:
Helical compression springs are str
Page 121 and 122:
Types of Ends. Four basic types of
Page 123 and 124:
TABLE 6.5 Typical Properties of Spr
Page 125 and 126:
SPRINGS SPRINGS 6.19 The rate equat
Page 127 and 128:
SPRINGS SPRINGS 6.21 FIGURE 6.9 End
Page 129 and 130:
The fatigue life estimates in Table
Page 131 and 132:
The spring rate for a rectangular-w
Page 133 and 134:
SPRINGS 6.27 FIGURE 6.15 Stress cor
Page 135 and 136:
6.5 HELICAL EXTENSION SPRINGS 6.5.1
Page 137 and 138:
6.5.2 Initial Tension Initial tensi
Page 139 and 140:
SPRINGS FIGURE 6.20 Common end conf
Page 141 and 142:
Dynamic considerations discussed pr
Page 143 and 144:
SPRINGS SPRINGS 6.37 TABLE 6.14 Tol
Page 145 and 146:
The number of coils is equal to the
Page 147 and 148:
SPRINGS SPRINGS 6.41 TABLE 6.17 Com
Page 149 and 150:
6.7.1 Nomenclature a OD/2, mm (in)
Page 151 and 152:
Ef Sc = C1 h − 2 2 (1 −µ )Ma
Page 153 and 154:
SPRINGS SPRINGS 6.47 FIGURE 6.31 Lo
Page 155 and 156:
Because of production variations in
Page 157 and 158:
7. h = 1.41t = 1.41(0.054) = 0.076
Page 159 and 160:
and Design equations are SPRINGS SP
Page 161 and 162:
6.9 FLAT SPRINGS 6.9.1 Introduction
Page 163 and 164: SPRINGS fEb P = ot (6.52) where K =
Page 165 and 166: SPRINGS SPRINGS 6.59 TABLE 6.25 Max
Page 167 and 168: If unknown, let b/t = 100/1, D2 = 1
Page 169 and 170: 6.11.2 Design Equations: Rectangula
Page 171 and 172: SPRINGS SPRINGS 6.65 FIGURE 6.50 Ty
Page 173 and 174: SPRINGS SPRINGS 6.67 FIGURE 6.51 Av
Page 175 and 176: used only for centerless ground all
Page 177 and 178: CHAPTER 7 FLYWHEELS Daniel M. Curti
Page 179 and 180: The energy-storage capacity of a fl
Page 181 and 182: FLYWHEELS Since the torque-angle cu
Page 183 and 184: 7.2.3 Coefficient of Energy Variati
Page 185 and 186: 7.2.5 Speed-Dependent Torques FLYWH
Page 187 and 188: FLYWHEELS FLYWHEELS 7.11 range [7.7
Page 189 and 190: and 205 rpm = 2π(205)/60 = 21.468
Page 191 and 192: Example 6. An alloy of density 26.6
Page 193 and 194: cos (π/8) f4 = =0.340 (7.42) 7.11
Page 195 and 196: For a constant-thickness disk witho
Page 197 and 198: factor F s = 1.0 for the fully stre
Page 199 and 200: FLYWHEELS FLYWHEELS 7.23 (g) (h) (i
Page 201 and 202: many composite flywheels shred, for
Page 203 and 204: Source: STANDARD HANDBOOK OF MACHIN
Page 205 and 206: CLUTCHES AND BRAKES CLUTCHES AND BR
Page 209 and 210: shaft begins to rotate.At the desig
Page 213: FIGURE 8.7 Classification of brakes
Page 217 and 218: TABLE 8.2 Selecting the Right Brake
Page 219 and 220: Similarly, In general, CLUTCHES AND
Page 221 and 222: IPIL(ΩP −ΩL) tS = (8.10) T(I
Page 223 and 224: The rate at which heat is generated
Page 225 and 226: Here ωo = 2π 60 (315) = 33 rad/
Page 227 and 228: for preliminary design estimates on
Page 229 and 230: CLUTCHES AND BRAKES FIGURE 8.16 Equ
Page 231 and 232: drum’s rotation, use the positive
Page 233 and 234: pmax Px = (θ2 −θ1 + sin θ1 cos
Page 235 and 236: 8.5.2 Centrifugal Clutches CLUTCHES
Page 237 and 238: CLUTCHES AND BRAKES FIGURE 8.19 For
Page 239 and 240: 3. Next the moment arm length for
Page 243 and 244: CLUTCHES AND BRAKES 8.41 to the dis
Page 245 and 246: CLUTCHES AND BRAKES Torque Capacity
Page 247 and 248: For finding the average contact pre
Page 249 and 250: CLUTCHES AND BRAKES (a) (b) (c) FIG
Page 253 and 254: Source: STANDARD HANDBOOK OF MACHIN
Page 255 and 256: CHAPTER 9 SPUR GEARS Joseph E. Shig
Page 257 and 258: SPUR GEARS SPUR GEARS 9.5 FIGURE 9.
Page 259 and 260: 9.3 FORCE ANALYSIS In Fig. 9.3 a ge
Page 261 and 262: SPUR GEARS SPUR GEARS 9.9 TABLE 9.5
Page 263 and 264: Allowable Bending Stress Number. Th
Page 265 and 266:
10.1 INTRODUCTION / 10.1 10.2 TYPES
Page 267 and 268:
HELICAL GEARS HELICAL GEARS 10.3 (a
Page 269 and 270:
helical gears are employed, a limit
Page 271 and 272:
contact ratio and the axial overlap
Page 273 and 274:
10.5.1 Strength and Durability HELI
Page 275 and 276:
HELICAL GEARS FIGURE 10.4 Dynamic f
Page 277 and 278:
HELICAL GEARS HELICAL GEARS 10.13 (
Page 279 and 280:
HELICAL GEARS housing which support
Page 281 and 282:
If the tooth contact pattern at nor
Page 283 and 284:
for external gears; for internal ge
Page 285 and 286:
HELICAL GEARS HELICAL GEARS 10.21 G
Page 287 and 288:
HELICAL GEARS HELICAL GEARS 10.23 F
Page 289 and 290:
Page 291 and 292:
Page 293 and 294:
Page 295 and 296:
Page 297 and 298:
Page 299 and 300:
Page 301 and 302:
Letting Ze = distance on line of ac
Page 303 and 304:
HELICAL GEARS HELICAL GEARS 10.39 H
Page 305 and 306:
HELICAL GEARS 10.41 Downloaded from
Page 307 and 308:
Page 309 and 310:
Page 311 and 312:
Page 313 and 314:
Page 315 and 316:
HELICAL GEARS HELICAL GEARS 10.51 p
Page 317 and 318:
HELICAL GEARS HELICAL GEARS 10.53 W
Page 319 and 320:
HELICAL GEARS HELICAL GEARS 10.55 E
Page 321 and 322:
In most cases the blank temperature
Page 323 and 324:
CHAPTER 11 BEVEL AND HYPOID GEARS T
Page 325 and 326:
FIGURE 11.3 Zerol bevel set. (Gleas
Page 327 and 328:
FIGURE 11.7 Hypoid gear nomenclatur
Page 329 and 330:
The taper you select depends in som
Page 331 and 332:
BEVEL AND HYPOID GEARS BEVEL AND HY
Page 333 and 334:
Hypoid gears are recommended where
Page 335 and 336:
TABLE 11.1 Material Factors C M BEV
Page 337 and 338:
11.4.7 Hypoid Offset BEVEL AND HYPO
Page 339 and 340:
FIGURE 11.16 Selection of spiral an
Page 341 and 342:
should be hardened and tempered abo
Page 343 and 344:
BEVEL AND HYPOID GEARS BEVEL AND HY
Page 345 and 346:
TABLE 11.7 Mean Addendum Factor BEV
Page 347 and 348:
11.5.4 AGMA References † The foll
Page 349 and 350:
BEVEL AND HYPOID GEARS TABLE 11.10
Page 351 and 352:
BEVEL AND HYPOID GEARS TABLE 11.10
Page 353 and 354:
BEVEL AND HYPOID GEARS area.The rec
Page 355 and 356:
TABLE 11.12 Load-Distribution Facto
Page 357 and 358:
BEVEL AND HYPOID GEARS FIGURE 11.21
Page 359 and 360:
Page 361 and 362:
Page 363 and 364:
Page 365 and 366:
BEVEL AND HYPOID GEARS 11.43 Downlo
Page 367 and 368:
Page 369 and 370:
Page 371 and 372:
Page 373 and 374:
TABLE 11.15 Allowable Bending Stres
Page 375 and 376:
BEVEL AND HYPOID GEARS 11.7.3 Axial
Page 377 and 378:
Pressure lubrication is recommended
Page 379 and 380:
CHAPTER 12 WORM GEARING K. S. Edwar
Page 381 and 382:
FIGURE 12.2 Photograph of a worm-ge
Page 383 and 384:
12.3 VELOCITY AND FRICTION Figure 1
Page 385 and 386:
where the subscripts are t for the
Page 387 and 388:
This force is the negative x direct
Page 389 and 390:
24, from Table 12.3, K m = 0.823 by
Page 391 and 392:
12.7 DESIGN STANDARDS The American
Page 393 and 394:
TABLE 12.6 Dimensions of the Gear a
Page 395 and 396:
Table 12.9 presents a system for st
Page 397 and 398:
12.8.3 Gear Ratio The gear ratio is
Page 399 and 400:
12.8.10 Worm Length The effective l
Page 401 and 402:
CHAPTER 13 POWER SCREWS Rudolph J.
Page 403 and 404:
FIGURE 13.1 Power screw assembly us
Page 405 and 406:
POWER SCREWS POWER SCREWS 13.5 TABL
Page 407 and 408:
POWER SCREWS POWER SCREWS 13.7 The
Page 409 and 410:
which can be solved for a circular
Page 411 and 412:
TABLE 13.3 Sizes and Capacities of
Page 413 and 414:
REFERENCES POWER SCREWS POWER SCREW
Page 415 and 416:
Page 417 and 418:
CHAPTER 14 BELT DRIVES Wolfram Funk
Page 419 and 420:
Disadvantages: ● Limited power tr
Page 421 and 422:
FIGURE 14.2 Multiple-pulley drives.
Page 423 and 424:
Because µβwπ Fu = F2′(m − 1)
Page 425 and 426:
The maximum power transmission capa
Page 427 and 428:
(a) (c) BELT DRIVES BELT DRIVES 14.
Page 429 and 430:
BELT DRIVES FIGURE 14.11 Pretension
Page 431 and 432:
BELT DRIVES 14.17 Taking into consi
Page 433 and 434:
FIGURE 14.15 Multiple-ply belt. BEL
Page 435 and 436:
4. The manufacturer can supply belt
Page 437 and 438:
BELT DRIVES FIGURE 14.18 Section of
Page 439 and 440:
The calculation of belt velocity (p
Page 441 and 442:
BELT DRIVES The flexibility of the
Page 443 and 444:
BELT DRIVES BELT DRIVES 14.29 FIGUR
Page 445 and 446:
transmissible power P is determined
Page 447 and 448:
BELT DRIVES BELT DRIVES 14.33 The a
Page 449 and 450:
BELT DRIVES BELT DRIVES 14.35 (a) (
Page 451 and 452:
(twisting of tension member and its
Page 453 and 454:
The power transmission capacity of
Page 455 and 456:
FIGURE 14.33 Comparison of system c
Page 457 and 458:
CHAPTER 15 CHAIN DRIVES John L. Wri
Page 459 and 460:
esponding chains in Ref. [15.1], bu
Page 461 and 462:
TABLE 15.1 Roller-Chain Dimensions
Page 463 and 464:
CHAIN DRIVES 15.3 SELECTION OF ROLL
Page 465 and 466:
sprockets may be required. Idler sp
Page 467 and 468:
CHAIN DRIVES TABLE 15.2 Service Fac
Page 469 and 470:
Determine Lubrication Type. The typ
Page 471 and 472:
CHAIN DRIVES CHAIN DRIVES 15.15 TAB
Page 473 and 474:
CHAIN DRIVES inexpensive, but they
Page 475 and 476:
TABLE 15.9 Offset Sidebar Chain Dim
Page 477 and 478:
CHAIN DRIVES CHAIN DRIVES 15.21 Cha
Page 479 and 480:
CHAIN DRIVES CHAIN DRIVES 15.23 TAB
Page 481 and 482:
15.6.3 Horsepower Ratings of Offset
Page 483 and 484:
15.7.3 Silent-Chain Sprockets CHAIN
Page 485 and 486:
In a drive where the shaft centers
Page 487 and 488:
CHAIN DRIVES silent-chain size when
Page 489 and 490:
Page 491 and 492:
7. Misalignment Amount and type of
Page 493 and 494:
COUPLINGS COUPLINGS 16.5 TABLE 16.1
Page 495 and 496:
alignment up to 45°. The maximum a
Page 497 and 498:
FIGURE 16.4 Portion of shaft showin
Page 499 and 500:
COUPLINGS 16.3.2 Chain, Grid, and B
Page 501 and 502:
COUPLINGS 16.13 FIGURE 16.11 (a) Si
Page 503 and 504:
COUPLINGS 16.15 FIGURE 16.16 Hydrau
Page 505 and 506:
operating radius corresponding to a
Page 507 and 508:
FIGURE 16.24 A bellows coupling. (S
Page 509 and 510:
COUPLINGS COUPLINGS 16.21 pression
Page 511 and 512:
FIGURE 16.30 Bonded type of a shear
Page 513 and 514:
16.5 UNIVERSAL JOINTS AND ROTATING-
Page 515 and 516:
COUPLINGS COUPLINGS 16.27 FIGURE 16
Page 517 and 518:
COUPLINGS The correction factor Ks
Page 519 and 520:
COUPLINGS COUPLINGS 16.31 Rzeppa Un
Page 521 and 522:
method of attachment allows a much
Page 523 and 524:
CHAPTER 17 SHAFTS Charles R. Mischk
Page 525 and 526:
Geometric fidelity is important to
Page 527 and 528:
Solution. Equation (17.1) is used.
Page 529 and 530:
SHAFTS Based on this, the designer
Page 531 and 532:
SHAFTS 17.9 The dual-entry slope dy
Page 533 and 534:
SHAFTS SHAFTS 17.11 The prediction
Page 535 and 536:
17.4 DISTORTION DUE TO TORSION Angu
Page 537 and 538:
A press fit induces a surface press
Page 539 and 540:
factor corrected for notch sensitiv
Page 541 and 542:
The methods of Secs. 17.2 and 17.3
Page 543 and 544:
REFERENCES 17.1 Joseph E. Shigley a
Page 545 and 546:
Page 547 and 548:
Page 549 and 550:
ROLLING-CONTACT BEARINGS 18.5 FIGUR
Page 551 and 552:
FIGURE 18.9 Tapered-roller thrust b
Page 553 and 554:
ROLLING-CONTACT BEARINGS where C s
Page 555 and 556:
ROLLING-CONTACT BEARINGS For exampl
Page 557 and 558:
ROLLING-CONTACT BEARINGS ROLLING-CO
Page 559 and 560:
age on the bearing per revolution a
Page 561 and 562:
ROLLING-CONTACT BEARINGS TABLE 18.5
Page 563 and 564:
deep-groove ball bearings. Self-ali
Page 565 and 566:
CHAPTER 19 JOURNAL BEARINGS Theo G.
Page 567 and 568:
Λ Bearing number = (6µω/p a)(R/C
Page 569 and 570:
TABLE 19.1 Characteristics of Lubri
Page 571 and 572:
A foil journal bearing (Fig. 19.3l)
Page 573 and 574:
TABLE 19.2 Physical Properties of J
Page 575 and 576:
TABLE 19.4 Performance Ratings from
Page 577 and 578:
Next the candidate materials are gi
Page 579 and 580:
This equation can be interpreted as
Page 581 and 582:
JOURNAL BEARINGS where θ 1 and θ
Page 583 and 584:
In general, volume flow rate per un
Page 585 and 586:
JOURNAL BEARINGS JOURNAL BEARINGS 1
Page 587 and 588:
It was proposed that the film press
Page 589 and 590:
Page 591 and 592:
Page 593 and 594:
Page 595 and 596:
Page 597 and 598:
L b 1 Sb2 + b3 (L/D) TABLE 19.15 S
Page 599 and 600:
show all

chapter 1 evolution of a successful design

You also want an ePaper? Increase the reach of your titles

Delete template?

Save as template?