chapter 1 evolution of a successful design

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HELICAL GEARS 10.26 GEARING FIGURE 10.16 Tool-tip radius adjustment factor for 25° spur teeth. Tool-tip radius = r T for a 1-diametral-pitch gear. FIGURE 10.17 Tooth thickness adjustment factor Q TT for 20° spur teeth. Tooth thickness modification =δ t for 1-diametral-pitch gears. 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 <strong>of</strong> Use as given at the website.
HELICAL GEARS HELICAL GEARS 10.27 FIGURE 10.18 Tooth thickness adjustment factor QTT for 22 1 ⁄2° spur teeth. Tooth thickness modification =δ t for 1-diametral-pitch gears. FIGURE 10.19 Tooth thickness adjustment factor Q TT for 25° spur teeth. Tooth thickness modification =δ t for 1-diametral-pitch gears. 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 <strong>of</strong> Use as given at the website.
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Source: STANDARD HANDBOOK OF MACHIN
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EVOLUTION OF A SUCCESSFUL DESIGN EV
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Flywheels are an important machine
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EVOLUTION OF A SUCCESSFUL DESIGN sp
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GLOSSARY OF SYMBOLS CHAPTER 2 A THE
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(a) A THESAURUS OF MECHANISMS 2.5 (
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(c) A THESAURUS OF MECHANISMS A THE
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(g) (l) (c) (e) A THESAURUS OF MECH
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(a) (g) (c) A THESAURUS OF MECHANIS
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(a) (c) (e) A THESAURUS OF MECHANIS
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(e) (a) (i) A THESAURUS OF MECHANIS
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(b) A THESAURUS OF MECHANISMS (d) A
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(a) (f) A THESAURUS OF MECHANISMS A
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(a) A THESAURUS OF MECHANISMS A THE
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(c) (a) A THESAURUS OF MECHANISMS A
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(c) (f) (i) A THESAURUS OF MECHANIS
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A THESAURUS OF MECHANISMS (a) A THE
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(a) (d) (j) (g) A THESAURUS OF MECH
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CHAPTER 3 LINKAGES Richard E. Gusta
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(a) (c) where l = number of links (
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(a) (c) LINKAGES LINKAGES 3.5 FIGUR
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Since both sides of (3.5) can be di
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The driven link d will be at angle
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LINKAGES FIGURE 3.8 Two positions o
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LINKAGES LINKAGES 3.13 FIGURE 3.10
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LINKAGES FIGURE 3.12 Determining th
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of motion. Proper care in selection
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4. With O B as vertex, set off a li
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3. Determine lines S ab(ab) and S a
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LINKAGES LINKAGES 3.23 3.13 John J.
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CHAPTER 4 CAM MECHANISMS Andrzej A.
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FIGURE 4.3 Plate cams with oscillat
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FIGURE 4.6 Types of follower motion
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CAM MECHANISMS CAM MECHANISMS 4.7 F
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CAM MECHANISMS CAM MECHANISMS 4.9 F
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the motion specification for the ri
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CAM MECHANISMS CAM MECHANISMS 4.13
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CAM MECHANISMS 4.15 This is called
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It is a common rule of thumb to ass
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For F23 = 0, roller and cam lose th
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FIGURE 4.20 Programming of cam syst
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n5 = N2N4 n2 (5.5) N3N5 and the t
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5.3 PLANETARY GEAR TRAINS GEAR TRAI
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GEAR TRAINS 5.7 termini of the velo
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GEAR TRAINS TABLE 5.1 Solution by T
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GEAR TRAINS 5.11 TABLE 5.2 Characte
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FIGURE 5.9 (a) Planetary train; (b)
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GEAR TRAINS GEAR TRAINS 5.15 (a) (b
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SPRINGS SPRINGS 6.5 close-wound: wo
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6.3.2 Heat Treatment of Springs Hea
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SPRINGS 6.9 Downloaded from Digital
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SPRINGS 6.11 Downloaded from Digita
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Helical compression springs are str
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Types of Ends. Four basic types of
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TABLE 6.5 Typical Properties of Spr
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SPRINGS SPRINGS 6.19 The rate equat
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SPRINGS SPRINGS 6.21 FIGURE 6.9 End
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The fatigue life estimates in Table
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The spring rate for a rectangular-w
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SPRINGS 6.27 FIGURE 6.15 Stress cor
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6.5 HELICAL EXTENSION SPRINGS 6.5.1
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6.5.2 Initial Tension Initial tensi
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SPRINGS FIGURE 6.20 Common end conf
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Dynamic considerations discussed pr
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SPRINGS SPRINGS 6.37 TABLE 6.14 Tol
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The number of coils is equal to the
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SPRINGS SPRINGS 6.41 TABLE 6.17 Com
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6.7.1 Nomenclature a OD/2, mm (in)
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Ef Sc = C1 h − 2 2 (1 −µ )Ma
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SPRINGS SPRINGS 6.47 FIGURE 6.31 Lo
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Because of production variations in
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7. h = 1.41t = 1.41(0.054) = 0.076
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and Design equations are SPRINGS SP
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6.9 FLAT SPRINGS 6.9.1 Introduction
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SPRINGS fEb P = ot (6.52) where K =
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SPRINGS SPRINGS 6.59 TABLE 6.25 Max
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If unknown, let b/t = 100/1, D2 = 1
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6.11.2 Design Equations: Rectangula
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SPRINGS SPRINGS 6.65 FIGURE 6.50 Ty
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SPRINGS SPRINGS 6.67 FIGURE 6.51 Av
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used only for centerless ground all
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CHAPTER 7 FLYWHEELS Daniel M. Curti
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The energy-storage capacity of a fl
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FLYWHEELS Since the torque-angle cu
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7.2.3 Coefficient of Energy Variati
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7.2.5 Speed-Dependent Torques FLYWH
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FLYWHEELS FLYWHEELS 7.11 range [7.7
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and 205 rpm = 2π(205)/60 = 21.468
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Example 6. An alloy of density 26.6
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cos (π/8) f4 = =0.340 (7.42) 7.11
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For a constant-thickness disk witho
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factor F s = 1.0 for the fully stre
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FLYWHEELS FLYWHEELS 7.23 (g) (h) (i
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many composite flywheels shred, for
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CLUTCHES AND BRAKES CLUTCHES AND BR
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shaft begins to rotate.At the desig
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FIGURE 8.7 Classification of brakes
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8.1.4 Selecting a Brake CLUTCHES AN
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TABLE 8.2 Selecting the Right Brake
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Similarly, In general, CLUTCHES AND
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IPIL(ΩP −ΩL) tS = (8.10) T(I
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The rate at which heat is generated
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Here ωo = 2π 60 (315) = 33 rad/
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for preliminary design estimates on
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CLUTCHES AND BRAKES FIGURE 8.16 Equ
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drum’s rotation, use the positive
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pmax Px = (θ2 −θ1 + sin θ1 cos
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8.5.2 Centrifugal Clutches CLUTCHES
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CLUTCHES AND BRAKES FIGURE 8.19 For
Page 239 and 240: 3. Next the moment arm length for
Page 241 and 242: CLUTCHES AND BRAKES CLUTCHES AND BR
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 251 and 252: CLUTCHES AND BRAKES CLUTCHES AND BR
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: HELICAL GEARS HELICAL GEARS 10.25 F
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 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
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should be hardened and tempered abo
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BEVEL AND HYPOID GEARS BEVEL AND HY
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TABLE 11.7 Mean Addendum Factor BEV
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11.5.4 AGMA References † The foll
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BEVEL AND HYPOID GEARS TABLE 11.10
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BEVEL AND HYPOID GEARS TABLE 11.10
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BEVEL AND HYPOID GEARS area.The rec
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TABLE 11.12 Load-Distribution Facto
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BEVEL AND HYPOID GEARS FIGURE 11.21
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BEVEL AND HYPOID GEARS 11.43 Downlo
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TABLE 11.15 Allowable Bending Stres
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BEVEL AND HYPOID GEARS 11.7.3 Axial
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Pressure lubrication is recommended
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CHAPTER 12 WORM GEARING K. S. Edwar
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FIGURE 12.2 Photograph of a worm-ge
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12.3 VELOCITY AND FRICTION Figure 1
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where the subscripts are t for the
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This force is the negative x direct
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24, from Table 12.3, K m = 0.823 by
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12.7 DESIGN STANDARDS The American
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TABLE 12.6 Dimensions of the Gear a
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Table 12.9 presents a system for st
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12.8.3 Gear Ratio The gear ratio is
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12.8.10 Worm Length The effective l
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CHAPTER 13 POWER SCREWS Rudolph J.
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FIGURE 13.1 Power screw assembly us
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POWER SCREWS POWER SCREWS 13.5 TABL
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POWER SCREWS POWER SCREWS 13.7 The
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which can be solved for a circular
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TABLE 13.3 Sizes and Capacities of
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REFERENCES POWER SCREWS POWER SCREW
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CHAPTER 14 BELT DRIVES Wolfram Funk
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Disadvantages: ● Limited power tr
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FIGURE 14.2 Multiple-pulley drives.
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Because µβwπ Fu = F2′(m − 1)
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The maximum power transmission capa
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(a) (c) BELT DRIVES BELT DRIVES 14.
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BELT DRIVES FIGURE 14.11 Pretension
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BELT DRIVES 14.17 Taking into consi
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FIGURE 14.15 Multiple-ply belt. BEL
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4. The manufacturer can supply belt
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BELT DRIVES FIGURE 14.18 Section of
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The calculation of belt velocity (p
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BELT DRIVES The flexibility of the
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BELT DRIVES BELT DRIVES 14.29 FIGUR
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transmissible power P is determined
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BELT DRIVES BELT DRIVES 14.33 The a
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BELT DRIVES BELT DRIVES 14.35 (a) (
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(twisting of tension member and its
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The power transmission capacity of
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FIGURE 14.33 Comparison of system c
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CHAPTER 15 CHAIN DRIVES John L. Wri
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esponding chains in Ref. [15.1], bu
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TABLE 15.1 Roller-Chain Dimensions
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CHAIN DRIVES 15.3 SELECTION OF ROLL
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sprockets may be required. Idler sp
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CHAIN DRIVES TABLE 15.2 Service Fac
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Determine Lubrication Type. The typ
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CHAIN DRIVES CHAIN DRIVES 15.15 TAB
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CHAIN DRIVES inexpensive, but they
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TABLE 15.9 Offset Sidebar Chain Dim
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CHAIN DRIVES CHAIN DRIVES 15.21 Cha
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CHAIN DRIVES CHAIN DRIVES 15.23 TAB
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15.6.3 Horsepower Ratings of Offset
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15.7.3 Silent-Chain Sprockets CHAIN
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In a drive where the shaft centers
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CHAIN DRIVES silent-chain size when
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7. Misalignment Amount and type of
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COUPLINGS COUPLINGS 16.5 TABLE 16.1
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alignment up to 45°. The maximum a
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FIGURE 16.4 Portion of shaft showin
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COUPLINGS 16.3.2 Chain, Grid, and B
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COUPLINGS 16.13 FIGURE 16.11 (a) Si
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COUPLINGS 16.15 FIGURE 16.16 Hydrau
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operating radius corresponding to a
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FIGURE 16.24 A bellows coupling. (S
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COUPLINGS COUPLINGS 16.21 pression
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FIGURE 16.30 Bonded type of a shear
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16.5 UNIVERSAL JOINTS AND ROTATING-
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COUPLINGS COUPLINGS 16.27 FIGURE 16
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COUPLINGS The correction factor Ks
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COUPLINGS COUPLINGS 16.31 Rzeppa Un
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method of attachment allows a much
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CHAPTER 17 SHAFTS Charles R. Mischk
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Geometric fidelity is important to
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Solution. Equation (17.1) is used.
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SHAFTS Based on this, the designer
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SHAFTS 17.9 The dual-entry slope dy
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SHAFTS SHAFTS 17.11 The prediction
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17.4 DISTORTION DUE TO TORSION Angu
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A press fit induces a surface press
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factor corrected for notch sensitiv
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The methods of Secs. 17.2 and 17.3
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REFERENCES 17.1 Joseph E. Shigley a
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ROLLING-CONTACT BEARINGS 18.5 FIGUR
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FIGURE 18.9 Tapered-roller thrust b
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ROLLING-CONTACT BEARINGS where C s
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ROLLING-CONTACT BEARINGS For exampl
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ROLLING-CONTACT BEARINGS ROLLING-CO
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age on the bearing per revolution a
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ROLLING-CONTACT BEARINGS TABLE 18.5
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deep-groove ball bearings. Self-ali
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CHAPTER 19 JOURNAL BEARINGS Theo G.
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Λ Bearing number = (6µω/p a)(R/C
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TABLE 19.1 Characteristics of Lubri
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A foil journal bearing (Fig. 19.3l)
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TABLE 19.2 Physical Properties of J
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TABLE 19.4 Performance Ratings from
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Next the candidate materials are gi
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This equation can be interpreted as
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JOURNAL BEARINGS where θ 1 and θ
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In general, volume flow rate per un
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JOURNAL BEARINGS JOURNAL BEARINGS 1
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It was proposed that the film press
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L b 1 Sb2 + b3 (L/D) TABLE 19.15 S
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