chapter 1 evolution of a successful design

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A THESAURUS OF MECHANISMS 2.26 MACHINE ELEMENTS IN MOTION (c) (d) (e) (a) FIGURE 2.25 Function generators. These are mechanical devices in which the output moves as some function of the input y = f(x). (a) Four-bar linkage function generator; (b) function generator in pressure gauge; (c), (d) function generator in a speedometer; (e) Scotch yoke sine-cosine generator; (f) epicyclic sine-cosine generator; (g) noncircular 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 of Use as given at the website. (g) (f) (b)
A THESAURUS OF MECHANISMS (a) A THESAURUS OF MECHANISMS 2.27 (e) (c) FIGURE 2.26 Computing mechanisms. These devices are used on mechanical computers for performing mathematical operations. (a) Ball disk integrator; (b) multiplier; (c), (d) adders; (e) epicyclic sine generators; (f) Scotch yoke sine generator; (g) noncircular gears; (h) specialfunction cams. 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. (d) (b) (f) (g)
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: Source: STANDARD HANDBOOK OF MACHIN
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: (c) (f) (i) A THESAURUS OF MECHANIS
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 81 and 82: It is a common rule of thumb to ass
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CAM MECHANISMS CAM MECHANISMS 4.23
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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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Source: STANDARD HANDBOOK OF MACHIN
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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
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3. Next the moment arm length for
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CLUTCHES AND BRAKES 8.41 to the dis
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CLUTCHES AND BRAKES Torque Capacity
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For finding the average contact pre
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CLUTCHES AND BRAKES (a) (b) (c) FIG
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CHAPTER 9 SPUR GEARS Joseph E. Shig
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SPUR GEARS SPUR GEARS 9.5 FIGURE 9.
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9.3 FORCE ANALYSIS In Fig. 9.3 a ge
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SPUR GEARS SPUR GEARS 9.9 TABLE 9.5
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Allowable Bending Stress Number. Th
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10.1 INTRODUCTION / 10.1 10.2 TYPES
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HELICAL GEARS HELICAL GEARS 10.3 (a
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helical gears are employed, a limit
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contact ratio and the axial overlap
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10.5.1 Strength and Durability HELI
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HELICAL GEARS FIGURE 10.4 Dynamic f
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HELICAL GEARS HELICAL GEARS 10.13 (
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HELICAL GEARS housing which support
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If the tooth contact pattern at nor
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for external gears; for internal ge
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HELICAL GEARS HELICAL GEARS 10.21 G
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HELICAL GEARS HELICAL GEARS 10.23 F
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Letting Ze = distance on line of ac
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HELICAL GEARS HELICAL GEARS 10.39 H
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HELICAL GEARS 10.41 Downloaded from
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HELICAL GEARS HELICAL GEARS 10.51 p
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HELICAL GEARS HELICAL GEARS 10.53 W
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HELICAL GEARS HELICAL GEARS 10.55 E
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In most cases the blank temperature
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CHAPTER 11 BEVEL AND HYPOID GEARS T
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FIGURE 11.3 Zerol bevel set. (Gleas
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FIGURE 11.7 Hypoid gear nomenclatur
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The taper you select depends in som
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BEVEL AND HYPOID GEARS BEVEL AND HY
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Hypoid gears are recommended where
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TABLE 11.1 Material Factors C M BEV
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11.4.7 Hypoid Offset BEVEL AND HYPO
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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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