chapter 1 evolution of a successful design

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SPUR GEARS 9.4 GEARING FIGURE 9.1 Terminology of gear teeth. A, addendum circle; B, pitch circle; C, clearance circle; D, dedendum circle; E, bottom land; F, top land; G, flank; H, face; a = addendum distance; b = dedendum distance; c = clearance distance; p = circular pitch; t = tooth thickness; u = undercut distance. meshing gears. Line E is the pressure line, and the angle φ is the pressure angle. The resultant force vector between a pair of operating gears acts along this line. The pressure line is tangent to both base circles C at points F. The operating diameters of the pitch circles depend on the center distance used in mounting the gears, but the base circle diameters are constant and depend only on how the tooth forms were generated, because they form the base or the starting point of the involute profile. TABLE 9.1 Basic Formulas for Spur 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.
SPUR GEARS SPUR GEARS 9.5 FIGURE 9.2 Layout drawing of a pair of spur gears in mesh.The pinion is the driver and rotates clockwise about the axis at O. A, addendum circles; B, pitch circles; C, base circles; D, dedendum circles; E, pressure line; F, tangent points; P, pitch point; a, initial point of contact; b, final point of contact. Line aPb is the line of action. Point a is the initial point of contact. This point is located at the intersection of the addendum circle of the gear with the pressure line. Should point a occur on the other side of point F on the pinion base circle, the pinion flank would be undercut during generation of the profile. Point b of Fig. 9.2 is the final point of contact. This point is located at the intersection of the addendum circle of the pinion with the pressure line. For no undercutting of the gear teeth, point b must be located between the pitch point P and point F on the base circle of the gear. Line aP represents the approach phase of tooth contact; line Pb is the recess phase. Tooth contact is a sliding contact throughout the line of action except for an instant at P when contact is pure rolling. The nature of the sliding is quite different during the approach action and the recess action; bevel-gear teeth, for example, are generated to obtain more recess action, thus reducing wear. Instead of using the theoretical pitch circle as an index of tooth size, the base circle, which is a more fundamental distance, can be used. The result is called the base pitch p b. It is related to the circular pitch p by the equation p b = p cos φ (9.5) If, in Fig. 9.2, the distance from a to b exactly equals the base pitch, then, when one pair of teeth are just beginning contact at a, the preceding pair will be leaving contact at b. Thus, for this special condition, there is never more or less than one pair 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.
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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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Page 205 and 206: CLUTCHES AND BRAKES CLUTCHES AND BR
Page 209 and 210: shaft begins to rotate.At the desig
Page 213 and 214: FIGURE 8.7 Classification of brakes
Page 215 and 216: 8.1.4 Selecting a Brake CLUTCHES AN
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: CHAPTER 9 SPUR GEARS Joseph E. Shig
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 301 and 302: Letting Ze = distance on line of ac
Page 303 and 304: HELICAL GEARS HELICAL GEARS 10.39 H
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HELICAL GEARS HELICAL GEARS 10.43 F
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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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