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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 MACHINE DESIGN
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SUMMARY / 4.1 4.1 CAM MECHANISM TYPES, CHARACTERISTICS, AND MOTIONS / 4.1 4.2 BASIC CAM MOTIONS / 4.6 4.3 LAYOUT AND DESIGN; MANUFACTURING CONSIDERATIONS / 4.17 4.4 FORCE AND TORQUE ANALYSIS / 4.22 4.5 CONTACT STRESS AND WEAR: PROGRAMMING / 4.25 REFERENCES / 4.28
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This chapter addresses the design of cam systems in which flexibility is not a consideration. Flexible, high-speed cam systems are too involved for handbook presentation. Therefore only two generic families of motion, trigonometric and polynomial, are discussed. This covers most of the practical problems. The rules concerning the reciprocating motion of a follower can be adapted to angular motion as well as to three-dimensional cams. Some material concerns circular-arc cams, which are still used in some fine mechanisms. In Sec. 4.3 the equations necessary in establishing basic parameters of the cam are given, and the important problem of accuracy is discussed. Force and torque analysis, return springs, and contact stresses are briefly presented in Secs. 4.4 and 4.5, respectively. The chapter closes with the logic associated with cam design to assist in creating a computer-aided cam design program.
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4.1 CAM MECHANISM TYPES, CHARACTERISTICS, AND MOTIONS
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Cam-and-follower mechanisms, as linkages, can be divided into two basic groups: 1. Planar cam mechanisms 2. Spatial cam mechanisms In a planar cam mechanism, all the points of the moving links describe paths in parallel planes. In a spatial mechanism, that requirement is not fulfilled. The design of mechanisms in the two groups has much in common. Thus the fundamentals of planar cam mechanism design can be easily applied to spatial cam mechanisms, which
Prepared while the author was Visiting Professor of Mechanical Engineering, Iowa State University, Ames, Iowa.
4.1 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.
CAM MECHANISMS 4.2
MACHINE ELEMENTS IN MOTION
FIGURE 4.1 (a) Planar cam mechanism of the internal-combustion-engine D-R-D-R type; (b) spatial cam mechanism of the 16-mm film projector R-D-R type.
is not the case in linkages. Examples of planar and spatial mechanisms are depicted in Fig. 4.1. Planar cam systems may be classified in four ways: (1) according to the motion of the follower reciprocating or oscillating; (2) in terms of the kind of follower surface in contact for example, knife-edged, flat-faced, curved-shoe, or roller; (3) in terms of the follower motion such as dwell-rise-dwell-return (D-R-D-R), dwellrise-return (D-R-R), rise-return-rise (R-R-R), or rise-dwell-rise (R-D-R); and (4) in terms of the constraining of the follower spring loading (Fig. 4.1a) or positive drive (Fig. 4.1b). Plate cams acting with four different reciprocating followers are depicted in Fig. 4.2 and with oscillating followers in Fig. 4.3. Further classification of reciprocating followers distinguishes whether the centerline of the follower stem is radial, as in Fig. 4.2, or offset, as in Fig. 4.4. Flexibility of the actual cam systems requires, in addition to the operating speed, some data concerning the dynamic properties of components in order to find discrepancies between rigid and deformable systems. Such data can be obtained from dynamic models. Almost every actual cam system can, with certain simplifications, be modeled by a one-degree-of-freedom system, shown in Fig. 4.5, where me denotes
FIGURE 4.2 Plate cams with reciprocating followers.
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.
CAM MECHANISMS 4.3
CAM MECHANISMS
FIGURE 4.3 Plate cams with oscillating followers.
an equivalent mass of the system, ke equals equivalent stiffness, and s and y denote, respectively, the input (coming from the shape of the cam profile) and the output of the system. The equivalent mass me of the system can be calculated from the following equation, based on the assumption that the kinetic energy of that mass equals the kinetic energy of all the links of the mechanism: me = where mi = vi = Ii = i = = s
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