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where constants A and B are given in Table 93 and N is the number of stress cycles for which a K value is required For numbers other than 100 million cycles the load stress factors can be interpreted from the load-life curves similar to Fig 99 Figure 99 presents typical load-life test data obtained from the roll test machine Comparisons are given for pure rolling and up to 300 percent sliding to indicate trends and slope comparison of the materials Figure 99a shows nodular iron and class 45 cast iron and Fig 99b shows cast bronze Let us consider the design approach for choosing the optimum combination of materials In fatigue design criteria, this choice is a modi cation of Fail-Safe Design by Fuchs and Stephens (1980) Fail-safe design recognizes that fatigue cracks may occur and arranges the structure so that cracks will not lead to a failure before they are detected In cam-follower system design we design and operate the machine so that the roller follower will wear out before the cam is ever affected In this manner the rollers will be periodically replaced This is the easiest and least expensive solution to the fatigue problem Therefore the roller diameter should be measured periodically and replaced when it has shown a reduction in size but before destructive wear of either the roller or cam occurs Experience over time will be necessary to succeed with this approach to discover compatible materials for each particular machine It is suggested that dependent on the size and reliability of the system a reduction of the roller diameter from -00004 to -0002 in requires a replacement For example, the author designed a newspaper folding mechanism run at 70,000 papers per hour with commercial ball-bearing rollers SAE 52100 hardened RC60-62 They were measured every six months and if the diameters were reduced by -0001 in they were replaced The cam material is SAE 8620 air-hardened die steel RC 58-60 and still running with accuracy and some surface polish over 35 years as well as operating properly and at a minimum cost Next, let us discuss some of the test data in Table 93 in which it was stated that the rollers were of equal size and the softer material of the combination failed rst However, this is not the case with cam-follower machines which use a roller smaller than the cam by a ratio of between 1 and 6 or 1 and 10 depending on the design Accordingly the follower roller surface has more fatigue stress cycles than the cam surface and will tend to fail rst This fact slants the test data of Table 93 positively to the periodic replacement of the roller follower Also, it may be noted that the roller will wear out rst even though it is a harder and more expensive surface material than that of the cam Occasionally, a soft metal ring may be added to the commercial roller follower as a choice over the manufactured bearing surface A shortcoming is the larger rotational moment of inertia of the roller and more skidding produced in contact with the cam.

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(1130)

14 34 4 4

Similarly, Eq 1121 can be directly used to obtain the moment of inertia of a body about a given point Moments of inertia of simple geometries can often be found in tables, Popov (1976), Fenster and Gould (1985) As a rst approximation, complex objects can often be broken into one or more simple shapes and the moments of inertia (about the center of mass of the combination of shapes) summed Moments of inertia can also be obtained experi-

= 40

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mentally While there are several ways to accomplish this, one of the more common methods is to calculate the natural frequency of a pendulum made from the object (an interesting application of this to moment of inertia calculation for passenger cars is described by Garrott and Monk (1988) The following simple example describes the direct use of the formulas for determining the mass, center of mass, and moment of inertia of a at plate

=ek+l,

EXAMPLE Consider the square plate with sides of length s, a thickness t, and a density r shown in Fig 116 The mass of the plate is given by

Use the method of cylindrical shells to calculate the volume enclosed when the curve y = x 2 , 0 x 3, is rotated about the x-axis (Figure 820)

The coordinates of the center of gravity of the plate are given by ycg = xcg = rst x 2 1 0 xr(st )dx = m 2 m x=

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We reverse, in our analysis, the roles of the x- and y-axes Of course y ranges from 0 to 9 For each position y in that range, there is a segment stretching from x = y to x = 3 Thus it has length 3 y Then the cylinder generated when this segment (thickened to a strip of width y) is rotated about the x-axis has volume V ( y) = 2 y [3

which, of course, describe the center of the plate The moment of inertia about the center of the plate is

1132 Moving Moments of Inertia to Other Points Sometimes the moment of inertia about the center of mass is known, but the moment of inertia about another point on the body is required While the moment of inertia about the desired point could be calculated directly, it is often easier to simply move the moment of inertia If the distance between the center of mass and the point O where the moment of inertia is desired is given by d, the two moments of inertia are related by the parallel-axis theorem Jo = Jcg + md 2 (1131)

Solution:

2 y [3

As with the previous results, planar motion is assumed (though an analogous result holds for spatial motion with proper de nition of the distance d and the axes of rotation) This relationship can be proven easily by substituting the expression xo = xcg + x into Eq 1121 and realizing that d2 = x2 + y2

(1132)

= 2

(1133)

= 2 = 2 = 2 =

Continuing with the example of the at plate in Fig 116, suppose that the plate is pinned to rotate around point O From the discussion above, the kinetic energy can be described in terms of the angular velocity and the moment of inertia about point O To derive the moment of inertia about point O from the moment of inertia about the center of mass, the parallel axis theorem can be used 1 s = Jcg + ms 2 Jo = Jcg + m 2 2 As a check, the moment of inertia about O can be derived using the basic formula:

y = ln(2x2 + 1)

x =0

y5/2 3y2 2 5/2

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