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Rim thicknesses are generally equal to or slightly greater than the whole depth of the teeth. 12.7.9 Worm Face The face or length of the worm should be such that it extends beyond the point where contact between its threads and the teeth of the gear begins. Unlike with spur and helical gears, the pressure angle of a worm gear varies along the length of the tooth and becomes quite low on the leaving, or recess, side. This causes contact to occur on the worm almost to the point where the outside diameter of the worm intersects the throat diameter of the gear. The formula in Table 12.7 provides a conservative value of the worm face width and is based on intersection of worm outside diameter with gear throat diameter. More exact worm face widths may be determined by detailed calculations or layouts which take into consideration the face width of the gear and fix more definitely the extent of contact along the worm threads. Good practice includes the breaking or rounding of the sharp edge of the worm threads at the end of the worm face. This procedure is particularly important where the worm face is less than provided for in the formula in Table 12.7. 12.7.10 Bored Worm Blanks Where it is necessary to use a bored worm, the blank is normally designed with a key seat for driving purposes. The thickness of material between the worm root and the key seat should be at least 0.5ht. This is a general recommendation which is governed to some extent by whether the blank is hardened or unhardened. An increase in this amount may be necessary if the blank is hardened, particularly if a case-hardening process is used.

2 2 vm = ( Am + Bm Am Bm)1/2 =

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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FIGURE 29.19 The principal stresses due to the steady stresses Am and Bm appear on the distortion-energy ellipse as point D. The transform to equivalent distortion energy in tension is point E, which becomes the abscissa of point P. The principal stresses due to stress amplitude Aa and Ba appear as point D ; the transform is E , which becomes the ordinate of point P.

TABLE 3-4 NCD-102 ADDRESSABLE PARALLEL-TO-SERIAL ENCODER NAME/ADDRESS PROGRAMMING NAME/ADDRESS PROGRAMMING NAME N2 N1

FIGURE 29.20 (a) A shaft subjected to a steady torque T and completely reversed flexure due to bending moment M; (b) the mean-stress element and the stress-amplitude element.

29.30 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.

FIGURE 29.21 Designer s fatigue diagram for geared shaft showing load line of slope r = 2M/( 3T ), the operating point P, using the Goodman failure locus, and the designer s line reflecting a design factor of n.

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