By William C. Orthwein
Written for engineers, this reference collects a variety of formulation, analytical tools, and graphs on the topic of the layout and choice of brakes and clutches to be used within the car, airplane, farming, and production industries. It simplifies calculations, introduces quite a lot of purposes, and assists within the number of parameters for particular layout demanding situations. a few of the layout options are awarded by means of a variety of examples, 550 exhibit equations, and approximately two hundred figures. Orthwein taught at Southern Illinois college at Carbondale.
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Extra resources for Clutches and Brakes: Design and Selection
Mechanics of Materials. 2nd ed. Englewood Cliﬀs, NJ: Prentice-Hall. Copyright © 2004 Marcel Dekker, Inc. 3 Externally and Internally Pivoted Shoe Brakes Typical externally and internally pivoted shoe brakes are shown in Figures 1 and 2. In all but extremely rare designs, equal forces act upon both shoes to produce equal applied moments about their pivots. External shoe brake control is usually through a lever system that may be driven by electromechanical, pneumatic, or hydraulic means. Internal shoe brake control is usually by means of a double-ended cylinder or a symmetrical cam.
Copyright © 2004 Marcel Dekker, Inc. 24 Chapter 2 III. LEVER-ACTUATED BAND BRAKE: BACKSTOP DESIGN This type of brake may be represented as shown in Figure 4(a). Moment equilibrium about the pivot point of the lever requires that F1 a À F2 b þ Pðb þ cÞ ¼ 0 ð3-1Þ so that substitution for F2 from equation (1-7) yields ÀF1 ða À beÀAa Þ ¼ Pðb þ cÞ ð3-2Þ as the force P required to activate the brake. Substitution for F1 in equation (3-2) from relation (1-11) yields P¼ beÀAa À a T ÀAa rð1 À e Þ b þ c ð3-3Þ Note that not only is the force related to the lever arm length, as is to be expected from elementary statics, but a braking torque may be exerted with no activating force if a ¼ beÀAa ð3-4Þ In other words, the lever portion of length c could be removed and the mechanism would stop rotation in the direction shown [Figure 4(b)].
II. 0 N-m subject to the conditions that the drum width be no greater than 100 mm and that the drum diameter be no greater than 750 mm. 5 when using a steel that has a working stress of 410 MPa. Other mechanisms require that the angle of wrap not exceed 290j. Lining temperature is not expected to rise above 300jF (148jC) during the most severe conditions. 10 MPa. Return to Chapter 1 to ﬁnd that the lining represented by Figure 4 is one of several that is ﬂexible enough for use in a band brake and has the limiting temperature and pressure capability.