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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.

both the driving and the driven pulleys. The belt tightener produces a constant force F2 for all operating conditions but increases the bending frequency fb, thus reducing the safety stress of the belt. Taking this into consideration, we see that the belt tightener used should have a minimum diameter equaling that of the smaller pulley, if possible. 4. Pretensioning by torque making use of a rocker or pivoting pulley: Figure 14.14 shows an arrangement with an eccentric pulley shaft pivoting the motor pulley shaft. The pulley is driven by a FIGURE 14.14 Pretensioning by torque. gear assembly. The shaft tensioning force Fw increases almost in proportion to the tooth force FZ, and with the correct ratio of h2/h1, adapts automatically to the specific torque to be transmitted. Belt slipping is impossible with this method of pretensioning. For all belt pretensioning methods using tensioning devices which can be adjusted during operation of the drive (e.g., methods 2 to 4 described above), the shaft tensioning force Fw and the usable forces F 1 and F2 in the belt sides are not influenced by centrifugal force. Centrifugal force increases the belt stress by f, though.

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Calculations for flat-belt drives are based on Eytelwein s fundamental equation of belt friction: F1 = exp F2 180 (14.29)

NOTE: If you re not used to C++, make sure you put that semicolon (;) at the end of the class declaration, after the closing brace!

For calculations for a belt drive, the arc of contact of the smaller pulley is substituted for the arc of contact , since the belt slips at the smaller pulley first, and the active arc of contact w is not known. The transmissible power P is calculated from the peripheral forces Fu = F 1 F2 = F2 exp and the belt velocity v and is expressed by P1 = v1Fu P2 = v2 Fu The belt velocities are v1 = n1d1 v2 = n2 d2 (14.32) (14.31) 1 180 (14.30)

0.1- F 50-V disk capacitor 4.7- F 50-V electrolytic capacitor 0.2- F 50-V electrolytic capacitor 2N2222 npn transistor 1N4001 silicon diode SPST power switch Momentary pushbutton switch (normally open) 5 6-V DPDT relay (RadioShack) Male and female headers, PC board, speaker, 9-pin RS-232 connector

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.

The energy-storage capacity of a flywheel is determined from its polar moment of inertia J and its maximum safe running speed. The necessary inertia depends on the cyclic torque variation and the allowable speed variation or, in the case of energystorage flywheels, the maximum energy requirements. The safe running speed depends on the geometry and material properties of the flywheel.

Flywheels store energy. Indeed, flywheels are used as energy reservoirs, and this use will be discussed in Sec. 7.4. Their principal use in machine design, however, is to smooth the variations in shaft speed that are caused by loads or power sources that vary in a cyclic fashion. By using its stored kinetic energy 0.5J 2 to absorb the variations in torque during a machine cycle, a flywheel smooths the fluctuating speed of a machine and reduces undesirable transient loads. The effect of a flywheel is therefore fundamentally different from that of a regulator: A flywheel limits the speed variation over one cycle and has minimal effect on the average speed; a regulator uses negative feedback to maintain a selected average speed with only secondary effects on the speed during a cycle. The flywheel has other features which have to be considered in design. Its size, speed, and windage effect can all be used to advantage in providing a secondary function as part of a clutch, gear, belt pulley, cooling fan, pump, gyroscope, or torsional damper.

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