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with the normal force, meaning that more power will be dissipated if a heavier load is moved From the standpoint of choosing an appropriate friction model, these characteristics can be used to determine whether a viscous friction or Coulomb friction model is a closer representation As the term dry friction implies Coulomb friction models are often useful when dry lubricants are used between moving surfaces The usefulness of the model is not limited to such cases, however, since transmissions with grease or oil lubricants also exhibit Coulomb friction Consequently, a combination of models is often used to capture the behavior of real systems For example, Pisano (1984) and Hanachi and Freudenstein (1986) demonstrated the need for Coulomb friction models in high-speed cam modeling despite the presence of lubricating oil It is commonly known that the friction coef cient in Eq 1165 is higher when the system is at rest (static friction) that when the system is moving (dynamic friction) This relationship can be captured in a smooth manner by a slightly more complicated version of the friction force (Friedland, 1996) F = ( m k + ( m s - m k )e - c d ) Fn sgn(d )

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f ( x) 1 + [ f ( x) ]2

(1167)

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where mk is the kinetic coef cient of friction, ms is the static coef cient of friction and c is a positive number used to produce a smooth transition between the two coef cients (the larger the value of c, the more abrupt the change between static and dynamic friction) This model is still not suf cient to capture stiction or stick-slip friction where the difference between static and dynamic friction values causes a system to move intermittently Capturing such effects is challenging because of the discontinuity involved as the system transitions between stasis and motion Models for stick-slip friction are available, Karnopp (1985), Haessig and Friedland (1991) but can be numerically dif cult to implement 1153 Mechanical Ef ciency Although mechanical ef ciency does not take the form of the damping element illustrated in Fig 1118, it does represent a form of system damping and can often be an effective way to model dissipation in the system Mechanical ef ciency, h, is de ned in terms of the ratio of input power to output power for a certain subsystem such as a gear train

= 2

(1168)

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The total area of this rectangle and triangle is 00955, thus In 11= 00955 The logarithm produced in most hand calculators is 00953, just a little bit smaller than this number as is expected from the shape of the curve

2x 3 1 + [6x 2 ]2

To make physical sense, the value of h must lie between zero (completely inef cient) and one (perfectly ef cient) The power lost due to dissipation is simply the difference between the input and output power or Peff = Pin - Pout = (1 - h) Pin (1169)

The power dissipated depends upon the amount of power being transmitted through the subsystem and so, like Coulomb friction, depends upon both the applied load and the speed of the system Gearboxes, lead screws, and other transmission devices are often successfully modeled using an overall ef ciency to account for system damping Mechanical ef ciency is somewhat different than the viscous or dry friction models presented above since its inclusion alters the effective mass, stiffness, and damping of the system Qualitatively, the loss of ef ciency associated with an inef cient transmission makes everything downstream of the transmission feel heavier, stiffer, and more damped This effect is illustrated in the example in the following section

54

1154 Combinations and Equivalent Dampers As mentioned before, one of the most common ways of adding damping to a system is to choose an appropriate form for the damping and determine the parameters experimentally If, however, damping values are known for individual dampers in the system, these elements may be combined according to the same rules as springs If two dampers have damping coef cients of b1 and b2, a single equivalent damper has a damping coef cient of beq = b1 + b2 if the dampers are combined in parallel and 1 1 1 = + beq b1 b2 (1171) (1170)

This integral is easily calculated using the u-substitution u = 36x 4 , du = 144x 3 dx With this substitution the limits of integration become 36 and 576; the area is thus equal to 54

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