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The simulation of the operating conditions of transmission gear is strongly influenced by the inevitable presence of various types of errors and/or tolerances, manufacturing processes and assembly, in the kinematic simulation. As a result, the path of contact moves from the theoretical position and appear transmission errors, increasing overload dynamics and the level of noise and vibration. The presence of errors produced that the position angle of the gear with respect to pinion differs from the theoretical transmission ratio, in general there is a delay in the gear, which generates: 1) loss of the conjugate action and transmission error, which causes jumps in the angular velocity, which indicates the presence of shocks, with a high level of noise and vibration, and 2) loss of contact linear transforms into contact point. The shift in the trajectory of the contact can lead to the contact edge, which increases substantially, the levels of tension reducing load capacity, [1]. The method of analysis of tooth contact (TCA) is included in the kinematic simulation, and allows investigating the displacement of the contact and the slope of the function of transmission errors, considering the gears as rigid bodies or under light loads. To solve the above problems, Krenzer and Litvin have proposed programs TCA in what pre-design a parabolic function square transmission errors to get continuity in the transmission. This paper presents the model and analysis of a pre-designed polynomial function of transmission errors (parabolic function of order n) with the aim of ensuring that the function of movement meets the basic law of the design of gears, for transmissions with high speeds of operation, which should be designed with the following restrictions: the transmission must be continued through the first and second derivative of displacement, and the function of the derivative of acceleration (jerk) must be finite, throughout the interval.Copyright © 2008 by ASME |
