Analysis method of quasi-static analytical model of deep groove ball bearing with combination angle misalignment

[0094] Take the SKF6011 deep groove ball bearing as an example, Table 1 shows the detailed geometric and material parameters of the type bearing.

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[0096] First, establish the quasi-static analysis model of SKF6011 deep groove ball bearings containing combined angles, the balance equation group of its ball is obtained, and the ball force balance equation is considered, and the combined angle is not in the preloading force. Abnormal equations and combined angles do not have the force balance equation of the inner ring under the inner load, according to a given bearing, the radial force is set to f y = 1KN. The inner ring speed is set to n = 5krpm. The outer ring and inner ring angle are not set to the azimuth of the center axis. The outer ring angle is not intended to be set to θ to = -1mRAD, based on Newton Lapus method to solve the balance equation group, the contact angle α between the ball and the raceway can be obtained ij/oj , Contact load Q ij/oj , Peaceful rubbing coefficient μ j , As well as non-normal pretension load f mistz , M mistx , And M misty. According to the above data, the quasi-static analysis model of SKF6011 deep groove ball bearings is solved based on the double-layer Newton Lapus iterative method, and the results are shown in Figures 8 and 9.

[0097] When the inner ring angle is not set to θ ti = 4mRAD. Since the bearing has a modified characteristic, after each set of inner ring angles, the results of 1000 times are taken after the result of 1000 times (the inner ring is rotated by 5 laps, each loop is divided into 200 times). According to the exercise relationship between the deep groove ball bearing parts, the inner ring rotates the 5-turn corresponding ball around the Z-axis 214 turns. In the combined angle, the contact force between each ball and the internal and external roller can be seen, and the change cycle is consistent with the rotation cycle of the ball with the rotation of the inner race. Due to the angle, the ball is passed through two different load-bearing regions within a rotation cycle. In the combined angle, the time-transition characteristics of the azimuth angle result in the periodic changes of the contact force seen in the inner circle. In this case, the inner ring rotation cycle and the rotation cycle of the ball determine the time-change cycle of the contact force. The time-change contact force between the combined angle is not the medium type A, the ball and the roller is shown in Figure 8. In response to the combined angle, the time variable contact force between the ball and the raceway is shown in Figure 9.