# Force analysis and meshing efficiency calculation

2022-08-16
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Force analysis and meshing efficiency calculation of swing bar reducer

1 introduction swing bar reducer is a typical representative structure in movable teeth transmission mechanism, which uses swing pair to transmit power. Compared with movable teeth transmission mechanism, the relative motion between the moving pairs of swing bar reducer is rotation without obvious forced sliding. This novel structure will bring obvious superior transmission performance, so it has great development potential and broad application prospects after eliminating this reason. In this paper, the force condition of the swing mechanism in the transmission process is analyzed, and the calculation formula of the meshing efficiency of the swing bar reducer is derived. The setup of the recovery system of the swing bar reducer is to restore the original setup of the computer before exiting the utilization program, which provides a basis for the optimal design and further research of the swing bar reducer. 2 force analysis of oscillating mechanism for the profile equation and kinematic characteristics of the internal gear teeth of the oscillating rod reducer, we have discussed it in literature . For the output and input rotating structure in the same direction, when the shock device rotates clockwise relative to the drive ring φ 1 angle, set the rotation angle of the stratasysconnex series gear relative to the drive ring as φ 2, then the transmission ratio is φ 1／ φ 2, as shown in Figure 1. At this time, the included angle between the normal at the contact point M1 between the inner roller and the shock absorber and the Y axis of the fixed coordinate system (O, x, y) α 1 is: α 1＝ φ 1－ δ (1) From △ obo1 in Figure 1, we can get: (2) in the formula: e - eccentric distance of shock absorber

rb, RZ -- radius of shock absorber and roller

Figure 1. If R0, R1 and R2 are used to represent the distance from the swing center p to the center O of the shock absorber, the center O1 of the inner roller and the center O2 of the outer roller, respectively, β 2 represents the included angle from the swing center p to the connecting line between the center of the inner and outer rollers, then e. the tension value used in the tensile test process is smaller than that of general rubber products Rb, RZ, R0, R1, R2 and β 2 constitutes a group of basic design parameters of swing rod reducer

from the expression △ opo1 in Figure 1, we can get: (3) in the formula: the included angle between the normal at the contact point m2 of the external roller and the internal gear profile of the swing mechanism and the Y axis of the fixed coordinate system (O, x, y) α 2 is: α 2＝ α＋φ 2 (4), where: α＝ Arctg (5)

set θ 1 is the friction angle between the inner roller and the shock absorber, then the included angle between the total reaction FJ of the shock absorber to the inner roller and the Y axis of the fixed coordinate system (O, x, y) α J is: α J＝ α 1＋ θ 1 (6) the included angle between force FJ and is ∠ pm1o1 ＋ θ 1. Where:

can be obtained from △ pm1o1 in Figure 1:

and ∠ po1m1 is ∠ po1b, which can be obtained from △ bpo1 as:

so:

the torque TJ of force FJ to the swing center P point of the swing mechanism is counterclockwise in Figure 1, and the value is: (7) set θ 2 is the friction angle between the outer roller and the inner gear, then the angle between the total reaction FN of the outer roller of the inner gear and the Y axis of the fixed coordinate system (O, x, y) α N is: α N＝ α 2－ θ 2 (8) force FN and

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