According to the sum of the displacement coefficients X2=Xi+X2, the gear transmission can be divided into three types: zero transmission (X2=0) positive transmission (X2=>0) and negative transmission (X2=<0) where zero transmission It can be divided into standard gear transmission (=2=0) and equal displacement gear transmission (X,=―X2 ping 0). Under normal circumstances, adopting X, >0, X2<0 and other variable displacement gear transmission can improve the bearing capacity and service life of the gear transmission, and the tooth surface anti-wear ability can be adjusted. This paper mainly discusses the performance of five aspects of contact strength, bending strength, wear, vibration and lubrication after the external meshing of the joint, and uses a pair of Z, =25Z2=38, m 2, X2=―1.2 The node external gears are compared.
1 tooth surface contact strength tooth surface contact stress is calculated according to the Hertz formula. P is a function of the position of the meshing point in the meshing line segment. The variation law is, for example, the gear transmission for the general end face coincidence degree ea<2, in the pinion single tooth The contact stress at the lower boundary point C of the meshing zone is the largest, and after the outer meshing of the joint, the C point is moved to the middle of the N, N2 line. In this example, in the case of Pc relative to the standard 2 tooth bending strength and other displacement gear transmission, since the pinion gear adopts a positive displacement, the radius of curvature is increased, and the index circle and the tooth root thickness of the tooth root are also increased. Thereby, the bending strength of the root of the tooth is improved. Although the large gear takes a negative displacement to reduce its bending strength, the bending strength of the large gear is still sufficient, especially the large and small gears are basically close to the same strength.
3 The wear of the tooth surface of the tooth surface and the material properties, normal pressure, surface finish, and the gear working under lubrication have the greatest influence on the wear of the tooth at each point of the tooth. The amount of wear at each point of the tooth is sliding. The coefficient is proportional. And when the B2 point is engaged, the sliding coefficient reaches the maximum Ullms respectively (and Ulmas>Uh indicates that the tooth profile wear is the most serious. Therefore, in actual design, the actual meshing line should be kept as far as possible from the limit point Ni on the pinion, thus The Ulmax value of the pinion is lowered. The values ​​of Ulmax and Umax are as close as possible so that the tooth roots of the large and small gears are close to each other. After the external meshing of the nodes is taken, for example, since the actual meshing line b1b2 moves to the left of the node, the pinion teeth When there is almost no high-speed gear transmission, the commutation of the tooth surface friction is one of the factors causing the vibration of the gear. During the meshing process, the tooth surface of the driving wheel is opposite in the direction of the frictional force of the joint, respectively The top and the root, and the frictional force on the surface of the driven tooth is respectively directed by the top and the root to the pitch line, and the frictional force changes, thereby causing the gear to vibrate.
The external meshing transmission is adopted to make the actual meshing line be biased to the node side, and the frictional force direction is consistent throughout the meshing process, thereby avoiding the excitation factor caused by the frictional force commutation. In the design of high-speed gear transmission, the performance of the node external meshing drive should be fully considered.
5 Lubrication between the tooth surfaces affects the tooth surface failure (such as pitting, wear, gluing, etc.) and the pressure distribution and values ​​related to the failure, such as the tooth surface friction resistance 222 joint surface bearing alloy shear According to the calculation of 221, it is not difficult to obtain the shear strength of the bearing alloy on the joint faces of the a and b sections. Note that the above two equations are established because the joint force of the two joint faces is sufficiently large; there is no relative movement between the two alloys on the joint surface. In fact, the two alloys are mostly caused by insufficient bonding strength due to insufficient bond strength. Therefore, the focus of the blank manufacturing process is the guarantee of the bonding ability of the two alloys.
3 The application of the quality inspection method for the bimetal sliding bearing blanks is tested by a state-owned large-scale machine manufacturer for hundreds of varieties and specifications and thousands of bearing blanks. The results show that the theoretical basis is consistent with the actual situation, the operation method is simple, practical, short cycle and low cost. At present, the company has developed corresponding enterprise standards for the detection and acceptance of the quality of bimetal sliding bearing blanks, which is suitable for popularization and application.
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