In fact, R2, the value of the tooth surface is equal to the distribution of the tooth surface load, both in direction and size, which is determined by the boundary conditions of the problem. It is worth noting that this symmetry of the stress distribution completely disappears when the node position moves toward the inside of the tooth, which is caused by geometric asymmetry. R1 is the principal stress that is nearly parallel to the tooth surface. It can be seen from the calculation results that the pressure on the tooth surface of the lower part (4 to 10 sections) is rapidly converted to the tensile stress due to the bending action of the teeth, and the effect is A significant increase in Tmax (visible from equation (12)) is completely different from the analytical solution of the elastic mechanics of the two cylinders.
From the strength theory and experimental observation, the location of Tmax and Tmax is important for the generation of pitting. According to the calculation of elastic mechanics, the Tmax value occurs at 0.796B from the surface of the symmetric cross section, and the maximum value is 0.3p. When the two gears are in contact (b), Tmax occurs at about 0.35B from the surface on the sixth section, and the maximum value is about 0.5p0. There is a significant difference between the two. The main reason for the above difference is the calculation model of the gear and the two-column model. There is a fundamental difference. After the tooth is loaded, the tensile stress is tangential to the tooth gallery in the direction of the tooth profile. The R1 direction is close to the tangential direction of the tooth profile. Due to the superposition of stress, the surface pressure is quickly applied in the surface. The stress p (mainly caused by contact) is transformed into tensile stress (mainly due to bending), and the tensile stress increases significantly at the lower part of the tooth (near the root of the tooth), causing an increase in the maximum shear stress Tmax, and (b) shows The symmetrical cross section of the two tooth profiles is the stress distribution on the fifth section.
The stress distribution on the symmetrical section above discusses the variation of the contact stress in the range of the meshing zone when the pair of teeth are meshed and driven in a certain meshing zone (point).
It can be seen that the tensile stress of the tooth profile of R1 is gradually reduced from (1) to (5). The reason is that the tensile stress caused by bending is more obvious when the contact point is away from the fixed end, and the contact point is calculated near the root of the tooth. This effect is of course reduced when the fixed end of the model is used. It can also be seen that the position of the maximum shear stress Tmax is gradually approached from the tooth profile surface by (1) to (5), which is caused by the steep distribution of the stress distribution at each meshing point on the symmetrical section of the distribution of R1.
In the Chinese language, the modern numerical calculation method is applied, and the stress of the spur gear contact area under the pure normal load without friction is studied in detail. Through calculation and analysis, the spur gear mechanism has a clearer understanding of the distribution and change of the tooth contact stress during the transmission process, which is of great significance for exploring the cause of the true failure of the tooth surface and improving the gear design and processing.
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