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The tooth root transition curve is realized by the tooth top arc part of the rack tool. It is assumed that the tool tooth tip arc radius is P, the arc center angle corresponding to the arc is, and the tooth tip height is ha. The machining is that when the wheel body turns over the angle, the moving distance of the rack is l. According to the processing principle of the forming method, the trajectory of the contact point on the rotating wheel body is the conjugate tooth shape of the rack tooth shape, therefore, the rack The coordinates of the point on the transition fillet are the equation basis and the frontier research circle of the tooth transition curve. It is generally considered that the boundary width and thickness of a single gear are 6 m and 1.75 m (m is a modulus), respectively, thereby drawing a portion below the root circle and then forming it into a face.
Material properties and meshing are used to divide the built model. The unit model of plane82 is used here. The elastic modulus is E=2e11Pa; the Poisson's ratio is μ=0.3, and the network partitioning is freely divided. The divided models are as shown.
Calculation examples and results Analysis of a spur gear for a reducer, the input power is 15KW; the speed is 1000r / min, take the pinion for analysis, Table 1 lists the relevant parameters. Through the finite element analysis, the deformation map of the gear can be obtained and the stress values ​​of the joints can be calculated. The deformation diagram and the stress diagram are as shown in the sum. It can be seen from the deformation of the gear that the gear teeth are subject to significant bending deformation. It can be seen that the stress of each node and unit of the gear and the maximum and minimum stress point and stress value of the gear, the maximum stress appears at the root of the tooth, the maximum tensile stress is 692MP, and the maximum compressive stress is 863MP. The root stress is 610.77 MP. Since the influence of the coincidence degree is considered when calculating by the conventional method, the influence of the coincidence degree is not considered in the finite element analysis, in order to compare the two methods under the same conditions, in the conventional In the calculation, the influence of the degree of coincidence is removed, and the maximum bending stress is 872.53 MP, which is much larger than the maximum bending stress obtained by the finite element analysis, and is close to the maximum compressive principal stress.
Conclusion The ANSYS finite element analysis of the stress at the root of the gear can truly indicate the actual stress state of the gear teeth, and the deformation of the gear teeth can be clearly seen. The distribution of the stress and the maximum and minimum stress values ​​are clearly defined, avoiding the tradition. The algorithm looks at the graph, the complexity of the lookup table and the cumbersomeness of the calculation, and the result is more accurate than the traditional calculation. The convenience and effectiveness of ANSYS finite element software in analyzing the stress at the tooth root of the gear are illustrated.