Gear double-sided wear method based on ABAQUS secondary development UMESHMOTION subprogram

Abstract

The invention provides a gear double-face abrasion method based on a UMESHMOTION subprogram secondarily developed on the basis of ABAQUS. According to the method, an Archard wear model or an energy dissipation model and other wear models are combined with a finite element-based gear contact model, so that quantitative calculation can be accurately carried out on gear wear, and a simulation method capable of rapidly and effectively carrying out accurate quantitative calculation on different gear types, loads, materials and working conditions of high-performance gear wear is provided. Through a subprogram UMESHMOTION, based on an Archard wear model or an energy dissipation model and other wear models, according to the wear loss of a gear pair contact area, grid node movement is carried out on the gear pair contact area to realize gear pair wear simulation. By means of the method, accurate quantitative calculation and process processing can be conducted on high-performance gear abrasion in a targeted and accurate mode, repeated finite element pretreatment steps are avoided, the finite element simulation efficiency is greatly improved, and the time cost is reduced.

Description

Technical Field

[0001] The invention relates to the technical field of gear simulation, and in particular to a gear double-sided wear method based on the secondary development of the UMESHMOTION subroutine of ABAQUS. Background Art

[0002] Tooth surface wear is one of the core causes of impaired gear service performance and destruction of tooth surface integrity. It manifests itself as a dynamic cumulative effect of gradual damage and shedding of tooth profile material, which runs through the entire service life of the gear transmission system and has a significant impact on the transmission efficiency and service life of the gear system. This phenomenon not only affects the tooth side clearance, tooth profile accuracy, time-varying meshing stiffness and pitch error, but is also an important factor in inducing internal excitation. Slight tooth surface wear can change the contact characteristics of gear meshing, reduce the accuracy of the transmission system, and increase the transmission error. When the degree of wear increases, it will cause vibration and noise problems, increase the dynamic load of the gear pair, and accelerate the development of other failure modes, such as pitting and tooth breakage.

[0003] Therefore, in engineering practice, it is particularly important to accurately calculate the wear of high-performance gears. However, this task is extremely complex because it requires accurate determination of tooth surface contact stress and slip distance, and also requires the construction of a reliable wear calculation model, which is affected by the combined action of multiple wear mechanisms. In order to deeply understand tooth surface wear and build a widely applicable and high-precision prediction model to quantify its specific impact on transmission performance, it depends on accurate wear calculation models and cutting-edge experimental testing technology.

[0004] However, gear wear testing is not only time-consuming and labor-intensive, but also highly dependent on professional equipment and precision measuring tools, which leads to high test costs, long cycles and limited application scope. In addition, many wear and tear methods are currently limited to a certain type of gear, with a small scope of application. In addition, in the pre-processing stage of finite element simulation, the construction of gear pair models is particularly complex. Whenever the shaping parameters need to be updated, the gear pair must be reassembled and the cumbersome pre-processing process must be repeated. This process is not only time-consuming and lengthy, but also difficult to implement process-based operations, which greatly reduces the simulation efficiency and increases the time cost.

[0005] Therefore, there is an urgent need to explore a new method that can quickly and accurately perform quantitative calculations on the wear of high-performance gears. Summary of the invention

[0006] The purpose of the present invention is to provide a gear double-sided wear method based on the secondary development of the UMESHMOTION subroutine in ABAQUS to solve the problems existing in the prior art.

[0007] The technical solution adopted to achieve the purpose of the present invention is as follows: a gear double-sided wear method based on the secondary development of the UMESHMOTION subroutine of ABAQUS includes the following steps:

[0008] 1) Establish the geometric model of the gear pair and import it into ABAQUS simulation software.

[0009] 2) Complete the pre-processing settings of the gear pair model through ABAQUS simulation software.

[0010] 2-1) Define the material properties of the gear pair model using ABAQUS simulation software.

[0011] 2-2) Establish assembly and contact relationships through the motion characteristics of the gear pair model.

[0012] 2-3) Create analysis steps and related output variables through ABAQUS simulation software.

[0013] 2-4) Update the grid through adaptive grid technology.

[0014] 2-5) Set loads and constraints according to the actual working conditions of the gear pair.

[0015] 2-6) Use ABAQUS simulation software to mesh the gear pair model.

[0016] 3) The first time you submit a job, the gears will go through a complete meshing process, and the subroutine UMESHMOTION will be used to extract and store the following two contents:

[0017] a) Extract the contact stress of the adaptive area of ​​the intermediate gear pair at each moment.

[0018] b) Extract the relative slip distance of the adaptive area of ​​the intermediate gear pair at each moment.

[0019] 4) Submit the job for the second time, and use the subroutine UMESHMOTION to extract the contact stress and relative slip distance of the gear pair in the first cycle of step 3), perform gear pair wear simulation based on the wear model, and store the wear amount, contact stress and slip distance of each node.

[0020] 5) Submit the job later, update the gear morphology according to the wear amount, and store the calculated wear amount, contact stress and slip distance.

[0021] 6) Repeatedly submit the job until the gear fails or the current wear reaches the given wear amount.

[0022] Furthermore, in steps 2-3), three analysis steps need to be created, and the solution time and incremental step need to be set. Among them, in time step 1, the gear morphology is updated according to the gear wear through mesh adaptation technology. In time step 2, the contact stress and relative slip distance of the gear pair in the previous cycle are extracted with the help of the subroutine UMESHMOTION, and the wear increment of the gear is calculated based on the Archard wear model or the energy dissipation model, and the wear of the cycle between them is accumulated into the total wear. In time step 3, the intermediate gear pair will be fully meshed, and the contact stress and slip distance of each node will be stored.

[0023] Furthermore, in step 2-3), a set needs to be created for the gear pair and the gear pair contact area, and the output variables are selected as contact pressure, stress, strain and displacement.

[0024] Furthermore, in step 2-4), the gear contact area is selected as the adaptive mesh area.

[0025] Furthermore, in step 2-5), the load is set as a moment, and the constraints include translations in three directions and rotations except the axial direction.

[0026] Furthermore, in step 3), the UMESHMOTION subroutine is called to accurately store the contact stress and sliding distance of each node, and the UMESHMOTION subroutine variables should include the wear coefficient and the jump coefficient and the compiled UMESHMOTION subroutine is submitted to the Job for the first time.

[0027] Furthermore, in step 5), the wear amount of each node is extracted cyclically by means of the subroutine UMESHMOTION, and the position of each node is moved in the adaptive mesh area, and the contact stress, sliding distance and calculated wear amount of each node during the meshing process are stored.

[0028] The technical effects of the present invention are unquestionable: it can quickly and effectively perform accurate quantitative calculations on the wear of high-performance gears of different gear types, loads, materials and working conditions; it can process gear wear in a streamlined manner to avoid repeated finite element pre-processing steps, greatly improving the efficiency of finite element simulation while ensuring calculation accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 It is the overall simulation flow chart;

[0030] Figure 2 Select the area for adaptive meshing of gear pairs; Figure 2 (a) is the planetary gear adaptive grid adjustment area. Figure 2 (b) is the adaptive mesh adjustment area of ​​the inner gear ring;

[0031] Figure 3 is the boundary condition and mesh size of the gear pair;

[0032] Figure 4 This is the result diagram of the slip distance of each node of the gear pair after 5000 cycles; Figure 4 (a) is the result diagram of the inner gear ring slip distance; Figure 4 (b) is the result diagram of planetary gear slip distance;

[0033] Figure 5 This is the maximum contact stress result diagram of each node of the gear pair after 5000 cycles; Figure 5 (a) is the contact stress result diagram of the inner gear ring; Figure 5 (b) is the contact stress result diagram of the planetary gear;

[0034] Figure 6 The wear depth results of the planetary gear and the inner ring gear for different cycles of the gear pair are shown in the figure; Figure 6 (a) is the result diagram of the wear depth of the inner gear ring; Figure 6 (b) is the result diagram of planetary gear wear depth. DETAILED DESCRIPTION

[0035] The present invention is further described below in conjunction with the embodiments, but it should not be understood that the above subject matter of the present invention is limited to the following embodiments. Without departing from the above technical ideas of the present invention, various substitutions and changes are made according to the common technical knowledge and customary means in the art, which should all be included in the protection scope of the present invention.

[0036] Embodiment 1:

[0037] See also Figure 1 This embodiment provides a gear double-sided wear method based on the secondary development of the UMESHMOTION subroutine in ABAQUS, including the following steps:

[0038] 1) Create a geometric model of the gear pair and import it into the ABAQUS simulation software. In actual production, to create a 3D or 2D model of the gear pair, you can use 3D modeling software such as KISSsoft, Romax, MASTA or Solidworks to accurately model the gear pair according to the design specifications and basic processing parameters of the gear. In this way, the required 3D or 2D model of the gear pair can be generated. In order to facilitate the subsequent import of these models into the finite element analysis software, it is recommended to save them in one of the following file formats: .x_t, .igs or .stp.

[0039] 2) Complete the pre-processing settings of the gear pair model through ABAQUS simulation software.

[0040] 2-1) Define the material properties of the gear pair model using ABAQUS simulation software.

[0041] 2-2) The assembly and contact relationships are established through the kinematic characteristics of the gear pair model. The material properties include Young's modulus and Poisson's ratio, and the units are mm-N-MPa.

[0042] 2-3) Create analysis steps and related output variables through ABAQUS simulation software.

[0043] 2-4) Update the grid through adaptive grid technology.

[0044] 2-5) Set loads and constraints according to the actual working conditions of the gear pair.

[0045] 2-6) Use ABAQUS simulation software to mesh the gear pair model.

[0046] 3) The first time you submit a job, the gears will go through a complete meshing process, and the subroutine UMESHMOTION will be used to extract and store the following two contents:

[0047] a) Extract the contact stress of the adaptive area of ​​the intermediate gear pair at each moment.

[0048] b) Extract the relative slip distance of the adaptive area of ​​the intermediate gear pair at each moment.

[0049] 4) Submit the job for the second time, extract the contact stress and relative slip distance of the gear pair in the first cycle of step 3) with the help of the subroutine UMESHMOTION, perform gear pair wear simulation based on a reasonable wear model, and store the wear amount, contact stress and slip distance of each node. Convert the model formula into the calculation formula in the UMESHMOTION subroutine. The widely used and recognized wear models used in this embodiment are the Archard wear model and the energy dissipation model.

[0050] Archard wear model:

[0051]

[0052] In the formula, ΔN is the wear jump coefficient, k is the wear coefficient, Δh n is the wear increment of the nth cycle, P i and S i They represent the contact pressure and relative sliding distance of the node at the end of the i-th incremental step, respectively. The superscripts 1 and 2 represent two orthogonal sliding directions. i-1 and S i-1 They respectively represent the contact pressure and relative sliding distance of the node at the end of the i-1th incremental step.

[0053] Energy dissipation model:

[0054]

[0055] In the formula, a e is the friction dissipation energy coefficient, and f is the friction coefficient.

[0056] Wear coefficient k and friction dissipation energy coefficient a e , usually using experimental methods, such as ball-disc, pin-disc, etc., to prepare experimental samples with the same process as the gear material, test the friction coefficient and wear volume under different loads, lubrication conditions, speeds and other test conditions, and statistically calculate the corresponding wear degree under gear working conditions, so as to calculate the wear coefficient k and friction dissipation energy coefficient a e .

[0057] 5) Submit the job later, update the gear morphology according to the wear amount, and store the calculated wear amount, contact stress and slip distance.

[0058] 6) Repeatedly submit the job until the gear fails or the current wear reaches the given wear amount.

[0059] Embodiment 2:

[0060] The main contents of this embodiment are the same as those of embodiment 1, wherein, in steps 2-3), three analysis steps need to be created, and the solution time and increment step need to be set. In time step 1, the gear morphology is updated according to the gear wear amount by using the mesh adaptive technology. In time step 2, the contact stress and relative slip distance of the gear pair in the previous cycle are extracted with the help of the subroutine UMESHMOTION, and the wear increment of the gear is calculated based on the wear model such as the Archard wear model or the energy dissipation model, and the wear of the cycles between them is accumulated into the total wear amount. In time step 3, the intermediate gear pair is fully meshed, and the contact stress and slip distance of each node are stored.

[0061] Embodiment 3:

[0062] The main contents of this embodiment are the same as those of Embodiment 1 or 2, wherein in step 2-3), a set needs to be created for the gear pair and the gear pair contact area, and the output variables are selected as contact pressure, stress, strain and displacement.

[0063] Embodiment 4:

[0064] The main content of this embodiment is the same as any one of Embodiments 1 to 3, wherein in step 2-4), the gear contact area is selected as the adaptive grid area.

[0065] Embodiment 5:

[0066] The main contents of this embodiment are the same as any one of embodiments 1 to 4, wherein the load in step 2-5) is set as a moment, and the constraints include translations in three directions and rotations except the axial direction.

[0067] Embodiment 6:

[0068] The main contents of this embodiment are the same as any one of embodiments 1 to 5, wherein in step 3), the UMESHMOTION subroutine is called to accurately store the contact stress and sliding distance of each node, and the UMESHMOTION subroutine variables should include the wear coefficient and the jump coefficient, and the compiled UMESHMOTION subroutine is submitted to the Job for the first time.

[0069] Embodiment 7:

[0070] The main contents of this embodiment are the same as any one of embodiments 1 to 6, wherein in step 5), the wear amount of each node is extracted cyclically by using the subroutine UMESHMOTION, and the position of each node is moved in the adaptive mesh area. The contact stress, sliding distance and calculated wear amount of each node during the meshing process are stored.

[0071] Embodiment 8:

[0072] The main contents of this embodiment are the same as any one of the embodiments 1, wherein, see Figure 2 to Figure 6 The gear pair in this embodiment is a planetary gear and an inner gear ring. This embodiment is used to simulate the double-sided wear of the gear.

[0073] In step 2-2), the assembly drawing is completed according to the characteristic that the gear pair is tangent to the pitch circle. Since the driven wheel is worn while the driving wheel is worn, the contact surface of the driving wheel should be set as both the master surface and the slave surface when setting the contact surface. The contact surface of the driven wheel should be set as both the master surface and the slave surface. Therefore, when one gear pair contacts another gear pair, two contact pairs should be set, and the contact mode and friction coefficient should be set at the same time.

[0074] In step 2-4), the contact area of ​​the gear pair is divided according to a certain depth, and the area is selected as the adaptive mesh area (ie, the gear wear area), and the gear pair contact surface is the adaptive mesh node movement area.

[0075] In step 2-5), the load application principle is:

[0076] a) Establish a coupling point on the inner surface of the driving wheel and apply a torque load to the node to simulate the actual load transfer.

[0077] b) Establish a coupling point on the inner annular surface of the driven wheel and impose a displacement constraint on the node to ensure the normal rotation of the subsequent gears.

[0078] Principles for imposing constraints:

[0079] a) The coupling point on the inner ring surface of the driving wheel restricts all degrees of freedom except the axial direction, that is, it can only rotate around the axis.

[0080] b) The coupling point on the inner annular surface of the driven wheel restricts all degrees of freedom except the axial direction, that is, it can only rotate around the axis.

[0081] In step 2-6), the contact area of ​​the gear pair is divided into fine grids. In order to ensure the continuity of the contact pressure image, the grid size ratio in the tooth diameter and tooth width direction is set to be approximately equal to the ratio of the tooth diameter to the tooth width, and the remaining area is divided into coarse grids.

[0082] The finite element simulation of the shifted spur gear pair is carried out, and the specific parameters of the gear pair are shown in Table 1. This example uses the UMESHMOTION subroutine secondary development of ABAQUS to calculate the gear wear based on the wear model, which specifically includes the following steps:

[0083] Table 1 Basic parameters of gear pairs

[0084]

[0085] 1) Establish a two-dimensional model of the gear pair. Enter the basic parameters in Table 1 in KISSsoft to generate a two-dimensional model of the gear pair. Save the file in .x_t format and import it into ABAQUS.

[0086] 2) Complete the pre-processing settings of the gear pair model through ABAQUS simulation software;

[0087] 2-1) Define the material properties of the gear pair model using ABAQUS simulation software; among them, Young's modulus is set to 206000MPa and Poisson's ratio is set to 0.3.

[0088] 2-2) The assembly and contact relationship is established through the motion characteristics of the gear pair model; wherein, the assembly drawing is completed according to the characteristic of the gear pair being tangent to the pitch circle. Since the driven wheel is worn while the driving wheel is worn, the contact surface of the driving wheel should be set as both the master surface and the slave surface when the contact surface is set. The contact surface of the driven wheel should be set as both the master surface and the slave surface. Therefore, when one gear pair contacts another gear pair, two contact pairs should be set, and the contact mode and friction coefficient should be set at the same time.

[0089] 2-3) Create 3 analysis steps and the required output variables, and turn on large deformation for all of them; set the time of the first and second analysis steps to 1s, and the time of the third analysis step to 150s. The specific settings are:

[0090] Step-1: The incremental step is set to 1, and the minimum increment is 1e-15. The purpose is to first give the inner gear ring a small angle so that the model is in contact and the planetary gear does not move. In the subroutine UMESHMOTION, the contact pressure and two sliding distances of each node are read. According to formula (1), the increment of the wear depth of the node in the current cycle is calculated, and the accumulated wear depth and the wear of the intermediate teeth are updated.

[0091] Step-2: The incremental step is set to 1, and the minimum increment is 1e-15. The purpose is to add torque to the inner ring gear. The planetary gear remains unchanged. In the subroutine UMESHMOTION, the accumulated wear depth of each node is read and the wear of the other four teeth is updated.

[0092] Step-3: The incremental step is set to 150, the minimum increment is 1e-9, the rotational freedom of the inner ring gear is released, and the planetary gear is given a rotation angle to simulate the complete meshing process of the intermediate gear in the subroutine UMESHMOTION.

[0093] 2-4) Update the gear morphology according to the gear wear amount by mesh adaptive technology; wherein, the contact area of ​​the gear pair is divided according to a certain depth, and the area is selected as the adaptive mesh area (i.e., the gear wear area), and the gear pair contact surface is the adaptive mesh node movement area, and different adaptive mesh areas are set in different analysis steps, in analysis step 1, only the middle tooth contact area is set as the adaptive mesh area, in analysis step 2, the remaining gear tooth contact areas are set as the adaptive mesh areas, and in analysis step 3, the middle tooth contact area is set as the adaptive mesh area. The total adaptive mesh area is as follows: Figure 4 shown.

[0094] 2-5) Set loads and constraints according to the actual working conditions of the gear pair: A coupling point is established on the inner ring surface of the inner ring wheel, and a torque load of 27555.5 N·mm is applied to the node in the second analysis step.

[0095] Principles for imposing constraints:

[0096] a) For the internal gear ring, all degrees of freedom are constrained in the initial analysis step and passed to the first analysis step. In the second analysis step, a rotational displacement constraint of 0.002 rad is applied around the axial direction, and the rotational displacement degrees of freedom around the axial direction are released in the subsequent analysis steps;

[0097] b) For the planetary gear, all degrees of freedom are constrained in the initial analysis step, and then transferred to the second analysis step. In the third analysis step, a displacement constraint of 0.675 rad is applied around the axial direction.

[0098] Through the above settings, it is ensured that the intermediate gear pair undergoes a complete meshing process during the simulated transmission process.

[0099] 2-6) The gear pair model is meshed by ABAQUS simulation software; the contact area of ​​the gear pair is finely meshed. In order to ensure the continuity of the contact pressure image, the mesh size ratio of the tooth diameter and tooth width is set to be approximately equal to the ratio of the tooth diameter to the tooth width. The planetary gear tooth diameter is 20.372mm and the tooth width is 20mm, so the mesh size is approximately 1:1, the mesh size is 50μm*50μm, the non-contact area is coarsely meshed, the global seed is set to 0.5, the gear boundary adjustment and mesh size are as follows Figure 3 shown.

[0100] 3) Submit the job for the first time, let the gears go through a complete meshing process, and use the subroutine UMESHMOTION to extract and store the following two contents;

[0101] 3-1) Extract the contact stress of the adaptive area of ​​the intermediate gear pair at each moment;

[0102] 3-2) Extract the relative slip distance of the adaptive area of ​​the intermediate gear pair at each moment; perform theoretical derivation of tooth profile modification, and apply its derivation formula to the subroutine UMESHMOTION. The results of the slip distance and the maximum contact pressure of each node during the 5000-cycle meshing process of the gear are as follows: Figure 4 and Figure 5 As shown, the X-axis is specific along the tooth profile direction, the 0 near the inner gear ring represents the tooth top and the 80 near the inner gear ring represents the tooth root; in the planetary gear, 0 represents the tooth root and 100 represents the tooth top;

[0103] 4) Submit the job for the second time and use the subroutine UMESHMOTION to extract the contact stress and relative slip distance of the gear pair in step 3) of the first cycle. Based on wear models such as the Archard wear model or the energy dissipation model, perform gear pair wear simulation and store the wear amount, contact stress and slip distance of each node.

[0104] 5) Submit the job later, update the gear morphology according to the wear amount, and store the calculated wear amount, contact stress and slip distance. Use the subroutine UMESHMOTION to extract the wear amount of each node, and move the position of each node in the adaptive mesh area. And store the contact stress, slip distance and calculated wear amount of each node during the meshing process. The contact stress and slip distance based on which the wear amount is calculated are stored in the previous cycle, so the wear of the gear pair in the previous step is calculated, and the wear depth of the gear at different cycles is inferred. Figure 6 As shown, the X-axis is the specific direction along the tooth profile, the area near 0 in the inner gear ring represents the tooth top and the area near 80 represents the tooth root; in the planetary gear, 0 represents the tooth root and about 100 represents the tooth top.

[0105] In addition, changing the definition of gear wear coefficient and corresponding material properties in ABAQUS can realize quantitative calculation of wear of different gears and different gear materials.

[0106] In summary, we can combine wear models such as the Archard wear model or the energy dissipation model with the gear contact model based on finite elements, which can accurately calculate the gear wear quantitatively, and provide a simulation method that can quickly and effectively perform accurate quantitative calculations on high-performance gear wear of different gear types, loads, materials, and working conditions. The gear wear process is programmed based on the UMESHMOTION subroutine, thereby realizing the process processing of gear wear in finite element analysis, which not only ensures the calculation accuracy, but also significantly simplifies the pre-processing work of finite element analysis. This method is not only applicable to the situation in this example, but also has the potential for promotion. It can be applied to the simulation analysis of other mechanical structures. At the same time, a variety of simulation software can also be used for corresponding finite element analysis.

Claims

1. The gear double-sided wear method based on the secondary development of UMESHMOTION subroutine in ABAQUS is characterized by: The following steps are involved: 1) Establish the geometric model of the gear pair and import it into ABAQUS simulation software; 2) Complete the pre-processing settings of the gear pair model through ABAQUS simulation software; 2-1) Define the material properties of the gear pair model using ABAQUS simulation software; 2-2) Establish assembly and contact relationships through the kinematic characteristics of the gear pair model; 2-3) Create analysis steps and related output variables through ABAQUS simulation software; 2-4) Updating the grid through adaptive grid technology; 2-5) Set loads and constraints according to the actual working conditions of the gear pair; 2-6) Mesh the gear pair model using ABAQUS simulation software; 3) The first time you submit a job, the gears will go through a complete meshing process, and the subroutine UMESHMOTION will be used to extract and store the following two contents: a) Extract the contact stress of the adaptive area of ​​the intermediate gear pair at each moment; b) extracting the relative slip distance of the adaptive area of ​​the intermediate gear pair at each moment; 4) Submit the job for the second time, extract the contact stress and relative slip distance of the gear pair in the first cycle of step 3) with the help of the subroutine UMESHMOTION, perform gear pair wear simulation based on the wear model, and store the wear amount, contact stress and slip distance of each node; 5) Submit the job later, update the gear morphology according to the wear amount, and store the calculated wear amount, contact stress and slip distance; 6) Repeatedly submit the job until the gear fails or the current wear reaches the given wear amount.

2. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In steps 2-3), three analysis steps need to be created, and the solution time and incremental step need to be set; in which, in time step 1, the gear morphology is updated according to the gear wear through mesh adaptation technology; in time step 2, the contact stress and relative slip distance of the gear pair in the previous cycle are extracted with the help of subroutine UMESHMOTION, and the gear wear increment is calculated based on the Archard wear model or energy dissipation model, and the wear of the cycles between them is accumulated into the total wear; in time step 3, the intermediate gear pair will be fully meshed, and the contact stress and slip distance of each node will be stored.

3. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In step 2-3), it is necessary to create a collection for the gear pair and the gear pair contact area, and select the output variables as contact pressure, stress, strain and displacement.

4. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In step 2-4), the gear contact area is selected as the adaptive mesh area.

5. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In step 2-5), the load is set as moment, and the constraints include translation in three directions and rotation except the axial direction.

6. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In step 3), call the UMESHMOTION subroutine to accurately store the contact stress and sliding distance of each node, and the UMESHMOTION subroutine variables should include the wear coefficient and jump coefficient, and submit the compiled UMESHMOTION subroutine to the Job for the first time.

7. The gear double-sided wear method based on the secondary development UMESHMOTION subroutine of ABAQUS according to claim 1 is characterized in that: In step 5), the wear amount of each node is extracted by the loop with the help of the subroutine UMESHMOTION, and the position of each node is moved in the adaptive mesh area; the contact stress, sliding distance and calculated wear amount of each node during the meshing process are stored.

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