Gear double-face wear method based on secondary development of umeshmotion subprogram of abaqus

Abstract

The application provides a gear double-face wear method based on the secondary development of the UMESHMOTION subprogram of ABAQUS. The method combines the wear model such as the Archard wear model or the energy dissipation model with the gear contact model based on the finite element, can accurately quantitatively calculate the gear wear, provides a simulation method which can quickly and effectively accurately quantitatively calculate the wear of different gear types, loads, materials and working conditions of high-performance gears, and realizes the gear pair wear simulation by moving the grid nodes of the gear pair according to the wear amount of the contact area of the gear pair based on the wear model such as the Archard wear model or the energy dissipation model through the subprogram UMESHMOTION. Through the method, the wear of high-performance gears can be accurately quantitatively calculated and processed in a flow, the repeated finite element preprocessing steps are avoided, the finite element simulation efficiency is greatly improved, and the time cost is reduced.

Description

Technical Field

[0001] The present 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 in ABAQUS. Background Art

[0002] Tooth surface wear is one of the core causes of impaired gear service performance and loss of tooth surface integrity. It manifests itself as a dynamic cumulative effect of gradual damage and shedding of tooth profile material, which lasts throughout 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 triggering internal excitation. Slight tooth surface wear can change the contact characteristics during gear meshing, reduce the accuracy of the transmission system, and lead to increased transmission errors. 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, accurate quantitative calculation of high-performance gear wear is crucial in engineering practice. However, this task is extremely complex, requiring precise measurement of tooth contact stress and slip distance, as well as the development of reliable wear calculation models, all of which are influenced by the combined effects of multiple wear mechanisms. A deeper understanding of tooth wear and the development of broadly applicable, highly accurate prediction models to quantify its specific impact on transmission performance require precise wear calculation models and cutting-edge experimental testing techniques.

[0004] However, gear wear testing is not only time-consuming and labor-intensive, but also highly dependent on specialized equipment and precision measuring tools. This leads to high test costs, long cycles, and limited application scope. Furthermore, many wear and tear methods are currently limited to a specific type of gear, resulting in a small scope of application. Furthermore, in the pre-processing stage of finite element simulation, the construction of gear pair models is particularly complex. Whenever the modification parameters need to be updated, the gear pair must be reassembled and the tedious pre-processing process repeated. This process is not only time-consuming and lengthy, but also difficult to implement in a streamlined manner, greatly reducing simulation efficiency and increasing time costs.

[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 in 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) When submitting the job for the first time, the gears undergo a complete meshing process and the subroutine UMESHMOTION extracts and stores the following two contents:

[0017] a) Extract the contact stress of the adaptive region 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 topography based on 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] Further, 3 analysis steps need to be created in step 2-3), and the solving time and increment step are set. Among them, in time step 1, the gear profile is updated according to the gear wear amount by means of the mesh self-adapting technology. In time step 2, the contact stress and relative slip distance of the gear pair in the previous cycle are extracted by means of the subprogram UMESHMOTION, and the wear increment of the gear is calculated based on the Archard wear model or the energy dissipation model, and the wear accumulated between the cycles is accumulated into the total wear amount. In time step 3, the intermediate gear pair will be completely engaged, and the contact stress and slip distance of each node are stored.

[0023] Further, in step 2-3), the gear pair and the contact area of the gear pair need to be created, and the output variables are selected as the contact pressure, stress, strain and displacement.

[0024] Further, in step 2-4), the gear contact area is selected as the self-adapting mesh area.

[0025] Further, in step 2-5), the load is set as the torque, and the constraints include three directions of translation and rotation except the axial direction.

[0026] Further, in step 3), the UMESHMOTION subprogram is called to accurately store the contact stress and slip distance of each node, and the UMESHMOTION subprogram variable should include the wear coefficient and the jump coefficient, and the prepared UMESHMOTION subprogram is submitted to the Job for the first time.

[0027] Further, in step 5), the wear amount of each node is extracted by means of the subprogram UMESHMOTION, and the position of each node in the self-adapting mesh area is moved. The contact stress, slip distance and calculated wear amount of each node in the meshing process are stored.

[0028] The technical effect of the present application is self-evident: it can quickly and effectively perform accurate quantitative calculation on high-performance gear wear of different gear types, loads, materials and working conditions; the gear wear is processed in a flow, avoiding repeated finite element preprocessing steps, greatly improving the finite element simulation efficiency while ensuring the calculation accuracy. BRIEF DESCRIPTION OF DRAWINGS

[0029] Figure 1 It is the overall simulation flowchart;

[0030] Figure 2 It is the gear pair self-adapting mesh selection area; Figure 2 (a) is the planetary gear self-adapting mesh adjustment area, Figure 2 (b) is the inner gear ring self-adapting mesh adjustment area;

[0031] Figure 3 It 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 graph shows the wear depth of the planetary gear and the inner ring gear at different cycle times of the gear pair; 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 will be further described below with reference to the following examples, but it should not be understood that the scope of the present invention is limited to the following examples. Without departing from the above technical ideas of the present invention, various substitutions and modifications can be made according to common technical knowledge and customary means in the art, and all should be included in the scope of protection of the present invention.

[0036] Example 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 ABAQUS simulation software. In actual production, a 3D or 2D model of the gear pair can be created using 3D modeling software such as KISSsoft, Romax, MASTA, or SolidWorks. Accurately model the gear pair based on the gear design specifications and basic machining parameters. This will generate the desired 3D or 2D model of the gear pair. To facilitate subsequent import into finite element analysis software, it is recommended to save these models 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) Establish assembly and contact relationships based on the kinematic characteristics of the gear pair model. Material properties include Young's modulus and Poisson's ratio, with units in 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) When submitting the job for the first time, the gears undergo a complete meshing process and the subroutine UMESHMOTION extracts and stores the following two contents:

[0047] a) Extract the contact stress of the adaptive region 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 a second time. Using the UMESHMOTION subroutine, extract the contact stress and relative slip distance of the gear pair from the first cycle of step 3. Based on a reasonable wear model, perform a gear pair wear simulation and store the wear, contact stress, and slip distance at each node. Convert the model formula into the calculation formula within the UMESHMOTION subroutine. This example uses the widely used and recognized wear models: the Archard wear model and the energy dissipation model.

[0050] Archard wear model:

[0051]

[0052] Where 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 are two orthogonal sliding directions. i-1 and S i-1 They represent the contact pressure and relative sliding distance of the node at the end of the i-1th incremental step respectively.

[0053] Energy dissipation model:

[0054]

[0055] Where 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 adopt experimental methods, such as ball-on-disc, pin-on-disc, etc., to prepare experimental samples with the same process as the gear material, test the friction coefficient and wear volume under different load, lubrication state, speed and other test conditions, and statistically calculate the corresponding wear degree under the gear working condition, so as to calculate the wear coefficient k and friction dissipation energy coefficient a e .

[0057] 5) Submit the job later, update the gear topography based on 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] Example 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 incremental step need to be set. In time step 1, the gear morphology is updated according to the gear wear amount 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 gear wear increment is calculated based on a wear model such as the Archard wear model or the energy dissipation model, and the wear of the intermediate cycles 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] Example 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] Example 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] Example 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 translation in three directions and rotation except the axial direction.

[0067] Example 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] Example 7:

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

[0071] Example 8:

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

[0073] In step 2-2), the assembly drawing is completed based on the characteristic that the gear pairs are tangent to the pitch circle. Since the driving wheel wears at the same time as the driven wheel, the contact surface of the driving wheel must be set as both the master surface and the slave surface when setting the contact surface. The contact surface of the driven wheel must also be set as both the master surface and the slave surface. Therefore, when a gear pair contacts a gear pair, two contact pairs must be set, and the contact mode and friction coefficient must 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 this 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.

[0075] In steps 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 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. To ensure the continuity of the contact pressure image, the grid size ratio in the tooth diameter and tooth width directions is set to be approximately equal to the ratio of the tooth diameter to the tooth width. The remaining areas are divided into coarse grids.

[0082] Finite element simulation is performed on the modified spur gear pair, where the specific parameters of the gear pair are shown in Table 1. This example uses the ABAQUS secondary development UMESHMOTION subroutine to calculate 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 using ABAQUS simulation software;

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

[0088] 2-2) The assembly and contact relationships are established through the motion characteristics of the gear pair model; among them, the assembly drawing is completed according to the characteristic that the gear pair is tangent to the pitch circle. Since the driving wheel wears at the same time as the driven wheel, the contact surface of the driving wheel must be set as both the master surface and the slave surface when setting the contact surface. The contact surface of the driven wheel must also be set as both the master surface and the slave surface. Therefore, when one gear pair contacts another, two contact pairs must be set, and the contact mode and friction coefficient must be set at the same time.

[0089] 2-3) Create three analysis steps and the required output variables, turning on large deformation for all. Set the first and second analysis steps to 1 second, and the third to 150 seconds. 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 of each node and the two sliding distances are read. According to formula (1), the increment of the wear depth of the node in the current cycle is calculated, the cumulative wear depth is updated, and the wear of the middle tooth is 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 through mesh adaptive technology; wherein, the contact area of ​​the gear pair is divided according to a certain depth, and this 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. In different analysis steps, different adaptive mesh areas are set. 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 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 based on the actual working conditions of the gear pair: Establish a coupling point on the inner annular surface of the inner ring gear, and apply a moment load of 27555.5 N·mm to this node in the second analysis step.

[0095] Principles for imposing constraints:

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

[0097] b) For the planetary gear, constrain all degrees of freedom in the initial analysis step, transfer to the second analysis step, and apply a displacement constraint of 0.675 rad around the axial direction in the third analysis step;

[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 using ABAQUS simulation software; the contact area of ​​the gear pair is finely meshed. To ensure the continuity of the contact pressure image, the mesh size ratio of the tooth diameter to the 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, and the mesh size is 50μm*50μm. The non-contact area is coarsely meshed, and the global seed is set to 0.5. The gear boundary adjustment and mesh size are as follows: Figure 3 shown.

[0100] 3) When submitting the job for the first time, the gears undergo a complete meshing process and the subroutine UMESHMOTION is used to extract and store the following two contents:

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

[0102] 3-2) Extract the relative slip distance of the adaptive region of the intermediate gear pair at each moment; perform theoretical derivation of tooth profile modification, and apply the 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 are as follows: Figure 4 and Figure 5 As shown, the X-axis is specific along the tooth profile direction, the area around 0 in the inner gear represents the tooth top and the area around 80 represents the tooth root; in the planetary gear, 0 represents the tooth root and around 100 represents the tooth top;

[0103] 4) Submit the job for the second time. Use the subroutine UMESHMOTION to extract the contact stress and relative slip distance of the gear pair in the first cycle of step 3). 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 based on 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 calculated in the same way. Figure 6 As shown, the X-axis is along the tooth profile direction, and the number near 0 in the inner gear ring represents the tooth top and the number near 80 represents the tooth root; in the planetary gear, 0 represents the tooth root and around 100 represents the tooth top.

[0105] In addition, changing the definition of gear wear coefficient and corresponding material properties in ABAQUS can realize the 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 a finite element-based gear contact model to accurately and quantitatively calculate gear wear. This provides a simulation method that can quickly and effectively perform precise quantitative calculations of high-performance gear wear for different gear types, loads, materials, and operating conditions. By programming the gear wear process based on the UMESHMOTION subroutine, we can streamline the processing of gear wear in finite element analysis, ensuring calculation accuracy while significantly simplifying the pre-processing of finite element analysis. This method is not only applicable to the situation in this example but also has the potential for generalization and can be applied to the simulation analysis of other mechanical structures. Furthermore, it can also be used to perform corresponding finite element analysis using a variety of simulation software.

Claims

1. The gear double-sided wear method based on the secondary development of the 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 using 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 using ABAQUS simulation software; create three analysis steps and set the solution time and incremental step; create sets for the gear pairs and the gear pair contact areas, and select the output variables as contact pressure, stress, strain, and displacement; wherein, in time step 1, the gear morphology is updated according to the gear wear using 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 gear wear increment is calculated based on the Archard wear model or the energy dissipation model, and the wear of the gear in the previous cycle is accumulated into the total wear; in time step 3, the intermediate gear pair is fully engaged, and the contact stress and slip distance of each node are stored; 2-4) Select the gear contact area as the adaptive mesh area; update the mesh using the adaptive mesh technology; 2-5) Set loads and constraints based on the actual working conditions of the gear pair; the load is set as torque, and the constraints include translation in three directions and rotation except the axial direction; 2-6) Mesh the gear pair model using ABAQUS simulation software; 3) When submitting the job for the first time, the gears undergo a complete meshing process and the subroutine UMESHMOTION extracts and stores the following two contents: a) Extract the contact stress of the adaptive region of the intermediate gear pair at each moment; b) Extract the relative slip distance of the adaptive region of the intermediate gear pair at each moment; 4) Submit the job a second time and use the UMESHMOTION subroutine 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. 5) Subsequent submission of the job updates the gear topography based on the wear amount, and stores 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 ABAQUS secondary development UMESHMOTION subroutine 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.

3. The gear double-sided wear method based on the ABAQUS secondary development UMESHMOTION subroutine according to claim 1 is characterized in that: In step 5), the wear amount of each node is extracted cyclically 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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