Method, system, medium and equipment for constructing dynamic wear model of wedge block type one-way clutch

Abstract

This invention relates to the field of mechanical transmission and friction and wear analysis, and discloses a method, system, medium, and equipment for constructing a dynamic wear model of a wedge-type one-way clutch. The method includes: establishing an analytical model of the dynamic interface force of the wedge, solving for the force and contact area; obtaining the contact pressure distribution, relative sliding velocity, and contact time of the wedge under different working conditions; constructing a wear volume evolution model over time; introducing a wear constitutive equation to establish a quantitative relationship between contact pressure, relative sliding distance, and wear amount; integrating and coupling the wear volume evolution model, the wear constitutive equation, and the dynamic interface force analytical model, correcting the contact friction coefficient and wear coefficient by temperature field factors, and constructing a multi-physics coupling framework; dynamically updating the contact surface geometry based on the wear accumulation results, and recalculating the contact force and wear parameters to form a continuous iterative wear evolution process. This invention can achieve dynamic and continuous prediction of wedge wear, improving the accuracy of wear assessment under complex working conditions.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission and friction and wear analysis technology, and in particular to a method, system, medium and equipment for constructing a dynamic wear model of a wedge-type one-way clutch wedge. Background Technology

[0002] With the development of high-end equipment manufacturing and heavy-duty transmission systems towards higher speeds, heavier loads, and higher reliability, one-way clutches, as key components for achieving unidirectional power transmission and overload protection, are widely used in bridge cranes, construction machinery, mining equipment, and aerospace. Among them, wedge-type one-way clutches have become an important choice for heavy-duty conditions due to their compact structure, high load-bearing capacity, and fast response speed. In actual service, wedge-type one-way clutches are often subjected to complex conditions of frequent engagement and disengagement, impact loads, and slip friction. Under dynamic loads, the contact interface between the wedge and the inner and outer rings is prone to significant contact stress concentration, transient slippage, and frictional heat generation, which in turn leads to surface wear, geometric evolution, and transmission performance degradation. After long-term operation, accumulated wear may lead to problems such as overrunning failure, slippage, or unstable engagement, seriously affecting the safety and service life of the system.

[0003] Existing research is generally based on contact mechanics theory, analyzing the normal force distribution, wedging conditions, and over-critical operating conditions between the wedge and the inner and outer rings. It also incorporates multibody dynamics methods to study the dynamic response characteristics of one-way clutches during starting, braking, and sudden changes in operating conditions. Building upon this foundation, some studies introduce friction models to describe the sliding friction behavior between the wedge and the inner and outer rings, thus assessing the impact of friction on transmission performance. In wear research, existing techniques mostly employ classical wear theory to estimate the wear amount of the wedge or contact pair. Common methods include wear calculations based on the Archard wear model or establishing empirical wear relationships through experimental data. These methods typically perform cumulative wear calculations in the post-processing stage, treating wear as an independent process related to contact pressure and relative slip distance, making it difficult to reflect the feedback influence of changes in contact geometry on the stress state and dynamic characteristics during the wear process.

[0004] Furthermore, while some existing numerical simulation techniques utilize the finite element method to analyze the contact stress and local deformation of the wedge and its inner and outer rings, these methods are mostly based on fixed geometric models, neglecting the evolution of the contact interface caused by wear. Even when wear effects are considered, simplified equivalent wear thickness updates are often used, lacking a continuous description of the wedge wear evolution process under dynamic conditions. Given the strong nonlinear contact and significant wear coupling characteristics exhibited by wedge-type one-way clutches under high-speed, heavy-load, and impact conditions, existing technologies still struggle to achieve unified modeling of wear and dynamic behavior.

[0005] However, the above-mentioned existing technologies have the following defects: (1) The wear modeling is static and it is difficult to reflect the dynamic working conditions. The existing technologies are mostly based on static or quasi-static assumptions to analyze the wear of the wedge block. Usually, the wear amount is used as a post-processing result for cumulative calculation. It fails to fully consider the dynamic response characteristics of the one-way clutch under frequent engagement and disengagement, sudden speed change and impact load, resulting in a deviation between the wear prediction results and the actual working conditions. (2) The wear and dynamic behavior are not sufficiently coupled. The existing methods generally treat the contact force analysis, dynamic response analysis and wear calculation independently, ignoring the reaction effect of the change of wedge block contact geometry on the contact pressure distribution, friction state and system dynamic characteristics during the wear process. It is difficult to describe the intrinsic coupling relationship between wedge block wear and clutch performance degradation. (3) The ability to describe the evolution of the contact interface is limited. In finite element simulation, the existing technologies mostly use fixed geometric models or simplified equivalent wear thickness update methods, which cannot realize the continuous evolution and real-time update of the wear surface. It is difficult to accurately depict the change law of the wedge block and the inner and outer ring contact interface in the dynamic wear process. (4) Insufficient adaptability to complex working conditions. For typical working conditions such as high speed, heavy load and strong impact, existing technologies often use simplified assumptions when dealing with problems such as strong nonlinear contact, transient slip and frictional heat generation. The applicable range of the models is limited and it is difficult to meet the requirements of engineering practice for the accuracy and stability of wear prediction. Summary of the Invention

[0006] To address the aforementioned problems, the present invention aims to provide a method, system, medium, and equipment for constructing a dynamic wear model of a wedge-type one-way clutch wedge. This method enables continuous calculation of wear evolution over time, overcomes the problems of static and discretized wear analysis in existing technologies, and improves the accuracy and reliability of wear prediction results.

[0007] To achieve the above objectives, in a first aspect, the technical solution adopted by the present invention is as follows: a method for constructing a dynamic wear model of a wedge-type one-way clutch, comprising: based on the power transmission path analysis of the wedge-type one-way clutch during the wedging stage, establishing a dynamic interface force analysis model of the wedge, and solving for the force and contact area of ​​the wedge during the wedging tightening stage; according to the force model, obtaining the geometric force of the wedge under different working conditions to obtain the contact pressure distribution, relative slip velocity, and contact time; introducing the contact pressure and slip parameters into the wear volume evolution relationship to construct a wear volume evolution model of wear volume evolution over time; and constructing a wear constitutive equation based on contact mechanics to determine the wedge contact pressure, relative slip distance, and... The quantitative relationship between wear amounts is established; the wear volume evolution model, wear constitutive equation, and dynamic interface force analytical model are integrated and coupled to construct a multi-physics coupling framework for mutual feedback between wear, force, and motion; at the same time, the temperature field factor is introduced to correct the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, so as to realize the multi-physics coupling analysis of temperature field, mechanical field, and wear field; a dynamic wear numerical model is established based on the multi-physics coupling framework to calculate the wear amount, and the contact surface geometric parameters of the wedge are dynamically updated according to the cumulative result of the wear amount, and the contact force and wear parameters are recalculated under the updated geometric parameters to achieve continuous iterative dynamic wear evolution.

[0008] Furthermore, the force model of the wedge includes:

[0009] Based on the clutch structural parameters and wedge angle geometry, a contact mechanics model between the wedge and the inner and outer rings is established. The normal force, friction force and their distribution on the wedge during the engagement stage are calculated, and the actual contact area and equivalent contact area between the wedge and the inner and outer rings are determined.

[0010] Furthermore, a wear volume evolution model is constructed to show the wear volume over time, including: Based on Archard's wear theory, the microscopic contact state of the wedge block and the inner and outer ring interfaces is equivalent to the discrete contact behavior of a micro-protrusion structure. A quantitative relationship between the normal load and the contact area of ​​a single micro-protrusion contact point is established, thus yielding the expression for the volumetric wear amount generated by the combined action of multiple contact points per unit sliding distance: n×(2 / 3)π a ³; The volumetric wear amount expression is n×(2 / 3)π a ³ The area of ​​the contact region is dimensionless to construct a wear volume evolution model characterizing interface wear.

[0011] Furthermore, the wear constitutive equation is a discretized Arcard wear model, used to calculate the local wear depth increment per unit time; The wear constitutive equation is as follows: , In the formula, Δh(x,τ) is the wear depth increment, p(x,τ) is the contact pressure, δ(x,τ) is the relative sliding, and k is the wear coefficient.

[0012] Furthermore, the wear volume evolution model, wear constitutive equation, and dynamic interface force analytical model are integrated and coupled to construct a multiphysics coupling framework with mutual feedback between wear, force, and motion, including: Establish a closed-loop iterative calculation system among the mechanical field, thermal field, and wear field; Among them, the mechanical field is used to determine the initial contact conditions and motion state, and to transmit the contact pressure distribution and relative slip parameters to the wear field; The thermal field calculates the temperature change in the contact area based on the principle of frictional heat generation, and corrects the lubricating oil film state, contact friction coefficient and material wear coefficient according to the temperature change, and feeds the corrected parameters back to the mechanical field and wear field. The wear field calculates the wear depth increment based on the contact pressure and slip parameters transmitted by the mechanical field and the wear coefficient corrected by the thermal field. It also dynamically updates the geometry of the wedge contact surface based on the wear accumulation results and feeds the updated geometry back to the mechanical field to recalculate the contact force state. By coupling data and physical mechanisms between the mechanical field, thermal field and wear field, a multi-physics coupling framework is formed that allows wear-force-motion mutual feedback.

[0013] Furthermore, temperature field factors are introduced to modify the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, including: Considering the influence of frictional heat generation on the state of the lubricating oil film in the contact area, the temperature field distribution at the contact interface is calculated based on the principle of frictional heat generation. The viscosity characteristics and film formation state of the lubricating oil film in the contact area are modified according to the temperature field distribution in order to adjust the contact friction coefficient. A temperature correction factor is introduced to modify the classic Archard wear model, establishing a generalized Archard wear model. The wear coefficient K is defined as a dynamic parameter related to the absolute temperature T: K = f (T); The influence mechanism of temperature gradient on material wear characteristics is quantitatively described by temperature correction factor, so that the wear coefficient exhibits dynamic nonlinear response characteristics with temperature change.

[0014] Furthermore, a dynamic wear numerical model is established based on a multiphysics coupling framework, including: Set the required basic parameters, including time step, total duration and time vector, to provide a time reference for discretization calculation, and set the material physical properties, wedge contact conditions and load parameters; Pre-allocate storage arrays for dynamic variables and set initial values ​​for initial geometry and wear-related parameters; The dynamic behavior of wear is simulated by iterative calculation in the time domain. In each iteration, the calculation of normal load, contact stress, temperature rise model, wear depth and dynamic adjustment of geometric parameters are performed in sequence. Output curves showing how key parameters change over time to illustrate the wear evolution pattern.

[0015] Secondly, the technical solution adopted by this invention is as follows: a dynamic wear model construction system for a wedge-type one-way clutch, comprising: a force model construction unit, which, based on the power transmission path analysis of the wedge-type one-way clutch during the wedging stage, establishes an analytical model of the wedge's interface force and solves for the force and contact area of ​​the wedge during the wedging tightening stage; a wear volume evolution unit, which, according to the force model, obtains the geometric force of the wedge under different working conditions to obtain the contact pressure distribution, relative slip velocity, and contact time; introduces the contact pressure and slip parameters into the wear volume evolution relationship to construct a wear volume evolution model that shows the wear volume evolution over time; and a constitutive equation introduction unit, which constructs a wear constitutive equation based on contact mechanics to determine the wedge contact pressure, relative slip distance, and... The quantitative relationship between wear amounts; the multiphysics coupling unit integrates and couples the wear volume evolution model, wear constitutive equation, and dynamic interface force analytical model to construct a multiphysics coupling framework for mutual feedback between wear, force, and motion; at the same time, the temperature field factor is introduced to correct the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature to realize multiphysics coupling analysis of temperature field, mechanical field, and wear field; the dynamic iterative update unit establishes a dynamic wear numerical model based on the multiphysics coupling framework to calculate the wear amount, dynamically updates the contact surface geometric parameters of the wedge according to the cumulative result of the wear amount, and recalculates the contact force and wear parameters under the updated geometric parameters to realize continuous iterative dynamic wear evolution.

[0016] Thirdly, the technical solution adopted by the present invention is: a computer-readable storage medium for storing one or more programs, wherein the one or more programs include instructions that, when executed by a computing device, cause the computing device to perform any of the methods described above.

[0017] Fourthly, the technical solution adopted by the present invention is: a computing device comprising: one or more processors, a memory, and one or more programs, wherein the one or more programs are stored in the memory and configured to be executed by one or more processors, and the one or more programs include instructions for performing any of the methods described above.

[0018] The present invention has the following advantages due to the adoption of the above technical solutions: 1. This invention enables a dynamic and continuous description of the wedge wear process. Based on the power transmission path and wedge force characteristics during the wedging stage, this invention establishes a wear model and introduces wear calculation into the dynamic analysis process, achieving continuous calculation of wear evolution over time. This overcomes the static and discretized problems of existing wear analysis, improving the accuracy and reliability of wear prediction results.

[0019] 2. This invention enhances the coupling ability between wear and dynamic behavior. By systematically integrating and coupling the wedge force model, the dynamic interface force analytical model, and the wear volume evolution model, the contact geometry changes caused by wedge wear can have a reverse effect on the contact pressure distribution and dynamic response, thereby more accurately reflecting the impact of wedge wear on the degradation of the overrunning clutch transmission performance.

[0020] 3. This invention improves the applicability of wear prediction under complex working conditions. By comprehensively considering different loads, rotational speeds, and wedging states during model construction, and incorporating the influence of temperature on the lubricating oil film state, this invention is applicable to complex working conditions such as high speed, heavy load, and impact, thus expanding the application scope of wear models in practical engineering.

[0021] 4. This invention improves the accuracy of describing the evolution of the contact interface. By dynamically updating the geometry of the wedge contact surface, the real-time evolution of the contact interface during the wear process is realized, avoiding errors caused by a fixed geometric model and making the contact force calculation more consistent with the actual service conditions. Attached Figure Description

[0022] Figure 1 This is a flowchart of the method for constructing a dynamic wear model of a wedge-type one-way clutch according to an embodiment of the present invention; Figure 2 This is a microscopic contact wear model diagram in an embodiment of the present invention; Figure 3 This is a force analysis diagram of the wedge block in the wedge engagement state in an embodiment of the present invention; Figure 4 This is a schematic diagram of multiphysics coupling in an embodiment of the present invention; Figure 5 This is a flowchart of dynamic wear calculation in an embodiment of the present invention. Detailed Implementation

[0023] To address the problems in existing wedge-type one-way clutch wedge wear modeling, such as static wear analysis, insufficient coupling between wear and dynamic behavior, limited ability to describe contact interface evolution, and difficulty in adapting to complex dynamic conditions, this invention proposes a method, system, medium, and equipment for constructing a dynamic wear model of a wedge-type one-way clutch wedge. This invention includes: analyzing the power transmission path of the wedge-type one-way clutch during the wedging stage to solve for the force and contact area of ​​the wedge during the wedging tightening stage, using this as a prerequisite for solving the dynamic wear process; calculating the geometric force of the wedge under different operating conditions based on the wedge force-contact model, using this as input for multi-physics coupling; and systematically integrating and coupling the wear volume evolution model under clutch wedging conditions, the Arcard constitutive equation based on contact mechanics, and the dynamic interface force analytical model, while considering the influence of temperature on the oil film lubrication of the contact area, thus constructing a dynamic numerical model of wedge wear.

[0024] This invention can comprehensively consider the nonlinear contact, frictional slippage, and wear evolution process between the wedge and the inner and outer rings under dynamic load conditions, and realize the continuous calculation of wear amount and real-time update of contact geometry, thereby improving the accuracy and applicability of wedge wear prediction. It provides a reliable theoretical basis and technical means for the structural optimization design, performance degradation analysis, and service life assessment of wedge-type one-way clutches.

[0025] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the described embodiments of the present invention are within the scope of protection of the present invention.

[0026] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0027] In one embodiment of the present invention, a method for constructing a dynamic wear model of a wedge-type one-way clutch is provided, which is a method for constructing a dynamic wear model of the wedge wear behavior of a wedge-type one-way clutch under dynamic load conditions. In this embodiment, the microscopic contact wear analysis model is first used to characterize the microscopic contact state at the interface between the wedge and the inner and outer rings, clarifying the contact pressure distribution, relative slippage, and wear mechanism, providing a basic physical basis for wear calculation. Based on this, a wedge wear contact force analysis model is established. Combining the power transmission characteristics of the wedge engagement stage, the macroscopic force state and contact load of the wedge under different working conditions are solved, linking the microscopic wear mechanism with actual working conditions. Subsequently, a multiphysics coupling model is constructed to uniformly describe the influence of contact mechanics, wear evolution, and temperature on lubrication, achieving mutual coupling and feedback between wear, force, and thermal effects. Finally, based on the above model, the dynamic wear process is solved. By iteratively updating the contact geometry and force state, continuous simulation of the wedge wear evolution over time is achieved, thus fully reflecting the wear evolution law of the wedge-type overrunning clutch under dynamic working conditions.

[0028] Specifically, such as Figure 1 As shown, the method for constructing the dynamic wear model of the wedge block of the wedge-type one-way clutch includes the following steps: 1) Based on the power transmission path analysis of the wedge-type one-way clutch in the wedge engagement stage, establish the state interface force analysis model of the wedge block, and solve the force and contact area of ​​the wedge block in the wedge tightening stage.

[0029] 2) Based on the force model, obtain the geometric force of the wedge under different working conditions to obtain the contact pressure distribution, relative sliding velocity and contact time; introduce the contact pressure and sliding parameters into the wear volume evolution relationship to construct a wear volume evolution model of wear volume evolution with time.

[0030] 3) Construct a wear constitutive equation based on contact mechanics to determine the quantitative relationship between wedge contact pressure, relative slip distance and wear amount.

[0031] 4) Integrate and couple the wear volume evolution model, wear constitutive equation and dynamic interface force analytical model to construct a multi-physics coupling framework for wear-force-motion mutual feedback; at the same time, introduce temperature field factors to correct the contact friction coefficient and wear coefficient, and define the wear coefficient as a dynamic parameter related to absolute temperature, so as to realize multi-physics coupling analysis of temperature field, mechanical field and wear field.

[0032] 5) A dynamic wear numerical model is established based on a multiphysics coupling framework to calculate the wear amount. The contact surface geometric parameters of the wedge are dynamically updated according to the cumulative wear amount, and the contact force and wear parameters are recalculated under the updated geometric parameters to achieve continuous iterative dynamic wear evolution.

[0033] In step 1) above, establishing the force model of the wedge includes: based on the clutch structural parameters and the geometric relationship of the wedge angle, establishing the contact mechanics model between the wedge and the inner and outer rings, calculating the normal force, friction force and their distribution form on the wedge during the wedge engagement stage, and determining the actual contact area and equivalent contact area between the wedge and the inner and outer rings.

[0034] Specifically, during the engagement phase of a wedge-type overrunning clutch, the power transmission path from the driving component to the driven component is analyzed to clarify the motion state and force characteristics of the wedge during the wedging process. Based on the clutch structural parameters and the geometric relationship of the wedge angle, a contact mechanics model between the wedge and the inner and outer rings is established. The normal force, friction force, and their distribution on the wedge during the engagement phase are calculated, and the actual contact area and equivalent contact area between the wedge and the inner and outer rings are determined.

[0035] In this embodiment, during the actual operation of the wedge-type one-way clutch, the contact interface between the wedge and the inner ring does not maintain its ideal initial geometry. Instead, under continuous friction and load, microscopic material removal and morphological evolution occur, causing the contact profile to gradually transform from its initial design state into a complex curved surface with local non-uniformity. This change typically manifests as subtle shifts in geometric parameters such as contact radius, surface inclination angle, and contact length. Although these geometric changes are small in magnitude, the wedge-type one-way clutch relies on the wedge clamping angle for self-locking transmission, making its structure highly sensitive to contact geometry. This means that minute geometric disturbances can be significantly amplified through nonlinear mechanisms: on the one hand, changes in the contact morphology directly cause the actual wedge clamping angle to deviate from the design value, thereby altering the force balance of the wedge and changing the matching state between the normal support force and the frictional force, thus affecting the wedging conditions and transmission stability; on the other hand, the non-uniform evolution of the contact area geometry causes a redistribution of load on the contact interface, transforming the originally relatively uniform contact stress field into a distribution with obvious local concentration characteristics, resulting in a significant increase in peak contact stress. Based on this, according to the wear evolution law, the increase in contact stress will further aggravate the material removal rate in the local area, thus forming a positive feedback coupling process of "contact geometry change - stress concentration - wear aggravation", making the wear exhibit obvious nonlinear acceleration characteristics. Therefore, in this type of clutch, contact geometry is no longer a static parameter that can be simplified, but a key variable that dynamically evolves with the operation process and profoundly affects the mechanical behavior of the system. If the traditional wear model based on the assumption of fixed contact geometry is still used, it is difficult to accurately characterize the dynamic evolution of the wedge angle and the real-time redistribution process of the contact stress field, which leads to a large deviation between the wear prediction results and the actual working conditions. Existing technologies mostly establish wear models for gear pairs or general sliding friction pairs, whose contact geometry changes usually have a relatively slow and approximately linear impact on the system response. However, as a typical self-locking amplification structure, the wedge-type one-way clutch has significant nonlinear sensitivity to small geometric disturbances. Without in-depth analysis of the characteristics of this type of structure, those skilled in the art cannot foresee the necessity and significant role of introducing the dynamic update mechanism of contact geometry into wear modeling for accurately describing its wedging behavior and wear evolution process. Therefore, this invention applies the dynamic update mechanism to the wear modeling of a wedge-type one-way clutch and constructs a corresponding multi-field coupling analysis method.

[0036] In step 2) above, constructing a wear volume evolution model that reflects the wear volume over time includes the following steps: 2.1) Based on Archard's wear theory, the microscopic contact state of the wedge block and the inner and outer ring contact interface is equivalent to the discrete contact behavior of a micro-protrusion structure. A quantitative relationship between the normal load and the contact area of ​​a single micro-protrusion contact point is established, thereby obtaining the expression for the volumetric wear amount generated by the combined action of multiple contact points per unit sliding distance: n×(2 / 3)π a ³.

[0037] 2.2) The volumetric wear amount expression is n×(2 / 3)π a ³ The area of ​​the contact region is dimensionless to construct a wear volume evolution model characterizing interface wear.

[0038] In this embodiment, specifically, as shown in... Figure 2 The diagram shown illustrates a microscopic contact wear model. According to Archard's wear theory, the interaction between two contact surfaces can be equivalent to the discrete contact behavior of a surface micro-protrusion structure. This theory assumes that the micro-protrusion contact region is an ideal circle (radius 1). a Its contact area can be quantified as π. a ², the normal load borne by a single contact point can be expressed as σ s π a ² (wherein) σ s (This refers to the yield strength limit of the material). When the relative sliding displacement between the contact surfaces exceeds 2... a At the critical value, a complete geometric sweeping action will occur between the micro-protrusions. Based on this, the theoretical model simplifies the wear process of a single micro-protrusion into the generation mechanism of hemispherical wear debris, and derives that the volume of a single wear debris is (2 / 3)π. a ³. Therefore, we can obtain the result for a unit sliding distance from... n The volumetric wear caused by the combined action of multiple contact points is expressed as n×(2 / 3)π a ³.

[0039] The normal load borne by a single contact point can be expressed as: σ s π a ², Total normal load F for: (1) In the formula, F The total normal load; n Number of contact points; σ s The yield strength limit of the material; a The radius of the ideal circle for the contact area of ​​the micro-convex body.

[0040] The wear formula can be transformed into: (2) In the formula, V This represents the wear volume of the wedge block; K The wear coefficient; F The total normal load; σ s This represents the yield strength limit of the material.

[0041] The mathematical model established by formula (2) reveals that the wear of the material exhibits a linear positive correlation with the pressure it experiences and the relative sliding distance, while showing a significant negative correlation with the yield strength limit of the material. For the special working conditions of the wedge-type one-way clutch, the wear height of the wedge-raceway pair... h As a key geometric morphology parameter, it is more convenient for engineering measurement and failure assessment. Therefore, by making formula (2) dimensionless (i.e., dividing both sides of the equation by the contact area), A This allows for the construction of an equivalent height model characterizing interface wear, i.e., a wear volume evolution model: (3) In step 2) above, when obtaining the geometric forces of the wedge under different working conditions, the influence of centrifugal force, spring frame force and Coulomb's friction law on the force balance of the wedge is further considered in order to solve the dynamic force state of the wedge under high-speed rotation.

[0042] In this embodiment, specifically, based on the established wedge force and contact model, geometric force calculations are performed on the wedge under different loads, rotational speeds, and wedging states to obtain key parameters such as the normal contact pressure distribution, relative sliding velocity, and contact time at the wedge contact interface. Figure 3 The diagram shown is a force analysis diagram of the wedge block in the wedge engagement state.

[0043] Through equilibrium force analysis, we can obtain: (4) (5) According to Coulomb's law of friction, the following equation can be obtained: (6) (7) The equation for calculating centrifugal force is: (8) From the moment of equilibrium, we can obtain: (9) (10) In the formula, N Bt and N BnThese are the inner ring forces acting on the wedge. x and y Components in direction; N At and N An These are the forces acting on the outer ring of the wedge block. x and y Components in direction; N Ct and N Cn The spring frame acts on the wedge force at... x and y Components in direction; F L It is centrifugal force; μ The coefficient of friction; x This represents the absolute difference between the x-coordinates of different points in the coordinate system. y This represents the absolute difference between the ordinate values ​​of different points in the coordinate system. m s The mass of the clutch; R c This is the distance from the center of rotation of the clutch to the center of mass of the wedge after thermal deformation; n 0 represents the outer ring speed; γ The angle between the center of mass of the connecting wedge and the center line of rotation of the clutch and the vertical direction; M A and M B The torques at points A and B are respectively. y CA Let C be the absolute difference between the ordinates of points A and C. y CB Let C be the absolute difference between the ordinates of points C and B. y AD Let be the absolute difference between the ordinates of points A and D. y BD Let the absolute difference between the ordinates of points B and D be the absolute difference between them. x CA Let C be the absolute difference between the x-coordinates of points A and C. x CB Let C be the absolute difference between the x-coordinates of points C and B. x AD Let A and D be the absolute difference between their x-coordinates. x BD Let B be the absolute difference between the x-coordinates of points B and D. y AB Let A be the absolute difference between the ordinates of points A and B. x AB Let A be the absolute difference between the x-coordinates of points A and B.

[0044] In step 2) above, when constructing the wear volume evolution model, Hertzian contact theory is further introduced to calculate the contact half-width between the wedge and the inner and outer raceways in order to determine the equivalent area of ​​the contact region.

[0045] Specifically, firstly, through multibody dynamics simulation, key physical quantities such as time-varying normal pressure, tangential relative sliding velocity, and sliding distance on the contact interface of the wedge under complex working conditions are extracted; then, these data are used as loads and motion boundary conditions and mapped into a finite element contact analysis coupled with wear models such as Archard, to calculate the local wear depth increment; finally, the geometry and stress distribution of the contact surface are dynamically updated based on the wear amount, and the updated state is fed back to the model for iterative iteration, thereby achieving quantitative prediction of wear volume evolution and interface morphology update.

[0046] The area A of the contact region is calculated as follows: (11) In the formula, b i The Hertz contact half-width between the wedge and the inner raceway. L This is the actual working length of the wedge. v This represents the relative sliding speed between the wedge and the inner raceway.

[0047] In step 3) above, the wear constitutive equation is a discretized Arcard wear model used to calculate the local wear depth increment per unit time. The wear constitutive equation is: (12) In the formula, Δh(x,τ) is the wear depth increment; p(x,τ) is the contact pressure; δ(x,τ) is the relative sliding; and k is the wear coefficient; where the wear coefficient is from the Archard wear model. i =2.75×10⁻⁸MPa -1 ; For time.

[0048] In this embodiment, based on the wear volume evolution model, the Arcard wear constitutive equation based on contact mechanics is introduced to establish a quantitative relationship between the wedge contact pressure, relative slip distance, and material wear coefficient. This constitutive equation enables the calculation of the local wear depth or wear amount of the wedge per unit time.

[0049] In step 4) above, a numerical calculation model for the dynamic wear of the wedge is constructed based on each model. During the calculation process, the geometry of the wedge contact surface is dynamically updated according to the cumulative wear amount, and the contact force and wear parameters are recalculated under the updated geometric conditions, forming a continuous iterative wear evolution process, such as... Figure 4 As shown.

[0050] In this embodiment, the wear volume evolution model, wear constitutive equation and dynamic interface force analytical model are integrated and coupled to construct a multi-physics field coupling framework with mutual feedback between wear, force and motion. Specifically, a closed-loop iterative calculation loop system is established between the mechanical field, the thermal field and the wear field.

[0051] Among them, the mechanical field is used to determine the initial contact conditions and motion state, and to transmit the contact pressure distribution and relative slip parameters to the wear field; The thermal field calculates the temperature change in the contact area based on the principle of frictional heat generation, and corrects the lubricating oil film state, contact friction coefficient and material wear coefficient according to the temperature change, and feeds the corrected parameters back to the mechanical field and wear field. The wear field calculates the wear depth increment based on the contact pressure and slip parameters transmitted by the mechanical field and the wear coefficient corrected by the thermal field. It also dynamically updates the geometry of the wedge contact surface based on the wear accumulation results and feeds the updated geometry back to the mechanical field to recalculate the contact force state. By coupling data and physical mechanisms between the mechanical field, thermal field and wear field, a multi-physics coupling framework is formed that allows wear-force-motion mutual feedback.

[0052] In this embodiment, the wedge wear volume evolution model, the Archard wear constitutive equation, and the dynamic interface force analytical model are systematically integrated and coupled to construct a computational framework in which wear, force, and motion mutually feedback. Simultaneously, a temperature field factor is introduced to consider the influence of frictional heat generation on the lubricating oil film state in the contact area, and the contact friction coefficient and wear coefficient are corrected to achieve multi-physics field coupled analysis of temperature, mechanics, and the wear process.

[0053] In this embodiment, in step 4), a temperature field factor is introduced to correct the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, including the following steps: 4.1) Considering the influence of frictional heat generation on the state of the lubricating oil film in the contact area, the temperature field distribution at the contact interface is calculated based on the principle of frictional heat generation.

[0054] 4.2) Modify the viscosity characteristics and film formation state of the lubricating oil film in the contact area according to the temperature field distribution in order to adjust the contact friction coefficient.

[0055] 4.3) A temperature correction factor is introduced to modify the classical Archard wear model, establishing a generalized Archard wear model. The wear coefficient K is defined as a dynamic parameter related to the absolute temperature T: K = f (T).

[0056] 4.4) The influence mechanism of temperature gradient on material wear characteristics is quantitatively described by temperature correction factor, so that the wear coefficient exhibits dynamic nonlinear response characteristics with temperature change.

[0057] In this embodiment, temperature is a key factor affecting the wear behavior of the clutch wedge. Its mechanism mainly involves changing the viscosity characteristics and film-forming state of the oil film at the contact interface, thereby affecting the actual contact area of ​​the friction contact region. Simultaneously, it also affects the material's wear coefficient and compressive yield strength. σ s It exhibits dynamic nonlinear response characteristics as the temperature field changes, in which the wear coefficient ( K The temperature sensitivity of clutches dominates the evolution of their wear life. To characterize this thermo-coupling effect, Lee and Jou introduced a temperature correction factor into the classic Archard wear model, establishing a generalized Archard model. The core improvement lies in defining the wear coefficient K as a temperature-dependent dynamic parameter, which can quantitatively describe the influence mechanism of temperature gradient on material wear characteristics.

[0058] Corrected wear coefficient K for: (13) In the formula, T This refers to absolute temperature.

[0059] In the multiphysics coupling analysis of a wedge-type one-way clutch, there is a close and complex interaction between the mechanical field, the thermal field, and the wear field, forming a closed-loop iterative calculation system. The entire analysis system reflects the coupling and mutual influence between the mechanical field, the thermal field, and the wear field. The mechanical field determines the initial contact conditions and motion state, the thermal field adjusts the lubrication state and the temperature sensitivity of material properties, and the wear field influences the structural design and contact mechanism through morphological evolution feedback. These three fields, through data interaction and the coupling of physical mechanisms, form a dynamic closed-loop iterative solution process.

[0060] In step 5) above, if Figure 5 As shown, a dynamic wear numerical model is established based on a multiphysics coupling framework, including the following steps: 5.1) Set the basic parameters required for simulation, including time step, total duration and time vector, to provide a time reference for discretization calculation, and set the material physical properties, wedge contact conditions and load parameters.

[0061] Specifically, the physical properties of the material are defined, and material parameters such as hardness, coefficient of friction, density and specific heat capacity are set. The contact conditions and load parameters such as spring force, centrifugal force and contact area of ​​the wedge are defined to realize the force analysis of the wedge.

[0062] 5.2) Pre-allocate storage arrays for dynamic variables and set initial values ​​for initial geometry and wear-related parameters.

[0063] Specifically, the variable initialization module pre-allocates storage arrays for dynamic variables such as angle, contact force, and wear depth, avoiding frequent memory allocation adjustments during loop calculations and improving operational efficiency. It also sets initial values ​​for parameters such as wedge angle and inner / outer contact angle, and defines the initial geometric state of the system. Other wear-related parameters are gradually updated from their initial values ​​as wear progresses.

[0064] 5.3) Perform iterative calculations in the time domain to simulate the dynamic behavior of wear. In each iteration, perform normal load calculation, contact stress calculation, temperature rise model calculation, wear depth calculation, and dynamic adjustment of geometric parameters in sequence.

[0065] Specifically, the dynamic behavior of wear is simulated through time iteration. The normal load is a superposition of static forces such as springs and centrifugal forces, and dynamic excitations, reflecting the complexity of actual working conditions. Contact stress calculations reflect the pressure distribution of instantaneous loads on the contact surface. The temperature rise model is based on the principle of frictional heat generation; cumulative temperature changes affect material properties (hardness and friction coefficient decay). The Archard wear model, combined with Hertzian impact wear theory, quantifies the wear depth resulting from the combined effects of sliding and impact. Geometric parameters such as wedge angle and contact angle are dynamically adjusted using an exponential asymptotic model, reflecting the coordinated evolution of mechanism kinematics and thermodynamic coupling.

[0066] 5.4) Output curves showing the changes of key parameters over time to demonstrate the wear evolution pattern.

[0067] Specifically, a custom function is used to generate visualizations that show the curves of key parameters (angle, stress, wear depth, etc.) changing over time.

[0068] In the above embodiments, the force model, wear volume evolution model, and dynamic interface force analysis model are all constructed based on the strong nonlinear contact and wear coupling characteristics of the wedge-type one-way clutch under dynamic load conditions.

[0069] In summary, this invention transforms the dynamic response of the wedge under different operating conditions into physical quantities that can be used for wear calculation. These parameters serve as inputs to a multiphysics coupled model, providing necessary load and motion boundary conditions for subsequent wear volume evolution and interface updates. The obtained contact pressure and slip parameters are introduced into the wear volume evolution relationship, providing a temporally continuous description for the dynamic calculation of wear. The empirical model at the wear mechanism level is unified with the aforementioned dynamic and contact parameters, enabling wear calculations to directly reflect the actual stress state of the wedge. This invention realizes the reverse influence of wear-induced contact geometry changes on the stress state, thereby ensuring the self-consistency and stability of the model under dynamic operating conditions. Simultaneously, this invention also achieves dynamic numerical simulation of the wedge wear process, enabling wear prediction results to truly reflect the wear evolution law of the wedge under long-term operation and complex conditions.

[0070] Furthermore, in the multiphysics coupling modeling process, this invention constructs a strongly coupled iterative solution system with a clear transmission path and feedback mechanism based on the objectively existing causal dependence among the mechanical field, thermal field, and wear field. First, taking the clutch transient condition as input, a wedge-inner / outer ring contact model is established in the mechanical field. Key parameters such as contact pressure distribution, contact area, and relative sliding velocity are solved using a nonlinear contact algorithm. The contact stiffness and friction coefficient are not constants but are variables related to temperature and surface state, participating in subsequent coupling. Then, the contact pressure and sliding velocity output from the mechanical field are used as boundary conditions for the thermal field. The interface heat flux density is calculated based on a frictional heat generation model, and the temperature field distribution is solved using the heat conduction equation, while considering the nonlinear changes in material thermophysical parameters with temperature and the influence of contact thermal resistance. After obtaining the temperature field, it is applied inversely to the mechanical field, and by correcting parameters such as the material's elastic modulus, yield strength, and friction coefficient, thermo-mechanical coupling feedback is achieved. Building upon this foundation, wear field calculation is introduced. Using contact pressure, sliding distance, and a temperature-corrected wear coefficient as input, a modified wear evolution model is used to calculate the local wear depth. A geometric update strategy is employed to correct the contact surface morphology in real time, allowing the contact geometry to be directly fed back into the mechanical field calculation for the next time step. This forms a closed-loop coupling path of "geometric update—mechanical response—thermal effect—wear evolution." To ensure the numerical stability and physical consistency of this coupling process, a step-by-step iterative strategy is adopted at each time step: first, the mechanical and thermal fields are iteratively solved under the current geometry until the relative changes in contact pressure and temperature fields meet preset convergence conditions (the maximum rate of change of contact stress between two adjacent iterations is below a given threshold, and the temperature field error is below a given threshold); then, wear calculation and geometric updates are performed based on the converged thermo-mechanical field, and the updated geometry is used as the initial condition for the next time step to continue iterating. Through the above coupling algorithm, the three types of physical fields form an organic whole with clear input-output relationships and feedback adjustment mechanisms: the mechanical field determines the initial contact state, the thermal field regulates the material and interface properties, the wear field drives geometric evolution and reacts on the contact behavior, and the fields achieve dynamic consistency through parameter transfer and state update. This can truly reflect the nonlinear wear evolution process of the wedge-type one-way clutch under complex working conditions, which is significantly different from the traditional analysis methods based on single-field or weak coupling assumptions.

[0071] In one embodiment of the present invention, a dynamic wear model construction system for a wedge-type one-way clutch is provided, comprising: The force model construction unit is based on the power transmission path analysis of the wedge-type one-way clutch in the wedging stage, establishes the state interface force analysis model of the wedge, and solves the force and contact area of ​​the wedge in the wedging tightening stage. The wear volume evolution unit obtains the geometric forces of the wedge under different working conditions based on the force model, so as to obtain the contact pressure distribution, relative sliding velocity and contact time; the contact pressure and sliding parameters are introduced into the wear volume evolution relationship to construct a wear volume evolution model of wear volume evolution over time. Constitutive equations are introduced into the element to construct a wear constitutive equation based on contact mechanics, in order to determine the quantitative relationship between wedge contact pressure, relative slip distance and wear amount; The multiphysics coupling unit integrates and couples the wear volume evolution model, the wear constitutive equation, and the dynamic interface force analysis model to construct a multiphysics coupling framework for mutual feedback between wear, force, and motion. At the same time, the temperature field factor is introduced to correct the contact friction coefficient and the wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, so as to realize the multiphysics coupling analysis of temperature field, mechanical field, and wear field. The dynamic iterative update unit establishes a dynamic wear numerical model based on a multi-physics coupling framework to calculate the wear amount. It dynamically updates the contact surface geometric parameters of the wedge based on the cumulative wear amount and recalculates the contact force and wear parameters under the updated geometric parameters to achieve continuous iterative dynamic wear evolution.

[0072] In the above embodiments, establishing the force model of the wedge includes: Based on the clutch structural parameters and wedge angle geometry, a contact mechanics model between the wedge and the inner and outer rings is established. The normal force, friction force and their distribution on the wedge during the engagement stage are calculated, and the actual contact area and equivalent contact area between the wedge and the inner and outer rings are determined.

[0073] In the above embodiments, constructing a wear volume evolution model that reflects the wear volume over time includes: Based on Archard's wear theory, the microscopic contact state of the wedge block and the inner and outer ring interfaces is equivalent to the discrete contact behavior of a micro-protrusion structure. A quantitative relationship between the normal load and the contact area of ​​a single micro-protrusion contact point is established, thus yielding the expression for the volumetric wear amount generated by the combined action of multiple contact points per unit sliding distance: n×(2 / 3)π a ³; The volumetric wear amount expression is n×(2 / 3)π a ³ The area of ​​the contact region is dimensionless to construct a wear volume evolution model characterizing interface wear.

[0074] In the above embodiments, the wear constitutive equation is a discretized Arcard wear model, used to calculate the local wear depth increment per unit time; The wear constitutive equation is as follows: , In the formula, Δh(x,τ) is the wear depth increment, p(x,τ) is the contact pressure, δ(x,τ) is the relative sliding, and k is the wear coefficient.

[0075] In the above embodiments, the wear volume evolution model, the wear constitutive equation, and the dynamic interface force analytical model are integrated and coupled to construct a multi-physics coupling framework with mutual feedback between wear, force, and motion, including: Establish a closed-loop iterative calculation system among the mechanical field, thermal field, and wear field; Among them, the mechanical field is used to determine the initial contact conditions and motion state, and to transmit the contact pressure distribution and relative slip parameters to the wear field; The thermal field calculates the temperature change in the contact area based on the principle of frictional heat generation, and corrects the lubricating oil film state, contact friction coefficient and material wear coefficient according to the temperature change, and feeds the corrected parameters back to the mechanical field and wear field. The wear field calculates the wear depth increment based on the contact pressure and slip parameters transmitted by the mechanical field and the wear coefficient corrected by the thermal field. It also dynamically updates the geometry of the wedge contact surface based on the wear accumulation results and feeds the updated geometry back to the mechanical field to recalculate the contact force state. By coupling data and physical mechanisms between the mechanical field, thermal field and wear field, a multi-physics coupling framework is formed that allows wear-force-motion mutual feedback.

[0076] In the above embodiments, a temperature field factor is introduced to correct the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, including: Considering the influence of frictional heat generation on the state of the lubricating oil film in the contact area, the temperature field distribution at the contact interface is calculated based on the principle of frictional heat generation. The viscosity characteristics and film formation state of the lubricating oil film in the contact area are modified according to the temperature field distribution in order to adjust the contact friction coefficient. A temperature correction factor is introduced to modify the classic Archard wear model, establishing a generalized Archard wear model. The wear coefficient K is defined as a dynamic parameter related to the absolute temperature T: K = f (T); The influence mechanism of temperature gradient on material wear characteristics is quantitatively described by temperature correction factor, so that the wear coefficient exhibits dynamic nonlinear response characteristics with temperature change.

[0077] In the above embodiments, a dynamic wear numerical model is established based on a multiphysics coupling framework, including: Set the required basic parameters, including time step, total duration and time vector, to provide a time reference for discretization calculation, and set the material physical properties, wedge contact conditions and load parameters; Pre-allocate storage arrays for dynamic variables and set initial values ​​for initial geometry and wear-related parameters; The dynamic behavior of wear is simulated by iterative calculation in the time domain. In each iteration, the calculation of normal load, contact stress, temperature rise model, wear depth and dynamic adjustment of geometric parameters are performed in sequence. Output curves showing how key parameters change over time to illustrate the wear evolution pattern.

[0078] The system provided in this embodiment is used to execute the above-described method embodiments. For specific processes and details, please refer to the above embodiments, which will not be repeated here.

[0079] In one embodiment of the present invention, a computing device is provided. This computing device can be a terminal and may include a processor, a communication interface, memory, a display screen, and an input device. The processor, communication interface, and memory communicate with each other via a communication bus. The processor provides computing and control capabilities. The memory includes a non-volatile storage medium and internal memory. The non-volatile storage medium stores an operating system and computer programs. When the computer programs are executed by the processor, they implement the methods described in the above embodiments. The internal memory provides an environment for the operation of the operating system and computer programs in the non-volatile storage medium. The communication interface is used for wired or wireless communication with external terminals. Wireless communication can be achieved through Wi-Fi, a network management system, NFC (Near Field Communication), or other technologies. The display screen can be a liquid crystal display (LCD) or an e-ink display. The input device can be a touch layer covering the display screen, or buttons, a trackball, or a touchpad mounted on the casing of the computing device, or an external keyboard, touchpad, or mouse. The processor can call logical instructions stored in the memory to execute the above methods.

[0080] In one embodiment of the present invention, a computer program product is provided, comprising a computer program stored on a non-transitory computer-readable storage medium, the computer program comprising program instructions, and when the program instructions are executed by a computer, the computer is able to perform the methods provided in the above-described method embodiments.

[0081] In one embodiment of the present invention, a non-transitory computer-readable storage medium is provided, which stores server instructions that cause a computer to perform the methods provided in the above embodiments.

[0082] The computer-readable storage medium provided in the above embodiments has a similar implementation principle and technical effect to the above method embodiments, and will not be described again here.

[0083] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0084] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0085] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0086] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A method for constructing a dynamic wear model of a wedge-type one-way clutch wedge, characterized in that, include: Based on the power transmission path analysis of the wedge-type one-way clutch during the wedging stage, a dynamic interface force analysis model of the wedge is established, and the force and contact area of ​​the wedge during the wedging tightening stage are solved. Based on the force model, the geometric force of the wedge under different working conditions is obtained to obtain the contact pressure distribution, relative sliding velocity and contact time; the contact pressure and sliding parameters are introduced into the wear volume evolution relationship to construct a wear volume evolution model of wear volume evolution over time. A wear constitutive equation based on contact mechanics is constructed to determine the quantitative relationship between wedge contact pressure, relative slip distance and wear amount; The wear volume evolution model, wear constitutive equation and dynamic interface force analytical model are integrated and coupled to construct a multi-physics coupling framework for wear-force-motion mutual feedback; at the same time, temperature field factors are introduced to modify the contact friction coefficient and wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, so as to realize the multi-physics coupling analysis of temperature field, mechanical field and wear field. A dynamic wear numerical model is established based on a multiphysics coupling framework to calculate the wear amount. The contact surface geometric parameters of the wedge are dynamically updated according to the cumulative wear amount, and the contact force and wear parameters are recalculated under the updated geometric parameters to achieve continuous iterative dynamic wear evolution.

2. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, Establishing the force model of the wedge includes: Based on the clutch structural parameters and wedge angle geometry, a contact mechanics model between the wedge and the inner and outer rings is established. The normal force, friction force and their distribution on the wedge during the engagement stage are calculated, and the actual contact area and equivalent contact area between the wedge and the inner and outer rings are determined.

3. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, The wear volume evolution model, which describes the wear volume over time, includes: Based on Archard's wear theory, the microscopic contact state of the wedge block and the inner and outer ring interfaces is equivalent to the discrete contact behavior of a micro-protrusion structure. A quantitative relationship between the normal load and the contact area of ​​a single micro-protrusion contact point is established, thus yielding the expression for the volumetric wear amount generated by the combined action of multiple contact points per unit sliding distance: n×(2 / 3)π a ³; The volumetric wear amount expression is n×(2 / 3)π a ³ The area of ​​the contact region is dimensionless to construct a wear volume evolution model characterizing interface wear.

4. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, The wear constitutive equation is a discretized Arcard wear model used to calculate the local wear depth increment per unit time; The wear constitutive equation is as follows: ， In the formula, Δh(x,τ) is the wear depth increment, p(x,τ) is the contact pressure, δ(x,τ) is the relative sliding, and k is the wear coefficient.

5. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, By integrating and coupling the wear volume evolution model, the wear constitutive equation, and the dynamic interface force analytical model, a multiphysics coupling framework with mutual feedback between wear, force, and motion is constructed, including: Establish a closed-loop iterative calculation system among the mechanical field, thermal field, and wear field; Among them, the mechanical field is used to determine the initial contact conditions and motion state, and to transmit the contact pressure distribution and relative slip parameters to the wear field; The thermal field calculates the temperature change in the contact area based on the principle of frictional heat generation, and corrects the lubricating oil film state, contact friction coefficient and material wear coefficient according to the temperature change, and feeds the corrected parameters back to the mechanical field and wear field. The wear field calculates the wear depth increment based on the contact pressure and slip parameters transmitted by the mechanical field and the wear coefficient corrected by the thermal field. It also dynamically updates the geometry of the wedge contact surface based on the wear accumulation results and feeds the updated geometry back to the mechanical field to recalculate the contact force state. By coupling data and physical mechanisms between the mechanical field, thermal field and wear field, a multi-physics coupling framework is formed that allows wear-force-motion mutual feedback.

6. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, By introducing temperature field factors, the contact friction coefficient and wear coefficient are corrected, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, including: Considering the influence of frictional heat generation on the state of the lubricating oil film in the contact area, the temperature field distribution at the contact interface is calculated based on the principle of frictional heat generation. The viscosity characteristics and film formation state of the lubricating oil film in the contact area are modified according to the temperature field distribution in order to adjust the contact friction coefficient. A temperature correction factor is introduced to modify the classic Archard wear model, establishing a generalized Archard wear model. The wear coefficient K is defined as a dynamic parameter related to the absolute temperature T: K = f (T); The influence mechanism of temperature gradient on material wear characteristics is quantitatively described by temperature correction factor, so that the wear coefficient exhibits dynamic nonlinear response characteristics with temperature change.

7. The method for constructing a dynamic wear model of a wedge-type one-way clutch as described in claim 1, characterized in that, A dynamic wear numerical model is established based on a multiphysics coupling framework, including: Set the required basic parameters, including time step, total duration and time vector, to provide a time reference for discretization calculation, and set the material physical properties, wedge contact conditions and load parameters; Pre-allocate storage arrays for dynamic variables and set initial values ​​for initial geometry and wear-related parameters; The dynamic behavior of wear is simulated by iterative calculation in the time domain. In each iteration, the calculation of normal load, contact stress, temperature rise model, wear depth and dynamic adjustment of geometric parameters are performed in sequence. Output curves showing how key parameters change over time to illustrate the wear evolution pattern.

8. A system for constructing a dynamic wear model of a wedge-type one-way clutch wedge, characterized in that, include: The force model construction unit is based on the power transmission path analysis of the wedge-type one-way clutch in the wedging stage, establishes the state interface force analysis model of the wedge, and solves the force and contact area of ​​the wedge in the wedging tightening stage. The wear volume evolution unit obtains the geometric forces of the wedge under different working conditions based on the force model, so as to obtain the contact pressure distribution, relative sliding velocity and contact time; the contact pressure and sliding parameters are introduced into the wear volume evolution relationship to construct a wear volume evolution model of wear volume evolution over time. Constitutive equations are introduced into the element to construct a wear constitutive equation based on contact mechanics, in order to determine the quantitative relationship between wedge contact pressure, relative slip distance and wear amount; The multiphysics coupling unit integrates and couples the wear volume evolution model, the wear constitutive equation, and the dynamic interface force analysis model to construct a multiphysics coupling framework for mutual feedback between wear, force, and motion. At the same time, the temperature field factor is introduced to correct the contact friction coefficient and the wear coefficient, and the wear coefficient is defined as a dynamic parameter related to absolute temperature, so as to realize the multiphysics coupling analysis of temperature field, mechanical field, and wear field. The dynamic iterative update unit establishes a dynamic wear numerical model based on a multi-physics coupling framework to calculate the wear amount. It dynamically updates the contact surface geometric parameters of the wedge based on the cumulative wear amount and recalculates the contact force and wear parameters under the updated geometric parameters to achieve continuous iterative dynamic wear evolution.

9. A computer-readable storage medium for storing one or more programs, characterized in that, One or more programs include instructions that, when executed by a computing device, cause the computing device to perform any of the methods described in claims 1 to 7.

10. A computing device, characterized in that, include: One or more processors, memory, and one or more programs, wherein the one or more programs are stored in memory and configured to be executed by the one or more processors, and the one or more programs include instructions for performing any of the methods described in claims 1 to 7.

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