A method and system for designing a structural element of a clutch for radial temperature difference homogenization

Abstract

The application discloses a kind of clutch radial temperature difference homogenization structure element design method and system, wherein method steps include: the pressing plate structure of clutch is optimized, and first improved pressing plate is obtained;Topology optimization is carried out to the first improved pressing plate, and second improved pressing plate is obtained;Clutch texture friction plate is designed based on the second improved pressing plate;The design of structure element is completed by optimizing clutch texture friction plate.The application can calculate the temperature field of clutch under different structural characteristics or texture friction plate conditions, can quantify the improvement degree of radial temperature difference of friction plate, so as to effectively evaluate the effectiveness of various radial temperature homogenization methods, can modify design scheme at any time, save a lot of time and test cost.

Description

Technical Field

[0001] This invention relates to the field of automotive clutch technology, and specifically to a structural element design method and system for uniform radial temperature difference in a clutch. Background Technology

[0002] Wet-type clutches are widely used in vehicle transmissions due to their unique advantages such as high load-bearing capacity, large torque transmission, and simple structure, and are a core component of various stepped transmission systems. During the slippage process of a wet clutch, the friction elements are subjected to the uniform surface pressure of the piston at both axial ends and the local constraint of the snap ring only near the outer ring. This results in a radially non-uniform pressure distribution at the friction interface, and pressure attenuation between multiple friction pairs, leading to radially non-uniform heat flow input at the friction interface and differences in temperature rise among the various friction elements. However, excessive radial temperature differences in the friction elements can lead to their failure, affecting the reliability of the transmission system and the safety of driving.

[0003] Clutch temperature prediction relies on the construction of temperature models, and scholars have conducted extensive research on the radial temperature distribution characteristics of clutch friction elements. Patent ZL202111278538.5 provides a method for constructing a simulation model of automatic transmission clutch temperature, which can obtain the theoretical temperatures of the clutch's mating steel plates and oil outlet based on real vehicle information. Patent CN202410376193.4 proposes a method and system for calculating the temperature field and thermal failure of clutch friction elements, capable of obtaining the temperature field and thermal stress of steel plates at different locations. Patent ZL202410166547.2 proposes a method for constructing a temperature field prediction model for wet multi-plate clutch assemblies, which can extract the temperature field distribution characteristics and patterns of the clutch assembly. Patent ZL202210564535.6 proposes a clutch friction torque prediction method based on lumped parameters and finite differences, improving the accuracy and applicability of the temperature rise calculation model.

[0004] Meanwhile, scholars have also proposed improved design schemes for clutch structural features to optimize the radial temperature field distribution of friction elements. Patent CN202310429647.5 adds a boss to the original clutch pressure plate, increasing the contact pressure at the inner diameter of the friction pair and reducing the difference in contact pressure distribution, thereby reducing the thermal load of the wet multi-plate clutch. Patent CN202310964752.9 provides an oil groove structure for friction elements, using the width variation of the arc-shaped oil groove to generate a squeezing effect, accelerating the flow of lubricating oil and preventing thermal warping. Patent CN202410158549.7 proposes a friction element that can reduce heat dissipation of lubricating oil at the inner diameter and increase heat dissipation at the outer diameter, thereby improving the uniformity of radial temperature distribution of the friction element and mitigating the phenomenon of excessive radial temperature difference.

[0005] However, current clutch temperature field modeling methods do not consider the need to improve the radial temperature of the clutch, making the temperature field model unsuitable for calculating the temperature field after clutch structure optimization. Furthermore, the clutch structure improvement schemes provided by scholars do not involve the calculation and evaluation of the clutch temperature field, thus failing to provide data support for clutch control strategies. Therefore, no papers or patents currently provide a design method or system for structural components to achieve uniform radial temperature difference in the clutch. Summary of the Invention

[0006] To address the problems in existing technologies, this invention proposes a structural element design method and system for achieving radial temperature difference uniformity in clutches. It provides an optimization design method for the actual structural features of the clutch, obtaining the true contact pressure distribution of the optimized friction elements. Furthermore, it presents an optimization design method for textured friction plates, determining the influence of pressure on the friction coefficient of different textured friction plates based on their texture characteristics. This yields the true heat flux density distribution of the friction elements, allowing for the solution of the clutch temperature field. The invention also provides feedback on the suitability of the structural features and textured friction plate design, enabling timely modification of the design and saving significant time and testing costs.

[0007] To achieve the above objectives, the present invention provides a structural component design method for uniform radial temperature difference in a clutch, comprising the following steps:

[0008] The pressure plate structure of the clutch is optimized to obtain the first improved pressure plate;

[0009] The first improved pressure plate is topologically optimized to obtain the second improved pressure plate;

[0010] Based on the second improved pressure plate, a clutch textured friction plate is designed;

[0011] The clutch textured friction plate was optimized, and the design of the structural components was completed.

[0012] Preferably, the method for obtaining the first improved pressure plate includes:

[0013] The pressure plate structure of the clutch is optimized, and an optimization domain for the pressure plate is constructed.

[0014] Establish a finite element model based on the actual structural characteristics of the clutch;

[0015] The finite element model is used to analyze the actual contact pressure distribution characteristics of each friction element under different pressure plate characteristics in the pressure plate optimization domain;

[0016] Based on the actual contact pressure distribution characteristics, the radial pressure difference of each friction element under different optimized pressure plate shapes is evaluated to obtain the first improved pressure plate.

[0017] Preferably, the method for evaluating the radial pressure difference includes: dividing the radial direction of the friction element into two regions and calculating the pressure difference between the two regions:

[0018]

[0019] Where k (A,B) This indicates the pressure difference between regions A and B; This represents the average radial distance of the steel sheets; it also represents the average contact stress of each component. This represents the average contact stress of each component.

[0020] Using the minimum total difference k of radial pressure of friction elements as the evaluation criterion, the optimal shape of the pressure plate is obtained, resulting in the first improved pressure plate.

[0021] Preferably, the method for performing the topology optimization includes: taking the growth quality of the first improved pressure plate as the optimization object, setting the optimization target, applying finite element software to perform topology optimization, identifying the removable area of ​​the optimized shape of the pressure plate, and obtaining the second improved pressure plate.

[0022] Preferably, the growth quality of the first improved pressure plate includes:

[0023] Δm=m1-m0

[0024] Where Δm represents the increased mass of the first improved pressure plate; m1 represents the pressure plate mass of the first improved pressure plate; and m0 represents the initial mass of the first improved pressure plate.

[0025] The optimization objectives set include:

[0026] a·Δm

[0027] Where 'a' represents the reduction ratio.

[0028] Preferably, the method for designing the clutch textured friction plate includes: designing small-sample textured friction plates with different parameters, conducting textured friction plate tests, and obtaining the friction coefficients of different textured friction plates under different pressure conditions; and designing the clutch textured friction plate based on the pressure and friction coefficient mapping relationship of the small-sample textured friction plates.

[0029] Preferably, the radial positional characteristics of the clutch textured friction plate include: a large inner diameter friction coefficient and a small outer diameter friction coefficient.

[0030] The present invention also provides a structural element design system for uniform radial temperature difference in a clutch. The system is used to implement the above method and includes: a shape determination module, a topology optimization module, a design module, and a friction plate optimization module.

[0031] The shape determination module is used to optimize the pressure plate structure of the clutch to obtain a first improved pressure plate;

[0032] The topology optimization module is used to perform topology optimization on the first improved pressure plate to obtain a second improved pressure plate.

[0033] The design module is used to design a clutch textured friction plate based on the second improved pressure plate;

[0034] The friction plate optimization module is used to optimize the clutch texture friction plate and complete the design of the structural components.

[0035] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0036] This invention can calculate the clutch temperature field under different structural features or textured friction plates, quantify the degree of improvement in radial temperature difference of friction plates, thereby effectively evaluating the effectiveness of various radial temperature homogenization methods, allowing for timely modification of design schemes, and saving a significant amount of time and testing costs. Attached Figure Description

[0037] To more clearly illustrate the technical solution of the present invention, the drawings used in the embodiments are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0038] Figure 1 This is a schematic diagram of the method structure according to an embodiment of the present invention;

[0039] Figure 2 This is a schematic diagram of the pressure characteristics according to an embodiment of the present invention;

[0040] Figure 3 This is a schematic diagram of the contact pressure function under different quality targets in an embodiment of the present invention;

[0041] Figure 4 This is a schematic diagram of the temperature field under different mass targets according to an embodiment of the present invention. Detailed Implementation

[0042] 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 embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0044] Example 1

[0045] like Figure 1 The diagram shown is a schematic representation of the method flow in this embodiment, and the steps include:

[0046] S1. The pressure plate structure of the clutch is optimized to obtain the first improved pressure plate.

[0047] S101. Optimize the pressure plate structure of the clutch and construct the pressure plate optimization domain.

[0048] The pressure plate structure is optimized, an optimization domain for the clutch pressure plate is constructed, and optimization shapes for the pressure plate are proposed, including: outer conical, inner conical, rectangular, and semi-circular pressure plate shapes.

[0049] S102. Establish a finite element model based on the actual structural characteristics of the clutch.

[0050] A finite element model of a six-friction-pair clutch was established using Abaqus software, taking into account the actual structural characteristics. The friction plates consist of a friction base plate and friction lining plates, with the lining plates arranged on both sides of the base plate. In the model, the outer end surface of the snap ring is fixed, and pressure is uniformly applied to the piston end surface. The mesh generation method used in this model is C3D8R, and the interaction between the friction pairs is a "penalty function" and "face-to-face contact" method.

[0051] S103. Analyze the actual contact pressure distribution characteristics of each friction element under different pressure plate characteristics in the pressure plate optimization domain using the finite element model.

[0052] The actual contact pressure distribution characteristics of each friction element under different pressure plate features are studied in the constructed finite element model. The radial pressure difference of each friction element under different optimized pressure plate shapes is evaluated, and the optimized pressure plate shape is determined. Specific methods include:

[0053] The radial direction of each friction element is divided into two regions, A and B. In this embodiment, the radial ranges of the two regions are (86mm, 105mm) and (105mm, 125mm), respectively. The pressure difference between the two regions is calculated:

[0054]

[0055] Where k (A,B) This indicates the pressure difference between regions A and B; This represents the average radial distance of the steel sheets; it also represents the average contact stress of each component. This represents the average contact stress of each component.

[0056] S104. Based on the actual contact pressure distribution characteristics, evaluate the radial pressure difference of each friction element under different optimized pressure plate shapes, and determine the optimized pressure plate shape.

[0057] Using the minimum total difference k of the radial pressure of the friction elements as the evaluation criterion, the optimal shape of the pressure plate is obtained, resulting in the first improved pressure plate. Following the above steps, the k values ​​for the four shapes (outer conical, inner conical, rectangular, and semi-circular pressure plates) are 0.85, 0.96, 0.41, and 0.61, respectively. Figure 2 As shown, the rectangular pressure plate structure exhibits the smallest pressure difference.

[0058] S2. Perform topology optimization on the first improved pressure plate to obtain the second improved pressure plate.

[0059] Taking the growth mass of the first improved pressure plate as the optimization object, an optimization objective was set, and topology optimization was performed using finite element software to identify the removable regions of the optimized pressure plate shape, thus obtaining the second improved pressure plate. The growth mass of the first improved pressure plate includes:

[0060] Δm=m1-m0

[0061] Where Δm represents the increased mass of the first improved pressure plate; m1 represents the pressure plate mass of the first improved pressure plate; and m0 represents the initial mass of the first improved pressure plate.

[0062] The optimization objectives set include:

[0063] a·Δm

[0064] Where 'a' represents the reduction ratio.

[0065] In the embodiment, a is taken as 80%, 50% and 30% respectively to confirm the removable area of ​​the pressure plate's optimized shape, thus obtaining the improved pressure plate 2.

[0066] S3. Based on the second improved pressure plate, design the clutch textured friction plate.

[0067] Design small-scale textured friction plates with different parameters, and conduct tests on the textured friction plates to obtain the friction coefficients of different textured friction plates under different pressure conditions; based on the mapping relationship between pressure and friction coefficient of the small-scale textured friction plates, design a clutch textured friction plate. Specific steps include:

[0068] First, the contact pressure characteristic function of each friction element of the clutch under the action of the second improved pressure plate is transformed to obtain p. i (r), such as Figure 3 As shown; where i = 1, 2, 3..., p i (r) represents the contact pressure function with the i-th independent variable being the radial coordinate r.

[0069] Subsequently, small-scale textured friction plates with different diameters, depths, shapes, and spacings were designed. The textured friction plates were then tested using a UMT friction and wear testing machine to obtain the friction coefficients of different textured friction plates under different pressure conditions. Based on the pressure-friction coefficient mapping relationship of the small-scale textured friction plates, a clutch textured friction plate was designed. Different textured features were designed at the radial position of the friction plate to ensure that the friction coefficient gradually decreases along the radial direction, i.e., the friction coefficient is larger at the inner diameter and smaller at the outer diameter.

[0070] Combining the contact pressure characteristic function p i (r) gives the radial friction coefficient distribution function μ of the textured friction pad. i (p i (r)); where μ i This indicates that the friction coefficient under different pressures p can be obtained through pin-plate testing, and then μ can be obtained through function fitting. i (p); then combine the contact pressure characteristic function p i (r), substituted into μ i (p) yields the radial friction coefficient distribution function μ of the textured friction pad. i (p i (r)).

[0071] S4. Optimize the clutch texture friction plate and complete the design of structural components.

[0072] Calculate the heat flux density of the i-th textured friction plate:

[0073] q i (t,r)=μ i (p i (r))·p i (r)·ω(t)·r

[0074] In the formula, ω(t) represents the rotational angular velocity of the friction element.

[0075] Calculate the radial temperature field characteristics of the i-th textured friction piece:

[0076]

[0077] T(r,z,t)| t＝0 =T0

[0078] In the formula, T represents temperature; ρ, c, and λ represent the material's density, specific heat capacity, and thermal conductivity, respectively. γ is the heat flow distribution coefficient between friction elements. T oil The ambient temperature is represented by T0, the initial temperature by H, and the steel sheet thickness by r. i and r o These are the inner and outer diameters of the friction element, respectively; h ih o These are the convective heat transfer coefficients at the inner and outer diameters, respectively, and the results are as follows: Figure 4 As shown.

[0079] Calculate the degree of improvement in radial temperature difference. Assume the clutch operates under constant speed slippage conditions, with the relative angular velocity difference ω(t) being a constant value, and the slippage time being t. m .

[0080] Calculate the final slippage time t under the original characteristic conditions of the clutch. m The radial temperature difference of the i-th friction plate,

[0081] ΛT i,y =T i,y (r o ,H,t m )-T i,y (r i ,H,t m )

[0082] After calculating the optimized structural characteristics of the clutch, the final time t of slippage is... m The radial temperature difference of the i-th textured friction plate,

[0083] ΛT i =T i (r o ,H,t m )-T i (r i ,H,t m )

[0084] The degree of improvement in radial temperature difference ξ of the optimized scheme is calculated as follows:

[0085]

[0086] If ξ does not meet the improvement requirements, the clutch pressure plate structure features, the reduction ratio a of the increased mass Δm, and the arrangement of the textured friction plates should be redesigned.

[0087] Example 2

[0088] This embodiment also provides a structural component design system for uniform radial temperature difference in a clutch, including: a shape determination module, a topology optimization module, a design module, and a friction plate optimization module; the shape determination module is used to optimize the pressure plate structure of the clutch to obtain a first improved pressure plate; the topology optimization module is used to perform topology optimization on the first improved pressure plate to obtain a second improved pressure plate; the design module is used to design the clutch textured friction plate based on the second improved pressure plate; the friction plate optimization module is used to optimize the clutch textured friction plate to complete the design of the structural component.

[0089] The following will describe in detail, with reference to this embodiment, how the present invention solves the technical problems in practical work.

[0090] First, the shape determination module is used to optimize the pressure plate structure of the clutch, resulting in the first improved pressure plate. The specific process includes:

[0091] S101. Optimize the pressure plate structure of the clutch and construct the pressure plate optimization domain.

[0092] The pressure plate structure is optimized, an optimization domain for the clutch pressure plate is constructed, and optimization shapes for the pressure plate are proposed, including: outer conical, inner conical, rectangular, and semi-circular pressure plate shapes.

[0093] S102. Establish a finite element model based on the actual structural characteristics of the clutch.

[0094] A finite element model of a six-friction-pair clutch was established using Abaqus software, taking into account the actual structural characteristics. The friction plates consist of a friction base plate and friction lining plates, with the lining plates arranged on both sides of the base plate. In the model, the outer end surface of the snap ring is fixed, and pressure is uniformly applied to the piston end surface. The mesh generation method used in this model is C3D8R, and the interaction between the friction pairs is a "penalty function" and "face-to-face contact" method.

[0095] S103. Analyze the actual contact pressure distribution characteristics of each friction element under different pressure plate characteristics in the pressure plate optimization domain using the finite element model.

[0096] The actual contact pressure distribution characteristics of each friction element under different pressure plate features are studied in the constructed finite element model. The radial pressure difference of each friction element under different optimized pressure plate shapes is evaluated, and the optimized pressure plate shape is determined. Specific methods include:

[0097] The radial direction of each friction element is divided into two regions, A and B. In this embodiment, the radial ranges of the two regions are (86mm, 105mm) and (105mm, 125mm), respectively. The pressure difference between the two regions is calculated:

[0098]

[0099] Where k (A,B) This indicates the pressure difference between regions A and B; This represents the average radial distance of the steel sheets; it also represents the average contact stress of each component. This represents the average contact stress of each component.

[0100] S104. Based on the actual contact pressure distribution characteristics, evaluate the radial pressure difference of each friction element under different optimized pressure plate shapes, and determine the optimized pressure plate shape.

[0101] Using the minimum total difference k of the radial pressure of the friction elements as the evaluation criterion, the optimal shape of the pressure plate is obtained, resulting in the first improved pressure plate. Following the above steps, the k values ​​for the four shapes (outer conical, inner conical, rectangular, and semi-circular pressure plates) are 0.85, 0.96, 0.41, and 0.61, respectively. Figure 2 As shown, the rectangular pressure plate structure exhibits the smallest pressure difference.

[0102] Then, the topology optimization module was used to optimize the topology of the first improved pressure plate to obtain the second improved pressure plate.

[0103] Taking the growth mass of the first improved pressure plate as the optimization object, an optimization objective was set, and topology optimization was performed using finite element software to identify the removable regions of the optimized pressure plate shape, thus obtaining the second improved pressure plate. The growth mass of the first improved pressure plate includes:

[0104] Δm=m1-m0

[0105] Where Δm represents the increased mass of the first improved pressure plate; m1 represents the pressure plate mass of the first improved pressure plate; and m0 represents the initial mass of the first improved pressure plate.

[0106] The optimization objectives set include:

[0107] a·Δm

[0108] Where 'a' represents the reduction ratio.

[0109] In the embodiment, a is taken as 80%, 50% and 30% respectively to confirm the removable area of ​​the pressure plate's optimized shape, thus obtaining the improved pressure plate 2.

[0110] The design module is based on the second improved pressure plate and designs the clutch textured friction plate.

[0111] Design small-scale textured friction plates with different parameters, and conduct tests on the textured friction plates to obtain the friction coefficients of different textured friction plates under different pressure conditions; based on the mapping relationship between pressure and friction coefficient of the small-scale textured friction plates, design a clutch textured friction plate. Specific steps include:

[0112] First, the contact pressure characteristic function of each friction element of the clutch under the action of the second improved pressure plate is transformed to obtain p. i (r), such as Figure 3 As shown; where i = 1, 2, 3..., p i (r) represents the contact pressure function with the i-th independent variable being the radial coordinate r.

[0113] Subsequently, small-scale textured friction plates with different diameters, depths, shapes, and spacings were designed. The textured friction plates were then tested using a UMT friction and wear testing machine to obtain the friction coefficients of different textured friction plates under different pressure conditions. Based on the pressure-friction coefficient mapping relationship of the small-scale textured friction plates, a clutch textured friction plate was designed. Different textured features were designed at the radial position of the friction plate to ensure that the friction coefficient gradually decreases along the radial direction, i.e., the friction coefficient is larger at the inner diameter and smaller at the outer diameter.

[0114] Combining the contact pressure characteristic function p i (r) gives the radial friction coefficient distribution function μ of the textured friction pad. i (p i (r)); where μ i This indicates that the friction coefficient under different pressures p can be obtained through pin-plate testing, and then μ can be obtained through function fitting. i (p); then combine the contact pressure characteristic function p i (r), substituted into μ i (p) yields the radial friction coefficient distribution function μ of the textured friction pad. i (p i (r)).

[0115] Finally, the friction plate optimization module was used to optimize the clutch texture friction plate, completing the design of the structural components.

[0116] Calculate the heat flux density of the i-th textured friction plate:

[0117] q i (t,r)=μ i (p i (r))·p i (r)·ω(t)·r

[0118] In the formula, ω(t) represents the rotational angular velocity of the friction element.

[0119] Calculate the radial temperature field characteristics of the i-th textured friction piece:

[0120]

[0121] T(r,z,t)| t＝0 =T0

[0122] In the formula, T represents temperature; ρ, c, and λ represent the material's density, specific heat capacity, and thermal conductivity, respectively. γ is the heat flow distribution coefficient between friction elements. T oil The ambient temperature is represented by T0, the initial temperature by H, and the steel sheet thickness by r. i and r o These are the inner and outer diameters of the friction element, respectively; h i ho These are the convective heat transfer coefficients at the inner and outer diameters, respectively, and the results are as follows: Figure 4 As shown.

[0123] Calculate the degree of improvement in radial temperature difference. Assume the clutch operates under constant speed slippage conditions, with the relative angular velocity difference ω(t) being a constant value, and the slippage time being t. m .

[0124] Calculate the final slippage time t under the original characteristic conditions of the clutch. m The radial temperature difference of the i-th friction plate,

[0125] ΛT i,y =T i,y (r o ,H,t m )-T i,y (r i ,H,t m )

[0126] After calculating the optimized structural characteristics of the clutch, the final time t of slippage is... m The radial temperature difference of the i-th textured friction plate,

[0127] ΛT i =T i (r o ,H,t m )-T i (r i ,H,t m )

[0128] The degree of improvement in radial temperature difference ξ of the optimized scheme is calculated as follows:

[0129]

[0130] If ξ does not meet the improvement requirements, the clutch pressure plate structure features, the reduction ratio a of the increased mass Δm, and the arrangement of the textured friction plates should be redesigned.

[0131] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Various modifications and improvements made by those skilled in the art to the technical solutions of the present invention without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. A structural component design method for uniform radial temperature difference in a clutch, characterized by the following steps: include: The pressure plate structure of the clutch is optimized to obtain the first improved pressure plate; The first improved pressure plate is topologically optimized to obtain the second improved pressure plate; Based on the second improved pressure plate, a clutch textured friction plate is designed; The steps include: transforming the contact pressure characteristic function of each friction element of the clutch under the action of the second improved pressure plate into the form of... p i ( r ),in, i= 1, 2, 3... p i ( r ) indicates the first i A contact pressure function with radial coordinate r as the independent variable; Based on the mapping relationship between pressure and friction coefficient of the small sample textured friction plate, a clutch textured friction plate is designed. Different forms of texture features are designed at the radial position of the friction plate to ensure that the friction coefficient gradually decreases along the radial direction, that is, the friction coefficient of the inner diameter is large and the friction coefficient of the outer diameter is small. The clutch textured friction plate was optimized, and the design of the structural components was completed.

2. The structural component design method for uniform radial temperature difference in a clutch according to claim 1, characterized in that, The method for obtaining the first improved pressure plate includes: The pressure plate structure of the clutch is optimized, and an optimization domain for the pressure plate is constructed. Establish a finite element model based on the actual structural characteristics of the clutch; The finite element model is used to analyze the actual contact pressure distribution characteristics of each friction element under different pressure plate characteristics in the pressure plate optimization domain; Based on the actual contact pressure distribution characteristics, the radial pressure difference of each friction element under different optimized pressure plate shapes is evaluated to obtain the first improved pressure plate.

3. The structural component design method for uniform radial temperature difference in a clutch according to claim 2, characterized in that, The method for evaluating the radial pressure difference includes dividing the radial direction of the friction element into two regions and calculating the pressure difference between these two regions: in k ( A , B This indicates the pressure difference between regions A and B; This represents the average radial distance of the steel sheets; This represents the average contact stress of each component. r Represents radial coordinates; Using the minimum total difference k of radial pressure of friction elements as the evaluation criterion, the optimal shape of the pressure plate is obtained, resulting in the first improved pressure plate.

4. The structural component design method for uniform radial temperature difference in a clutch according to claim 3, characterized in that, The method for performing the topology optimization includes: taking the growth quality of the first improved pressure plate as the optimization object, setting the optimization target, applying finite element software to perform topology optimization, identifying the removable area of ​​the optimized shape of the pressure plate, and obtaining the second improved pressure plate.

5. The structural component design method for uniform radial temperature difference in a clutch according to claim 4, characterized in that, The growth quality of the first improved pressure plate includes: in, This indicates the increased quality of the first improved pressure plate; m 1 indicates the quality of the first improved pressure plate; m 0 indicates the initial mass of the first improved pressure plate; The optimization objectives set include: Where 'a' represents the reduction ratio.

6. The structural component design method for uniform radial temperature difference in a clutch according to claim 1, characterized in that, The method for designing the clutch textured friction plate includes: designing small-sample textured friction plates with different parameters, conducting textured friction plate tests, and obtaining the friction coefficients of different textured friction plates under different pressure conditions; and designing the clutch textured friction plate based on the pressure and friction coefficient mapping relationship of the small-sample textured friction plates.

7. A structural element design system for uniform radial temperature difference in a clutch, said system being used to implement the method according to any one of claims 1-6, characterized in that, include: The module includes a shape determination module, a topology optimization module, a design module, and a friction plate optimization module. The shape determination module is used to optimize the pressure plate structure of the clutch to obtain a first improved pressure plate; The topology optimization module is used to perform topology optimization on the first improved pressure plate to obtain a second improved pressure plate. The design module is used to design a clutch textured friction plate based on the second improved pressure plate; The process includes: quantifying the contact pressure characteristic function of each friction element of the clutch under the action of the second improved pressure plate, to obtain... p i ( r ),in, i= 1, 2, 3... p i ( r ) indicates the first i A contact pressure function with radial coordinate r as the independent variable; Based on the mapping relationship between pressure and friction coefficient of the small sample textured friction plate, a clutch textured friction plate is designed. Different forms of texture features are designed at the radial position of the friction plate to ensure that the friction coefficient gradually decreases along the radial direction, that is, the friction coefficient of the inner diameter is large and the friction coefficient of the outer diameter is small. The friction plate optimization module is used to optimize the clutch texture friction plate and complete the design of the structural components.

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