Clutch cover strength simulation analysis method, device, equipment and medium

Abstract

The invention provides a clutch cover strength simulation analysis method, device and equipment and a medium. The method comprises the following steps: configuring three-dimensional models of a clutch cover, a flywheel and a connecting bolt; defining a flywheel inner side constraint set point, a transmission sheet constraint set point and a diaphragm spring constraint set point in the clutch cover strength calculation finite element model; respectively setting degrees of freedom and loads of a flywheel inner side constraint set point, a transmission sheet constraint set point and a diaphragm spring constraint set point; and calling a stress distribution cloud picture of the three-dimensional model of the clutch cover, identifying a yield strength threshold exceeding region in the stress distribution cloud picture, defining the yield strength threshold exceeding region as a dangerous position, respectively determining the dangerous positions of the front surface and the back surface of the clutch cover, and extracting a stress calculation result maximum value of the dangerous positions. Through structural design and strength calculation, related data is provided for design and optimization of the clutch cover, the actual stress condition can be simulated more accurately, and the strength of the clutch cover can be evaluated.

Description

Technical Field

[0001] The present invention belongs to the technical field of clutches, and particularly relates to a method, device, equipment and medium for simulating and analyzing the strength of a clutch cover. Background Art

[0002] In a dry diaphragm spring clutch, the clutch cover is connected to the engine flywheel through bolts and is connected to the pressure plate through four groups of drive plates, playing an important role in transmitting the engine torque to the pressure plate. Moreover, a support structure for the diaphragm spring is usually designed on the clutch cover, and the clutch cover is also subjected to the thrust of the diaphragm spring. Since the stress condition of the clutch cover is complex and it is a key torque transmission component, it is necessary to design and check its strength.

[0003] Regarding the method of stress simulation analysis, in the related art, a method for simulating and calculating the clutch separation force is disclosed. The related art mainly obtains the three-dimensional model of the diaphragm spring and the three-dimensional model of the wave washer; establishes a finite element model of the clutch assembly; inputs the material characteristic parameters of the diaphragm spring and the material characteristic parameters of the wave washer into the finite element model of the clutch assembly, and simulates and calculates the clutch separation force of the clutch assembly by applying the first boundary condition to the finite element model of the clutch assembly. In the related art, the simulation calculation mainly focuses on the clutch separation force, and emphasizes the influence of the diaphragm spring and the wave washer on the separation force, while ignoring the influence of other components of the clutch on the overall performance. This limitation makes it impossible to comprehensively evaluate the strength and reliability of the clutch. The identification and analysis of the dangerous positions of each component of the clutch are not involved in the related art. In actual engineering, there may be some weak areas with stress concentration in the clutch, and these areas are prone to failure, making it difficult to ensure the reliability and safety of the clutch. Moreover, since the dangerous positions cannot be determined, it is impossible to design and improve for these weak areas, which may lead to failures in the actual use of the clutch. Summary of the Invention

[0004] The present invention provides a method for simulating and analyzing the strength of a clutch cover. By establishing a finite element model for calculating the strength of a dry diaphragm spring clutch cover, including a flywheel, a clutch cover, and connecting bolts, and by setting a stress distribution cloud chart scale and a yield strength value, the dangerous positions can be quickly identified and the maximum stress value can be obtained. Compared with the complex or inaccurate dangerous position judgment methods in the prior art, this method is simple, efficient and accurate.

[0005] The method includes: Configuring the three-dimensional models of the clutch cover, the flywheel, and the connecting bolts, and establishing a finite element model for calculating the strength of the clutch cover with the mesh type of the clutch cover and the flywheel being second-order meshes and the mesh type of the connecting bolts being first-order meshes; Define the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 in the finite element model for calculating the strength of the clutch cover; Set the degrees of freedom and loads of the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 respectively; Retrieve the stress distribution nephogram of the clutch cover three-dimensional model, and set the scale value of the stress distribution nephogram and the yield strength value of the clutch cover material; Identify the area where the yield strength exceeds the threshold in the stress distribution nephogram as the dangerous position, and determine the dangerous positions on the front and back of the clutch cover respectively, and extract the maximum value of the stress calculation results at the dangerous positions.

[0006] It should be further noted that the step of establishing the finite element model for calculating the strength of the clutch cover with the mesh type of the connecting bolts being first-order mesh also includes: Construct the three-dimensional solid models of the clutch cover and the flywheel; Perform second-order mesh division on the three-dimensional models of the clutch cover and the flywheel, and set the spatial distribution of the displacement vectors of the clutch cover and the flywheel in the three-dimensional space based on the following method:

[0007] The finite element representation of the clutch cover and the flywheel is: GQ(x,y,z)=F, where G is the overall stiffness matrix of the clutch cover and the flywheel, and F is the nodal force vector in the clutch cover and the flywheel; q0 is the basic offset of the displacement vector of the clutch cover and the flywheel in the three-dimensional space; q1, q2, and q3 are constant terms. q1 is related to the coordinate x and represents the linear change rate of the displacement vector with respect to the x coordinate; q2 is related to the coordinate y and represents the linear change rate of the displacement vector with respect to the y coordinate; q3 is related to the coordinate z and represents the linear change rate of the displacement vector with respect to the z coordinate; q4 is the change state of the square of the x coordinate of the displacement vector; q5 is the change state of the displacement vector with respect to the product of x and y; q6y 2 is the change state of the square of the displacement vector with respect to y; q7z 2 is the change state of the square of the displacement vector with respect to z; q8xz is the change state of the square of the displacement vector with respect to the product of x and z; q9yz is the change state of the square of the displacement vector with respect to the product of y and z.

[0008] It should be further noted that the method for establishing the finite element model for calculating the strength of the clutch cover with the mesh type of the connecting bolts being first-order mesh also includes: Define the displacement vector control of the bolt to represent the linear spatial distribution in the axial direction of the bolt; H(x) = p1 + p2x; Establish the stiffness matrix of the bolt GL = EM / L; E is the elastic modulus of the bolt, M is the cross-sectional area of the bolt, and L is the length of the bolt; After multiple bolts are assembled, the finite element equation of the bolt as a whole is formed, and the bolt stiffness matrix and the overall finite element equation are established based on the principle of minimum potential energy.

[0009] It should be further noted that the three-dimensional model of the step clutch cover also includes: In the finite element model for calculating the strength of the clutch cover, contact constraints are respectively defined between the clutch cover and the flywheel in the axial and radial directions, a binding constraint is defined between the bolt head and the clutch cover, a binding constraint is defined between the bolt thread part and the flywheel, and a bolt mid-surface is established at the middle part of each bolt.

[0010] It should be further noted that in the finite element model for calculating the strength of the clutch cover, the configuration at least includes material property parameters such as density, elastic modulus, and Poisson's ratio.

[0011] It should be further noted that in the method, the stress cloud chart scale is set to [0, σ , and the gray area is the dangerous position where the stress exceeds the limit; Manually or automatically select the transition fillet areas on the front and back of the clutch cover; Extract the stress values of all nodes in the transition fillet area and save them as a data set; Compare the stress values of all nodes one by one based on the following method, record and update the current maximum value;

[0012] σ n is the stress value of the n th node; Among them, all nodes in the transition fillet area are divided into multiple sub-blocks, and the maximum stress value of each block is calculated in parallel using multi-threading, and the results are finally merged.

[0013] It should be further noted that the method also includes: extracting the stress values of all nodes of the three-dimensional model of the clutch cover from the data set to form an analysis set; Set a stress value σ max1 , and assign the first stress value in the analysis set to σ m1 , as the initial maximum value estimate; Use a loop structure to start from the second stress value in the analysis set σm2 Take out each stress value in sequence σ mn ; Compare the taken-out stress value σ m1 with the currently set stress value σ max ; If the taken-out stress value σ m1 is greater than the stress value σ max1 , update the stress value σ max1 ; σ m1 ; Continue the above steps until all stress values in the entire analysis set are traversed; After the loop ends, the value stored in the stress value is the maximum value of the stress result of the three-dimensional model of the clutch cover.

[0014] This application also provides a clutch cover strength simulation analysis device, which includes: A model configuration module for configuring the three-dimensional model of the clutch cover and establishing a finite element model for calculating the strength of the clutch cover based on the second-order mesh for the clutch cover and flywheel and the first-order mesh for the connecting bolts; A set point definition module for defining the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 in the finite element model for calculating the strength of the clutch cover; A constraint setting module for setting the degrees of freedom and loads of the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 respectively; A contour map setting module for retrieving the stress distribution contour map of the three-dimensional model of the clutch cover and setting the scale value of the stress distribution contour map and the yield strength value of the clutch cover material; An analysis and identification module for identifying the area where the yield strength exceeds the threshold in the stress distribution contour map as a dangerous position, and respectively determining the dangerous positions on the front and back of the clutch cover, and extracting the maximum value of the stress calculation results at the dangerous positions.

[0015] According to another embodiment of the present application, there is provided an electronic device, including a memory, a processor, and a computer program stored on the memory and executable on the processor. When the processor executes the program, the steps of the clutch cover strength simulation analysis method are implemented.

[0016] According to another embodiment of the present application, a storage medium is further provided, on which a computer program is stored. When the computer program is executed by a processor, the steps of the clutch cover strength simulation analysis method are implemented.

[0017] As can be seen from the above technical solutions, the present invention has the following advantages: The clutch cover strength simulation analysis method provided by the present invention uses a second-order mesh and a quadratic polynomial to approximate the spatial distribution of the displacement vector, and can describe the deformation of the clutch cover and the flywheel when stressed. Compared with the linear approximation used by the first-order mesh, the second-order mesh takes into account the non-linear variation of the displacement, and can provide more accurate simulation results for complex stress distributions and deformation modes, thereby improving the accuracy of the finite element analysis.

[0018] The present invention dynamically adjusts the stress cloud map scale, sets it from 0 MPa to the yield strength, displays the over-limit area, and quickly locates dangerous positions such as transition fillets. Combining with the quadratic term distribution of the displacement vector, the stress concentration area can be predicted to avoid missing potential failure points.

[0019] The embodiments involved in the present application also focus on the clutch cover strength, covering the cooperation of multiple components and the stress analysis of dangerous positions. By setting the stress cloud map scale, dangerous positions can be intuitively identified, and the stress values are extracted in detail for the transition fillet area. Multithreaded parallel computing is used to improve efficiency. In the stress value calculation, multithreaded parallel computing and loop comparison algorithms are used to obtain the maximum value, improving the calculation efficiency and accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the technical solutions of the present invention, the drawings required to be used in the description will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0021] Figure 1 It is a schematic diagram of a finite element model for clutch cover strength calculation; Figure 2 It is a schematic diagram of a flywheel with a constraint set point; Figure 3 It is a schematic diagram of a three-dimensional model of a clutch cover with a drive plate constraint set point; Figure 4 It is a schematic diagram of a three-dimensional model of a clutch cover with a diaphragm spring constraint set point; Figure 5 It is a schematic diagram of a bolt; Figure 6 It is a flowchart of the clutch cover strength simulation analysis method; Figure 7 It is a schematic diagram of an electronic device. Specific Embodiments

[0022] The method provided in this application is a way to perform strength simulation analysis on the clutch cover as shown Figure 1 in the figure. Figure 1 The finite element model for calculating the strength of the clutch cover in the figure shows the main structure of the clutch cover 3, and also includes the flywheel 1, the bolts 2, and the interaction relationship between them. Among them, the clutch cover 3 needs to bear a certain mechanical load, and its design needs to ensure sufficient strength and stiffness to meet the requirements in actual use. The bolts are used to connect the clutch cover and the flywheel. This application needs to calculate and analyze the strength of the bolts. The flywheel and the clutch cover are fixed together through connecting parts such as bolts.

[0023] As shown Figures 2 to 4 in the figure, three constraint set points P1, P2, and P3 are set in the finite element model for calculating the strength of the clutch cover, which are located on the inner side of the flywheel, the drive plate, and the diaphragm spring respectively. These constraint set points are used to fix or restrict the movement of certain parts in the finite element analysis, so as to more accurately simulate the stress situation of the clutch cover in actual work. This setting can improve the accuracy of strength calculation.

[0024] As shown Figure 5 in the figure, the mid-plane view of the bolt 2 is shown. It is convenient to analyze the mechanical properties of the bolt and its influence on the overall structure. In the finite element analysis, factors such as the pre-tightening force and shear force of the bolt are considered, which can ensure the strength and stability of the clutch cover. The finite element model for calculating the strength of the clutch cover involved in this application provides relevant data for the design and optimization of the clutch cover through structural design and strength calculation, and can more accurately simulate the actual stress situation and evaluate the strength of the clutch cover.

[0025] The following will describe in detail the specific steps of the method for strength simulation analysis of the clutch cover. For the purpose of illustration rather than limitation, specific details such as specific system structures and technologies are proposed to thoroughly understand the embodiments of this application. However, those skilled in the art should clearly understand that this application can also be implemented in other embodiments without these specific details.

[0026] It should be understood that when used in the specification of this application, the term "comprising" indicates the existence of the described features, wholes, steps, operations, elements, and / or components, but does not exclude the existence or addition of one or more other features, wholes, steps, operations, elements, components, and / or their combinations. The terms "comprising", "including", "having" and their variants all mean "including but not limited to", unless otherwise specifically emphasized in other ways.

[0027] Statements such as "an embodiment" or "some embodiments" described in this application mean that the specific features, structures, or characteristics described in the embodiment are included in one or more embodiments of this application. Thus, statements such as "in one embodiment", "in some embodiments", "in other some embodiments", "in still other embodiments" that appear in different parts of this application do not necessarily refer to the same embodiment, but mean "one or more but not all embodiments", unless otherwise specifically emphasized in other ways.

[0028] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0029] Please refer to Figure 6 The figure shows a flowchart of a method for simulating and analyzing the strength of a clutch cover in a specific embodiment. The method includes: S101: Configure the three-dimensional models of the clutch cover, flywheel, and connecting bolts, specifically as Figure 1 shown, and establish a finite element model for calculating the strength of the clutch cover with the mesh type of the clutch cover and flywheel being second-order mesh and the mesh type of the connecting bolts being first-order mesh.

[0030] It should be noted that in this embodiment, a three-dimensional solid model of the clutch cover and flywheel is constructed, and mesh division is configured. The mesh type is set as second-order mesh, and the three-dimensional models of the clutch cover and flywheel are meshed. When meshing, according to the geometric shape, size, and analysis accuracy requirements of the model, the density and size parameters of the mesh are set to ensure that the mechanical properties of the clutch cover and flywheel can be accurately reflected.

[0031] Specifically, establishing a second-order mesh for the clutch cover and flywheel also includes: Construct a three-dimensional solid model of the clutch cover and flywheel, perform second-order mesh division on the three-dimensional models of the clutch cover and flywheel, and set the spatial distribution of the displacement vectors of the clutch cover and flywheel in three-dimensional space based on the following method:

[0032] The finite element representation of the clutch cover and flywheel is: GQ(x, y, z) = F, where G is the overall stiffness matrix of the clutch cover and flywheel, and F is the nodal force vector in the clutch cover and flywheel.

[0033] q0 is the basic offset of the displacement vector of the clutch cover and the flywheel in three-dimensional space; q1, q2, and q3 are constant terms. q1 is related to the coordinate x and represents the linear change rate of the displacement vector with respect to the x coordinate; q2 is related to the coordinate y and represents the linear change rate of the displacement vector with respect to the y coordinate; q3 is related to the coordinate z and represents the linear change rate of the displacement vector with respect to the z coordinate; q4 is the change state of the square of the x coordinate of the displacement vector; q5 is the change state of the displacement vector with respect to the product of x and y; q6y 2 is the change state of the square of the displacement vector with respect to y; q7z 2 is the change state of the square of the displacement vector with respect to z; q8xz is the change state of the square of the product of the displacement vector with respect to x and z; q9yz is the change state of the square of the product of the displacement vector with respect to y and z.

[0034] For this embodiment, the method for establishing a finite element model for calculating the strength of the clutch cover with the connection bolt mesh type being a first-order mesh further includes: Defining the displacement vector control of the bolt to be represented by the linear spatial distribution in the axial direction of the bolt; H(x) = p1 + p2x.

[0035] Establishing the stiffness matrix of the bolt GL = EM / L; E is the elastic modulus of the bolt, M is the cross-sectional area of the bolt, and L is the length of the bolt; after assembling multiple bolts, a finite element equation of the bolt as a whole is formed, and the bolt stiffness matrix and the overall finite element equation are established based on the principle of minimum potential energy.

[0036] It can be seen that this application uses a second-order mesh and uses a quadratic polynomial to approximate the spatial distribution of the displacement vector, which can describe the deformation of the clutch cover and the flywheel when stressed. Compared with the linear approximation used by the first-order mesh, the second-order mesh takes into account the non-linear change of the displacement, and can provide more accurate simulation results for complex stress distributions and deformation modes, thereby improving the accuracy of the finite element analysis.

[0037] From the attachment Figure 1 as shown, the clutch cover and the flywheel have complex geometric shapes, and the second-order mesh can better fit these complex shapes, reducing the error caused by mesh discretization. By representing the geometric shape, the model can more realistically reflect the mechanical behavior of the actual structure.

[0038] Combined with Figures 2 to 4 as shown, in the clutch cover and the flywheel, there are such as transition fillets, hole edges, etc., where stress concentration phenomena are likely to occur. The high-precision characteristics of the second-order mesh can capture the stress changes in these stress concentration regions.

[0039] In this embodiment, the displacement vector of the bolt is also controlled to be axially linearly distributed and described by a first-order linear function H(x) = p1 + p2x, which simplifies the mechanical model of the bolt. For such slender structures as bolts, in most cases, axial tensile or compressive deformation is the main mechanical behavior. Using a first-order linear model can reasonably approximate the axial mechanical characteristics of the bolt while ignoring some secondary deformation and stress components, improving the calculation efficiency and the practicality of the model on the premise of ensuring the calculation accuracy.

[0040] By establishing the stiffness matrix of the bolt GL = EM / L and establishing the bolt stiffness matrix and the overall finite element equation based on the principle of minimum potential energy, it is convenient to assemble the bolt model with the models of the clutch cover and the flywheel to form a complete finite element model, which is convenient for overall strength analysis.

[0041] S102: Define the set points of constraints P1 on the inner side of the flywheel, the set points of constraints P2 of the driving plate, and the set points of constraints P3 of the diaphragm spring in the finite element model for calculating the strength of the clutch cover.

[0042] S103: Set the degrees of freedom and loads of the set points of constraints P1 on the inner side of the flywheel, the set points of constraints P2 of the driving plate, and the set points of constraints P3 of the diaphragm spring respectively.

[0043] In this embodiment, combined with Figures 2 to 4 As shown, the established finite element model for calculating the strength of the clutch cover includes the set points of constraints P1 on the inner side of the flywheel, the set points of constraints P2 of the driving plate, and the set points of constraints P3 of the diaphragm spring. In the finite element model for calculating the strength of the clutch cover, contact constraints are established between the clutch cover and the flywheel axially and radially respectively. A binding constraint is established between the bolt head and the clutch cover, and a binding constraint is established between the threaded part of the bolt and the flywheel. A bolt mid-plane is established at the middle part of each bolt.

[0044] In the finite element model for calculating the strength of the clutch cover, this embodiment also configures the material property parameters of each part, including at least: density, elastic modulus, and Poisson's ratio.

[0045] In some specific embodiments, for the established finite element model for calculating the strength of the clutch cover, the calculation steps of the clutch cover strength may include the following specific processes: S201: Apply a small displacement of a specified size, specifically 0.01 mm, in the axial direction of the bolt mid-plane of all bolts to establish pre-contact between the clutch cover and the flywheel.

[0046] S202: Apply a specified pre-tightening force in the axial direction of the bolt mid-plane of all bolts.

[0047] S203: Apply a specified diaphragm spring acting force in the axial direction of the set point of constraints P3 of the diaphragm spring.

[0048] S204: Apply an engine torque of a specified magnitude in the axial rotation direction of the constraint set point P1 on the inner side of the flywheel.

[0049] During steps S202 to S204, apply a preset load, which varies for dry diaphragm spring clutches adapted to different engine torque magnitudes and needs to be determined according to the specific clutch model.

[0050] Define all degrees of freedom (1 to 6 degrees of freedom) of the constraint set point P1; the 1st, 2nd, and 3rd degrees of freedom respectively represent the translational degrees of freedom of the set point along the x, y, and z axes, and the 4th, 5th, and 6th degrees of freedom respectively represent the rotational degrees of freedom of the set point around the x, y, and z axes.

[0051] In step S203, constrain all degrees of freedom (1 to 6 degrees of freedom) of the constraint set point P1 and apply a fixed constraint on the mid-plane of all bolts.

[0052] In step S204, constrain the other five degrees of freedom of the constraint set point P1 except for the axial rotation, constrain the axial rotation degree of freedom of the constraint set point P2, and apply a fixed constraint on the mid-plane of all bolts.

[0053] By establishing the above finite element model for calculating the strength of the clutch cover, importing the 3D mesh model, establishing the constraint set points P1 to P3, establishing contact and binding constraints, inputting material property parameters, setting constraints and loads in each analysis step, and calculating the model in sequence according to the calculation steps S201 to S204, output the simulation result file.

[0054] It can be seen that in this embodiment, according to the characteristics of the dry diaphragm spring clutch, pre-contact, application of pre-tightening force, action of the diaphragm spring, action of the engine torque, etc. are set for the constraint set points and the mid-plane of the bolts under different working conditions in different calculation steps. The degrees of freedom are constrained and corresponding loads are applied according to the actual working conditions, and the stress state of the clutch cover in actual work can be simulated. This embodiment considers the multi-working condition characteristics of the clutch cover from establishing pre-contact to applying pre-tightening force, diaphragm spring force, and engine torque. Compared with only considering a single or a few working conditions, it can provide real strength simulation analysis results.

[0055] S104: Retrieve the stress distribution nephogram of the clutch cover 3D model and set the scale value of the stress distribution nephogram and the yield strength value of the clutch cover material; S105: Identify the area where the yield strength exceeds the threshold value in the stress distribution nephogram as the dangerous position, and respectively determine the dangerous positions on the front and back of the clutch cover, and extract the maximum value of the stress calculation result at the dangerous position.

[0056] It should be noted that after obtaining the simulation result file in this embodiment, the Mises stress distribution nephogram of the clutch cover is retrieved; the minimum value of the scale of the stress distribution nephogram is adjusted to 0 MPa, and the maximum value of the scale is adjusted to the yield strength of the clutch cover material. The positions where the Mises stress exceeds the yield strength will be displayed in gray, and the gray area is the dangerous position, usually the transition fillet area; the dangerous positions on the front and back of the clutch cover are determined respectively, and the maximum value of the stress calculation results at the dangerous positions is extracted.

[0057] In an embodiment of the present invention, based on step S105, a possible embodiment will be given below to non-restrictively elaborate on its specific implementation scheme.

[0058] In the method, the stress cloud map scale is set to [0, σ , and the gray area is the dangerous position where the stress exceeds the limit; Manually or automatically select the transition fillet areas on the front and back of the clutch cover; Extract the stress values of all nodes in the transition fillet area and save them as a data set; Based on the following method, compare the stress values of all nodes one by one, record and update the current maximum value;

[0059] σ n is the stress value of the n th node; Among them, all nodes in the transition fillet area are divided into multiple sub-blocks, and the maximum stress of each block is calculated in parallel using multi-threading, and the results are finally merged.

[0060] As an example of this application, the method further includes: extracting the stress values of all nodes of the three-dimensional model of the clutch cover from the data set to form an analysis set; Set a stress value σ max1 , and assign the first stress value in the analysis set σ m1 as the initial maximum value estimate; Use a loop structure to sequentially take out each stress value σ m2 from the second stress value σ mn in the analysis set; Compare the taken stress value σ m1 with the currently set stress value σ max ; If the taken stress value σ m1 is greater than the stress valueσ max1 , the stress value σ max1 Update the stress value σ m1 ; Continuously perform the above steps until all stress values in the entire analysis set are traversed; After the loop ends, the value stored in the stress value is the maximum value of the stress result of the three-dimensional model of the clutch cover.

[0061] It can be seen that in this application, by using second-order mesh division for the clutch cover and the flywheel, the secondary stress gradient of the transition fillet can be captured, improving the simulation accuracy. The mathematical model of the displacement vector includes linear terms and quadratic terms, which is more in line with the actual deformation law and reduces the error caused by linear assumptions.

[0062] By dynamically adjusting the scale of the stress cloud diagram and setting it from 0 MPa to the yield strength, the over-limit area is displayed to quickly locate dangerous positions such as transition fillets. Combining with the quadratic term distribution of the displacement vector, the stress concentration area can be predicted to avoid missing potential failure points.

[0063] The embodiments involved in this application also focus on the strength of the clutch cover, covering the cooperation of multiple components and the stress analysis of dangerous positions. By setting the scale of the stress cloud diagram, dangerous positions can be intuitively identified, and stress values are extracted in detail for the transition fillet area. Multithreaded parallel computing is used to improve efficiency. In the calculation of stress values, multithreaded parallel computing and loop comparison algorithms are used to obtain the maximum value, improving the calculation efficiency and accuracy.

[0064] It should be understood that the magnitudes of the sequence numbers of the steps in the above embodiments do not mean the order of execution. The execution order of each process should be determined according to its function and internal logic, and should not constitute any limitation to the implementation process of the embodiments of the present invention.

[0065] The following are embodiments of the clutch cover strength simulation analysis device provided by the embodiments of the present disclosure. This device belongs to the same inventive concept as the clutch cover strength simulation analysis method in the above embodiments. For the details not described in detail in the embodiments of the clutch cover strength simulation analysis device, reference can be made to the embodiments of the clutch cover strength simulation analysis method.

[0066] The device includes: A model configuration module, used to configure the three-dimensional model of the clutch cover and establish a finite element model for calculating the strength of the clutch cover with a second-order mesh for the clutch cover and the flywheel and a first-order mesh for the connecting bolts; A set point definition module, used to define the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 in the finite element model for calculating the strength of the clutch cover; A constraint setting module for separately setting the degrees of freedom and loads of the inner flywheel constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3. A contour map setting module for retrieving the stress distribution contour map of the clutch cover three-dimensional model and setting the scale value of the stress distribution contour map and the yield strength value of the clutch cover material. An analysis and identification module for identifying the area where the yield strength exceeds the threshold value in the stress distribution contour map as a dangerous position, respectively determining the dangerous positions on the front and back of the clutch cover, and extracting the maximum value of the stress calculation results at the dangerous positions.

[0067] The clutch cover strength simulation analysis device involved herein can adopt a combination of second-order and first-order meshes according to the different mechanical properties and structural characteristics of the clutch cover, flywheel, and connecting bolts. This differential mesh division method is more in line with the actual situation, improves the analysis accuracy while controlling the calculation cost. By setting the stress distribution contour map scale and yield strength value, the dangerous position can be quickly identified and the maximum stress value can be obtained. Compared with the complex or inaccurate dangerous position judgment methods in the prior art, this method is simple, efficient, and accurate. In this embodiment, a finite element model is established considering the interaction of the clutch cover, flywheel, and connecting bolts, and the strength of the clutch cover is analyzed from the perspective of the overall system. Different from the prior art that may only analyze individual components separately, this multi-component collaborative analysis can more truly reflect the actual working state of the product.

[0068] As Figure 7 shown, the present application also provides an electronic device, including a display module 103, a memory 102, a processor 101, and a computer program stored on the memory and executable on the processor 101. When the processor 101 executes the program, the steps of the clutch cover strength simulation analysis method are implemented.

[0069] In the embodiments of the present invention, the electronic device includes, but is not limited to, a laptop computer, a desktop computer, a workbench, a personal digital assistant, a server, a blade server, a mainframe computer, and other suitable computers. The electronic device can also represent various forms of mobile devices, such as, a personal digital processor, a cellular phone, a smart phone, a wearable device, and other similar computing devices. The components shown herein, their connections and relationships, and their functions are only examples and are not intended to limit the implementation of the embodiments of the present application described herein and / or claimed.

[0070] In the embodiments of the present application, the processor 101 may be implemented by using at least one of an application specific integrated circuit (ASIC), a programmable logic device (PLD), a field programmable gate array (FPGA), a processor, a controller, a microcontroller, a microprocessor, and an electronic unit designed to execute the functions described herein. In some cases, such an implementation may be implemented in the controller. For a software implementation, an implementation of a process or function may be implemented with a separate software module that permits execution of at least one function or operation. The software code may be implemented by a software application (or program) written in any suitable programming language. The software code may be stored in a memory and executed by the controller.

[0071] The display module 103 is configured to display information input by the user or information provided to the user. The display module 103 may include a display panel, and the display panel may be configured in the form of, for example, a liquid crystal display (LCD), an organic light-emitting diode (OLED), or the like.

[0072] The memory 102 may be used to store software programs and various data. The memory 102 may include a high-speed random access memory, and may further include a non-volatile memory, such as at least one magnetic disk storage device, a flash memory device, or other volatile solid-state storage devices.

[0073] The present application further provides a storage medium, on which a computer program is stored. When the computer program is executed by a processor, the steps of the clutch cover strength simulation analysis method are implemented.

[0074] The storage medium may be any combination of one or more readable media. The readable media may be a readable signal medium or a readable storage medium. The readable storage medium may, for example, but is not limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination of the above. More specific examples (a non-exhaustive list) of the readable storage medium include: an electrical connection having one or more wires, a portable disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above.

[0075] The foregoing description of the disclosed embodiments enables those skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A method for simulating and analyzing the strength of a clutch cover, characterized in that the method Including: Configure the three-dimensional models of the clutch cover, flywheel, and connecting bolts, and establish a finite element model for calculating the strength of the clutch cover based on the second-order mesh for the clutch cover and flywheel and the first-order mesh for the connecting bolts; Define the set point P1 of the inner side of the flywheel constraint, the set point P2 of the driving plate constraint, and the set point P3 of the diaphragm spring constraint in the finite element model for calculating the strength of the clutch cover; Set the degrees of freedom and loads of the set point P1 of the inner side of the flywheel constraint, the set point P2 of the driving plate constraint, and the set point P3 of the diaphragm spring constraint respectively; Retrieve the stress distribution nephogram of the three-dimensional model of the clutch cover, and set the scale value of the stress distribution nephogram and the yield strength value of the clutch cover material; Identify the area where the yield strength exceeds the threshold value in the stress distribution nephogram as the dangerous position, and determine the dangerous positions on the front and back of the clutch cover respectively, and extract the maximum value of the stress calculation results at the dangerous positions.

2. The method for simulating and analyzing the strength of the clutch cover according to claim 1, wherein The step of establishing a finite element model for calculating the strength of the clutch cover based on the second-order mesh for the clutch cover and flywheel further includes: Construct three-dimensional solid models of the clutch cover and flywheel; Perform second-order mesh division on the three-dimensional models of the clutch cover and flywheel, and set the spatial distribution of the displacement vectors of the clutch cover and flywheel in three-dimensional space based on the following method: The finite element representation of the clutch cover and flywheel is: GQ(x, y, z)=F, where G is the overall stiffness matrix of the clutch cover and flywheel, and F is the nodal force vector in the clutch cover and flywheel; q0 is the basic offset of the displacement vector of the clutch cover and flywheel in three-dimensional space; q1, q2, and q3 are constant terms. q1 is related to the coordinate x and represents the linear change rate of the displacement vector with respect to the x coordinate; q2 is related to the coordinate y and represents the linear change rate of the displacement vector with respect to the y coordinate; q3 is related to the coordinate z and represents the linear change rate of the displacement vector with respect to the z coordinate; q4 is the change state of the square of the x coordinate of the displacement vector; q5 is the change state of the displacement vector with respect to the product of x and y; q6y 2 is the variation state of the displacement vector with the square of y; q7z 2 is the variation state of the displacement vector with the square of z; q8xz is the change state of the square of the product of x and z of the displacement vector; q9yz is the change state of the square of the product of y and z of the displacement vector.

3. The method for simulating and analyzing the strength of the clutch cover according to claim 1, wherein The method for establishing a finite element model for calculating the strength of the clutch cover with the first-order mesh for the connecting bolts in the step further includes: Define that the displacement vector of the bolt is controlled by the linear spatial distribution representation in the axial direction of the bolt; H(x)=p1 + p2x; Establish the stiffness matrix of the bolt GL = EM / L; E is the elastic modulus of the bolt, M is the cross-sectional area of the bolt, and L is the length of the bolt; After assembling multiple bolts, form the finite element equation of the bolt as a whole, and establish the bolt stiffness matrix and the overall finite element equation based on the principle of minimum potential energy.

4. The method for simulating and analyzing the strength of the clutch cover according to claim 1, wherein The three-dimensional model of the clutch cover in the step further includes: In the finite element model for the strength calculation of the clutch cover, contact constraints are respectively defined between the clutch cover and the flywheel in the axial and radial directions. A bonded constraint is defined between the bolt head and the clutch cover, and a bonded constraint is defined between the bolt thread part and the flywheel. Also, a bolt mid-plane is established at the middle part of each bolt.

5. The method for simulating and analyzing the strength of the clutch cover according to claim 1, characterized in that In the finite element model for the strength calculation of the clutch cover, the configured material property parameters at least include: density, elastic modulus, and Poisson's ratio.

6. The method for simulating and analyzing the strength of the clutch cover according to claim 1, characterized in that In the method, set the stress cloud chart scale to [0, σ , and the gray area is the dangerous position where the stress exceeds the limit; Manually or automatically select the transition fillet regions on the front and back of the clutch cover; Extract the stress values of all nodes within the transition fillet regions and save them as a data set; Compare the stress values of all nodes one by one based on the following method, record and update the current maximum value; σ n is the stress value of the n th node; Among them, all nodes within the transition fillet regions are divided into multiple sub-blocks, and the maximum stress value of each block is calculated in parallel using multi-threading, and finally the results are merged.

7. The method for simulating and analyzing the strength of the clutch cover according to claim 6, characterized in that The method further includes: extracting the stress values of all nodes of the three-dimensional model of the clutch cover from the data set to form an analysis set; Set a stress value σ max1 , and assign the first stress value in the analysis set σ m1 as the initial maximum value estimate; Using a loop structure, starting from the second stress value in the analysis set σ m2 , sequentially extract each stress value σ mn ; The extracted stress value σ m1 is compared with the currently set stress value σ max ; If the stress value taken out σ m1 is greater than the stress value σ max1 , then the stress value σ max1 Update the stress value σ m1 ; Continuously perform the above steps until all stress values in the entire analysis set are traversed; After the loop ends, the value stored in the stress values is the maximum value of the stress result of the three-dimensional model of the clutch cover.

8. An apparatus for simulating and analyzing the strength of a clutch cover, characterized in that, The device is used to implement the method for simulating and analyzing the strength of the clutch cover according to any one of claims 1 to 7; the device includes: A model configuration module, used to configure the three-dimensional model of the clutch cover and establish a finite element model for the strength calculation of the clutch cover based on a second-order mesh for the clutch cover and the flywheel and a first-order mesh for the connecting bolts; A set point definition module, used to define the flywheel inner side constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 in the finite element model for the strength calculation of the clutch cover; A constraint setting module, used to set the degrees of freedom and loads of the flywheel inner side constraint set point P1, the drive plate constraint set point P2, and the diaphragm spring constraint set point P3 respectively; A contour map setting module, used to retrieve the stress distribution contour map of the three-dimensional model of the clutch cover and set the scale value of the stress distribution contour map and the yield strength value of the clutch cover material; An analysis and identification module, used to identify the region where the yield strength exceeds the threshold value in the stress distribution contour map as a dangerous position, and respectively determine the dangerous positions on the front and back of the clutch cover, and extract the maximum value of the stress calculation results at the dangerous positions.

9. An electronic device, comprising a memory, a processor, and a computer program stored on the memory and executable on the processor, characterized in that, When the processor executes the program, it implements the steps of the method for simulating and analyzing the strength of the clutch cover according to any one of claims 1 to 7.

10. A storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by the processor, it implements the steps of the method for simulating and analyzing the strength of the clutch cover according to any one of claims 1 to 7.

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