Plate spring system strength optimization method and device, terminal and medium
Through finite element simulation and pressure plate structure optimization, the problem of failure of the leaf spring center hole is solved, the vehicle's operating safety and handling performance are improved, and the operation and maintenance costs are reduced.
Patent Information
- Application Number
- CN202510118596.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-01-24
- Publication Date
- 2025-05-09
AI Technical Summary
The failure problem of the central hole of the leaf spring is more common in leaf spring systems, resulting in the attenuation of the preload force of the U-bolt, affecting the normal operation of the suspension system. Existing solutions such as the use of higher-strength leaf springs or the increase in tightening torque have the impact of the handling performance and the risk of bolt breakage.
Through finite element simulation, a simulation model of the leaf spring system is established, the stress of the leaf spring center hole in different states is calculated, the elastic modulus and cross-sectional moment of inertia of the pressure plate are adjusted, and the strength of the leaf spring system is optimized to reduce the probability of the center hole failure.
It effectively reduces the probability of failure of the central hole of the leaf spring, improves the safety and handling performance of the vehicle, and reduces operation and maintenance costs.
Smart Images
Figure CN119962312A_ABST
Abstract
Description
Technical Field
[0001] The present invention belongs to the field of vehicles, and in particular relates to a leaf spring system strength optimization method, device, terminal and medium. Background Art
[0002] The leaf spring system is the main load-bearing and buffering component of the vehicle suspension system, and its performance directly affects the driving safety and comfort of the vehicle. The entire leaf spring system contains multiple important components, such as the pressure plate, leaf spring assembly, axle housing, U-bolts, etc. They work together to bear the various loads borne by the vehicle during driving, including impact from the road, the weight of the vehicle itself, and the inertia force generated during acceleration, deceleration and steering. Among them, the center hole of the leaf spring is a key part in the leaf spring system. It is subjected to a complex stress state. Once a failure occurs, it will have a serious impact on the normal operation of the entire suspension system.
[0003] In actual vehicle use and after-sales maintenance, it is found that the failure of the center hole of the leaf spring accounts for a high proportion of all leaf spring system failure problems. The occurrence of the center hole failure of the leaf spring is usually accompanied by a significant attenuation of the U-bolt preload, which may be caused by a variety of factors. For example, the vehicle has been driving in harsh road conditions for a long time and is constantly subjected to strong vibration and impact, which gradually reduces the U-bolt preload and causes the stress in the center hole of the leaf spring to change. After the center hole of the leaf spring fails, it is often impossible to solve it through simple repairs. The leaf spring needs to be replaced, which not only increases the downtime of the vehicle and affects the normal use of the user, but also greatly increases the after-sales maintenance costs.
[0004] At present, there are several solutions to solve the problem of center hole failure: 1. Use higher strength leaf springs; 2. Increase the tightening torque and add anti-loosening measures, requiring users to re-tighten regularly according to time nodes. However, using higher strength leaf springs will affect the vehicle's handling performance, and increasing the tightening torque requires higher strength for the U-bolts, which can easily cause the bolts to break. Summary of the invention
[0005] To solve the above problems, the present invention provides a leaf spring system strength optimization method, device, terminal and medium. Combined with finite element simulation, the stress in the center hole of the leaf spring is reduced by increasing the stiffness of the leaf spring pressure plate, thereby solving the problem of leaf spring center hole fracture, improving vehicle operation safety and reducing operation and maintenance costs.
[0006] In a first aspect, the technical solution of the present invention provides a leaf spring system strength optimization method, comprising the following steps: Step 1, establishing a leaf spring system simulation model in finite element simulation software; Step 2, converting the specified U-bolt tightening torque into the U-bolt axial preload; Step 3, according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, the leaf spring system simulation model is simulated and calculated, and the stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read, and recorded as the first leaf spring center hole stress; Step 4, attenuating the axial preload of the U-bolt, and then re-performing the step of simulating and calculating the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, reading the stress of the center hole of the leaf spring after the axial preload of the U-bolt is attenuated, and recording it as the stress of the center hole of the second leaf spring; Step 5, adjusting the elastic modulus of the pressing plate so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and recording the elastic modulus of the pressing plate before and after the adjustment; Step 6, adjusting the height of the pressure plate section so that the increase in the moment of inertia of the pressure plate section is the same as the increase in the elastic modulus of the pressure plate recorded in step 5 before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0007] In an optional implementation, step 2 converts the specified U-bolt tightening torque into the U-bolt axial preload, specifically comprising: Refer to relevant standards and determine the tightening torque of the U-bolt according to the corresponding U-bolt strength and diameter; Calculate the axial preload of the U-bolt according to the following formula:
[0008] in, is the tightening torque of the U-bolt, is the torque coefficient, is the axial preload of the U-bolt, It is the basic dimension of the major diameter of the external thread of the U-bolt.
[0009] In an optional implementation, step 5 specifically includes: Step 5.1, record the initial platen elastic modulus corresponding to the stress of the center hole of the first leaf spring ; Step 5.2, adjusting the elastic modulus of the pressure plate in a stepwise iterative manner to change the stress of the center hole of the second leaf spring; Step 5.2.1, determine the initial iteration step size ; Step 5.2.2, perform the first iteration: Update the platen elastic modulus to , and substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation; Step 5.2.3, reading the updated stress of the center hole of the second leaf spring; Step 5.2.4, compare the updated stress of the center hole of the second leaf spring with the stress of the center hole of the first leaf spring. If the updated stress of the center hole of the second leaf spring is greater than the stress of the center hole of the first leaf spring, change the iteration step size to , update the elastic modulus of the pressure plate to ; If the updated stress of the second leaf spring center hole is less than the stress of the first leaf spring center hole, keep the iteration step size , update the elastic modulus of the pressure plate to ; Substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation, and so on until the conditions of step 5.3 are met; Step 5.3, when the stress in the center hole of the second leaf spring is the same as the stress in the center hole of the second leaf spring, record the elastic modulus of the pressure plate at this time .
[0010] In an optional implementation, step 6 specifically includes: Calculate the elastic modulus of the platen before adjusting the platen section height The corresponding moment of inertia of the platen section ; Maintain initial platen elastic modulus No change, adjust the height of the pressure plate section and recalculate the moment of inertia of the pressure plate section , so that the optimized platen section moment of inertia Satisfies the following formula,
[0011] Based on the moment of inertia of the platen section The specific value of the height of the pressure plate section can be determined by using formula (2).
[0012] In an optional embodiment, the elastic modulus of the press plate before adjusting the height of the press plate section is calculated. The corresponding moment of inertia of the platen section , including: Get the initial platen height , initial height of the middle hollow area and the length of the middle hollow area ; The height of the centroid of the initial cross section of the platen along the Z axis is calculated by the following formula ,
[0013] The initial cross-sectional area of the platen is calculated by the following formula ,
[0014] The moment of inertia of the platen section is calculated by the following formula , .
[0015] In an optional embodiment, the height of the pressure plate section is adjusted to recalculate the moment of inertia of the pressure plate section. , including: Note that the thickness of the pressure plate to be increased is ; Get the optimized height of the hollow area in the middle after adjusting the thickness of the pressure plate ; The height of the centroid of the optimized cross section of the pressure plate along the Z axis is calculated by the following formula ,
[0016] The optimized cross-sectional area of the pressure plate is calculated by the following formula ,
[0017] The moment of inertia of the platen section is calculated by the following formula , .
[0018] In an optional implementation, in step 4, the axial preload force of the U-bolt is attenuated at a ratio of 25% attenuation of the preload force.
[0019] In a second aspect, the technical solution of the present invention provides a leaf spring system strength optimization device, comprising: A preload conversion module, used to convert the specified U-bolt tightening torque into the U-bolt axial preload; The first leaf spring center hole stress reading module is used to perform simulation calculation on the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, and read the stress of the center hole of the leaf spring before the axial preload of the U-bolt is attenuated, which is recorded as the first leaf spring center hole stress; The second leaf spring center hole stress reading module is used to attenuate the axial preload force of the U-bolt, and then re-execute the step of simulating and calculating the leaf spring system simulation model according to the axial preload force of the U-bolt and the maximum vertical load of the leaf spring, and read the stress of the center hole of the leaf spring after the axial preload force of the U-bolt is attenuated, which is recorded as the second leaf spring center hole stress; A pressing plate elastic modulus adjustment module, used to adjust the pressing plate elastic modulus so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and record the elastic modulus of the pressing plate before and after the adjustment; The pressure plate section height adjustment module is used to adjust the pressure plate section height so that the increase in the pressure plate section inertia moment is the same as the increase in the recorded pressure plate elastic modulus before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0020] In a third aspect, the technical solution of the present invention provides a terminal, including: A memory for storing a leaf spring system strength optimization program; A processor is used to implement the steps of the leaf spring system strength optimization method as described in any of the above items when executing the leaf spring system strength optimization program.
[0021] In a fourth aspect, the technical solution of the present invention provides a computer-readable storage medium, on which a leaf spring system strength optimization program is stored. When the leaf spring system strength optimization program is executed by a processor, the steps of the leaf spring system strength optimization method as described in any of the above items are implemented.
[0022] A leaf spring system strength optimization method, device, terminal and medium provided by the present invention have the following beneficial effects compared with the prior art: by establishing a leaf spring system simulation model, the stress of the center hole of the leaf spring under different states (the axial preload of the U-bolt is not attenuated and attenuated) is accurately simulated and calculated, and the elastic modulus and section inertia moment of the pressure plate are adjusted according to the calculation results, and then the section height of the pressure plate is adjusted to optimize the strength of the leaf spring system, fundamentally improving the stress condition of the center hole of the leaf spring, reducing the probability of failure of the center hole, and reducing the need for leaf spring replacement due to center hole failure, thereby improving vehicle operation safety, avoiding affecting the vehicle's handling performance and the risk of U-bolt breakage, and reducing operating and maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS In order to more clearly illustrate the technical solution of the present invention, the drawings required for use in the description will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.
[0023] Figure 1 A schematic flow chart of a leaf spring system strength optimization method provided in an embodiment of the present invention.
[0024] Figure 2 Schematic diagram of the middle section dimensions of the pressure plate before adjusting the height of the pressure plate section.
[0025] Figure 3 Schematic diagram of the middle section dimensions of the pressure plate after adjusting the height of the pressure plate section.
[0026] Figure 4 A schematic block diagram of the structure of a leaf spring system strength optimization device provided in an embodiment of the present invention.
[0027] Figure 5 A schematic diagram of the structure of a terminal provided by an embodiment of the present invention. DETAILED DESCRIPTION
[0028] In order to make the purpose, features and advantages of the present invention more obvious and easy to understand, the technical scheme of the present invention will be clearly and completely described below in conjunction with the drawings in this specific embodiment. Obviously, the embodiments described below are only part of the embodiments of the present invention, not all of them. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.
[0029] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used in the specification of the present invention herein are only for the purpose of describing specific embodiments and are not intended to limit the present invention.
[0030] Figure 1 A schematic diagram of a leaf spring system strength optimization method provided by an embodiment of the present invention. Figure 1 The execution subject may be a leaf spring system strength optimization system. The leaf spring system strength optimization method provided in the embodiment of the present invention is executed by a computer device, and accordingly, the leaf spring system strength optimization system runs in the computer device. According to different requirements, the order of the steps in the flowchart can be changed, and some can be omitted.
[0031] like Figure 1 As shown, the method includes the following steps.
[0032] S1, establish a leaf spring system simulation model in the finite element simulation software.
[0033] The leaf spring system simulation model at least includes: leaf spring, pressure plate, gasket, U-bolt, balance shaft housing, and the components are in contact with each other and fixed together by U-bolts. First, according to the geometric shape, size and material properties of the actual leaf spring system, a geometric model of the leaf spring system is created in the selected finite element simulation software (such as ANSYS, ABAQUS, etc.). For each component in the leaf spring system, including the pressure plate, leaf spring assembly, shaft housing, U-bolt, etc., its three-dimensional geometric information needs to be accurately input. For example, accurately describe the length, width, thickness, curvature of the leaf spring leaf of the leaf spring assembly and the contact relationship between each leaf; consider the geometric parameters such as the shape, size, wall thickness of the shaft housing; input the diameter, length, threaded part size and U-shaped part size of the U-bolt bolt rod.
[0034] Based on geometric modeling, the corresponding material properties are assigned to each component. According to the actual materials used, the leaf spring is assigned physical parameters such as elastic modulus, Poisson's ratio, density, and yield strength to accurately simulate the deformation and stress response of the leaf spring under stress. For the pressure plate, the elastic modulus, Poisson's ratio, and density of the material are input. These parameters affect the deformation of the pressure plate under stress and the constraint effect on the leaf spring. At the same time, the shaft housing and U-bolts need to be assigned appropriate material properties to ensure that their mechanical properties are accurately reflected in the simulation.
[0035] Model the connection relationship between the components in the leaf spring system. This includes defining appropriate constraints to define the installation relationship between the leaf spring assembly and the axle housing, thereby simulating the connection method during actual installation. When defining the connection between the U-bolt and the leaf spring assembly, consider the application method of the bolt preload. You can define a bolt connection unit and convert it into an axial preload based on the actual tightening torque. At the same time, consider the contact and friction between the bolt and the leaf spring to simulate the impact of friction and bolt preload on the leaf spring system during actual installation.
[0036] According to the actual usage scenario, the installation position and stress conditions of the leaf spring system on the vehicle are determined, and boundary constraints are applied to the corresponding nodes or surfaces. For example, at the installation point of the leaf spring system, fixed constraints need to be applied or displacement constraints need to be applied according to the actual situation to simulate the installation and support of the leaf spring system on the vehicle frame during vehicle driving. At the same time, for possible load application positions, corresponding nodes or surfaces should be reserved so that external loads such as the maximum vertical load of the leaf spring can be accurately applied later.
[0037] The leaf spring system simulation model established in this embodiment will serve as the basis for subsequent simulation calculations and optimizations, providing reliable model support for accurate evaluation and optimization of the leaf spring system strength, and ensuring that subsequent simulation results can truly reflect the performance of the leaf spring system under actual working conditions.
[0038] S2, converts the specified U-bolt tightening torque into the U-bolt axial preload.
[0039] This embodiment converts the tightening torque of the U-bolt into the axial pre-tightening force of the U-bolt, and the tightening torque is determined according to the corresponding bolt strength grade and diameter in reference to GB / T3098.9. The specific steps include the following steps.
[0040] S2.1, refer to relevant standards and determine the U-bolt tightening torque based on the corresponding U-bolt strength and diameter.
[0041] An optional implementation method refers to the standard GB / T3098.9, which defines the U-bolt tightening torque corresponding to different U-bolt strengths and diameters. The corresponding information can be found in the standard according to the actual strength grade (such as grade 8.8, grade 10.9, etc.) and the basic size of the major diameter of the external thread.
[0042] S2.2, calculate the axial preload of the U-bolt according to the following formula:
[0043] in, is the tightening torque of the U-bolt, is the torque coefficient, is the axial preload of the U-bolt, It is the basic dimension of the major diameter of the external thread of the U-bolt.
[0044] In some embodiments, the torque coefficient The value range is generally 0.15 to 0.2. The torque coefficient is affected by many factors, including the roughness of the thread surface, lubrication conditions, materials and surface treatment of the connecting parts. In practical applications, if the surface of the connecting parts of the U-bolt and leaf spring system is smooth and appropriate lubricants are used, the torque coefficient may be closer to 0.15; if the surface of the connecting parts is rough or no lubricant is used, the torque coefficient may be closer to 0.2.
[0045] S3: According to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, the leaf spring system simulation model is simulated and calculated, and the stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read, which is recorded as the first leaf spring center hole stress. .
[0046] This step will be based on the preload force determined above. , combined with the maximum vertical load of the leaf spring, applied to the finite element model for simulation calculation. In some embodiments, the maximum vertical load of the leaf spring is twice the axle load of the drive axle. The stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read through simulation calculation and recorded as the first center hole stress of the leaf spring. The first center hole stress of the leaf spring is used as the subsequent optimization target.
[0047] Specifically, the axial preload of the U-bolt and the maximum vertical load of the leaf spring are first determined, and the determined conditions are used as the input conditions of the solver of the finite element simulation software. The solver of the finite element simulation software is executed, and the entire leaf spring system is divided into many small units according to the geometric model, material properties, boundary conditions (including preload and vertical load) and unit type of the leaf spring system, and the equation group is established according to the mechanical principles. After the simulation calculation is completed, the area where the center hole of the leaf spring is located is found from the simulation results through the geometric information when the leaf spring system simulation model was established previously. Since the position of the center hole of the leaf spring is clear, its position in the entire leaf spring system can be determined by the node number, unit number or geometric coordinate range. For example, the range of nodes or units around the center hole can be determined according to the geometric size of the leaf spring and the size of the center hole.
[0048] After locating the center hole area of the leaf spring, the stress data of the area is extracted. It should be noted that stress is usually presented in the form of node stress or unit stress in the finite element results, including different stress components, such as normal stress (axial stress, radial stress, hoop stress) and shear stress. For reading the stress of the center hole of the leaf spring, a suitable stress index can be selected according to the specific failure criterion. For example, the maximum principal stress, equivalent stress (von Mises stress) or normal stress in a certain direction at the center hole is selected as the representative stress. The read stress data is recorded as the first leaf spring center hole stress, which reflects the stress state of the center hole of the leaf spring when the axial preload of the U-bolt is not attenuated and the leaf spring is subjected to the maximum vertical load. The first leaf spring center hole stress serves as the basis for subsequent comparison and optimization work to evaluate the stress changes and potential failure risks of the center hole of the leaf spring under different working conditions.
[0049] S4, attenuating the axial preload force of the U-bolt, and then re-performing the step of simulating and calculating the leaf spring system simulation model according to the axial preload force of the U-bolt and the maximum vertical load of the leaf spring, reading the stress of the center hole of the leaf spring after the axial preload force of the U-bolt is attenuated, and recording it as the stress of the center hole of the second leaf spring .
[0050] First, determine the preload attenuation ratio, then attenuate the preload, and perform the simulation calculation in step S3 again based on the attenuated preload to obtain the stress of the leaf spring center hole in the current state. In an optional implementation, the preload is attenuated by 25% to obtain a preload of 0.75 It should be noted that the specific attenuation rate can be verified through experiments.
[0051] S5, adjusting the elastic modulus of the pressing plate so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and recording the elastic modulus of the pressing plate before and after the adjustment.
[0052] According to the bending stiffness formula ,in is the elastic modulus, is the section moment of inertia, is the bending moment, is the radius of curvature. Let the initial elastic modulus be , the initial section moment of inertia of the platen is By adjusting the elastic modulus of the pressure plate, the required stiffness of the pressure plate can be quickly verified, and the stress of the center hole can reach When the elastic modulus is . Specifically include the following steps.
[0053] S5.1, record the initial platen elastic modulus corresponding to the stress of the center hole of the first leaf spring .
[0054] In the previous simulation calculation step, the stress of the center hole of the first leaf spring has been obtained, and the leaf spring system is in the initial state at this time, and the corresponding elastic modulus of the pressure plate is the initial elastic modulus. Record it as a basis for subsequent adjustments.
[0055] S5.2, adjusting the elastic modulus of the pressure plate by a stepwise iteration method to change the stress in the center hole of the second leaf spring.
[0056] S5.2.1, Determine the initial iteration step size The size of this step determines the amplitude of each adjustment of the elastic modulus of the pressure plate. The choice of step size can be based on experience and preliminary judgment of the leaf spring system. Generally, a smaller value can be selected to ensure the accuracy and stability of the adjustment process. For example, As the initial step length, it is understandable that the specific value can be adjusted according to the actual situation.
[0057] S5.2.2, perform the first iteration: Update the platen elastic modulus to , and substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation. In the finite element simulation software, find the material property setting section of the pressure plate and modify the original elastic modulus to .
[0058] Using the modified platen elastic modulus As well as other previously determined boundary conditions (such as the axial preload of the U-bolt and the maximum vertical load of the leaf spring), the leaf spring system simulation model is simulated and calculated. The calculation process is the same as before, calling the solver of the finite element software to solve the mechanical response of the updated leaf spring system under this elastic modulus.
[0059] S5.2.3, read the updated stress in the center hole of the second leaf spring.
[0060] After the simulation calculation is completed, the stress of the center hole of the second leaf spring is read from the simulation results and recorded as .
[0061] S5.2.4, compare the updated stress of the second leaf spring center hole with the stress of the first leaf spring center hole. If the updated stress of the second leaf spring center hole is greater than the stress of the first leaf spring center hole, change the iteration step size to , update the elastic modulus of the pressure plate to ; If the updated stress of the second leaf spring center hole is less than the stress of the first leaf spring center hole, keep the iteration step size , update the elastic modulus of the pressure plate to ; Substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation, and so on until the conditions of step S5.3 are met.
[0062] Specifically, compare and If the size > , indicating that the currently adjusted elastic modulus causes the stress in the center hole of the second leaf spring to be too large, and the elastic modulus needs to be reduced. At this time, the step length is changed to (i.e. reverse adjustment), and update the elastic modulus of the pressure plate to , and then repeat the above simulation calculation and stress reading steps. < , indicating that the currently adjusted elastic modulus makes the stress in the center hole of the second leaf spring too small, and the elastic modulus needs to be further increased. At this time, continue to maintain the step length of , update the elastic modulus of the pressure plate to , and repeat the above simulation calculation and stress reading steps.
[0063] Repeat the above process of updating elastic modulus, re-simulating, reading stress and judging until Less than the set error tolerance (n is the number of iterations). The allowable error range is set according to actual needs. For example, you can set , indicating that when the difference between the stress of the center hole of the second leaf spring and the stress of the center hole of the first leaf spring is within 1% of the stress of the center hole of the first leaf spring, the two are considered to be basically consistent.
[0064] S5.3, when the stress in the center hole of the second leaf spring is the same as the stress in the center hole of the second leaf spring, record the elastic modulus of the pressure plate at this time .
[0065] During the iteration process, when When the condition is met, it means that by gradually adjusting the elastic modulus of the pressure plate, the stress of the center hole of the second leaf spring has been made basically equal to the stress of the center hole of the first leaf spring. At this time, the current elastic modulus of the pressure plate is recorded as This final elastic modulus It is the elastic modulus found through iterative adjustment that can make the stress of the center hole of the second leaf spring consistent with the stress of the center hole of the first leaf spring.
[0066] The elastic modulus of the pressure plate is adjusted in a step-by-step iterative manner to make the stress in the center hole of the second leaf spring consistent with the stress in the center hole of the first leaf spring, and the elastic modulus of the pressure plate before and after adjustment is recorded to provide important data support for the subsequent strength optimization of the leaf spring system.
[0067] S6, adjusting the height of the pressure plate section so that the increase in the moment of inertia of the pressure plate section is the same as the increase in the elastic modulus of the pressure plate recorded in step S5 before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0068] S6.1, calculate the elastic modulus of the platen before adjusting the platen section height The corresponding moment of inertia of the platen section .
[0069] Figure 2 To adjust the height of the platen before the middle section of the platen is adjusted, first obtain the initial platen height , initial height of the middle hollow area and the length of the middle hollow area ; Then calculate the height of the initial cross-section centroid of the platen along the Z axis using the following formula: ,
[0070] The initial cross-sectional area of the platen is calculated by the following formula ,
[0071] The moment of inertia of the platen section is calculated by the following formula ,
[0072] S6.2, maintain the initial platen elastic modulus No change, adjust the height of the pressure plate section and recalculate the moment of inertia of the pressure plate section , so that the optimized platen section moment of inertia Satisfies the following formula,
[0073] Figure 3To adjust the height of the pressure plate, the middle section of the pressure plate is shown in the figure. First, the thickness of the pressure plate to be increased is Then get the optimized height of the hollow area in the middle after adjusting the thickness of the pressure plate , and then calculate the height of the centroid of the optimized section of the pressure plate along the Z axis using the following formula: ,
[0074] The optimized cross-sectional area of the pressure plate is calculated by the following formula ,
[0075] The moment of inertia of the platen section is calculated by the following formula ,
[0076] From formulas (4), (5), and (8), we can get the required height of the pressure plate section: The specific value of .
[0077] An embodiment of a leaf spring system strength optimization method is described in detail above. Based on the leaf spring system strength optimization method described in the above embodiment, an embodiment of the present invention further provides a leaf spring system strength optimization device corresponding to the method.
[0078] Figure 4 A schematic block diagram of the structure of a leaf spring system strength optimization device provided in an embodiment of the present invention. In this embodiment, the leaf spring system strength optimization device 400 can be divided into multiple functional modules according to the functions it performs. The module referred to in the present invention refers to a series of computer program segments that can be executed by at least one processor and can complete fixed functions, which are stored in a memory.
[0079] A preload conversion module 410, for converting a prescribed U-bolt tightening torque into an axial preload of the U-bolt; The first leaf spring center hole stress reading module 420 is used to perform simulation calculation on the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, and read the stress of the center hole of the leaf spring before the axial preload of the U-bolt is attenuated, which is recorded as the first leaf spring center hole stress; The second leaf spring center hole stress reading module 430 is used to attenuate the axial preload force of the U-bolt, and then re-execute the step of simulating and calculating the leaf spring system simulation model according to the axial preload force of the U-bolt and the maximum vertical load of the leaf spring, and read the leaf spring center hole stress after the axial preload force of the U-bolt is attenuated, which is recorded as the second leaf spring center hole stress; A pressing plate elastic modulus adjustment module 440, used to adjust the pressing plate elastic modulus so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and record the pressing plate elastic modulus before and after the adjustment; The pressure plate section height adjustment module 450 is used to adjust the pressure plate section height so that the increase in the pressure plate section inertia moment is the same as the increase in the recorded pressure plate elastic modulus before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0080] The leaf spring system strength optimization device of this embodiment is used to implement the aforementioned leaf spring system strength optimization method. Therefore, the specific implementation method of the device can be seen in the embodiment part of the leaf spring system strength optimization method in the previous text. Therefore, its specific implementation method can refer to the description of the corresponding various parts of the embodiment, which will not be elaborated here.
[0081] In addition, since the leaf spring system strength optimization device of the present embodiment is used to implement the aforementioned leaf spring system strength optimization method, its function corresponds to that of the aforementioned method and will not be described in detail here.
[0082] Figure 5 A schematic diagram of the structure of a terminal 500 provided in an embodiment of the present invention includes: a processor 510, a memory 520 and a communication unit 530. The processor 510 is used to implement the following steps when implementing the leaf spring system strength optimization program stored in the memory 520: Step 1, establishing a leaf spring system simulation model in finite element simulation software; Step 2, converting the specified U-bolt tightening torque into the U-bolt axial preload; Step 3, according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, the leaf spring system simulation model is simulated and calculated, and the stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read, and recorded as the first leaf spring center hole stress; Step 4, attenuating the axial preload of the U-bolt, and then re-performing the step of simulating and calculating the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, reading the stress of the center hole of the leaf spring after the axial preload of the U-bolt is attenuated, and recording it as the stress of the center hole of the second leaf spring; Step 5, adjusting the elastic modulus of the pressing plate so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and recording the elastic modulus of the pressing plate before and after the adjustment; Step 6, adjusting the height of the pressure plate section so that the increase in the moment of inertia of the pressure plate section is the same as the increase in the elastic modulus of the pressure plate recorded in step 5 before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0083] The present invention also provides a computer storage medium, wherein the storage medium may be a magnetic disk, an optical disk, a read-only memory (ROM) or a random access memory (RAM).
[0084] The computer storage medium stores a leaf spring system strength optimization program, and when the leaf spring system strength optimization program is executed by a processor, the following steps are implemented: Step 1, establishing a leaf spring system simulation model in finite element simulation software; Step 2, converting the specified U-bolt tightening torque into the U-bolt axial preload; Step 3, according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, the leaf spring system simulation model is simulated and calculated, and the stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read, and recorded as the first leaf spring center hole stress; Step 4, attenuating the axial preload of the U-bolt, and then re-performing the step of simulating and calculating the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, reading the stress of the center hole of the leaf spring after the axial preload of the U-bolt is attenuated, and recording it as the stress of the center hole of the second leaf spring; Step 5, adjusting the elastic modulus of the pressing plate so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and recording the elastic modulus of the pressing plate before and after the adjustment; Step 6, adjusting the height of the pressure plate section so that the increase in the moment of inertia of the pressure plate section is the same as the increase in the elastic modulus of the pressure plate recorded in step 5 before and after adjustment, thereby optimizing the strength of the leaf spring system.
[0085] The above description of the disclosed embodiments enables one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be apparent to one 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. Therefore, the present invention will not be limited to the embodiments shown herein, but rather to the widest scope consistent with the principles and novel features disclosed herein.
Claims
1. A leaf spring system strength optimization method, characterized in that: The following steps are involved: Step 1, establishing a leaf spring system simulation model in finite element simulation software; Step 2, converting the specified U-bolt tightening torque into the U-bolt axial preload; Step 3, according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, the leaf spring system simulation model is simulated and calculated, and the stress of the center hole of the leaf spring before the axial preload of the U-bolt is not attenuated is read, and recorded as the first leaf spring center hole stress; Step 4, attenuating the axial preload of the U-bolt, and then re-performing the step of simulating and calculating the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, reading the stress of the center hole of the leaf spring after the axial preload of the U-bolt is attenuated, and recording it as the stress of the center hole of the second leaf spring; Step 5, adjusting the elastic modulus of the pressing plate so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and recording the elastic modulus of the pressing plate before and after the adjustment; Step 6, adjusting the height of the pressure plate section so that the increase in the moment of inertia of the pressure plate section is the same as the increase in the elastic modulus of the pressure plate recorded in step 5 before and after adjustment, thereby optimizing the strength of the leaf spring system.
2. The leaf spring system strength optimization method according to claim 1, characterized in that: Step 2 converts the specified U-bolt tightening torque into the U-bolt axial preload, including: Refer to relevant standards and determine the tightening torque of the U-bolt according to the corresponding U-bolt strength and diameter; Calculate the axial preload of the U-bolt according to the following formula: in, is the tightening torque of the U-bolt, is the torque coefficient, is the axial preload of the U-bolt, It is the basic dimension of the major diameter of the external thread of the U-bolt.
3. The leaf spring system strength optimization method according to claim 2, characterized in that: Step 5 specifically includes: Step 5.1, record the initial platen elastic modulus corresponding to the stress of the center hole of the first leaf spring ; Step 5.2, adjusting the elastic modulus of the pressure plate in a stepwise iterative manner to change the stress of the center hole of the second leaf spring; Step 5.2.1, determine the initial iteration step size ; Step 5.2.2, perform the first iteration: Update the platen elastic modulus to , and substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation; Step 5.2.3, reading the updated stress of the center hole of the second leaf spring; Step 5.2.4, compare the updated stress of the center hole of the second leaf spring with the stress of the center hole of the first leaf spring. If the updated stress of the center hole of the second leaf spring is greater than the stress of the center hole of the first leaf spring, change the iteration step size to , update the elastic modulus of the pressure plate to ; If the updated stress of the second leaf spring center hole is less than the stress of the first leaf spring center hole, keep the iteration step size , update the elastic modulus of the pressure plate to ; Substitute the updated elastic modulus into the leaf spring system simulation model for simulation calculation, and so on until the conditions of step 5.3 are met; Step 5.3, when the stress in the center hole of the second leaf spring is the same as the stress in the center hole of the second leaf spring, record the elastic modulus of the pressure plate at this time .
4. The leaf spring system strength optimization method according to claim 3, characterized in that: Step 6 specifically includes: Calculate the elastic modulus of the platen before adjusting the platen section height The corresponding moment of inertia of the platen section ; Maintain the initial platen elastic modulus No change, adjust the height of the pressure plate section and recalculate the moment of inertia of the pressure plate section , so that the optimized platen section moment of inertia Satisfies the following formula, Based on the moment of inertia of the platen section The specific value of the height of the pressure plate section can be determined by using formula (2).
5. The leaf spring system strength optimization method according to claim 4, characterized in that: Calculate the elastic modulus of the platen before adjusting the platen section height The corresponding moment of inertia of the platen section , specifically including: Get the initial platen height , initial height of the middle hollow area and the length of the middle hollow area ; The height of the centroid of the initial cross section of the platen along the Z axis is calculated by the following formula , The initial cross-sectional area of the platen is calculated by the following formula , The moment of inertia of the platen section is calculated by the following formula , 。 6. The leaf spring system strength optimization method according to claim 5, characterized in that: Adjust the height of the pressure plate section and recalculate the moment of inertia of the pressure plate section , specifically including: Note that the thickness of the pressure plate to be increased is ; Get the optimized height of the hollow area in the middle after adjusting the thickness of the pressure plate ; The height of the centroid of the optimized cross section of the pressure plate along the Z axis is calculated by the following formula , The optimized cross-sectional area of the pressure plate is calculated by the following formula , The moment of inertia of the platen section is calculated by the following formula , 。 7. The leaf spring system strength optimization method according to any one of claims 1 to 6, characterized in that: In step 4, the axial preload force of the U-bolt is attenuated at a ratio of 25%.
8. A leaf spring system strength optimization device, characterized in that: include: A preload conversion module, used to convert the specified U-bolt tightening torque into the U-bolt axial preload; The first leaf spring center hole stress reading module is used to perform simulation calculation on the leaf spring system simulation model according to the axial preload of the U-bolt and the maximum vertical load of the leaf spring, and read the stress of the center hole of the leaf spring before the axial preload of the U-bolt is attenuated, which is recorded as the first leaf spring center hole stress; The second leaf spring center hole stress reading module is used to attenuate the axial preload force of the U-bolt, and then re-execute the step of simulating and calculating the leaf spring system simulation model according to the axial preload force of the U-bolt and the maximum vertical load of the leaf spring, and read the stress of the center hole of the leaf spring after the axial preload force of the U-bolt is attenuated, which is recorded as the second leaf spring center hole stress; A pressing plate elastic modulus adjustment module, used to adjust the pressing plate elastic modulus so that the stress of the center hole of the second leaf spring is consistent with the stress of the center hole of the first leaf spring, and record the elastic modulus of the pressing plate before and after the adjustment; The pressure plate section height adjustment module is used to adjust the pressure plate section height so that the increase in the pressure plate section inertia moment is the same as the increase in the recorded pressure plate elastic modulus before and after adjustment, thereby optimizing the strength of the leaf spring system.
9. A terminal, characterized in that: include: A memory for storing a leaf spring system strength optimization program; A processor is used to implement the steps of the leaf spring system strength optimization method as described in any one of claims 1 to 7 when executing the leaf spring system strength optimization program.
10. A computer-readable storage medium, characterized in that: The readable storage medium stores a leaf spring system strength optimization program, and when the leaf spring system strength optimization program is executed by a processor, the steps of the leaf spring system strength optimization method according to any one of claims 1 to 7 are implemented.