A fatigue life prediction method for wheel hub tapered roller bearings

Abstract

The present invention relates to a method for predicting fatigue life of a hub tapered roller bearing, comprising step S1, establishing a digital model of a tapered roller bearing and a digital model of a hub; step S2, establishing and combining a finite element model of a tapered roller bearing and a finite element model of a hub; step S3, assigning material properties and cross-sectional properties to the finite element model of the tapered roller bearing and the finite element model of the hub, creating a reference point on the finite element model of the hub, and establishing coupling constraints between the reference point and the finite element model of the hub; step S4, applying a preset load to the finite element model of the hub based on the reference point, applying a constraint that limits six degrees of freedom on the inner ring surface of the inner ring of the finite element model of the tapered roller bearing, performing dynamic simulation, and obtaining a stress cloud map; step S5, predicting the fatigue life of the hub tapered roller bearing under a preset load based on the stress cloud map. The present invention reduces the difficulty of solving the simulation calculation of the hub tapered roller bearing and improves the prediction accuracy of the fatigue life of the hub tapered roller bearing.

Description

Technical Field

[0001] The invention relates to the technical field of bearing fatigue life prediction, and in particular to a method for predicting the fatigue life of a hub tapered roller bearing. Background Art

[0002] With the development of simulation technology, numerical simulation has become an important means to predict the stress distribution and fatigue life of bearings under periodic dynamic radial, axial and bending preset loads. Tapered roller bearings are important bearing components in heavy truck rear axle hubs and other vehicle parts, and fatigue life prediction is usually required. The existing wheel hub bearing fatigue life prediction technology is mainly achieved in three ways: Method 1: The four-row tapered roller bearing model is simulated and calculated under a three-dimensional preset load by finite element analysis software, and the fatigue life of the wheel hub bearing is predicted using theoretical formulas. Method 2: The static simulation result model of the rolling bearing is used as the fatigue analysis model, and the time-stress variation law of its dynamic simulation results is used as the preset load cycle variable for fatigue analysis. The wheel hub bearing life cloud map is obtained using fatigue analysis software such as nCode DesignLife. Method 3: Combined with the actual working conditions of the wheel hub bearing, a bearing working mechanics model is established, and the fatigue life of the bearing is simulated and analyzed using finite element statics software, and the fatigue life of the wheel hub bearing is predicted in combination with dynamic simulation.

[0003] However, the existing wheel hub bearing fatigue life prediction technologies have partially simplified the structure of the bearings and removed features such as the fillet of the bearing rolling elements. Although this process makes grid division convenient, its stress distribution is quite different from that of the actual bearing. In addition, the existing wheel hub bearing fatigue life prediction technologies all use the method of using static calculation results to calculate fatigue life. Under complex working conditions with multiple rolling elements, it is very difficult to converge the calculation results. The excessive constraints set for debugging convergence also limit the actual freedom of movement of the bearings, causing the simulation calculation results to be distorted and differing greatly from the actual bearing force results. It can be seen from this that if the existing wheel hub bearing fatigue life prediction technology is directly used to predict the fatigue life of the wheel hub tapered roller bearing, the accuracy of the prediction results cannot be guaranteed. Summary of the invention

[0004] The purpose of the present invention is to provide a method for predicting the fatigue life of a hub tapered roller bearing, which reduces the difficulty of solving the simulation calculation of the hub tapered roller bearing and improves the prediction accuracy of the fatigue life of the hub tapered roller bearing.

[0005] According to a first aspect of the present invention, a method for predicting fatigue life of a hub tapered roller bearing is provided, comprising:

[0006] Step S1, obtaining the structural parameters of the tapered roller bearing and the structural parameters of the wheel hub, establishing a digital model of the tapered roller bearing based on the structural parameters of the tapered roller bearing, and establishing a digital model of the wheel hub based on the structural parameters of the wheel hub, wherein the digital model of the tapered roller bearing is a digital model that is completely consistent with the structural parameters of the actual tapered roller bearing, and the digital model of the wheel hub is a simplified digital model;

[0007] Step S2, establishing a finite element model of a tapered roller bearing based on the digital model of the tapered roller bearing, establishing a finite element model of a wheel hub based on the digital model of the wheel hub, and combining the finite element model of the tapered roller bearing and the finite element model of the wheel hub according to the actual assembly relationship between the tapered roller bearing and the wheel hub;

[0008] Step S3, pre-processing the tapered roller bearing finite element model and the wheel hub finite element model, assigning corresponding material properties and cross-sectional properties to the tapered roller bearing finite element model and the wheel hub finite element model, creating a preset reference point on the wheel hub finite element model, and establishing a coupling constraint between the reference point and the wheel hub finite element model;

[0009] Step S4, applying a preset load to the hub finite element model based on the reference point, applying constraints that limit all six degrees of freedom on the inner annular surface of the bearing inner ring of the tapered roller bearing finite element model, performing dynamic simulation on the combined tapered roller bearing finite element model and the hub finite element model, and obtaining a stress cloud diagram of the tapered roller bearing corresponding to the end time of the dynamic analysis;

[0010] Step S5: predicting the fatigue life of the hub tapered roller bearing under a preset load based on the tapered roller bearing stress cloud map.

[0011] According to a second aspect of the present invention, there is provided an electronic device, comprising: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, the instructions being configured to execute the method described in the first aspect of the present invention.

[0012] According to a third aspect of the present invention, a computer-readable storage medium is provided, wherein the computer instructions are used to execute the method described in the first aspect of the present invention.

[0013] Compared with the prior art, the present invention has obvious advantages and beneficial effects. By means of the above technical solution, the fatigue life prediction method of a hub tapered roller bearing provided by the present invention can achieve considerable technical advancement and practicality, and has wide industrial utilization value, and has at least the following advantages:

[0014] The present invention establishes a digital model of a tapered roller bearing that is completely consistent with the characteristics of an actual tapered roller bearing, optimizes its surface curve, and establishes a finite element model of a tapered roller bearing with a high-quality mesh to ensure that the calculation results are more accurate. The present invention also adopts a method of coupling the loading of the load surface with multiple reference points and the stable loading of the dynamic analysis step, which greatly reduces the difficulty of simulation convergence calculation. In addition, the present invention also adopts the local stress-strain method to predict the bending fatigue life of the tapered roller bearing. The numerical value obtained by this method is closer to the actual test value, which reduces the difficulty of solving the simulation calculation of the hub tapered roller bearing and improves the accuracy of the prediction result.

[0015] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following specifically cites a preferred embodiment and describes it in detail with the accompanying drawings as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 A flow chart of a method for predicting fatigue life of a hub tapered roller bearing provided in an embodiment of the present invention;

[0017] Figure 2 A schematic diagram of the three-dimensional spatial orientation of a model provided by an embodiment of the present invention;

[0018] Figure 3 A schematic diagram of coupling four reference points provided by an embodiment of the present invention;

[0019] Figure 4 A schematic diagram of applying loads to four reference points provided in an embodiment of the present invention. DETAILED DESCRIPTION

[0020] In order to further explain the technical means and effects adopted by the present invention to achieve the predetermined invention purpose, the specific implementation method and effects of a hub tapered roller bearing fatigue life prediction method proposed by the present invention are described in detail below in combination with the accompanying drawings and preferred embodiments.

[0021] The embodiment of the present invention provides a method for predicting fatigue life of a hub tapered roller bearing. Figure 1 As shown, including:

[0022] Step S1, obtaining the structural parameters of the tapered roller bearing and the structural parameters of the wheel hub, establishing a digital model of the tapered roller bearing based on the structural parameters of the tapered roller bearing, and establishing a digital model of the wheel hub based on the structural parameters of the wheel hub, wherein the digital model of the tapered roller bearing is a digital model that is completely consistent with the structural parameters of the actual tapered roller bearing, and the digital model of the wheel hub is a simplified digital model;

[0023] The digital model of the tapered roller bearing includes chamfer features and fillet features, and the digital model of the wheel hub includes hexahedral features. Specifically, the digital model of the tapered roller bearing and the digital model of the wheel hub can be established using existing CAD modeling software such as Solidworks or UG. It should be noted that the digital model of the bearing in the prior art is usually a simplified model, while the digital model of the tapered roller bearing established in the embodiment of the present invention is a digital model that is completely consistent with the structural parameters of the actual tapered roller bearing.

[0024] Step S2, establishing a finite element model of a tapered roller bearing based on the digital model of the tapered roller bearing, establishing a finite element model of a wheel hub based on the digital model of the wheel hub, and combining the finite element model of the tapered roller bearing and the finite element model of the wheel hub according to the actual assembly relationship between the tapered roller bearing and the wheel hub;

[0025] Step S3, assigning corresponding material properties and cross-sectional properties to the tapered roller bearing finite element model and the wheel hub finite element model, creating a preset reference point on the wheel hub finite element model, and establishing a coupling constraint between the reference point and the wheel hub finite element model;

[0026] Step S4, applying a preset load to the hub finite element model based on the reference point, applying constraints that limit all six degrees of freedom on the inner annular surface of the bearing inner ring of the tapered roller bearing finite element model, performing dynamic simulation on the combined tapered roller bearing finite element model and the hub finite element model, and obtaining a stress cloud diagram of the tapered roller bearing corresponding to the end time of the dynamic analysis;

[0027] It should be noted that there are multiple instantaneous states in the dynamic analysis process, so the stress cloud diagram of the tapered roller bearing corresponding to the end moment of the dynamic analysis, that is, the final moment of the dynamic analysis, when the kinetic energy of the load has been fully converted into the internal energy of the system, should be taken. In addition, the specific process of obtaining the stress cloud diagram is an existing technology and will not be repeated here.

[0028] Step S5: predicting the fatigue life of the hub tapered roller bearing under a preset load based on the tapered roller bearing stress cloud map.

[0029] As an embodiment, in step S2, establishing a finite element model of a tapered roller bearing based on the digital model of the tapered roller bearing, and establishing a finite element model of a wheel hub based on the digital model of the wheel hub, comprises:

[0030] Step S21, suppressing redundant lines in the generation process of the tapered roller bearing digital model and the wheel hub digital model, merging the narrow and long faces and normal faces on the tapered roller bearing digital model and the wheel hub digital model into a smooth curved surface, wherein the smooth curved surface may be a larger, normal curved surface;

[0031] Among them, redundant lines refer to process lines drawn during the model building process to establish certain special surfaces. After the model is imported into the meshing software, the surface will no longer change due to deleting or suppressing these process lines. However, when meshing, deleting these redundant lines will divide the surface into better meshes, reduce the number of low-quality meshes caused by dense lines, and thus improve the quality of model meshing. Narrow faces refer to slender surfaces with excessive length and width formed by three or more process lines. Narrow faces will also affect the quality of meshing when the surface is meshed. By deleting or suppressing redundant process lines, merging multiple narrow faces, or merging narrow faces with normal faces, the surface can be divided into better meshes, which can improve the quality of model meshing.

[0032] Step S22, meshing the tapered roller bearing digital model and the wheel hub digital model to generate corresponding two-dimensional quadrilateral meshes, and based on the two-dimensional quadrilateral meshes, performing finite element meshing on the tapered roller bearing digital model and the wheel hub digital model to generate three-dimensional hexahedral meshes;

[0033] Specifically, the digital model of the tapered roller bearing and the digital model of the wheel hub can be output as corresponding Step (product data exchange standard) files using CAD modeling software, and then imported into existing meshing software, such as Hypermesh, for meshing.

[0034] Step S23, deleting the two-dimensional quadrilateral meshes corresponding to the tapered roller bearing digital model and the wheel hub digital model, retaining the corresponding three-dimensional hexahedral meshes, and generating a tapered roller bearing finite element model and a wheel hub finite element model based on the three-dimensional hexahedral meshes corresponding to the tapered roller bearing digital model and the wheel hub digital model.

[0035] Among them, the commonly used meshes include two-dimensional surface meshes and three-dimensional volume meshes. The three-dimensional volume meshes are divided on the basis of two-dimensional surface meshes, that is, a model surface is divided into two-dimensional plane meshes, and three-dimensional volume meshes are divided internally based on the two-dimensional meshes. Finite element division can divide an overall model into a finite number of mesh aggregates. Through the algorithm to calculate the meshes, all mesh calculation results are combined into an overall result, which is the result of the finite element analysis solution. Two-dimensional surface meshes include triangular surface meshes and quadrilateral surface meshes. Three-dimensional volume meshes include tetrahedral meshes and hexahedral meshes, which are cones and cuboids. The finite element model of the tapered roller bearing and the finite element model of the wheel hub are relatively regular, which is convenient for dividing the hexahedral mesh, and the calculation results of the hexahedral mesh are more accurate.

[0036] As an embodiment, in the step S3, the hexahedral mesh model of the bearing and the hub divided into meshes in Hypermesh can be output as an inp file, and the inp file can be imported into the existing engineering structure simulation software, such as Abaqus, to pre-process the tapered roller bearing finite element model and the wheel hub finite element model; establish the material properties and cross-sectional properties of each part of the tapered roller bearing and the wheel hub, and assign the material cross-sectional properties to each part in the tapered roller bearing finite element model and the wheel hub finite element model.

[0037] As an embodiment, the wheel hub finite element model is a simplified rectangular parallelepiped model with a through hole, the tapered roller bearing finite element model is located in the wheel hub finite element model, and the axis of the tapered roller bearing finite element model coincides with the axis of the through hole of the wheel hub finite element model. Figure 2 As shown, the axis of the through hole of the hub finite element model is the X-axis direction, the direction of the through hole toward the small end of the inner ring of the large-size bearing is the positive direction of the X-axis, the direction toward the small end of the inner ring of the small-size bearing is the negative direction of the X-axis, the direction perpendicular to the bottom surface of the hub finite element model upward is the positive direction of the Y-axis, and the direction perpendicular to the plane formed by the X-axis and the Y-axis and facing away from the hub finite element model is the positive direction of the Z-axis;

[0038] In the step S3, creating a preset reference point on the hub finite element model includes:

[0039] Step S31, establish a first reference point at the center point of the upper surface of the hub finite element model, establish a second reference point at the midpoint of the line connecting the center point of the first side surface and the center point of the second side surface of the hub finite element model, the first side surface and the second side surface are arranged face to face, establish a third reference point at the center of the positive surface of the X-axis of the hub finite element model, and establish a fourth reference point at the center of the negative surface of the X-axis.

[0040] As an embodiment, in step S3, establishing the coupling constraint between the reference point and the hub finite element model includes:

[0041] Step S32: coupling the first reference point with the upper surface of the hub finite element model, such as Figure 3 As shown in (a), the second reference point is coupled with the first side surface and the second side surface of the hub finite element model, as shown in Figure 3 (b); the third reference point is coupled to the positive surface of the hub finite element model, as shown in Figure 3 (c); the fourth reference point is coupled to the negative surface of the hub finite element model, as shown in Figure 3 As shown in (d); establish a preset load action surface coupling constraint, and set the coupling constraint type to a kinematic coupling constraint.

[0042] It can be understood that coupling is similar to an equivalent medium, that is, the effect acting on the coupling point will be directly synchronized to the coupling surface. In the embodiment of the present invention, it is impossible to apply a concentrated point load on multiple surfaces, so by coupling multiple surfaces to one point, applying a concentrated point load on the point can achieve the corresponding effect. The embodiment of the present invention can be specifically based on software function coupling: select the control point, that is, select the reference point as the control point, and select the coupled surface, that is, the surface of the hub finite element model to be coupled. That is, let the reference point control the surfaces of these hub finite element models, and then the effect applied to the reference point will be converted into an effect on the surface of the hub finite element model.

[0043] It should be noted that the prior art predicts the fatigue life of tapered roller bearings by directly applying loads to the finite element model of the tapered roller bearing, excluding the wheel hub finite element model. This method will inevitably lead to stress problems with degrees of freedom and loads. In the embodiment of the present invention, a simplified wheel hub finite element model is set up, and the load is applied to the wheel hub finite element model, and then indirectly acts on the surface of the outer ring of the bearing of the tapered roller bearing finite element model, so as to ensure the authenticity of the model and prevent distortion. In addition, the prior art uses statics to predict the fatigue life of tapered roller bearings, while the present application is implemented through kinematic coupling. As an embodiment, in step S4, a preset load is applied to the wheel hub finite element model based on the reference point, including:

[0044] Step S41, set the dynamic analysis time corresponding to the i-th reference point to Ti, the preset load value to Li, and establish the corresponding linear function amplitude curve (Smooth step), the value range of i is 1 to 4, the initial time and the initial preset load of the linear function amplitude curve corresponding to Li are both 0, the end time is Ti / N, the end preset load is Li, and N is an integer greater than or equal to 2;

[0045] It should be noted that the specific process of establishing the corresponding linear function amplitude curve is an existing algorithm and will not be repeated here. The purpose of the linear function amplitude curve is to allow the load to act on the surface of the hub finite element model in a relatively stable process, rather than an instantaneous impact. In addition, the overall kinetic energy of the system is fully converted into internal energy, thereby obtaining stress analysis results. This processing method not only ensures the actual effect of the load on the tapered roller bearing, but also greatly reduces the difficulty of convergence of results during static analysis.

[0046] Step S42: dynamically apply a preset load to the i-th reference point based on the linear function amplitude curve corresponding to the i-th reference point, wherein a concentrated radial preset load in the negative direction of the Y axis is applied to the first reference point, such as Figure 4 (a); a preset bending moment load in the positive direction of the Y axis is applied to the second reference point, as shown in Figure 4(b); As shown in FIG. 1 , a concentrated axial positive preset load or a negative preset load is applied to the third reference point or the fourth reference point according to the actual load condition. Figure 4 (c) Figure 4 (d) as shown.

[0047] As an embodiment, in step S4, constraints that restrict all six degrees of freedom are imposed on the inner annular surface of the inner ring of the tapered roller bearing finite element model, including:

[0048] Step S43: Apply constraints to limit the Z-axis movement and the X-axis and Z-axis rotational freedom at the first reference point, and apply a global vertical downward gravity acceleration g=9.8m / s2, wherein the Z axis is perpendicular to both the X axis and the Y axis.

[0049] As an embodiment, step S5 includes:

[0050] Step S51, determining the maximum stress point in the tapered roller bearing stress cloud map as a dangerous point, and extracting the corresponding maximum stress value;

[0051] It should be noted that after performing finite element analysis on the tapered roller bearing finite element model in the simulation software, the stress cloud diagram of the tapered roller bearing under the corresponding load condition can be obtained in the software post-processing module. In the tapered roller bearing stress cloud diagram, the maximum stress point and the specific stress value of this point can be queried through settings.

[0052] Step S52, generating a stress spectrum of a dangerous point based on the dangerous point;

[0053] Among them, the nominal stress spectrum of a certain point can be extracted through existing software post-processing, which will not be described in detail here.

[0054] Step S53, using an elastic-plastic finite element method algorithm to generate a stress-strain spectrum of a dangerous point based on the stress spectrum of the dangerous point;

[0055] It should be noted that a metal material, when subjected to force, has two situations: elastic deformation and plastic deformation. Elastic deformation means that the material returns to its original state after the force is withdrawn, and plastic deformation means that the material does not return to its original state after the force is withdrawn. Fatigue analysis is for the elastic deformation stage, because the structure is damaged during plastic deformation. In the elastic stage, there is a corresponding relationship between the stress-strain of the material, and each material is different. After the simulation calculation, the stress-strain spectrum under a certain force can be obtained in the post-processing module. Step S53 can be implemented directly using the existing technology, which will not be repeated here.

[0056] Step S54, obtaining an ε-N curve corresponding to the stress-strain spectrum of the dangerous point, wherein ε is the symbol of strain and N is the symbol of life;

[0057] Among them, the SN curve is a stress-life curve, and the stress-life curve of each material is also known. In step S53, it is mentioned that for each material within the elastic deformation range, the stress S-strain value ε corresponds one to one, then SN can be converted into ε-N, and then the ε-N curve under the stress-strain level is obtained, which will not be repeated here.

[0058] Step S55: According to the ε-N curve, a preset strain-life formula is used to predict the fatigue life of the tapered roller bearing under a preset load.

[0059] Step S55 is directly based on the fatigue cumulative damage theory and uses the strain-life formula The fatigue life of the dangerous point is calculated, which is the fatigue life of the bearing under the design load.

[0060] Among them, σ max is the maximum stress value, ε a is the strain amplitude, σ' f is the fatigue strength coefficient, E is the elastic modulus of the bearing material, N f is fatigue life, A is fatigue strength index, ε' f is the fatigue ductility coefficient, and B is the fatigue ductility index. The fatigue cumulative damage theory and the strain-life formula are both existing technologies and will not be described in detail here.

[0061] The embodiment of the present invention establishes a digital model of a tapered roller bearing that is completely consistent with the characteristics of an actual tapered roller bearing, optimizes its surface curve, and establishes a finite element model of a tapered roller bearing with a high-quality mesh to ensure that the calculation results are more accurate. The present invention also adopts a method of coupling the loading of the load surface with multiple reference points and the stable loading of the dynamic analysis step, which greatly reduces the difficulty of simulation convergence calculation. In addition, the present invention also adopts a local stress-strain method to predict the bending fatigue life of tapered roller bearings. The numerical value obtained by this method is closer to the actual test value, which improves the accuracy of the prediction result.

[0062] It should be noted that some exemplary embodiments are described as processes or methods depicted as flow charts. Although the flow charts describe the steps as sequential processes, many of the steps can be implemented in parallel, concurrently or simultaneously. In addition, the order of the steps can be rearranged. The process can be terminated when its operation is completed, but it can also have additional steps not included in the accompanying drawings. The process can correspond to a method, function, procedure, subroutine, subprogram, etc.

[0063] An embodiment of the present invention also provides an electronic device, comprising: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are configured to execute the method described in the embodiment of the present invention.

[0064] The embodiment of the present invention further provides a computer-readable storage medium, wherein the computer instructions are used to execute the method described in the embodiment of the present invention.

[0065] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any form. Although the present invention has been disclosed as a preferred embodiment as above, it is not used to limit the present invention. Any technician familiar with this profession can make some changes or modifications to equivalent embodiments of equivalent changes using the technical contents disclosed above without departing from the scope of the technical solution of the present invention. However, any simple modification, equivalent change and modification made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention still falls within the scope of the technical solution of the present invention.

Claims

1. A method for predicting fatigue life of a hub tapered roller bearing, characterized in that: include: Step S1, obtaining the structural parameters of the tapered roller bearing and the structural parameters of the wheel hub, establishing a digital model of the tapered roller bearing based on the structural parameters of the tapered roller bearing, and establishing a digital model of the wheel hub based on the structural parameters of the wheel hub, wherein the digital model of the tapered roller bearing is a digital model that is completely consistent with the structural parameters of the actual tapered roller bearing, and the digital model of the wheel hub is a simplified digital model; Step S2, establishing a finite element model of a tapered roller bearing based on the digital model of the tapered roller bearing, establishing a finite element model of a wheel hub based on the digital model of the wheel hub, and combining the finite element model of the tapered roller bearing and the finite element model of the wheel hub according to the actual assembly relationship between the tapered roller bearing and the wheel hub; Step S3, assigning corresponding material properties and cross-sectional properties to the tapered roller bearing finite element model and the wheel hub finite element model, creating a preset reference point on the wheel hub finite element model, and establishing a coupling constraint between the reference point and the wheel hub finite element model; Step S4, applying a preset load to the wheel hub finite element model based on the reference point, applying constraints that limit all six degrees of freedom on the inner ring surface of the bearing inner ring of the tapered roller bearing finite element model, dynamically simulating the combined tapered roller bearing finite element model and the wheel hub finite element model, and obtaining a stress cloud diagram of the tapered roller bearing corresponding to the end time of the dynamic analysis; in the step S4, applying a preset load to the wheel hub finite element model based on the reference point includes: Step S41, set the dynamic analysis time corresponding to the i-th reference point to Ti, the preset load value to Li, and establish the corresponding linear function amplitude curve, the value range of i is 1 to 4, the initial time and the initial preset load of the linear function amplitude curve corresponding to Li are both 0, the end time is Ti / N, the end preset load is Li, and N is an integer greater than or equal to 2; Step S42, dynamically applying a preset load to the i-th reference point based on the linear function amplitude curve corresponding to the i-th reference point, wherein a concentrated radial preset load in the negative direction of the Y-axis is applied to the first reference point, a bending moment preset load in the positive direction of the Y-axis is applied to the second reference point, and a concentrated axial positive preset load or a negative preset load is applied to the third reference point or the fourth reference point according to the actual load condition; Step S5: predicting the fatigue life of the hub tapered roller bearing under a preset load based on the tapered roller bearing stress cloud map.

2. The method according to claim 1, characterized in that: In the step S1, the tapered roller bearing digital model includes chamfer features and fillet features, and the wheel hub digital model includes hexahedron features.

3. The method according to claim 1, characterized in that In the step S2, a finite element model of a tapered roller bearing is established based on the digital model of the tapered roller bearing, and a finite element model of a wheel hub is established based on the digital model of the wheel hub, including: Step S21, suppressing redundant lines in the generation process of the tapered roller bearing digital model and the wheel hub digital model, and merging the narrow and long surfaces and normal surfaces on the tapered roller bearing digital model and the wheel hub digital model into a smooth curved surface; Step S22, meshing the tapered roller bearing digital model and the wheel hub digital model to generate corresponding two-dimensional quadrilateral meshes, and based on the two-dimensional quadrilateral meshes, performing finite element meshing on the tapered roller bearing digital model and the wheel hub digital model to generate three-dimensional hexahedral meshes; Step S23, deleting the two-dimensional quadrilateral meshes corresponding to the tapered roller bearing digital model and the wheel hub digital model, retaining the corresponding three-dimensional hexahedral meshes, and generating a tapered roller bearing finite element model and a wheel hub finite element model based on the three-dimensional hexahedral meshes corresponding to the tapered roller bearing digital model and the wheel hub digital model.

4. The method according to claim 1, characterized in that: The wheel hub finite element model is a simplified rectangular parallelepiped model with a through hole. The tapered roller bearing finite element model is located in the wheel hub finite element model. The axis of the tapered roller bearing finite element model coincides with the axis of the through hole of the wheel hub finite element model. The axis of the through hole of the wheel hub finite element model is the X-axis direction. The direction of the through hole toward the small end of the inner ring of the large-size bearing is the positive direction of the X-axis. The direction toward the small end of the inner ring of the small-size bearing is the negative direction of the X-axis. The direction perpendicular to the bottom surface of the wheel hub finite element model upward is the positive direction of the Y-axis. The direction perpendicular to the plane formed by the X-axis and the Y-axis and facing away from the wheel hub finite element model is the positive direction of the Z-axis. In the step S3, creating a preset reference point on the hub finite element model includes: Step S31, establish a first reference point at the center point of the upper surface of the hub finite element model, establish a second reference point at the midpoint of the line connecting the center point of the first side surface and the center point of the second side surface of the hub finite element model, the first side surface and the second side surface are arranged face to face, establish a third reference point at the center of the positive surface of the X-axis of the hub finite element model, and establish a fourth reference point at the center of the negative surface of the X-axis.

5. The method according to claim 4, characterized in that In the step S3, establishing the coupling constraint between the reference point and the hub finite element model includes: Step S32, couple the first reference point with the upper surface of the wheel hub finite element model, couple the second reference point with the first side surface and the second side surface of the wheel hub finite element model, couple the third reference point with the positive surface of the wheel hub finite element model, couple the fourth reference point with the negative surface of the wheel hub finite element model, establish a preset load action surface coupling constraint, and set the coupling constraint type to a kinematic coupling constraint.

6. The method according to claim 5, characterized in that In step S4, constraints are imposed on the inner ring surface of the inner ring of the tapered roller bearing finite element model to limit all six degrees of freedom, including: Step S43: applying constraints to limit the Z-axis movement and the X-axis and Z-axis rotational freedom at the first reference point, and applying a global vertical downward gravity acceleration, wherein the Z axis is perpendicular to both the X axis and the Y axis.

7. The method according to claim 1, characterized in that Step S5 includes: Step S51, determining the maximum stress point in the tapered roller bearing stress cloud map as a dangerous point, and extracting the corresponding maximum stress value; Step S52, generating a stress spectrum of a dangerous point based on the dangerous point; Step S53, using an elastic-plastic finite element method algorithm to generate a stress-strain spectrum of a dangerous point based on the stress spectrum of the dangerous point; Step S54, obtaining an ε-N curve corresponding to the stress-strain spectrum of the dangerous point, wherein ε is the symbol of strain and N is the symbol of life; Step S55: According to the ε-N curve, a preset strain-life formula is used to predict the fatigue life of the tapered roller bearing under a preset load.

8. An electronic device, characterized in that: include: at least one processor; and, a memory communicatively coupled to the at least one processor; The memory stores instructions executable by the at least one processor, wherein the instructions are configured to execute the method according to any one of claims 1 to 7.

9. A computer-readable storage medium, characterized in that: Computer executable instructions are stored, and the computer executable instructions are used to execute the method of any one of the preceding claims 1-7.

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