Finite element-based railway vehicle axle box bearing load characteristic analysis method

Abstract

According to the railway vehicle axle box bearing load characteristic analysis method based on the finite element, a three-dimensional model of a tapered roller bearing is established in SolidWorks software, and Abaqus software is imported for grid division and contact design, so that stress distribution and deformation characteristics of the bearing under different working conditions can be deeply researched. Comprising the steps of model establishment, self-adaptive grid division, contact relation design and load and boundary condition application, parameters can be quickly adjusted in a virtual environment, the actual test cost is reduced, and the accuracy and reliability of an analysis result are ensured by adopting a display solution center difference method theory; according to the method, the dynamic behaviors of the axle box bearing under different loads and rotating speeds can be effectively predicted, the method has remarkable economic benefits and application values, parameters can be rapidly adjusted in a virtual environment, the actual test cost is reduced, the research efficiency is improved, and an important basis is provided for design optimization and maintenance decision making of railway vehicles.

Description

Technical Field

[0001] The invention relates to the research field of dynamic load characteristics of axle box bearings of high-speed trains, and in particular to a finite element-based analytical method for load characteristics of axle box bearings of rail vehicles. Background Art

[0002] In modern rail transit systems, the axle box bearings of rail vehicles carry high-frequency and high-amplitude dynamic loads, and their performance directly affects the safety, comfort and operating efficiency of the vehicle. With the widespread use of high-speed trains, the working conditions faced by axle box bearings have become more complex, and traditional analysis methods can no longer meet the needs of accurately evaluating their load characteristics. In recent years, finite element analysis (FEA) technology has received widespread attention due to its advantages in analyzing complex structures and material behaviors.

[0003] By performing finite element modeling on axlebox bearings, we can deeply study their stress distribution and deformation characteristics under different working conditions, thus providing a theoretical basis for optimized design and maintenance. However, existing analysis methods often lack systematicity and pertinence, and fail to effectively combine actual working conditions and material properties.

[0004] In the Chinese patent with publication number CN103625497A, a rail vehicle bogie axle box bearing positioning structure is mentioned, including an axle and a bearing pressed onto the axle, and also including a large nut and a stop washer, wherein the end of the axle has an external thread, the large nut is connected to the end of the axle, the stop washer is fixedly connected to the large nut by bolts, and the side of the large nut abuts against the end of the bearing for positioning; the overall structure is simple and practical, low in cost, firmly fixed, and easy to install and disassemble, which can not only improve production efficiency, but also facilitate daily maintenance; however, it is only applicable to the design of axle box systems for hollow shaft wheelsets, and cannot withstand large bearing forces for conventional rail vehicle bearing installations, and the load characteristics of the relevant axle box bearings are not specifically described, resulting in the inability to determine its load-bearing capacity.

[0005] Therefore, the present invention proposes a finite element-based method for analyzing the load characteristics of a rail vehicle axle box bearing, which is of great significance for improving the design and performance of a rail vehicle axle box bearing. Summary of the invention

[0006] In order to solve the above technical problems, the present invention provides a method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite elements to solve the problems raised in the background technology.

[0007] According to a first aspect of the present disclosure, a method for analyzing load characteristics of axle box bearings of railway vehicles based on finite element analysis is proposed, comprising the following steps:

[0008] S1. According to the outer dimensions of the double-row tapered roller bearing, a three-dimensional solid model of the tapered roller bearing is established in Solidworks software by means of a parametric design method;

[0009] S2, loading the exported bearing model file into the finite element analysis software Abaqus, and meshing the bearing model using an adaptive meshing method;

[0010] S3, inputting the contact relationship and contact parameters between the components of the tapered roller bearing finite element model;

[0011] S4. The radial load results of the tapered rollers in the axle box bearings in the high-speed train vehicle-track coupled dynamics model are calculated and solved using the multi-body dynamics software UM, and the displacement boundary conditions and load boundary conditions are accurately applied.

[0012] Preferably, the three-dimensional solid model of the tapered roller bearing established in S1 includes the inner ring, outer ring, cage, spacer and single tapered roller of the tapered roller bearing;

[0013] Assemble the components through the assembly module and use the circular array function to generate tapered rollers;

[0014] Export the model as a binary file.

[0015] Preferably, the step S2 performs a coarse and fine mesh processing on each component of the bearing model, comprising the following steps:

[0016] S201. Mesh the inner ring, outer ring and spacer models of the tapered roller bearing: evenly divide the inner ring, outer ring and spacer models of the bearing in the axial direction, ensure that the mesh can be divided into hexahedral units according to the component color prompt in the Abaqus software, mesh the inner ring, outer ring and spacer models after segmentation, set the mesh density to 3mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral units, reduce the integral hourglass control, and generate the mesh models of the inner ring, outer ring and spacer respectively;

[0017] S202, meshing the tapered roller bearing cage model: first, the cage model is divided along the two end faces in contact with the rollers, and then the divided cage model is divided again along the two side faces in contact with the rollers, a total of 34 parts, and the divided cages are meshed in sequence, the unit type is set to a mesh density of 2mm, a minimum deviation factor of 0.2, an eight-node linear hexahedral unit, and a reduced integral hourglass control, to generate a bearing cage mesh model;

[0018] S203. Mesh the roller model of the tapered roller bearing: first divide the tapered roller model into four equal parts along the axial direction, mesh the cage after the division, set the mesh density to 1.5 mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral unit, reduce the integral hourglass control, and generate the tapered roller mesh model.

[0019] Preferably, the contact relationship and contact parameter input between the components of S3 are as follows: surface-to-surface contact is set between the inner ring and the outer ring of the bearing and the tapered roller respectively, and surface-to-surface contact is also set between the two end surfaces of the inner ring of the bearing and the two end surfaces of the tapered roller. The normal of the contact interface adopts a "hard" contact model, and the tangential contact attribute adopts a static-dynamic attenuation coefficient model, wherein the static friction coefficient is 0.02, the dynamic friction coefficient is 0.05, and the attenuation coefficient is 0.01; a general contact model is adopted between the tapered roller and the cage pocket, the normal attribute of the contact interface adopts a "hard" contact model, the tangential contact attribute adopts a penalty function model, and the friction coefficient is set to 0.005;

[0020] Reference points 1, 2, and 3 are established at the center positions of the bearing inner ring, cage, and outer ring, respectively. Reference points 1, 2, and 3 are coupled with the outer surfaces of the bearing inner ring, cage, and bearing outer ring, respectively, so that the displacements of reference point 1 and the inner surface of the bearing inner ring are consistent in six degrees of freedom, the displacements of reference point 2 and the inner surface of the cage are consistent in six degrees of freedom, and the displacements of reference point 3 and the inner surface of the bearing outer ring are consistent in three translational degrees of freedom.

[0021] Preferably, the S4 fully constrains and fixes the outer ring of the bearing; and uses the Abaqus / Explicit analysis solver to establish two analysis steps:

[0022] S401. In the first analysis step, the vertical load borne by the bearing is applied at reference point 1, the translational freedom of the inner ring and the cage in the Z direction is released, and the other five degrees of freedom are restricted;

[0023] S402, in the second analysis step, the rotation speed of the bearing is applied at the reference point 1, and the freedom of the inner ring and the retainer in the rotation direction around the Y axis is released;

[0024] S403. The improved implicit integration method is used in the multi-body dynamics software UM, and the radial load results of the axle box bearing obtained by solving the problem have higher numerical stability;

[0025] S404. In the Abaqus display dynamics analysis, an adaptive time step control mechanism is introduced to dynamically adjust the time step according to the propagation characteristics of the stress wave and the current grid size, and the propagation speed of the stress wave is analyzed to estimate the maximum time step.

[0026] Preferably, the vertical load of the bearing and the rotation speed in the direction of rotation around the Y-axis are both smooth loads; the entire model is provided with a gravity load in the Z direction to simulate the effect of gravity on the tapered roller bearing model.

[0027] According to the second aspect of the present disclosure, an axle box bearing for a rail vehicle is also proposed, which is prepared by the method proposed in the first aspect of the present disclosure, and includes an outer ring, two groups of opposing retaining frames are arranged on the inner side of the outer ring, tapered rollers are installed in the upper grooves of the retaining frames, inner rings are arranged on the inner sides of the retaining frames, and a spacer ring is arranged between the two groups of inner rings.

[0028] Preferably, the contact angle between the tapered roller and the inner ring is 7.55°, the contact angle between the tapered roller and the outer ring is 10°, the outer diameter of the outer ring is 240 mm, the diameter of the inner ring is 130 mm, the average diameter of the tapered roller is 26 mm, and the number of rollers in a single row is 17.

[0029] Preferably, the outer ring, inner ring, spacer ring and retainer are all made of high carbon chromium bearing steel, and the density of the outer ring and inner ring is 7850kg / m 3 , elastic modulus is 206GPa, Poisson's ratio is 0.3; tapered roller and spacer density is 7801kg / m 3 , elastic modulus is 207GPa, Poisson's ratio is 0.29; the cage is a composite material with a density of 1150kg / m 3 , the elastic modulus is 8.6 GPa, and the Poisson's ratio is 0.4.

[0030] Compared with the prior art, the present invention has the following beneficial effects:

[0031] 1. The present invention can accurately simulate the dynamic behavior of the bearing under complex working conditions by establishing a three-dimensional model of the tapered roller bearing in SolidWorks and performing detailed meshing and interaction settings in Abaqus; it can effectively predict the stress distribution and deformation characteristics of the axle box bearing under different loads and speeds, thereby providing an important basis for the design optimization and maintenance decision of the bearing.

[0032] 2. The present invention comprehensively considers the geometric characteristics, material properties and actual working conditions of the bearing through this method, ensuring the accuracy and reliability of the analysis results. Its research method based on finite element analysis can quickly adjust parameters in a virtual environment, reduce the cost and time of actual experiments, and improve the efficiency of research. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 It is a 3 / 4 cross-sectional view of the double-row tapered roller bearing of the present invention;

[0034] Figure 2The structure diagram of the inner ring of the bearing of the present invention, wherein a is a schematic diagram of the inner ring cutting method, and b is a schematic diagram of the inner ring grid division;

[0035] Figure 3 The structure diagram of the bearing outer ring of the present invention, wherein a is a schematic diagram of the outer ring cutting method, and b is a schematic diagram of the outer ring grid division;

[0036] Figure 4 The structure diagram of the bearing cage of the present invention, wherein a is a schematic diagram of the cage cutting method, and b is a schematic diagram of the cage grid division;

[0037] Figure 5 The structure diagram of the tapered roller of the bearing of the present invention, wherein a is a schematic diagram of the tapered roller cutting method, and b is a schematic diagram of the tapered roller grid division;

[0038] Figure 6 It is a schematic diagram of the overall finite element model of the bearing of the present invention.

[0039] In the figure:

[0040] 1. Outer ring; 2. Cage; 3. Tapered roller; 4. Inner ring; 5. Spacer ring. DETAILED DESCRIPTION

[0041] The following embodiments of the present invention are described in further detail in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0042] Embodiment 1: The present invention provides a method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite elements, comprising the following steps:

[0043] S1. According to the outer dimensions of FAG 807811.09 double-row tapered roller bearing, a three-dimensional solid model of the tapered roller bearing is established in Solidworks software through a parametric design method to achieve adjustable model; the three-dimensional solid model includes the inner ring, outer ring, cage, spacer and single tapered roller of the tapered roller bearing;

[0044] Assemble the components through the assembly module and use the circular array function to generate tapered rollers;

[0045] Export the model to a binary file in x_t format.

[0046] S2, loading the exported bearing model file into the finite element analysis software Abaqus, meshing the bearing model; and performing coarse and fine mesh processing on each component of the bearing model, including the following steps:

[0047] S201. Mesh the inner ring, outer ring and spacer models of the tapered roller bearing: evenly divide the inner ring, outer ring and spacer models of the bearing in the axial direction, ensure that the mesh can be divided into hexahedral units according to the component color prompt in the Abaqus software, mesh the inner ring, outer ring and spacer models after segmentation, set the mesh density to 3mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral units, reduce the integral hourglass control, and generate the mesh models of the inner ring, outer ring and spacer respectively;

[0048] S202, meshing the tapered roller bearing cage model: first, the cage model is divided along the two end faces in contact with the rollers, and then the divided cage model is divided again along the two side faces in contact with the rollers, a total of 34 parts, and the divided cages are meshed in sequence, the unit type is set to a mesh density of 2mm, a minimum deviation factor of 0.2, an eight-node linear hexahedral unit, and a reduced integral hourglass control, to generate a bearing cage mesh model;

[0049] S203. Mesh the roller model of the tapered roller bearing: first divide the tapered roller model into four equal parts along the axial direction, mesh the cage after the division, set the mesh density to 1.5 mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral unit, reduce the integral hourglass control, and generate the tapered roller mesh model.

[0050] S3. Input the contact relationship and contact parameters between the various components of the tapered roller bearing finite element model; in order to better simulate the contact state of the various components inside the bearing, in the Abaqus interaction option, set the outer surface of the bearing inner ring, the front and rear end surfaces of the inner ring, and the inner surface of the outer ring as the first contact surface, and the outer surface and front and rear side surfaces of each tapered roller as the second contact surface. In turn, establish the contact between the outer surface of the bearing inner ring and the outer surface of the tapered roller, the front and rear end surfaces of the bearing inner ring and the front and rear side surfaces of each tapered roller, and the inner surface of the bearing outer ring and the outer surface of the tapered roller. Select the kinematic contact method for mechanical constraints. In the interaction property option, select the hard contact principle in the normal direction of the contact surface, that is, the contact force can only be a compressive force, and contact between the contacting objects is not allowed. There is no geometric penetration between the two surfaces. The static-dynamic friction exponential attenuation principle is used in the tangential direction of the contact surface. This is based on the energy dissipation mechanism and attenuation characteristics of the material or structure under static and dynamic loads. The static friction coefficient is 0.02, the dynamic friction coefficient is 0.05, and the attenuation coefficient is 0.01. The contact relationship is set between the tapered roller and the cage pocket. The outer surface and the front and rear end surfaces of each tapered roller are set as the first surface, and the inner surface of the cage pocket is set as the second surface. In the interaction property option, the general contact principle is selected. This takes into account the geometric deformation, surface morphology, material properties and other factors of the contacting objects, simulates the interaction between objects, calculates the contact force and deformation between objects, and sets the friction coefficient to 0.005.

[0051] In order to meet the loading conditions and boundary conditions of the bearing in actual application conditions, reference points 1, 2, and 3 are established at the center positions of the inner ring, cage, and outer ring of the bearing, respectively. Among them, reference points 1, 2, and 3 are coupled with the outer surfaces of the inner ring, cage, and outer ring of the bearing, respectively, so that the displacements of reference point 1 and the inner surface of the inner ring of the bearing are consistent in six degrees of freedom, namely, translation along the X, Y, and Z directions and rotation around the X, Y, and Z directions. The displacements of reference point 2 and the inner surface of the cage are consistent in six degrees of freedom. The displacements of reference point 3 and the inner surface of the outer ring of the bearing are consistent in three degrees of freedom, namely, translation along the X, Y, and Z directions.

[0052] S4. The radial load condition of the tapered roller of the axle box bearing in the high-speed train vehicle-track coupled dynamics model is calculated and solved by the multi-body dynamics software UM, and the displacement and load boundary conditions are applied; the Abaqus / Explicit analysis solver is used to establish two analysis steps:

[0053] S401. In the first analysis step, the vertical load borne by the bearing is applied at reference point 1, the translational freedom of the inner ring and the cage in the Z direction is released, and the other five degrees of freedom are restricted;

[0054] S402, in the second analysis step, the rotation speed of the bearing is applied at the reference point 1, and the freedom of the inner ring and the retainer in the rotation direction around the Y axis is released;

[0055] S403. The improved implicit integration method is used in the multi-body dynamics software UM, and the radial load results of the axle box bearing obtained by solving the problem have higher numerical stability;

[0056] S404. In Abaqus dynamic analysis, an adaptive time step control mechanism is introduced to dynamically adjust the time step according to the propagation characteristics of stress waves and the current grid size. The propagation speed of stress waves is analyzed to estimate the maximum time step, so as to improve the computational efficiency and numerical stability.

[0057] In order to prevent serious local distortion of the model during the calculation process, the vertical load of the bearing and the rotation speed around the Y-axis are both smooth loading to avoid sudden jump changes; the entire model is also equipped with a gravity load in the Z direction to simulate the effect of gravity on the tapered roller bearing model.

[0058] Embodiment 2: The present invention also provides an axle box bearing for a rail vehicle, comprising an outer ring 1, two sets of opposite retaining frames 2 are arranged on the inner side of the outer ring 1, tapered rollers 3 are installed in the upper grooves of the retaining frames 2, inner rings 4 are arranged on the inner side of the retaining frames 2, and a spacer ring 5 is arranged between the two sets of inner rings 4.

[0059] The contact angle between the tapered roller 3 and the inner ring 4 is 7.55°, the contact angle between the tapered roller 3 and the outer ring 1 is 10°, the outer diameter of the outer ring 1 is 240mm, the diameter of the inner ring 4 is 130mm, the average diameter of the tapered roller 3 is 26mm, and the number of rollers in a single row is 17.

[0060] Outer ring 1, inner ring 4, spacer 5 and cage 2 are all made of high carbon chromium bearing steel. The density of outer ring 1 and inner ring 4 is 7850kg / m 3 , elastic modulus is 206GPa, Poisson's ratio is 0.3; the density of tapered roller 3 and spacer 5 is 7801kg / m 3 , elastic modulus is 207GPa, Poisson's ratio is 0.29; cage 2 is a composite material with a density of 1150kg / m 3 , the elastic modulus is 8.6 GPa, and the Poisson's ratio is 0.4.

[0061] Importantly, it should be noted that the construction and arrangement of the present application shown in a plurality of different exemplary embodiments are only exemplary. Although only a few embodiments are described in detail in this disclosure, it should be readily understood by those who refer to this disclosure that many modifications are possible without substantially departing from the novel teachings and advantages of the subject matter described in this application. Without departing from the scope of the present invention, other replacements, improvements, changes and omissions may be made in the design, operating conditions and arrangement of the exemplary embodiments. Therefore, the present invention is not limited to specific embodiments, but extends to a variety of modifications still falling within the scope of the appended claims.

[0062] Additionally, in order to provide a concise description of exemplary embodiments, all features of an actual embodiment (ie, those features that are not relevant to the best mode presently contemplated for carrying out the invention or those that are not relevant to implementing the invention) may not be described.

[0063] It should be understood that in the development of any actual implementation, as in any engineering or design project, numerous implementation-specific decisions may be made. Such a development effort may be complex and time-consuming, but for those of ordinary skill having the benefit of this disclosure, without undue experimentation, the development effort will be a routine task of design, fabrication, and production.

[0064] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the spirit and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A finite element-based method for analyzing the load characteristics of axle box bearings of rail vehicles, characterized in that: The following steps are involved: S1. According to the outer dimensions of the double-row tapered roller bearing, a three-dimensional solid model of the tapered roller bearing is established in Solidworks software by means of a parametric design method; S2, loading the exported bearing model file into the finite element analysis software Abaqus, and meshing the bearing model using an adaptive meshing method; S3, inputting the contact relationship and contact parameters between the components of the tapered roller bearing finite element model; S4. The radial load results of the tapered rollers in the axle box bearings in the high-speed train vehicle-track coupled dynamics model are calculated and solved using the multi-body dynamics software UM, and the displacement boundary conditions and load boundary conditions are accurately applied.

2. A method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite element analysis as claimed in claim 1, characterized in that: The three-dimensional solid model of the tapered roller bearing established in S1 includes an inner ring, an outer ring, a cage, a spacer ring and a single tapered roller of the tapered roller bearing; Assemble the components through the assembly module and use the circular array function to generate tapered rollers; Export the model as a binary file.

3. The method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite element analysis as claimed in claim 1, characterized in that: S2 performs coarse and fine mesh processing on each component of the bearing model. The following steps are involved: S201. Mesh the inner ring, outer ring and spacer models of the tapered roller bearing: evenly divide the inner ring, outer ring and spacer models of the bearing in the axial direction, ensure that the mesh can be divided into hexahedral units according to the component color prompt in the Abaqus software, mesh the inner ring, outer ring and spacer models after segmentation, set the mesh density to 3mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral units, reduce the integral hourglass control, and generate the mesh models of the inner ring, outer ring and spacer respectively; S202, meshing the tapered roller bearing cage model: first, the cage model is divided along the two end faces in contact with the rollers, and then the divided cage model is divided again along the two side faces in contact with the rollers, a total of 34 parts, and the divided cages are meshed in sequence, the unit type is set to a mesh density of 2mm, a minimum deviation factor of 0.2, an eight-node linear hexahedral unit, and a reduced integral hourglass control, to generate a bearing cage mesh model; S203. Mesh the roller model of the tapered roller bearing: first divide the tapered roller model into four equal parts along the axial direction, mesh the cage after the division, set the mesh density to 1.5 mm, the minimum deviation factor to 0.1, assign the unit type to eight-node linear hexahedral unit, reduce the integral hourglass control, and generate the tapered roller mesh model.

4. The method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite element analysis as claimed in claim 1, characterized in that: The contact relationship and contact parameter input between the components of S3 are as follows: surface-to-surface contact is set between the inner ring and the outer ring of the bearing and the tapered roller respectively, and surface-to-surface contact is also set between the two end surfaces of the inner ring of the bearing and the two end surfaces of the tapered roller. The normal of the contact interface adopts a "hard" contact model, and the tangential contact attribute adopts a static-dynamic attenuation coefficient model, in which the static friction coefficient is 0.02, the dynamic friction coefficient is 0.05, and the attenuation coefficient is 0.01; a general contact model is used between the tapered roller and the cage pocket, the normal attribute of the contact interface adopts a "hard" contact model, the tangential contact attribute adopts a penalty function model, and the friction coefficient is set to 0.005; Reference points 1, 2, and 3 are established at the center positions of the bearing inner ring, cage, and outer ring, respectively. Reference points 1, 2, and 3 are coupled with the outer surfaces of the bearing inner ring, cage, and bearing outer ring, respectively, so that the displacements of reference point 1 and the inner surface of the bearing inner ring are consistent in six degrees of freedom, the displacements of reference point 2 and the inner surface of the cage are consistent in six degrees of freedom, and the displacements of reference point 3 and the inner surface of the bearing outer ring are consistent in three translational degrees of freedom.

5. The method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite element analysis as claimed in claim 4, characterized in that: The S4 fully constrains and fixes the outer ring of the bearing; the Abaqus / Explicit analysis solver is used to establish two analysis steps: S401. In the first analysis step, the vertical load borne by the bearing is applied at reference point 1, the translational freedom of the inner ring and the cage in the Z direction is released, and the other five degrees of freedom are restricted; S402, in the second analysis step, the rotation speed of the bearing is applied at the reference point 1, and the freedom of the inner ring and the retainer in the rotation direction around the Y axis is released; S403. The improved implicit integration method is used in the multi-body dynamics software UM, and the radial load results of the axle box bearing obtained by solving the problem have higher numerical stability; S404. In the Abaqus display dynamics analysis, an adaptive time step control mechanism is introduced to dynamically adjust the time step according to the propagation characteristics of the stress wave and the current grid size, and the propagation speed of the stress wave is analyzed to estimate the maximum time step.

6. A method for analyzing the load characteristics of axle box bearings of rail vehicles based on finite element analysis as claimed in claim 5, characterized in that: The vertical load of the bearing and the speed in the direction of rotation around the Y-axis are both smooth loads; the entire model is provided with a gravity load in the Z direction to simulate the effect of gravity on the tapered roller bearing model.

7. An axle box bearing of a rail vehicle, arranged by using a finite element-based load characteristic analysis method for axle box bearing of a rail vehicle as claimed in claims 1 to 6, characterized in that: It comprises an outer ring (1), two groups of opposite retaining frames (2) are arranged on the inner side of the outer ring (1), tapered rollers (3) are installed in the upper grooves of the retaining frames (2), inner rings (4) are arranged on the inner side of the retaining frames (2), and a spacer ring (5) is arranged between the two groups of inner rings (4).

8. An axle box bearing for a rail vehicle as claimed in claim 7, characterized in that: The contact angle between the tapered roller (3) and the inner ring (4) is 7.55°, the contact angle between the tapered roller (3) and the outer ring (1) is 10°, the outer diameter of the outer ring (1) is 240 mm, the diameter of the inner ring (4) is 130 mm, the average diameter of the tapered roller (3) is 26 mm, and the number of rollers in a single row is 17.

9. The axle box bearing of a rail vehicle according to claim 7, characterized in that: The outer ring (1), inner ring (4), spacer (5) and retainer (2) are all made of high carbon chromium bearing steel. The outer ring (1) and inner ring (4) have a density of 7850 kg / m3, an elastic modulus of 206 GPa and a Poisson's ratio of 0.3; the tapered roller (3) and spacer (5) have a density of 7801 kg / m3, an elastic modulus of 207 GPa and a Poisson's ratio of 0.29; the retainer (2) is a composite material with a density of 1150 kg / m3, an elastic modulus of 8.6 GPa and a Poisson's ratio of 0.4.

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