Spiral bevel gear mixed elastohydrodynamic lubrication analysis method and device based on surface roughness

Abstract

The invention discloses a spiral bevel gear mixed elastohydrodynamic lubrication analysis method and device based on surface roughness, and relates to the field of gear monitoring. Calculating a tooth surface curvature radius change sequence, an entrainment speed size and direction change sequence and a contact ellipse long and short axis change sequence by using a gear dynamics algorithm; and according to the tooth surface curvature radius change sequence, the entrainment speed and direction change sequence, the contact ellipse long and short axis change sequence and the surface topography matrix, a multi-physics field coupling thermal elastohydrodynamic mixed lubrication model is used for conducting mixed elastohydrodynamic lubrication analysis on the target spiral bevel gear, and elastohydrodynamic lubrication characteristic parameters of the target spiral bevel gear are obtained. According to the method, the accuracy of mixed elastohydrodynamic lubrication analysis of the spiral bevel gear is improved, and the problem of oil film temperature detection lag is solved.

Description

Technical Field

[0001] The present application relates to the field of gear monitoring, and in particular to a surface roughness-based hybrid elastohydrodynamic lubrication analysis method and device for spiral bevel gears. Background Art

[0002] Spiral bevel gears have complex spatial meshing characteristics and are often used as core components of high-speed, heavy-load mechanical transmissions. Their lubrication performance directly affects the reliability and life of the equipment.

[0003] Existing research shows that surface roughness can significantly change the oil film pressure, thickness, and temperature distribution of elastohydrodynamic lubrication (ELHL). However, in the lubrication analysis of spiral bevel gears, roughness characterization is mostly based on numerical simulation, lacking consideration of the actual machined surface morphology. This results in low accuracy in the mixed ELHL analysis of spiral bevel gears and the problem of delayed oil film temperature detection. Summary of the Invention

[0004] The purpose of this application is to provide a surface roughness-based hybrid elastohydrodynamic lubrication analysis method and equipment for spiral bevel gears, which can improve the accuracy of hybrid elastohydrodynamic lubrication analysis of spiral bevel gears and solve the problem of oil film temperature detection lag under real rough surfaces.

[0005] To achieve the above objectives, this application provides the following solutions.

[0006] In the first aspect, the present application provides a hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness, the hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness comprises: obtaining the large and small wheel structural parameters, thermal conductivity parameters, lubricating oil physical parameters and surface morphology matrix of the target spiral bevel gear; the surface morphology matrix is ​​a matrix obtained by measuring the tooth surface contact area of ​​the target spiral bevel gear using a white light interferometer and performing two-dimensionalization; based on the large and small wheel structural parameters, thermal conductivity parameters and lubricating oil physical parameters of the target spiral bevel gear, the gear dynamics algorithm is used to calculate the tooth surface curvature radius, the entrainment velocity and the maximum entrainment velocity. The changes of the magnitude and direction of the entrainment velocity and the major and minor axes of the contact ellipse with time during the process from engagement to engagement are obtained, and the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, and the contact ellipse major and minor axis change sequence are obtained; based on the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, the contact ellipse major and minor axis change sequence and the surface morphology matrix, a multi-physics field coupled thermal elastohydrodynamic mixed lubrication model is used to perform a mixed elastohydrodynamic lubrication analysis on the target spiral bevel gear, and the elastohydrodynamic lubrication characteristic parameters of the target spiral bevel gear are obtained; the elastohydrodynamic lubrication characteristic parameters include at least: oil film pressure, film thickness and temperature distribution in the tooth surface contact area.

[0007] In a second aspect, the present application provides a computer device comprising: a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the above-mentioned surface roughness-based hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears.

[0008] According to the specific embodiments provided in this application, this application discloses the following technical effects.

[0009] This application uses a gear dynamics algorithm to calculate the tooth surface curvature radius variation sequence, the entrainment velocity magnitude and direction variation sequence, and the contact ellipse major and minor axis variation sequence based on the target spiral bevel gear's wheel and gear structural parameters, thermal conductivity parameters, and lubricant physical parameters. Based on the tooth surface curvature radius variation sequence, the entrainment velocity magnitude and direction variation sequence, the contact ellipse major and minor axis variation sequence, and the surface topography matrix, a multi-physics field coupled thermal elastohydrodynamic mixed lubrication model is used to perform a mixed elastohydrodynamic lubrication analysis on the target spiral bevel gear, obtaining the elastohydrodynamic lubrication characteristic parameters of the target spiral bevel gear. This application improves the accuracy of the mixed elastohydrodynamic lubrication analysis of spiral bevel gears and solves the problem of oil film temperature detection lag. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] In order to more clearly illustrate the technical solutions in the embodiments of the present application or related technologies, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0011] Figure 1 A flow chart of a hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness provided in an embodiment of the present application.

[0012] Figure 2 This is a curve diagram of the tooth surface curvature radius change sequence provided in an embodiment of the present application.

[0013] Figure 3 A curve diagram showing the change sequence of the suction speed and direction provided in the embodiment of the present application.

[0014] Figure 4 A curve diagram of the change sequence of the major and minor axes of the contact ellipse provided in an embodiment of the present application.

[0015] Figure 5 Schematic diagram of the initial morphology and surface morphology matrix of the spiral bevel gear under different processing methods provided in the embodiment of the present application; wherein, Figure 5 (a) is the initial surface morphology under polishing mode; Figure 5 (b) is the surface morphology matrix diagram under polishing mode; Figure 5(c) is the initial surface morphology under the grinding mode; Figure 5 (d) is the surface morphology matrix diagram under the grinding mode; Figure 5 (e) is the initial surface morphology under turning mode; Figure 5 (f) is the surface morphology matrix diagram under turning mode; Figure 5 (g) is the initial surface morphology under the milling cutting mode; Figure 5 (h) is the surface morphology matrix diagram under milling method.

[0016] Figure 6 Schematic diagram of mixed elastohydrodynamic lubrication contact on rough surfaces provided in an embodiment of the present application.

[0017] Figure 7 The oil film characteristic diagram of the polishing surface contact area provided in the embodiment of the present application; wherein, Figure 7 (a) is the oil film pressure diagram of the tooth surface contact area under the polishing method; Figure 7 (b) is the film thickness diagram of the tooth surface contact area under the polishing method; Figure 7 (c) in the figure is the temperature distribution diagram of the tooth surface contact area under the polishing method.

[0018] Figure 8 The oil film characteristic diagram of the grinding surface contact area provided in the embodiment of the present application; wherein, Figure 8 (a) is the oil film pressure diagram of the tooth surface contact area under the grinding mode; Figure 8 (b) is the film thickness diagram of the tooth contact area under the grinding mode; Figure 8 (c) in the figure is the temperature distribution diagram of the tooth surface contact area under the grinding method.

[0019] Figure 9 The oil film characteristic diagram of the contact area of ​​the turning surface provided in the embodiment of the present application; wherein, Figure 9 (a) is the oil film pressure diagram of the tooth surface contact area under turning mode; Figure 9 (b) is the film thickness diagram of the tooth contact area under turning mode; Figure 9 (c) in the figure is the temperature distribution diagram of the tooth surface contact area under turning.

[0020] Figure 10 The oil film characteristic diagram of the milling surface contact area provided in the embodiment of the present application; wherein, Figure 10 (a) is the oil film pressure diagram of the tooth surface contact area under the milling method; Figure 10 (b) is the film thickness diagram of the tooth surface contact area under the milling method; Figure 10 (c) in the figure is the temperature distribution diagram of the tooth surface contact area under milling method.

[0021] Figure 11A schematic diagram of the structure of a computer device provided in an embodiment of the present application. DETAILED DESCRIPTION

[0022] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0023] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the present application is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0024] Example 1, as Figure 1 As shown, this embodiment provides a hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness, and the method includes the following steps.

[0025] S1. Obtain the gear and wheel structural parameters, thermal conductivity parameters, lubricant physical parameters, and surface topography matrix of the target spiral bevel gear. The surface topography matrix is ​​a matrix obtained by measuring the tooth surface contact area of ​​the target spiral bevel gear using a white light interferometer and converting it into two dimensions. It is used to characterize the surface roughness of the tooth surface contact area of ​​the target spiral bevel gear.

[0026] Furthermore, the structural parameters of the large and small wheels specifically include: axis intersection angle, large end face module, number of teeth, tooth width, midpoint helix angle, outer cone pitch, sub-cone angle, root cone angle, face cone angle, tooth top height and tooth root height; the thermal conductivity parameters specifically include: Poisson's ratio, density, thermal conductivity coefficient and specific heat coefficient; the physical parameters of the lubricating oil specifically include: viscosity, density, viscosity-pressure coefficient, viscosity-temperature coefficient, thermal conductivity coefficient, specific heat coefficient and ambient temperature.

[0027] In actual application, taking a pair of spiral bevel gears as an example, the large gear rotates right and the small gear rotates left, the overlap is 2.83, and the input speed of the small gear is 5000r / min. The structural parameters, thermal conductivity parameters, and physical parameters of the lubricating oil of the target spiral bevel gears are shown in Tables 1 to 3.

[0028] Table 1 Structural parameters of spiral bevel gears, large and small wheels

[0029]

[0030] Table 2 Thermal conductivity related parameters of spiral bevel gears

[0031] parameter Numerical <![CDATA[Poisson's ratio υ 1,2 > 0.3 <![CDATA[Density ρ 1,2 (kg / m 3 )]]> 7850 <![CDATA[Thermal conductivity k 1,2 (m·K)]]> 48 <![CDATA[Specific heat coefficient c 1,2 (J / Kg·K)]]> 460

[0032] Table 3 Lubricant related physical parameters

[0033] parameter Numerical <![CDATA[Viscosity η0 (Pa·S)]]> 0.033 <![CDATA[Density ρ0 (Kg / m 3 )]]> 970 <![CDATA[Coefficient of viscous pressure α (GPa -1 )]]> 18.5 <![CDATA[Viscosity-temperature coefficient β (K -1 )]]> 0.032 <![CDATA[Thermal conductivity C f (m·K)]]> 0.0966 <![CDATA[Specific heat coefficient K f (J / Kg·K)]]> 1910 <![CDATA[Ambient temperature T0 (K)]]> 300

[0034] Further, if Figure 5 As shown in FIG, the process of obtaining the surface topography matrix is ​​as follows: a white light interferometer is used to measure the tooth surface contact area of ​​the target spiral bevel gear to obtain initial topography data; the initial topography data is three-dimensional data; the initial topography data is converted into two dimensions to obtain a surface topography matrix; the surface topography matrix is ​​two-dimensional data.

[0035] In actual application, white light interferometry is used to measure the surface morphology of grinding, turning, milling and polishing disc specimens (the material is 9310 steel), and 129×129 node data are extracted and expressed as z(x, y).

[0036] S2. Figure 2-Figure 4 As shown in the figure, based on the structural parameters of the large and small wheels, thermal conductivity parameters and physical parameters of the lubricating oil of the target spiral bevel gear, the gear dynamics algorithm is used to calculate the changes of the tooth surface curvature radius, the magnitude and direction of the entrainment velocity, and the major and minor axes of the contact ellipse during the process from engagement to engagement. The change sequence of the tooth surface curvature radius, the change sequence of the magnitude and direction of the entrainment velocity, and the change sequence of the major and minor axes of the contact ellipse are obtained.

[0037] Furthermore, the gear dynamics algorithm includes at least: a tooth surface contact analysis algorithm.

[0038] In actual application, the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, and the contact ellipse major and minor axis change sequence are used as dynamic parameters of the gear meshing process, providing key boundary conditions for constructing a multi-physics field coupled thermal-elastic-hydrodynamic mixed lubrication model.

[0039] S3. Based on the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, the contact ellipse major and minor axis change sequence and the surface morphology matrix, a multi-physics field coupled thermal elastohydrodynamic mixed lubrication model is used to perform a mixed elastohydrodynamic lubrication analysis on the target involute bevel gear to obtain the elastohydrodynamic lubrication characteristic parameters of the target involute bevel gear; the elastohydrodynamic lubrication characteristic parameters include at least: oil film pressure, film thickness and temperature distribution in the tooth surface contact area.

[0040] Further, if Figure 6 As shown, step S3 specifically includes the following steps.

[0041] S31. Input the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, the contact ellipse major and minor axis change sequence and the surface morphology matrix into the multi-physics field coupled thermal-elastic-hydrodynamic mixed lubrication model.

[0042] S32. The multi-grid method is used to solve the multi-physics field coupled thermal-elastic-hydrodynamic mixed lubrication model to obtain the elastic deformation of the target spiral bevel gear.

[0043] Furthermore, the calculation formula of elastic deformation is as follows.

[0044]

[0045] Where v(x,y) represents the elastic deformation of the target point (x,y); E' represents the combined elastic modulus of the upper and lower contact surfaces; p(x',y') represents the pressure at the action point (x',y'); and Ω represents the elliptical contact area.

[0046] S33. The oil film pressure and film thickness of the multi-physics field coupled thermal-elastic-hydrodynamic mixed lubrication model are iteratively solved by the progressive mesh encryption method to obtain the oil film pressure and film thickness of the target spiral bevel gear.

[0047] Furthermore, the solution process of the oil film pressure is as follows.

[0048] The Gauss-Seidel and Jacobi dipole iteration methods are used to numerically solve the oil film pressure to obtain the oil film pressure; among them, the Gauss-Seidel iteration method is used in the low pressure area; the Jacobi dipole iteration method is used in the high pressure area.

[0049] Furthermore, the calculation formula for the target film thickness of the spiral bevel gear is as follows.

[0050]

[0051] Where h is the film thickness of the tooth surface contact area of ​​the target spiral bevel gear, h0 represents the film thickness at the center of the rigid body, R x 、R y They represent the comprehensive curvature radius in the x and y directions respectively, v(x, y) represents the elastic deformation, and z(x, y) is the surface topography matrix.

[0052] S34. Based on the oil film pressure and film thickness, a coupled iterative method is used to solve the energy equation to obtain the temperature distribution.

[0053] Furthermore, the solution process of temperature distribution is as follows.

[0054] Based on the oil film pressure and film thickness, the viscosity and density are determined using the oil film flow velocity equation (velocity field), viscosity-pressure-temperature equation, and density-pressure-temperature equation. The temperature field is obtained by solving the energy equation based on the viscosity and density. The oil film pressure and film thickness are re-iteratively calculated based on the temperature field until the pressure and temperature converge, and finally the temperature distribution is obtained in a self-consistent manner.

[0055] like Figure 7-10 As shown in the figure, it can be seen that due to the discontinuous cutting process and the continuous changes in cutting layer parameters, the lubrication characteristics of the milling surface are relatively poor, the maximum pressure is as high as about 3GPa, and the maximum temperature is as high as about 300℃, which makes it easy to fail.

[0056] In practical applications, the solution of oil film pressure, oil film thickness, and oil film energy in elastohydrodynamic lubrication theory is strongly coupled: the Reynolds equation takes the oil film thickness h and the lubricant physical properties η and ρ as inputs, and outputs the oil film pressure p. The oil film pressure p modifies the oil film thickness h via the elastic deformation v(x,y) equation. The pressure p and thickness h jointly determine the velocity field (the oil film velocity equation) and the viscosity and density fields (the viscosity-pressure-temperature equation and the density-pressure-temperature equation), thereby controlling the dissipation and storage of oil film energy (the oil film energy equation). Temperature changes caused by energy dissipation alter the viscosity η and density ρ, negatively affecting the calculation of the Reynolds equation and elastic deformation.

[0057] In this embodiment, the formulas of the equations are as follows.

[0058] 1) Reynolds equation is as follows.

[0059]

[0060] Wherein, the positive directions of the x-axis and y-axis respectively represent the minor and major axes that form acute angles with the entrainment velocity at the meshing point, ρ is the lubricating oil density, h is the film thickness, p is the pressure, η is the lubricating oil viscosity, u and v represent the entrainment velocities of the lubricating oil along the major and minor axes of the contact ellipse, respectively, and t represents the single tooth meshing time of the spiral bevel gear.

[0061] 2) The viscosity-pressure-temperature equation is as follows.

[0062]

[0063] Where η0 is the viscosity of the lubricating oil at normal pressure, T0 is the initial temperature, and Z and S are both calculation indices.

[0064] 3) The density-pressure-temperature equation is as follows.

[0065]

[0066] Where ρ0 is the initial density, D = 0.0007K -1 .

[0067] 4) The load balance equation is as follows.

[0068]

[0069] Where Q is the applied external load, that is, the load at the gear meshing point.

[0070] 5) The oil film flow velocity equation is as follows.

[0071] The entrainment velocity of the lubricating oil along the major and minor axis directions is as follows.

[0072]

[0073] Where u1 and u2 are the velocities of the solid along the x-direction, and v1 is the velocity of the solid along the y-direction.

[0074] The velocity gradients of the lubricating oil along the major and minor axes are as follows.

[0075]

[0076] 6) The oil film energy equation is as follows.

[0077]

[0078] Where, c p is the heat transfer coefficient, k is the specific heat coefficient, and T is the oil film temperature.

[0079] The technical effects of this application are as follows.

[0080] 1) This application integrates numerical simulations with measured surface topography data to construct a multi-physics coupled model for hybrid elastohydrodynamic lubrication of spiral bevel gears based on realistic roughness characteristics. Compared to traditional single numerical simulation methods, this model dynamically correlates texture characteristics with lubrication behavior, accurately characterizing the differential effects of surface topography generated by different processes, such as grinding and milling, on oil film pressure fluctuations, temperature gradients, and necking effects.

[0081] 2) To address the complex meshing characteristics of spiral bevel gears, a coupled thermal-elastic-hydrodynamic solution based on progressive mesh refinement and multi-directional stress transfer was proposed. Combined with white-light interferometric 3D topography reconstruction, this approach overcomes the challenge of oil film temperature hysteresis on realistically rough surfaces. This approach transcends the traditional elastohydrodynamic lubrication model's reliance on ideally smooth surfaces and establishes a mapping system between machining parameters, surface topography, and lubrication performance indicators. This provides key technical support for high-precision gear surface integrity design and lubrication optimization, filling a gap in the research on complex gear lubrication mechanisms.

[0082] Example 2: This application also provides a computer device, which can be a server or a terminal, and its internal structure diagram can be as follows: Figure 11As shown. The computer device includes a processor, a memory, an input / output interface (Input / Output, abbreviated as I / O) and a communication interface. The processor, memory and input / output interface are connected through a system bus, and the communication interface is connected to the system bus through the input / output interface. The processor of the computer device is used to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system, a computer program and a database. The internal memory provides an environment for the operation of the operating system and computer program in the non-volatile storage medium. The database of the computer device is used to store processing data. The input / output interface of the computer device is used to exchange information between the processor and an external device. The communication interface of the computer device is used to communicate with an external terminal through a network connection. When the computer program is executed by the processor, the above-mentioned methods are implemented.

[0083] Those skilled in the art will understand that Figure 11 The structure shown in the figure is only a block diagram of a part of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied. The specific computer device may include more or fewer components than shown in the figure, or combine certain components, or have a different component arrangement.

[0084] Those skilled in the art will understand that all or part of the processes in the above-mentioned embodiment methods can be implemented by instructing the relevant hardware through a computer program, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to memory, database or other media used in the embodiments provided in this application may include at least one of non-volatile and volatile memory. Non-volatile memory may include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetic random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory may include random access memory (RAM) or external cache memory, etc. By way of illustration and not limitation, RAM may be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM).

[0085] The technical features of the above embodiments can be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0086] This document uses specific examples to illustrate the principles and implementation methods of this application. The description of the above examples is only intended to help understand the method and core concept of this application. At the same time, for those skilled in the art, based on the concept of this application, there may be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as limiting this application.

Claims

1. A hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness, characterized in that: The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness includes: Obtaining the gear and wheel structural parameters, thermal conductivity parameters, lubricant physical parameters, and surface topography matrix of the target spiral bevel gear; the surface topography matrix is ​​obtained by measuring the tooth surface contact area of ​​the target spiral bevel gear using a white light interferometer and converting it into a two-dimensional matrix, and is used to characterize the surface roughness of the tooth surface contact area of ​​the target spiral bevel gear; Based on the structural parameters of the large and small wheels, thermal conductivity parameters, and physical parameters of the lubricant of the target spiral bevel gear, a gear dynamics algorithm was used to calculate the time-varying changes in the tooth surface curvature radius, the magnitude and direction of the entrainment velocity, and the major and minor axes of the contact ellipse from engagement to disengagement. The resulting series of changes in the tooth surface curvature radius, the magnitude and direction of the entrainment velocity, and the major and minor axes of the contact ellipse were obtained. Based on the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, the contact ellipse major and minor axis change sequence and the surface morphology matrix, a multi-physics field coupled thermal elastohydrodynamic mixed lubrication model is used to perform a mixed elastohydrodynamic lubrication analysis on the target spiral bevel gear, and the elastohydrodynamic lubrication characteristic parameters of the target spiral bevel gear are obtained; the elastohydrodynamic lubrication characteristic parameters include at least: oil film pressure, film thickness and temperature distribution in the tooth surface contact area.

2. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 1, characterized in that: The structural parameters of the large and small wheels specifically include: axis intersection angle, large end face module, number of teeth, tooth width, midpoint helix angle, outer cone pitch, sub-cone angle, root cone angle, face cone angle, tooth addendum height and tooth root height; The thermal conductivity parameters specifically include: Poisson's ratio, density, thermal conductivity and specific heat coefficient; The physical parameters of the lubricating oil specifically include: viscosity, density, viscosity-pressure coefficient, viscosity-temperature coefficient, thermal conductivity, specific heat coefficient and ambient temperature.

3. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 1, characterized in that: The acquisition process of the surface topography matrix is ​​as follows: The tooth surface contact area of ​​the target spiral bevel gear is measured using a white light interferometer to obtain initial topography data; the initial topography data is three-dimensional data; The initial topography data is converted into two dimensions to obtain a surface topography matrix; the surface topography matrix is ​​two-dimensional data.

4. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 1, characterized in that: The gear dynamics algorithm at least includes: a tooth surface contact analysis algorithm.

5. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 1, characterized in that: Based on the tooth surface curvature radius change sequence, the entrainment velocity magnitude and direction change sequence, the contact ellipse major and minor axis change sequence, and the surface topography matrix, a multi-physics field coupled thermal elastohydrodynamic lubrication model is used to perform a mixed elastohydrodynamic lubrication analysis on the target spiral bevel gear. The elastohydrodynamic lubrication characteristic parameters of the target spiral bevel gear are obtained, including: The tooth surface curvature radius variation sequence, the entrainment velocity magnitude and direction variation sequence, the contact ellipse major and minor axis variation sequence, and the surface morphology matrix are input into the multi-physics field coupled thermoelastic-hydrodynamic mixed lubrication model; The multi-grid method is used to solve the multi-physics field coupled thermoelastic-hydrodynamic mixed lubrication model to obtain the elastic deformation of the target spiral bevel gear. The oil film pressure and film thickness of the multi-physics field coupled thermoelastic-hydrodynamic lubrication model are solved iteratively by using the progressive mesh refinement method to obtain the oil film pressure and film thickness of the target spiral bevel gear. Based on the oil film pressure and film thickness, the temperature distribution is obtained by solving the energy equation using a coupled iterative method.

6. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 5, characterized in that: The calculation formula of the elastic deformation is as follows: Where v(x,y) represents the elastic deformation of the target point (x,y); E' represents the combined elastic modulus of the upper and lower contact surfaces; p(x',y') represents the pressure at the action point (x',y'); and Ω represents the elliptical contact area.

7. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 5, characterized in that: The solution process of the oil film pressure is as follows: The Gauss-Seidel and Jacobi dipole iteration methods are used to numerically solve the oil film pressure and obtain the oil film pressure.

8. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 5, characterized in that: The calculation formula of the film thickness of the target spiral bevel gear is as follows: Where h is the film thickness of the tooth surface contact area of ​​the target spiral bevel gear, h0 represents the film thickness at the center of the rigid body, and R x 、R y They represent the comprehensive curvature radius in the x and y directions respectively, v(x, y) represents the elastic deformation, and z(x, y) is the surface topography matrix.

9. The hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears based on surface roughness according to claim 5, characterized in that: The solution process of the temperature distribution is as follows: Based on the oil film pressure and film thickness, the viscosity and density are determined using the oil film velocity equation, the viscosity-pressure-temperature equation, and the density-pressure-temperature equation. Solve the energy equation based on viscosity and density to obtain the temperature field; The oil film pressure and film thickness are recalculated iteratively based on the temperature field until the pressure and temperature converge, and finally the temperature distribution is obtained in a self-consistent manner.

10. A computer device comprising: A memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the surface roughness-based hybrid elastohydrodynamic lubrication analysis method for spiral bevel gears according to any one of claims 1 to 9.

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