A method, device, medium and product for calculating load distribution coefficient between gear teeth

Abstract

The present invention discloses a method, device, medium, and product for calculating the load distribution coefficient between gear teeth, relating to the field of gear load distribution. The method comprises obtaining tooth profile data of a spur gear; calculating the gear meshing stiffness based on the tooth profile data; the gear meshing stiffness is a stiffness that takes into account gear tooth deformation, gear base deformation, and contact deformation; calculating the potential energy of the spur gear based on the gear meshing stiffness; determining a normal contact force constraint; the normal contact force constraint is determined according to the general form of the load torque expression; determining a solution constraint based on the normal contact force constraint and the potential energy of the spur gear; and solving the solution constraint to obtain a final load distribution coefficient. The present invention can improve the calculation accuracy of the load distribution coefficient and reduce the calculation time.

Description

Technical Field

[0001] The present invention relates to the field of gear load distribution, and in particular to a method, device, medium and product for calculating a load distribution coefficient between gear teeth. Background Art

[0002] During the meshing process, a gear pair experiences single-tooth and double-tooth meshing intervals, resulting in different normal forces acting on the tooth surfaces. Calculating the load distribution coefficient reveals the variation in the normal force acting on a particular tooth within the meshing cycle. Accurately calculating the load distribution coefficient is crucial for strength verification calculations of gears with multiple tooth pairs meshing.

[0003] Current methods for calculating the load distribution coefficient include traditional methods and the finite element method (FEM). The traditional method calculates the load distribution coefficient using mesh stiffness and an analytical meshing model. However, its accuracy is limited by the analytical meshing model. The contact deformation formula used in this analytical meshing model has large errors, and the normal contact force constraint is not applicable to non-involute gears. This results in a low-precision load distribution coefficient. While the FEM method provides a more accurate load distribution coefficient, it requires the establishment of a finite element model. For complex situations, calculating the load distribution coefficient using the FEM method can require significant computational resources and time, increasing the cost and complexity of the calculation. Summary of the Invention

[0004] The purpose of the present invention is to provide a method, device, medium and product for calculating the load distribution coefficient between gear teeth, which can improve the calculation accuracy of the load distribution coefficient and reduce the calculation time.

[0005] To achieve the above object, the present invention provides the following solutions:

[0006] In a first aspect, the present invention provides a method for calculating a load distribution coefficient between gear teeth, the method comprising:

[0007] The tooth profile data of the spur gear is obtained; the tooth profile data includes: the shape of the entire tooth profile, the relative curvature of each point, the direction of the normal contact force and the meshing position at all contact moments.

[0008] The gear meshing stiffness is calculated based on the tooth profile data of the spur gear; the gear meshing stiffness is a stiffness that takes into account gear tooth deformation, gear base deformation, and contact deformation.

[0009] Based on the gear mesh stiffness, the potential energy of the spur gear is calculated.

[0010] A normal contact force constraint is determined; the normal contact force constraint is determined according to a general form of a load torque expression.

[0011] A solution constraint is determined according to the normal contact force constraint and the potential energy of the spur gear.

[0012] The solution constraints are solved to obtain a final load distribution coefficient.

[0013] In a second aspect, the present invention 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 any one of the above-described methods for calculating the load distribution coefficient between gear teeth.

[0014] In a third aspect, the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements any one of the above-mentioned methods for calculating the load distribution coefficient between gear teeth.

[0015] In a fourth aspect, the present invention provides a computer program product, comprising a computer program, which, when executed by a processor, implements any one of the above-mentioned methods for calculating the load distribution coefficient between gear teeth.

[0016] According to the specific embodiments provided by the present invention, the present invention discloses the following technical effects:

[0017] The present invention provides a method, device, medium, and product for calculating the load distribution coefficient between gear teeth. By obtaining tooth profile data and calculating the gear mesh stiffness based on the tooth profile data, the potential energy of the spur gear can be calculated based on the gear mesh stiffness. The load distribution coefficient can then be solved using the potential energy of the spur gear and a determined normal contact force constraint. The present invention improves upon the contact deformation formula used in traditional methods, expands the normal contact force constraint into a universal form, and simplifies the meshing analytical model, resulting in more accurate calculation results than traditional calculation methods. Furthermore, the present invention uses an analytical method to solve the load distribution coefficient, eliminating the need for a finite element model, thus saving computation time. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0019] Figure 1 FIG2 is an application environment diagram of a method for calculating a load distribution coefficient between gear teeth in one embodiment of the present invention.

[0020] Figure 2A schematic flow chart of a method for calculating a load distribution coefficient between gear teeth provided by one embodiment of the present invention.

[0021] Figure 3 A diagram of a gear cantilever beam model provided for an embodiment of the present invention.

[0022] Figure 4a A schematic diagram of a single pair of teeth meshing according to an embodiment of the present invention.

[0023] Figure 4b A schematic diagram of an analytical model of a single pair of teeth meshing provided by an embodiment of the present invention.

[0024] Figure 5a A schematic diagram of two pairs of teeth meshing according to an embodiment of the present invention.

[0025] Figure 5b A schematic diagram of an analytical model of double-pair tooth meshing provided by an embodiment of the present invention.

[0026] Figure 6 A schematic diagram of the direction of normal contact force when two pairs of teeth are engaged provides an embodiment of the present invention.

[0027] Figure 7 A comparison chart of three methods for calculating the inter-tooth load distribution coefficient of involute gears provided in one embodiment of the present invention.

[0028] Figure 8 A comparison chart of three methods for calculating the inter-tooth load distribution coefficient of a non-involute gear (gear with constant relative curvature) provided in one embodiment of the present invention.

[0029] Figure 9 A schematic diagram of the structure of a computer device provided in one embodiment of the present invention. DETAILED DESCRIPTION

[0030] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0031] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0032] The method for calculating the load distribution coefficient between gear teeth provided by the embodiment of the present invention can be applied to Figure 1In the application environment shown, the terminal 102 communicates with the server 104 via a network. The data storage system can store data that the server 104 needs to process. The data storage system can be set up separately, integrated on the server 104, or placed on the cloud or other servers. Terminal 102 can send the acquired tooth profile data of the spur gear to server 104. The tooth profile data includes: the shape of the entire tooth profile, the relative curvature of each point, the direction of the normal contact force, and the meshing position at all contact moments. After receiving the tooth profile data, server 104 calculates the gear mesh stiffness based on the tooth profile data of the spur gear. The gear mesh stiffness is a stiffness that takes into account gear tooth deformation, gear base deformation, and contact deformation. Based on the gear mesh stiffness, the potential energy of the spur gear is calculated. A normal contact force constraint is determined. The normal contact force constraint is determined according to the general form of the load torque expression. A solution constraint is determined based on the normal contact force constraint and the potential energy of the spur gear. The solution constraint is solved to obtain a final load distribution coefficient. Server 104 can provide feedback to terminal 102 on the final load distribution coefficient obtained. In addition, in some embodiments, the method for calculating the load distribution coefficient between gear teeth can also be implemented separately by the server 104 or the terminal 102. For example, the terminal 102 can directly calculate the load distribution coefficient for the acquired tooth profile data, or the server 104 can obtain the tooth profile data from the data storage system and calculate the load distribution coefficient for the tooth profile data.

[0033] In an exemplary embodiment, Figure 2 As shown, a method for calculating the load distribution coefficient between gear teeth is provided. The method is executed by a computer device, specifically, it can be executed by a computer device such as a terminal or a server alone, or it can be executed by a terminal and a server together. In an embodiment of the present invention, the method is applied to Figure 1 The server 104 in the example is used as an example to illustrate the method, which includes the following steps S1 to S6.

[0034] S1: Acquire tooth profile data; the tooth profile data includes: the shape of the entire tooth profile, the relative curvature of each point, the direction of the normal contact force and the meshing position of all contact moments.

[0035] The tooth profile data is required to describe the shape of the entire tooth profile, the relative curvature of each point, and the direction of the normal contact force; the meshing period of a pair of teeth is divided into two double-pair tooth meshing intervals and one single-pair tooth meshing interval, with a total of m contact moments. At this time, the position of the meshing point of the two pairs of teeth relative to the gear teeth at each contact moment in the double-pair tooth meshing interval is obtained until the meshing position of all contact moments is obtained.

[0036] S2: Calculating the gear meshing stiffness based on the tooth profile data of the spur gear; the gear meshing stiffness is a stiffness that takes into account gear tooth deformation, gear base deformation, and contact deformation.

[0037] Gear tooth meshing produces deformation, with the main factors influencing the load distribution coefficient being tooth deformation, gear matrix deformation, and contact deformation. Since the gear matrix stiffness has a minimal effect on the load distribution coefficient, the gear matrix deformation is neglected. The gear tooth is considered a cantilever beam with a variable cross-section, fixed to a vertical section. The tooth is divided into k cross-sectional elements i along the tooth centerline. Each element is considered to have its left end fixed and the portion connected to the right end face as a rigid body. The deformation of the element is calculated using Timoshenko beam theory. The deformation at the meshing point is obtained by superimposing the element deformation from the meshing point to the fixed surface.

[0038] The gear tooth deformation includes bending deformation, shear deformation and compression deformation.

[0039] The calculation formula for the bending deformation is:

[0040]

[0041] The calculation formula of the shear deformation is:

[0042]

[0043] The calculation formula for the compression deformation is:

[0044]

[0045] Among them, δ bb is the bending deformation, W b is the normal contact force at the meshing point b, E e is the equivalent elastic modulus, when B / H p >5, take E e =E / (1-v 2 ), otherwise take Ee=E, E is the elastic modulus of the material used, H p is the tooth thickness at the node, B is the gear width, I i is the moment of inertia of element i, L i is the thickness of element i, β b is the angle between the normal contact force at meshing point b and the y-axis, S ib Y is the distance between the projection of the infinitesimal element i and the meshing point b on the x-axis, b is the half tooth thickness at the meshing point b, k is the total number of cross-sectional elements, δ sb is shear deformation, A i is the cross-sectional area of ​​element i, ν is Poisson’s ratio, δ pb Compression deformation.

[0046] The calculation formula of the contact deformation is:

[0047]

[0048] Among them, δ hb is the contact deformation, W b is the normal contact force, ν is the Poisson's ratio, E is the elastic modulus of the material used for the gear teeth, B is the gear width, and Y b1 is the half tooth thickness of the first gear at the meshing point b, Y b2 is the half tooth thickness of the second gear at the meshing point b, and c is the Hertzian contact half width.

[0049] Simplify the meshing model of two pairs of teeth and use the integral method to calculate the elastic potential energy. The formula is as follows:

[0050]

[0051] Among them, U h is the elastic potential energy, δ h is the contact deformation, and F is the load size.

[0052] S3: Calculate the potential energy of the spur gear based on the gear meshing stiffness.

[0053] The potential energy of the spur gear is expressed as:

[0054]

[0055] Where U is the potential energy of the spur gear, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, δ M1 is the tooth deformation of the first gear at the meshing point b, δ M2 is the tooth deformation of the second gear at the meshing point b, δ M3 is the tooth deformation of the first gear at the meshing point a, δ M4 is the tooth deformation of the second gear at the meshing point a, U ha is the elastic potential energy calculated based on the contact deformation at the meshing point a, U hb is the elastic potential energy calculated based on the contact deformation at the meshing point b.

[0056] S4: Determine a normal contact force constraint; the normal contact force constraint is determined according to a general form of a load torque expression.

[0057] The constraint of normal contact force is expanded into a general form, and the calculation formula is as follows:

[0058] F a R a +Fb R b =T;

[0059] Among them, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, R a R is the distance from the center of the load gear to the meshing point a in the direction of the meshing force, b is the distance from the center of the load gear to the meshing point b in the direction of the meshing force, and T is the load torque.

[0060] In this case, the load distribution coefficient is redefined and the load distribution coefficient when a certain tooth is meshing at a is solved as follows:

[0061]

[0062] S5: Determine solution constraints based on the normal contact force constraint and the potential energy of the spur gear.

[0063] The expression for solving the constraint is:

[0064]

[0065] Where U is the potential energy of the spur gear, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, R a R is the distance from the center of the load gear to the first meshing force direction, b is the distance from the center of the load gear to the second meshing force direction, and T is the load torque.

[0066] S6: Solve the solution constraints to obtain the final load distribution coefficient.

[0067] Implementing the above steps S1 to S6 simplifies the meshing analytical model, and the calculation results are more accurate than those of traditional methods. At the same time, the present invention uses an analytical method to solve the load distribution coefficient without using a finite element model, saving calculation time.

[0068] In another exemplary embodiment of the present invention, step S6 specifically includes:

[0069] S61: Determine the initial load distribution coefficient.

[0070] S62: Optimizing and solving the solution constraint according to the initial load distribution coefficient to obtain a final load distribution coefficient.

[0071] The present invention first determines the relative positions of the meshing points of the two pairs of teeth at each contact moment during the meshing interval. This yields the stiffness components of each meshing position, which are then substituted into the preset initial load distribution coefficient to optimize the inter-tooth load distribution coefficient. The present invention's advantage lies in using an analytical method to solve the load distribution coefficient, eliminating the need for a finite element model. This reduces computational time and offers a lower error rate than traditional analytical methods.

[0072] In addition, the method of the present invention can be used to calculate the inter-tooth load distribution coefficient of various spur gears (involute gears or non-involute gears).

[0073] Figure 3 is a diagram of the gear cantilever beam model, such as Figure 3 As shown, the gear tooth is considered a cantilever beam with a variable cross-section, fixed to a vertical section perpendicular to the tooth centerline and passing through the intersection of the tooth root circle and the gear centerline. The gear tooth is divided into k cross-sectional elements i along the tooth centerline. Each element is considered to have its left end fixed and the connected portion of the right end surface as a rigid body. The deformation of the element is calculated using the principles of material mechanics and Timoshenko beam theory. The deformation at the meshing point is calculated by superimposing the deformation of the element onto the fixed surface. The deformation at each meshing point is then calculated to determine the tooth stiffness at different positions on the individual tooth.

[0074] The calculation formula for the bending deformation of a gear tooth at point b is as follows:

[0075]

[0076] The calculation formula for shear deformation is:

[0077]

[0078] The calculation formula for compression deformation is:

[0079]

[0080] Among them, δ bb is the bending deformation, W b is the normal contact force at the meshing point b, E e is the equivalent elastic modulus, I i is the moment of inertia of element i, L i is the thickness of element i, β b is the angle between the normal contact force at meshing point b and the y-axis, S ib Y is the distance between the projection of the infinitesimal element i and the meshing point b on the x-axis, b is the half tooth thickness at the meshing point b, k is the total number of cross-sectional elements, δ sb is shear deformation, A i is the cross-sectional area of ​​element i, ν is Poisson’s ratio, δ pbCompression deformation.

[0081] Figure 4 is a schematic diagram and analytical model diagram of a single pair of teeth meshing. As shown in Figure 4, when a single pair of teeth meshes, the total deformation is obtained by adding the deformations, and the total deformation is calculated with the meshing force to obtain the meshing stiffness of the single pair of teeth. For the convenience of subsequent analysis, the bending deformation, shear deformation, and compression deformation of tooth 1 are combined as the tooth deformation δ M1 At this time, the analytical model is simplified to the series connection of the matrix stiffness of gear 1 and gear 2 and the tooth stiffness and contact stiffness of gear 1 and gear 2.

[0082] Figure 5 shows a schematic diagram and analytical model of double-pair tooth meshing. As shown in Figure 5, since the change trend of the matrix stiffness under single-pair tooth meshing is consistent with the gear tooth stiffness, its influence on the calculation of the load distribution coefficient is small, and the matrix part can be regarded as a whole. By simplifying the analytical model of double-pair tooth meshing, the potential energy calculation formula of the entire system is as follows:

[0083]

[0084] Where U is the potential energy of the spur gear, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, δ M1 is the tooth deformation of the first gear at the meshing point b, δ M2 is the tooth deformation of the second gear at the meshing point b, δ M3 is the tooth deformation of the first gear at the meshing point a, δ M4 is the tooth deformation of the second gear at the meshing point a, U ha is the elastic potential energy calculated based on the contact deformation at the meshing point a, U hb is the elastic potential energy calculated based on the contact deformation at the meshing point b.

[0085] Figure 6 It is a schematic diagram of the direction of the normal contact force when two pairs of teeth are engaged, as shown in Figure 6 As shown, according to the principle of conjugate tooth profile meshing, the meshing force F a , F b The directions are along the lines connecting the corresponding meshing points and nodes. In the figure, R a , R b It is the distance from the center of the load gear O1 to the two meshing force directions. For involute gears, R a With R b Equal to and equal to the base circle radius of the load gear, thereby expanding the normal contact force constraint to a general form, the calculation formula is as follows:

[0086] F a R a +F b Rb =T;

[0087] Among them, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, R a R is the distance from the center of the load gear to the first meshing force direction, b is the distance from the center of the load gear to the second meshing force direction, and T is the load torque.

[0088] In this case, the definition of the load distribution factor is modified to:

[0089]

[0090] Figure 7 This is a comparison chart of the three methods for calculating the inter-tooth load distribution coefficient of involute gears. The gear pair parameters are: the number of teeth of the large gear is 47, the number of teeth of the small gear is 23, the module is 3mm, the pressure angle is 20°, the tooth top height coefficient is 1, and the top clearance coefficient is 0.25. The finite element model parameters are: elastic modulus is 206GPa, Poisson's ratio is 0.269, pinion load is 40N·m, and tooth width is 20mm. The initial load distribution coefficient is 0.5, and the inter-tooth load distribution coefficient is calculated by optimization solution. The mesh of the finite element method uses the linear reduced integration unit C3D8R. In order to overcome the hourglass problem and ensure the accuracy of the contact analysis, the mesh size along the tooth profile surface is one-third of the minimum Hertzian contact half-width of each meshing position of the gear, which is about 0.04mm. For example Figure 7 As shown, compared with the traditional load distribution coefficient calculation method, the inter-tooth load distribution coefficient calculation method of the present invention is closer to the calculation result of the finite element method.

[0091] Figure 8 This is a comparison chart of three methods for calculating the inter-tooth load distribution coefficient of non-involute gears (equal relative curvature gears). The design concept of equal relative curvature gears (CRC gears) is to keep the relative curvature unchanged during the meshing process, and equal to the minimum relative curvature of the involute gear under the same parameters. Compared with the involute gear, the meshing stiffness of this gear is greater, but because its meshing line is not a straight line, there are problems in the theoretical calculation of the load distribution coefficient. Therefore, it is necessary to use a general normal contact force constraint to accurately calculate its load distribution coefficient. The values ​​of the basic parameters of the CRC gear are the same as those of the involute gear, and the relative curvature is 0.1114, the minimum relative curvature of the involute gear with the same parameters. Figure 8 As shown, for CRC gears, the calculation method of the inter-tooth load distribution coefficient of the present invention can be consistent with the finite element results in terms of change trend, indicating that the calculation method of the inter-tooth load distribution coefficient of the present invention has a wide range of application and the results are more accurate.

[0092] The present invention also provides an application scenario, which applies the above-mentioned method for calculating the load distribution coefficient between gear teeth. Specifically: the method for calculating the load distribution coefficient between gear teeth provided in this embodiment can be applied in a gear transmission scenario. The gear transmission scenario includes a tooth profile data acquisition link, a load distribution coefficient calculation link and a load distribution link; the acquired tooth profile data is calculated by the load distribution coefficient, so that the corresponding load distribution can be obtained. The method for calculating the load distribution coefficient between gear teeth provided in this embodiment belongs to the load distribution coefficient calculation link. Specifically, after obtaining the tooth profile data, the gear meshing stiffness can be calculated according to the tooth profile data, and the potential energy of the spur gear can be calculated according to the gear meshing stiffness. Then, according to the potential energy of the spur gear and the determined normal contact force constraint, the solution constraint can be determined, and the final load distribution coefficient can be obtained by solving the solution constraint.

[0093] In an exemplary embodiment, a computer device is provided. The computer device may be a server or a terminal. The internal structure diagram thereof may be as follows: Figure 9 As 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 the computer program in the non-volatile storage medium. The database of the computer device is used to store the acquired tooth profile 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, a method for calculating the load distribution coefficient between gear teeth is implemented.

[0094] Those skilled in the art will understand that Figure 9 The structure shown in the figure is merely a block diagram of a portion of the structure related to the solution of the present invention and does not constitute a limitation on the computer device to which the solution of the present invention 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.

[0095] In an exemplary embodiment, a computer device is further provided, including a memory and a processor. The memory stores a computer program, and the processor implements the above method embodiments when executing the computer program.

[0096] In an exemplary embodiment, a computer-readable storage medium is provided, storing a computer program, which implements the above-mentioned method embodiments when executed by a processor.

[0097] In an exemplary embodiment, a computer program product is provided, including a computer program. When the computer program is executed by a processor, the above method embodiments are implemented.

[0098] It should be noted that the user information (including but not limited to user device information, user personal information, etc.) and data (including but not limited to data used for analysis, stored data, displayed data, etc.) involved in the present invention are all information and data authorized by the user or fully authorized by all parties, and the collection, use and processing of relevant data must comply with relevant regulations.

[0099] Those skilled in the art will appreciate that all or part of the processes in the above-mentioned embodiments can be implemented by instructing the relevant hardware through a computer program. 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 by the present invention can include at least one of non-volatile and volatile memory. Non-volatile memory can 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 can 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).

[0100] The database involved in each embodiment provided by the present invention may include at least one of a relational database and a non-relational database. Non-relational databases may include, but are not limited to, distributed databases based on blockchain. The processor involved in each embodiment provided by the present invention may be, but is not limited to, a general-purpose processor, a central processing unit, a graphics processing unit, a digital signal processor, a programmable logic unit, a data processing logic unit based on quantum computing, etc.

[0101] 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.

[0102] This document uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.

Claims

1. A method for calculating the load distribution coefficient between gear teeth, characterized in that: The method for calculating the gear teeth load distribution coefficient includes: Obtaining tooth profile data of a spur gear; the tooth profile data includes: the shape of the entire tooth profile, the relative curvature of each point, the direction of the normal contact force, and the meshing position at all contact moments; Calculating the gear meshing stiffness based on the tooth profile data of the spur gear; the gear meshing stiffness is a stiffness that takes into account gear tooth deformation, gear base deformation, and contact deformation; Calculate the potential energy of the spur gear based on the gear mesh stiffness; Determining a normal contact force constraint; the normal contact force constraint is determined according to a load torque expression form; determining a solution constraint based on the normal contact force constraint and the potential energy of the spur gear; Solving the solution constraints to obtain a final load distribution coefficient; The gear tooth deformation includes bending deformation, shear deformation and compression deformation; The calculation formula for the bending deformation is: The calculation formula of the shear deformation is: The calculation formula for the compression deformation is: Among them, δ bb is the bending deformation, W b is the normal contact force at the meshing point b, E e is the equivalent elastic modulus, I i is the moment of inertia of element i, L i is the thickness of element i, β b is the angle between the normal contact force at meshing point b and the y-axis, S ib Y is the distance between the projection of the infinitesimal element i and the meshing point b on the x-axis, b is the half tooth thickness at the meshing point b, k is the total number of cross-sectional elements, δ sb is shear deformation, A i is the cross-sectional area of ​​element i, ν is Poisson’s ratio, δ pb is compression deformation; The calculation formula of the contact deformation is: Among them, δ hb is the contact deformation, W b is the normal contact force, ν is the Poisson's ratio, E is the elastic modulus of the material used for the gear teeth, B is the gear width, and Y b1 is the half tooth thickness of the first gear at the meshing point b, Y b2 is the half tooth thickness of the second gear at the meshing point b, and c is the Hertzian contact half width.

2. The method for calculating the gear teeth load distribution coefficient according to claim 1, characterized in that: The potential energy of the spur gear is expressed as: Where U is the potential energy of the spur gear, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, δ M1 is the tooth deformation of the first gear at the meshing point b, δ M2 is the tooth deformation of the second gear at the meshing point b, δ M3 is the tooth deformation of the first gear at the meshing point a, δ M4 is the tooth deformation of the second gear at the meshing point a, U ha is the elastic potential energy calculated based on the contact deformation at the meshing point a, U hb is the elastic potential energy calculated based on the contact deformation at the meshing point b.

3. The method for calculating the gear tooth load distribution coefficient according to claim 1, wherein: The expression of the normal contact force constraint is: F a R a +F b R b =T; Among them, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, R a R is the distance from the center of the load gear to the meshing point a in the direction of the meshing force, b is the distance from the center of the load gear to the meshing point b in the direction of the meshing force, and T is the load torque.

4. The method for calculating the gear teeth load distribution coefficient according to claim 1, wherein: Solving the solution constraints to obtain the final load distribution coefficient, specifically including: Determine the initial load distribution factor; The solution constraint is optimized and solved according to the initial load distribution coefficient to obtain a final load distribution coefficient.

5. The method for calculating the gear teeth load distribution coefficient according to claim 1, wherein: The expression for solving the constraint is: Where U is the potential energy of the spur gear, F a is the meshing force at meshing point a, F b is the meshing force at the meshing point b, R a R is the distance from the center of the load gear to the first meshing force direction, b is the distance from the center of the load gear to the second meshing force direction, and T is the load torque.

6. 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 method for calculating the load distribution coefficient between gear teeth according to any one of claims 1 to 5.

7. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the method for calculating the load distribution coefficient between gear teeth according to any one of claims 1 to 5 is implemented.

8. A computer program product comprising a computer program, characterized in that When the computer program is executed by a processor, the method for calculating the load distribution coefficient between gear teeth according to any one of claims 1 to 5 is implemented.

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