A bevel gear engagement stiffness calculation method, system, device and storage medium

Abstract

The application discloses a bevel gear engagement stiffness calculation method, system, device and storage medium. The bevel gear engagement stiffness calculation method comprises the following steps: determining a target contact area of an engagement interface of a bevel gear pair in the case of gear tooth bearing contact analysis on the engagement process of the bevel gear pair; determining the entrainment velocity and the first bevel gear engagement stiffness of the bevel gear pair based on the target contact area, and constructing a bevel gear mixed thermal elastohydrodynamic lubrication control equation based on the entrainment velocity; in the case of setting a first pressure distribution value, a first oil film thickness distribution value and a first temperature field distribution value, determining the second bevel gear engagement stiffness through the bevel gear mixed thermal elastohydrodynamic lubrication control equation based on the first pressure distribution value, the first oil film thickness distribution value and the first temperature field distribution value, and determining the target engagement stiffness of the bevel gear pair based on the first bevel gear engagement stiffness and the second bevel gear engagement stiffness, thereby improving the accuracy of the bevel gear engagement stiffness calculation.

Description

Technical Field

[0001] This application relates to the technical field of bevel gear meshing stiffness calculation, and in particular to a bevel gear meshing stiffness calculation method, system, device and storage medium. Background Technology

[0002] In practical engineering applications, gears typically operate in a lubricated oil environment. The hydrodynamic effect of the lubricating oil separates the gear interfaces, effectively reducing the risk of frictional wear failure caused by direct contact between the tooth surfaces. This phenomenon can be explained by the theory of elastohydrodynamic lubrication. Since the actual machined gear surfaces are not ideally smooth, but possess microscopic morphologies related to the machining process, rough surfaces, due to the presence of micron-scale micro-protrusions, are more prone to direct contact between interface materials. In this case, the interface load is shared by the lubricating oil and the directly contacting micro-protrusions. This lubrication state, where the micro-protrusion contact area and the fluid lubrication area coexist, is described as mixed lubrication. Meshing stiffness, as one of the most significant internal excitation forces affecting bevel gear transmissions, is the primary source of vibration and noise in bevel gear transmission systems.

[0003] In the existing technology, the solution method for bevel gear meshing stiffness often ignores the lubrication conditions of the bevel gear pair, and the model for calculating the meshing stiffness of bevel gears often assumes that the bevel gear tooth surface is smooth. This ignores the surface roughness of the bevel gear tooth surface under actual conditions and the mixed thermo-elasto-fluid lubrication conditions under actual working conditions, making it difficult to achieve an accurate solution for the meshing stiffness of bevel gears. Summary of the Invention

[0004] This application aims to at least solve the technical problems existing in the prior art. To this end, this application proposes a method, system, device and storage medium for calculating the meshing stiffness of bevel gears, which can realize the accurate solution of the meshing stiffness of bevel gears under mixed thermo-elasto-fluid lubrication conditions and improve the accuracy of bevel gear meshing stiffness calculation.

[0005] A first aspect of this application provides a method for calculating the meshing stiffness of bevel gears, comprising the following steps:

[0006] In the case of performing gear tooth bearing contact analysis on the meshing process of bevel gear pairs, the target contact area of ​​the meshing interface of the bevel gear pairs is determined;

[0007] Based on the target contact area, the entrainment speed of the bevel gear pair and the meshing stiffness of the first bevel gear are determined, wherein the meshing stiffness of the first bevel gear is the meshing stiffness of the bevel gear without considering lubrication.

[0008] Based on the aforementioned suction speed, a control equation for the hybrid thermo-elasto-fluidic lubrication of bevel gears is constructed.

[0009] Given a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value, the second bevel gear meshing stiffness is determined based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value, using the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, wherein the second bevel gear meshing stiffness is the oil film stiffness.

[0010] The target meshing stiffness of the bevel gear pair is determined based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear.

[0011] The bevel gear meshing stiffness calculation method according to the embodiments of this application has at least the following beneficial effects:

[0012] This method, after performing gear tooth bearing contact analysis on the meshing process of bevel gear pairs, determines the target contact area of ​​the meshing interface of the bevel gear pairs. Based on the target contact area, it determines the entrainment velocity and the first bevel gear meshing stiffness, where the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication. Based on the entrainment velocity, it constructs a bevel gear hybrid thermo-elasto-fluidic lubrication control equation. With a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value set, it determines the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness. Based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness, it determines the target meshing stiffness of the bevel gear pairs. In this way, it achieves an accurate solution for the bevel gear meshing stiffness under hybrid thermo-elasto-fluidic lubrication conditions, improving the accuracy of bevel gear meshing stiffness calculation.

[0013] According to some embodiments of this application, the target contact area is an elliptical region, the bevel gear pair includes a large gear and a small gear, and determining the entrainment speed of the bevel gear pair and the meshing stiffness of the first bevel gear based on the target contact area includes:

[0014] When the meshing process of the bevel gear pair is discretized into several meshing points according to a preset time interval, the meshing point position vector and meshing force vector of each meshing point are obtained;

[0015] Obtain the angular velocity of the large wheel, the angular velocity of the small wheel, the major semi-axis vector of the target contact area, and the minor semi-axis vector of the target contact area;

[0016] Based on the large wheel angular velocity, the small wheel angular velocity, the major semi-axis vector, and the minor semi-axis vector, the entrainment speed at each meshing point is determined;

[0017] When the first torque value is set so that the bevel gear pair is unloaded, the no-load transmission error is determined; when the second torque value is set so that the bevel gear pair is under load, the load transmission error is determined.

[0018] Based on the no-load transmission error, the load transmission error, the meshing point position vector, and the meshing force vector, the meshing stiffness of the first bevel gear at each meshing point is determined.

[0019] According to some embodiments of this application, the control equation for the hybrid thermo-elasto-fluidic lubrication of the bevel gear includes the Reynolds equation, film thickness equation, viscosity-pressure-temperature equation, density-pressure-temperature equation, and energy equation. The construction of the control equation for the hybrid thermo-elasto-fluidic lubrication of the bevel gear based on the entrainment velocity includes:

[0020] Determine the entrainment velocity at each engagement point and the entrainment angle between the short semi-axis vector;

[0021] Based on the major semi-axis vector, the minor semi-axis vector, the entrainment angle, and the entrainment speed, the Reynolds equation is constructed.

[0022] Based on the major semi-axis vector and the minor semi-axis vector, the film thickness equation is constructed;

[0023] Given the rated temperature and the ambient viscosity of the lubricating oil, the viscosity-pressure-temperature equation is constructed based on the rated temperature and the ambient viscosity of the lubricating oil.

[0024] Given the ambient density of the lubricating oil, the density-pressure-temperature equation is constructed based on the ambient density of the lubricating oil.

[0025] Given the flow rates of the lubricating oil along the x-direction, y-direction, and z-direction, the energy equation is constructed based on these flow rates.

[0026] According to some embodiments of this application, determining the meshing stiffness of the second bevel gear based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear hybrid thermo-elasto-fluidic lubrication control equation includes:

[0027] The minimum oil film thickness value among the first oil film thickness distribution values ​​is taken as the first rigid body center displacement value;

[0028] Based on the first pressure distribution value and the first temperature field distribution value, the apparent viscosity value of the first lubricating oil is determined by the viscosity-pressure-temperature equation.

[0029] Based on the first pressure distribution value and the first temperature field distribution value, the first lubricating oil density value is determined by the density-pressure-temperature equation.

[0030] Based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value, the second pressure distribution value is determined by the film thickness equation.

[0031] The meshing stiffness of the second bevel gear is determined based on the second pressure distribution value and the preset oil film distribution conditions.

[0032] According to some embodiments of this application, determining the meshing stiffness of the second bevel gear based on the second pressure distribution value and the preset oil film distribution conditions includes:

[0033] When the preset pressure distribution iteration number threshold is greater than one and the second pressure distribution value meets the preset oil film distribution condition, the second temperature field distribution value is determined by the energy equation based on the second pressure distribution value and the first lubricating oil density value.

[0034] If the second temperature field distribution value meets the preset temperature field distribution conditions, the first oil film thickness distribution value is taken as the final oil film thickness distribution value, and the second pressure distribution value is taken as the final pressure distribution value.

[0035] If the preset pressure distribution iteration number threshold is greater than one, and the second pressure distribution value does not meet the preset oil film distribution condition, the first pressure distribution value is updated to the second pressure distribution value.

[0036] Based on the second pressure distribution value and the first rigid body center displacement value, the second oil film thickness distribution value is determined by the film thickness equation.

[0037] Based on the second pressure distribution value and the first temperature field distribution value, the apparent viscosity value of the second lubricating oil is determined by the viscosity-pressure-temperature equation.

[0038] Based on the second pressure distribution value and the first temperature field distribution value, the second lubricating oil density value is determined by the density-pressure-temperature equation.

[0039] Based on the second oil film thickness distribution value, the second lubricating oil apparent viscosity value, and the second lubricating oil density value, the third pressure distribution value is determined by the film thickness equation.

[0040] This process continues until the Kth lubricating oil density value, the K+1th pressure distribution value, and the Kth oil film thickness distribution value are obtained. Based on the Kth lubricating oil density value and the K+1th pressure distribution value, the second temperature field distribution value is determined through the energy equation, where K is the first iteration number less than the preset pressure distribution iteration number threshold, and the K+1th pressure distribution value satisfies the preset oil film distribution condition.

[0041] When the second temperature field distribution value meets the preset temperature field distribution conditions, the Kth oil film thickness distribution value is taken as the final oil film thickness distribution value, and the Kth plus one pressure distribution value is taken as the final pressure distribution value.

[0042] The meshing stiffness of the second bevel gear is determined based on the final oil film thickness distribution value and the final pressure distribution value.

[0043] According to some embodiments of this application, after determining the second temperature field distribution value based on the energy equation using the Kth lubricating oil density value and the Kth plus one pressure distribution value, the method further includes:

[0044] If the second temperature field distribution value does not meet the preset temperature field distribution conditions, the first temperature field distribution value is updated to the second temperature field distribution value.

[0045] Based on the Kth pressure distribution value and the first rigid body center displacement value, the Kth oil film thickness distribution value is determined by the film thickness equation.

[0046] Based on the Kth pressure distribution value and the second temperature field distribution value, the Kth lubricating oil apparent viscosity value is determined by the viscosity-pressure-temperature equation.

[0047] Based on the Kth pressure distribution value and the second temperature field distribution value, the Kth lubricating oil density value is determined by the density-pressure-temperature equation.

[0048] Based on the K+1 oil film thickness distribution value, the K+1 lubricating oil apparent viscosity value, and the K+1 lubricating oil density value, the K+2 pressure distribution value is determined through the film thickness equation;

[0049] This process continues until the Qth lubricating oil density value, the Q+1th pressure distribution value, and the Qth oil film thickness distribution value are obtained. Based on the Qth lubricating oil density value and the Q+1th pressure distribution value, the third temperature field distribution value is determined through the energy equation, where Q is the second iteration number that is less than the preset pressure distribution iteration number threshold and greater than K+1, and the Q+1th pressure distribution value satisfies the preset oil film distribution condition.

[0050] If the third temperature field distribution value meets the preset temperature field distribution conditions, the Qth oil film thickness distribution value is taken as the final oil film thickness distribution value, and the Qth plus one pressure distribution value is taken as the final pressure distribution value.

[0051] According to some embodiments of this application, determining the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear includes:

[0052] Based on the final oil film thickness distribution value, determine the dry contact area in the target contact area where the oil film thickness is less than or equal to a preset oil film thickness threshold and the area of ​​the dry contact area;

[0053] Based on the final pressure distribution value, the dry contact area, and the area, the third bevel gear meshing stiffness corresponding to the dry contact area is determined;

[0054] The target meshing stiffness of the bevel gear pair is determined based on the meshing stiffness of the first bevel gear, the meshing stiffness of the second bevel gear, and the meshing stiffness of the third bevel gear.

[0055] A second aspect of this application provides a bevel gear meshing stiffness calculation system, the bevel gear meshing stiffness calculation system comprising:

[0056] The target contact area determination module is used to determine the target contact area of ​​the meshing interface of the bevel gear pair when performing gear tooth bearing contact analysis on the meshing process of the bevel gear pair.

[0057] The first bevel gear meshing stiffness determination module is used to determine the entrainment speed of the bevel gear pair and the first bevel gear meshing stiffness based on the target contact area, wherein the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication.

[0058] An equation construction module is used to construct a control equation for the hybrid thermo-elasto-fluidic lubrication of bevel gears based on the entrainment speed.

[0059] The second bevel gear meshing stiffness determination module is used to determine the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value, using the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness.

[0060] The target meshing stiffness determination module is used to determine the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear.

[0061] This system, by performing gear tooth bearing contact analysis on the meshing process of bevel gear pairs, determines the target contact area of ​​the meshing interface of the bevel gear pairs. Based on the target contact area, it determines the entrainment velocity and the first bevel gear meshing stiffness, where the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication. Based on the entrainment velocity, it constructs a bevel gear hybrid thermo-elasto-fluidic lubrication control equation. With a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value set, it determines the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness. Based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness, it determines the target meshing stiffness of the bevel gear pairs. In this way, it achieves accurate solution of bevel gear meshing stiffness under hybrid thermo-elasto-fluidic lubrication conditions, improving the accuracy of bevel gear meshing stiffness calculation.

[0062] A third aspect of this application provides an electronic device for calculating the meshing stiffness of bevel gears, including at least one control processor and a memory for communicatively connecting to the at least one control processor; the memory stores instructions that can be executed by the at least one control processor, and the instructions are executed by the at least one control processor to enable the at least one control processor to perform the above-described method for calculating the meshing stiffness of bevel gears.

[0063] In a fourth aspect, this application provides a computer-readable storage medium storing computer-executable instructions for causing a computer to perform the aforementioned method for calculating the meshing stiffness of bevel gears.

[0064] It should be noted that the beneficial effects of the second to fourth aspects of this application with respect to the prior art are the same as the beneficial effects of the aforementioned bevel gear meshing stiffness calculation system with respect to the prior art, and will not be described in detail here.

[0065] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0066] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0067] Figure 1 This is a schematic flowchart of an embodiment of the bevel gear meshing stiffness calculation method provided in this application;

[0068] Figure 2 This is a schematic diagram of a spiral bevel gear loading contact analysis model, which is an embodiment of the bevel gear meshing stiffness calculation method provided in this application.

[0069] Figure 3 This is a schematic diagram showing the load parameter changes in an embodiment of the bevel gear meshing stiffness calculation method provided in this application;

[0070] Figure 4 This is a schematic diagram showing the changes in geometric parameters of an embodiment of the bevel gear meshing stiffness calculation method provided in this application;

[0071] Figure 5 This is a schematic diagram showing the changes in the suction speed and suction angle of an embodiment of the bevel gear meshing stiffness calculation method provided in this application;

[0072] Figure 6 This is a schematic diagram of the dry contact portion of the bevel gear meshing stiffness according to an embodiment of the bevel gear meshing stiffness calculation method provided in this application;

[0073] Figure 7 This is a schematic diagram of the oil film portion of the bevel gear meshing stiffness in an embodiment of the bevel gear meshing stiffness calculation method provided in this application.

[0074] Figure 8 This is a schematic diagram of the bevel gear meshing stiffness under mixed friction conditions, representing an embodiment of the bevel gear meshing stiffness calculation method provided in this application.

[0075] Figure 9 This is a schematic diagram of an embodiment of the bevel gear meshing stiffness calculation system provided in this application;

[0076] Figure 10 This is a schematic diagram of the structure of an embodiment of the electronic device provided in this application. Detailed Implementation

[0077] The embodiments of this application are described in detail below. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0078] In the description of this application, the use of terms such as "first," "second," etc., is for the purpose of distinguishing technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or the order of the technical features indicated.

[0079] In the description of this application, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0080] In the description of this application, it should be noted that, unless otherwise explicitly defined, terms such as "setup," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this application in conjunction with the specific content of the technical solution.

[0081] In practical engineering applications, gears typically operate in a lubricated oil environment. The hydrodynamic effect of the lubricating oil separates the gear interfaces, effectively reducing the risk of frictional wear failure caused by direct contact between the tooth surfaces. This phenomenon can be explained by the theory of elastohydrodynamic lubrication. Since the actual machined gear surfaces are not ideally smooth, but possess microscopic morphologies related to the machining process, rough surfaces, due to the presence of micron-scale micro-protrusions, are more prone to direct contact between interface materials. In this case, the interface load is shared by the lubricating oil and the directly contacting micro-protrusions. This lubrication state, where the micro-protrusion contact area and the fluid lubrication area coexist, is described as mixed lubrication. Meshing stiffness, as one of the most significant internal excitation forces affecting bevel gear transmissions, is the primary source of vibration and noise in bevel gear transmission systems.

[0082] In the existing technology, the solution method for bevel gear meshing stiffness often ignores the lubrication conditions of the bevel gear pair, and the model for calculating the meshing stiffness of bevel gears often assumes that the bevel gear tooth surface is smooth. This ignores the surface roughness of the bevel gear tooth surface under actual conditions and the mixed thermo-elasto-fluid lubrication conditions under actual working conditions, making it difficult to achieve an accurate solution for the meshing stiffness of bevel gears.

[0083] To address the aforementioned technical deficiencies, this application provides a method, system, device, and storage medium for calculating the meshing stiffness of bevel gears.

[0084] Please see Figure 1 This is a flowchart illustrating a method for calculating the meshing stiffness of bevel gears according to an embodiment of this application. This method is applied to electronic devices, such as servers. Figure 1 As shown, the method for calculating the meshing stiffness of the bevel gear includes:

[0085] Step S101: Under the condition of performing gear tooth bearing contact analysis on the meshing process of the bevel gear pair, determine the target contact area of ​​the meshing interface of the bevel gear pair;

[0086] The aforementioned bevel gear pair may include a large gear and a small gear, where the large gear can be the driven gear and the small gear can be the driving gear.

[0087] In step S101, when performing gear tooth bearing contact analysis on the meshing process of the bevel gear pair, determining the target contact area of ​​the meshing interface of the bevel gear pair may include:

[0088] Construct a local coordinate system for the large wheel, a local coordinate system for the small wheel, and a global coordinate system. The global coordinate system coincides with the local coordinate system of the large wheel, and the axes of the local coordinate system of the small wheel align with the axes of the global coordinate system. The offset distance in the negative direction of the axis is E;

[0089] The first transformation matrix from the global coordinate system to the small wheel's local coordinate system is calculated using the following formula:

[0090] ;

[0091] in, Let be the first transformation matrix. The axes of the local coordinate system and the global coordinate system are along... Offset distance in the negative direction of the axis;

[0092] The second transformation matrix from the local coordinate system to the global coordinate system of the small wheel is calculated using the following formula:

[0093] ;

[0094] in, This is the second transformation matrix;

[0095] The initial position coordinates of the small gear tooth surface point in the global coordinate system, the initial position coordinates of the large gear tooth surface point in the global coordinate system, and the current position coordinates of the small gear tooth surface point are obtained. The first rotation angle of the shaft in the positive direction counterclockwise and the current moment of the large gear tooth surface point rotation In the case of a second rotation angle that is counterclockwise in the positive direction of the axis, where, The axis is the horizontal axis of the local coordinate system of the small wheel. The axis is the vertical axis of the local coordinate system of the large wheel. The first rotation matrix and the second rotation matrix are calculated using the following formulas:

[0096] ;

[0097] in, Let be the first rotation matrix. This is the second rotation matrix. The first rotation angle, This is the second rotation angle;

[0098] The current position coordinates of the pinion tooth surface point in the global coordinate system are calculated using the following formula:

[0099] ;

[0100] in, Let X be the initial position coordinate of the small gear tooth face point in the global coordinate system. Let Y be the initial position coordinate of the small gear tooth face point in the global coordinate system. Let Z be the initial position coordinate of the small gear tooth face point in the global coordinate system. For the small gear tooth surface point at the current moment The X-axis coordinate of the position coordinates in the global coordinate system For the small gear tooth surface point at the current moment The Y-axis coordinate of the position coordinates in the global coordinate system. For the small gear tooth surface point at the current moment The Z-axis coordinate of the position coordinates in the global coordinate system;

[0101] The current position coordinates of the large gear tooth surface point in the global coordinate system are calculated using the following formula:

[0102] ;

[0103] in, The X-axis coordinate of the initial position of the large gear tooth face point in the global coordinate system. The Y-axis coordinate of the initial position of the large gear tooth face point in the global coordinate system. The Z-axis coordinate of the initial position of the large gear tooth surface point in the global coordinate system. For the point of the large gear tooth surface at the current moment The X-axis coordinate of the position coordinates in the global coordinate system. For the point of the large gear tooth surface at the current moment The Y-axis coordinate of the position coordinates in the global coordinate system. For the point of the large gear tooth surface at the current moment The Z-axis coordinate of the position coordinates in the global coordinate system;

[0104] When the meshing process of the bevel gear pair is discretized into several meshing points according to a preset time interval, the meshing point position vector and meshing force vector of each meshing point are obtained, wherein the preset time interval is a value preset according to actual needs;

[0105] The unit normal vector at each engagement point is calculated using the following formula:

[0106] ;

[0107] in, Let C be the unit normal vector of the meshing point. Let be the normal vector along the X-axis of the meshing point C. Let be the unit normal vector along the Y-axis of the meshing point C. Let be the unit normal vector along the Z-axis coordinate direction of the meshing point C. Let C be the meshing force vector along the X-axis. Let C be the meshing force vector along the Y-axis. The meshing force vector is the unit normal vector in the Z-axis coordinate direction of the meshing point C;

[0108] With the meshing point C as the origin of the coordinate system Establish a local coordinate system ,in, The Z-axis of the local coordinate system The direction of the axis and the unit normal vector With the same direction, the local coordinate system is determined using the following formula. shaft and axis:

[0109] ;

[0110] in, Let C be the position vector of the meshing point. Let X be the local coordinate system. The Y-axis of the local coordinate system Let C be the position vector of the meshing point along the X-axis. Let C be the position vector of the engagement point along the Y-axis. The meshing point position vector is the unit normal vector in the Z-axis coordinate direction of the meshing point C;

[0111] The third transformation matrix from the global coordinate system to the local coordinate system is calculated using the following formula:

[0112] ;

[0113] in, This is the third transformation matrix. The X-axis of the global coordinate system The Y-axis of the global coordinate system The Z-axis of the global coordinate system;

[0114] The coordinate vector of the projection point D of the tooth surface point P (including the tooth surface points of the large gear and the small gear) onto the tangent plane is calculated using the following formula:

[0115] ;

[0116] in, Let P be the coordinate vector of the tooth surface point. Let be the coordinate vector of the projection point D of the tooth surface point P onto the tangent plane. Let be the X-axis coordinate of the projection point D of tooth surface point P onto the tangent plane. Let be the Y-coordinate of the coordinate vector of the projection point D of tooth surface point P onto the tangent plane. Let be the Z-axis coordinate of the coordinate vector of the projection point D of the tooth surface point P onto the tangent plane;

[0117] The coordinate vector of the projection point D in the local coordinate system is calculated using the following formula:

[0118] ;

[0119] in, Let D be the coordinate vector of the projection point D in the local coordinate system. Let X be the coordinate of the projection point D in the local coordinate system. Let Y be the Y-axis coordinate of the coordinate vector of the projection point D in the local coordinate system. Let Z be the coordinate of the coordinate vector of the projection point D in the local coordinate system;

[0120] The target contact area is obtained by fitting all projection points using the least squares ellipse fitting algorithm. The target contact area is an elliptical region.

[0121] Step S102: Based on the target contact area, determine the entrainment speed of the bevel gear pair and the meshing stiffness of the first bevel gear, wherein the meshing stiffness of the first bevel gear is the meshing stiffness of the bevel gear without considering lubrication.

[0122] Step S103: Based on the entrainment speed, construct the control equation for the hybrid thermo-elasto-fluidic lubrication of the bevel gear;

[0123] The aforementioned control equations for the mixed thermo-elasto-fluidic lubrication of bevel gears may include the Reynolds equation, film thickness equation, viscosity-pressure-temperature equation, density-pressure-temperature equation, and energy equation.

[0124] Step S104: With the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value set, the second bevel gear meshing stiffness is determined based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear mixed thermo-elasto-fluidic lubrication control equation, wherein the second bevel gear meshing stiffness is the oil film stiffness.

[0125] The aforementioned first pressure distribution value can be a value preset according to actual needs.

[0126] The aforementioned first oil film thickness distribution value can be a value preset according to actual needs.

[0127] The aforementioned first temperature field distribution value can be a value preset according to actual needs.

[0128] Step S105: Determine the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear.

[0129] This method, after performing gear tooth bearing contact analysis on the meshing process of bevel gear pairs, determines the target contact area of ​​the meshing interface of the bevel gear pairs. Based on the target contact area, it determines the entrainment velocity and the first bevel gear meshing stiffness, where the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication. Based on the entrainment velocity, it constructs a bevel gear hybrid thermo-elasto-fluidic lubrication control equation. With a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value set, it determines the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness. Based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness, it determines the target meshing stiffness of the bevel gear pairs. In this way, it achieves an accurate solution for the bevel gear meshing stiffness under hybrid thermo-elasto-fluidic lubrication conditions, improving the accuracy of bevel gear meshing stiffness calculation.

[0130] In some embodiments, step S102 may include steps S201 to S205:

[0131] Step S201: When the meshing process of the bevel gear pair is discretized into several meshing points according to a preset time interval, the meshing point position vector and meshing force vector of each meshing point are obtained;

[0132] The aforementioned preset time interval can be a value that is pre-set according to actual needs.

[0133] Step S202: Obtain the angular velocity of the large wheel, the angular velocity of the small wheel, the major semi-axis vector of the target contact area, and the minor semi-axis vector of the target contact area;

[0134] In step S202, the above-mentioned acquisition of the major semi-axis vector and the minor semi-axis vector of the target contact area can be calculated by using Carlsen elliptic integral theory.

[0135] Step S203: Based on the large wheel angular velocity, the small wheel angular velocity, the meshing point position vector, the meshing force vector, the major half-axis vector, and the minor half-axis vector, determine the entrainment speed at each meshing point;

[0136] Reference Figures 2 to 5In step S203, determining the entrainment speed at each engagement point based on the large wheel angular velocity, the small wheel angular velocity, the engagement point position vector, the engagement force vector, the major semi-axis vector, and the minor semi-axis vector may include:

[0137] Given the axial direction vectors of the large wheel and the small wheel, obtain the position vectors of the meshing point C relative to the coordinate system attached to the small wheel (small wheel local coordinate system) and the position vectors of the meshing point C relative to the coordinate system attached to the large wheel (large wheel local coordinate system).

[0138] The surface velocities of the larger wheel and the smaller wheel at meshing point C are calculated using the following formulas:

[0139] ;

[0140] in, Let C be the surface velocity of the large wheel at the meshing point. Let C be the surface velocity of the pinion at the meshing point. For large wheel angular velocity, For the small wheel angular velocity, This is the axial direction vector of the large wheel. Let be the axial direction vector of the small wheel. Let C be the position vector of the meshing point C relative to the coordinate system attached to the large wheel. Let C be the position vector of the meshing point C relative to the coordinate system attached to the pinion;

[0141] The surface velocity of the large wheel is decomposed into a first large wheel surface velocity component along the unit normal vector direction of the meshing point C and a second large wheel surface velocity component along the tangent plane direction of the major and minor axes of the target contact area; the surface velocity of the small wheel is decomposed into a first small wheel surface velocity component along the unit normal vector direction of the meshing point C and a second small wheel surface velocity component along the tangent plane direction of the major and minor axes of the target contact area.

[0142] The entrainment velocity at each engagement point is calculated using the following formula:

[0143] ;

[0144] in, The surface velocity component of the first small wheel. The first large wheel surface velocity component, Let C be the entrainment velocity at the engagement point. The second largest surface velocity component, The surface velocity component of the second small wheel. The direction of the minor axis of the contact ellipse (where the contact ellipse is the target contact area) is defined. The major axis direction is defined by the contact ellipse (where the contact ellipse represents the target contact area). Let be the velocity component of the small wheel in the target contact area along the minor axis of the contact ellipse. Let be the velocity component of the small wheel in the target contact area along the major axis of the contact ellipse. The velocity component of the large wheel in the target contact area is the velocity component along the minor axis of the contact ellipse. The velocity component of the large wheel in the target contact area is the velocity component along the major axis of the contact ellipse. The suction speed is the speed at which the suction is drawn in. It is the angle of entrainment.

[0145] Step S204: When the first torque value is set so that the bevel gear pair is unloaded, determine the no-load transmission error; when the second torque value is set so that the bevel gear pair is under load, determine the load transmission error.

[0146] The aforementioned first torque value can be a value preset according to actual needs.

[0147] The aforementioned second torque value can be a value preset according to actual needs.

[0148] In step S204, the determination of no-load transmission error when setting a first torque value to make the bevel gear pair unloaded and the determination of load transmission error when setting a second torque value to make the bevel gear pair under load may include:

[0149] With the first torque value set so that the bevel gear pair is unloaded, the number of teeth of the large gear, the number of teeth of the small gear, the unloaded small gear rotation angle value, the unloaded large gear rotation angle value, the unloaded small gear initial rotation angle value, and the unloaded large gear initial rotation angle value are obtained.

[0150] The no-load transmission error is calculated using the following formula:

[0151] ;

[0152] in, For no-load transmission error, The number of teeth on the pinion. For the large gear teeth, This is the initial turning angle value of the unloaded large wheel. This is the initial rotation angle value of the unloaded small wheel. This is the rotation angle value of the unloaded large wheel. This is the rotation angle value of the unloaded small wheel;

[0153] With the second torque value set so that the bevel gear pair is under load, the rotation angle values ​​of the load pinion, the load gear, the initial rotation angle value of the load pinion, and the initial rotation angle value of the load gear are obtained.

[0154] The load transmission error is calculated using the following formula:

[0155] ;

[0156] in, For load transmission error, This is the initial rotation angle value of the load-bearing wheel. This is the initial rotation angle value of the load wheel. This is the rotation angle value of the large wheel under load. This represents the rotation angle of the small wheel under load.

[0157] Step S205: Based on the no-load transmission error, the load transmission error, the meshing point position vector, and the meshing force vector, determine the first bevel gear meshing stiffness at each meshing point.

[0158] In step S205, determining the first bevel gear meshing stiffness at each meshing point based on the no-load transmission error, the load transmission error, the meshing point position vector, and the meshing force vector may include:

[0159] The meshing stiffness of the first bevel gear at each meshing point is calculated using the following formula:

[0160] ;

[0161] in, Let C be the meshing stiffness of the first bevel gear at the meshing point.

[0162] This application calculates the meshing stiffness of the first bevel gear as the meshing stiffness of the bevel gear without considering lubrication, providing accurate data for subsequent calculation of the target meshing stiffness of the bevel gear pair.

[0163] In some embodiments, step S103 may include steps S301 to S306:

[0164] Step S301: Determine the entrainment speed at each engagement point and the entrainment angle between the short half-axis vector;

[0165] In step S301, the aforementioned determination of the entrainment velocity at each engagement point and the entrainment angle between the minor semi-axis vector can be... The angle between the entrainment velocity at each engagement point and the minor semi-axis vector.

[0166] Step S302: Construct the Reynolds equation based on the major semi-axis vector, minor semi-axis vector, entrainment angle, and entrainment speed;

[0167] In step S302, the expression for the Reynolds equation, constructed based on the major semi-axis vector, minor semi-axis vector, entrainment angle, and entrainment velocity, can be:

[0168] ;

[0169] in, This represents the pressure distribution value (the oil film pressure value at all points). This refers to the apparent viscosity value of the lubricating oil. The coordinates of the target contact area along the minor semi-axis direction. The coordinates are along the semi-major axis of the target contact area. This represents the oil film thickness distribution value (oil film thickness distribution at all points). This is the density value of the lubricating oil.

[0170] Step S303: Construct the film thickness equation based on the major and minor semi-axis vectors;

[0171] In step S303, the expression for constructing the film thickness equation based on the major and minor semi-axis vectors may include:

[0172] After measuring the roughness amplitude of the large gear surface and the small gear surface, the roughness amplitude of the large gear surface and the small gear surface are added together to obtain the total roughness amplitude of each point on the plane where the target contact area is located.

[0173] When the solution domain in the meshing process is pre-set according to actual needs, the surface contact elastic deformation value of each point in the solution domain is calculated by Businski integration, wherein the target contact area includes the solution domain.

[0174] The expression for constructing the film thickness equation can be:

[0175] ;

[0176] in, The coordinates of the plane containing the target contact area are... Oil film thickness at the location, This is the displacement value of the rigid body's center. The combined radius of curvature along the minor semi-axis of the target contact area is obtained in advance. The combined radius of curvature along the semi-major axis of the target contact area is obtained in advance. The coordinates of the plane containing the target contact area are... The surface contact elastic deformation value at that location, The coordinates of the plane containing the target contact area are... The total roughness amplitude at the location;

[0177] Step S304: Given the rated temperature and ambient viscosity of the lubricating oil, construct the viscosity-pressure-temperature equation based on the rated temperature and ambient viscosity of the lubricating oil.

[0178] In step S304, the expression for constructing the viscosity-pressure-temperature equation based on the rated temperature and the ambient viscosity of the lubricating oil can be:

[0179] ;

[0180] in, It is a dimensionless viscosity-pressure index. The viscosity-pressure coefficient is preset according to actual needs. The viscosity of the lubricating oil in the environment. The viscosity-temperature index is a dimensionless viscosity-temperature index. The viscosity-temperature coefficient is preset according to actual needs. Rated temperature This represents the temperature field distribution value.

[0181] Step S305: Given the ambient density of the lubricating oil, construct a density-pressure-temperature equation based on the ambient density of the lubricating oil.

[0182] In step S305, the expression for constructing the density-pressure-temperature equation based on the ambient density of the lubricating oil can be:

[0183] ;

[0184] in, For the ambient density of the lubricating oil, The coefficient of thermal expansion is preset according to actual needs.

[0185] Step S306: Given the flow rates of the lubricating oil along the x-direction, y-direction, and z-direction, construct an energy equation based on these flow rates.

[0186] In step S306, given the flow rates of the lubricating oil along the x-direction, y-direction, and z-direction, the expression for the energy equation based on these flow rates can be:

[0187] ;

[0188] ;

[0189] in, The flow rate of the lubricating oil along the x-direction (the direction of the minor semi-axis of the target contact area) is [value missing]. The flow rate of the lubricating oil along the y-direction (the direction of the major semi-axis of the target contact area), The flow rate of lubricating oil along the Z-axis (oil film thickness direction), The coordinates of the target contact area along the minor semi-axis direction. Let be the fluid shear stress along the x-direction. Let be the fluid shear stress along the y-direction. For the composite shear stress of lubricating oil, For the characteristic shear stress of the lubricating oil obtained in advance, This is the equivalent viscosity of the lubricating oil. The specific heat capacity of the lubricating oil is obtained in advance. The thermal conductivity of the lubricating oil is obtained in advance.

[0190] This application constructs a hybrid thermo-elasto-fluidic lubrication control equation for bevel gears, providing accurate data for subsequent calculation of the meshing stiffness of the second bevel gear and improving the accuracy of bevel gear meshing stiffness calculation.

[0191] In some embodiments, step S104 may include steps S401 to S405:

[0192] Step S401: Take the minimum oil film thickness value in the first oil film thickness distribution value as the first rigid body center displacement value;

[0193] Step S402: Based on the first pressure distribution value and the first temperature field distribution value, determine the first apparent viscosity value of the lubricating oil through the viscosity-pressure-temperature equation;

[0194] In step S402, the determination of the apparent viscosity of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value using the viscosity-pressure-temperature equation can be achieved by using the first pressure distribution value as the expression for the viscosity-pressure-temperature equation. The first temperature field distribution value is used as the expression for the viscosity-pressure-temperature equation. Calculate the expression for the viscosity-pressure-temperature equation. , which is the first apparent viscosity value of the lubricating oil.

[0195] Step S403: Based on the first pressure distribution value and the first temperature field distribution value, determine the first lubricating oil density value through the density-pressure-temperature equation;

[0196] In step S403, the determination of the first lubricating oil density value based on the first pressure distribution value and the first temperature field distribution value using the density-pressure-temperature equation can be achieved by using the first pressure distribution value as the expression for the density-pressure-temperature equation. The first temperature field distribution value is used as the expression for the density-pressure-temperature equation. Calculate the expression for the density-pressure-temperature equation. , which serves as the first density value for lubricating oil.

[0197] Step S404: Based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value, determine the second pressure distribution value through the film thickness equation;

[0198] In step S404, the determination of the second pressure distribution value based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value using the film thickness equation can be achieved by using the first oil film thickness distribution value as the expression for the film thickness equation. The apparent viscosity of the first lubricating oil is used as the expression for the film thickness equation. The density value of the first lubricating oil is used as the expression for the film thickness equation. The expression for the equation for calculating film thickness. , as the second pressure distribution value.

[0199] Step S405: Determine the meshing stiffness of the second bevel gear based on the second pressure distribution value and the preset oil film distribution conditions.

[0200] The expression for the above-mentioned preset oil film distribution conditions can be:

[0201] ;

[0202] in, The coordinates of the plane containing the target contact area are... The oil film pressure value at that location, Let C be the meshing force vector. The solution domain for the meshing process is pre-defined according to actual needs. The solution domain, pre-defined according to actual needs, is the side length along the x-direction (the minor semi-axis direction of the target contact area) after meshing. The solution domain, pre-defined according to actual needs, is the side length along the y-direction (the semi-major axis of the target contact area) after meshing. This represents the total number of grid nodes along the x-direction (the minor semi-axis direction of the target contact area) after mesh generation. This represents the total number of grid nodes along the y-direction (the semi-major axis of the target contact area) after meshing. For the first The next iteration is along the x-direction (the direction of the minor semi-axis of the target contact area). Each grid node and along the y-direction (the semi-major axis of the target contact area). Pressure distribution values ​​of each grid node For the nth iteration, the x-direction (the direction of the minor semi-axis of the target contact area) is considered. Each grid node and along the y-direction (the semi-major axis of the target contact area). Pressure distribution values ​​of each grid node The pressure error tolerance limit value is preset according to actual needs. The load balance error tolerance limit is a pre-set value based on actual needs. This refers to the x-direction (the direction of the minor semi-axis of the target contact area). Each grid node and along the y-direction (the semi-major axis of the target contact area). Pressure distribution values ​​for each grid node.

[0203] This application determines the meshing stiffness of the second bevel gear based on the second pressure distribution value and the preset oil film distribution conditions. It combines the meshing stiffness calculation based on the preset oil film distribution conditions, providing more accurate data for subsequent calculation of the meshing stiffness of the second bevel gear and improving the accuracy of the bevel gear meshing stiffness calculation.

[0204] In some embodiments, step S405 may include steps S501 to S510:

[0205] Step S501: When the preset pressure distribution iteration number threshold is greater than one and the second pressure distribution value meets the preset oil film distribution conditions, the second temperature field distribution value is determined by the energy equation based on the second pressure distribution value and the first lubricating oil density value.

[0206] The aforementioned preset pressure distribution iteration number threshold can be a value preset according to actual needs.

[0207] In step S501, the determination of the second temperature field distribution value based on the second pressure distribution value and the first lubricating oil density value using an energy equation can be expressed by using the second pressure distribution value as the expression for the energy equation. The density value of the first lubricating oil is used as the expression for the energy equation. Calculate the expression for the energy equation. , as the second temperature field distribution value.

[0208] Step S502: If the second temperature field distribution value meets the preset temperature field distribution conditions, the first oil film thickness distribution value is used as the final oil film thickness distribution value, and the second pressure distribution value is used as the final pressure distribution value.

[0209] The expression for the above-mentioned preset temperature field distribution conditions can be:

[0210] ;

[0211] in, This represents the total number of mesh nodes along the z-direction (the direction of oil film thickness in the target contact area) after mesh generation. This refers to the x-direction (the direction of the minor semi-axis of the target contact area). One grid node, along the y-direction (the semi-major axis of the target contact area). Each grid node and along the z-direction (the direction of oil film thickness in the target contact area) The first grid node Temperature field distribution values, This refers to the x-direction (the direction of the minor semi-axis of the target contact area). One grid node, along the y-direction (the semi-major axis of the target contact area). Each grid node and along the z-direction (the direction of oil film thickness in the target contact area) The temperature field distribution value of the nth grid node.

[0212] Step S503: If the preset pressure distribution iteration number threshold is greater than one, and the second pressure distribution value does not meet the preset oil film distribution conditions, update the first pressure distribution value to the second pressure distribution value.

[0213] Step S504: Based on the second pressure distribution value and the first rigid body center displacement value, determine the second oil film thickness distribution value through the film thickness equation;

[0214] In step S504, the above-mentioned determination of the second oil film thickness distribution value based on the second pressure distribution value and the first rigid body center displacement value through the film thickness equation can be achieved by, in the case that the solution domain in the meshing process is preset according to actual needs, calculating the first surface contact elastic deformation value at each point in the solution domain where the pressure distribution value is the second pressure distribution value through the Businsk integral, and using the first surface contact elastic deformation value as the surface contact elastic deformation value in the expression, and using the first rigid body center displacement value as... The second oil film thickness distribution value is calculated using the expression (in the expression of the film thickness equation). ).

[0215] Step S505: Based on the second pressure distribution value and the first temperature field distribution value, determine the apparent viscosity value of the second lubricating oil through the viscosity-pressure-temperature equation;

[0216] In step S505, the calculation process of determining the apparent viscosity value of the second lubricating oil based on the second pressure distribution value and the first temperature field distribution value through the viscosity-pressure-temperature equation is the same as the calculation process of determining the apparent viscosity value of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value through the viscosity-pressure-temperature equation in step S402, and will not be repeated here.

[0217] Step S506: Based on the second pressure distribution value and the first temperature field distribution value, determine the second lubricating oil density value through the density-pressure-temperature equation;

[0218] In step S506, the calculation process of determining the second lubricating oil density value based on the second pressure distribution value and the first temperature field distribution value through the density-pressure-temperature equation is the same as the calculation process of determining the first lubricating oil density value based on the first pressure distribution value and the first temperature field distribution value through the density-pressure-temperature equation in step S403, and will not be repeated here.

[0219] Step S507: Based on the second oil film thickness distribution value, the second lubricating oil apparent viscosity value, and the second lubricating oil density value, determine the third pressure distribution value through the film thickness equation;

[0220] In step S507, the calculation process of determining the third pressure distribution value based on the second oil film thickness distribution value, the second lubricating oil apparent viscosity value, and the second lubricating oil density value through the film thickness equation is the same as the calculation process of determining the second pressure distribution value based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value in step S404, and will not be repeated here.

[0221] Step S508, and so on, until the Kth lubricating oil density value, the K+1 pressure distribution value and the Kth oil film thickness distribution value are obtained. Based on the Kth lubricating oil density value and the K+1 pressure distribution value, the second temperature field distribution value is determined by the energy equation, where K is the first iteration number which is less than the preset pressure distribution iteration number threshold, and the K+1 pressure distribution value satisfies the preset oil film distribution condition.

[0222] In step S508, the calculation process of determining the second temperature field distribution value based on the Kth lubricating oil density value and the K+1 pressure distribution value through the energy equation is the same as the calculation process of determining the second temperature field distribution value based on the second pressure distribution value and the first lubricating oil density value through the energy equation in step S501, and will not be repeated here.

[0223] Step S509: If the second temperature field distribution value meets the preset temperature field distribution conditions, the Kth oil film thickness distribution value is taken as the final oil film thickness distribution value, and the Kth plus one pressure distribution value is taken as the final pressure distribution value.

[0224] Step S510: Determine the meshing stiffness of the second bevel gear based on the final oil film thickness distribution value and the final pressure distribution value.

[0225] In step S510, the determination of the second bevel gear meshing stiffness based on the final oil film thickness distribution value and the final pressure distribution value can be performed by calculating the second bevel gear meshing stiffness using the following formula:

[0226] ;

[0227] in, This represents the final pressure distribution value. This represents the final oil film thickness distribution value. This represents the meshing stiffness of the second bevel gear.

[0228] This application provides more accurate data for the subsequent calculation of the meshing stiffness of the second bevel gear by combining the meshing stiffness calculation with the preset temperature field distribution conditions, thereby improving the accuracy of the bevel gear meshing stiffness calculation.

[0229] In some embodiments, after step S508, steps S601 to S607 may also be included:

[0230] Step S601: If the second temperature field distribution value does not meet the preset temperature field distribution conditions, update the first temperature field distribution value to the second temperature field distribution value.

[0231] Step S602: Based on the Kth pressure distribution value and the displacement value of the first rigid body center, determine the Kth oil film thickness distribution value through the film thickness equation;

[0232] In step S602, the calculation process of determining the oil film thickness distribution value of the Kth plus one pressure distribution value and the displacement value of the first rigid body center through the film thickness equation is the same as the calculation process of determining the second oil film thickness distribution value based on the second pressure distribution value and the displacement value of the first rigid body center through the film thickness equation in step S504, and will not be repeated here.

[0233] Step S603: Based on the Kth pressure distribution value and the second temperature field distribution value, determine the Kth lubricating oil apparent viscosity value through the viscosity-pressure-temperature equation;

[0234] In step S603, the calculation process of determining the apparent viscosity value of the K+1 lubricating oil based on the K+1 pressure distribution value and the second temperature field distribution value through the viscosity-pressure-temperature equation is the same as the calculation process of determining the apparent viscosity value of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value through the viscosity-pressure-temperature equation in step S402, and will not be repeated here.

[0235] Step S604: Based on the K+1 pressure distribution value and the second temperature field distribution value, determine the K+1 lubricating oil density value through the density-pressure-temperature equation;

[0236] In step S604, the calculation process of determining the density value of the K+1 lubricating oil based on the K+1 pressure distribution value and the second temperature field distribution value through the density-pressure-temperature equation is the same as the calculation process of determining the density value of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value through the density-pressure-temperature equation in step S403, and will not be repeated here.

[0237] Step S605: Based on the K+1 oil film thickness distribution value, the K+1 lubricating oil apparent viscosity value, and the K+1 lubricating oil density value, determine the K+2 pressure distribution value through the film thickness equation;

[0238] In step S605, the calculation process of determining the second pressure distribution value based on the K+1 oil film thickness distribution value, the K+1 lubricating oil apparent viscosity value, and the K+1 lubricating oil density value through the film thickness equation is the same as the calculation process of determining the second pressure distribution value based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value in step S404, and will not be repeated here.

[0239] Step S606, and so on, until the Qth lubricating oil density value, the Q+1th pressure distribution value and the Qth oil film thickness distribution value are obtained. Based on the Qth lubricating oil density value and the Q+1th pressure distribution value, the third temperature field distribution value is determined by the energy equation, where Q is the second iteration number that is less than the preset pressure distribution iteration number threshold and greater than K+1, and the Q+1th pressure distribution value satisfies the preset oil film distribution condition.

[0240] In step S606, the calculation process of determining the third temperature field distribution value based on the Qth lubricating oil density value and the Q+1th pressure distribution value through the energy equation is the same as the calculation process of determining the second temperature field distribution value based on the second pressure distribution value and the first lubricating oil density value through the energy equation in step S501, and will not be repeated here.

[0241] Step S607: If the third temperature field distribution value meets the preset temperature field distribution conditions, take the Qth oil film thickness distribution value as the final oil film thickness distribution value and take the Qth plus one pressure distribution value as the final pressure distribution value.

[0242] In some embodiments, the following may be included after step S605:

[0243] And so on, until the Ath lubricating oil density value, the A+1th pressure distribution value, and the Ath oil film thickness distribution value are obtained, and when A is the third iteration number greater than or equal to the preset pressure distribution iteration number threshold, the displacement value of the second rigid body center is calculated using the following formula:

[0244] ;

[0245] in, This is the displacement value of the center of the second rigid body. This is the displacement value of the center of the first rigid body. The relaxation factor value is preset according to actual needs. This is the load difference;

[0246] Based on the A+1 pressure distribution value and the second rigid body center displacement value, the A+1 oil film thickness distribution value is determined by the film thickness equation.

[0247] The above calculation process for determining the A+3 oil film thickness distribution value based on the A+1 pressure distribution value and the second rigid body center displacement value through the film thickness equation is the same as the calculation process for determining the second oil film thickness distribution value based on the second pressure distribution value and the first rigid body center displacement value through the film thickness equation in step S504, and will not be repeated here.

[0248] Based on the pressure distribution value of the A+1th lubricating oil and the second temperature field distribution value, the apparent viscosity value of the A+1th lubricating oil is determined by the viscosity-pressure-temperature equation.

[0249] The above calculation process for determining the apparent viscosity of the lubricating oil based on the pressure distribution value of the A+1 and the temperature field distribution value through the viscosity-pressure-temperature equation is the same as the calculation process for determining the apparent viscosity of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value through the viscosity-pressure-temperature equation in step S402, and will not be repeated here.

[0250] Based on the pressure distribution value of the A+1th pressure field and the temperature field distribution value of the second temperature field, the density value of the A+1th lubricating oil is determined by the density-pressure-temperature equation.

[0251] The above calculation process for determining the density value of lubricating oil A+1 based on the pressure distribution value and the temperature field distribution value through the density-pressure-temperature equation is the same as the calculation process for determining the density value of the first lubricating oil based on the first pressure distribution value and the first temperature field distribution value through the density-pressure-temperature equation in step S403, and will not be repeated here.

[0252] Based on the A+1 oil film thickness distribution value, the A+1 lubricating oil apparent viscosity value, and the A+1 lubricating oil density value, the A+2 pressure distribution value is determined by the film thickness equation.

[0253] The above calculation process for determining the pressure distribution value of the A+2nd oil film based on the A+1th oil film thickness distribution value, the A+1th lubricating oil apparent viscosity value, and the A+1th lubricating oil density value through the film thickness equation is the same as the calculation process for determining the second pressure distribution value based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value, and the first lubricating oil density value in step S404, and will not be repeated here.

[0254] This process continues until the A+B oil film thickness distribution value, the A+B lubricating oil density value, and the A+B+1 pressure distribution value are obtained. Based on the A+B lubricating oil density value and the A+B+1 pressure distribution value, the third temperature field distribution value is determined through the energy equation, where B is the fourth iteration number less than the preset pressure distribution iteration number threshold, and the A+B+1 pressure distribution value satisfies the preset oil film distribution condition.

[0255] The above calculation process for determining the third temperature field distribution value based on the density value of lubricating oil A+B and the pressure distribution value of A+B+I through the energy equation is the same as the calculation process for determining the second temperature field distribution value based on the second pressure distribution value and the first lubricating oil density value through the energy equation in step S501, and will not be repeated here.

[0256] If the third temperature field distribution value meets the preset temperature field distribution conditions, the A+B oil film thickness distribution value is taken as the final oil film thickness distribution value, and the A+B+I pressure distribution value is taken as the final pressure distribution value.

[0257] This application improves the convergence efficiency by updating the oil film thickness distribution value using the above method when the number of iterations is greater than or equal to a preset pressure distribution iteration threshold, thereby improving the efficiency of bevel gear meshing stiffness calculation.

[0258] In some embodiments, step S105 may include steps S701 to S703:

[0259] Step S701: Based on the final oil film thickness distribution value, determine the dry contact area and the area of ​​the dry contact area where the oil film thickness is less than or equal to the preset oil film thickness threshold in the target contact area.

[0260] In step S701, the above-mentioned determination of the dry contact area and the area of ​​the dry contact area in the target contact area based on the final oil film thickness distribution value, where the oil film thickness is less than or equal to the preset oil film thickness threshold, can be done by taking the area in the target contact area where the oil film thickness is less than or equal to the preset oil film thickness threshold in the final oil film thickness distribution value as the dry contact area and calculating the area of ​​the dry contact area.

[0261] Step S702: Based on the final pressure distribution value, dry contact area and area, determine the meshing stiffness of the third bevel gear corresponding to the dry contact area;

[0262] In step S702, the determination of the third bevel gear meshing stiffness corresponding to the dry contact area based on the final pressure distribution value, dry contact area, and area can be performed by calculating the third bevel gear meshing stiffness corresponding to the dry contact area using the following formula:

[0263] ;

[0264] in, For the meshing stiffness of the third bevel gear, The coordinates of the plane containing the dry contact area are The oil film pressure value at that location, The coordinates of the plane containing the dry contact area are The surface contact elastic deformation value at that location, This represents the area of ​​the dry contact zone.

[0265] Step S703: Determine the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear, the meshing stiffness of the second bevel gear, and the meshing stiffness of the third bevel gear.

[0266] In step S703, the target meshing stiffness of the bevel gear pair, determined based on the meshing stiffness of the first bevel gear, the meshing stiffness of the second bevel gear, and the meshing stiffness of the third bevel gear, can be calculated using the following formula:

[0267] ;

[0268] in, This represents the target meshing stiffness of the bevel gear pair.

[0269] This application determines the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear, thereby achieving an accurate solution for the meshing stiffness of the bevel gear under mixed thermo-elasto-fluid lubrication conditions and improving the accuracy of the bevel gear meshing stiffness calculation.

[0270] Reference Figure 6 Experimental data on the meshing stiffness of bevel gears in the dry contact section are as follows: Figure 6 As shown, the X-axis represents the sampling points within the meshing cycle under dimensionless conditions, and the Y-axis represents the corresponding meshing stiffness of the third bevel gear. Figure 6 (The dry contact portion of the bevel gear meshing stiffness).

[0271] Reference Figure 7 The region in the final oil film thickness distribution where the oil film thickness in the target contact area is greater than the preset oil film thickness threshold is defined as the oil film lubrication zone. Experimental data within the oil film lubrication zone are as follows: Figure 7 As shown, the X-axis represents the sampling points within the meshing cycle under dimensionless conditions, and the Y-axis represents the bevel gear meshing stiffness in the corresponding oil film lubrication zone. The value of the bevel gear meshing stiffness in the corresponding oil film lubrication zone is... ( Figure 7 (The oil film portion of the bevel gear meshing stiffness).

[0272] Reference Figure 8 Experimental data on target meshing stiffness, such as Figure 8 As shown, the X-axis represents the sampling points within the meshing cycle under dimensionless conditions, and the Y-axis represents the corresponding target meshing stiffness (…). Figure 8 (Bevel gear meshing stiffness under mixed friction conditions).

[0273] Additionally, refer to Figure 9 One embodiment of this application provides a bevel gear meshing stiffness calculation system, including a target contact area determination module 1100, a first bevel gear meshing stiffness determination module 1200, an equation construction module 1300, a second bevel gear meshing stiffness determination module 1400, and a target meshing stiffness determination module 1500, wherein:

[0274] The target contact area determination module 1100 is used to determine the target contact area of ​​the meshing interface of the bevel gear pair when performing gear tooth bearing contact analysis on the meshing process of the bevel gear pair.

[0275] The first bevel gear meshing stiffness determination module 1200 is used to determine the entrainment speed of the bevel gear pair and the first bevel gear meshing stiffness based on the target contact area, wherein the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication.

[0276] The equation building module 1300 is used to build control equations for the hybrid thermo-elasto-fluidic lubrication of bevel gears based on the entrainment speed;

[0277] The second bevel gear meshing stiffness determination module 1400 is used to determine the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value, through the bevel gear mixed thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness.

[0278] The target meshing stiffness determination module 1500 is used to determine the target meshing stiffness of the bevel gear pair based on the meshing stiffness of the first bevel gear and the meshing stiffness of the second bevel gear.

[0279] This system, by performing gear tooth bearing contact analysis on the meshing process of bevel gear pairs, determines the target contact area of ​​the meshing interface of the bevel gear pairs. Based on the target contact area, it determines the entrainment velocity and the first bevel gear meshing stiffness, where the first bevel gear meshing stiffness is the bevel gear meshing stiffness without considering lubrication. Based on the entrainment velocity, it constructs a bevel gear hybrid thermo-elasto-fluidic lubrication control equation. With a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value set, it determines the second bevel gear meshing stiffness based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value through the bevel gear hybrid thermo-elasto-fluidic lubrication control equation, where the second bevel gear meshing stiffness is the oil film stiffness. Based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness, it determines the target meshing stiffness of the bevel gear pairs. In this way, it achieves accurate solution of bevel gear meshing stiffness under hybrid thermo-elasto-fluidic lubrication conditions, improving the accuracy of bevel gear meshing stiffness calculation.

[0280] It should be noted that the system embodiments described above are based on the same inventive concept as the method embodiments described above. Therefore, the relevant content of the method embodiments described above is also applicable to the system embodiments described above, and will not be repeated here.

[0281] Figure 10 A schematic diagram of the hardware structure for calculating the meshing stiffness of bevel gears provided in an embodiment of this application is shown.

[0282] The bevel gear meshing stiffness calculation device may include a processor 301 and a memory 302 storing computer program instructions.

[0283] Specifically, the processor 301 may include a central processing unit (CPU), an application-specific integrated circuit (ASIC), or one or more integrated circuits that can be configured to implement the embodiments of this application.

[0284] Memory 302 may include mass storage for data or instructions. For example, and not limitingly, memory 302 may include a hard disk drive (HDD), floppy disk drive, flash memory, optical disk, magneto-optical disk, magnetic tape, or Universal Serial Bus (USB) drive, or a combination of two or more of these. Where appropriate, memory 302 may include removable or non-removable (or fixed) media. Where appropriate, memory 302 may be internal or external to the integrated gateway disaster recovery device. In a particular embodiment, memory 302 is non-volatile solid-state memory.

[0285] In some embodiments, memory 302 may include read-only memory (ROM), random access memory (RAM), disk storage media device, optical storage media device, flash memory device, electrical, optical, or other physical / tangible memory storage device. Thus, generally, memory includes one or more tangible (non-transitory) computer-readable storage media (e.g., memory devices) encoded with software including computer-executable instructions, and when the software is executed (e.g., by one or more processors), it is operable to perform the operations described with reference to the method according to one aspect of this disclosure.

[0286] The processor 301 reads and executes computer program instructions stored in the memory 302 to implement any of the bevel gear meshing stiffness calculation methods in the above embodiments.

[0287] In one example, the bevel gear meshing stiffness calculation device may also include a communication interface 303 and a bus 310. Wherein, as Figure 10 As shown, the processor 301, memory 302, and communication interface 303 are connected through bus 310 and complete communication with each other.

[0288] The communication interface 303 is mainly used to realize communication between various modules, devices, units and / or equipment in the embodiments of this application.

[0289] Bus 310 includes hardware, software, or both, that couples components of a bevel gear meshing stiffness calculation device together. For example, and not limitingly, the bus may include an Accelerated Graphics Port (AGP) or other graphics bus, an Enhanced Industry Standard Architecture (EISA) bus, a Front Side Bus (FSB), HyperTransport (HT) interconnect, an Industry Standard Architecture (ISA) bus, an Infinite Bandwidth Interconnect, a Low Pin Count (LPC) bus, a memory bus, a Microchannel Architecture (MCA) bus, a Peripheral Component Interconnect (PCI) bus, a PCI-Express (PCI-X) bus, a Serial Advanced Technology Attachment (SATA) bus, a Video Electronics Standards Association Local (VLB) bus, or other suitable buses, or combinations of two or more of these. Where appropriate, bus 310 may include one or more buses. Although specific buses are described and illustrated in embodiments of this application, any suitable bus or interconnect is contemplated herein.

[0290] The bevel gear meshing stiffness calculation device can execute the bevel gear meshing stiffness calculation method in the embodiments of this application based on a three-dimensional design model, thereby achieving a combination Figure 1 and Figure 9 The method and system for calculating the meshing stiffness of bevel gears are described.

[0291] Furthermore, in conjunction with the bevel gear meshing stiffness calculation method in the above embodiments, this application embodiment can provide a computer storage medium for implementation. This computer storage medium stores computer program instructions; when these computer program instructions are executed by a processor, they implement any of the bevel gear meshing stiffness calculation methods in the above embodiments.

[0292] It should be clarified that this application is not limited to the specific configurations and processes described above and shown in the figures. For the sake of brevity, detailed descriptions of known methods are omitted here. In the above embodiments, several specific steps are described and shown as examples. However, the method process of this application is not limited to the specific steps described and shown. Those skilled in the art can make various changes, modifications, and additions, or change the order of steps, after understanding the spirit of this application.

[0293] The functional blocks shown in the above block diagram can be implemented as hardware, software, firmware, or a combination thereof. When implemented in hardware, they can be, for example, electronic circuits, application-specific integrated circuits (ASICs), appropriate firmware, plug-ins, function cards, etc. When implemented in software, the elements of this application are programs or code segments used to perform the required tasks. Programs or code segments can be stored on a machine-readable medium or transmitted over a transmission medium or communication link via data signals carried on a carrier wave. "Machine-readable medium" can include any medium capable of storing or transmitting information. Examples of machine-readable media include electronic circuits, semiconductor memory devices, ROM, flash memory, erasable ROM (EROM), floppy disks, CD-ROMs, optical disks, hard disks, fiber optic media, radio frequency (RF) links, etc. Code segments can be downloaded via computer networks such as the Internet, intranets, etc.

[0294] It should also be noted that the exemplary embodiments mentioned in this application describe methods or systems based on a series of steps or apparatus. However, this application is not limited to the order of the above steps; that is, the steps can be performed in the order mentioned in the embodiments, or in a different order, or several steps can be performed simultaneously.

[0295] The aspects of this disclosure have been described above with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this disclosure. It should be understood that each block in the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, or other programmable data processing apparatus to produce a machine such that these instructions, executable via the processor of the computer or other programmable data processing apparatus, enable the implementation of the functions / actions specified in one or more blocks of the flowchart illustrations and / or block diagrams. Such a processor can be, but is not limited to, a general-purpose processor, a special-purpose processor, a special application processor, or a field-programmable logic circuit. It is also understood that each block in the block diagrams and / or flowcharts, and combinations of blocks in the block diagrams and / or flowcharts, can also be implemented by special-purpose hardware performing the specified functions or actions, or can be implemented by a combination of special-purpose hardware and computer instructions.

[0296] The above description is merely a specific implementation of this application. Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the specific working processes of the systems, modules, and units described above can be referred to the corresponding processes in the foregoing method embodiments, and will not be repeated here. It should be understood that the protection scope of this application is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in this application, and these modifications or substitutions should all be covered within the protection scope of this application.

Claims

1. A bevel gear mesh stiffness calculation method, characterized by, The bevel gear engagement stiffness calculation method comprises: In the case of gear tooth bearing contact analysis on the meshing process of the bevel gear pair, determining a target contact area of the meshing interface of the bevel gear pair; Based on the target contact area, determining the entrainment speed and the first bevel gear engagement stiffness of the bevel gear pair, wherein the first bevel gear engagement stiffness is the bevel gear engagement stiffness without considering lubrication, the target contact area is an elliptical area, and the bevel gear pair comprises a large gear and a small gear, specifically: In the case of discretizing the meshing process of the bevel gear pair into a plurality of meshing points at a preset time interval, obtaining the meshing point position vector and the meshing force vector of each meshing point; Obtaining the large gear angular velocity of the large gear, the small gear angular velocity of the small gear, the long semi-axis vector of the target contact area, and the short semi-axis vector of the target contact area; Based on the large gear angular velocity of the large gear, the small gear angular velocity of the small gear, the long semi-axis vector, and the short semi-axis vector, determining the entrainment speed of each meshing point; In the case of setting a first torque value to make the bevel gear pair in an unloaded state, determining an unloaded transmission error; in the case of setting a second torque value to make the bevel gear pair in a loaded state, determining a loaded transmission error; Based on the unloaded transmission error, the loaded transmission error, the meshing point position vector, and the meshing force vector, determining the first bevel gear engagement stiffness of each meshing point; Based on the entrainment speed, constructing a bevel gear mixed thermal elastohydrodynamic lubrication control equation, wherein the bevel gear mixed thermal elastohydrodynamic lubrication control equation comprises a Reynolds equation, a film thickness equation, a viscosity-pressure-temperature equation, a density-pressure-temperature equation, and an energy equation, specifically: Determining the entrainment included angle between the entrainment speed and the short semi-axis vector of each meshing point; Based on the long semi-axis vector, the short semi-axis vector, the entrainment included angle, and the entrainment speed, constructing the Reynolds equation; Based on the long semi-axis vector and the short semi-axis vector, constructing the film thickness equation; In the case of obtaining a rated temperature and a lubricating oil environment viscosity, based on the rated temperature and the lubricating oil environment viscosity, constructing the viscosity-pressure-temperature equation; In the case of obtaining a lubricating oil environment density, based on the lubricating oil environment density, constructing the density-pressure-temperature equation; In the case of determining the flow velocity of the lubricating oil along the x direction, the flow velocity of the lubricating oil along the y direction, and the flow velocity of the lubricating oil along the z direction, based on the flow velocity of the lubricating oil along the x direction, the flow velocity of the lubricating oil along the y direction, and the flow velocity of the lubricating oil along the z direction, constructing the energy equation; In the case of setting a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value, based on the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value, determining a second bevel gear engagement stiffness through the bevel gear mixed thermal elastohydrodynamic lubrication control equation, wherein the second bevel gear engagement stiffness is the oil film stiffness; Based on the first bevel gear engagement stiffness and the second bevel gear engagement stiffness, determining the target engagement stiffness of the bevel gear pair.

2. The bevel gear mesh stiffness calculation method of claim 1, wherein, determining a second bevel gear mesh stiffness based on the first pressure distribution value, the first oil film thickness distribution value and the first temperature field distribution value by using a bevel gear mixed thermal elastohydrodynamic lubrication control equation, comprising: taking a minimum oil film thickness value in the first oil film thickness distribution value as a first rigid body center displacement value; determining a first lubricating oil apparent viscosity value based on the first pressure distribution value and the first temperature field distribution value by using a viscosity-pressure-temperature equation; determining a first lubricating oil density value based on the first pressure distribution value and the first temperature field distribution value by using a density-pressure-temperature equation; determining a second pressure distribution value based on the first oil film thickness distribution value, the first lubricating oil apparent viscosity value and the first lubricating oil density value by using a film thickness equation; determining the second bevel gear mesh stiffness based on the second pressure distribution value and a preset oil film distribution condition.

3. The bevel gear mesh stiffness calculation method of claim 2, wherein, determining the second bevel gear mesh stiffness based on the second pressure distribution value and a preset oil film distribution condition, comprising: determining a second temperature field distribution value based on the second pressure distribution value and the first lubricating oil density value by using an energy equation in a case that a preset pressure distribution iteration number threshold is greater than one and the second pressure distribution value satisfies the preset oil film distribution condition; taking the first oil film thickness distribution value as a final oil film thickness distribution value and taking the second pressure distribution value as a final pressure distribution value in a case that the second temperature field distribution value satisfies a preset temperature field distribution condition; updating the first pressure distribution value to the second pressure distribution value in a case that the preset pressure distribution iteration number threshold is greater than one and the second pressure distribution value does not satisfy the preset oil film distribution condition; determining a second oil film thickness distribution value based on the second pressure distribution value and the first rigid body center displacement value by using the film thickness equation; determining a second lubricating oil apparent viscosity value based on the second pressure distribution value and the first temperature field distribution value by using the viscosity-pressure-temperature equation; determining a second lubricating oil density value based on the second pressure distribution value and the first temperature field distribution value by using the density-pressure-temperature equation; determining a third pressure distribution value based on the second oil film thickness distribution value, the second lubricating oil apparent viscosity value and the second lubricating oil density value by using the film thickness equation; iterating until a Kth lubricating oil density value, a Kth plus one pressure distribution value and a Kth oil film thickness distribution value are obtained, and determining a second temperature field distribution value based on the Kth lubricating oil density value and the Kth plus one pressure distribution value by using the energy equation, wherein K is a first iteration number less than the preset pressure distribution iteration number threshold, and the Kth plus one pressure distribution value satisfies the preset oil film distribution condition; taking the Kth oil film thickness distribution value as the final oil film thickness distribution value and taking the Kth plus one pressure distribution value as the final pressure distribution value in a case that the second temperature field distribution value satisfies a preset temperature field distribution condition; determining the second bevel gear mesh stiffness based on the final oil film thickness distribution value and the final pressure distribution value.

4. The bevel gear mesh stiffness calculation method of claim 3, wherein, after the second temperature field distribution value is determined based on the Kth lubricating oil density value and the Kth plus one pressure distribution value through the energy equation, further comprising: in the case where the second temperature field distribution value does not satisfy the preset temperature field distribution condition, updating the first temperature field distribution value to the second temperature field distribution value; determining a Kth plus one oil film thickness distribution value based on the Kth plus one pressure distribution value and the first rigid body center displacement value through the film thickness equation; determining a Kth plus one apparent viscosity value of the lubricating oil based on the Kth plus one pressure distribution value and the second temperature field distribution value through the viscosity-pressure-temperature equation; determining a Kth plus one lubricating oil density value based on the Kth plus one pressure distribution value and the second temperature field distribution value through the density-pressure-temperature equation; determining a Kth plus two pressure distribution value based on the Kth plus one oil film thickness distribution value, the Kth plus one apparent viscosity value of the lubricating oil and the Kth plus one lubricating oil density value through the film thickness equation; and so on, until a Qth lubricating oil density value, a Qth plus one pressure distribution value and a Qth oil film thickness distribution value are obtained, and a third temperature field distribution value is determined based on the Qth lubricating oil density value and the Qth plus one pressure distribution value through the energy equation, wherein Q is a second iteration number smaller than the preset pressure distribution iteration number threshold and larger than K plus one, the Qth plus one pressure distribution value satisfies the preset oil film distribution condition; in the case where the third temperature field distribution value satisfies the preset temperature field distribution condition, taking the Qth oil film thickness distribution value as a final oil film thickness distribution value and taking the Qth plus one pressure distribution value as a final pressure distribution value.

5. The bevel gear mesh stiffness calculation method of claim 4, wherein, determining the target meshing stiffness of the bevel gear pair based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness, comprising: determining a dry contact area in the target contact area in which the oil film thickness is less than or equal to a preset oil film thickness threshold value based on the final oil film thickness distribution value; determining a third bevel gear meshing stiffness corresponding to the dry contact area based on the final pressure distribution value, the dry contact area and the area; determining the target meshing stiffness of the bevel gear pair based on the first bevel gear meshing stiffness, the second bevel gear meshing stiffness and the third bevel gear meshing stiffness.

6. A bevel gear mesh stiffness calculation system characterized by, The bevel gear meshing stiffness calculation system comprises: a target contact area determination module, configured to determine a target contact area of an engagement interface of a bevel gear pair in the case of gear tooth bearing contact analysis on the engagement process of the bevel gear pair; a first bevel gear meshing stiffness determination module, configured to determine a first bevel gear meshing stiffness and an entrainment velocity of the bevel gear pair based on the target contact area, wherein the first bevel gear meshing stiffness is a bevel gear meshing stiffness without considering lubrication, the target contact area is an elliptical area, and the bevel gear pair comprises a large gear and a small gear, specifically: in the case of discretizing the engagement process of the bevel gear pair into a plurality of engagement points at a preset time interval, obtaining an engagement point position vector and an engagement force vector of each engagement point; obtaining a large wheel angular velocity of the large wheel, a small wheel angular velocity of the small wheel, a long semi-axis vector of the target contact area, and a short semi-axis vector of the target contact area; determining the entraining velocity of each meshing point based on the large wheel angular velocity of the large wheel, the small wheel angular velocity of the small wheel, the long semi-axis vector, and the short semi-axis vector; determining an empty load transmission error in a case where a first torque value is set to make the bevel gear pair in an empty load, and determining a load transmission error in a case where a second torque value is set to make the bevel gear pair in a load; determining the first bevel gear meshing stiffness of each meshing point based on the empty load transmission error, the load transmission error, the meshing point position vector, and the meshing force vector; an equation construction module configured to construct a bevel gear mixed thermal elastohydrodynamic lubrication control equation based on the entraining velocity, wherein the bevel gear mixed thermal elastohydrodynamic lubrication control equation comprises a Reynolds equation, a film thickness equation, a viscosity-pressure-temperature equation, a density-pressure-temperature equation, and an energy equation, and specifically: determining an entraining included angle of the entraining velocity and the short semi-axis vector; constructing the Reynolds equation based on the long semi-axis vector, the short semi-axis vector, the entraining included angle, and the entraining velocity; constructing the film thickness equation based on the long semi-axis vector and the short semi-axis vector; constructing the viscosity-pressure-temperature equation based on a rated temperature and a lubricating oil environment viscosity in a case where the rated temperature and the lubricating oil environment viscosity are obtained; constructing the density-pressure-temperature equation based on a lubricating oil environment density in a case where the lubricating oil environment density is obtained; constructing the energy equation based on a lubricating oil flow velocity along an x direction, a lubricating oil flow velocity along a y direction, and a lubricating oil flow velocity along a z direction in a case where the lubricating oil flow velocity along the x direction, the lubricating oil flow velocity along the y direction, and the lubricating oil flow velocity along the z direction are determined; a second bevel gear meshing stiffness determination module configured to determine a second bevel gear meshing stiffness based on a first pressure distribution value, a first oil film thickness distribution value, and a first temperature field distribution value through the bevel gear mixed thermal elastohydrodynamic lubrication control equation in a case where the first pressure distribution value, the first oil film thickness distribution value, and the first temperature field distribution value are set, wherein the second bevel gear meshing stiffness is an oil film stiffness; a target meshing stiffness determination module configured to determine a target meshing stiffness of the bevel gear pair based on the first bevel gear meshing stiffness and the second bevel gear meshing stiffness.

7. A bevel gear mesh stiffness calculation device characterized by, The computer readable storage medium stores computer executable instructions for causing a computer to perform a bevel gear meshing stiffness calculation method according to any one of claims 1 to 5.

8. A computer-readable storage medium, characterized in that: The computer readable storage medium stores computer executable instructions for causing a computer to perform a bevel gear meshing stiffness calculation method according to any one of claims 1 to 5.

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