Heat balance calculation method and device of differential mechanism, differential mechanism, storage medium and electronic device

Abstract

The invention provides a thermal balance calculation method and device of a differential mechanism, the differential mechanism, a storage medium and an electronic device.The method comprises the steps that geometric parameters of a planetary gear and a half axle gear of the differential mechanism, the rotating speed of the half axle gear and the input torque are obtained; calculating contact pressure data between the planetary gear and the half axle gear according to the geometric parameters and the input torque; calculating a friction pair bearing characteristic number of the differential according to the contact pressure data; acquiring the friction coefficient in the differential according to the characteristic number of the friction pair bearing; calculating the total friction loss power of the differential according to the friction coefficient, the half axle gear rotating speed and the contact pressure data; and the cooling oil amount needed by the differential in unit time is calculated according to the friction loss total power and the lubricating oil parameters. According to the embodiment, a scheme for accurately calculating the cooling lubricating oil amount of the differential mechanism is achieved, a forced lubrication differential mechanism structure is provided, and the problems of reliability and efficiency caused by cooling lubrication of the differential mechanism in the related technology are solved.

Description

Technical Field

[0001] This invention relates to the field of vehicle technology, and more specifically, to a method and apparatus for calculating the thermal balance of a differential, a differential, a storage medium, and an electronic device. Background Technology

[0002] In related technologies, the differential, as a core component of vehicle power transmission, directly affects transmission efficiency and service life due to its lubrication and thermal management performance. Traditional differentials mainly rely on gear-driven oil splash lubrication. The required amount of cooling lubrication oil is generally determined through experience and repeated testing, rather than being given a direct result through thermal balance calculations. Furthermore, to meet reliability requirements, as much oil churning as possible is used to ensure the differential receives sufficient oil, leading to increased oil churning losses and reduced efficiency. In particular, when the reducer adopts fully active lubrication technology to improve efficiency, a forced lubrication differential structure is also required. Under different operating conditions during vehicle operation, traditional differential and oil quantity determination methods are no longer sufficient to meet the cooling oil requirements for thermal balance. In such cases, improper supply of cooling lubricating oil can lead to reliability issues or excessive energy consumption due to excessive load on the lubrication system.

[0003] No efficient and accurate solution has yet been found to address the aforementioned issues in the relevant technologies. Summary of the Invention

[0004] This invention provides a method and apparatus for calculating the thermal balance of a differential, a differential, a storage medium, and an electronic device to solve technical problems in related technologies.

[0005] According to an embodiment of the present invention, a method for calculating the thermal balance of a differential is provided, comprising: acquiring the geometric parameters of the planetary gears and axle gears of the differential, the rotational speed of the axle gears, and the input torque; calculating the contact pressure data between the planetary gears and the axle gears based on the geometric parameters and the input torque; calculating the bearing characteristic number of the friction pair of the differential based on the contact pressure data; acquiring the friction coefficient inside the differential based on the bearing characteristic number of the friction pair; calculating the total friction loss power of the differential based on the friction coefficient, the rotational speed of the axle gears, and the contact pressure data; and calculating the amount of cooling oil required by the differential per unit time based on the total friction loss power and lubricating oil parameters.

[0006] Optionally, calculating the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed, and the contact pressure data includes: calculating the friction torque of each friction pair and the bevel gear meshing transmission efficiency of the differential based on the friction coefficient, the contact pressure data, and the bevel gear geometric parameters of the differential; calculating the friction power of each friction pair based on the friction torque of each friction pair, the half-shaft gear speed, and the bevel gear meshing transmission efficiency; and using the friction power of each friction pair to calculate the total friction loss power of the differential.

[0007] Optionally, calculating the frictional torque of each friction pair and the bevel gear meshing transmission efficiency of the differential based on the friction coefficient, the contact pressure data, and the bevel gear geometric parameters of the differential includes: calculating the frictional torque of each friction pair and the bevel gear meshing transmission efficiency of the differential using the following formula: ; ; ; ; in, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency. The coefficient of friction between the planetary shaft and the planetary gear. The force exerted by the planetary gear shaft on the planetary gear is d, where d is the diameter of the planetary gear shaft. Let Fc be the coefficient of friction between the ball bearing and the planetary gear, and Fc be the force exerted by the differential shell on the planetary gear. The outer diameter of the ball pad, The inner diameter of the ball pad, The coefficient of friction between the ball bearing and the planetary gear is denoted as . The force exerted by the differential housing on the half-shaft gear, The outer diameter of the flat pad, The inner diameter of the flat washer, Let K1 be the equivalent spur gear meshing transmission efficiency, K2 be the coefficient for the first process, Q1 be the coefficient for the second process, and Q2 be the coefficient for the third process. The equivalent number of teeth for a planetary gear. The equivalent number of teeth for the half-shaft gear. The equivalent total overlap, The equivalent planetary gear overlap ratio, This refers to the equivalent half-shaft gear overlap ratio. Where k is the equivalent transmission ratio, and Z is the differential coefficient. hZ represents the number of teeth on the half-shaft gear. s Where μ is the number of teeth on the planetary gear, and μ4 is the coefficient of friction between the planetary gear and the half-shaft gear. The rotational speed of the left half-shaft gear. This represents the rotational speed of the right half-shaft gear.

[0008] Optionally, the frictional power of each friction pair is calculated based on the frictional torque of each friction pair, the rotational speed of the half-shaft gear, and the meshing transmission efficiency of the bevel gear, including: The frictional power of each friction pair is calculated using the following formula: ; in, The frictional power between the planetary gears and the planetary shafts. The frictional power between the planetary gear and the ball bearing pad. The frictional power between the half-shaft gear and the flat washer. The power loss due to the meshing of planetary gears and half-shaft gears, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency, Input torque to the main reduction gear, The angular velocity of the main reducer gear. The rotational angular velocity of the planetary gear. Z is the angular velocity of the half-shaft gear's rotation. h Z represents the number of teeth on the half-shaft gear. s This refers to the number of teeth on a planetary gear. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. This is the rotational speed of the planetary gear.

[0009] Optionally, calculating the amount of cooling oil required by the differential per unit time based on the total friction loss power and lubricating oil parameters includes: calculating the amount of cooling oil q required by the differential per unit time using the following formula: ; in, Let ρ be the specific heat capacity of the lubricating oil, ρ be the density of the lubricating oil, and ΔT be the temperature difference between the lubricating oil inlet and outlet. The total power of frictional loss, the lubricating oil parameters include , ρ, △T.

[0010] Optionally, calculating the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque includes: calculating directional force data based on the input torque and the geometric parameters, wherein the directional force data includes the tangential force, axial force, and axial displacement of the half-shaft gear; calculating force data based on the directional force data, wherein the force data includes the force exerted by the planetary shaft on the planetary gear, the force exerted by the differential housing on the planetary gear, and the force exerted by the differential housing on the half-shaft gear; and calculating the contact pressure data between the planetary gear and the half-shaft gear using the force data, wherein the contact pressure data includes the contact pressure between the planetary shaft and the planetary gear, the contact pressure between the ball washer and the planetary gear, and the contact pressure between the flat washer and the half-shaft gear.

[0011] Optionally, calculating the friction pair bearing characteristic number of the differential based on the contact pressure data includes: determining the lubricating oil viscosity, left half-shaft gear speed, and right half-shaft gear speed of the differential; and calculating the friction pair bearing characteristic number of the differential based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed.

[0012] Optionally, calculating the friction pair bearing characteristic numbers of the differential based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed includes: calculating the planetary gear rotation speed using the left half-shaft gear speed and the right half-shaft gear speed; and calculating the friction pair bearing characteristic numbers of the differential using the following formula: ; in, For the bearing characteristic numbers of the friction pair between the planetary shaft and the planetary gear, For the bearing characteristic parameters of the friction pair between the ball washer and the planetary gear, η represents the bearing characteristic number of the friction pair between the flat washer and the half-shaft gear, and η is the viscosity of the lubricating oil. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. For the contact pressure between the planetary shaft and the planetary gear, For the contact pressure between the ball washer and the planetary gear, The contact pressure between the flat washer and the half-shaft gear. This is the rotational speed of the planetary gear.

[0013] According to another embodiment of the present invention, a thermal balance calculation device for a differential is provided, comprising: a first acquisition module for acquiring geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed, and the input torque; a first calculation module for calculating contact pressure data between the planetary gears and the half-shaft gears based on the geometric parameters and the input torque; a second calculation module for calculating the bearing characteristic number of the friction pair of the differential based on the contact pressure data; a second acquisition module for acquiring the friction coefficient inside the differential based on the bearing characteristic number of the friction pair; a third calculation module for calculating the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed, and the contact pressure data; and a fourth calculation module for calculating the amount of cooling oil required by the differential per unit time based on the total friction loss power and lubricating oil parameters.

[0014] According to another embodiment of the present invention, a differential is provided, comprising an end cover, a differential housing, a controller, and a planetary gear shaft, two planetary gears, and two half-shaft gears disposed within the differential housing. The controller, connected to the end cover and the differential housing, includes the thermal balance calculation device for the differential described in the above embodiment. The end cover has gears that can transmit power to the differential. An outer annular groove and a radial oil hole are formed on the end cover journal. An inner annular groove and an axial groove are formed in the inner hole. An end face groove is formed on the right end face. The radial oil hole communicates with the outer and inner annular grooves, and the inner annular groove communicates with the axial groove. An annular volume cavity is provided at the end of the axial groove of the end cover, communicating with both the axial groove and the end face groove to form a smooth oil passage, allowing forced oil supply to the differential interior through the radial oil hole. The differential housing and the end cover are connected by connecting bolts. The planetary gear shaft, after mating with the differential housing, forms an oil discharge channel, through which lubricating oil entering the differential interior is discharged, forming a dynamic circulation.

[0015] Optionally, the area outside the outer annular groove of the end cover journal mates with the housing to form a sealing section, which can ensure that lubricating oil enters the outer annular groove of the end cover through the oil passage of the housing.

[0016] Optionally, the outer annular groove of the end cap journal is provided with a number of radial oil holes evenly distributed around its circumference, through which lubricating oil enters the inner annular groove from the outer annular groove.

[0017] Optionally, a certain number of axial grooves are uniformly formed in the circumferential direction of the inner hole of the end cap.

[0018] Optionally, the portion of the end cover outside the annular groove may mate with the drive shaft to form a sealing section, ensuring that lubricating oil flows into the differential through the axial groove.

[0019] Optionally, the end cap axial groove is provided with an annular volume cavity to ensure that lubricating oil is collected in the annular volume cavity through the axial groove.

[0020] Optionally, the right end face of the end cover is provided with an end face groove that communicates with the annular volume cavity, ensuring that the lubricating oil in the annular volume cavity enters the differential through the end face groove.

[0021] Optionally, the differential housing is a sealed housing, and lubricating oil can fill the interior of the differential to ensure that the lubricating oil fully lubricates the internal parts of the differential.

[0022] Optionally, the cross-sectional profile of the planetary gear shaft is composed of double circular arcs and straight lines, which, after mating with the differential housing, form a circular arc channel. The lubricating oil entering the differential is discharged through the circular arc channel, forming a dynamic circulation.

[0023] According to another aspect of the embodiments of this application, a storage medium is also provided, the storage medium including a stored program that executes the above steps when the program is run.

[0024] According to another aspect of the embodiments of this application, an electronic device is also provided, including a processor, a communication interface, a memory, and a communication bus, wherein the processor, the communication interface, and the memory communicate with each other through the communication bus; wherein: the memory is used to store computer programs; and the processor is used to execute the steps in the above method by running the programs stored in the memory.

[0025] This application also provides a computer program product containing instructions that, when run on a computer, cause the computer to perform the steps in the above-described method.

[0026] The beneficial effects of this invention are: 1. By calculating the cooling oil requirements under different operating conditions through thermal balance calculations, a solution for accurately calculating the cooling lubricating oil volume of the differential was realized, which solved the reliability problem of the differential caused by poor lubrication in related technologies and avoided the efficiency loss caused by splash lubrication. 2. Using the forced lubrication differential structure in this embodiment, precise oil supply and dynamic adjustment of oil quantity are achieved inside the differential, which solves the reliability problem of the differential caused by insufficient lubrication and avoids the increased loss of churning power caused by excessive oil addition in traditional churning lubrication. 3. The differential housing adopts a closed oil circuit structure, which does not require additional sealing parts, making it easier to implement in engineering and simplifying the manufacturing process. Attached Figure Description

[0027] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this application, illustrate exemplary embodiments of the invention and, together with their description, serve to explain the invention and do not constitute an undue limitation thereof. In the drawings: Figure 1This is a hardware structure block diagram of a differential according to an embodiment of the present invention; Figure 2 This is a flowchart of a thermal balance calculation method for a differential according to an embodiment of the present invention; Figure 3 This is an optional flowchart of the differential thermal balance calculation method in the embodiments of the present invention; Figure 4 This is a structural block diagram of a differential thermal balance calculation device according to an embodiment of the present invention; Figure 5 This is a schematic diagram of the differential assembly in an embodiment of the present invention; Figure 6 This is a schematic diagram of the end cap structure in an embodiment of the present invention. Figure 1 ; Figure 7 This is a schematic diagram of the end cap structure in an embodiment of the present invention. Figure 2 ; Figure 8 This is a schematic diagram of the differential housing structure in an embodiment of the present invention; Figure 9 This is a schematic diagram of the planetary gear shaft in an embodiment of the present invention. Detailed Implementation

[0028] To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present application, and not all of them. Based on the embodiments of the present application, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of the present application. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of the present application can be combined with each other.

[0029] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0030] Example 1 The method embodiment provided in Embodiment 1 of this application can be executed in an automobile, differential, fluid controller, or similar processing device. Taking operation on a differential as an example, Figure 1 This is a hardware structure block diagram of a differential according to an embodiment of the present invention. Figure 1 As shown, a differential may include one or more ( Figure 1 Only one is shown in the diagram. A processor 101 (which may include, but is not limited to, a microprocessor MCU or a programmable logic device FPGA, etc.) and a memory 102 for storing data are also shown. Optionally, the differential may further include a transmission device 103 for communication functions and an input / output device 104. Those skilled in the art will understand that... Figure 1 The structure shown is for illustrative purposes only and does not limit the structure of the differential described above. For example, the differential may also include a... Figure 1 The more or fewer components shown, or having the same Figure 1 The different configurations shown.

[0031] The memory 102 can be used to store differential programs, such as application software programs and modules, like the differential program corresponding to a vehicle instability control method for a differential in this embodiment of the invention. The processor 101 executes various functional applications and data processing by running the differential program stored in the memory 102, thereby implementing the aforementioned method. The memory 102 may include high-speed random access memory and may also include non-volatile memory, such as one or more magnetic storage devices, flash memory, or other non-volatile solid-state memory. In some instances, the memory 102 may further include memory remotely located relative to the processor 101, and these remote memories can be connected to the differential via a network. Examples of such networks include, but are not limited to, the Internet, corporate intranets, local area networks, mobile communication networks, and combinations thereof.

[0032] The transmission device 103 is used to receive or send data via a network. Specific examples of the network described above may include a wireless network provided by the differential's communication provider. In one example, the transmission device 103 includes a Network Interface Controller (NIC), which can connect to other network devices via a base station to communicate with the Internet. In another example, the transmission device 103 may be a Radio Frequency (RF) module used for wireless communication with the Internet.

[0033] This embodiment provides a method for calculating the thermal balance of a differential. Figure 2 This is a flowchart of a differential thermal balance calculation method according to an embodiment of the present invention, such as... Figure 2As shown, the process includes the following steps: Step S201: Obtain the geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed and the input torque; The geometric parameters of this embodiment include the specific dimensions of the bevel gears (including planetary gears and axle gears) of the differential, the number of gear teeth (number of axle gear teeth, number of planetary gear teeth, equivalent number of planetary gear teeth, equivalent number of axle gear teeth), the pitch circle diameter of the axle gear, the pressure angle, the pitch cone angle of the axle gear, the contact area between the planetary gear shaft and the planetary gear, the contact area between the ball washer and the planetary gear, the contact area between the flat washer and the axle gear, the diameter of the planetary gear shaft, the outer diameter of the ball washer, the inner diameter of the ball washer, the outer diameter of the flat washer, the inner diameter of the flat washer, the equivalent planetary gear overlap ratio, and the equivalent axle gear overlap ratio. In addition, known parameters also include the torque transmitted by the differential under specific operating conditions (axle gear torque, main reduction gear input torque) and the speed difference between the left and right axle gears (the axle gear speed is obtained through sensor acquisition), and the lubricating oil parameters used in the electric drive reducer, which can be directly obtained from tables, such as the specific heat capacity of the lubricating oil, the density of the lubricating oil, and the dynamic viscosity of the lubricating oil.

[0034] Step S202: Calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque; Optionally, the contact pressure data includes the contact pressure between the planetary shaft and the planetary gear, the contact pressure between the ball washer and the planetary gear, and the contact pressure between the flat washer and the half-shaft gear.

[0035] Step S203: Calculate the bearing characteristic numbers of the friction pair of the differential based on the contact pressure data; Step S204: Obtain the friction coefficient inside the differential based on the characteristic number of the friction pair bearing; The bearing characteristic numbers of the friction pair can identify the lubrication type of the differential. By looking up the bearing characteristic numbers in a table, the friction coefficient corresponding to the lubrication type can be obtained.

[0036] Step S205: Calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed, and the contact pressure data; Step S206: Calculate the amount of cooling oil required by the differential per unit time based on the total power of friction loss and the lubricating oil parameters.

[0037] Through the above steps, the geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed, and the input torque are obtained; the contact pressure data between the planetary gears and half-shaft gears are calculated based on the geometric parameters and the input torque; the bearing characteristic number of the friction pair of the differential is calculated based on the contact pressure data; the friction coefficient inside the differential is obtained based on the bearing characteristic number of the friction pair; the total friction loss power of the differential is calculated based on the friction coefficient, the half-shaft gear speed, and the contact pressure data; and the amount of cooling oil required by the differential per unit time is calculated based on the total friction loss power and the lubricating oil parameters. This achieves a precise calculation method for the amount of cooling lubricating oil required by the differential, solving the reliability problem of differentials caused by poor lubrication in related technologies and avoiding efficiency loss caused by splash lubrication.

[0038] In one embodiment of this example, calculating the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque includes: calculating directional force data based on the input torque and the geometric parameters, wherein the directional force data includes the tangential force of the half-shaft gear, the axial force of the half-shaft gear, and the axial force of the half-shaft gear; calculating force data based on the directional force data, wherein the force data includes the force exerted by the planetary shaft on the planetary gear, the force exerted by the differential housing on the planetary gear, and the force exerted by the differential housing on the half-shaft gear; and using the force data to calculate the contact pressure data between the planetary gear and the half-shaft gear, wherein the contact pressure data includes the contact pressure between the planetary shaft and the planetary gear, the contact pressure between the ball washer and the planetary gear, and the contact pressure between the flat washer and the half-shaft gear.

[0039] The meshing forces on the planetary gear and the half-shaft gear are calculated using the following formula to obtain the tangential force F of the half-shaft gear. t Axial force Fa1 of the half-shaft gear, radial force Fr2 of the planetary gear: ; In the formula: F t dm1 is the pitch circle diameter of the half-shaft gear, Fr1 is the radial force of the half-shaft gear, Fa1 is the axial force of the half-shaft gear, Fr2 is the radial force of the planetary gear, Fa2 is the axial force of the planetary gear, Fn is the directional force of the tooth surface meshing; α is the pressure angle, and δ1 is the pitch cone angle of the half-shaft gear.

[0040] Calculate the force F exerted by the planetary shaft on the planetary gear using the following formula. x The force F exerted by the differential shell on the planetary gear c The force F exerted by the differential housing on the half-shaft gear b : ; In the formula: F xF is the force exerted by the planetary axis on the planetary gear. c F is the force exerted by the differential shell on the planetary gear. b The force exerted by the differential housing on the half-shaft gear.

[0041] Calculate the planetary gear rotation speed n using the following formula. s : ; Where: n s Z is the rotational speed of the planetary gear. h Z represents the number of teeth on the half-shaft gear. s n1 represents the number of teeth on the planetary gear, n2 represents the rotational speed of the left half-shaft gear, and n3 represents the rotational speed of the right half-shaft gear.

[0042] The contact pressure P between the planetary shaft and the planetary gears is calculated using the following formula. x Contact pressure P between the ball washer and the planetary gear c The contact pressure P between the flat washer and the half-shaft gear b : ; In the formula: P x P is the contact pressure between the planetary shaft and the planetary gear. c The contact pressure between the ball washer and the planetary gear, P b A represents the contact pressure between the flat washer and the half-shaft gear. x Let A be the contact area between the planetary gear shaft and the planetary gear. c A is the contact area between the ball washer and the planetary gear. b This represents the contact area between the flat washer and the half-shaft gear.

[0043] In this embodiment, calculating the friction pair bearing characteristic number of the differential based on the contact pressure data includes: determining the lubricating oil viscosity, left half-shaft gear speed, and right half-shaft gear speed of the differential; and calculating the friction pair bearing characteristic number of the differential based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed.

[0044] In one example, calculating the friction pair bearing characteristic numbers of the differential based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed includes: calculating the planetary gear rotation speed using the left half-shaft gear speed and the right half-shaft gear speed; and calculating the friction pair bearing characteristic numbers of the differential using the following formula: ; in, For the bearing characteristic numbers of the friction pair between the planetary shaft and the planetary gear, For the bearing characteristic parameters of the friction pair between the ball washer and the planetary gear, η represents the bearing characteristic number of the friction pair between the flat washer and the half-shaft gear, and η is the viscosity of the lubricating oil. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. This is the rotational speed of the planetary gear. For the contact pressure between the planetary shaft and the planetary gear, For the contact pressure between the ball washer and the planetary gear, The contact pressure between the flat washer and the half-shaft gear. This is the rotational speed of the planetary gear.

[0045] In one embodiment of this invention, calculating the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed, and the contact pressure data includes: calculating the friction torque of each friction pair and the bevel gear meshing transmission efficiency of the differential based on the friction coefficient, the contact pressure data, and the bevel gear geometric parameters of the differential; calculating the friction power of each friction pair based on the friction torque of each friction pair, the half-shaft gear speed, and the bevel gear meshing transmission efficiency; and using the friction power of each friction pair to calculate the total friction loss power of the differential.

[0046] In one example, calculating the frictional torque of each friction pair and the bevel gear meshing efficiency of the differential based on the friction coefficient, the contact pressure data, and the bevel gear geometry parameters of the differential includes: calculating the frictional torque of each friction pair and the bevel gear meshing efficiency of the differential using the following formula: ; ; ; ; in, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency. The coefficient of friction between the planetary shaft and the planetary gear. The force exerted by the planetary gear shaft on the planetary gear is d, where d is the diameter of the planetary gear shaft. Let Fc be the coefficient of friction between the ball bearing and the planetary gear, and Fc be the force exerted by the differential shell on the planetary gear. The outer diameter of the ball pad, The inner diameter of the ball pad, The coefficient of friction between the ball bearing and the planetary gear is denoted as . The force exerted by the differential housing on the half-shaft gear, The outer diameter of the flat pad, The inner diameter of the flat washer, Let K1 be the equivalent spur gear meshing transmission efficiency, K2 be the coefficient for the first process, Q1 be the coefficient for the second process, and Q2 be the coefficient for the third process. The equivalent number of teeth for a planetary gear. The equivalent number of teeth for the half-shaft gear. The equivalent total overlap, The equivalent planetary gear overlap ratio, This refers to the equivalent half-shaft gear overlap ratio. Where k is the equivalent transmission ratio, and Z is the differential coefficient. h Z represents the number of teeth on the half-shaft gear. s Where μ is the number of teeth on the planetary gear, and μ4 is the coefficient of friction between the planetary gear and the half-shaft gear. The rotational speed of the left half-shaft gear. This represents the rotational speed of the right half-shaft gear.

[0047] In one example, the frictional power of each friction pair is calculated based on the frictional torque of each friction pair, the rotational speed of the half-shaft gear, and the meshing transmission efficiency of the bevel gear, including: The frictional power of each friction pair is calculated using the following formula: ; in, The frictional power between the planetary gears and the planetary shafts. The frictional power between the planetary gear and the ball bearing pad. The frictional power between the half-shaft gear and the flat washer. The power loss due to the meshing of planetary gears and half-shaft gears, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency, Input torque to the main reduction gear, The angular velocity of the main reducer gear. The rotational angular velocity of the planetary gear. Z is the angular velocity of the half-shaft gear's rotation. h Z represents the number of teeth on the half-shaft gear. s This refers to the number of teeth on a planetary gear. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. This is the rotational speed of the planetary gear.

[0048] Optionally, calculating the total friction loss power of the differential using the friction power of each friction pair includes: calculating the total friction loss power of the differential using the following formula. : .

[0049] In one embodiment of this example, calculating the amount of cooling oil required by the differential per unit time based on the total friction loss power and lubricating oil parameters includes: calculating the amount of cooling oil q required by the differential per unit time using the following formula: ; in, Let ρ be the specific heat capacity of the lubricating oil, ρ be the density of the lubricating oil, and ΔT be the temperature difference between the lubricating oil inlet and outlet. The total power of frictional loss, the lubricating oil parameters include ρ, ΔT (user-defined parameters, constants).

[0050] In one implementation scenario, the total power loss due to friction of the differential was calculated to be 3.23kW, and the required amount of cooling lubricating oil was 2.3L / min.

[0051] This embodiment provides a method and apparatus for calculating the thermal balance of a differential, a differential, a storage medium, and electronic devices to solve the reliability problems caused by poor lubrication, the efficiency loss caused by splash lubrication, and the inability to accurately calculate the amount of cooling lubricating oil in the differential in the prior art.

[0052] Figure 3 This is an optional flowchart of the differential thermal balance calculation method in this embodiment of the invention, including: calculating the force on the parts using torque and bevel gear parameters (obtaining contact pressure data); calculating the bearing characteristic numbers of each friction pair using lubricating oil parameters and speed difference; determining the lubrication type based on the calculated bearing characteristic numbers of each friction pair to obtain the friction coefficient; calculating the friction torque using the friction coefficient and the force on the parts; obtaining the torque ratio and friction power (total power loss due to friction) based on the friction torque; and finally calculating the cooling oil quantity. A typical application scenario of this embodiment is to obtain the cooling oil quantity requirements under different operating conditions through thermal balance calculation, and to use the forced lubrication differential structure of this invention to precisely supply oil and dynamically adjust the oil quantity inside the differential. This solves the differential reliability problem caused by insufficient lubrication and avoids the increased power loss caused by excessive oil churning in traditional churning lubrication. Based on the thermal balance calculation method provided in the above embodiment, the cooling oil requirement of the differential under specific operating conditions can be calculated, providing input for the precise supply of cooling lubricating oil to the differential.

[0053] Through the above description of the embodiments, those skilled in the art can clearly understand that the methods according to the above embodiments can be implemented by means of software plus necessary general-purpose hardware platforms. Of course, they can also be implemented by hardware, but in many cases the former is a better implementation method. Based on this understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art, can be embodied in the form of a software product. This computer software product is stored in a storage medium (such as ROM / RAM, magnetic disk, optical disk) and includes several instructions to cause a terminal device (which may be a mobile phone, computer, server, or network device, etc.) to execute the methods described in the various embodiments of the present invention.

[0054] Example 2 This embodiment also provides a differential thermal balance calculation device for implementing the above embodiments and preferred embodiments; details already described will not be repeated. As used below, the term "module" can refer to a combination of software and / or hardware that performs a predetermined function. Although the device described in the following embodiments is preferably implemented in software, hardware implementation, or a combination of software and hardware, is also possible and contemplated.

[0055] Figure 4 This is a structural block diagram of a differential thermal balance calculation device according to an embodiment of the present invention, such as... Figure 4 As shown, the device includes: The first acquisition module 41 is used to acquire the geometric parameters of the planetary gears and half-shaft gears of the differential, the speed of the half-shaft gears, and the input torque. The first calculation module 42 is used to calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque; The second calculation module 43 is used to calculate the friction pair bearing characteristic number of the differential based on the contact pressure data. The second acquisition module 44 is used to acquire the friction coefficient inside the differential based on the characteristic number of the friction pair bearing; The third calculation module 45 is used to calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed and the contact pressure data; The fourth calculation module 46 is used to calculate the amount of cooling oil required by the differential per unit time based on the total power of friction loss and the lubricating oil parameters.

[0056] This embodiment also provides a differential including an end cover, a differential housing, a controller, and a planetary gear shaft, two planetary gears, and two half-shaft gears disposed within the differential housing. The controller, connected to the end cover and the differential housing, includes the thermal balance calculation device for the differential described in the previous embodiment. The end cover has gears that transmit power to the differential. An outer annular groove and a radial oil hole are formed on the end cover journal. An inner annular groove and an axial groove are formed in the inner hole. An end face groove is formed on the right end face. The radial oil hole communicates with the outer and inner annular grooves, and the inner annular groove communicates with the axial groove. An annular volume cavity is provided at the end of the axial groove of the end cover, communicating with both the axial groove and the end face groove to form a smooth oil passage. Oil can be forcibly supplied to the differential interior through the radial oil hole. The differential housing and the end cover are connected by connecting bolts. The planetary gear shaft, after mating with the differential housing, forms an oil discharge channel. Lubricating oil entering the differential interior is discharged through this channel, forming a dynamic circulation.

[0057] Figure 5 This is a schematic diagram of a differential assembly in an embodiment of the present invention. The differential includes a differential housing 10, an end cover 20, a housing 30, connecting bolts 40, a half-shaft gear 50, a planetary gear 60, a planetary gear shaft 70, a drive shaft 80, a ball washer 90, and a flat washer 100. The housing 30 includes a housing oil passage 301 and a sealing section 302. The planetary gear shaft 70 includes a channel 702, and the drive shaft 80 includes a sealing section 801. The differential housing 10 and the end cover 20 are connected by connecting bolts 40. The planetary gear shaft 70, the planetary gear 60, and the half-shaft gear 50 are disposed inside the differential housing 10. The cross-section of the planetary gear shaft 70 is a contour 701 composed of double circular arcs and straight lines, which forms a channel 702 after mating with the differential housing 10. The lubricating oil entering the differential is discharged through the channel 702, forming a dynamic circulation.

[0058] Applying the technical solution of this embodiment, lubricating oil enters from the oil hole 301 of the housing, passes through the outer annular groove 201, radial oil hole 202, inner annular groove 203, axial groove 204, annular volume cavity 205 and end face groove 206 and enters the interior of the differential to cool and lubricate the internal parts. The lubricating oil that enters the interior of the differential is discharged through the oil drain channel 702, forming a dynamic circulation.

[0059] Based on the structure of the differential in this embodiment, its lubrication method is forced lubrication, which can accurately supply and dynamically adjust the oil quantity inside the differential under any operating conditions. The differential housing has no large window, which can ensure that the lubricating oil stays inside the differential as much as possible to fully lubricate and cool the parts, thus solving the reliability problem of differentials in the prior art caused by poor lubrication under extreme operating conditions.

[0060] Optionally, the area outside the outer annular groove of the end cover journal mates with the housing to form a sealing section, which can ensure that lubricating oil enters the outer annular groove of the end cover through the oil passage of the housing.

[0061] Optionally, the outer annular groove of the end cap journal is provided with a number of radial oil holes evenly distributed around its circumference, through which lubricating oil enters the inner annular groove from the outer annular groove.

[0062] Optionally, a certain number of axial grooves are evenly formed around the inner hole of the end cap. The cross-section of the axial groove 204 can be rectangular, trapezoidal, triangular, or arc-shaped. By designing a specific cross-sectional shape for the axial groove 204, it is more conducive to oil intake.

[0063] Optionally, the portion of the end cover outside the annular groove may mate with the drive shaft to form a sealing section, ensuring that lubricating oil flows into the differential through the axial groove.

[0064] Optionally, the end cap axial groove is provided with an annular volume cavity to ensure that lubricating oil is collected in the annular volume cavity through the axial groove.

[0065] Optionally, the right end face of the end cover is provided with an end face groove that communicates with the annular volume cavity, ensuring that the lubricating oil in the annular volume cavity enters the differential through the end face groove.

[0066] Figure 6 This is a schematic diagram of the end cap structure in an embodiment of the present invention. Figure 1 , Figure 7 This is a schematic diagram of the end cap structure in an embodiment of the present invention. Figure 2 The end cover 20 includes: an outer annular groove 201, a radial oil hole 202, an inner annular groove 203, an axial groove 204, an annular volume cavity 205, an end face groove 206, and a gear 207. The end cover 20 is equipped with a gear 207, which can transmit power to the differential. The journal of the end cover 20 has an outer annular groove 201 and a radial oil hole 202, the inner hole has an inner annular groove 203 and an axial groove 204, and the right end face has an end face groove 206. The radial oil hole 202 communicates with the outer annular groove 201 and the inner annular groove 203, and the inner annular groove 203 communicates with the axial groove 204. The end of the axial groove 204 of the end cover 20 has an annular volume cavity 205, which communicates with both the axial groove 204 and the end face groove 206, forming a smooth oil passage, which can force oil to be supplied to the inside of the differential through the radial oil hole 202.

[0067] Optionally, the differential housing is a sealed housing, allowing lubricating oil to fill the interior of the differential, ensuring sufficient lubrication of the internal parts. Figure 8 This is a schematic diagram of the differential housing in an embodiment of the present invention.

[0068] Optionally, the planetary gear shaft cross-section is composed of double circular arcs and straight lines, which, after mating with the differential housing, form a circular arc channel. The lubricating oil entering the differential is discharged through the circular arc channel, forming a dynamic circulation.

[0069] Figure 9 This is a schematic diagram of the structure of the planetary gear shaft in an embodiment of the present invention. The planetary gear shaft 70 includes a profile 701 whose cross-section is composed of double circular arcs and straight lines.

[0070] It should be noted that the above modules can be implemented by software or hardware. For the latter, they can be implemented in the following ways, but are not limited to: all the above modules are located in the same processor; or, the above modules are located in different processors in any combination.

[0071] Example 3 Embodiments of the present invention also provide a storage medium storing a computer program, wherein the computer program is configured to execute the steps in any of the above method embodiments when running.

[0072] Optionally, in this embodiment, the storage medium may be configured to store a computer program for performing the following steps: S1, obtain the geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed and the input torque; S2, calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque; S3, calculate the bearing characteristic number of the friction pair of the differential based on the contact pressure data; S4, Obtain the friction coefficient inside the differential based on the characteristic number of the friction pair bearing; S5, calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed and the contact pressure data; S6, calculate the amount of cooling oil required by the differential per unit time based on the total power of friction loss and lubricating oil parameters.

[0073] Optionally, in this embodiment, the storage medium may include, but is not limited to, various media capable of storing computer programs, such as USB flash drives, read-only memory (ROM), random access memory (RAM), portable hard drives, magnetic disks, or optical disks.

[0074] Embodiments of the present invention also provide an electronic device including a memory and a processor, the memory storing a computer program and the processor being configured to run the computer program to perform the steps in any of the above method embodiments.

[0075] Optionally, the electronic device may further include a transmission device and an input / output device, wherein the transmission device is connected to the processor and the input / output device is connected to the processor.

[0076] Optionally, in this embodiment, the processor can be configured to perform the following steps via a computer program: S1, obtain the geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed and the input torque; S2, calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque; S3, calculate the bearing characteristic number of the friction pair of the differential based on the contact pressure data; S4, Obtain the friction coefficient inside the differential based on the characteristic number of the friction pair bearing; S5, calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed and the contact pressure data; S6, calculate the amount of cooling oil required by the differential per unit time based on the total power of friction loss and lubricating oil parameters.

[0077] Optionally, specific examples in this embodiment can refer to the examples described in the above embodiments and optional implementations, and will not be repeated here.

[0078] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs.

[0079] Through the above description of the embodiments, those skilled in the art can clearly understand that each embodiment can be implemented using software plus a general-purpose hardware platform, or of course, using hardware. Based on this understanding, the above technical solutions, in essence or the parts that contribute to the related technology, can be embodied in the form of a software product. This computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute the methods described in the various embodiments or some parts of the embodiments.

[0080] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0081] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A method for calculating the thermal balance of a differential, characterized in that, include: Obtain the geometric parameters of the planetary gears and axle gears of the differential, the axle gear speed, and the input torque; Calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque; Calculate the bearing characteristic parameters of the friction pair of the differential based on the contact pressure data; The friction coefficient inside the differential is obtained based on the bearing characteristic parameters of the friction pair. Calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed, and the contact pressure data; The amount of cooling oil required by the differential per unit time is calculated based on the total power of frictional loss and the lubricating oil parameters.

2. The method according to claim 1, characterized in that, The total frictional loss power of the differential is calculated based on the friction coefficient, the half-shaft gear speed, and the contact pressure data, including: The friction torque of each friction pair and the meshing transmission efficiency of the bevel gear in the differential are calculated based on the friction coefficient, the contact pressure data, and the geometric parameters of the bevel gear in the differential. The frictional power of each friction pair is calculated based on the frictional torque of each friction pair, the rotational speed of the half-shaft gear, and the meshing transmission efficiency of the bevel gear. The total friction loss power of the differential is calculated using the friction power of each friction pair.

3. The method according to claim 2, characterized in that, The frictional torques of each friction pair and the bevel gear meshing transmission efficiency of the differential are calculated based on the friction coefficient, the contact pressure data, and the geometric parameters of the bevel gears of the differential, including: The frictional torques of each friction pair in the differential and the meshing transmission efficiency of the bevel gears are calculated using the following formulas: ； ； ； ； in, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency. The coefficient of friction between the planetary shaft and the planetary gear. The force exerted by the planetary gear shaft on the planetary gear is d, where d is the diameter of the planetary gear shaft. Let Fc be the coefficient of friction between the ball bearing and the planetary gear, and Fc be the force exerted by the differential shell on the planetary gear. The outer diameter of the ball pad, The inner diameter of the ball pad, The coefficient of friction between the ball bearing and the planetary gear is denoted as . The force exerted by the differential housing on the half-shaft gear, The outer diameter of the flat pad, The inner diameter of the flat washer, Let K1 be the equivalent spur gear meshing transmission efficiency, K2 be the coefficient for the first process, Q1 be the coefficient for the second process, and Q2 be the coefficient for the third process. The equivalent number of teeth for a planetary gear. The equivalent number of teeth for the half-shaft gear. The equivalent total overlap, The equivalent planetary gear overlap ratio, This refers to the equivalent half-shaft gear overlap ratio. Where k is the equivalent transmission ratio, and Z is the differential coefficient. h Z represents the number of teeth on the half-shaft gear. s Where μ is the number of teeth on the planetary gear, and μ4 is the coefficient of friction between the planetary gear and the half-shaft gear. The rotational speed of the left half-shaft gear. This represents the rotational speed of the right half-shaft gear.

4. The method according to claim 2, characterized in that, The frictional power of each friction pair is calculated based on the frictional torque of each friction pair, the rotational speed of the half-shaft gear, and the meshing transmission efficiency of the bevel gear, including: The frictional power of each friction pair is calculated using the following formula: ； in, The frictional power between the planetary gears and the planetary shafts. The frictional power between the planetary gear and the ball bearing pad. The frictional power between the half-shaft gear and the flat washer. The power loss due to the meshing of planetary gears and half-shaft gears, This refers to the frictional torque between the planetary shaft and the planetary gears. The frictional torque between the planetary gear and the ball bearing is... The frictional torque between the half-shaft gear and the flat pad. For bevel gear meshing transmission efficiency, Input torque to the main reduction gear, The angular velocity of the main reducer gear. The rotational angular velocity of the planetary gear. Z is the angular velocity of the half-shaft gear's rotation. h Z represents the number of teeth on the half-shaft gear. s This refers to the number of teeth on a planetary gear. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. This is the rotational speed of the planetary gear.

5. The method according to claim 1, characterized in that, The amount of cooling oil required by the differential per unit time is calculated based on the total power loss due to friction and the lubricating oil parameters, including: The amount of cooling oil q required by the differential per unit time is calculated using the following formula: ； in, Let ρ be the specific heat capacity of the lubricating oil, ρ be the density of the lubricating oil, and ΔT be the temperature difference between the lubricating oil inlet and outlet. The total power of frictional loss, the lubricating oil parameters include , ρ, △T.

6. The method according to claim 1, characterized in that, The contact pressure data between the planetary gear and the half-shaft gear calculated based on the geometric parameters and the input torque includes: The directional force data is calculated based on the input torque and the geometric parameters, wherein the directional force data includes the tangential force of the half-shaft gear, the axial force of the half-shaft gear, and the axial force of the half-shaft gear. The force data is calculated based on the directional force data, wherein the force data includes the force exerted by the planetary shaft on the planetary gear, the force exerted by the differential housing on the planetary gear, and the force exerted by the differential housing on the half-shaft gear; The contact pressure data between the planetary gear and the half-shaft gear is calculated using the force data, wherein the contact pressure data includes the contact pressure between the planetary shaft and the planetary gear, the contact pressure between the ball washer and the planetary gear, and the contact pressure between the flat washer and the half-shaft gear.

7. The method according to claim 1, characterized in that, The calculation of the bearing characteristic parameters of the differential's friction pair based on the contact pressure data includes: Determine the lubricating oil viscosity, left half-shaft gear speed, and right half-shaft gear speed of the differential; The bearing characteristic parameters of the differential's friction pair are calculated based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed.

8. The method according to claim 7, characterized in that, The friction pair bearing characteristic parameters of the differential are calculated based on the contact pressure data, the lubricating oil viscosity, the left half-shaft gear speed, and the right half-shaft gear speed, including: The rotational speed of the planetary gear is calculated using the rotational speed of the left half-shaft gear and the rotational speed of the right half-shaft gear; The characteristic parameters of the friction pair bearings of the differential are calculated using the following formula: ； in, For the bearing characteristic numbers of the friction pair between the planetary shaft and the planetary gear, For the bearing characteristic parameters of the friction pair between the ball washer and the planetary gear, η represents the bearing characteristic number of the friction pair between the flat washer and the half-shaft gear, and η is the viscosity of the lubricating oil. The rotational speed of the left half-shaft gear. The rotational speed of the right half-shaft gear. For the contact pressure between the planetary shaft and the planetary gear, For the contact pressure between the ball washer and the planetary gear, The contact pressure between the flat washer and the half-shaft gear. This is the rotational speed of the planetary gear.

9. A thermal balance calculation device for a differential, characterized in that, include: The first acquisition module is used to acquire the geometric parameters of the planetary gears and half-shaft gears of the differential, the half-shaft gear speed and the input torque; The first calculation module is used to calculate the contact pressure data between the planetary gear and the half-shaft gear based on the geometric parameters and the input torque. The second calculation module is used to calculate the bearing characteristic numbers of the friction pair of the differential based on the contact pressure data. The second acquisition module is used to acquire the friction coefficient inside the differential based on the characteristic number of the friction pair bearing; The third calculation module is used to calculate the total friction loss power of the differential based on the friction coefficient, the half-shaft gear speed and the contact pressure data; The fourth calculation module is used to calculate the amount of cooling oil required by the differential per unit time based on the total power of friction loss and the lubricating oil parameters.

10. A differential, characterized in that, This includes end caps, a differential housing, a controller, and a planetary gear shaft, two planetary gears, and two half-shaft gears housed within the differential housing. The controller, connected to the end cover and the differential housing, includes the thermal balance calculation device for the differential as described in claim 9: The end cover is equipped with gears to transmit power to the differential. The end cover journal has an outer annular groove and a radial oil hole, the inner hole has an inner annular groove and an axial groove, and the right end face has an end face groove. The radial oil hole communicates with the outer and inner annular grooves, and the inner annular groove communicates with the axial groove. An annular volume cavity is located at the end of the axial groove of the end cover, communicating with both the axial groove and the end face groove, forming a smooth oil passage. Oil can be forcibly supplied to the differential through the radial oil hole. The differential housing is connected to the end cover by connecting bolts. The planetary gear shaft, after mating with the differential housing, forms an oil drain channel. Lubricating oil entering the differential is discharged through this channel, forming a dynamic circulation.

11. The differential according to claim 10, characterized in that, The area outside the outer annular groove of the end cover journal mates with the housing to form a sealed section, which ensures that lubricating oil enters the outer annular groove of the end cover through the oil passage of the housing.

12. The differential according to claim 10, characterized in that, The outer annular groove of the end cap journal is uniformly provided with a number of radial oil holes, through which lubricating oil enters the inner annular groove from the outer annular groove.

13. The differential according to claim 10, characterized in that, The end cap has a certain number of axial grooves evenly distributed around its inner hole.

14. The differential according to claim 10, characterized in that, The portion of the end cover outside the annular groove mates with the drive shaft to form a sealed section, ensuring that lubricating oil flows into the differential through the axial groove.

15. The differential according to claim 10, characterized in that, The end cap has an annular volume cavity at the end of the axial groove, which ensures that the lubricating oil is collected in the annular volume cavity through the axial groove.

16. The differential according to claim 10, characterized in that, The right end face of the end cover has an end face groove that communicates with the annular volume cavity, ensuring that the lubricating oil in the annular volume cavity enters the differential through the end face groove.

17. The differential according to claim 10, characterized in that, The differential housing is a sealed housing, and the lubricating oil can fill the interior of the differential, ensuring that the lubricating oil fully lubricates the internal parts of the differential.

18. The differential according to claim 10, characterized in that, The planetary gear shaft has a cross-sectional profile consisting of double circular arcs and straight lines. When it mates with the differential housing, it forms a circular arc channel. The lubricating oil that enters the differential is discharged through the circular arc channel, forming a dynamic circulation.

19. A storage medium, characterized in that, The storage medium stores a computer program, wherein the computer program is configured to execute the method described in any one of claims 1 to 9 when it is run.

20. An electronic device comprising a memory and a processor, characterized in that, The memory stores a computer program, and the processor is configured to run the computer program to perform the method as described in any one of claims 1 to 9.

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