Anti-sintering openable oil guide structure for differentials, differentials and automobiles

Abstract

This invention belongs to the field of new energy vehicle technology and solves the problem of sintering between planetary gears and planetary shafts in existing differentials. It provides an anti-sintering, openable oil-guiding structure for differentials, a differential itself, and a vehicle. The anti-sintering, openable oil-guiding structure includes a differential housing with a hollow cavity; a half-shaft bevel gear disposed within the hollow cavity; a planetary shaft disposed within the differential housing; and planetary gears fitted onto the planetary shaft and meshing with the half-shaft bevel gear. Planetary oil-guiding grooves are provided on the inner bore of the planetary gears, located between the planetary gears and the planetary shaft. These grooves guide lubricating oil through the surface of the planetary shaft and between the planetary gears, directing the lubricating oil to the outside of the differential housing or to the inside of the differential. This invention prevents sintering by creating planetary oil-guiding grooves on the planetary gears, and its structure is simple and practical.

Description

[0001] This application is a divisional application of the invention patent application filed on September 29, 2021, entitled "Anti-sintering oil guiding structure for differential, differential and automobile", with application number 202111151896X. Technical Field

[0002] This invention belongs to the field of new energy vehicle technology, specifically relating to an anti-sintering openable oil guide structure for a differential, a differential, and a vehicle. Background Technology

[0003] In the new energy vehicle industry, differentials are typically installed to ensure vehicle stability when turning or driving on icy or snowy roads. However, the differentials currently used in new energy vehicles are mostly simple planetary systems. While this structure can effectively achieve differential speed between the left and right tires, under extreme conditions, excessively high differential speeds can cause a rapid increase in heat inside the differential, leading to sintering between the planetary gears and planetary shafts, resulting in loss of differential function. In severe cases, this can even cause vehicle rollovers or other safety accidents. Summary of the Invention

[0004] In view of this, the present invention provides an anti-sintering openable oil guide structure for differentials, a differential, and an automobile, to solve the problem of sintering between planetary gears and planetary shafts in the differential under some extreme operating conditions in the prior art.

[0005] The technical solution adopted in this invention is:

[0006] In a first aspect, the present invention provides an anti-sintering, openable oil guiding structure for a differential, comprising:

[0007] Differential housing with a hollow cavity;

[0008] A half-shaft bevel gear, wherein the half-shaft bevel gear is disposed within the hollow cavity;

[0009] A planetary shaft, which is disposed within the differential housing;

[0010] A planetary gear, which is sleeved on the planetary shaft and meshes with the half-shaft bevel gear;

[0011] The planetary gear has a planetary oil guide groove on its inner hole. The planetary oil guide groove is located between the planetary gear and the planetary shaft. The planetary oil guide groove is used to guide the lubricating oil to flow between the planetary shaft surface and the planetary gear, and to guide the lubricating oil to the outside of the differential housing or to the inside of the differential.

[0012] The hollow cavity is provided with a lubrication ring wall, which is used to carry the lubricating oil splashed out by the rotation of the planetary gear and the half-shaft bevel gear.

[0013] The planetary oil guide groove is provided with a number of planetary oil holes that store lubricating oil. The oil outlet end of the planetary oil hole has two states: open and closed. The planetary shaft is provided with an oil guide shaft groove. The oil guide shaft groove is provided with a number of shaft groove oil holes that store lubricating oil. The oil outlet end of the shaft groove oil hole also has two states: open and closed.

[0014] Preferably, a mounting platform coaxial with the half-shaft mounting through hole is provided on the outside of the differential housing, and several flanges are provided on the mounting platform for connecting with other external equipment.

[0015] Preferably, there are six flanges, with three flanges forming a group. Each group of flanges has connecting ribs between adjacent flanges to reinforce the mounting platform and enhance the stability and strength of the flanges.

[0016] Preferably, the differential housing is provided with a plurality of reinforcing ribs arranged circumferentially along the mounting through holes of the half shaft, and the reinforcing ribs are arranged on the mounting platform and located on the side away from the flange.

[0017] Preferably, a planetary bushing is fitted on the inner hole of the planetary gear. The planetary bushing has a bushing through hole at its center, which mates with the planetary shaft. The planetary bushing is then fitted onto the planetary shaft, and the planetary shaft and the planetary bushing can rotate relative to each other.

[0018] Preferably, a bushing oil groove is provided on the inner wall of the bushing through hole of the planetary bushing. The bushing oil groove is spiral in shape and extends from one end of the bushing through hole to the other end.

[0019] Preferably, the length of the bushing through hole is equal to the length of the planetary gear inner hole, or the length of the bushing through hole is greater than the length of the planetary gear inner hole.

[0020] Preferably, the vertical distance between the middle portion of the inner hole of the planetary gear and the central axis of the inner hole is less than the vertical distance between the two ends of the inner hole of the planetary gear and the central axis of the inner hole.

[0021] Secondly, the present invention provides a differential, the differential including any of the above-mentioned anti-sintering openable oil guiding structures for differentials.

[0022] Thirdly, the present invention provides an automobile, the automobile comprising any of the above-described anti-sintering openable oil guide structures for differentials or comprising the above-described differentials.

[0023] In summary, the beneficial effects of the present invention are as follows:

[0024] The differential anti-sintering openable oil guiding structure, differential and automobile provided by the present invention have planetary oil guiding grooves opened in the inner hole of the planetary gear. The planetary oil guiding grooves are located between the planetary shaft surface and the planetary gear. Lubricating oil can be guided to the planetary shaft surface and the planetary gear through the planetary oil guiding grooves. The lubricating oil flows in the planetary oil guiding grooves and passes through the planetary shaft surface to form a lubricating oil film, which plays a lubricating role between the planetary gear and the planetary shaft. In addition, the lubricating oil guided to the planetary gear and the planetary shaft by the planetary oil guiding grooves can also carry away the heat generated between the planetary gear and the planetary shaft, so as to prevent sintering between the planetary shaft and the planetary gear. Attached Figure Description

[0025] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the embodiments of the present invention will be briefly introduced below. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort, and these are all within the protection scope of the present invention.

[0026] Figure 1 This is a three-dimensional structural diagram of the anti-sintering openable oil guide structure for the differential in Embodiment 1 of the present invention;

[0027] Figure 2 for Figure 1 Exploded view;

[0028] Figure 3 This is a cross-sectional view of the differential housing in Embodiment 1 of the present invention;

[0029] Figure 4 This is a schematic diagram of the planetary gear structure in Embodiment 1 of the present invention;

[0030] Figure 5 This is a schematic diagram of the structure of the planetary shaft sleeve being fitted onto the planetary shaft in Embodiment 2 of the present invention;

[0031] Figure 6 This is a cross-sectional view of the planetary bushing in Embodiment 2 of the present invention;

[0032] Figure 7 This is a three-dimensional structural diagram of the transmission flange of Embodiment 6 of the present invention;

[0033] Figure 8 This is a three-dimensional structural diagram of the transmission flange of Embodiment 6 of the present invention from another perspective;

[0034] Figure 9 This is a three-dimensional view of the structure of the transmission flange for connecting with the transmission shaft in Embodiment 6 of the present invention;

[0035] Figure 10 This is a side view of the transmission flange of Embodiment 6 of the present invention;

[0036] Figure 11 This is a front view of the transmission flange of Embodiment 6 of the present invention;

[0037] Figure 12 This is a schematic diagram of the three sets of sub-transmission structures disconnected in Embodiment 6 of the present invention;

[0038] Figure 13 This is a schematic diagram of the two sets of sub-transmission structures of the transmission flange in Embodiment 6 of the present invention, which are staggered in the circumferential direction.

[0039] Figure 14 This is a three-dimensional structural diagram of the four-speed shifting device of the transmission of the present invention;

[0040] Figure 15 This is a diagram showing the angular positional relationship between the shifting zone of the shift drum of the present invention and the first and second drive mechanisms;

[0041] Figure 16 This is a three-dimensional structural diagram of the shift drum of the present invention;

[0042] Figure 17 This is a three-dimensional structural diagram of the first drive mechanism of the present invention in conjunction with the shift drum;

[0043] Figure 18 This is a three-dimensional structural diagram of the first drive mechanism of the present invention in conjunction with the shift drum;

[0044] Figure 19 This is a three-dimensional structural diagram of the first drive mechanism and the first synchronizer of the present invention.

[0045] Figure 20 This is a top view of the structure of the present invention that allows the rotating belt to rotate with the synchronizer;

[0046] Figure 21 This is a side view of the structure of the present invention that allows the rotating belt to rotate with the synchronizer;

[0047] Figure 22 This is a diagram showing the positional relationship of the four rotating components of the present invention;

[0048] Figure 23 This is a structural diagram of the vehicle.

[0049] Parts and their numbers in the diagram:

[0050] 10. Differential housing; 11. Half-shaft mounting through hole; 111. Half-shaft oil guide groove; 12. Lubrication ring wall; 13. Gasket groove; 14. Oil collection groove; 15. Mounting platform; 151. Flange; 20. Half-shaft bevel gear; 30. Planetary gear; 31. Planetary oil guide groove; 40. Planetary shaft; 50. Planetary bushing; 51. Bushing oil groove;

[0051] 410. Flange body; 411. First connecting part; 412. Second connecting part; 4121. Limiting hole; 4122. Stop; 420. First transmission structure; 430. First connecting structure; 440. Second transmission structure; 441. First sub-transmission structure group; 442. Second sub-transmission structure group; 443. Third sub-transmission structure group; 444. Fourth sub-transmission structure group; 445. Fifth sub-transmission structure group;

[0052] 1. Shift drum; 110. Guide groove; 112. Shift area; 113. First guide section; 114. Second guide section; 115. Third guide section; 120. First angle position; 130. Second angle position;

[0053] 21. Limiting groove; 3. First drive mechanism; 310. First sliding member; 32. First shift fork; 33. First connecting member; 321. First rotating member; 322. Second rotating member; 323. Third rotating member; 324. Fourth rotating member; 325. Actuating member; 326. Rotating belt; 5. Second drive mechanism; 510. Second sliding member; 52. Second shift fork; 53. Second connecting member; 6. Motor; 7. Rotating shaft;

[0054] 600. Powertrain; 700. Transmission; 800. Body. Detailed Implementation

[0055] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. In the description of the present invention, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate orientations or positional relationships based on the orientations or positional relationships 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 referred device or element must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, the element defined by the phrase "comprising..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element. Where there is no conflict, embodiments of the present invention and the various features thereof can be combined with each other, all of which are within the scope of protection of the present invention.

[0056] Please see Figure 23 A vehicle is a common means of transportation, mainly composed of a power system 600, a transmission system 700, a body 800, and a chassis. The transmission system 700 includes a gearbox, driveshaft, and differential. When the vehicle is in motion, the power from the power system 600 is transmitted to the gearbox. The gearbox converts the power from the power system 600 and outputs power with appropriate torque and speed. This converted power is then transmitted to the driveshaft, which in turn transmits power to the differential. The differential then distributes the power to the wheels on both sides. The converted power can also be transmitted to the differential. For parking and shifting, the gearbox is equipped with shifting and parking mechanisms. A lubrication system is also provided for the gearbox, differential, and other components.

[0057] Example 1

[0058] Please see Figures 1 to 4Embodiment 1 of this invention discloses an anti-sintering, openable oil-guiding structure for a differential, comprising: a differential housing 10, a half-shaft bevel gear 20, a planetary gear 30, and a planetary shaft 40. A hollow cavity is formed within the differential housing 10, wherein the half-shaft bevel gear 20, the planetary gear 30, and the planetary shaft 40 are all disposed within the hollow cavity. The central axis of the half-shaft bevel gear 20 is perpendicular to the central axis of the planetary gear 30, and the half-shaft bevel gear 20 meshes with the planetary gear 30, which is a bevel gear. Two half-shaft bevel gears 20 and two planetary gears 30 are provided, coaxially arranged. The two planetary gears 30 are respectively sleeved on both ends of the planetary shaft 40, and the planetary gears 30 are rotatably connected to the planetary shaft 40.

[0059] Since the structure of the half-shaft bevel gear 20 and the planetary shaft 40 is well known to those skilled in the art, it will not be described in detail here.

[0060] To facilitate understanding of the structure of the anti-sintering openable oil guide structure for the differential, the differential housing 10 and the planetary gear 30 are described below:

[0061] Differential housing 10: Both ends of the differential housing 10 are provided with half-shaft mounting through holes 11. The inner wall of each half-shaft mounting through hole 11 has a half-shaft oil guide groove 111 for guiding oil. The half-shaft oil guide groove 111 is spiral in shape and extends along the axial direction of the half-shaft mounting through hole 11. When lubricating oil needs to flow into or out of the half-shaft mounting through hole 11, it will flow along the path of the half-shaft oil guide groove 111 as the differential housing 10 rotates. The spiral shape of the half-shaft oil guide groove 111 facilitates the flow of lubricating oil, especially at higher speeds. This allows the lubricating oil to flow along the spiral direction of the half-shaft oil guide groove 111 with the rotation, avoiding the problem of lubricating oil sticking to the groove wall and failing to fall due to excessive centrifugal force at high speeds. Two lubrication ring walls 12 are provided in the hollow cavity of the differential housing 10, located at both ends of the hollow cavity and coaxially arranged with the half-shaft mounting through holes 11 at both ends of the differential housing 10. The lubrication ring walls 12 are used to receive the lubricating oil splashed from the rotation of the planetary gear 30 and the half-shaft bevel gear 20, and guide the lubricating oil from the lubrication ring wall 12 at one end of the hollow cavity to the lubrication ring wall 12 at the other end of the hollow cavity, so that the lubricating oil covers the entire inner wall of the hollow cavity as much as possible.

[0062] A gasket groove 13 is also provided in the hollow cavity of the differential housing 10. The gasket groove 13 is annular and coaxially arranged with the half-shaft mounting through hole 11. The gasket groove 13 is located between the lubrication ring wall 12 and the half-shaft mounting through hole 11, and the radius of the gasket groove 13 is larger than the radius of the half-shaft mounting through hole 11 but smaller than the radius of the lubrication ring wall 12. When lubricating oil passes through the half-shaft oil guide groove 111 in the half-shaft mounting through hole 11 at one end, the lubricating oil will flow along the half-shaft oil guide groove 111 into the gasket groove 13 that communicates with it, while the lubricating oil in the gasket groove 13 at the other end will flow out of the differential housing 10 along the half-shaft oil guide groove 111. Half-shaft washers are provided on the gasket grooves 13 at both ends of the hollow cavity to protect the half-shaft bevel gear 20 and prevent excessive wear between it and the inner wall of the differential housing 10. After the lubricating oil flows into the gasket groove 13 through the half-shaft oil guide groove 111, the lubricating oil fills the gasket groove 13 and flows through the gap between the half-shaft gasket and the half-shaft bevel gear 20, so that the half-shaft gasket and the half-shaft bevel gear 20 are fully lubricated. The heat generated by the friction between the half-shaft bevel gear 20 and the half-shaft gasket is carried away, achieving a cooling effect. When the lubricating oil flows to the gasket groove 13 at the other end of the hollow cavity, the lubricating oil also enters between the half-shaft gasket and the half-shaft bevel gear 20 through the gap. With the rotation of the half-shaft bevel gear 20, the lubricating oil fully covers the half-shaft gasket and the half-shaft bevel gear 20, achieving sufficient lubrication, reducing friction, and at the same time, the lubricating oil also carries away the heat generated by friction.

[0063] An oil collection groove 14 is also provided in the hollow cavity of the differential housing 10. The oil collection groove 14 is formed on the lubrication ring wall 12 and communicates with the gasket groove 13. The contact point between the oil collection groove 14 and the lubrication ring wall 12 is chamfered to facilitate the flow of lubricating oil from the lubrication ring wall 12 into the oil collection groove 14. The contact point between the oil collection groove 14 and the gasket groove 13 is also chamfered to facilitate the flow of lubricating oil from the gasket groove 13 into the oil collection groove 14. There are four oil collection grooves 14, two of which are located on one of the lubrication ring walls 12 and the other two are located on the other lubrication ring wall 12. The two oil collection grooves 14 on the same lubrication ring wall 12 are centrally symmetrically arranged so that the lubricating oil can flow into the oil collection groove 14 more evenly.

[0064] On the outside of the differential housing 10, there is a mounting platform 15 coaxial with the half-shaft mounting through-hole 11. Several flanges 151 are provided on the mounting platform 15 for connecting to other external equipment. There are six flanges 151, arranged in groups of three. Between adjacent flanges 151 in each group, connecting ribs are provided to enhance the stability and strength of the mounting platform 15 and the flanges 151. The side of the connecting ribs facing away from the hollow cavity has a certain curvature to better match with external equipment and to guide the installation. Several reinforcing ribs are also provided on the outside of the differential housing 10, located on the side facing away from the flanges 151. These reinforcing ribs are arranged circumferentially coaxially with the half-shaft mounting through-hole 11 to increase the overall strength of the differential and distribute the force to multiple points on the differential housing 10.

[0065] Planetary gear 30: Preferably, the planetary gear 30 is a bevel gear, which is sleeved on the planetary shaft 40 and rotatably connected to the planetary shaft 40 to achieve differential speed adjustment of the wheels. A spiral planetary oil guide groove 31 is formed on the inner wall of the planetary gear 30. The spiral planetary oil guide groove 31 allows lubricating oil to flow along the groove and repeatedly pass through the mating surface between the planetary gear 30 and the planetary shaft 40, continuously carrying away the heat generated by the rotational friction between the planetary shaft 40 and the planetary gear 30, achieving cooling and preventing sintering. Simultaneously, as the lubricating oil repeatedly passes through the mating surface, an oil film is formed on the mating surface, reducing the friction between the planetary shaft 40 and the planetary gear 30 and slowing down the wear rate. When the planetary gear 30 rotates in the first direction, the planetary oil guide groove 31 guides the lubricating oil adhering to the planetary shaft 40 from the hollow cavity to the outside of the differential housing 10. When the planetary gear 30 rotates in the second direction, the planetary oil guide groove 31 guides the lubricating oil from the outside of the differential housing 10 or from both ends of the planetary shaft 40 to the middle of the planetary shaft 40. This demonstrates that the spiral shape allows the lubricating oil to be guided in a regular manner according to the rotation direction of the planetary gear 30, and to fully cover the mating surfaces between the planetary gear 30 and the planetary shaft 40. The first direction refers to the axial direction from the center of the hollow cavity along the planetary shaft 40 towards the outside of the differential housing 10, where the spiral direction of the planetary oil guide groove 31 is consistent with the rotation direction of the planetary gear 30. The second direction refers to the axial direction from the center of the hollow cavity along the planetary shaft 40 towards the outside of the differential housing 10, where the spiral direction of the planetary oil guide groove 31 is opposite to the rotation direction of the planetary gear 30.

[0066] Working principle of Embodiment 1 of the present invention:

[0067] When the vehicle is in motion, the differential rotates with the wheels, guiding some of the lubricating oil located inside the vehicle to the differential's interior. When the oil enters the differential housing 10 through the half-shaft mounting hole 11, it first flows through the half-shaft oil guide groove 111 into the gasket groove 13. As the differential rotates, the lubricating oil fills the entire gasket groove 13. Some lubricating oil flows into the gap between the gasket and the half-shaft bevel gear 20, lubricating and cooling the mating surfaces of the gasket and the half-shaft bevel gear 20. As the lubricating oil continues to flow, some flows to the lubrication ring wall 12, and another part flows to the oil collection groove 14. Lubricating oil splashed out by the rotation of the half-shaft bevel gear 20 also splashes onto the inner wall of the hollow cavity and then flows into the lubrication ring wall 12. The planetary gear 30 meshes with the half-shaft bevel gear 20, carrying away some lubricating oil while also receiving lubrication through the lubrication ring wall 12. Some lubricating oil remains on the planetary shaft 40, where it is further lubricated by the rotation of the planetary gear 30 and the spiral... The spiral-shaped planetary oil guide groove 31 guides the lubricating oil adhering to the planetary shaft 40 to the mating surface of the planetary shaft 40 and the planetary gear 30. As the planetary gear 30 rotates, the oil is discharged from the inside of the differential housing 10 (or introduced from the outside of the differential) along the spiral-shaped planetary oil guide groove 31. During this process, the flowing lubricating oil forms an oil film between the planetary gear 30 and the planetary shaft 40, increasing lubrication and preventing abnormal wear between the planetary shaft 40 and the planetary gear 30. The flowing lubricating oil also carries away the heat generated by friction, preventing sintering. The lubricating oil from one end of the lubrication ring wall 12 to the other end of the lubrication ring wall 12 will continue to flow into the oil collection groove 14 at the other end. The lubricating oil then flows from the oil collection groove 14 to the space between the half-shaft bevel gear 20 and the gasket for lubrication. Subsequently, the lubricating oil is discharged through the spiral-shaped oil guide groove on the half-shaft mounting through hole 11.

[0068] Example 2

[0069] Please see Figure 5 and Figure 6 The anti-sintering openable oil guide structure for differential in Embodiment 2 of the present invention is an improvement on Embodiment 1.

[0070] Specifically, a planetary bushing 50 is fitted onto the inner bore of the planetary gear 30. The planetary bushing 50 is fixedly fitted onto the inner bore of the planetary gear 30, preferably using a detachable fixing method such as bolts and nuts. The planetary bushing 50 has a central through-hole that mates with the planetary shaft 40, allowing the planetary bushing 50 to be fitted onto the planetary shaft 40 and enabling relative rotation between them. An oil groove 51, spirally shaped, is provided on the inner wall of the through-hole of the planetary bushing 50, extending from one end to the other. The length of the through-hole is equal to or greater than the length of the inner bore of the planetary gear 30, ensuring that the lubricating oil completely covers the entire length of the planetary shaft 40 containing the planetary gear 30, preventing direct contact between the planetary shaft 40 and the planetary gear 30, which could lead to wear and damage. When lubricating oil flows into the planetary bushing 50, the planetary bushing 50 rotates with the planetary gear 30, and the lubricating oil moves along the spiral bushing oil groove 51. A layer of oil film is formed where the lubricating oil passes, adhering to the surface of the planetary shaft 40, lubricating the planetary shaft 40, reducing friction, and carrying away the heat generated between the planetary shaft 40 and the planetary bushing 50 to prevent sintering.

[0071] When there is no lubricating oil in the differential housing 10 or between the planetary bushing 50 and the planetary shaft 40, the planetary bushing 50 can still provide protection. The planetary shaft 40 will rub against the planetary bushing 50. Under extreme conditions of excessively high differential speeds, this can cause a rapid increase in heat between the planetary shaft 40 and the planetary bushing 50, leading to sintering. However, because the sintering occurs between the planetary bushing 50 and the planetary shaft 40, the planetary gear 30 will not be damaged. During vehicle maintenance, only the planetary bushing 50 needs to be replaced; there is no need to replace the entire planetary gear 30, the planetary shaft 40, or even the entire differential. Furthermore, as mentioned above, the planetary bushing 50 and the planetary gear 30 are detachably connected, which facilitates future replacement in case of damage. Compared to directly lubricating the planetary gear 30 and the planetary shaft 40, this embodiment provides an extra layer of protection, effectively preventing unexpected situations where lubricating oil is unavailable and saving on maintenance costs.

[0072] The remaining structure and working principle of Example 2 are the same as those of Example 1.

[0073] Example 3

[0074] The anti-sintering openable oil guide structure for differential in Embodiment 3 of the present invention is an improvement on Embodiment 1.

[0075] Specifically, the planetary oil guide groove 31 is provided with several planetary oil holes for storing spare lubricating oil. The planetary oil holes are arranged sequentially along the spiral direction of the planetary oil guide groove 31, and spare lubricating oil is injected into each of the planetary oil holes. When the planetary gear 30 rotates at high speed, due to centrifugal force and the continuous flow of lubricating oil in the planetary oil guide groove 31, the lubricating oil will block the planetary oil holes, so the lubricating oil in some planetary oil holes will continue to remain in the oil holes. However, when there is no continuous flow of lubricating oil between the planetary gear 30 and the planetary shaft 40, or even when there is no lubricating oil at all, a large frictional force will be generated between the planetary gear 30 and the planetary shaft 40, and the temperature will rise sharply. At this time, the lubricating oil stored in the oil holes will flow into the planetary oil guide groove 31 due to the lack of continuous lubricating oil blocking and the reduction of centrifugal force caused by the vehicle differential. The lubricating oil in the oil holes will play a lubricating role between the planetary shaft 40 and the planetary gear 30. At the same time, through the rotation of the planetary gear 30, the lubricating oil flows with the spiral planetary oil guide groove 31, repeatedly passing through the mating surface of the planetary shaft 40 and the planetary gear 30, carrying away heat, achieving the effect of cooling and preventing sintering. Compared to Embodiment 1, this provides further protection, preventing sintering between the planetary shaft 40 and the planetary gear 30 due to lack of lubrication in the differential housing 10. Compared to Embodiment 2, this not only protects the planetary gear 30 but also the planetary shaft 40, while allowing normal operation to continue and preventing vehicle rollover. Furthermore, it requires no additional components, resulting in a simple structure and low cost.

[0076] The remaining structure and working principle of Example 3 are the same as those of Example 1.

[0077] Example 4

[0078] The anti-sintering openable oil guide structure for differential in Embodiment 4 of the present invention is an improvement on Embodiment 3.

[0079] Specifically, a spiral-shaped oil guide groove is formed on the planetary shaft 40 along its axial direction. Several oil groove holes for storing spare lubricating oil are provided within the oil guide groove, arranged sequentially along the spiral direction of the groove. Spare lubricating oil is injected into each of these holes. Several planetary oil holes pre-filled with lubricating oil are also formed on the surface of the planetary shaft 40. These planetary oil holes are arranged in a spiral pattern, consistent with the spiral shape of the planetary oil guide groove 31, facilitating the smooth flow of lubricating oil from the planetary oil holes directly into the oil guide groove for lubrication. Under normal operating conditions and at normal temperatures, the oil outlet of each groove oil hole and each planetary oil hole is closed, preventing pre-lubricated lubricating oil from flowing into the groove oil holes or planetary oil holes, thus avoiding mixing of new and old oil and affecting the lubrication and cooling effect. Simultaneously, the closed-state setting prevents oil from flowing out of the planetary oil holes and shaft groove oil holes when there is sufficient lubricating oil between the planetary gear 30 and the planetary shaft 40. This would prevent a continuous flow of lubricating oil into the differential housing 10, resulting in a lack of lubricating oil in the planetary oil holes and shaft groove oil holes. Because the planetary gear 30 and planetary shaft 40 need to withstand large torques and high strength, ductile iron is preferred. The closed ends of the planetary oil holes and shaft groove oil holes are subject to thermal expansion and contraction, causing them to open and close. Small pits are provided on the inner walls of the planetary oil holes and shaft groove oil holes to enhance the adhesion of lubricating oil within them and prevent lubricating oil from flowing out.

[0080] When the differential housing 10 is normally supplied with lubricating oil, and there is a continuous flow of lubricating oil between the planetary shaft 40 and the planetary gear 30, the differential works normally. The heat is continuously carried away by the lubricating oil, and an oil film is continuously formed between the planetary shaft 40 and the planetary gear 30 to reduce friction. The oil outlets of the planetary oil holes and the shaft groove oil holes are all in a closed state. When there is not enough lubricating oil in the differential housing 10, or when there is no continuous flow of lubricating oil between the planetary shaft 40 and the planetary gear 30, under some extreme working conditions, such as driving on icy roads or continuous turning and sharp turns, the differential speed is too high, the friction between the planetary gear 30 and the planetary shaft 40 increases, and the overall temperature inside the differential housing 10 rises sharply, especially the heat between the planetary gear 30 and the planetary shaft 40 increases sharply. At this point, due to the rapid increase in heat and the sudden rise in temperature, the oil outlets of the shaft groove oil holes and planetary oil holes, due to thermal expansion and contraction, change from a closed state to an open state. Since there is no lubricating oil in the guide shaft groove, the flow of lubricating oil in the planetary oil holes and shaft groove oil holes is not obstructed. The lubricating oil in the shaft groove oil holes and planetary oil holes flows into the guide shaft groove by gravity or centrifugal force, lubricating the planetary shaft 40 and planetary gear 30, forming an oil film between them, reducing friction, and carrying away heat through the lubricating oil in the guide shaft groove, thus preventing sintering. Simultaneously, after the heat is carried away and the temperature decreases, the planetary oil holes and shaft groove oil holes will contract to some extent. However, because they are made of cast iron, they will not completely close, slowing the outflow of lubricating oil. This continuously delivers lubricating oil to the guide shaft groove, prolonging the normal lubrication state between the planetary shaft 40 and planetary gear 30 as much as possible, allowing the vehicle to maintain normal operation for as long as possible until subsequent lubrication is replenished.

[0081] Specifically, the vertical distance between the middle part of the inner hole of the planetary gear 30 and the central axis of the inner hole is smaller than the vertical distance between the two ends of the inner hole of the planetary gear 30 and the central axis of the inner hole. This increases the contact area between the planetary gear 30 and the planetary shaft 40, thereby reducing the stress on both ends of the planetary gear 30, which helps to enhance the strength of the planetary gear 30 and the planetary shaft 40 and increase their service life.

[0082] The remaining structure and working principle of Example 4 are the same as those of Example 1.

[0083] Example 5

[0084] Embodiment 5 of the present invention discloses a differential, which includes any one of the anti-sintering openable oil guiding structures for differentials in Embodiments 1 to 4.

[0085] In embodiment 5 of the invention, the differential adopts the above-described structure. When the vehicle is in motion, the differential will rotate with the rotation of the wheels, guiding some of the lubricating oil located in the vehicle to the interior of the differential. When the oil enters the differential housing 10 through the half-shaft mounting through-hole 11, the lubricating oil is first guided by the half-shaft oil guide groove 111 and flows into the gasket groove 13. As the differential rotates, the lubricating oil fills the entire gasket groove 13. Some of the lubricating oil flows into the gap between the gasket and the half-shaft bevel gear 20, lubricating and cooling the mating surfaces of the gasket and the half-shaft bevel gear 20. As the lubricating oil continues to flow, some flows to the lubrication ring wall 12, and another part flows to the oil collection groove 14. The lubricating oil splashed out by the rotation of the half-shaft bevel gear 20 will also splash onto the inner wall of the hollow cavity and then flow into the lubrication ring wall 12. When the planetary gear 30 meshes with the half-shaft bevel gear 20, it can carry away some of the lubricating oil, while also obtaining lubrication through the lubrication ring wall 12. Some of the lubricating oil will remain on the planetary shaft 40, and through the rotation of the planetary gear 30 and the spiral... The spiral-shaped planetary oil guide groove 31 guides the lubricating oil adhering to the planetary shaft 40 to the mating surface of the planetary shaft 40 and the planetary gear 30. As the planetary gear 30 rotates, the oil is discharged from the inside of the differential housing 10 (or introduced from the outside of the differential) along the spiral-shaped planetary oil guide groove 31. During this process, the flowing lubricating oil forms an oil film between the planetary gear 30 and the planetary shaft 40, increasing lubrication and preventing abnormal wear between the planetary shaft 40 and the planetary gear 30. The flowing lubricating oil also carries away the heat generated by friction, preventing sintering. The lubricating oil from one end of the lubrication ring wall 12 to the other end of the lubrication ring wall 12 will continue to flow into the oil collection groove 14 at the other end. The lubricating oil then flows from the oil collection groove 14 to the space between the half-shaft bevel gear 20 and the gasket for lubrication. Subsequently, the lubricating oil is discharged through the spiral-shaped oil guide groove on the half-shaft mounting through hole 11.

[0086] Example 6

[0087] like Figure 7 As shown, this embodiment provides a transmission flange, which mainly includes a flange body 410, a first transmission structure 420, a first connection structure 430, and a second transmission structure 440.

[0088] The first transmission structure 420 is disposed on the flange body 410. The first transmission structure 420 is used to connect with the differential half-shaft mounting through hole and transmit the torque of the differential half-shaft to the flange body 410.

[0089] like Figure 8 and Figure 10As shown, the half-shaft of the differential is connected to the flange body 410 through the first transmission structure 420. When the half-shaft of the differential rotates, the torque of the half-shaft of the differential acts on the first transmission structure 420, and drives the flange body 410 to rotate together through the first transmission structure 420, so that the rotation and torque of the output shaft are transmitted to the flange body 410.

[0090] The first connecting structure 430 is disposed on the flange body 410, and the first connecting structure 430 is used to connect the flange body 410 with the drive shaft.

[0091] In this embodiment, the first connecting structure 430 serves a connecting function. The first connecting structure 430 connects the flange body 410 to the drive shaft, thereby preventing the drive shaft from becoming loose from the flange body 410.

[0092] The second transmission structure 440 is disposed at one end of the flange body 410 facing the transmission shaft. The second transmission structure 440 is used to transmit the torque of the flange body 410 to the transmission shaft and prevent the torque from being transmitted to the first connection structure 430.

[0093] When the flange body 410 rotates under the drive of the differential half-shaft, the torque of the flange body 410 is transmitted to the drive shaft through the second transmission structure 440. During the rotation of the drive shaft driven by the flange body 410, the second transmission structure 440 is responsible for bearing the transmitted torque. Furthermore, the second transmission structure 440 also prevents torque from being transmitted to the first connecting structure 430. Thus, during the process of the flange transmitting torque to the transmission shaft, the first connecting structure 430 is not subjected to torque, making it less prone to damage. This ensures that the first connecting structure 430 can always connect the flange body 410 and the drive shaft, thereby improving the safety of the flange connection and reducing the number of first connecting structures 430, thus simplifying the structure and reducing costs.

[0094] In a preferred embodiment, the second transmission structure 440 is a rectangular tooth, which is disposed on the end face of the flange body 410 connected to the transmission shaft. The rectangular tooth on the flange body 410 is used to cooperate with the rectangular tooth on the transmission shaft to transmit torque.

[0095] The rectangular teeth are elongated and have a rectangular cross-section. In this embodiment, the drive shaft can be provided with rectangular teeth that mate with the rectangular teeth on the flange body 410. After the flange body 410 is installed and connected to the drive shaft, the end face of the flange body 410 mates with the drive shaft, and the rectangular teeth on the flange body 410 and the rectangular teeth on the drive shaft are engaged together. When the flange body 410 rotates, the rectangular teeth on the flange body 410 contact the rectangular teeth on its adjacent drive shaft, and the rectangular teeth on the flange body 410 push the rectangular teeth on its adjacent drive shaft, causing the drive shaft and the flange body 410 to rotate together. The rectangular teeth can be directly machined on the end face of the flange body 410 by milling. In order to simplify the flange structure while enabling the rectangular teeth to bear torque, the rectangular teeth are formed by two adjacent tooth grooves, and the tooth grooves are formed by the recess of the end face of the flange body 410 in the direction away from the drive shaft. Using the aforementioned structure to form rectangular teeth allows the top of the rectangular teeth to be flush with the end face of the flange body 410, thus not occupying extra space. Furthermore, the teeth can be formed simply by removing material from the existing flange body 410. The resulting rectangular teeth are an integral part of the flange body 410, minimizing impact on the original flange body 410. The overall structure is simple and has a strong load-bearing capacity.

[0096] In this embodiment, the first connecting structure 430 is connected to the drive shaft via a first connecting member; in the flange rotation direction, the fitting clearance between the first connecting member and the first connecting structure 430 is greater than the fitting clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the drive shaft.

[0097] Because the clearance between the first connector and the first connecting structure 430 is greater than the clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the drive shaft in the flange rotation direction, during flange transmission, before the first connector contacts the first connecting structure 430 and is subjected to force, the rectangular teeth on the flange body 410 contact the rectangular teeth on the drive shaft. Due to the obstruction of the rectangular teeth on the drive shaft, a clearance is always maintained between the first connector and the first connecting structure 430, thus effectively preventing torque action between the first connecting structure 430 and the first connector during transmission. The aforementioned first connector can be a bolt, and the first connecting structure 430 can be a bolt hole. When the flange body 410 is connected to the drive shaft, the bolt passes through the bolt hole.

[0098] In this embodiment, the flange body 410 is provided with multiple sets of transmission structure groups. Each set of transmission structure groups includes several first transmission structures 420 arranged in parallel with each other. The number of first connecting structures 430 is the same as the number of transmission structure groups, and the first connecting structures 430 correspond one-to-one with the transmission structure groups. The transmission structure groups are used to prevent torque from being transmitted to the corresponding first connecting structures 430.

[0099] like Figure 11 As shown, this embodiment can provide multiple first connecting structures 430 along the circumferential direction of the flange body 410 to improve the reliability of the connection. Furthermore, this embodiment adopts a one-to-one correspondence between transmission structure groups and first connecting structures 430. This ensures that each first connecting structure 430 is protected by a corresponding transmission structure group, guaranteeing that the transmission structure group preferably bears the torque, avoiding the problem that when multiple first connecting structures 430 are provided, it cannot be guaranteed that all first connecting structures 430 will not be subjected to torque. Each transmission structure group can provide multiple parallel first transmission structures 420. During transmission, each first transmission structure 420 in the same group can share the torque. Thus, the torque acting on the flange is distributed to each transmission structure group and then further distributed to each first transmission structure 420, reducing the torque borne by each first transmission mechanism while increasing the overall torque borne.

[0100] Furthermore, in the direction of rotation, the first connecting structure 430 is located at the center of its corresponding transmission structure group. By employing the aforementioned method, regardless of whether the flange body 410 rotates clockwise or counterclockwise, each first transmission structure 420 in the transmission structure group is subjected to torque before the first connecting structure 430 contacts the first connecting member, thereby ensuring that torque is not transmitted to the first connecting structure 430.

[0101] For example, six sets of transmission structure groups can be arranged on the flange body 410, each set having four rectangular teeth. These four rectangular teeth are parallel to each other and symmetrically arranged with the diameter of the flange body 410 parallel to these four rectangular teeth as the axis of symmetry. The first transmission structure 420 corresponding to this set of rectangular teeth is arranged on this axis of symmetry. The six sets of transmission structure groups are evenly distributed along the circumferential direction of the flange body 410, that is, the angle between any two adjacent sets of transmission structure groups is the same, and the interval between adjacent sets is 60 degrees. It is understood that the number of transmission groups and the number of first connecting structures 430 in each set of transmission structure groups can also be other numbers, which are not limited here.

[0102] This embodiment can employ multiple parallel rectangular teeth in a set of transmission structure groups, with the length of each rectangular tooth being the same as the radial dimension of the flange body 410 end face. Using the aforementioned method, the torque capacity of each set of transmission structure groups can be further increased without increasing the number of rectangular teeth in each group.

[0103] like Figure 10 As shown, in this embodiment, the flange body 410 includes a cylindrical first connecting portion 411 and a disc-shaped second connecting portion 412. The first connecting portion 411 and the second connecting portion 412 are arranged along the axial direction of the flange body 410. The first connecting portion 411 is provided with a through hole penetrating the connecting portion. The first transmission structure 420 is a spline, which is disposed on the through hole of the first connecting portion 411. The first connecting structure 430 is disposed on the second connecting portion 412.

[0104] When the first connecting structure 430 adopts rectangular teeth, the rectangular teeth are set on the disk surface of the second connecting part 412 facing the drive shaft.

[0105] In this embodiment, the first connecting part 411 is used to connect the flange body 410 to the differential half-shaft, while the second connecting part 412 is used to connect the flange body 410 to the drive shaft. By arranging the first connecting part 411 and the second connecting part 412 along the axial direction of the flange body 410, this embodiment compactly distributes the differential half-shaft drive shaft on both sides of the flange in the axial direction, thus avoiding mutual interference between the power input side and the power output side.

[0106] This embodiment uses splines for power transmission on the power input side, resulting in a strong load-bearing capacity. A through hole can be machined first at the first connecting part 411, and then splines can be machined on the inner wall.

[0107] In this embodiment, the second transmission structure 440 extends radially from the inner wall of the through hole to the outer wall of the second connecting portion 412. This method fully utilizes the radial dimension of the second connecting portion 412 disk, maximizing the length of the rectangular teeth capable of withstanding torque.

[0108] When the rectangular tooth is long, its deformation under torque increases. If the deformation exceeds a certain level, insufficient contact between the same rectangular tooth and its mating teeth will reduce the load-bearing capacity of the rectangular tooth. To address this, in this embodiment, each rectangular tooth is composed of multiple shorter sub-rectangular teeth, with adjacent sub-rectangular teeth disconnected. Using this method, the deformation of each sub-rectangular tooth will not accumulate on other sub-rectangular teeth, thus distributing the deformation of the rectangular tooth among all sub-rectangular teeth. Therefore, the deformation of each sub-rectangular tooth is very small and will not exceed the level that would cause insufficient contact between the rectangular teeth. The gap between adjacent sub-rectangular teeth can be very small; therefore, using the aforementioned structure will not significantly reduce the length of the portion of the rectangular tooth that can withstand torque.

[0109] like Figure 13 As shown, in this embodiment, each transmission structure group consists of two sub-transmission structure groups, namely the first sub-transmission structure group 441 and the second sub-transmission structure group 442. The number, cross-sectional shape, and spacing of the rectangular teeth in the two sub-transmission structure groups are equal; however, the two sub-transmission structure groups are staggered in the circumferential direction, and each rectangular tooth is divided into two disconnected parts, belonging to the two sub-transmission structure groups respectively. Using the aforementioned method, the deformation of the rectangular teeth can be reduced without reducing the total length of the portion of the rectangular teeth used to bear torque. After the two sub-transmission structure groups are staggered in the circumferential direction, the force on the flange body 410 is not concentrated at the same circumferential position of the flange body 410, and the deformation of the flange body 410 is also distributed to various positions in the circumferential direction of the flange body 410.

[0110] In the first sub-transmission structure group 441, one end of each rectangular tooth extends to the outer wall of the flange body 410. In this way, the milling cutter can remove material from the outside of the flange body 410 to the inside in one go to complete the machining of the rectangular teeth, which can significantly improve the machining efficiency.

[0111] In the circumferential direction, the first sub-drive structure group 441 and the second sub-drive structure group 442 can be completely offset or partially offset. When completely offset, the first sub-drive structure group 441 and the second sub-drive structure group 442 partially overlap in the radial direction. The disconnected portion of the first sub-drive structure group 441 and the second sub-drive structure group 442 on the flange body 410 cannot withstand torque, and the stress on the portion of the first sub-drive structure group 441 and the second sub-drive structure group 442 near the disconnection position will also change abruptly, all of which will affect the service life of the flange. However, after the first sub-drive structure group 441 and the second sub-drive structure group 442 partially overlap in the radial direction, the portion of the flange body 410 that cannot withstand torque in the radial direction due to the radial tooth disconnection is eliminated, and the abrupt change in stress on the portion of the first sub-drive structure group 441 and the second sub-drive structure group 442 near the disconnection position is avoided.

[0112] When the teeth are not completely staggered, the tooth grooves of the rectangular teeth in the first sub-transmission structure group 441 and the tooth tips of the rectangular teeth in the second sub-transmission structure group 442 can be aligned. By adopting the aforementioned method, the portion of the flange body 410 used to bear torque in the circumferential direction can be maximized within the same group of transmission structures, thus allowing the flange body 410 to withstand a greater amount of torque.

[0113] like Figure 12 As shown, in this embodiment, the same transmission structure group consists of three sub-transmission structure groups, which are the third sub-transmission structure group 443, the fourth sub-transmission structure group 444, and the fifth sub-transmission structure group 445, respectively, from the outer wall of the flange body 410 inwards. The rectangular teeth of each transmission structure group are disconnected from each other, and the length of the rectangular teeth of the third sub-transmission structure group 443 is less than that of the fourth sub-transmission structure group 444, the length of the rectangular teeth of the fourth sub-transmission structure group 444 is less than that of the fifth sub-transmission structure group 445. Under the same torque, the deformation of the outer side of the flange body 410 is greater than that of the inner side. This embodiment adopts the aforementioned structure in which the length of the rectangular teeth decreases from the inside to the outside, which can reduce the variance of the deformation of the rectangular teeth at various radial positions of the flange body 410, and avoid excessive deformation of the rectangular teeth at local positions in the radial direction of the flange body 410, which would affect the service life of the flange.

[0114] like Figure 9 As shown, in this embodiment, the second connecting part 412 is provided with a limiting hole 4121 that cooperates with the drive shaft. The end of the limiting hole 4121 facing the first connecting part 411 is provided with a stop 4122 for limiting the axial position of the drive shaft. The spline extends to the position of the stop 4122.

[0115] During installation, the end of the drive shaft can be inserted into the limiting hole 4121 of the second connecting part 412 until the end of the drive shaft abuts against the stop 4122. The output shaft of the gearbox can be inserted into the through hole. Because the spline in the through hole extends to the stop 4122, the distance between the position where the input torque is transmitted and the end of the drive shaft is relatively short. Using the aforementioned method shortens the distance between the position where the input torque is transmitted and the position where the output torque is transmitted, thereby reducing the deformation of the transmission components between the input and output ends under torque.

[0116] Example 7

[0117] like Figure 14 This embodiment provides a four-speed gear shifting device for a transmission, which is used to perform four-speed shifting operations and can also be applied to the transmission in Embodiment 1. For ease of description, these four speeds are divided into two groups: the first group and the second group, with each group including two speeds. The four-speed gear shifting device of this embodiment includes a shift drum 1, a motor 6, a first synchronizer, a first drive mechanism 3, a second synchronizer 4, and a second drive mechanism 5.

[0118] like Figure 15 and Figure 16 As shown, the shift drum 1 is provided with a guide groove 110 extending in its circumferential direction, and the guide groove 110 includes a shift area 112 that rotates with the shift drum 1 to different angular positions;

[0119] like Figure 14 As shown, the shift drum 1 can be cylindrical, and the aforementioned guide groove 110 can be set on the cylindrical peripheral wall of the shift drum 1. The shift area 112 is a part of the entire guide groove 110. The shift drum 1 can rotate around its own axis, and the shift area 112 also rotates to different positions as the shift drum 1 rotates.

[0120] like Figure 17 As shown, the first synchronizer is used to participate in the gear engagement operation of the first gear group. The first synchronizer can be synchronously connected to the input shaft or the output shaft. The first synchronizer is equipped with a gear engagement component, which can move axially along the first synchronizer under the action of an external force (e.g., by the action of a shift fork). When the gear engagement component of the first synchronizer moves to fully engage with a gear of a certain gear, the first synchronizer rotates synchronously with that gear. At this time, the power of the input shaft can be transmitted to that gear through the first synchronizer, or the power of that gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that allows the first synchronizer and the input shaft or output shaft to rotate synchronously.

[0121] The first drive mechanism 3 is slidably connected to the guide groove 110 at the first corner position 120 of the shift drum 1. The first drive mechanism 3 is used to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to the first axial position for shifting under the drive of the shifting area 112, or to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to the second axial position for shifting, wherein the first axial position and the second axial position are different.

[0122] The first axial position refers to the position where the engagement component of the first synchronizer is fully engaged with the gear of one of the gears in the first group of gears, causing that gear to rotate synchronously with it. The second axial position refers to the position where the engagement component of the first synchronizer is fully engaged with the gear of the other gear in the first group of gears, causing that gear to rotate synchronously with it. The aforementioned engagement component can be the synchronization ring of the first synchronizer.

[0123] As the shift drum 1 rotates, the shift area 112 can rotate to an angular position range where it is slidably connected to the first drive mechanism 3. Within this angular position range, the position of the shift area 112 connected to the first drive mechanism changes continuously as the shift drum 1 rotates. Since the distances between the shift area 112 and the first synchronizer differ along the axial direction at various positions, the shift area 112 can drive the first drive mechanism 3 to move axially during rotation. Simultaneously, the first drive mechanism 3, while moving axially, also pushes the shifting component of the first synchronizer to move axially.

[0124] In this embodiment, the first driving mechanism 3 includes a first sliding member 310, a first shift fork 32 and a first connecting member 33. The first connecting member 33 is connected to the first sliding member 310 and the first shift fork 32 respectively. The first sliding member 310 slides along the guide groove 110.

[0125] The width of the guide groove is slightly larger than the width of the first sliding member 310, and the movement direction of the first connecting member 33 is constrained, allowing it to move only along the axial direction. Looking along the axial direction of the shift drum 1, the distance between the guide groove 110 and the first synchronizer or second synchronizer 4 varies at different circumferential positions in some areas. When the shift drum 1 rotates, different positions of the guide groove 110 contact the first sliding member 310. The sliding member slides circumferentially relative to the guide groove 110 while simultaneously moving back and forth along the axial direction under the drive of the guide groove 110. Since the first connecting member 33 connects the first sliding member 310 and the first shift fork 32 together, the first shift fork 32 also moves synchronously along the axial direction with the first sliding member 310. The first connecting member 33 can be located on the radial side of the shift drum 1, and the first sliding member 310 is located along the radial direction of the shift drum 1. One end of the first sliding member 310 is connected to the first connecting member 33, and the other end is embedded in the guide groove 110.

[0126] like Figure 14 and Figure 18 As shown, the second synchronizer 4 is used to participate in the gear engagement operation of the second gear group. The second synchronizer 4 can be synchronously connected to the input shaft or the output shaft. The second synchronizer 4 is equipped with a gear engagement component, which can move axially along the second synchronizer 4 under the action of an external force (e.g., by the action of a shift fork). When the gear engagement component of the second synchronizer 4 moves to fully engage with a gear of a certain gear, the second synchronizer 4 rotates synchronously with that gear. At this time, the power of the input shaft can be transmitted to that gear through the second synchronizer 4, or the power of that gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that allows the second synchronizer 4 to rotate synchronously with the input shaft or the output shaft.

[0127] The second drive mechanism 5 is slidably connected to the guide groove 110 at the second corner position 130 of the shift drum 1. The second drive mechanism 5 is used to push the shifting component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the third axial position for shifting under the drive of the shifting area 112, or to push the shifting component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the fourth axial position for shifting. The third axial position and the fourth axial position are different, and the second corner position 130 is different from the first corner position 120.

[0128] The third axial position refers to the position where the gear engagement component of the second synchronizer 4 is fully engaged with the gear of one of the gears in the second group of gears, causing that gear to rotate synchronously with it. The fourth axial position refers to the position where the gear engagement component of the second synchronizer 4 is fully engaged with the gear of another gear in the second group of gears, causing that gear to rotate synchronously with it. The aforementioned gear engagement component can be the synchronization ring of the second synchronizer 4.

[0129] As the shift drum 1 rotates, the shift zone 112 can rotate to an angular position range where it is slidably connected to the second drive mechanism 5. Within this angular position range, the position of the shift zone 112 connected to the second drive mechanism 5 changes continuously as the shift drum 1 rotates. Since the distances between the shift zone 112 and the second synchronizer 4 vary along the axial direction at different positions, the shift zone 112 can drive the second drive mechanism 5 to move axially during rotation. Simultaneously, the second drive mechanism 5 moves axially and pushes the gear engagement component of the second synchronizer 4 to move axially.

[0130] In this embodiment, the second driving mechanism 5 includes a second sliding member 510, a second shift fork 52, and a second connecting member 53. The second connecting member 53 is connected to the second sliding member 510 and the second shift fork 52 respectively. The second sliding member 510 slides along the guide groove 110.

[0131] The width of the guide groove is slightly larger than the width of the second sliding member 510, and the movement direction of the second connecting member 53 is constrained, allowing it to move only in the axial direction. Looking along the axial direction of the shift drum 1, the distance between the guide groove 110 and the first synchronizer or the second synchronizer 4 varies at different circumferential positions in some areas. When the shift drum 1 rotates, different positions of the guide groove 110 contact the second sliding member 510. The sliding member slides circumferentially relative to the guide groove 110 while simultaneously moving back and forth in the axial direction under the drive of the guide groove 110. Since the second connecting member 53 connects the second sliding member 510 and the second shift fork 52 together, the second shift fork 52 also moves synchronously in the axial direction with the second sliding member 510. The second connecting member 53 can be located on the radial side of the shift drum 1, and the second sliding member 510 is located radially along the shift drum 1. One end of the second sliding member 510 is connected to the second connecting member 53, and the other end is embedded in the guide groove 110.

[0132] like Figure 14 As shown, motor 6 drives the shift drum 1 to rotate so that shift zone 112 drives the first drive mechanism 3 and the second drive mechanism 5 to move back and forth along the axial direction of shift drum 1. The motor 6, the first synchronizer, and the second synchronizer 4 are located on both sides of the shift drum 1 in the axial direction, and the motor 6 is coaxially arranged with the shift drum 1.

[0133] In this embodiment, the motor 6 and the two drive mechanisms are set separately along the axial direction, so that they are located on both sides of the shift drum 1. In this way, the operation of the motor 6 and the drive mechanism can not affect each other. Furthermore, setting the motor 6 and the shift drum 1 coaxially can make the structure more compact and also utilize the power transmission between the motor 6 and the shift drum 1.

[0134] In a preferred embodiment, the four-speed shifting device of the transmission further includes a rotating shaft 7. The shift drum 1 is interference-fitted with the rotating shaft 7, and the motor 6 drives the rotating shaft 7 to rotate, thereby driving the shift drum 1 to rotate. The transmission is simpler and more reliable because the rotating shaft and the shift drum 1 are directly coupled by an interference fit. The motor 6 is mounted on the assembly housing, and the shift drum 1 is positioned on the housing via the rotating shaft 7. The shift drum 1 and the rotating shaft 7 are relatively fixed, while the rotating shaft 7 can rotate on the housing.

[0135] like Figure 19 As shown, in this embodiment, an annular limiting groove 21 is provided on the peripheral wall of the first synchronizer and / or the second synchronizer 4, and an actuating member 325 is provided at the end of the first shift fork 32 and / or the second shift fork 52. The actuating member 325 actuates the shifting component of the first synchronizer and / or the second synchronizer 4 by actuating the side wall of the limiting groove 21.

[0136] In this embodiment, the width of the limiting groove 21 is greater than 1.1 times the width of the actuating member 325, and the distance between the first axial position and the second axial position is greater than twice the axial gap between the actuating member 325 and the limiting groove 21. With the aforementioned structure, after the actuating member 325 is inserted into the limiting groove 21 and the synchronizer's shifting component is shifted to the shifting position, one side of the actuating member 325 contacts one sidewall of the limiting groove 21, while the other side of the actuating member 325 has sufficient clearance from the other sidewall of the limiting groove 21. This ensures that even if a small, unexpected vibration causes relative displacement between the actuating member 325 and the limiting groove 21, the other side of the actuating member 325 will not contact the other sidewall of the limiting groove 21. This prevents the actuating member 325 from shifting the limiting groove 21 due to unexpected vibration, thus disengaging the shifting component from the current gear position and making shifting more reliable. When shifting gears normally, the distance that the actuating element 325 moves in the axial direction must exceed the axial gap between the actuating element 325 and the limiting groove 21. Therefore, during the shifting movement, the other side of the actuating element 325 can also push the shifting component to move by contacting the other side wall of the limiting groove 21.

[0137] When the shifter 325 engages the synchronizer to shift gears, the shifter 325 contacts the synchronizer. Since the synchronizer is rotating at high speed, relative motion occurs between the shifter 325 and the synchronizer, resulting in continuous sliding friction. Both the shifter 325 and the synchronizer are prone to wear and deformation, and the heat generated by friction can also affect the transmission. One solution is to install a replaceable wear-resistant part on the shifter 325, allowing it to contact the synchronizer. The wear-resistant part is then replaced when it wears down to a certain extent. However, this method requires disassembling and reassembling the transmission to replace the wear-resistant part, making it very inconvenient in practical use.

[0138] To address this, an oil guide groove can be provided on the first shift fork 32, and the outlet of the oil guide groove can be located on the surface where the shift member 325 contacts the synchronizer. The lubricating oil flows along the oil guide groove to the surface of the shift member 325, forming an oil film between the shift member 325 and the synchronizer to reduce the friction between the two.

[0139] Alternatively, rollers or needle rollers can be installed on the actuating element 325 to reduce friction. However, since the rollers make point contact with the synchronizer and the needle rollers make line contact with the synchronizer, the contact area of ​​both contact methods is very small, which can easily cause the synchronizer and the shift fork to be subjected to excessive force concentration.

[0140] To address this, this embodiment employs a structure that allows the actuating element 325 to rotate synchronously with the synchronizer to avoid friction. For example, 20 to... Figure 22As shown, the first shift fork 32 in this embodiment further includes a cylindrical first rotating member 321, a second rotating member 322, a third rotating member 323, and a fourth rotating member 324. The first rotating member 321, the second rotating member 322, the third rotating member 323, and the fourth rotating member 324 are rotatably connected to the first shift fork 32. The extension lines of the rotation axes of the first rotating member 321, the second rotating member 322, the third rotating member 323, and the fourth rotating member 324 intersect at the same intersection point, which is located on the rotation axis of the first synchronizer. The rotation axis of the first rotating member 321 and the rotation axis of the second rotating member 322 are located in a first plane, and the rotation axis of the third rotating member 323 and the rotation axis of the fourth rotating member 324 are located in a second plane different from the first plane. The first plane and the second plane are arranged along the axial direction of the first synchronizer. The actuating element 325 is a rotating belt 326. One end of the rotating belt 326 successively wraps around the outer walls of the first rotating element 321, the second rotating element 322, the third rotating element 323, and the fourth rotating element 324 before connecting to the opposite end. The rotating belt 326 can be a steel belt or a leather belt. In specific implementation, the rotating belt 326 is taut and wrapped around the outer walls of the four rotating elements, with the ends of the rotating belt 326 connected to form a loop. The rotating belt 326 unfolds into an arc shape. When the distance between the first rotating element 321 and the second rotating element 322 is too long, a fifth rotating element can be set between the first rotating element 321 and the second rotating element 322 to provide support for the rotating belt 326 in the middle; when the distance between the third rotating element 323 and the fourth rotating element 324 is too long, a fifth rotating element can be set between the first rotating element 321 and the second rotating element 322 to provide support for the rotating belt 326 in the middle. Multiple fifth and sixth rotating members can be provided, and their number can be determined based on the distance between the first rotating member 321 and the second rotating member 322, or the distance between the third rotating member 323 and the fourth rotating member 324. Each of the aforementioned rotating members can be rotatably connected to the first shift fork 32 via a smooth-surfaced rotating shaft.

[0141] With the aforementioned structure, when the rotating belt 326 moves with the first shift fork 32 to the position of contact with the synchronizer, the rotating belt 326 rotates under the drive of the synchronizer, and the rotation direction of the rotating belt 326 is as follows: Figures 8 to 10As indicated by the arrow in the diagram. Initially, when the rotating belt 326 first contacts the synchronizer, there will be sliding friction between the rotating belt 326 and the synchronizer. Once the rotating belt 326 and the synchronizer rotate at the same speed, there will be no relative sliding between the rotating belt 326 and the synchronizer, and no sliding friction will occur that would cause wear on the rotating belt 326 and the synchronizer. At this time, the rotating belt 326 rotates in sequence around the four rotating parts under the drive of the synchronizer. The contact between the rotating belt 326 and the synchronizer is a surface contact, which makes it less likely for the force to be too concentrated, and the rotating belt 326 can always rotate synchronously with the synchronizer.

[0142] This embodiment also provides another implementation method to solve the aforementioned sliding friction problem. The first shift fork 32 further includes multiple sets of rotating components. Each set of rotating components includes a seventh rotating member, an eighth rotating member, and a rotating belt 326. The seventh and eighth rotating members are rotatably connected to the first shift fork 32. One end of the rotating belt 326 passes around the outer wall of the seventh and eighth rotating members and connects to the opposite end. The rotation axes 7 of the seventh and eighth rotating members are parallel to each other. The eighth and ninth rotating members are axially symmetrically arranged, and their axis of symmetry serves as the axis of symmetry of the rotating components. The extension lines of the axes of symmetry of each set of rotating components intersect at the same point, which is located on the rotation axis of the first synchronizer.

[0143] Each set of rotating components forms a small rotating unit, and the rotating belt 326 of each set of rotating components can rotate cyclically around four rotating parts. Since the extension line of the axis of symmetry of the rotating components lies on the rotation axis of the first synchronizer, when the rotating belt 326 moves with the first fork 32 to the position of contact with the synchronizer, the rotation direction of the rotating belt 326 of each rotating component is almost the same as the rotation direction of the corresponding position on the synchronizer, resulting in very little sliding friction between the rotating belt 326 of each rotating component and the synchronizer. Using the aforementioned method, the structure is simple, the rotating components can be arranged in parallel, facilitating installation, achieving both surface contact and reduced sliding friction.

[0144] In this embodiment, the four-speed gear shifting device can use a motor 6 to drive the shift drum 1 to rotate. When the shifting area 112 of the shift drum 1 rotates to the position connected to the first drive mechanism 3, the shifting area 112 can rotate with the shift drum 1 and push the first synchronizer through the first drive mechanism 3 to perform two gear shifting operations. When the shifting area 112 of the shift drum 1 rotates to the position connected to the second drive mechanism 5, the shifting area 112 can rotate with the shift drum 1 and push the second synchronizer 4 through the second drive mechanism 5 to perform the other two gear shifting operations. Since the areas where the first drive mechanism 3 and the second drive mechanism 5 are connected to the shift drum 1 are at different angular positions, only one shift drum 1 and two drive mechanisms are needed to perform two gear shifting operations respectively. The aforementioned four gear shifting operations can be completed by only one motor 6 driving one shift drum 1 to rotate. Therefore, the number of shifting actuators is small, the shifting action is simple, and the operation is more reliable.

[0145] Example 8

[0146] Embodiment 8 of the present invention discloses an automobile, which includes any differential anti-sintering oil guiding structure in Embodiments 1 to 4, or the differential in Embodiment 5, or the transmission flange in Embodiment 6, or the four-speed shifting device of the transmission in Embodiment 7.

[0147] The vehicle in Embodiment 8 can be a traditional fuel-powered vehicle, such as a gasoline vehicle or a diesel vehicle, or a new energy vehicle. New energy vehicles include, but are not limited to, battery electric vehicles (BEV / EV), hybrid electric vehicles (HEV, PHEV, and REEV), fuel cell vehicles (FCEV), and solar cell vehicles.

[0148] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A differential anti-sintering openable oil guiding structure, characterized in that, The differential gear includes: a differential housing with a hollow cavity; a half shaft bevel gear arranged in the hollow cavity; a planet shaft arranged in the differential housing; a planet gear sleeved on the planet shaft and engaged with the half shaft bevel gear; wherein a planet oil guide groove is arranged on an inner hole of the planet gear, the planet oil guide groove is located between the planet gear and the planet shaft, the planet oil guide groove is used for guiding lubricating oil to flow through a surface of the planet shaft and the planet gear, and guiding the lubricating oil to an outside of the differential housing or an inside of the differential; a lubricating ring wall is arranged in the hollow cavity, and the lubricating ring wall is used for bearing lubricating oil splashed by rotation of the planet gear and the half shaft bevel gear; a plurality of planet oil holes storing lubricating oil are arranged on the planet oil guide groove, and the planet oil holes have two states of opening and closing; and 2. The anti-seizure openable oil guiding structure for a differential according to claim 1, characterized by, a plurality of shaft groove oil holes storing lubricating oil are arranged on an oil guide shaft groove of the planet shaft, and the shaft groove oil holes also have two states of opening and closing.

3. The anti-seizure openable oil guiding structure for a differential according to claim 2, characterized by, A mounting table coaxial with the half shaft mounting through hole is arranged on an outside of the differential housing, a plurality of flanges are arranged on the mounting table, and the flanges are used for connecting with other external equipment.

4. The anti-seizure openable oil guiding structure for a differential according to claim 3, characterized by, The flanges are arranged in six groups, each three flanges form a group, and a connecting rib for strengthening stability and strength of the mounting table and the flanges is arranged between adjacent flanges in each group.

5. The anti-seizure openable oil guiding structure for a differential according to claim 1, characterized by, A plurality of reinforcing ribs are arranged on the mounting table and located on a side away from the flanges in a circumferential direction of the half shaft mounting through hole.

6. The anti-seizure openable oil guiding structure for a differential according to claim 5, characterized by, A planet shaft sleeve is sleeved on an inner hole of the planet gear, a shaft sleeve through hole is arranged at a center of the planet shaft sleeve, the shaft sleeve through hole is matched with the planet shaft, the planet shaft sleeve is sleeved on the planet shaft, and the planet shaft and the planet shaft sleeve are relatively rotatable.

7. The anti-seizure openable oil guiding structure for a differential according to claim 5, characterized by, A shaft sleeve oil groove is arranged on an inner wall of the shaft sleeve through hole, and the shaft sleeve oil groove is in a spiral shape and extends from one end of the shaft sleeve through hole to the other end.

8. The anti-seizure openable oil guide structure for a differential according to any one of claims 1 to 7, characterized by, A length of the shaft sleeve through hole is equal to or greater than a length of the inner hole of the planet gear.

9. A differential characterized by, A vertical distance between a middle part of the inner hole of the planet gear and a center axis of the inner hole is less than vertical distances between two end parts of the inner hole of the planet gear and the center axis of the inner hole.

10. An automobile characterized by comprising: The differential gear includes the anti-seizing openable and closable oil guide structure according to any one of claims 1 to 8. The automobile includes the anti-seizing openable and closable oil guide structure according to any one of claims 1 to 8 or the differential gear according to claim 9.

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