Differential, reducer and vehicle with uniform force

Abstract

The present invention belongs to the technical field of new energy vehicles, solves the problem in the prior art that the half shaft gear rotates around the planetary gear inside the differential, resulting in difficulties in subsequent half shaft installation, and provides a differential, a reducer and a vehicle with uniform force. The differential includes a differential housing, a spherical mounting housing, a half shaft gear and a planetary gear. The planetary gear is sleeved on the planetary shaft, and the planetary gear meshes with the half shaft gear. The spherical mounting housing is provided with a first circumferential fixing rib extending along the circumferential direction of the half shaft gear, and the half shaft gear is provided with a second circumferential fixing rib extending along the circumferential direction of the half shaft gear. The first circumferential fixing rib and the second circumferential fixing rib are in clearance fit to limit the rotation of the half shaft gear around the axis of the planetary gear. The present invention simply and effectively limits the rotation of the half shaft gear around the axis of the planetary gear, and avoids the problem of difficult half shaft installation caused by the offset of the half shaft gear.

Description

[0001] This application is a divisional application of the invention patent application with the application date of September 29, 2021, the invention name of "Differential, Reducer and Vehicle for Preventing Eccentricity of Half Axle Gear", and the application number of 2021111528764. Technical Field

[0002] The present invention belongs to the technical field of new energy vehicles, and particularly relates to a differential, a reducer and a vehicle with uniform force. Background Art

[0003] The planetary gears and half axle gears in the differential usually have two fixing methods in the differential housing. The first method is that the end faces of the planetary gears and half axle gears are fixed on the differential housing by using two flat gaskets and two spherical gaskets respectively; the second method is that the end faces of the planetary gears and half axle gears are both fixed inside the spherical differential housing. Both of these two methods are widely used. However, for the first method, because the manufacturing process of its gaskets is relatively complex, involving molds, forming, surface grinding and surface treatment, the cost is relatively high; for the second method, only one plastic mold is needed to achieve it, the process is simple and the cost is low.

[0004] However, for the second method, there is a most prominent problem: the half axle gear is prone to rotate around the planetary gear inside the differential during the working process, and the spline hole of the half axle gear and the half axle hole of the differential housing will be misaligned, resulting in difficulties in subsequent half axle installation. Summary of the Invention

[0005] In view of this, the present invention provides a differential, a reducer and a vehicle with uniform force to solve the problem in the prior art that the half axle gear rotates around the planetary gear inside the differential, resulting in difficulties in subsequent half axle installation.

[0006] The technical solution adopted by the present invention is:

[0007] In a first aspect, the present invention provides a differential with uniform force, and the differential includes:

[0008] A differential housing, in which a spherical cavity and two windows for receiving lubricating oil are provided. The two windows are located on both sides of the spherical cavity, both windows are communicated with the spherical cavity, and the two windows are symmetrically arranged;

[0009] A spherical mounting housing, the shape of the spherical mounting housing matches the shape of the spherical cavity, and the spherical mounting housing is fixed in the spherical cavity;

[0010] A half axle gear, and the half axle gear is arranged in the spherical mounting housing;

[0011] A planetary gear, which is also arranged inside the spherical mounting housing. The planetary gear is sleeved on a planetary shaft, and the planetary gear meshes with the half-axle gear.

[0012] Inside the spherical mounting housing, there is a first circumferential fixing rib extending along the circumferential direction of the half-axle gear. On the half-axle gear, there is a second circumferential fixing rib extending along the circumferential direction of the half-axle gear. The first circumferential fixing rib and the second circumferential fixing rib are in clearance fit to limit the rotation of the half-axle gear around the axis of the planetary gear.

[0013] Preferably, the central axes of the spherical cavity and the window coincide. Taking the direction from one window looking at the other window as the projection direction, the projected area of the spherical cavity is larger than the projected area of the window.

[0014] Preferably, the spherical mounting housing includes a planetary part and a half-axle part. The central axis of the planetary part is perpendicular to the central axis of the half-axle part. On the half-axle part, in the direction away from the center of the spherical mounting housing, there is a fixing ring, which is used to limit the rotation of the spherical mounting housing around the horizontal axis in the spherical cavity.

[0015] Preferably, the half-axle part is recessed in the direction away from the center of the spherical mounting housing, the planetary part is recessed in the direction away from the center of the spherical mounting housing, and a planetary hole is provided on the planetary part.

[0016] Preferably, both ends of the differential housing are provided with half-axle mounting through holes. Outside the differential housing, there is a mounting table coaxial with the half-axle mounting through holes. On the mounting table, a number of mounting holes are provided, and the mounting holes are used to connect with other external devices. At one end of the mounting table facing away from the spherical mounting housing, there are a number of reinforcing ribs, and the number of reinforcing ribs is arranged in a circumferential pattern with the central axis of the mounting table as the axis.

[0017] Preferably, a planetary shaft sleeve is sleeved on the inner hole of the planetary gear. A sleeve through hole is provided in the center of the planetary shaft sleeve. The sleeve through hole is matched with the planetary shaft, and the planetary shaft and the planetary shaft sleeve can rotate relative to each other. An oil groove is provided on the inner wall of the sleeve through hole of the planetary shaft sleeve.

[0018] Preferably, the oil groove on the shaft sleeve is in a spiral shape, extending from one end of the sleeve through hole to the other end.

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

[0020] In a second aspect, the present invention provides a speed reducer, and the speed reducer includes any one of the above differential mechanisms with uniform force.

[0021] In a third aspect, the present invention provides a vehicle, which includes any one of the above differential mechanisms with uniform force or the vehicle described above.

[0022] In summary, the beneficial effects of the present invention are as follows:

[0023] The differential mechanism with uniform force, the speed reducer and the vehicle provided by the present invention are provided with second circumferential fixing ribs in the circumferential direction of the half shaft gear, and first circumferential fixing ribs are arranged in the spherical mounting housing. The second circumferential fixing ribs are in clearance fit with the first circumferential fixing ribs, which is used to limit the rotation of the half shaft gear around the axis of the planetary gear, ensuring that the half shaft gear can only rotate along the circumferential direction of the first circumferential fixing ribs, so that the half shaft gear will not be offset or misaligned, avoiding the subsequent installation between the half shaft and the differential housing becoming difficult. By arranging two windows on both sides of the spherical cavity, both windows communicate with the spherical cavity and are symmetrically arranged, so that the overall force and weight of the differential housing are uniform. Description of the Drawings

[0024] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the embodiments of the present invention will be briefly introduced below. For those of ordinary skill in the art, other drawings can also be obtained based on these drawings without creative efforts, and all of these are within the protection scope of the present invention.

[0025] Figure 1 Structural schematic diagram of the differential mechanism with uniform force in Embodiment 1 of the present invention;

[0026] Figure 2 For Figure 1 exploded view of

[0027] Figure 3 Cross-sectional view of the differential mechanism with uniform force in Embodiment 1 of the present invention;

[0028] Figure 4 Cross-sectional view of the differential housing in Embodiment 1 of the present invention;

[0029] Figure 5 Structural schematic diagram of the spherical mounting housing in Embodiment 1 of the present invention;

[0030] Figure 6 Structural schematic diagram of the half shaft gear in Embodiment 1 of the present invention;

[0031] Figure 7 Structural schematic diagram of the cooperation between the planetary gear and the planetary shaft in Embodiment 2 of the present invention;

[0032] Figure 8 Structural schematic diagram of the planetary oil guiding groove in Embodiment 2 of the present invention;

[0033] Figure 9 Structural schematic diagram of the planetary bushing sleeved on the planetary shaft in Embodiment 3 of the present invention;

[0034] Figure 10 Cross-sectional view of the planetary bushing in Embodiment 3 of the present invention;

[0035] Figure 11 Three-dimensional structure diagram of the transmission flange in Embodiment 5 of the present invention;

[0036] Figure 12 Three-dimensional structure diagram of the transmission flange in another perspective in Embodiment 5 of the present invention;

[0037] Figure 13 Three-dimensional view of the structure of the transmission flange in Embodiment 5 of the present invention for connection with the transmission shaft;

[0038] Figure 14 Side view of the transmission flange in Embodiment 5 of the present invention;

[0039] Figure 15 Front view of the transmission flange in Embodiment 5 of the present invention;

[0040] Figure 16 Structural schematic diagram of the three groups of sub-transmission structure groups of the present invention in Embodiment 5 being disconnected;

[0041] Figure 17 Structural schematic diagram of the two groups of sub-transmission structures of the transmission flange in Embodiment 5 of the present invention being staggered in the circumferential direction;

[0042] Figure 18 Three-dimensional structure diagram of the four-speed shifting device of the transmission of the present invention;

[0043] Figure 19 Angular position optical relationship diagram of the shifting area of the shifting drum of the present invention with the first driving mechanism and the second driving mechanism;

[0044] Figure 20 Three-dimensional structure diagram of the shifting drum of the present invention;

[0045] Figure 21 Three-dimensional structure diagram of the cooperation between the first driving mechanism and the shifting drum of the present invention;

[0046] Figure 22 Three-dimensional structure diagram of the cooperation between the first driving mechanism and the shifting drum of the present invention;

[0047] Figure 23 Three-dimensional structure diagram of the cooperation between the first driving mechanism and the first synchronizer of the present invention

[0048] Figure 24 Top view of the structure of the present invention that can make the rotating belt rotate with the synchronizer;

[0049] Figure 25 A side view of a structure of the present invention that enables a rotating belt to rotate with a synchronizer;

[0050] Figure 26 A diagram showing the positional relationship of the four rotating parts of the present invention;

[0051] Figure 27 It is a structural schematic diagram of the vehicle in the present invention.

[0052] Parts and numbers in the picture:

[0053] 10. Differential housing; 11. Spherical cavity; 12. Axle shaft mounting through hole; 13. Window; 14. Mounting platform; 141. Mounting hole;

[0054] 20. Spherical mounting housing; 21. Axle portion; 211. First circumferential fixing rib; 22. Planet portion; 23. Fixing ring;

[0055] 30. Axle gear; 31. Second circumferential fixing rib;

[0056] 40. Planetary gear; 41. Planetary oil guide groove;

[0057] 50. Planetary shaft; 60. Planetary shaft sleeve; 61. Shaft sleeve oil groove;

[0058] 410, flange body; 411, first connecting portion; 412, second connecting portion; 4121, limiting hole; 4122, stopper; 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;

[0059] 1. Shift drum; 110. Guide groove; 112. Shift zone; 113. First guide section; 114. Second guide section; 115. Third guide section; 120. First angular position; 130. Second angular position;

[0060] 210, limiting slot; 3, first driving 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, shifting member; 326, rotating belt; 5, second driving mechanism; 51, second sliding member; 52, second shift fork; 53, second connecting member; 6, motor; 7, rotating shaft;

[0061] 600, power system; 700, transmission system; 800, body. DETAILED DESCRIPTION

[0062] To make the objectives, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It should be noted that in this text, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any 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", "outer", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. This is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention. Moreover, the term "comprising", "including" or any other variant thereof is intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements not only includes those elements, but also includes other elements not expressly listed, or also includes elements inherent to such process, method, article or device. Without further limitation, the elements defined by the statement "comprising..." do not exclude the existence of additional identical elements in the process, method, article or device comprising the said elements. If there is no conflict, the embodiments of the present invention and the various features in the embodiments may be combined with each other, and all are within the protection scope of the present invention.

[0063] Please refer to Figure 27 , a vehicle is a commonly used means of transportation, mainly composed of a power system 600, a transmission system 700, a vehicle body 800, a chassis, etc. Among them, the transmission system 700 further includes a transmission, a four-speed shifting device of the transmission, a propeller shaft, a differential, and a transmission flange, etc. When the vehicle is running, the power of the power system 600 is transmitted to the transmission, and the transmission converts the power of the power system 600 and then outputs power with appropriate torque and speed. The converted power is then transmitted to the propeller shaft, and after the propeller shaft transmits the power to the differential, the differential transmits the power to the wheels on both sides respectively. The converted power can also be transmitted to the differential. In order to achieve parking and shifting, the transmission is also provided with a shifting device and a parking device. In order to lubricate devices such as the transmission and the differential, a lubrication system is also configured for the transmission, the differential and other devices.

[0064] Embodiment 1

[0065] Please refer to Figures 1 to 6, Embodiment 1 of the present invention discloses a differential with uniform force, effectively solving the problem that the spline hole on the half shaft gear 30 is offset and misaligned in the differential, resulting in the axis of the spline hole on the half shaft gear 30 not matching the axis of the through hole 12 for half shaft installation, making it difficult to install the subsequent half shaft. The differential includes: a differential housing 10, a half shaft gear 30, a planetary gear 40, a planetary shaft 50, and a spherical mounting housing 20. A spherical cavity 11 is formed in the differential housing 10, and the spherical mounting housing 20 is arranged in the spherical cavity 11. The half shaft gear 30, the planetary gear 40, and the planetary shaft 50 are all arranged in the spherical mounting housing 20. The central axis of the half shaft gear 30 is perpendicular to the central axis of the planetary gear 40. The half shaft gear 30 meshes with the planetary gear 40, and both the planetary gear 40 and the half shaft gear 30 are bevel gears. There are two half shaft gears 30, and there are also two planetary gears 40. The two half shaft gears 30 are coaxially arranged, and the two planetary gears 40 are also coaxially arranged. The two planetary gears 40 are respectively sleeved at both ends of the planetary shaft 50, and the planetary gear 40 is rotatably connected to the planetary shaft 50.

[0066] Since the structure of the planetary shaft 50 is well known to those skilled in the art, it will not be described in detail here.

[0067] To facilitate understanding of the structure of the differential in this embodiment, the differential housing 10 and the spherical mounting housing 20 will be described separately as follows:

[0068] Please refer to Figure 3 and Figure 4 , Differential housing 10: Through holes 12 for half shaft installation are provided at both ends of the differential housing 10, and the subsequent half shafts are installed in the through holes 12 for half shaft installation. A spherical cavity 11 and two windows 13 for receiving lubricating oil are formed in the differential housing 10. The two windows 13 are located on both sides of the spherical cavity 11, and both windows 13 communicate with the spherical cavity 11. The two windows 13 are symmetrically arranged to ensure that the overall force and weight of the differential housing 10 are uniform, enabling the differential housing 10 to rotate stably. When the differential rotates, the lubricating oil is carried by the differential and adheres to the differential. When the centrifugal force is greater than the adhesion force, the oil is thrown onto the inner wall of the reducer housing (not shown in the figure), and then flows into the spherical cavity 11 through the window 13. The central axis of the spherical cavity 11 coincides with the central axis of the window 13. Taking the direction from one window 13 to the other window 13 as the projection direction, the projected area of the spherical cavity 11 is larger than the projected area of the window 13, and the image projected by the window 13 is located inside the projected figure of the spherical cavity 11, which plays a role in restricting the rotation of the spherical mounting housing 20 around the axis of the through hole 12 for half shaft installation and positioning the installation of the half shaft mounting housing.

[0069] On the outside of the differential housing 10, there is a ring of mounting platforms 14 coaxial with the half-shaft mounting through holes 12. A number of mounting holes 141 are provided on the mounting platforms 14, and the mounting holes 141 are used to connect with other external devices. At one end of the mounting platform 14 facing away from the spherical mounting housing 20, there are a number of reinforcing ribs. The number of reinforcing ribs is arranged in a circular pattern with the central axis of the mounting platform 14 as the axis, enhancing the overall strength of the reducer housing, sharing the force received to each part of the reducer housing, and avoiding excessive force on a certain part of the reducer housing, resulting in damage.

[0070] Please refer to Figure 2 and Figure 5 , spherical mounting housing 20: The spherical mounting housing 20 is arranged in the spherical cavity 11. The shape of the spherical mounting housing 20 matches the shape of the spherical cavity 11, that is, the outer wall of the spherical mounting housing 20 is in mating contact with the inner wall of the spherical cavity 11. Also, due to the internal structure of the aforementioned spherical cavity 11, when the spherical mounting housing 20 is installed, it can be directly placed into the spherical cavity 11, directly positioned and placed, which has a certain anti-mistake function.

[0071] The spherical mounting housing 20 includes: a half-shaft portion 21 and a planetary portion 22. There are two half-shaft portions 21 and two planetary portions 22. The central axis of the half-shaft portion 21 is perpendicular to the central axis of the planetary portion 22. A half-shaft hole is provided on the half-shaft portion 21, and a planetary hole is provided on the planetary shaft 50. The half-shaft hole is used for the installation of the half-shaft, and the planetary hole is used for the installation of the planetary shaft 50. A fixing ring 23 is provided on the half-shaft portion 21 in the direction away from the center of the spherical mounting housing 20. The fixing ring 23 is used to limit the rotation of the spherical mounting housing 20 in the spherical cavity 11 and fix the spherical mounting housing 20 in the spherical cavity 11. One end of the fixing ring 23 facing the inside of the spherical mounting housing 20 is communicated with the half-shaft hole, and the other end is communicated with the half-shaft mounting through hole 12. The half-shaft sequentially passes through the half-shaft mounting through hole 12, the fixing ring 23, and the half-shaft hole and is fixed on the differential housing 10. The half-shaft portion 21 is recessed in the direction away from the center of the spherical mounting housing 20, and the planetary portion 22 is recessed in the direction away from the center of the spherical mounting housing 20. The recess of the half-shaft portion 21 matches the end of the half-shaft gear 30 away from the teeth, and the recess of the planetary portion 22 matches the end of the planetary gear 40 away from the teeth. Both the half-shaft portion 21 and the planetary portion 22 can act as washers to protect the inner wall of the differential housing 10, the planetary gear 40, and the half-shaft gear 30. At the same time, because both the half-shaft portion 21 and the planetary portion 22 have recesses, they play a role in positioning and a certain fixing role for the planetary gear 40 and the half-shaft gear 30.

[0072] Please refer to Figure 5 and Figure 6A first circumferential securing rib 211 is also provided around the circumference of the axle portion 21. The first circumferential securing rib 211 is located at the end facing away from the axle hole and is coaxial with the axle portion 21 and the axle gear 30. A second circumferential securing rib 31 is provided at the end of the axle gear 30 facing away from the tooth meshing. When the axle gear 30 is placed on the axle portion 21, the first circumferential securing rib 211 and the second circumferential securing rib 31 form a clearance fit, wrapping around the second circumferential securing rib 31 and restricting the rotational direction of the axle gear 30. The fit between the first and second circumferential securing ribs 211, 31 also helps store lubricant, retaining some lubricant for an extended period between the first and second circumferential securing ribs 211, ensuring lubrication between the axle gear 30 and the spherical mounting housing 20. When the differential is being transported or in other working situations, the movement of the side gear 30 is restricted by the first circumferential fixing rib 211 and the second circumferential fixing rib 31, so that the side gear 30 can only rotate along the trajectory of the first circumferential fixing rib 211, preventing the side gear 30 from rotating in other directions, such as rotating around the planetary shaft 50 with the planetary shaft 50 as the rotation axis, causing the side gear 30 to shift and misalign within the spherical mounting housing 20, and the center axis of the side gear 30 no longer coincides with the center axis of the side gear mounting through hole 12. During the subsequent installation of the side shaft, if the center axis of the side gear 30 and the side shaft mounting through hole 12 do not coincide, the installation of the side shaft will become more difficult and troublesome. Therefore, a clearance fit is provided between the first circumferential fixing rib 211 and the second circumferential fixing rib 31 to fix the rotation direction of the side gear 30, which can solve the problem of the side gear 30 shifting.

[0073] Working principle of embodiment 1 of the present invention:

[0074] During the installation of the differential, first, the spherical mounting housing 20 is positioned and installed in the spherical cavity 11. Then, the planet gears 40 and the half-axle gears 30 are installed in the spherical mounting housing 20. Through the recesses in the spherical mounting housing 20, the planet gears 40 and the half-axle gears 30 are respectively positioned and installed. The planet gears 40 mesh with the half-axle gears 30. The planet shafts 50 pass through the planet gears 40 and the planet holes, and the planet gears 40 are rotatably connected to the planet shafts 50. When the half-axle gears 30 are installed in the spherical mounting housing 20, a clearance fit is made between the second circumferential fixing ribs 31 formed on the half-axle gears 30 and the first circumferential fixing ribs 211 formed on the half-axle portions 21. The first circumferential fixing ribs 211 wrap the second circumferential fixing ribs 31, so that the half-axle gears 30 can only rotate along the path of the first circumferential fixing ribs 211, ensuring that the half-axle gears 30 do not rotate in a direction deviating from the axis of the half-axle mounting through holes 12 during the transportation or operation of the differential, especially the rotation around the planet shafts 50, so that the central axis of the half-axle gears 30 always coincides with the central axis of the half-axle mounting through holes 12, facilitating the subsequent installation of the half-axles.

[0075] Embodiment 2

[0076] Please refer to Figure 7 and Figure 8 , the differential with uniform force in Embodiment 2 of the present invention is improved on the basis of Embodiment 1.

[0077] Specifically, the planetary gear 40 is improved: The planetary gear 40 is sleeved on the planetary shaft 50 and is rotatably connected to the planetary shaft 50 to achieve differential adjustment of the wheels. A spiral planetary oil guide groove 41 is provided on the inner hole wall of the planetary gear 40. The spiral planetary oil guide groove 41 can enable the lubricating oil to flow along the groove, and can enable the lubricating oil to repeatedly pass through the mating surface between the planetary gear 40 and the planetary shaft 50, continuously taking away the heat generated by the rotational friction between the planetary shaft 50 and the planetary gear 40, achieving the effect of cooling and preventing sintering. At the same time, when the lubricating oil repeatedly passes through the mating surface, an oil film will also be formed on the mating surface to reduce the frictional force between the planetary shaft 50 and the planetary gear 40 and reduce the wear rate. When the planetary gear 40 rotates in the first direction, the planetary oil guide groove 41 guides the lubricating oil attached to the planetary shaft 50 from the hollow cavity to the outside of the differential housing 10; when the planetary gear 40 rotates in the second direction, the planetary oil guide groove 41 guides the lubricating oil outside the differential housing 10 or at both ends of the planetary shaft 50 to the middle of the planetary shaft 50. It can be seen from this that by utilizing the spiral characteristics, the lubricating oil can be regularly guided in the flowing direction according to the rotation direction of the planetary gear 40, and the mating surface between the planetary gear 40 and the planetary shaft 50 is fully covered. The first direction refers to the direction in which the spiral direction of the planetary oil guide groove 41 is consistent with the rotation direction of the planetary gear 40 when viewed axially from the center of the spherical cavity 11 along the planetary shaft 50 towards the outside of the differential housing 10; the second direction refers to the direction in which the spiral direction of the planetary oil guide groove 41 is opposite to the rotation direction of the planetary gear 40 when viewed axially from the center of the hollow cavity along the planetary shaft 50 towards the outside of the differential housing 10.

[0078] The remaining structures and working principles of Embodiment 2 are the same as those of Embodiment 1.

[0079] Embodiment 3

[0080] Please refer to Figure 9 and Figure 10 , the anti-sintering oil guiding structure for the differential in Embodiment 3 of the present invention is improved on the basis of Embodiment 1.

[0081] Specifically, a planetary shaft sleeve 60 is sleeved on the inner hole of the planetary gear 40. The planetary shaft sleeve 60 is fixedly sleeved on the inner hole of the planetary gear 40, and the fixing method is preferably a detachable fixing method, such as bolts and nuts. A shaft sleeve through hole is provided at the center of the planetary shaft sleeve 60. The shaft sleeve through hole is matched with the planetary shaft 50, and the planetary shaft sleeve 60 is sleeved on the planetary shaft 50. The planetary shaft 50 and the planetary shaft sleeve 60 can rotate relative to each other. An oil groove of the shaft sleeve is provided on the inner wall of the shaft sleeve through hole of the planetary shaft sleeve 60. The oil groove of the shaft sleeve is spiral and extends from one end of the shaft sleeve through hole to the other end. The length of the shaft sleeve through hole is equal to the length of the inner hole of the planetary gear 40 or the length of the shaft sleeve through hole is greater than the length of the inner hole of the planetary gear 40, so as to ensure that the lubricating oil can completely cover the length of the planetary shaft 50 where the planetary gear 40 is located, and prevent the planetary shaft 50 from directly contacting the planetary gear 40, resulting in wear and damage of the planetary gear 40. When the lubricating oil flows into the planetary shaft sleeve 60, the planetary shaft sleeve 60 rotates with the planetary gear 40, and the lubricating oil moves along the spiral oil groove of the shaft sleeve. An oil film will be formed where the lubricating oil passes and adheres to the surface of the planetary shaft 50, lubricating the planetary shaft 50, reducing the friction force and taking away the heat generated between the planetary shaft 50 and the planetary shaft sleeve 60, preventing sintering.

[0082] When there is no lubricating oil in the differential case 10 or there is no lubricating oil between the planetary shaft sleeve 60 and the planetary shaft 50, the planetary shaft sleeve 60 can play a protective role again. The planetary shaft 50 will rub against the planetary shaft sleeve 60. Under some extreme working conditions with too high differential rates, it will cause the heat generation between the planetary shaft 50 and the planetary shaft sleeve 60 to rise sharply and sintering will occur. However, because it is the contact between the planetary shaft sleeve 60 and the planetary shaft 50 and sintering occurs, the planetary gear 40 will not be damaged. When performing vehicle maintenance, only the planetary shaft sleeve 60 needs to be replaced, and there is no need to replace the entire planetary gear 40 and the planetary shaft 50, or even the entire differential. At the same time, as mentioned above, the connection between the planetary shaft sleeve 60 and the planetary gear 40 is detachable, which is also for the convenience of subsequent damage replacement. Compared with directly lubricating the contact between the planetary gear 40 and the planetary shaft 50, the solution of this embodiment has an additional layer of insurance, which can effectively prevent the sudden situation of no lubricating oil and save the maintenance cost.

[0083] The rest of the structure and working principle of Embodiment 3 are the same as those of Embodiment 1.

[0084] Embodiment 4

[0085] The anti-sintering oil guiding structure for the differential in Embodiment 4 of the present invention is improved on the basis of Embodiment 2.

[0086] Specifically, a number of shaft groove oil holes for storing spare lubricating oil are provided in the planetary oil guide groove 41. The number of shaft groove oil holes are arranged in sequence along the spiral direction of the planetary oil guide groove 41, and spare lubricating oil is injected into each of the shaft groove oil holes; a number of planetary oil holes pre-injected with lubricating oil are also provided on the surface of the planetary shaft 50. The arrangement path of the number of planetary oil holes is spiral, and the arrangement path is the same as the spiral shape of the planetary oil guide groove 41, which is conducive to the lubricating oil in the planetary oil holes flowing out smoothly and directly into the planetary oil guide groove 41 for lubrication. When the planetary shaft 50 and the planetary gear 40 are operating normally and the temperature is normal, the oil outlet ends of each shaft groove oil hole and each planetary oil hole are in a closed state, preventing the lubricating oil that has been used for lubrication from flowing into the shaft groove oil holes or the planetary oil holes, resulting in the mixing of new oil and old oil and affecting the lubrication and cooling effect. At the same time, through the setting of the closed state, it can also prevent the oil in the planetary oil holes and the shaft groove oil holes from flowing out when there is sufficient lubricating oil between the planetary gear 40 and the planetary shaft 50, resulting in no lubricating oil in the planetary oil holes and the shaft groove oil holes when there is no continuous inflow of lubricating oil into the subsequent differential housing 10. Since the planetary gear 40 and the planetary shaft 50 need to withstand relatively large torque and high strength, nodular cast iron material is preferably used. The closed joints at the oil outlet ends of the planetary oil holes and the shaft groove oil holes are affected by thermal expansion and contraction and open and close. Some small pits are provided on the inner walls of the planetary oil holes and the shaft groove oil holes to enhance the adhesion of the lubricating oil in the planetary oil holes and the shaft groove oil holes and prevent the lubricating oil in the planetary oil holes and the shaft groove oil holes from flowing out.

[0087] When lubricating oil is normally supplied to the differential case 10 and lubricating oil continuously flows in and out between the planetary shaft 50 and the planetary gear 40, the differential operates normally, heat is continuously carried away by the lubricating oil, and an oil film is continuously formed between the planetary shaft 50 and the planetary gear 40 to reduce friction. The oil outlet ends of the planetary oil hole and the shaft groove oil hole are both in a closed state; when there is insufficient lubricating oil in the differential case 10 or the lubricating oil cannot continuously flow in and out between the planetary shaft 50 and the planetary gear 40, in some extreme working conditions, such as driving on icy roads or continuous turns or sharp turns, the differential rate is too high, the friction between the planetary gear 40 and the planetary shaft 50 increases, and the overall temperature in the differential case 10 rises sharply, especially the heat between the planetary gear 40 and the planetary shaft 50 increases sharply. At this time, due to the rapid increase in heat and temperature, the oil outlet ends of the shaft groove oil hole and the planetary oil hole change from a closed state to an open state due to thermal expansion and contraction. Since there is no lubricating oil in the planetary oil guide groove 41, the flow of lubricating oil in the planetary oil holes and shaft groove oil hole is not hindered. The lubricating oil in the shaft groove oil hole and the planetary oil hole flows into the planetary oil guide groove 41 by gravity or centrifugal force, lubricating the planetary shaft 50 and the planetary gear 40, forming an oil film between the planetary shaft 50 and the planetary gear 40, reducing friction and carrying away heat through the lubricating oil in the planetary oil guide groove 41, thereby preventing sintering. At the same time, after the heat is taken away, the temperature drops, and the planetary oil holes and the shaft groove oil holes will shrink to a certain extent, but because they are made of cast iron, they will not close completely, and the speed at which the lubricating oil flows out will be slowed down. The lubricating oil is continuously delivered to the planetary oil guide groove 41, and the normal lubrication state between the planetary shaft 50 and the planetary gear 40 is prolonged as much as possible, so that the vehicle can maintain normal operation for as long as possible until the lubricating oil is replenished later.

[0088] Specifically, the vertical distance between the middle portion of the inner hole of the planetary gear 40 and the central axis of the inner hole is smaller than the vertical distance between the two end portions of the inner hole of the planetary gear 40 and the central axis of the inner hole, so that the contact area between the planetary gear 40 and the planetary shaft 50 is increased, thereby reducing the stress on the two ends of the planetary gear 40, which is beneficial to enhancing the strength of the planetary gear 40 and the planetary shaft 50 and increasing their service life.

[0089] The rest of the structure and working principle of Example 4 are the same as those of Example 1.

[0090] Example 5

[0091] like Figure 18This embodiment provides a four-speed transmission shifting device for shifting four gears. This device can also be used in the transmission described in Example 1. For ease of description, these four gears are divided into two groups: a first group and a second group, each group consisting of two gears. 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.

[0092] like Figure 19 and Figure 20 As shown, the shift drum 1 is provided with a guide groove 110 extending along its circumferential direction, and the guide groove 110 includes a shift area 112 which rotates to different angular positions as the shift drum 1 rotates;

[0093] like Figure 18 As shown, the shift drum 1 can be set to a cylindrical shape, 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.

[0094] like Figure 21 As shown, the first synchronizer is used to participate in the gear shifting operation of the first group of gears. The first synchronizer can be connected to the input shaft or the output shaft in synchronous rotation; the first synchronizer is provided with a gear shifting component, which can move along the axial direction of the first synchronizer under the action of an external force (for example, under the shifting of a shift fork). When the gear shifting component of the first synchronizer moves to fully engage with the gear of a certain gear, the first synchronizer rotates synchronously with the gear. At this time, the power of the input shaft can be transmitted to the gear through the first synchronizer, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the first synchronizer and the input shaft or the output shaft rotate synchronously.

[0095] The first driving mechanism 3 is slidably connected to the guide groove 110 at the first angular position 120 of the shift drum 1. The first driving mechanism 3 is used to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to a first axial position to engage a gear, or to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to a second axial position to engage a gear, wherein the first axial position and the second axial position are different.

[0096] The first axial position refers to the position where the gear-shifting component of the first synchronizer is fully engaged with one of the gears in the first set of gear positions and causes the gear to rotate synchronously therewith. The second axial position refers to the position where the gear-shifting component of the first synchronizer is fully engaged with another gear in the first set of gear positions and causes the gear to rotate synchronously therewith. The aforementioned gear-shifting component may be the synchronizing ring of the first synchronizer.

[0097] As the shift drum 1 rotates, the shift area 112 can rotate to an angular position range that is slidably connected to the first driving mechanism 3. Within this angular position range, as the shift drum 1 rotates, the position of the shift area 112 connected to the first drive also continuously changes. Since the distances of the various positions of the shift area 112 from the first synchronizer in the axial direction are different, the shift area 112 can drive the first driving mechanism 3 to move in the axial direction during rotation. While the first driving mechanism 3 moves in the axial direction, it also pushes the gear-shifting component of the first synchronizer to move in the axial direction.

[0098] 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 respectively connected to the first sliding member 310 and the first shift fork 32, and the first sliding member 310 slides along the guiding groove 110.

[0099] Wherein the width of the guiding groove is slightly larger than the width of the first sliding member 310, and the movement direction of the first connecting member 33 is restricted, and it can only move in the axial direction. Looking along the axial direction of the shift drum 1, in some areas, the distances of the guiding groove 110 from the first synchronizer or the second synchronizer 4 at different circumferential positions are different. When the shift drum 1 rotates, different positions of the guiding groove 110 come into contact with the first sliding member 310. The sliding member slides relative to the guiding groove 110 in the circumferential direction while also moving back and forth in the axial direction under the drive of the guiding 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 with the first sliding member 310 in the axial direction. The first connecting member 33 can be arranged on the side surface in the radial direction of the shift drum 1. The first sliding member 310 is arranged in 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 opposite end is inserted into the guiding groove 110.

[0100] Such as Figure 18 and Figure 22As shown, the second synchronizer 4 is used to participate in the gear operation of the second group of gears. The second synchronizer 4 can be connected to the input shaft or the output shaft for synchronous rotation. The second synchronizer 4 is provided with a gear engaging component, which can move along the axial direction of the second synchronizer 4 under the action of an external force (for example, under the shifting of a shift fork). When the gear engaging component of the second synchronizer 4 moves to fully engage with the gear of a certain gear, the second synchronizer 4 rotates synchronously with the gear. At this time, the power of the input shaft can be transmitted to the gear through the second synchronizer 4, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the second synchronizer 4 and the input shaft or the output shaft rotate synchronously.

[0101] The second driving mechanism 5 is slidably connected to the guide groove 110 at the second angular position 130 of the shift drum 1. The second driving mechanism 5 is used to push the gear engaging component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the third axial position to engage gear, or to push the gear engaging component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the fourth axial position to engage gear, under the drive of the shift zone 112. The third axial position is different from the fourth axial position, and the second angular position 130 is different from the first angular position 120.

[0102] The third axial position refers to the position at which the shifting component of the second synchronizer 4 is fully engaged with the gear of one of the second gear positions and rotates synchronously therewith. The fourth axial position refers to the position at which the shifting component of the second synchronizer 4 is fully engaged with the gear of another gear position in the second gear position and rotates synchronously therewith. The shifting component may be a synchronizer ring of the second synchronizer 4.

[0103] As the shift drum 1 rotates, the shift zone 112 can rotate to a range of angular positions where it is slidably connected to the second drive mechanism 5. Within this angular position range, the position of the shift zone 112 in contact with the second drive mechanism 5 continuously changes as the shift drum 1 rotates. Because the axial distances between the shift zone 112 and the second synchronizer 4 vary at different positions, the shift zone 112 can drive the second drive mechanism 5 to move axially during rotation. This axial movement of the second drive mechanism 5 simultaneously pushes the engaging component of the second synchronizer 4 to move axially.

[0104] In this embodiment, the second driving mechanism 5 includes a second sliding member 51 , a second shift fork 52 and a second connecting member 53 . The second connecting member 53 is connected to the second sliding member 51 and the second shift fork 52 , respectively. The second sliding member 51 slides along the guide groove 110 .

[0105] The width of the guide groove is slightly larger than that of the second slider 51, constraining the movement of the second connecting member 53 to axial movement. Viewed along the axial direction of the shift drum 1, the guide groove 110 has varying distances from the first synchronizer or the second synchronizer 4 at different circumferential locations in some areas. As the shift drum 1 rotates, the guide groove 110 contacts the second slider 51 at different locations. While sliding circumferentially relative to the guide groove 110, the slider also moves back and forth axially, driven by the guide groove 110. Because the second connecting member 53 connects the second slider 51 and the second shift fork 52, the second shift fork 52 also moves axially in sync with the second slider 51. The second connecting member 53 can be positioned on a radially lateral surface of the shift drum 1. The second slider 51 is positioned radially along the shift drum 1. One end of the second slider 51 is connected to the second connecting member 53, while the other end is embedded in the guide groove 110.

[0106] like Figure 18 As shown, the motor 6 is used to drive the shift drum 1 to rotate so that the shift area 112 drives the first drive mechanism 3 and the second drive mechanism 5 to move back and forth in the axial direction of the shift drum 1. The motor 6 and 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.

[0107] In this embodiment, the motor 6 and the two drive mechanisms are separated in the axial direction so that they are located on both sides of the shift drum 1. In this way, the actions of the motor 6 and the drive mechanisms do not affect each other, and the coaxial arrangement of the motor 6 and the shift drum 1 can make the structure more compact and also utilize the power transmission between the motor 6 and the shift drum 1.

[0108] As a preferred embodiment, in this embodiment, the four-speed transmission shifting device further includes a rotating shaft 7. The shift drum 1 has an interference fit with the rotating shaft 7. The motor 6 drives the rotating shaft 7 to rotate, thereby driving the shift drum 1. The direct interference fit between the rotating shaft and the shift drum 1 facilitates transmission, making the transmission process simpler and more reliable. 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, and the rotating shaft 7 is rotatable on the housing.

[0109] like Figure 23 As shown, in this embodiment, an annular limiting groove is provided on the peripheral wall of the first synchronizer and / or the second synchronizer 4, and a shifting member 325 is provided at the end of the first shift fork 32 and / or the second shift fork 52. The shifting member 325 shifts the gear engaging component of the first synchronizer and / or the second synchronizer 4 by shifting the side wall of the limiting groove.

[0110] In this embodiment, the width of the limiting groove is greater than 1.1 times the width of the toggle member 325, the distance between the first axial position and the second axial position is greater than twice the axial gap between the toggle member 325 and the limiting groove, and the distance between the first axial position and the second axial position is greater than twice the axial gap between the toggle member 325 and the limiting groove. With the aforementioned structure, after the toggle member 325 is inserted into the limiting groove and the synchronizer's gear engaging component is toggled to the gear engaging position, one side of the toggle member 325 contacts one sidewall of the limiting groove, while the other side of the toggle member 325 remains sufficiently clear of the other sidewall of the limiting groove. This prevents the toggle member 325 from shifting the limiting groove due to unexpected small vibrations, causing the gear engaging component to disengage from the current gear position, thereby ensuring more reliable gear engagement. When shifting gears normally, the distance that the toggle member 325 moves in the axial direction must exceed the axial gap between the toggle member 325 and the limiting groove. Therefore, during the shifting movement, the other side of the toggle member 325 can also push the shifting component to move by contacting the other side wall of the limiting groove.

[0111] When the toggle 325 toggles the synchronizer to shift gears, the toggle 325 contacts the synchronizer, and the synchronizer is in high-speed rotation, and relative motion occurs between the toggle 325 and the synchronizer. Therefore, there is continuous sliding friction between the toggle 325 and the synchronizer. Both the toggle 325 and the synchronizer are prone to wear and deformation, and the heat generated by friction will also affect the gearbox. To this end, replaceable wear-resistant parts can be set on the toggle 325 to allow the wear-resistant parts to contact the synchronizer. When the wear-resistant parts are worn to a certain extent, new wear-resistant parts can be replaced. When this method is used, the gearbox needs to be disassembled and assembled before the wear-resistant parts can be replaced, so it is very inconvenient during actual use.

[0112] To this end, an oil guide groove can be set on the first shift fork 32, and the outlet of the oil guide groove can be set 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.

[0113] In addition, rollers or needle rollers can be set on the shifting member 325 to reduce friction. However, since the roller contacts the synchronizer in point contact and the needle roller contacts the synchronizer in line contact, the contact areas of these two contact methods are very small, which can easily cause the synchronizer and the shift fork to be subjected to excessive force.

[0114] In this regard, this embodiment adopts a structure that can make the toggle member 325 rotate synchronously with the synchronizer to avoid friction. Figure 26As shown, the first shift fork 32 of this embodiment also includes a cylindrical first rotating member 321, a second rotating member 322, a third rotating member 323 and a fourth rotating member 324, and 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, and 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, and the same intersection 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, and the first plane and the second plane are arranged along the axial direction of the first synchronizer. The shifting member 325 is a rotating belt 326. One end of the rotating belt 326 passes sequentially around the outer walls of the first rotating member 321, the second rotating member 322, the third rotating member 323, and the fourth rotating member 324 before connecting to the opposite end. The rotating belt 326 may be a steel belt or a leather belt. In practice, the rotating belt 326 is tightened and wrapped around the outer walls of the four rotating members, connecting end to end to form a ring. When unfolded, the rotating belt 326 has an arc shape. If the distance between the first rotating member 321 and the second rotating member 322 is too long, a fifth rotating member may be provided between the first rotating member 321 and the second rotating member 322 to provide support for the rotating belt 326 in the middle. If the distance between the third rotating member 323 and the fourth rotating member 324 is too long, a fifth rotating member may be provided between the first rotating member 321 and the second rotating member 322 to provide support for the rotating belt 326 in the middle. The fifth and sixth rotating members may be provided in plurality, and their number may be determined by 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 may be rotatably connected to the first shift fork 32 via a smooth rotating shaft.

[0115] After adopting the above structure, when the rotating belt 326 moves with the first shift fork 32 to the position of contacting the synchronizer, the rotating belt 326 rotates under the drive of the synchronizer. The rotation direction of the rotating belt 326 is as follows: Figures 8 to 10As shown by the arrow direction in []. When the rotating belt 326 just comes into contact with the synchronizer at the initial stage, there will be sliding friction between the rotating belt 326 and the synchronizer. After the rotating belt 326 and the synchronizer reach the same rotational speed, there is no relative sliding between the rotating belt 326 and the synchronizer, and no sliding friction will occur to cause wear of the rotating belt 326 and the synchronizer. At this time, the rotating belt 326 rotates cyclically around the four rotating parts in sequence under the drive of the synchronizer. The contact mode between the rotating belt 326 and the synchronizer is surface contact, which is not prone to the situation of over-concentrated force, and the rotating belt 326 can always rotate synchronously with the synchronizer.

[0116] This embodiment also provides another implementation manner to solve the foregoing sliding friction problem. The first shift fork 32 further includes multiple sets of rotating components. Each set of rotating components includes a seventh rotating part, an eighth rotating part and a rotating belt 326. The seventh rotating part and the eighth rotating part are rotatably connected to the first shift fork 32. One end of the rotating belt 326 sequentially bypasses the outer walls of the seventh rotating part and the eighth rotating part and then is connected to the opposite end. The axes of the seventh rotating part and the eighth rotating part are parallel to each other. The eighth rotating part and the ninth rotating part are axially symmetrically arranged, and their axis of symmetry serves as the axis of symmetry of the rotating component. The extension lines of the axes of symmetry of each set of rotating components intersect at the same intersection point, and the intersection point is located on the rotation axis of the first synchronizer.

[0117] 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 the four rotating parts. Since the extension line of the axis of symmetry of the rotating component is located on the rotation axis of the first synchronizer, when the rotating belt 326 moves with the first shift fork 32 to the position in contact with the synchronizer, the rotation directions of the rotating belts 326 of each rotating component are almost the same as the rotation directions at the corresponding positions on the synchronizer, and the sliding friction between the rotating belts 326 of each rotating component and the synchronizer is very small. By adopting the foregoing method, the structure is simple, and each set of rotating components can be arranged in parallel, which is convenient for installation, realizes surface contact, and reduces sliding friction.

[0118] The four-speed shift device of the transmission in this embodiment can drive the shift drum 1 to rotate by using the motor 6. When the shift area 112 of the shift drum 1 rotates to the position connected to the first driving mechanism 3, the shift area 112 can rotate with the shift drum 1 and push the first synchronizer to perform the gear shifting operations of two gears through the first driving mechanism 3; when the shift area 112 of the shift drum 1 rotates to the position connected to the second driving mechanism 5, the shift area 112 can rotate with the shift drum 1 and push the second synchronizer 4 to perform the gear shifting operations of the other two gears through the second driving mechanism 5; since the areas where the first driving mechanism 3 and the second driving mechanism 5 are connected to the shift drum 1 are at different angular positions, only one shift drum 1 and two driving mechanisms can respectively perform the gear shifting of two gears, and the gear shifting operations of the aforementioned four gears can be completed only by driving one shift drum 1 to rotate with one motor 6. Therefore, there are fewer shift execution mechanisms, the gear shifting action is simple, and the operation is more reliable.

[0119] Embodiment 6

[0120] As Figure 11 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;

[0121] Wherein the first transmission structure 420 is arranged on the flange body 410, and the first transmission structure 420 is used to be connected to the output shaft of the differential and transmit the torque of the differential to the flange body 410;

[0122] As Figure 12 and Figure 14 shown, the output shaft of the differential is connected to the flange body 410 through the first transmission structure 420. When the output shaft of the differential rotates, the torque of the output 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.

[0123] Wherein the first connection structure 430 is arranged on the flange body 410, and the first connection structure 430 is used to connect the flange body 410 to the transmission shaft; [[ID=2...]]

[0124] In this embodiment, the first connection structure 430 only plays a connecting role. The first connection structure 430 connects the flange body 410 to the transmission shaft to prevent the transmission shaft from becoming loose from the flange body 410.

[0125] The second transmission structure 440 is disposed at one end of the flange main body 410 facing the transmission shaft. The second transmission structure 440 is configured to transmit the torque of the flange main body 410 to the transmission shaft and prevent the torque from being transmitted to the first connection structure 430.

[0126] When the flange main body 410 rotates driven by the differential output shaft, the torque of the flange main body 410 is transmitted to the transmission shaft through the second transmission structure 440. During the process of the flange main body 410 driving the transmission shaft to rotate, the second transmission structure 440 is responsible for bearing the transmitted torque. And the second transmission structure 440 is also used to prevent the torque from being transmitted to the first connection structure 430. In this way, during the process of the flange transmitting torque to the transmission shaft, the first connection structure 430 will not be affected by the torque, so it is not easily damaged, and it can ensure that the first connection structure 430 can always connect the flange main body 410 and the transmission shaft, thereby improving the safety of the flange connection, and the number of the first connection structures 430 can be reduced to simplify the structure and reduce the cost.

[0127] As a preferred embodiment, in this embodiment, the second transmission structure 440 is a rectangular tooth. The rectangular tooth is disposed on the end face of the flange main body 410 connected to the transmission shaft. The rectangular tooth on the flange main body 410 is used to cooperate with the rectangular tooth on the transmission shaft to transmit torque.

[0128] The rectangular tooth is in a long strip shape, and the cross section of the rectangular tooth is rectangular. In this embodiment, the transmission shaft may be provided with a rectangular tooth that cooperates with the rectangular tooth on the flange main body 410. After the flange main body 410 and the transmission shaft are installed and connected, the end face of the flange main body 410 cooperates with the transmission shaft, and the rectangular tooth on the flange main body 410 is engaged with the rectangular tooth on the transmission shaft. When the flange main body 410 rotates, the rectangular tooth on the flange main body 410 contacts the adjacent rectangular tooth on the transmission shaft, and the rectangular tooth on the flange main body 410 pushes the adjacent rectangular tooth on the transmission shaft, so that the transmission shaft and the flange main body 410 rotate together. The rectangular tooth can be directly machined on the end face of the flange main body 410 by milling. In order to make the flange structure simpler while the rectangular tooth bears the torque, the rectangular tooth is formed by two adjacent tooth grooves, and the tooth groove is recessed from the end face of the flange main body 410 in a direction away from the transmission shaft. Adopting the foregoing structure to form the rectangular tooth can make the top of the rectangular tooth flush with the end face of the flange main body 410, so it does not occupy extra space, and only the material needs to be removed from the original flange main body 410 to form the tooth groove. The rectangular tooth formed in this way and the flange main body 410 are of an integral structure, and have little influence on the original flange main body 410. The overall structure is simple and the load-bearing capacity is strong.

[0129] In this embodiment, the first connection structure 430 is connected to the transmission shaft through a first connecting member; in the rotation direction of the flange, the clearance between the first connecting member and the first connection structure 430 is greater than the clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the transmission shaft.

[0130] Since in the rotation direction of the flange, the clearance between the first connecting member and the first connection structure 430 is greater than the clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the transmission shaft, when the flange is driven, before the first connecting member contacts and is stressed with the first connection structure 430, the rectangular teeth on the flange body 410 first contact the rectangular teeth on the transmission shaft. Due to the blocking of the rectangular teeth on the transmission shaft, there is always a clearance for the cooperation between the first connecting member and the first connection structure 430, so that the torque action between the first connection structure 430 and the first connecting member during transmission can be well avoided. The aforementioned first connecting member can be a bolt, and the first connection structure 430 can be a bolt hole. When the flange body 410 is connected to the transmission shaft, the bolt passes through the bolt hole.

[0131] In this embodiment, multiple groups of transmission structure groups are provided on the flange body 410. Each group of transmission structure groups includes several first transmission structures 420 arranged in parallel with each other. The number of the first connection structures 430 is the same as the number of the transmission structure groups, and the first connection structures 430 correspond to the transmission structure groups one by one. The transmission structure groups are used to prevent torque from being transmitted to the corresponding first connection structures 430.

[0132] As Figure 15 shown, in this embodiment, a plurality of first connection structures 430 can be arranged along the circumferential direction of the flange body 410 to improve the connection reliability. In addition, in this embodiment, the transmission structure groups and the first connection structures 430 are arranged in a one-to-one correspondence. So that each first connection structure 430 has a corresponding transmission structure group for protection, ensuring that in the corresponding first connection structure 430 and the transmission structure group, the transmission structure group preferably bears the torque instead of the first connection structure 430, avoiding the problem that when multiple first connection structures 430 are provided, it cannot be guaranteed that all the first connection structures 430 will not be affected by torque. Each group of transmission structure groups can be provided with a plurality of first transmission structures 420 arranged in parallel with each other. During transmission, each of the first transmission structures 420 in the same group can jointly bear the torque. In this way, the torque acting on the flange is dispersed to each transmission structure group and then further dispersed to each first transmission structure 420, making the torque borne by each first transmission mechanism smaller, while the overall torque that can be borne becomes larger.

[0133] In addition, in the rotational direction, the first connection structure 430 is located at the central position of the corresponding transmission structure group. By adopting the foregoing method, regardless of whether the flange body 410 rotates forward or backward, each first transmission structure 420 in the transmission structure group can be subjected to a torque before contacting the first connection structure 430, thereby ensuring that the torque is not transmitted to the first connection structure 430.

[0134] For example, 6 groups of transmission structure groups can be provided on the flange body 410, and 4 rectangular teeth are provided in each group of transmission structure groups. These 4 rectangular teeth are parallel to each other and are symmetrically arranged with respect to the diameter of the flange body 410 parallel to these four rectangular teeth. The first transmission structure 420 corresponding to this group of rectangular teeth is provided on the axis of symmetry of this group. Among them, the 6 groups of transmission structure groups are evenly distributed in the circumferential direction of the flange body 410, that is, the angles between any two adjacent groups of transmission structure groups among the 6 groups of transmission structure groups are the same, and the interval between two adjacent groups is 60 degrees. It can be understood that the number of the foregoing transmission groups and the number of the first connection structures 430 in each group of transmission structure groups can also adopt other numbers, which are not limited herein.

[0135] In this embodiment, multiple mutually parallel rectangular teeth can be adopted in a group of transmission structure groups, and the length of each rectangular tooth is the same as the radial dimension of the end face of the flange body 410. By adopting the foregoing method, the torque-bearing capacity of each group of transmission structure groups can be further increased without increasing the number of rectangular teeth in each group.

[0136] As Figure 14 shown, in this embodiment, the flange body 410 includes a cylindrical first connection portion 411 and a disc-shaped second connection portion 412. The first connection portion 411 and the second connection portion 412 are arranged along the axial direction of the flange body 410. A through hole penetrating the connection portion is provided on the first connection portion 411. The first transmission structure 420 is a spline, and the spline is provided on the through hole of the first connection portion 411. The first connection structure 430 is provided on the second connection portion 412.

[0137] When the first connection structure 430 adopts rectangular teeth, the rectangular teeth are provided on the disc surface of the second connection portion 412 facing the transmission shaft.

[0138] In this embodiment, the first connection portion 411 is used to realize the connection between the flange body 410 and the differential output shaft, and the second connection portion 412 is used to realize the connection between the flange body 410 and the transmission shaft. In this embodiment, by adopting the method that the first connection portion 411 and the second connection portion 412 are arranged along the axial direction of the flange body 410, the differential output shaft and the transmission shaft are compactly distributed on both sides of the flange in the axial direction, so that the mutual influence between the power input side and the power output side can be avoided.

[0139] In this embodiment, a spline is adopted for transmission on the power input side, and the transmission has a strong load-bearing capacity. A through hole can be machined on the first connecting portion 411 first, and then a spline can be machined on the inner wall.

[0140] In this embodiment, the second transmission structure 440 extends from the inner wall position of the through hole to the outer wall position of the second connecting portion 412 in the radial direction of the second connecting portion 412. In this way, the radial dimension of the disk of the second connecting portion 412 can be fully utilized, so that the length of the rectangular teeth that can bear torque is the longest.

[0141] When the length of the rectangular teeth is relatively long, the deformation amount of the rectangular teeth under the action of torque will increase. When the deformation amount exceeds a certain degree, the insufficient contact between the same rectangular tooth and the rectangular teeth it cooperates with will cause the load-bearing capacity of the rectangular teeth to decrease. For this reason, in this embodiment, each rectangular tooth is composed of a plurality of sub-rectangular teeth with smaller lengths, and there is a break between adjacent two sub-rectangular teeth. After adopting the foregoing method, the deformations of the respective sub-rectangular teeth will not accumulate to other sub-rectangular teeth, so that the deformation amount of the rectangular teeth can be dispersed to each sub-rectangular tooth, and the deformation amount of each sub-rectangular tooth is very small and will not exceed the degree that can cause insufficient contact of the rectangular teeth. The gap between adjacent sub-rectangular teeth can be very small, so the foregoing structure will not significantly reduce the length of the part of the rectangular teeth that can bear torque.

[0142] As Figure 17 shown, in this embodiment, each set of transmission structure groups is composed of two sets of 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 arrangement interval of the rectangular teeth in the two sets of sub-transmission structure groups are equal. Only the two sets of sub-transmission structure groups are staggered with each other in the circumferential direction, and each rectangular tooth is also divided into two mutually disconnected parts and belongs to the two sets of sub-transmission structure groups respectively. By adopting the foregoing method, the deformation amount of the rectangular teeth can be reduced without reducing the total length of the part of the rectangular teeth for bearing torque. After the two sets of sub-transmission structure groups are staggered with each other in the circumferential direction, the force on the flange main body 410 will not be concentrated at the same circumferential position of the flange main body 410, and the deformation of the flange main body 410 is also dispersed to each position in the circumferential direction of the flange main body 410.

[0143] One end of each rectangular tooth in the first sub-transmission structure group 441 extends to the outer wall position of the flange main body 410, so that the milling cutter can remove the material from the outside to the inside of the flange main body 410 at one time to complete the machining of the rectangular teeth, which can significantly improve the machining efficiency.

[0144] In the circumferential direction, the first sub-drive structure group 441 and the second sub-drive structure group 442 can be completely staggered or not completely staggered. When adopting the completely staggered method, the first sub-drive structure group 441 and the second sub-drive structure group 442 partially overlap in the radial direction. The part where the first sub-drive structure group 441 and the second sub-drive structure group 442 are disconnected on the flange main body 410 cannot bear torque, and the force on the parts of the first sub-drive structure group 441 and the second sub-drive structure group 442 close to the disconnection position will also change abruptly, which will affect the service life of the flange. After the first sub-drive structure group 441 and the second sub-drive structure group 442 partially overlap in the radial direction, the part that could not bear torque due to the disconnection of the radial teeth in the radial direction of the original flange main body 410 is eliminated, and the abrupt change in the force on the parts of the first sub-drive structure group 441 and the second sub-drive structure group 442 close to the disconnection position is avoided.

[0145] When adopting the not completely staggered method, the tooth grooves of the rectangular teeth in the first sub-drive structure group 441 can be aligned with the tooth tips of the rectangular teeth in the second sub-drive structure group 442. By adopting the foregoing method, in the same drive structure group, the part for bearing torque in the circumferential direction of the flange main body 410 can be the most, so that the flange main body 410 can bear more torque.

[0146] As Figure 16 shown, in this embodiment, the same drive structure group is composed of three sub-drive structure groups. From the outer wall of the flange main body 410 inward, they are the third sub-drive structure group 443, the fourth sub-drive structure group 444, and the fifth sub-drive structure group 445 in sequence. The rectangular teeth of each drive structure group are disconnected from each other, and the length of the rectangular teeth of the third sub-drive structure group 443 is less than that of the fourth sub-drive structure group 444, and the length of the rectangular teeth of the fourth sub-drive structure group 444 is less than the length of the rectangular teeth of the fifth sub-drive structure group 445. Under the condition of bearing the same torque, the deformation amount of the outer side of the flange main body 410 is larger than that of its inner side. In this embodiment, the structure with the decreasing length of the rectangular teeth from the inside to the outside is adopted, which can reduce the variance of the deformation amount of the rectangular teeth at each radial position of the flange main body 410 and avoid the excessive deformation amount of the rectangular teeth at local positions in the radial direction of the flange main body 410 from affecting the service life of the flange.

[0147] As Figure 13 shown, in this embodiment, a limit hole 4121 for cooperating with the transmission shaft is provided on the second connection part 412. A stop 4122 for restricting the axial position of the transmission shaft is provided at one end of the limit hole 4121 facing the first connection part 411, and the spline extends to the position of the stop 4122.

[0148] During installation, the end of the transmission shaft can be inserted into the limiting hole 4121 of the second connecting part 412 until the end of the transmission shaft abuts against the stop 4122. The output shaft of the gearbox can be inserted into the through hole. Since the spline in the through hole extends to the position of the stop 4122, the distance between the position where the input end transmits torque and the end of the transmission shaft is relatively short. By adopting the foregoing method, the distance between the position where the input end transmits torque and the position where the output end transmits torque can be shortened, thereby reducing the deformation amount of the transmission components between the input end and the output end under the action of torque.

[0149] Embodiment 7

[0150] Embodiment 7 of the present invention discloses a speed reducer, which includes a differential that is evenly stressed in any one of Embodiments 1 to.

[0151] In the speed reducer of Embodiment 7 of the invention, with the above structure, during the installation process of the differential, first, the spherical installation housing 20 is positioned and installed in the spherical cavity 11, and then the planetary gears 40 and the half-axle gears 30 are installed in the spherical installation housing 20. Through the recesses in the spherical installation housing 20, the planetary gears 40 and the half-axle gears 30 are respectively positioned and installed. The planetary gears 40 mesh with the half-axle gears 30. The planetary shafts 50 pass through the planetary gears 40 and the planetary holes, and the planetary gears 40 are rotatably connected to the planetary shafts 50. When the half-axle gears 30 are installed in the spherical installation housing 20, the second circumferential fixing ribs 31 provided on the half-axle gears 30 are in clearance fit with the first circumferential fixing ribs 211 provided on the half-axle part 21. The first circumferential fixing ribs 211 wrap the second circumferential fixing ribs 31, so that the half-axle gears 30 can only rotate along the path of the first circumferential fixing ribs 211, ensuring that the half-axle gears 30 do not rotate in a direction deviating from the axis of the half-axle installation through hole 12 during the transportation process of the differential or during the operation of the differential, especially the rotation around the planetary shafts 50, so that the central axis of the half-axle gears 30 always coincides with the central axis of the half-axle installation through hole 12, facilitating the subsequent installation of the half-axles.

[0152] Embodiment 8

[0153] Embodiment 8 of the present invention discloses a vehicle, which includes any one of the above-mentioned differentials with uniform stress and / or includes the transmission flange and / or the four-speed shift device of the transmission.

[0154] The vehicle in Embodiment 8 of the invention can be a traditional fuel vehicle such as a gasoline vehicle, a diesel vehicle, etc., or a new energy vehicle. The new energy vehicles include, but are not limited to, pure electric (BEV / EV) vehicles, hybrid (HEV, PHEV, and REEV) vehicles, fuel cell vehicles (FCEV), and solar cell vehicles.

[0155] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements on some or all of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A differential with uniform force, characterized in that, The differential includes: A differential housing, within which a spherical cavity and two windows for receiving lubricating oil are provided. The two windows are located on both sides of the spherical cavity, both are in communication with the spherical cavity, and the two windows are symmetrically arranged; A spherical mounting housing, the shape of which matches that of the spherical cavity, and the spherical mounting housing is fixed within the spherical cavity; Axle gears, which are arranged within the spherical mounting housing; Planet gears, which are also arranged within the spherical mounting housing. The planet gears are sleeved on planet shafts, and the planet gears mesh with the axle gears; A first circumferential fixing rib extending along the circumferential direction of the axle gear is provided within the spherical mounting housing, and a second circumferential fixing rib extending along the circumferential direction of the axle gear is provided on the axle gear. The first circumferential fixing rib and the second circumferential fixing rib are in clearance fit to limit the rotation of the axle gear around the axis of the planet gear.

2. The differential with uniform force according to claim 1, wherein The central axes of the spherical cavity and the windows coincide. Taking the direction from one window to the other window as the projection direction, the projected area of the spherical cavity is larger than the projected area of the window.

3. The differential with uniform force according to claim 1, characterized in that, The spherical mounting housing includes: a planet part and an axle part. The central axis of the planet part is perpendicular to the central axis of the axle part. A fixing ring is provided on the axle part in the direction away from the center of the spherical mounting housing, and the fixing ring is used to limit the rotation of the spherical mounting housing around the horizontal axis within the spherical cavity.

4. The differential with uniform force according to claim 3, characterized in that The axle part is recessed in the direction away from the center of the spherical mounting housing, the planet part is recessed in the direction away from the center of the spherical mounting housing, and a planet hole is provided on the planet part.

5. The differential with uniform force according to claim 4, wherein Axle mounting through holes are provided at both ends of the differential housing. A mounting platform coaxial with the axle mounting through holes is provided outside the differential housing. A number of mounting holes are provided on the mounting platform, and the mounting holes are used for connection with other external devices. A number of reinforcing ribs are provided at the end of the mounting platform away from the spherical mounting housing, and the number of reinforcing ribs is arranged in a circle with the central axis of the mounting platform as the axis.

6. The differential with uniform force according to any one of claims 1 to 5, characterized in that A planet shaft sleeve is sleeved on the inner hole of the planet gear. A sleeve through hole is provided at the center of the planet shaft sleeve, and the sleeve through hole is matched with the planet shaft. The planet shaft and the planet shaft sleeve can rotate relative to each other. An oil groove is provided on the inner wall of the sleeve through hole of the planet shaft sleeve.

7. The differential with uniform force according to claim 6, wherein The oil groove of the sleeve is in a spiral shape and extends from one end of the sleeve through hole to the other end.

8. The differential with uniform force according to claim 6, characterized in that, The length of the sleeve through hole is equal to the length of the inner hole of the planet gear or the length of the sleeve through hole is greater than the length of the inner hole of the planet gear.

9. A speed reducer, characterized in that, The reducer includes the differential with uniform force as described in any one of claims 1 to 8.

10. A vehicle, characterized in that, The vehicle includes the differential with uniform force as described in any one of claims 1 to 8 or the reducer as described in claim 9.

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