阅读说明：本技术 差速器用防烧结导油结构、差速器及汽车 (Differential is with preventing sintering oil guide structure, differential and car ) 是由 苏倩 唐亚卓 于 2021-09-29 设计创作，主要内容包括：本发明属于新能源汽车技术领域,解决了现有技术中差速器内行星齿轮与行星轴之间发生烧结的问题,提供了一种差速器用防烧结导油结构、差速器及汽车。该差速器用防烧结导油结构包括具有中空腔体的差速器壳体；半轴锥齿轮,半轴锥齿轮设置在中空腔体内；行星轴,行星轴设置在差速器壳体内；行星齿轮,行星齿轮套设于行星轴上,且行星齿轮与半轴锥齿轮啮合；其中,在行星齿轮的内孔上设有行星导油槽,行星导油槽位于行星齿轮与行星轴之间,行星导油槽用于导流润滑油流经行星轴表面与行星齿轮之间,且将润滑油导流至差速器壳体外部或者导流至差速器内部。本发明通过在行星齿轮上开设行星导油槽,防止烧结的发生,结构简单实用。(The invention belongs to the technical field of new energy automobiles, solves the problem of sintering between a planetary gear and a planetary shaft in a differential in the prior art, and provides an anti-sintering oil guide structure for the differential, the differential and an automobile. The anti-sintering oil guide structure for the differential comprises a differential shell with a hollow cavity; the half shaft bevel gear is arranged in the hollow cavity; the planet shaft is arranged in the differential shell; the planetary gear is sleeved on the planetary shaft and meshed with the half shaft bevel gear; the inner hole of the planetary gear is provided with a planetary oil guide groove, the planetary oil guide groove is positioned between the planetary gear and the planetary shaft, and the planetary oil guide groove is used for guiding lubricating oil to flow between the surface of the planetary shaft and the planetary gear and guiding the lubricating oil to the outside of the differential shell or the inside of the differential. According to the invention, the planetary oil guide groove is formed in the planetary gear, so that sintering is prevented, and the structure is simple and practical.)

1. The utility model provides a differential mechanism is with preventing sintering oil guide structure which characterized in that includes:

a differential housing having a hollow cavity;

a half shaft bevel gear disposed within the hollow cavity;

a planet axle disposed within the differential housing;

the planetary gear is sleeved on the planetary shaft and meshed with the half shaft bevel gear;

the inner hole of the planet gear is provided with a planet oil guide groove, the planet oil guide groove is positioned between the planet gear and the planet shaft, and the planet oil guide groove is used for guiding lubricating oil to flow between the surface of the planet shaft and the planet gear and guiding the lubricating oil to the outside of the differential shell or the inside of the differential;

and a lubricating ring wall is arranged in the hollow cavity and is used for bearing lubricating oil splashed by the rotation of the planetary gear and the half shaft bevel gear.

2. The anti-sintering oil guide structure for the differential according to claim 1, wherein the planetary oil guide groove is formed in a spiral shape, and guides the lubricating oil attached to the planetary shaft from the hollow cavity to the outside of the differential case when the planetary gear rotates in the first direction; when the planet gear takes the second direction as the rotation direction, the planet oil guide groove guides the lubricating oil outside the differential shell or at two ends of the planet shaft to the middle part of the planet shaft.

3. The anti-sintering oil guide structure for a differential gear according to claim 1, wherein said differential case includes: the semi-axis installation through-hole, be equipped with the helical shape semi-axis on the hole of semi-axis installation through-hole and lead the oil groove, with lubricating oil water conservancy diversion extremely in the cavity or water conservancy diversion extremely outside the cavity.

4. The anti-sintering oil guide structure for the differential gear according to claim 3, wherein a gasket groove is provided between the lubricating ring wall and the half shaft mounting through hole, and the gasket groove is used for receiving lubricating oil from the half shaft mounting through hole or the lubricating ring wall.

5. The anti-sintering oil guide structure for the differential gear according to claim 4, wherein the radius of the gasket groove is larger than that of the half shaft mounting through hole, and the radius of the gasket groove is smaller than that of the lubricating ring wall.

6. The differential gear anti-sintering oil guide structure as claimed in claim 5, wherein the lubricating ring wall is further provided with an oil collection groove, and the oil collection groove is communicated with the gasket groove and is used for guiding lubricating oil into the half shaft oil guide groove or receiving lubricating oil from the half shaft oil guide groove.

7. The anti-sintering oil guide structure for the differential gear according to claim 3, wherein a plurality of reinforcing ribs are provided on the outside of the differential case in the circumferential direction of the axle shaft mounting through-hole.

8. The anti-sintering oil guide structure for the differential gear according to claim 2, wherein the planetary oil guide groove is provided with a plurality of planetary oil holes for storing lubricating oil, and the oil outlet ends of the planetary oil holes are opened and closed; the planet shaft is provided with an oil guide shaft groove, the oil guide shaft groove is provided with a plurality of shaft groove oil holes for storing lubricating oil, and the oil outlet end of the shaft groove oil hole is opened and closed.

9. A differential gear, characterized by comprising the anti-sintering oil guide structure for a differential gear according to any one of claims 1 to 8.

10. An automobile characterized by comprising the anti-sintering oil guide structure for a differential gear according to any one of claims 1 to 8 or the differential gear according to claim 9.

Technical Field

The invention belongs to the technical field of new energy automobiles, and particularly relates to an anti-sintering oil guide structure for a differential mechanism, the differential mechanism and an automobile.

Background

In the new energy automobile industry, when an automobile turns or runs on an icy or snowy road surface, in order to ensure the stability of the running, the running stability is generally realized by installing a differential. However, the differential mechanism used by the current new energy automobile basically adopts a planetary system with a simpler structure, the structure can effectively realize the differential function of left and right tires, but under some extreme working conditions, the over-high differential speed can cause the heat productivity in the differential mechanism to rapidly rise, and the sintering between the planetary gear and the planetary shaft is generated, so that the differential function is lost, and the automobile rollover or other safety accidents are even caused in serious cases.

Disclosure of Invention

In view of the above, the invention provides an anti-sintering oil guide structure for a differential, the differential and an automobile, which are used for solving the problem that sintering occurs between a planetary gear and a planetary shaft in the differential under some limit working conditions of the automobile in the prior art.

The technical scheme adopted by the invention is as follows:

in a first aspect, the present invention provides an anti-sintering oil guiding structure for a differential, comprising:

a differential housing having a hollow cavity;

a half shaft bevel gear disposed within the hollow cavity;

a planet axle disposed within the differential housing;

the planetary gear is sleeved on the planetary shaft and meshed with the half shaft bevel gear;

the inner hole of the planet gear is provided with a planet oil guide groove, the planet oil guide groove is positioned between the planet gear and the planet shaft, and the planet oil guide groove is used for guiding lubricating oil to flow between the surface of the planet shaft and the planet gear and guiding the lubricating oil to the outside of the differential shell or the inside of the differential;

and a lubricating ring wall is arranged in the hollow cavity and is used for bearing lubricating oil splashed by the rotation of the planetary gear and the half shaft bevel gear.

As a preferable scheme of the anti-sintering oil guide structure for the differential, the planet oil guide groove is spiral, and when the planet gear rotates in a first direction, the planet oil guide groove guides the lubricating oil attached to the planet shaft from the hollow cavity to the outside of the differential case; when the planet gear takes the second direction as the rotation direction, the planet oil guide groove guides the lubricating oil outside the differential shell or at two ends of the planet shaft to the middle part of the planet shaft.

As a preferable aspect of the above anti-seize oil guide structure for a differential, the differential case includes: the semi-axis installation through-hole, be equipped with the helical shape semi-axis on the hole of semi-axis installation through-hole and lead the oil groove, with lubricating oil water conservancy diversion extremely in the cavity or water conservancy diversion extremely outside the cavity.

As a preferable scheme of the anti-sintering oil guide structure for the differential, a gasket groove is arranged between the lubricating ring wall and the half shaft mounting through hole, and the gasket groove is used for receiving lubricating oil from the half shaft mounting through hole or the lubricating ring wall.

In a preferable embodiment of the above anti-sintering oil guide structure for a differential, the radius of the gasket groove is larger than the radius of the axle shaft mounting through hole, and the radius of the gasket groove is smaller than the radius of the lubrication ring wall.

As a preferable scheme of the anti-sintering oil guide structure for the differential, an oil collecting groove is further formed in the lubricating ring wall, and the oil collecting groove is communicated with the gasket groove and is used for guiding lubricating oil into the half shaft oil guide groove or receiving the lubricating oil from the half shaft oil guide groove.

As a preferable scheme of the anti-sintering oil guide structure for the differential, a plurality of reinforcing ribs arranged along the circumferential direction of the half axle mounting through hole are arranged outside the differential shell.

As a preferred scheme of the anti-sintering oil guide structure for the differential, the planet oil guide groove is provided with a plurality of planet oil holes for storing lubricating oil, and the oil outlet ends of the planet oil holes are opened and closed; the planet shaft is provided with an oil guide shaft groove, the oil guide shaft groove is provided with a plurality of shaft groove oil holes for storing lubricating oil, and the oil outlet end of the shaft groove oil hole is opened and closed.

In a second aspect, the invention provides a differential mechanism, which comprises any one of the anti-sintering oil guiding structures for the differential mechanism.

In a third aspect, the invention provides an automobile, which comprises any one of the anti-sintering oil guiding structures for the differential mechanism or the differential mechanism.

In conclusion, the beneficial effects of the invention are as follows:

according to the anti-sintering oil guide structure for the differential, the differential and the automobile, the planet oil guide groove is formed in the inner hole of the planet gear, the planet oil guide groove is located between the surface of the planet shaft and the planet gear, lubricating oil can be guided to a position between the surface of the planet shaft and the planet gear through the planet oil guide groove, the lubricating oil flows in the planet oil guide groove and passes through the surface of the planet shaft to form a layer of lubricating oil film, a lubricating effect is achieved between the planet gear and the planet shaft, besides, the lubricating oil guided to the position between the planet gear and the planet shaft by the planet oil guide groove can take away heat generated between the planet gear and the planet shaft, and sintering between the planet shaft and the planet gear is avoided.

Drawings

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 described below, and for those skilled in the art, without any creative effort, other drawings may be obtained according to the drawings, and these drawings are all within the protection scope of the present invention.

FIG. 1 is a schematic perspective view showing an oil guide structure for a differential in example 1 of the present invention;

FIG. 2 is an exploded view of FIG. 1;

fig. 3 is a sectional view of the differential case in embodiment 1 of the invention;

FIG. 4 is a schematic structural view of a planetary gear in embodiment 1 of the invention;

fig. 5 is a schematic structural view of a planetary shaft sleeve sleeved on a planetary shaft in embodiment 2 of the present invention;

fig. 6 is a sectional view of a planetary sleeve in embodiment 2 of the invention;

FIG. 7 is a three-dimensional structural view of a driving flange of embodiment 6 of the invention;

FIG. 8 is a three-dimensional structural view of another perspective of a driving flange according to embodiment 6 of the invention;

FIG. 9 is a three-dimensional view of a structure for connecting a driving flange to a driving shaft according to embodiment 6 of the present invention;

FIG. 10 is a side view of a driving flange according to embodiment 6 of the invention;

FIG. 11 is a front view of a driving flange according to embodiment 6 of the invention;

FIG. 12 is a schematic structural view showing a three-group sub transmission structure group disconnection arrangement according to embodiment 6 of the present invention;

fig. 13 is a schematic structural view of two sets of sub-transmission structures of the transmission flange according to embodiment 6 of the present invention, which are arranged in a staggered manner in the circumferential direction;

FIG. 14 is a three-dimensional block diagram of the transmission four speed shift device of the present invention;

FIG. 15 is a graph of the angular position of the shift area of the shift drum of the present invention with the first and second drive mechanisms;

FIG. 16 is a three dimensional block diagram of the shift drum of the present invention;

FIG. 17 is a three-dimensional block diagram of the first drive mechanism of the present invention engaged with a shift drum;

FIG. 18 is a three dimensional block diagram of the first drive mechanism of the present invention engaged with a shift drum;

FIG. 19 is a three-dimensional block diagram of the first drive mechanism of the present invention engaged with a first synchronizer

FIG. 20 is a top view of the structure for allowing the rotating belt to rotate with the synchronizer according to the present invention;

FIG. 21 is a side view of the structure for allowing the rotating belt to rotate with the synchronizer according to the present invention;

FIG. 22 is a view showing the positional relationship of four rotating members according to the present invention;

fig. 23 is a schematic structural view of a vehicle.

Parts and numbering in the drawings:

10. a differential housing; 11. a through hole is arranged on the half shaft; 111. the half shaft oil guide groove; 12. lubricating the annular wall; 13. a gasket groove; 14. an oil sump; 15. an installation table; 151. a flange; 20. a half shaft bevel gear; 30. a planetary gear; 31. a planetary oil guide groove; 40. a planet shaft; 50. a planetary shaft sleeve; 51. an oil groove of the shaft sleeve;

410. a flange body; 411. a first connection portion; 412. a second connecting portion; 4121. a limiting hole; 4122. stopping the opening; 420. a first transmission structure; 430. a first connecting structure; 440. a second transmission structure; 441. a first sub-transmission structure group; 442. a second sub-transmission structure group; 443. a third sub-transmission structure group; 444. a fourth sub-transmission structure group; 445. a fifth sub-transmission structure group;

1. a shift drum; 110. a guide groove; 112. a shift area; 113. a first guide section; 114. a second guide section; 115. a third guide section; 120. a first angular position; 130. a second angular position;

21. a limit groove 21; 3. a first drive mechanism; 310. a first slider; 32. a first shift fork; 33. a first connecting member; 321. a first rotating member; 322. a second rotating member; 323. a third rotating member; 324. a fourth rotating member; 325. a toggle piece; 326. a rotating belt; 5. a second drive mechanism; 510. a second slider; 52. a second fork; 53. a second connecting member; 6. a motor; 7. a rotating shaft;

600. a power system; 700. a transmission system; 800. a vehicle body.

Detailed Description

In order to make the objects, 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 drawings in the embodiments of the present invention. It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element. In case of conflict, the embodiments of the present invention and the various features of the embodiments may be combined with each other within the scope of the present invention.

Referring to fig. 23, a vehicle is a common vehicle, and mainly includes a power system 600, a transmission system 700, a vehicle body 800, a chassis, and the like. The drive train 700 may include a transmission, a propeller shaft, a differential, etc. When the vehicle runs, the power of the power system 600 is transmitted to the transmission, the transmission converts the power of the power system 600 and outputs power with proper torque and rotating speed, the converted power is transmitted to the transmission shaft, the transmission shaft transmits the power to the differential, the differential transmits the power to wheels on two sides, and the converted power can also be transmitted to the differential. In order to achieve parking and gear shifting, the transmission is also provided with a gear shifting device and a parking device. In order to lubricate the devices such as the transmission and the differential, a lubrication system is also provided for the devices such as the transmission and the differential.

Example 1

Referring to fig. 1 to 4, embodiment 1 of the present invention discloses an anti-sintering oil guiding structure for a differential, including: a differential case 10, side bevel gears 20, planetary gears 30, and planetary shafts 40. A hollow cavity is formed in the differential case 10, wherein the half shaft bevel gear 20, the planetary gear 30, and the planetary shaft 40 are all disposed in the hollow cavity. The central axis of the side bevel gear 20 is perpendicular to the central axis of the planetary gear 30, the side bevel gear 20 meshes with the planetary gear 30, and the planetary gear 30 is a bevel gear. Two half bevel gears 20 are provided, and two planetary gears 30 are provided, the two half bevel gears 20 being disposed coaxially, and the planetary gears 30 being disposed coaxially. The two planetary gears 30 are respectively sleeved at two ends of the planetary shaft 40, and the planetary gears 30 are rotatably connected with the planetary shaft 40.

Since the construction of the side bevel gear 20 and the planet shaft 40 is well known to those skilled in the art, it will not be described in detail herein.

To facilitate understanding of the structure of the anti-seize oil guide structure for the differential, the differential case 10 and the planetary gears 30 will now be described separately as follows:

differential case 10: both ends of the differential case 10 are provided with half shaft mounting through holes 11, the inner hole wall of the half shaft mounting through hole 11 is provided with a half shaft oil guide groove 111 for guiding oil, and the half shaft oil guide groove 111 is spiral and extends along the axial direction of the half shaft mounting through hole 11. When the lubricating oil needs to flow into or out of the axle shaft mounting through-hole 11, the lubricating oil flows along the path of the axle shaft oil guide groove 111 as the differential case 10 rotates. Adopt spiral half axle to lead oil groove 111 to more do benefit to the flow of lubricating oil, especially to the higher condition of rotational speed for lubricating oil can flow along with rotating, leads the helical direction of oil groove 111 along the half axle, avoids because of the rotational speed is too high, and centrifugal force is too big, causes lubricating oil to hug closely and leads the cell wall of oil groove and can't fall down late, and the problem of lubricating oil whereabouts difficulty takes place. A lubricating ring wall 12 is arranged in the hollow cavity of the differential case 10, and two lubricating ring walls 12 are arranged, are respectively located at two ends of the hollow cavity, and are coaxially arranged with the half shaft mounting through holes 11 at two ends of the differential case 10. The lubricating ring wall 12 is used for receiving lubricating oil splashed by the rotation of the planetary gear 30 and the rotation of the half-shaft bevel gear 20, and the lubricating oil is guided from the lubricating ring wall 12 at one end of the hollow cavity to the lubricating ring wall 12 at the other end of the hollow cavity, so that the lubricating oil covers the whole inner wall of the hollow cavity as much as possible.

A gasket groove 13 is further formed in the hollow cavity of the differential case 10, and the gasket groove 13 is annular and is coaxial with the half shaft mounting through hole 11. The gasket groove 13 is positioned between the lubricating ring wall 12 and the half shaft mounting through hole 11, and the radius of the gasket groove 13 is larger than that of the half shaft mounting through hole 11 and smaller than that of the lubricating ring wall 12. When the 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 flows into the shim groove 13 communicating therewith along the half shaft oil guide groove 111, and the lubricating oil in the shim groove 13 at the other end flows out of the differential case 10 along the half shaft oil guide groove 111. And half-shaft gaskets are arranged on the gasket grooves 13 at the two ends of the hollow cavity and are used for protecting the half-shaft bevel gear 20 and avoiding transitional abrasion between the half-shaft bevel gear and the inner wall of the differential case 10. Lubricating oil leads oil groove 111 to flow in to gasket groove 13 back through the semi-axis, and lubricating oil just can be full of gasket groove 13 to flow in to between semi-axis gasket and semi-axis bevel gear 20 through the clearance, make semi-axis gasket and semi-axis bevel gear 20 obtain fully lubricated, rotatory semi-axis bevel gear 20, and the produced heat of friction is taken away between the semi-axis gasket, reaches the effect of cooling. When the lubricating oil flows to the gasket groove 13 at the other end of the hollow cavity, the lubricating oil enters between the half shaft gasket and the half shaft bevel gear 20 through the gap between the half shaft gasket and the half shaft bevel gear 20, and the lubricating oil fully covers the half shaft gasket and the half shaft bevel gear 20 through the rotation of the half shaft bevel gear 20, so that the lubricating oil is fully lubricated, the friction is reduced, and meanwhile, the heat generated by the friction is taken away.

An oil collecting groove 14 is further formed in the hollow cavity of the differential case 10, the oil collecting groove 14 is formed in the lubricating annular wall 12, the oil collecting groove 14 is communicated with the gasket groove 13, and a chamfer is formed at the contact position of the oil collecting groove 14 and the lubricating annular wall 12, so that lubricating oil can conveniently flow into the oil collecting groove 14 from the lubricating annular wall 12; the contact part of the oil collecting groove 14 and the gasket groove 13 is also provided with a chamfer, so that the lubricating oil can conveniently flow into the oil collecting groove 14 from the gasket groove 13. Four oil sumps 14 are provided, two of the oil sumps 14 are positioned on one of the lubricating annular walls 12, the other two oil sumps 14 are positioned on the other lubricating annular wall 12, and the two oil sumps 14 on the same lubricating annular wall 12 are arranged in a central symmetry mode, so that lubricating oil can flow into the oil sumps 14 more uniformly.

The differential case 10 is provided with a circle of mounting tables 15 coaxial with the half-shaft mounting through holes 11 outside, the mounting tables 15 are provided with a plurality of flanges 151, the flanges 151 are used for being connected with other external devices, the flanges 151 are provided with six, every three flanges 151 are a group, a connecting rib used for reinforcing the stability and the strength of the mounting tables 15 and the flanges 151 is arranged between the adjacent flanges 151 on each group of flanges 151, one side of the connecting rib departing from the hollow cavity has a certain radian, the connecting rib is better used for being matched with external devices, and a certain guiding effect is installed by butting with the external devices. A plurality of ribs are also provided on the exterior of the differential case 10, also on the mounting table 15 and on the side facing away from the flange 151. The plurality of reinforcing ribs and the half shaft mounting through holes 11 are coaxially and circumferentially arranged and used for increasing the overall strength of the differential and dispersing the received force to a plurality of positions of the differential case 10.

The planetary gear 30: the planetary gear 30 is preferably a bevel gear, which is sleeved on the planetary shaft 40 and is rotationally connected with the planetary shaft 40 to realize differential speed adjustment of the wheels. The spiral planet oil guide groove 31 is formed in the inner hole wall of the planet gear 30, the spiral planet oil guide groove 31 enables lubricating oil to flow along the groove, the lubricating oil can repeatedly pass through the matching surface of the planet gear 30 and the planet shaft 40, heat generated by the rotation friction of the planet shaft 40 and the planet gear 30 is continuously taken away, and the effects of cooling and preventing sintering are achieved. Meanwhile, when the lubricating oil repeatedly passes through the matching surface, a layer of oil film is formed on the matching surface, so that the friction force between the planet shaft 40 and the planet gear 30 is reduced, and the abrasion speed is reduced. When the planetary gear 30 rotates in the first direction, the planetary oil guiding groove 31 guides the lubricating oil attached to the planetary shaft 40 from the hollow body to the outside of the differential case 10; when the planet gear 30 rotates in the second direction, the planet oil guiding groove 31 guides the lubricant oil outside the differential case 10 or at two ends of the planet shaft 40 to the middle of the planet shaft 40, so that the lubricant oil can regularly guide the flow direction of the lubricant oil according to the rotation direction of the planet gear 30 by using the spiral feature, and the matching surface between the planet gear 30 and the planet shaft 40 is fully covered. The first direction is a direction in which the planetary oil groove 31 spirals coincides with the direction in which the planetary gear 30 rotates, as viewed from the center of the hollow housing in the axial direction of the planetary shaft 40 toward the outside of the differential case 10; the second direction is a direction in which the planetary oil groove 31 spirals in a direction opposite to the rotation direction of the planetary gear 30, as viewed from the center of the hollow housing in the axial direction of the planetary shaft 40 toward the outside of the differential case 10.

The working principle of embodiment 1 of the invention is as follows:

when the vehicle runs, the differential mechanism can rotate along with the rotation of the wheels, and partial lubricating oil in the vehicle is guided to the interior of the differential mechanism. When oil enters the differential case 10 through the half shaft mounting through hole 11, firstly, lubricating oil flows into the gasket groove 13 under the guidance of the half shaft oil guide groove 111, the lubricating oil is spread in the whole gasket groove 13 along with the rotation of the differential, part of the lubricating oil flows into a gap between the gasket and the half shaft bevel gear 20, and the matching surface between the gasket and the half shaft bevel gear 20 is lubricated and cooled; the lubricating oil continues to flow, a part of the lubricating oil flows to the lubricating annular wall 12, another part of the lubricating oil flows to the oil collecting groove 14, the lubricating oil splashed by the rotation of the half bevel gear 20 also splashes to the inner wall of the hollow cavity and then flows into the lubricating annular wall 12, the planetary gear 30 is meshed with the half bevel gear 20, a part of the lubricating oil can be carried away, the lubricating oil can be lubricated by the lubricating annular wall 12, a part of the lubricating oil can stay on the planetary shaft 40, the lubricating oil attached to the planetary shaft 40 is guided to the matching surfaces of the planetary shaft 40 and the planetary gear 30 through the rotation of the planetary gear 30 and the spiral planetary oil guiding groove 31, the lubricating oil is guided out of the inside of the differential case 10 (or guided in from the outside of the differential) along the spiral planetary oil guiding groove 31 along with the rotation of the planetary gear 30, and the flowing lubricating oil passes through, an oil film is formed between the planetary gear 30 and the planetary shaft 40, so that lubrication is increased, and abnormal abrasion between the planetary shaft 40 and the planetary gear 30 is avoided; the flowing lubricating oil can also take away heat generated by friction, so that sintering is avoided; the lubricating oil from the lubricating annular wall 12 at one end to the lubricating annular wall 12 at the other end continues to flow into the oil collecting groove 14 at the other end, and the lubricating oil flows from the oil collecting groove 14 to the space between the half shaft bevel gear 20 and the gasket for lubrication and is then guided out through the spiral oil guide groove in the half shaft mounting through hole 11.

Example 2

Referring to fig. 5 and 6, the anti-sintering oil guide structure for a differential gear in embodiment 2 of the present invention is improved based on embodiment 1.

Specifically, a planetary shaft sleeve 50 is sleeved on an inner hole of the planetary gear 30, the planetary shaft sleeve 50 is fixedly sleeved on the inner hole of the planetary gear 30, and the fixing mode is preferably a detachable fixing mode, such as a bolt and a nut. The center of the planetary shaft sleeve 50 is provided with a shaft sleeve through hole which is matched with the planetary shaft 40, the planetary shaft sleeve 50 is sleeved on the planetary shaft 40, and the planetary shaft 40 and the planetary shaft sleeve 50 can rotate relatively. Be equipped with axle sleeve oil groove 51 on planet axle sleeve 50's axle sleeve through-hole inner wall, axle sleeve oil groove 51 is the spiral shape, extends to the other end from the one end of axle sleeve through-hole. The length of the shaft sleeve through hole is equal to the length of the inner hole of the planetary gear 30 or the length of the shaft sleeve through hole is larger than the length of the inner hole of the planetary gear 30, so that the lubricating oil can completely cover the length of the planetary shaft 40 where the planetary gear 30 is located, and the planetary shaft 40 is prevented from directly contacting with the planetary gear 30 to cause abrasion damage to the planetary gear 30. When the lubricating oil flows into the planetary shaft sleeve 50, the planetary shaft sleeve 50 rotates along with the planetary gear 30, the lubricating oil moves along the spiral shaft sleeve oil groove 51, a layer of oil film is formed at the position where the lubricating oil passes and is attached to the surface of the planetary shaft 40, the planetary shaft 40 is lubricated, the friction force is reduced, heat generated between the planetary shaft 40 and the planetary shaft sleeve 50 is taken away, and sintering is prevented.

When no lubricating oil exists in the differential case 10 or between the planetary shaft sleeve 50 and the planetary shaft 40, the planetary shaft sleeve 50 can play a role of protection, the planetary shaft 40 can rub against the planetary shaft sleeve 50, under some extreme working conditions with excessively high differential rate, the heat generation between the planetary shaft 40 and the planetary shaft sleeve 50 can be increased rapidly, and sintering occurs, but because the planetary shaft sleeve 50 is in contact with the planetary shaft 40 and is sintered, the planetary gear 30 cannot be damaged, and when a vehicle is overhauled, the planetary shaft sleeve 50 only needs to be replaced, and the whole planetary gear 30, the planetary shaft 40 and even the whole differential do not need to be replaced. Meanwhile, the planetary shaft sleeve 50 is detachably connected with the planetary gear 30, so that subsequent damage and replacement are facilitated, and compared with the method of directly contacting and lubricating the planetary gear 30 and the planetary shaft 40, the scheme of the embodiment has one more layer of safety, so that the emergency situation that lubricating oil does not exist can be effectively prevented, and the maintenance cost is saved.

Embodiment 2 the rest of the structure and the operation principle are the same as those of embodiment 1.

Example 3

The anti-sintering oil guide structure for the differential in the embodiment 3 of the invention is improved on the basis of the embodiment 1.

Specifically, a plurality of planetary oil holes for storing standby lubricating oil are arranged in the planetary oil guide groove 31, the plurality of planetary oil holes are sequentially arranged along the spiral direction of the planetary oil guide groove 31, and the standby lubricating oil is injected into the plurality of planetary oil holes. When the planetary gear 30 rotates at a high speed, because of the centrifugal force and the continuous passage of the lubricating oil in the planetary oil guiding groove 31, the planetary oil guiding groove 31 is filled with the lubricating oil, and the planetary oil holes are blocked by the passing lubricating oil, so that the lubricating oil in a plurality of planetary oil holes is continuously kept in the oil holes; however, when there is no continuous lubricant flowing in between the planet gear 30 and the planet shaft 40, even there is no lubricant, a large friction force is generated between the planet gear 30 and the planet shaft 40, the temperature rises sharply, at this time, the lubricant stored in the oil hole flows into the planet oil guiding groove 31 because there is no blockage of the lubricant passing through continuously, and the vehicle differential speed, and the centrifugal force is reduced, the lubricant in the oil hole flows into the planet oil guiding groove 31, and plays a role of lubrication between the planet shaft 40 and the planet gear 30, meanwhile, the lubricant flows along with the spiral planet oil guiding groove 31 by the rotation of the planet gear 30, and passes through the matching surface between the planet shaft 40 and the planet gear 30 repeatedly, and the heat is taken away, thereby achieving the effects of cooling and preventing sintering. Compared with embodiment 1, the differential case 10 can further protect the planetary shafts 40 and the planetary gears 30 from being sintered due to the absence of lubricating oil in the differential case 10. Compared with the embodiment 2, the planetary gear protection device can protect the planetary gear 30, the planetary shaft 40 and the vehicle, can continue to normally operate, avoids the vehicle from being overturned, does not need to add other parts, and is simple in structure and low in cost.

Embodiment 3 the rest of the structure and the operation principle are the same as those of embodiment 1.

Example 4

The anti-sintering oil guide structure for the differential in embodiment 4 of the invention is improved on the basis of embodiment 3.

Specifically, a spiral oil guide shaft groove is formed in the planet shaft 40 along the axial direction of the planet shaft 40, a plurality of shaft groove oil holes used for storing standby lubricating oil are formed in the oil guide shaft groove, the plurality of shaft groove oil holes are sequentially formed along the spiral direction of the oil guide shaft groove, and the standby lubricating oil is injected into the plurality of shaft groove oil holes; a plurality of planet oil holes into which lubricating oil is injected in advance are also formed on the surface of the planet shaft 40, the arrangement path of the plurality of planet oil holes is spiral, and the arrangement path is consistent with the spiral shape of the planet oil guide groove 31, so that the lubricating oil in the planet oil holes can smoothly and directly enter the oil guide shaft groove for lubricating when flowing out. Under the condition that the planet shaft 40 and the planet gear 30 normally operate and the temperature is normal, the oil outlet ends of each shaft groove oil hole and each planet oil hole are in a closed state, so that the phenomenon that the lubricating oil which is already lubricated flows into the shaft groove oil holes or the planet oil holes to cause mixing of new oil and old oil and influence on the lubricating and cooling effects is avoided. Meanwhile, through the arrangement of the folding state, the situation that when sufficient lubricating oil exists between the planetary gear 30 and the planetary shaft 40, oil in the planetary oil holes and the shaft groove oil holes flows out, and therefore continuous lubricating oil does not flow in the subsequent differential case 10, and lubricating oil does not exist in the planetary oil holes and the shaft groove oil holes. The spheroidal graphite cast iron material is preferable for the planetary gear 30 and the planetary shaft 40 because it is required to withstand a large torque and a high strength. The folding part of the oil outlet end of the planet oil hole and the shaft groove oil hole can be affected by expansion with heat and contraction with cold, and the planet oil hole and the shaft groove oil hole are opened and folded. And the inner walls of the planet oil holes and the shaft groove oil holes are provided with small pits for enhancing the adhesive force of lubricating oil in the planet oil holes and the shaft groove oil holes and avoiding the outflow of the lubricating oil in the planet oil holes and the shaft groove oil holes.

When lubricating oil is normally supplied in the differential case 10 and continuously flows in and out between the planet shaft 40 and the planet gear 30, the differential normally works, heat is continuously taken away by the lubricating oil, a layer of oil film is continuously formed between the planet shaft 40 and the planet gear 30, friction is reduced, and oil outlet ends of the planet oil holes and the shaft groove oil holes are all in a folding state; when there is not enough lubricant in the differential case 10 or the lubricant cannot continuously flow in and out between the planetary shafts 40 and the planetary gears 30, in some extreme conditions, such as running on ice road or continuously turning, sharp curve running, etc., the difference rate is too high, the friction between the planetary gears 30 and the planetary shafts 40 increases, the overall temperature in the differential case 10 rises sharply, and especially the heat between the planetary gears 30 and the planetary shafts 40 increases sharply. At this time, the oil outlet end of the shaft groove oil hole and the oil outlet end of the planet oil hole are changed from the closed state to the open state due to the heat expansion and the cold contraction because of the rapid increase of the heat and the rapid increase of the temperature, and the lubricating oil in the planet oil hole and the shaft groove oil hole is not obstructed because the lubricating oil is not in the oil guide shaft groove. Lubricating oil in the shaft groove oil hole and the planet oil hole flows into the oil guide shaft groove by means of gravity or centrifugal force to lubricate the planet shaft 40 and the planet gear 30, an oil film is formed between the planet shaft 40 and the planet gear 30, friction is reduced, heat is taken away by the lubricating oil in the oil guide shaft groove, and the effect of preventing sintering is achieved. Meanwhile, after the heat is taken away, the temperature is reduced, the planet oil holes and the shaft groove oil holes can shrink to a certain degree, but the planet oil holes and the shaft groove oil holes are made of cast iron materials, so that the planet oil holes and the shaft groove oil holes cannot be completely closed, the outflow speed of lubricating oil can be slowed down, the lubricating oil is continuously conveyed to the oil guide shaft groove, the normal lubricating state between the planet shaft 40 and the planet gear 30 is prolonged as far as possible, and the vehicle can keep normal running as long as possible until the lubricating oil is replenished subsequently.

Specifically, the vertical distance from the middle part of the inner hole of the planetary gear 30 to the central axis of the inner hole is smaller than the vertical distance from the two end parts of the inner hole of the planetary gear 30 to the central axis of the inner hole, so that the contact area between the planetary gear 30 and the planetary shaft 40 is increased, the stress applied to the two ends of the planetary gear 30 is reduced, the strength of the planetary gear 30 and the planetary shaft 40 is enhanced, and the service life is prolonged.

Example 4 the rest of the structure and the operation principle are the same as those of example 1.

Example 5

Embodiment 5 of the invention discloses a differential gear, which comprises an anti-sintering oil guide structure for any one of embodiments 1 to 4.

In the differential mechanism in the embodiment 5 of the invention, the differential mechanism adopts the structure, when a vehicle runs, the differential mechanism can run along with the rotation of the wheels, and part of lubricating oil in the vehicle is guided to the inside of the differential mechanism. When oil enters the differential case 10 through the half shaft mounting through hole 11, firstly, lubricating oil flows into the gasket groove 13 under the guidance of the half shaft oil guide groove 111, the lubricating oil is spread in the whole gasket groove 13 along with the rotation of the differential, part of the lubricating oil flows into a gap between the gasket and the half shaft bevel gear 20, and the matching surface between the gasket and the half shaft bevel gear 20 is lubricated and cooled; the lubricating oil continues to flow, a part of the lubricating oil flows to the lubricating annular wall 12, another part of the lubricating oil flows to the oil collecting groove 14, the lubricating oil splashed by the rotation of the half bevel gear 20 also splashes to the inner wall of the hollow cavity and then flows into the lubricating annular wall 12, the planetary gear 30 is meshed with the half bevel gear 20, a part of the lubricating oil can be carried away, the lubricating oil can be lubricated by the lubricating annular wall 12, a part of the lubricating oil can stay on the planetary shaft 40, the lubricating oil attached to the planetary shaft 40 is guided to the matching surfaces of the planetary shaft 40 and the planetary gear 30 through the rotation of the planetary gear 30 and the spiral planetary oil guiding groove 31, the lubricating oil is guided out of the inside of the differential case 10 (or guided in from the outside of the differential) along the spiral planetary oil guiding groove 31 along with the rotation of the planetary gear 30, and the flowing lubricating oil passes through, an oil film is formed between the planetary gear 30 and the planetary shaft 40, so that lubrication is increased, and abnormal abrasion between the planetary shaft 40 and the planetary gear 30 is avoided; the flowing lubricating oil can also take away heat generated by friction, so that sintering is avoided; the lubricating oil from the lubricating annular wall 12 at one end to the lubricating annular wall 12 at the other end continues to flow into the oil collecting groove 14 at the other end, and the lubricating oil flows from the oil collecting groove 14 to the space between the half shaft bevel gear 20 and the gasket for lubrication and is then guided out through the spiral oil guide groove in the half shaft mounting through hole 11.

Example 6

As shown in fig. 7, the present embodiment provides a transmission flange, which mainly includes a flange main body 410, a first transmission structure 420, a first connection structure 430, and a second transmission structure 440;

wherein the first transmission structure 420 is disposed on the flange body 410, the first transmission structure 420 is used for connecting with the differential half shaft mounting through hole and transmitting the torque of the differential half shaft to the flange body 410;

as shown in fig. 8 and 10, the differential half shaft is connected to the flange body 410 through the first transmission structure 420, when the differential half shaft rotates, the torque of the differential half shaft acts on the first transmission structure 420, and the flange body 410 is driven to rotate together through the first transmission structure 420, and the rotation and the torque of the output shaft are transmitted to the flange body 410.

Wherein the first connecting structure 430 is disposed on the flange main body 410, and the first connecting structure 430 is used for connecting the flange main body 410 with a transmission shaft;

in the embodiment, the first connecting structure 430 plays a role in connection, and the first connecting structure 430 prevents the transmission shaft from loosening from the flange main body 410 by connecting the flange main body 410 with the transmission shaft.

A second transmission structure 440, wherein the second transmission structure 440 is disposed at an end of the flange main body 410 facing the transmission shaft, and the second transmission structure 440 is used for transmitting the torque of the flange main body 410 to the transmission shaft and preventing the torque from being transmitted to the first connection structure 430.

When the flange body 410 is rotated by the differential half shafts, the torque of the flange body 410 is transmitted to the propeller shafts through the second drive structure 440. The second transmission structure 440 is responsible for bearing the transmission torque during the process of the flange body 410 driving the transmission shaft to rotate. And second transmission structure 440 is still used for preventing the moment of torsion from being transmitted to first connection structure 430, like this at the flange with the in-process that the moment of torsion was transmitted to the transmission shaft, first connection structure 430 can not receive the effect of moment of torsion, consequently be difficult to damage, can guarantee that first connection structure 430 can be connected flange main part 410 and transmission shaft all the time to the security of flange joint has been improved, and thereby can be suitable for the quantity of few first connection structure 430 and simplify structure reduce cost.

In a preferred embodiment, the second transmission structure 440 is a rectangular tooth disposed on an end surface of the flange body 410 connected to the transmission shaft, and the rectangular tooth on the flange body 410 is used for transmitting torque in cooperation with the rectangular tooth on the transmission shaft.

The rectangular teeth are long strips, and the sections of the rectangular teeth are rectangular. In this embodiment, the drive shaft may have rectangular teeth that are aligned with the rectangular teeth on the flange body 410. After the flange main body 410 is installed and connected with the transmission shaft, the end face of the flange main body 410 is matched with the transmission shaft, and the rectangular teeth on the flange main body 410 are embedded with the rectangular teeth on the transmission shaft. When the flange body 410 rotates, the rectangular teeth on the flange body 410 contact the rectangular teeth on the adjacent drive shaft, and the rectangular teeth on the flange body 410 push the rectangular teeth on the adjacent drive shaft, so that the drive shaft and the flange body 410 rotate together. Rectangular teeth can be machined directly into the end face of the flange body 410 by milling. In order to make the flange structure simpler while realizing that the rectangular teeth bear the torque, the rectangular teeth are formed by two adjacent tooth grooves which are formed by the end surfaces of the flange main body 410 being recessed in the direction away from the transmission shaft. By adopting the structure to form the rectangular teeth, the tops of the rectangular teeth can be flush with the end face of the flange main body 410, so that redundant space is not occupied, and only the original flange main body 410 is directly removed to form tooth grooves. The rectangular teeth and the flange body 410 formed in this way are of an integrated structure, and the influence on the original flange body 410 is small. The whole structure is simple, and the bearing capacity is strong.

In the present embodiment, the first connecting structure 430 is connected to the transmission shaft through a first connecting member; in the flange rotation direction, the fit clearance between the first connecting piece and the first connecting structure 430 is larger than the fit clearance between the rectangular teeth on the flange main body 410 and the rectangular teeth on the transmission shaft.

Because the fit clearance between the first connecting piece and the first connecting structure 430 is larger than the fit clearance between the rectangular teeth on the flange main body 410 and the rectangular teeth on the transmission shaft in the flange rotation direction, the rectangular teeth on the flange main body 410 are firstly contacted with the rectangular teeth on the transmission shaft before the first connecting piece is contacted and stressed with the first connecting structure 430 during flange transmission, and the first connecting piece and the first connecting structure 430 always have fit clearance due to the blockage of the rectangular teeth on the transmission shaft, so that the torque action of the first connecting structure 430 and the first connecting piece during transmission can be well avoided. The first coupling member may be a bolt, and the first coupling structure 430 may be a bolt hole through which the bolt passes when the flange body 410 is coupled to the drive shaft.

In this embodiment, a plurality of sets of transmission structures are disposed on the flange main body 410, each set of transmission structures includes a plurality of first transmission structures 420 disposed in parallel, the number of the first connection structures 430 is the same as that of the transmission structures, the first connection structures 430 correspond to the transmission structures one to one, and the transmission structures are configured to prevent torque from being transmitted to the corresponding first connection structures 430.

As shown in fig. 11, the present embodiment may provide a plurality of first connection structures 430 in a circumferential direction of the flange main body 410 to improve connection reliability. In addition, the present embodiment adopts a one-to-one corresponding arrangement manner of the transmission structure sets and the first connection structures 430. Each first connection structure 430 is protected by a corresponding transmission structure group, and it is ensured that the transmission structure group preferentially bears torque in the first connection structure 430 in the corresponding first connection structure 430 and the corresponding transmission structure group, so that the problem that when a plurality of first connection structures 430 are arranged, all the first connection structures 430 cannot be ensured to not bear torque is avoided. Wherein each group of transmission structures may be provided with a plurality of first transmission structures 420 arranged in parallel. During transmission, each first transmission structure 420 in the same group can collectively bear torque. The torque applied to the flange is further distributed to the first transmission structures 420 after being distributed to the transmission structure groups, so that the torque borne by each first transmission mechanism is reduced, and the torque borne by the whole flange is increased.

In addition, in the rotation direction, the first connecting structure 430 is located at the center of the corresponding transmission structure group. By adopting the above manner, each first transmission structure 420 in the transmission structure group can be subjected to torque before the first connection structure 430 contacts with the first connecting piece no matter the flange main body 410 rotates forwards or reversely, so that it is ensured that the torque is not transmitted to the first connection structure 430.

For example, 6 sets of drive structures may be provided on the flange body 410, with 4 rectangular teeth provided for each set of drive structures. The 4 rectangular teeth are parallel to each other and are symmetrically arranged with the diameter of the flange body 410 parallel to the four rectangular teeth as an axis of symmetry. And the first transmission structure 420 corresponding to the set of rectangular teeth is disposed on the set of symmetrical axes. The 6 groups of transmission structure groups are uniformly distributed along the circumferential direction of the flange main body 410, that is, the angles of the intervals between any two adjacent transmission structure groups in the 6 groups of transmission structure groups are the same, and the intervals between the two adjacent groups are 60 degrees. It is understood that the number of the aforementioned transmission sets and the number of the first connecting structures 430 in each transmission structure set may adopt other numbers, and are not limited herein.

This embodiment may employ a plurality of rectangular teeth parallel to each other in a set of drive structures, 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 mode, the torque bearing capacity of each group of transmission structure can be further increased under the condition that the number of the rectangular teeth of each group is not increased.

As shown in fig. 10, in the present embodiment, the flange main body 410 includes a first connecting portion 411 having a cylindrical shape and a second connecting portion 412 having a disk shape, the first connecting portion 411 and the second connecting portion 412 are arranged along an axial direction of the flange main body 410, a through hole penetrating the connecting portions is formed in the first connecting portion 411, the first transmission structure 420 is a spline, the spline is formed in the through hole of the first connecting portion 411, and the first connecting structure 430 is formed in the second connecting portion 412.

When the first coupling structure 430 employs rectangular teeth, the rectangular teeth are disposed on a disk surface of the second coupling portion 412 facing the drive shaft.

In the present embodiment, the first connection portion 411 is used to effect connection of the flange body 410 to the differential half shaft, while the second connection portion 412 is used to effect connection of the flange body 410 to the propeller shaft. In the present embodiment, the first connecting portion 411 and the second connecting portion 412 are arranged along the axial direction of the flange main body 410, so that the differential half-shaft transmission shafts are compactly distributed on both sides of the flange in the axial direction, and thus the mutual influence between the power input side and the power output side can be avoided.

In the embodiment, the spline is adopted on the power input side for transmission, and the bearing capacity of the transmission is high. A through hole may be machined in the first connection portion 411 before a spline is machined in the through inner wall.

In the present embodiment, the second transmission structure 440 extends from the inner wall position of the through hole to the outer wall position of the second connection portion 412 along the radial direction of the second connection portion 412. In this manner, the radial dimension of the disk of the second coupling portion 412 is fully utilized to maximize the length of the rectangular tooth that can withstand torque.

When the length of the rectangular tooth is longer, the deformation amount of the rectangular tooth under the action of torque can be increased, and when the deformation amount exceeds a certain degree, the bearing capacity of the rectangular tooth can be reduced due to the fact that the same rectangular tooth is not in sufficient contact with the rectangular tooth matched with the rectangular tooth. In this regard, in the present embodiment, each rectangular tooth is composed of a plurality of sub-rectangular teeth having a smaller length, and two adjacent sub-rectangular teeth are disconnected from each other. By adopting the mode, the deformation of each sub-rectangular tooth is not accumulated on other sub-rectangular teeth, so that the deformation of the rectangular tooth can be dispersed to each sub-rectangular tooth, and the deformation of each sub-rectangular tooth is very small and cannot exceed the degree of insufficient contact of the rectangular tooth. The gap between adjacent sub-rectangular teeth can be small, so that the length of the part of the rectangular teeth which can bear the torque can not be obviously reduced by adopting the structure.

As shown in fig. 13, in the present embodiment, each transmission structure group is composed of two sub-transmission structure groups, namely a first sub-transmission structure group 441 and a second sub-transmission structure group 442. The number of the rectangular teeth in the two groups of sub-transmission structure groups, the cross-sectional shapes and the arrangement intervals are equal, only the two groups of sub-transmission structure groups are staggered in the circumferential direction, and each rectangular tooth is also divided into two mutually disconnected parts which belong to the two groups of sub-transmission structure groups. By adopting the method, the deformation amount of the rectangular tooth can be reduced without reducing the total length of the part of the rectangular tooth for bearing the torque. After the two sub-transmission structure groups are staggered in the circumferential direction, the stress of the flange main body 410 is not concentrated on 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 of the flange main body 410 in the circumferential direction.

One end of each rectangular tooth in the first sub-transmission structure group 441 extends to the outer wall of the flange main body 410, so that the milling cutter can remove materials from the outer side to the inner side of the flange main body 410 at one time to complete processing of the rectangular teeth, and processing efficiency can be obviously improved.

The first sub transmission structure group 441 and the second sub transmission structure group 442 may or may not be completely staggered in the circumferential direction. When the completely staggered manner is adopted, the first sub transmission structure group 441 and the second sub transmission structure group 442 partially overlap in the radial direction. The disconnected positions of the first sub-transmission structure group 441 and the second sub-transmission structure group 442 on the flange main body 410 cannot bear torque, and the stress applied to the positions, close to the disconnected positions, of the first sub-transmission structure group 441 and the second sub-transmission structure group 442 is also changed abruptly, which affects the service life of the flange. After the first sub-transmission structure group 441 and the second sub-transmission structure group 442 are partially overlapped in the radial direction, the original part, which cannot bear torque and is generated by the disconnection of the radial teeth of the flange main body 410 in the radial direction, is eliminated, and the stress of the part, close to the disconnection position, of the first sub-transmission structure group 441 and the second sub-transmission structure group 442 is prevented from being suddenly changed.

When the method of incomplete staggering is adopted, the tooth spaces of the rectangular teeth in the first sub-transmission structure group 441 and the tooth tops of the rectangular teeth in the second sub-transmission structure group 442 can be aligned. In the foregoing manner, the portion of the flange main body 410 for bearing torque in the circumferential direction can be maximized in the same group of transmission structures, so that the flange main body 410 can bear more torque.

As shown in fig. 12, in the present embodiment, the same transmission structure group is composed of three sub-transmission structure groups, which are respectively the third sub-transmission structure group 443, the fourth sub-transmission structure group 444 and the fifth sub-transmission structure group 445 from the outer wall of the flange main body 410 inward. The rectangular teeth of each group of transmission structure group are mutually disconnected, the length of the rectangular teeth of the third sub-transmission structure group 443 is smaller than that of the fourth sub-transmission structure group 444, and the length of the rectangular teeth of the fourth sub-transmission structure group 444 is smaller than that of the rectangular teeth of the fifth sub-transmission structure group 445. Under the condition of bearing the same torque, the deformation of the outer side of the flange main body 410 is larger than that of the inner side of the flange main body, and the structure that the length of the rectangular teeth from inside to outside is shortened is adopted in the embodiment, so that the variance of the deformation of the rectangular teeth at each radial position of the flange main body 410 can be reduced, and the influence on the service life of the flange due to the overlarge deformation of the rectangular teeth at the local position in the radial direction of the flange main body 410 is avoided.

As shown in fig. 9, in the present embodiment, the second connecting portion 412 is provided with a limiting hole 4121 engaged with the transmission shaft, one end of the limiting hole 4121 facing the first connecting portion 411 is provided with a spigot 4122 for limiting the axial position of the transmission shaft, and the spline extends to the position of the spigot 4122.

When the end of the transmission shaft is installed, 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. And the output shaft of the gearbox can be inserted into the through hole. Because the splines in the through bore extend to the location of the stop 4122, the input end transmits torque at a short distance from the end of the driveshaft. By adopting the mode, the distance between the position of the input end for transmitting the torque and the position of the output end for transmitting the torque can be shortened, so that the deformation of the transmission component between the input end and the output end under the action of the torque is reduced.

Example 7

As shown in fig. 14, the present embodiment provides a transmission four-speed shift device for performing a four-speed shift operation, which can also be applied to the transmission of embodiment 1. For convenience of description, the four gears are divided into two groups, namely a first group of gears and a second group of gears, and each group of gears comprises two gears. The transmission four-speed gear shift device of the present 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.

As shown in fig. 15 and 16, in which the shift drum 1 is provided with a guide groove 110 extending in a circumferential direction thereof, the guide groove 110 includes shift areas 112 that rotate to different angular positions with the shift drum 1;

as shown in fig. 14, the shift drum 1 may be provided in a cylindrical shape, the aforementioned guide groove 110 may be provided on a cylindrical peripheral wall of the shift drum 1, the shift block 112 is a partial area of the entire guide groove 110, the shift drum 1 may rotate around its own axis, and the shift block 112 may also rotate to different positions in accordance with the rotation of the shift drum 1.

As shown in fig. 17, in which the first synchronizer is used to participate in the operation of engaging a first set of gears. The first synchronizer can be synchronously and rotationally connected with the input shaft or the output shaft; the first synchronizer is provided with a gear engaging part, the gear engaging part can move along the axial direction of the first synchronizer under the action of external force (for example, under the shifting of a shifting fork), when the gear engaging part of the first synchronizer moves to be completely combined with a gear of a certain gear, the first synchronizer and the gear synchronously rotate, at the moment, 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 synchronous transmission connection refers to a connection mode which can enable the first synchronizer and the input shaft or the output shaft to synchronously rotate.

Wherein the first driving mechanism 3 is slidably connected with the guiding groove 110 at a first angular position 120 of the shift drum 1, the first driving mechanism 3 is configured to push the engaging member of the first synchronizer to move to a first axial position to engage along the axial direction of the first synchronizer or push the engaging member of the first synchronizer to move to a second axial position to engage along the axial direction of the first synchronizer under the driving of the shift area 112, wherein the first axial position is different from the second axial position;

wherein the first axial position is the position in which the engaging member of the first synchronizer is fully engaged with and rotates the gear of one of the first set of gears synchronously therewith. Wherein the second axial position is the position in which the engaging member of the first synchronizer is fully engaged with and rotates the gear of another gear of the first set of gears synchronously therewith. The aforementioned engaging means may be a synchronizing ring of the first synchronizer.

As the shift drum 1 rotates, the shift region 112 can rotate to a range of angular positions in sliding connection with the first drive mechanism 3. In this angular position range, the position of the shift area 112 connected to the first drive also changes as the shift drum 1 rotates. Due to the difference in the distance between each position of the shift area 112 and the first synchronizer in the axial direction, the shift area 112 can drive the first driving mechanism 3 to move in the axial direction during the rotation process, and the first driving mechanism 3 moves in the axial direction and simultaneously pushes the engaging member of the first synchronizer to move in the axial direction.

In the present embodiment, the first driving mechanism 3 includes a first slider 310, a first fork 32 and a first link 33, the first link 33 is connected to the first slider 310 and the first fork 32, respectively, and the first slider 310 slides along the guide slot 110.

Wherein the width of the guiding slot is slightly larger than the width of the first slider 310, the direction of movement of the first link 33 is constrained and it can only move in the axial direction. The guide grooves 110 are at different circumferential positions at different distances from the first synchronizer or the second synchronizer 4 in some areas, seen in the axial direction of the shift drum 1. When the shift drum 1 rotates, different positions of the guide groove 110 come into contact with the first slider 310, which moves back and forth in the axial direction by the drive of the guide groove 110 while sliding in the circumferential direction relative to the guide groove 110. Since the first link 33 connects the first slider 310 and the first fork 32, the first fork 32 also moves in the axial direction in synchronization with the first slider 310. Wherein the first coupling member 33 may be disposed at a side of the shift drum 1 in a radial direction, the first slider 310 is disposed in the radial direction of the shift drum 1, one end of the first slider 310 is coupled to the first coupling member 33, and the opposite end is inserted into the guide groove 110.

As shown in fig. 14 and 18, in which the second synchronizer 4 is used to engage the gear operation of the second group of gears, the second synchronizer 4 can be synchronously and rotationally connected with the input shaft or the output shaft; the second synchronizer 4 is provided with a gear engaging component, the gear engaging component can move along the axial direction of the second synchronizer 4 under the action of external force (for example, under the shifting of a shifting fork), when the gear engaging component of the second synchronizer 4 moves to be completely combined with a gear of a certain gear, the second synchronizer 4 and the gear rotate synchronously, 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 synchronous transmission connection means a connection mode that can synchronously rotate the second synchronizer 4 and the input shaft or the output shaft.

Wherein the second drive mechanism 5 is in sliding connection with the guide slot 110 in a second angular position 130 of the shift drum 1, the second drive mechanism 5 being adapted to push the engaging member of the second synchronizer 4 to move in the axial direction of the second synchronizer 4 into a third axial position engaging or to push the engaging member of the second synchronizer 4 to move in the axial direction of the second synchronizer 4 into a fourth axial position engaging under the drive of the shift area 112, wherein the third axial position is different from the fourth axial position, the second angular position 130 being different from the first angular position 120;

wherein the third axial position is the position in which the gear engaging member of the second synchronizer 4 is fully engaged with and rotates the gear of one of the gears of the second set of gears synchronously therewith. Wherein the fourth axial position is the position in which the gear engaging member of the second synchronizer 4 is fully engaged with and rotates the gear of another gear of the second group of gears synchronously therewith. The aforementioned engaging means may be a synchronizing ring of the second synchronizer 4.

As the shift drum 1 rotates, the shift region 112 can rotate to a range of angular positions in sliding connection with the second drive mechanism 5. In this angular position range, the position of the shift area 112 connected to the secondary drive also changes as the shift drum 1 rotates. Due to the difference in the distance between the shift area 112 and the second synchronizer 4 in the axial direction at each position, the shift area 112 can drive the second driving mechanism 5 to move in the axial direction during the rotation, and the second driving mechanism 5 moves in the axial direction and pushes the engaging member of the second synchronizer 4 to move in the axial direction.

In the present embodiment, the second driving mechanism 5 includes a second slider 510, a second fork 52 and a second link 53, the second link 53 is connected to the second slider 510 and the second fork 52, respectively, and the second slider 510 slides along the guide slot 110.

Wherein the width of the guiding slot is slightly larger than the width of the second slider 510, the direction of movement of the second link 53 is constrained and it can only move in the axial direction. The guide grooves 110 are at different circumferential positions at different distances from the first synchronizer or the second synchronizer 4 in some areas, seen in the axial direction of the shift drum 1. When the shift drum 1 rotates, different positions of the guide groove 110 come into contact with the second slider 510, which moves back and forth in the axial direction by the drive of the guide groove 110 while sliding in the circumferential direction relative to the guide groove 110. Since the second link 53 connects the second slider 510 and the second fork 52 together, the second fork 52 also moves in the axial direction in synchronization with the second slider 510. Wherein the second link 53 may be provided at a side of the shift drum 1 in a radial direction, the second slider 510 is provided along the radial direction of the shift drum 1, one end of the second slider 510 is connected to the second link 53, and the opposite end is inserted into the guide groove 110.

As shown in fig. 14, the electric motor 6 is used to drive the shift drum 1 to rotate, so that the shift area 112 drives the first driving mechanism 3 and the second driving mechanism 5 to move back and forth along the axial direction of the shift drum 1. The motor 6 bit and the first synchronizer and the second synchronizer 4 are located on two sides of the axial direction of the gear shifting drum 1, and the motor 6 and the gear shifting drum 1 are coaxially arranged.

In the embodiment, the motor 6 and the two driving mechanisms are separately arranged along the axial direction and are positioned on two sides of the shift drum 1, so that the actions of the motor 6 and the driving mechanisms can not be influenced by each other, the motor 6 and the shift drum 1 are coaxially arranged, the structure can be more compact, and the transmission of power between the motor 6 and the shift drum 1 is also utilized.

As a preferable implementation manner, in this embodiment, the transmission four-gear shifting device further includes a rotating shaft 7, the shift drum 1 is in interference fit with the rotating shaft 7, and the motor 6 drives the rotating shaft 7 to rotate so as to drive the shift drum 1 to rotate. The transmission is carried out by directly adopting an interference fit mode through the rotating shaft and the gear shifting drum 1, and the transmission process is simpler and more reliable. Wherein motor 6 installs on the assembly box, and shift drum 1 fixes a position on the box through pivot 7, and shift drum 1 and 1 axle pivot 7 relatively fixed of shift drum, and pivot 7 can rotate on the box.

As shown in fig. 19, in the present embodiment, an annular limiting groove 21 is formed in a peripheral wall of the first synchronizer and/or the second synchronizer 4, a toggle member 325 is provided at an end of the first fork 32 and/or the second fork 52, and the toggle member 325 toggles a gear engaging member of the first synchronizer and/or the second synchronizer 4 by toggling a side wall of the limiting groove 21.

In the present embodiment, the width of the limiting groove 21 is greater than 1.1 times the width of the toggle member 325, and the distance between the first axial position and the second axial position is greater than 2 times the axial gap between the toggle member 325 and the limiting groove 21. By adopting the structure, after the shifting piece 325 is inserted into the limiting groove 21 and shifts the gear engaging part of the synchronizer to the gear engaging position, one side of the shifting piece 325 is in contact with one side wall of the limiting groove 21, and a sufficient gap is left between the other side of the shifting piece 325 and the other side wall of the limiting groove 21. Therefore, after the shifting part 325 and the limiting groove 21 are relatively displaced due to unexpected small vibration, the other side of the shifting part 325 cannot be contacted with the other side wall of the limiting groove 21, so that the situation that the shifting part 325 shifts the limiting groove 21 due to unexpected vibration is avoided, the gear engaging component is disengaged from the current gear, and the gear engaging is more reliable. In normal gear, the distance of the shifting member 325 moving along the axial direction exceeds the axial gap between the shifting member 325 and the limiting groove 21, so that the other side of the shifting member 325 can also push the gear engaging member to move by contacting with the other side wall of the limiting groove 21 during shifting movement.

When the toggle member 325 toggles the synchronizer to shift gears, the toggle member 325 contacts with the synchronizer, and the synchronizer rotates at a high speed, so that relative motion is generated between the toggle member 325 and the synchronizer, continuous sliding friction exists between the toggle member 325 and the synchronizer, the toggle member 325 and the synchronizer are easy to wear and deform, and heat generated by friction can also affect the gearbox. For this purpose, a wear part that can be exchanged can be provided on the toggle part 325, so that the wear part comes into contact with the synchronizer. When the wear-resistant part is worn to a certain extent, the wear-resistant part is replaced by a new wear-resistant part. When the mode is adopted, the gearbox needs to be disassembled and assembled, and the wear-resistant part can be replaced, so that the wear-resistant part is very inconvenient in the actual use process.

For this, an oil guide groove may be provided on the first fork 32, and an outlet of the oil guide groove may be provided on a surface of the toggle member 325 contacting the synchronizer, and the lubricating oil flows to the surface of the toggle member 325 along the oil guide groove, and an oil film is formed between the toggle member 325 and the synchronizer to reduce friction therebetween.

In addition, a roller or a needle roller may be disposed on the shifting member 325 to reduce friction, but because the roller is in point contact when contacting with the synchronizer and the needle roller is in line contact when contacting with the synchronizer, the contact areas of the two contact methods are small, which easily causes the synchronizer and the shifting fork to be stressed too intensively.

In this regard, the present embodiment employs a structure that allows the toggle member 325 to rotate synchronously with the synchronizer to avoid friction. As shown in fig. 20 to 22, the first fork 32 of the present embodiment further includes a first rotating member 321, a second rotating member 322, a third rotating member 323 and a fourth rotating member 324 which are cylindrical, 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 fork 32, 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, the same intersection point 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 on a first plane, the rotational axis of the third rotating member 323 and the rotational axis of the fourth rotating member 324 are located on a second plane different from the first plane, and the first plane and the second plane are arranged in the axial direction of the first synchronizer. The toggle member 325 is a rotating belt 326, and one end of the rotating belt 326 sequentially bypasses 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 and is connected to the other opposite end. The rotating belt 326 may be a steel belt or a belt. In one embodiment, the rotating belt 326 is tightened and wound around the outer walls of the four rotating members, and the rotating belt 326 is connected end to form a ring. The rotating band 326 is unfolded to have a circular arc shape. When the distance between the first rotating member 321 and the second rotating member 322 is too long, a fifth rotating member may be further disposed between the first rotating member 321 and the second rotating member 322, and the fifth rotating member is used to provide a support for the rotating belt 326 in the middle; a fifth rotating member may be further provided between the first rotating member 321 and the second rotating member 322 when the distance between the third rotating member 323 and the fourth rotating member 324 is excessively long, and a support for the rotating band 326 is provided at the middle portion by the sixth rotating member. The number of the fifth rotating member and the sixth rotating member may be plural, and the number may be determined according to 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. The aforementioned rotation can be rotationally connected to the first fork 32 through a smooth-surfaced shaft.

With the above-described structure, when the rotating band 326 moves to a position contacting the synchronizer with the first fork 32, the rotating band 326 is rotated by the synchronizer, and the rotating direction of the rotating band 326 is shown by the arrow direction in fig. 8 to 10. At the initial stage when the rotating belt 326 is just in contact with the synchronizer, sliding friction exists between the rotating belt 326 and the synchronizer, and after the rotating speed of the rotating belt 326 is the same as that of the synchronizer, relative sliding does not exist between the rotating belt 326 and the synchronizer, so that the rotating belt 326 and the synchronizer are not abraded due to the sliding friction, at the moment, the rotating belt 326 is driven by the synchronizer to rotate around the four rotating members in a circulating manner in sequence, the rotating belt 326 is in surface contact with the synchronizer, the condition that stress is too concentrated is not easy to occur, and the rotating belt 326 can always rotate synchronously with the synchronizer.

The present embodiment also provides another embodiment to solve the aforementioned sliding friction problem. First shift fork 32 still includes the multiunit runner assembly, and every group runner assembly includes that the seventh rotates the piece, the eighth rotates the piece and rotates and take 326 the seventh rotation piece, the eighth rotation piece with first shift fork 32 rotates and connects, rotate the one end of taking 326 and meet with the relative other end after the outer wall of the seventh rotation piece, the eighth rotation piece is walked around in proper order. Wherein the rotating shafts 7 of the seventh rotating member and the eighth rotating member are parallel to each other. The eighth rotating piece and the ninth rotating piece are arranged in an axisymmetric mode, the symmetric axes of the eighth rotating piece and the ninth rotating piece are used as the symmetric axes of the rotating assemblies, the extension lines of the symmetric axes of the rotating assemblies of all groups are compared with the same intersection point, and the intersection point is located on the rotating axis of the first synchronizer.

Each set of rotating assemblies forms a small rotating unit, and the rotating band 326 of each set of rotating assemblies can rotate cyclically around the four rotating members. Since the extension line of the symmetry axis of the rotation assembly is located on the rotation axis of the first synchronizer, when the rotation band 326 moves to a position contacting with the synchronizer with the first fork 32, the rotation direction of the rotation band 326 of each rotation assembly is almost the same as the rotation direction of the corresponding position on the synchronizer, and the sliding friction of the rotation band 326 of each rotation assembly with the synchronizer is small. By adopting the mode, the structure is simple, the rotating assemblies can be arranged in parallel, the installation is convenient, the surface contact is realized, and the sliding friction is reduced.

The transmission four-gear shifting device of the 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 with the first driving mechanism 3, the shift area 112 can push the first synchronizer to carry out the gear engaging operation of two gears by the first driving mechanism 3 along with the rotation of the shift drum 1; when the shift area 112 of the shift drum 1 is rotated to a position where it is connected to the second driving mechanism 5, the shift area 112 can push the second synchronizer 4 to perform an engaging operation of the other two gears by the second driving mechanism 5 as the shift drum 1 is rotated; because the areas where the first driving mechanism 3 and the second driving mechanism 5 are connected with the gear shifting drum 1 are in different angular positions, two gears can be respectively engaged only by two driving mechanisms of one gear shifting drum 1, and the engaging operation of the four gears can be completed only by driving one gear shifting drum 1 to rotate by one motor 6, so that fewer executing mechanisms for gear shifting are needed, the engaging action is simple, and the operation is more reliable.

Example 8

Embodiment 8 of the present invention discloses an automobile including the anti-sintering oil guide structure of any one of the differentials of embodiments 1 to 4, or the differential of embodiment 5, or the drive flange of embodiment 6, or the transmission four-gear shift device of embodiment 7.

The automobile in embodiment 8 of the invention may be a conventional fuel automobile such as a gasoline automobile, a diesel automobile, or the like, or may be a new energy automobile. The new energy vehicles include, but are not limited to, pure electric (BEV/EV), hybrid electric (HEV, PHEV, and REEV), Fuel Cell Electric (FCEV), and solar cell electric (pv) vehicles.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.