CN113833832A

CN113833832A - Gearbox lubricating system, transmission and vehicle

Info

Publication number: CN113833832A
Application number: CN202111167794.7A
Authority: CN
Inventors: 苏倩; 唐亚卓
Original assignee: Amte Shanghai New Energy Technology Co ltd
Current assignee: Amte Shanghai New Energy Technology Co ltd
Priority date: 2021-09-29
Filing date: 2021-09-29
Publication date: 2021-12-24

Abstract

The invention provides a gearbox lubricating system, a gearbox and a vehicle, belongs to the technical field of gearboxes, and solves the problems that in the prior art, cost is increased due to independent lubrication between gearbox bodies and large temperature difference possibly exists between the gearbox bodies. This gearbox lubricating system includes main gear box, auxiliary transmission, first oilhole and second oilhole, is provided with first gear pair in the main gear box, and first oilhole and second oilhole all communicate main gear box and auxiliary transmission, and wherein, along vertical direction, first oilhole position is less than second oilhole position, and first gear pair is used for sending the lubricating oil in the main gear box to auxiliary transmission through the second oilhole in to unnecessary lubricating oil can flow back to the main gear box in through first oilhole in the auxiliary transmission. The gearbox lubricating system, the transmission and the vehicle provided by the invention have the advantages of low cost, good lubricating effect, convenience for monitoring and controlling the oil temperature and good system stability.

Description

Gearbox lubricating system, transmission and vehicle

Technical Field

The invention belongs to the technical field of transmissions, and particularly relates to a gearbox lubricating system, a transmission and a vehicle.

Background

With the development of new energy automobiles, the energy conversion efficiency of the power assembly has always been a major concern, wherein in addition to the conversion efficiency of the driving motor, the transmission efficiency of the transmission is also an important index.

In an automobile gearbox, bearings and gears are indispensable important components, and the lubricating effect of the bearings and the gears under the operating condition is one of key factors influencing the transmission efficiency of the gearbox. For the lubrication of a multi-box gearbox system, a design mode of independent lubrication of each box is usually adopted, but the cost is correspondingly increased because sealing parts such as oil seals and the like need to be added at the connecting positions between the boxes, and in addition, because the lubricating oil between the boxes is in a mutually isolated state, a large temperature difference possibly exists between the boxes, and the monitoring and the control of the oil temperature of the system are not facilitated.

Disclosure of Invention

In view of the above, the invention provides a gearbox lubrication system, a transmission and a vehicle, which are used for solving the problems that in the prior art, cost is increased due to independent lubrication between gearbox bodies and a large temperature difference possibly exists between the gearbox bodies.

The technical scheme adopted by the invention is as follows:

in a first aspect, the present invention provides a gearbox lubrication system comprising: the gearbox comprises a main gearbox and an auxiliary gearbox, wherein a first gear pair is arranged in the main gearbox; the first oil hole and the second oil hole are communicated with the main gearbox and the auxiliary gearbox; the first oil hole is lower than the second oil hole in the vertical direction, the first gear pair is used for conveying lubricating oil in the main gearbox to the auxiliary gearbox through the second oil hole, and redundant lubricating oil in the auxiliary gearbox flows back to the main gearbox through the first oil hole.

As a preferable mode of the transmission lubrication system, when the lubricating oil in the sub-transmission is accumulated to a first liquid level, the lubricating oil in the sub-transmission flows into the main transmission through the first oil hole, the lubricating oil level in the main transmission is a second liquid level, the first liquid level is the same as the lowest point of the first oil hole, and the second liquid level is lower than the first liquid level.

As a preferable mode of the transmission lubrication system described above, the first oil hole maximum flow rate is greater than or equal to the second oil hole maximum flow rate.

As a preferable scheme of the transmission lubrication system, the main transmission includes a first case wall, the first oil hole and the second oil hole penetrate through the first case wall, and an oil collecting mechanism is disposed on the first case wall.

As a preferable mode of the transmission lubrication system, the oil collecting mechanism includes a first oil guiding rib, and a vertical end of the first oil guiding rib is disposed on one side of the second oil hole.

As a preferable scheme of the gearbox lubricating system, the oil collecting mechanism further comprises a second oil guiding rib, an oil collecting groove is formed between the second oil guiding rib and the first oil guiding rib, and the oil collecting groove is communicated with the second oil hole.

As a preferable mode of the transmission lubrication system described above, an end of the oil sump that is away from the second oil hole is higher than an end of the oil sump that is close to the second oil hole in the vertical direction.

In a preferred embodiment of the transmission lubrication system, the first gear pair includes a first gear and a second gear, the first gear and the second gear are helical gears, and a leading meshing portion of the first gear and a trailing meshing portion of the second gear are closer to the oil collecting mechanism than the trailing meshing portion.

In a second aspect, the present invention provides a transmission comprising a gearbox lubrication system as described above.

In a third aspect, the present invention provides a vehicle comprising a gearbox lubrication system or transmission as described above.

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

the invention provides a gearbox lubricating system which comprises a main gearbox, an auxiliary gearbox, a first oil hole and a second oil hole, wherein a first gear pair is arranged in the main gearbox, the first gear pair generates rotary motion in the running process of the gearbox, part of lubricating oil in the main gearbox is attached to the first gear pair to generate rotary motion along with the first gear pair, centrifugal motion is generated around the first gear pair, the first oil hole and the second oil hole are communicated with the main gearbox and the auxiliary gearbox, the lubricating oil splashed outwards flows into the auxiliary gearbox along with the second oil hole, the position of the first oil hole is lower than that of the second oil hole along the vertical direction, after the lubricating oil flowing into the auxiliary gearbox from the second oil hole accumulates to the lowest point of the first oil hole, the redundant lubricating oil in the auxiliary gearbox overflows into the main gearbox from the first oil hole, and thus a dynamic circulation communicated lubricating system is formed, the invention can ensure that the main gearbox and the auxiliary gearbox respectively maintain the designed oil quantity in a good lubricating state, and a dynamic circulating system can be formed between the main box and the auxiliary box, so that the oil temperature of the whole transmission system tends to be more stable and level, and the oil temperature is convenient to monitor and control. The transmission provided by the invention comprises the transmission lubricating system, the cost is low, the lubricating effect is good, and the oil temperature can be conveniently monitored and controlled. The vehicle provided by the invention comprises the gearbox lubricating system or the transmission, is low in cost, is convenient for monitoring and controlling the oil temperature, and is good in system stability.

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 diagram illustrating the relationship between the first liquid level and the second liquid level according to the present invention;

FIG. 2 is a diagram showing the positional relationship of the first and second oil holes in accordance with the present invention;

FIG. 3 is a schematic structural view of the main transmission case of the present invention;

FIG. 4 is a three-dimensional block diagram of the transmission four speed shifter of the present invention;

FIG. 5 is a graph of the angular position of the shift area of the shift drum of the present invention in relation to the first and second drive mechanisms;

FIG. 6 is a three-dimensional block diagram of the shift drum of the present invention;

FIG. 7 is a three-dimensional block diagram of the first drive mechanism of the present invention engaged with a shift drum;

FIG. 8 is a three-dimensional block diagram of the first drive mechanism of the present invention engaged with a shift drum;

FIG. 9 is a three-dimensional block diagram of the first drive mechanism of the present invention in cooperation with a first synchronizer;

FIG. 10 is a top view of the structure for allowing the rotating belt to rotate with the synchronizer according to the present invention;

FIG. 11 is a side view of the structure for rotating the rotating belt with the synchronizer according to the present invention;

FIG. 12 is a view showing the positional relationship of four rotating members according to the present invention;

FIG. 13 is a three-dimensional block diagram of a drive flange of the present invention;

FIG. 14 is a three-dimensional block diagram of another perspective of the drive flange of the present invention;

FIG. 15 is a three-dimensional view of the structure of the drive flange of the present invention for connection to a drive shaft;

FIG. 16 is a side view of the drive flange of the present invention;

FIG. 17 is a front view of the drive flange of the present invention;

FIG. 18 is a schematic illustration of a three-element transmission structure of the present invention in a disconnected configuration;

FIG. 19 is a schematic diagram of two sets of sub-transmission structures of the transmission flange of the present invention arranged in a staggered manner in the circumferential direction;

FIG. 20 is a schematic structural view of a vehicle;

parts and numbering in the drawings:

1. a main gear box; 10. a first gear pair; 101. a first gear; 102. a second gear; 11. second liquid level

2. A sub-transmission case; 20. a first liquid level;

3. a first tank wall; 30. a first oil hole; 31. a second oil hole; 32. an oil collecting mechanism; 321. a first oil guiding rib; 322. a second oil guiding rib; 323. an oil sump;

100. a shift drum; 110. a guide groove; 111. a shift area; 112. a neutral zone; 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;

210. a limiting groove; 300. a first drive mechanism; 310. a first slider; 320. a first shift fork; 330. 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; 51. a second slider; 52. a second fork; 53. a second connecting member; 6. a motor; 7. a rotating shaft;

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;

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. 20, 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 fig. 3, an embodiment of the present invention discloses a gearbox lubrication system, including:

the lubricating oil lubricating device comprises a main gearbox 1 and an auxiliary gearbox 2, wherein a first gear pair 10 is arranged in the main gearbox 1, a second gear pair is arranged in the auxiliary gearbox 2, the first gear pair 10 rotates in the running process of the gearbox, a part of lubricating oil in the main gearbox 1 adheres to the first gear pair 10 and rotates along with the first gear pair 10, centrifugal motion is generated around the lubricating oil, and the first gear pair 10 is used for conveying the lubricating oil in the main gearbox 1 to the auxiliary gearbox 2 through a second oil hole 31;

the first oil hole 30 and the second oil hole 31, the first oil hole 30 and the second oil hole 31 are both communicated with the main transmission case 1 and the auxiliary transmission case 2, the lubricating oil which is driven by the first gear pair 10 and splashed outwards flows into the auxiliary transmission case 2 along with the second oil hole 31, the position of the first oil hole 30 is lower than the position of the second oil hole 31 along the vertical direction, the lubricating oil which flows into the auxiliary transmission case 2 from the second oil hole 31 can be accumulated to the lowest point of the first oil hole 30, and the redundant lubricating oil in the auxiliary transmission case 2 can overflow from the first oil hole 30 to the main transmission case 1, thereby forming a dynamic circulation communication type lubricating system, not only ensuring that the main transmission case 2 maintains the designed oil quantity in a good lubricating state respectively, but also forming a dynamic circulation system between the main transmission case and the auxiliary transmission case, enabling the oil temperature of the whole transmission system to tend to be more stable and level, and being convenient for monitoring and controlling the oil temperature, in addition, the invention utilizes the gear pair which normally runs in the gearbox to provide power for the lubricating system of the gearbox, thereby saving the cost.

To facilitate understanding of the gearbox lubrication system, the main gearbox 1 and the auxiliary gearbox 2 will now be further described as follows:

the main gear box 1 functions in the operation of the vehicle as follows: the transmission ratio is changed to meet the requirements of different driving conditions on traction force, so that the engine can work under the favorable condition as much as possible and the driving speed requirement can be met; the vehicle can run in reverse to meet the requirement of the vehicle running in reverse; interrupting power transmission, namely interrupting power transmission to a driving wheel when an engine is started, runs at an idle speed, shifts gears of the automobile or needs to stop; neutral is achieved and when the clutch is engaged, the transmission stops outputting power. The auxiliary gearbox 2 is used for heavy-duty automobiles which have large empty and full-load mass change, complex use conditions, and particularly have mild torque change of diesel engines, poor adaptability, need to enlarge the transmission ratio range and increase multiple gear numbers so as to meet the requirements of dynamic property and economy under various use conditions.

Referring to fig. 1 to 3, the transmission lubrication system after normal operation is a dynamic circulation communication lubrication system, and when the lubrication system operates, a certain amount of lubricating oil is added into the main transmission case 1, and at this time, no lubricating oil exists in the auxiliary transmission case 2. With the rotation of the first gear pair 10, the lubricating oil in the main transmission case 1 gradually flows into the sub-transmission case 2 through the second oil holes, the auxiliary gearbox 2 is a closed box body, lubricating oil can be continuously accumulated when entering the auxiliary gearbox 2, when the lubricating oil in the sub-transmission 2 has accumulated to the lowest point of the first oil hole 30, the lubricating oil in the sub-transmission 2 flows back to the main transmission 1 through the first oil hole, and at this time, the lubricating oil page in the auxiliary gearbox 2 is a first liquid level 20, the height of the first liquid level 20 is consistent with the height of the lowest point of the first oil hole 30, in this case, the lubricating oil in the sub-transmission 2 is merged with the original lubricating oil thereafter, and an equal amount of merged lubricating oil overflows, meanwhile, the liquid level of the lubricating oil flowing into the main transmission case 1 is the second liquid level 11, and the height of the second liquid level 11 is always lower than the height of the first liquid level 20, so that the principle that the liquid flows from top to bottom is satisfied. In the lubricating system that has reached dynamic circulation, the volume that lubricating oil reduces in the main gearbox 1 is unanimous with the volume that lubricating oil increases in the auxiliary gearbox 2, and the oil mass of the lubricating oil that overflows in the auxiliary gearbox 2 is unanimous with the lubricating oil mass of backward flow to main gearbox 1, so reciprocating circulation can guarantee that main and auxiliary gearbox 2 keeps the design oil mass of good lubricated state separately, and makes the oil temperature of whole derailleur system tend to more steady level, the monitoring and the control of the oil temperature of being convenient for.

In this embodiment, preferably, the first oil hole 30 and the second oil hole 31 are both circular holes, and the number of the second oil holes 31 is equal to one of the two first oil holes 30, so as to ensure that the maximum flow of the first oil hole 30 is greater than or equal to the maximum flow of the second oil hole 31, the sectional area of the first oil hole 30 should be greater than or equal to the sum of the sectional areas of the two second oil holes 31, so as to ensure that the lubricating oil flowing into the auxiliary transmission 2 can completely overflow the auxiliary transmission 2, if the maximum flow of the first oil hole 30 is less than the maximum flow of the second oil hole 31, that is, the lubricating oil flowing into the auxiliary transmission 2 is more than the lubricating oil flowing back into the main transmission 1, and the lubricating oil can be accumulated in the auxiliary transmission 2, so that the effect of dynamic circulation lubrication cannot be achieved. The core of ensuring that the maximum flow of the first oil hole 30 is greater than or equal to the maximum flow of the second oil hole 31 is that the sectional area of the first oil hole 30 should be greater than or equal to the sum of the sectional areas of the second oil holes 31, therefore, the shapes of the first oil hole 30 and the second oil hole 31 include but are not limited to circular holes, which can be square holes or other irregular holes, and the number of the first oil hole 30 and the second oil hole 31 should not be limited, the two second oil holes 31 adopted in the embodiment also have an advantage, the first gear pair 10 in the main transmission case 1 includes two gears, each gear can correspond to one second oil hole, so that the internal space of the transmission can be fully utilized, the alternate oil feeding of the maximized oil quantity is realized, and the oil temperature of the whole transmission system tends to be more stable.

Referring to fig. 1 to 3, the main transmission case 1 includes a first case wall 3, the first case wall 3 is close to the sub-transmission case 2, a first oil hole 30 and a second oil hole 31 penetrate through the first case wall 3, an oil collecting mechanism 32 is disposed on the first case wall 3, the lubricating oil splashed by the first gear pair 10 during the rotation process is dispersed outwards, only a small amount of the lubricating oil passes through the second oil hole and enters the sub-transmission case 2, in order to make the transmission lubrication system fully function, the oil collecting mechanism 32 is disposed to gather the dispersed lubricating oil together, the circulating amount of the lubricating oil of the lubrication system is increased, the lubrication effect is better, and the oil temperature between the two case bodies is more stable.

Preferably, the oil collecting mechanism 32 includes a first oil guiding rib 321, the first oil guiding rib 321 is a plate-shaped structure and is disposed on the first case wall 3, and the end of the first oil guiding rib 321 in the vertical direction is disposed on one side of the second oil hole 31 and contacts with the edge of the second oil hole 31. In this embodiment, the first oil guiding rib 321 is vertically arranged from top to bottom along a vertical direction, an upper portion is a head end, a lower portion is a tail end, the head end is connected with the first wall 3 and the top wall of the main transmission case 1 in a seamless manner, during the rotation of the first gear pair 10, the splashed lubricating oil is blocked by the first oil guiding rib 321, the splashed lubricating oil is attached to the first oil guiding rib 321 after contacting the first oil guiding rib 321, and flows down from top to bottom along the plate surface of the first oil guiding rib 321 under the action of gravity, because the tail end of the first oil guiding rib 321 is arranged at one side of the second oil hole 31, the attached lubricating oil finally flows to the tail end of the first oil guiding rib 321 and flows into the second oil hole 31, so that the larger the amount of the lubricating oil in the second oil hole 31 depends on the amount of the lubricating oil attached to the first oil guiding rib 321, the larger the surface area of the first oil guiding rib 321, the larger the amount of the lubricating oil attached to the first oil guiding rib, the more lubricating oil that gearbox lubricating system circulates in a certain period of time, lubricating system's lubricated effect is better, and the oil temperature between two boxes can be more steady. In the present embodiment, the first oil bead 321 is not limited to a plate shape, and may be a columnar shape, a curved shape, or the like, and generally, the larger the surface area of the first oil bead 321, the better the lubrication effect of the transmission lubrication system.

In the present embodiment, the specific structure of the oil collecting mechanism 32 includes, but is not limited to, the first oil guiding rib 321, and may also be a groove-like structure, for example, a groove is formed in the first case wall 3, the four walls of the groove are inclined surfaces, the notch of the groove connects with the second oil hole 31, and the splashed lubricating oil adheres to the four walls of the groove and gathers together to flow into the second oil hole 31.

Preferably, the oil collecting mechanism 32 further includes a second oil guiding rib 322, an oil collecting groove 323 is formed between the second oil guiding rib 322 and the first oil guiding rib 321, the oil collecting groove 323 is communicated with the second oil hole, the second oil guiding rib 322 is obliquely arranged and extends upwards along the joint of the second oil guiding rib and the first oil guiding rib 321, and the splashed lubricating oil can be effectively gathered in the oil collecting groove 323. Further, the end of the oil collecting groove 323 away from the second oil hole 31 is higher than the end of the oil collecting groove 323 close to the second oil hole 31 in the vertical direction, so that the lubricating oil in the oil collecting groove 323 is prevented from flowing out.

Referring to fig. 3, the first gear pair 10 includes a first gear 101 and a second gear 102, the first gear 101 and the second gear 102 are helical gears, the first meshing portion of the first gear 101 and the second gear 102 is closer to the oil collecting mechanism 32 than the second meshing portion, because the first gear 101 and the second gear 102 are both helical gears, the lubricating oil excited by the two gears will not only do centrifugal motion, but also will spread along the rack-and-pinion rotation direction, in this embodiment, the gear meshing portion closer to the oil collecting mechanism 32 is the first meshing portion, the gear meshing portion farther from the oil collecting mechanism 32 is the second meshing portion, the first gear 101 rotates right, the second gear 102 rotates left, the first gear 101 and the second gear 102 rotate in the direction toward the meshing portions of the two, the oil collecting mechanism 32 of the main transmission case 1 is closer to the middle portions of the first gear 101 and the second gear 102, when the first gear 101 and the second gear 102 rotate, the right-handed first gear 101 throws the kicked-up lubricating oil to one side of the oil collecting mechanism 32, and the left-handed second gear 102 throws the kicked-up lubricating oil to the other side of the oil collecting mechanism 32, so that the dispersed lubricating oil can be sufficiently collected.

Example 2

The embodiment 2 of the invention discloses a transmission, which adopts the transmission lubricating system, has low cost and good lubricating effect and is convenient for monitoring and controlling the oil temperature.

In addition, 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 shift device of the present embodiment includes a shift drum 100, a motor 6, a first synchronizer, a first drive mechanism 300, a second synchronizer 4, and a second drive mechanism 5.

As shown in fig. 5 and 6, in which the shift drum 100 is provided with a guide groove 110 extending in a circumferential direction thereof, the guide groove 110 includes shift areas 111 that rotate to different angular positions with the shift drum 100;

as shown in fig. 6, the shift drum 100 may be provided in a cylindrical shape, the aforementioned guide groove 110 may be provided on a cylindrical peripheral wall of the shift drum 100, the shift block 111 is a partial area of the entire guide groove 110, the shift drum 100 may rotate around its own axis, and the shift block 111 may also rotate to different positions in response to the rotation of the shift drum 100.

As shown in fig. 7, wherein the first synchronizer is used to engage in a gear operation in the 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 300 is slidably connected with the guiding groove 110 at the first angular position 120 of the shift drum 100, and the first driving mechanism 300 is configured to push the engaging member of the first synchronizer to move to engage in a first axial position along the axial direction of the first synchronizer or push the engaging member of the first synchronizer to move to engage in a second axial position along the axial direction of the first synchronizer under the driving of the shift area 111, 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 100 rotates, the shift area 111 can rotate to a range of angular positions in sliding connection with the first drive mechanism 300. In this angular position range, the position of the shift area 111 in connection with the first drive also changes as the shift drum 100 rotates. Due to the difference in the distance between each position of the shift region 111 and the first synchronizer in the axial direction, the shift region 111 can drive the first driving mechanism 300 to move in the axial direction during the rotation process, and the first driving mechanism 300 moves in the axial direction and pushes the engaging member of the first synchronizer to move in the axial direction.

In this embodiment, the first driving mechanism 300 includes a first slider 310, a first fork 320, and a first link 330, the first link 330 is connected to the first slider 310 and the first fork 320, 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 moving direction of the first connecting member 330 is restricted, and it can move only in the axial direction. The guide grooves 110 are different in distance from the first synchronizer or the second synchronizer 4 at different circumferential positions in some regions as viewed in the axial direction of the shift drum 100. When the shift drum 100 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 with respect to the guide groove 110. Since the first link 330 connects the first slider 310 and the first fork 320 together, the first fork 320 also moves in the axial direction in synchronization with the first slider 310. Wherein the first coupling member 330 may be disposed at a side of the shift drum 100 in a radial direction, the first slider 310 is disposed in the radial direction of the shift drum 100, one end of the first slider 310 is coupled to the first coupling member 330, and the opposite end is inserted into the guide groove 110.

As shown in fig. 4 and 8, wherein the second synchronizer 4 is used for engaging the gear engaging 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 100, 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 to engage in a third axial position under the drive of the shift area 111, or to push the engaging member of the second synchronizer 4 to move in the axial direction of the second synchronizer 4 to engage in a fourth axial position, 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 100 rotates, the shift region 111 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 111 in connection with the second drive also changes as the shift drum 100 rotates. Due to the difference in the distance between the shift area 111 and the second synchronizer 4 in the axial direction at each position, the shift area 111 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 simultaneously 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 51, a second fork 52 and a second link 53, the second link 53 is connected to the second slider 51 and the second fork 52, respectively, and the second slider 51 slides along the guide slot 110.

Wherein the width of the guiding groove is slightly larger than the width of the second slider 51 and the direction of movement of the second link 53 is constrained such that it can only move in the axial direction. The guide grooves 110 are different in distance from the first synchronizer or the second synchronizer 4 at different circumferential positions in some regions as viewed in the axial direction of the shift drum 100. When the shift drum 100 rotates, different positions of the guide groove 110 come into contact with the second slider 51, 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 slide member 51 and the second fork 52 together, the second fork 52 also moves in the axial direction in synchronization with the second slide member 51. Wherein the second link 53 may be disposed at a side of the shift drum 100 in a radial direction, the second slider 51 is disposed in the radial direction of the shift drum 100, one end of the second slider 51 is connected to the second link 53, and the opposite end is inserted into the guide groove 110.

As shown in fig. 4, the motor 6 is used to drive the shift drum 100 to rotate, so that the shift area 111 drives the first driving mechanism 300 and the second driving mechanism 5 to move back and forth along the axial direction of the shift drum 100. The motor 6 bit, the first synchronizer and the second synchronizer 4 are located on two sides of the axial direction of the gear shifting drum 100, and the motor 6 and the gear shifting drum 100 are coaxially arranged.

In the embodiment, the motor 6 and the two driving mechanisms are separately arranged along the axial direction and are positioned at two sides of the shift drum 100, 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 100 are coaxially arranged, the structure can be more compact, and the transmission of power between the motor 6 and the shift drum 100 is also utilized.

As a preferred implementation manner, in this embodiment, the transmission four-gear shifting device further includes a rotating shaft 7, the shift drum 100 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 100 to rotate. The transmission process is simpler and more reliable by directly adopting the interference fit mode for transmission between the rotating shaft and the gear shifting drum 100. The motor 6 is arranged on an assembly box body, the gear shifting drum 100 is positioned on the box body through a rotating shaft 7, the shaft rotating shaft 7 of the gear shifting drum 100 and the shaft rotating shaft 7 of the gear shifting drum 100 are relatively fixed, and the rotating shaft 7 can rotate on the box body.

As shown in fig. 9, in the present embodiment, an annular stopper groove 210 is formed in a peripheral wall of the first synchronizer and/or the second synchronizer 4, a toggle member 325 is disposed at an end of the first fork 320 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 stopper groove 210.

In this embodiment, the width of the limiting groove 210 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 2 times the axial gap between the toggle member 325 and the limiting groove 210, 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 210. By adopting the structure, after the shifting piece 325 is inserted into the limit groove 210 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 limit groove 210, and a sufficient gap is left between the other side of the shifting piece 325 and the other side wall of the limit groove 210. Therefore, after the shifting part 325 and the limiting groove 210 are relatively displaced due to unexpected small vibration, the other side of the shifting part 325 cannot be in contact with the other side wall of the limiting groove 210, so that the situation that the shifting part 325 shifts the limiting groove 210 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 in the axial direction exceeds the axial gap between the shifting member 325 and the limiting groove 210, 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 210 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 320, 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. 10 to 12, the first fork 320 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 having a cylindrical shape, 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 320, 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 connected to the first fork 320 by a smooth surface.

With the above-described structure, when the rotating band 326 moves to a position contacting the synchronizer with the first fork 320, 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 320 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 320 rotates and connects, rotate the one end of taking 326 and meet with the relative other end after the outer wall that the seventh rotation piece, the eighth rotation piece was 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 320, the rotation direction of the rotation band 326 of each rotation assembly is almost the same as that 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 100 to rotate by using the motor 6, when the shift area 111 of the shift drum 100 rotates to the position connected with the first driving mechanism 300, the shift area 111 can push the first synchronizer to carry out the gear engaging operation of two gears by the first driving mechanism 300 along with the rotation of the shift drum 100; when the shift area 111 of the shift drum 100 is rotated to a position connected with the second driving mechanism 5, the shift area 111 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 100 rotates; since the areas where the first driving mechanism 300 and the second driving mechanism 5 are connected with the shift drum 100 are at different angular positions, two gears can be engaged by only one shift drum 100 and two driving mechanisms respectively, and the four-gear engaging operation can be completed by only one motor 6 driving one shift drum 100 to rotate, so that fewer gear shifting executing mechanisms are needed, the engaging action is simple, and the operation is more reliable.

Example 3

As shown in fig. 13, the present embodiment further 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, and the first transmission structure 420 is used for connecting with a transmission output shaft and transmitting the torque of the transmission output shaft to the flange body 410;

as shown in fig. 14 and 16, the output shaft of the transmission is connected to the flange body 410 through the first transmission structure 420, when the output shaft of the transmission rotates, the torque of the output shaft of the transmission acts on the first transmission structure 420, and the flange body 410 is driven to rotate together through the first transmission structure 420, so that 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 driven to rotate by the gearbox output shaft, the torque of the flange body 410 is transmitted to the drive shaft through the second transmission 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. 17, 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. 16, 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 achieve connection of the flange main body 410 with the transmission output shaft, and the second connection portion 412 is used to achieve connection of the flange main body 410 with 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 transmission output shaft transmission shafts are compactly distributed on both sides of the flange 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. 19, 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. 18, 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. 15, 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 4

The embodiment 4 of the invention discloses a vehicle which comprises all the systems or structures, is low in cost, is convenient for monitoring and controlling the oil temperature, and is good in system stability. The vehicle further comprises the aforementioned drive flange.

The vehicle in embodiment 4 of the invention can be a traditional fuel vehicle such as a gasoline vehicle, a diesel vehicle and the like, and can also be a new energy vehicle. 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.

Claims

1. A transmission lubrication system, comprising:

the gearbox comprises a main gearbox and an auxiliary gearbox, wherein a first gear pair is arranged in the main gearbox;

the first oil hole and the second oil hole are communicated with the main gearbox and the auxiliary gearbox;

the first oil hole is lower than the second oil hole in the vertical direction, the first gear pair is used for conveying lubricating oil in the main gearbox to the auxiliary gearbox through the second oil hole, and redundant lubricating oil in the auxiliary gearbox flows back to the main gearbox through the first oil hole.

2. The transmission lubrication system according to claim 1, wherein when the lubricating oil in the sub-transmission accumulates to a first level, the lubricating oil in the sub-transmission flows into the main transmission through the first oil hole, the lubricating oil level in the main transmission is a second level, the first level coincides with the lowest point height of the first oil hole, and the second level is lower than the first level.

3. The transmission lubrication system of claim 1, wherein the first oil hole maximum flow rate is greater than or equal to the second oil hole maximum flow rate.

4. The transmission lubrication system of claim 1, wherein said main transmission case includes a first case wall, said first oil hole and said second oil hole extending through said first case wall, said first case wall having oil collection means disposed thereon.

5. The transmission lubrication system according to claim 4, wherein the oil gathering mechanism includes a first oil guide rib, and a tip end of the first oil guide rib in a vertical direction is provided on one side of the second oil hole.

6. The lubrication system of a transmission according to claim 5, wherein the oil collecting mechanism further comprises a second oil guiding rib, an oil collecting groove is formed between the second oil guiding rib and the first oil guiding rib, and the oil collecting groove is communicated with the second oil hole.

7. The transmission lubrication system of claim 6, wherein an end of the oil sump that is distal from the second oil hole is higher than an end of the oil sump that is proximal to the second oil hole in the vertical direction.

8. A gearbox lubrication system as claimed in any one of claims 4 to 6 in which the first gear pair comprises a first gear and a second gear, the first and second gears being helical gears, the first and second gears being closer to the oil gathering means at the leading engagement than at the trailing engagement.

9. A transmission comprising a gearbox lubrication system according to any of claims 1-8.

10. A vehicle comprising a gearbox lubrication system as defined in any one of claims 1 to 8 or a transmission as defined in claim 9.