Transmission lubrication system, transmission and vehicle

Abstract

The present invention provides a gearbox lubrication system, a transmission and a vehicle, which belongs to the technical field of transmissions, and solves the problems existing in the prior art that independent lubrication between gearbox housings leads to increased costs and that there may be a large temperature difference between housings. The gearbox lubrication system includes a main gearbox, an auxiliary gearbox, a first oil hole and a second oil hole, wherein a first gear pair is provided in the main gearbox, and the first oil hole and the second oil hole are both connected to the main gearbox and the auxiliary gearbox, wherein the first oil hole is located lower than the second oil hole in the vertical direction, and the first gear pair is used to deliver the lubricating oil in the main gearbox to the auxiliary gearbox through the second oil hole, and the excess lubricating oil in the auxiliary gearbox will flow back to the main gearbox through the first oil hole. The gearbox lubrication system, transmission and vehicle provided by the present invention have low cost, good lubrication effect, are convenient for monitoring and controlling the oil temperature, and have good system stability.

Description

Technical Field

[0001] The present invention belongs to the technical field of transmissions, and in particular relates to a transmission lubrication system, a transmission and a vehicle. Background Art

[0002] With the development of new energy vehicles, the energy conversion efficiency of the powertrain has always been a focus of attention. In addition to the conversion efficiency of the drive motor, the transmission efficiency of the gearbox is also a very important indicator.

[0003] In automobile gearboxes, bearings and gears are indispensable and important components, and their lubrication effect under operating conditions is one of the key factors affecting the transmission efficiency of the gearbox. For the lubrication of multi-box gearbox systems, the design method of independent lubrication of each box is often adopted, but since sealing components such as oil seals need to be added at the connection positions between the boxes, the cost will increase accordingly. In addition, since the lubricating oil between the boxes is isolated from each other, there may be a large temperature difference between the boxes, which is not conducive to the monitoring and control of the system oil temperature. Summary of the invention

[0004] In view of this, the present invention provides a gearbox lubrication system, a transmission and a vehicle to solve the problems in the prior art of independent lubrication between gearbox cases leading to increased costs and possible large temperature differences between the cases.

[0005] The technical solution adopted by the present invention is:

[0006] In a first aspect, the present invention provides a gearbox lubrication system, comprising: a main gearbox and an auxiliary gearbox, wherein a first gear pair is arranged in the main gearbox; a first oil hole and a second oil hole, wherein the first oil hole and the second oil hole both communicate with the main gearbox and the auxiliary gearbox; wherein, along the vertical direction, a position of the first oil hole is lower than a position of the second oil hole, the first gear pair is used to deliver the lubricating oil in the main gearbox to the auxiliary gearbox through the second oil hole, and excess lubricating oil in the auxiliary gearbox will flow back to the main gearbox through the first oil hole.

[0007] As a preferred solution of the above-mentioned gearbox lubrication system, when the lubricating oil in the auxiliary gearbox accumulates to a first liquid level, the lubricating oil in the auxiliary gearbox flows into the main gearbox through the first oil hole, and the lubricating oil liquid level in the main gearbox is a second liquid level. The first liquid level height is consistent with the lowest point height of the first oil hole, and the second liquid level height is lower than the first liquid level height.

[0008] As a preferred solution of the above-mentioned gearbox lubrication system, the maximum flow rate of the first oil hole is greater than or equal to the maximum flow rate of the second oil hole.

[0009] As a preferred solution of the above-mentioned gearbox lubrication system, the main gearbox includes a first box wall, the first oil hole and the second oil hole penetrate the first box wall, and an oil collecting mechanism is provided on the first box wall.

[0010] As a preferred solution of the above-mentioned gearbox lubrication system, the oil collecting mechanism includes a first oil guiding rib, and the end of the first oil guiding rib in the vertical direction is arranged on one side of the second oil hole.

[0011] As a preferred solution of the above-mentioned gearbox lubrication system, the oil collecting mechanism further includes 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 connected to the second oil hole.

[0012] As a preferred solution of the above-mentioned gearbox lubrication system, along the vertical direction, an end of the oil collecting groove away from the second oil hole is higher than an end of the oil collecting groove close to the second oil hole.

[0013] As a preferred solution of the above-mentioned gearbox 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 the first gear and the second gear are closer to the oil collecting mechanism at the preceding meshing portion than at the following meshing portion.

[0014] In a second aspect, the present invention provides a transmission, comprising the aforementioned transmission lubrication system.

[0015] In a third aspect, the present invention provides a vehicle comprising the aforementioned transmission lubrication system or transmission.

[0016] In summary, the beneficial effects of the present invention are as follows:

[0017] The gearbox lubrication system provided by the present invention comprises a main gearbox, an auxiliary gearbox, a first oil hole and a second oil hole. A first gear pair is arranged in the main gearbox. During the operation of the gearbox, the first gear pair will generate a rotational motion, and a part of the lubricating oil in the main gearbox will adhere to the first gear pair and then generate a rotational motion, and generate a centrifugal motion in all directions. The first oil hole and the second oil hole are both connected to the main gearbox and the auxiliary gearbox. The lubricating oil splashing outward will flow into the auxiliary gearbox along the second oil hole, and in the vertical direction, the position of the first oil hole is lower than the position of the second oil hole. 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 excess lubricating oil in the auxiliary gearbox will overflow from the first oil hole into the main gearbox, thereby forming a dynamic circulation interconnected lubrication system, which can not only ensure that the main and auxiliary gearboxes each maintain a designed oil volume in a good lubrication state, but also form a dynamic circulation system between the main box and the auxiliary box, so that the oil temperature of the overall transmission system tends to a more stable level, which is convenient for monitoring and controlling the oil temperature. In addition, the present invention uses the gear pair in normal operation in the gearbox to provide power for the gearbox lubrication system, saving costs. The transmission provided by the present invention includes the aforementioned transmission lubrication system, which has low cost, good lubrication effect, and is convenient for monitoring and controlling the oil temperature. The vehicle provided by the present invention includes the aforementioned transmission lubrication system or transmission, which has low cost, is convenient for monitoring and controlling the oil temperature, and has good system stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solution of the embodiment of the present invention, the drawings required for use in the embodiment of the present invention will be briefly introduced below. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work, and these are all within the protection scope of the present invention.

[0019] Figure 1 is a positional relationship diagram of the first liquid level and the second liquid level of the present invention;

[0020] Figure 2 A diagram showing the position relationship between the first oil hole and the second oil hole of the present invention;

[0021] Figure 3 It is a structural schematic diagram of the main gearbox of the present invention;

[0022] Figure 4 A three-dimensional structural diagram of the transmission four-speed shifting device of the present invention;

[0023] Figure 5 The optical relationship diagram of the angular position of the shifting area of ​​the shifting drum of the present invention and the first driving mechanism and the second driving mechanism;

[0024] Figure 6 A three-dimensional structural diagram of the shift drum of the present invention;

[0025] Figure 7 It is a three-dimensional structural diagram of the cooperation between the first driving mechanism and the shift drum of the present invention;

[0026] Figure 8 It is a three-dimensional structural diagram of the cooperation between the first driving mechanism and the shift drum of the present invention;

[0027] Fig. 9 A three-dimensional structural diagram of the cooperation between the first driving mechanism and the first synchronizer of the present invention;

[0028] Fig.10 A top view of the structure of the present invention that enables the rotating belt to rotate with the synchronizer;

[0029] Fig.11 A side view of a structure of the present invention that enables a rotating belt to rotate with a synchronizer;

[0030] Fig.12 is a position relationship diagram of four rotating parts of the present invention;

[0031] Fig.13 It is a three-dimensional structural diagram of the transmission flange of the present invention;

[0032] Fig.14 A three-dimensional structural diagram of the transmission flange of the present invention from another perspective;

[0033] Fig.15 A three-dimensional view of a structure in which the transmission flange of the present invention is connected to a transmission shaft;

[0034] Fig.16 It is a side view of the transmission flange of the present invention;

[0035] Fig.17 It is a front view of the transmission flange of the present invention;

[0036] Fig.18 It is a structural schematic diagram of the disconnection arrangement of three groups of sub-transmission structure groups of the present invention;

[0037] Fig.19 It is a structural schematic diagram of two groups of sub-transmission structures of the transmission flange of the present invention being staggered in the circumferential direction;

[0038] Fig. 20 A schematic diagram of the structure of the vehicle;

[0039] Parts and numbers in the picture:

[0040] 1. Main gearbox; 10. First gear pair; 101. First gear; 102. Second gear; 11. Second liquid level

[0041] 2. Auxiliary gearbox; 20. First liquid level;

[0042] 3. First box wall; 30. First oil hole; 31. Second oil hole; 32. Oil collecting mechanism; 321. First oil guide rib; 322. Second oil guide rib; 323. Oil collecting tank;

[0043] 100, shift drum; 110, guide groove; 111, shift area; 112, neutral area; 113, first guide section; 114, second guide section; 115, third guide section; 120, first angular position; 130, second angular position;

[0044] 210, limit groove; 300, first driving mechanism; 310, first sliding member; 320, first shift fork; 330, first connecting member; 321, first rotating member; 322, second rotating member; 323, third rotating member; 324, fourth rotating member; 325, shifting member; 326, rotating belt; 5, second driving mechanism; 51, second sliding member; 52, second shift fork; 53, second connecting member; 6, motor; 7, rotating shaft;

[0045] 410, flange body; 411, first connection part; 412, second connection part; 4121, limit hole; 4122, stopper; 420, first transmission structure; 430, first connection structure; 440, second transmission structure; 441, first sub-transmission structure group; 442, second sub-transmission structure group; 443, third sub-transmission structure group; 444, fourth sub-transmission structure group; 445, fifth sub-transmission structure group;

[0046] 600, power system; 700, transmission system; 800, body. DETAILED DESCRIPTION

[0047] In order to make the purpose, technical solution and advantages of the embodiment of the present invention clearer, the technical solution in the embodiment of the present invention will be clearly and completely described in conjunction with the drawings in the embodiment of the present invention. It should be noted that, in this article, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply that there is any such actual relationship or order between these entities or operations. In the description of the present invention, it should be understood that the orientation or position relationship indicated by the terms "center", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc. is based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. Moreover, the term "include", "comprise" or any other variant thereof is intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such a process, method, article or device. In the absence of further restrictions, the elements defined by the phrase "comprising..." do not exclude the existence of other identical elements in the process, method, article or device comprising the elements. If there is no conflict, the embodiments of the present invention and the various features in the embodiments can be combined with each other, all within the protection scope of the present invention.

[0048] See also Fig. 20 The vehicle is a commonly used means of transportation, mainly composed of a power system 600, a transmission system 700, a vehicle body 800, a chassis, etc. The transmission system 700 includes a transmission, a drive shaft, a differential, etc. When the vehicle is running, 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 suitable torque and speed. The converted power is then transmitted to the drive shaft. After the drive shaft transmits the power to the differential, the differential transmits the power to the wheels on both sides respectively. The converted power can also be transmitted to the differential. In order to achieve parking and shifting, the transmission is also provided with a shifting device and a parking device. In order to lubricate the transmission, differential and other devices, a lubrication system is also configured for the transmission, differential and other devices.

[0049] Example 1

[0050] See also Figures 1 to 3 , an embodiment of the present invention discloses a gearbox lubrication system, comprising:

[0051] The main gearbox 1 and the auxiliary gearbox 2, the main gearbox 1 is provided with a first gear pair 10, and the auxiliary gearbox 2 is provided with a second gear pair. During the operation of the gearbox, the first gear pair 10 will generate a rotational motion, and a part of the lubricating oil in the main gearbox 1 will adhere to the first gear pair 10 and then generate a rotational motion, and generate centrifugal motion around. The first gear pair 10 is used to deliver the lubricating oil in the main gearbox 1 to the auxiliary gearbox 2 through the second oil hole 31;

[0052] The first oil hole 30 and the second oil hole 31 are connected to the main gearbox 1 and the auxiliary gearbox 2. The lubricating oil splashed outward by the first gear pair 10 will flow into the auxiliary gearbox 2 along the second oil hole 31. In the vertical direction, the position of the first oil hole 30 is lower than the position of the second oil hole 31. After the lubricating oil flowing into the auxiliary gearbox 2 from the second oil hole 31 accumulates to the lowest point of the first oil hole 30, the excess lubricating oil in the auxiliary gearbox 2 will overflow from the first oil hole 30 into the main gearbox 1, thereby forming a dynamic circulation interconnected lubrication system, which can not only ensure that the main and auxiliary gearboxes 2 each maintain a designed amount of oil in a good lubrication state, but also form a dynamic circulation system between the main box and the auxiliary box, so that the oil temperature of the overall transmission system tends to a more stable level, which is convenient for monitoring and controlling the oil temperature. In addition, the present invention uses the normally operating gear pair in the gearbox to provide power for the gearbox lubrication system, saving costs.

[0053] To facilitate understanding of the gearbox lubrication system, the main gearbox 1 and the auxiliary gearbox 2 are further described as follows:

[0054] The main gearbox 1 plays the following roles in vehicle operation: changing the transmission ratio to meet the traction requirements of different driving conditions, making the engine work in a favorable situation as much as possible to meet the driving speed requirements; achieving reverse driving to meet the reverse driving of the car; interrupting power transmission to the drive wheels when the engine starts, idles, the car shifts gears or needs to stop; achieving neutral gear, when the clutch is engaged, the gearbox stops outputting power. The auxiliary gearbox 2 is used for heavy-duty vehicles with large changes in empty and full-load mass, complex operating conditions, especially diesel engine torque changes slowly, poor adaptability, and the need to expand the transmission ratio range and increase the number of gears to meet the power and economy requirements under various operating conditions.

[0055] See also Figures 1 to 3, the transmission lubrication system after normal operation is a dynamic circulation interconnected lubrication system. When the lubrication system is running, a certain amount of lubricating oil is added to the main gearbox 1. At this time, there is no lubricating oil in the auxiliary gearbox 2. As the first gear pair 10 rotates, the lubricating oil in the main gearbox 1 gradually flows into the auxiliary gearbox 2 through the second oil hole. The auxiliary gearbox 2 is a closed box. The lubricating oil will continue to accumulate after entering the auxiliary gearbox 2. When the lubricating oil in the auxiliary gearbox 2 accumulates to the lowest point of the first oil hole 30, the lubricating oil in the auxiliary gearbox 2 flows back to the main gearbox 1 through the first oil hole. At this time, the lubricating oil page in the auxiliary gearbox 2 is the first liquid level 20, and 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 auxiliary gearbox 2 will be fused with the original lubricating oil, and an equal amount of fused lubricating oil will overflow. At the same time, the liquid level of the lubricating oil after flowing into the main gearbox 1 is the second liquid level 11. The height of the second liquid level 11 is always lower than the height of the first liquid level 20, which conforms to the principle that liquid flows from top to bottom. In a lubrication system that has achieved dynamic circulation, the amount of lubricating oil reduced in the main gearbox 1 is consistent with the amount of lubricating oil increased in the auxiliary gearbox 2, and the amount of lubricating oil overflowing from the auxiliary gearbox 2 is consistent with the amount of lubricating oil returning to the main gearbox 1. Such a reciprocating cycle can ensure that the main and auxiliary gearboxes 2 each maintain the designed oil amount in a good lubrication state, and make the oil temperature of the overall transmission system tend to a more stable level, which is convenient for monitoring and control of the oil temperature.

[0056] The maximum flow rate of the first oil hole 30 of the gearbox lubrication system is greater than or equal to the maximum flow rate of the second oil hole 31. In the present embodiment, preferably, the first oil hole 30 and the second oil hole 31 are both round holes, and the number of the second oil holes 31 is two and the number of the first oil hole 30 is one. To ensure that the maximum flow rate of the first oil hole 30 is greater than or equal to the maximum flow rate of the second oil hole 31, the cross-sectional area of ​​the first oil hole 30 should be greater than or equal to the sum of the cross-sectional areas of the two second oil holes 31. Only in this way can it be ensured that the lubricating oil flowing into the auxiliary gearbox 2 can completely overflow the auxiliary gearbox 2. If the maximum flow rate of the first oil hole 30 is less than the maximum flow rate of the second oil hole 31, that is, the lubricating oil flowing into the auxiliary gearbox 2 is more than the lubricating oil flowing back into the main gearbox 1, the lubricating oil will accumulate in the auxiliary gearbox 2, and the effect of dynamic circulation lubrication cannot be achieved. The key to ensuring that the maximum flow rate of the first oil hole 30 is greater than or equal to the maximum flow rate of the second oil hole 31 is that the cross-sectional area of ​​the first oil hole 30 should be greater than or equal to the sum of the cross-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 round holes, and can be square holes or other irregular holes. In addition, the number of the first oil hole 30 and the second oil hole 31 should not be limited. In this embodiment, the use of two second oil holes 31 also has an advantage. The first gear pair 10 in the main gearbox 1 includes two gears, and each gear can correspond to a second oil hole. In this way, the internal space of the gearbox can be fully utilized to achieve alternating oil delivery with a maximized amount of oil, so that the oil temperature of the overall transmission system tends to a more stable level.

[0057] See also Figures 1 to 3 The main gearbox 1 includes a first box wall 3, the first box wall 3 is close to the auxiliary gearbox 2, the first oil hole 30 and the second oil hole 31 penetrate the first box wall 3, and an oil collecting mechanism 32 is provided on the first box wall 3. The lubricating oil splashed by the first gear pair 10 during the rotation makes centrifugal motion and is dispersed outward, and only a small amount passes through the second oil hole and enters the auxiliary gearbox 2. In order to make the gearbox lubrication system fully play its role, the oil collecting mechanism 32 is provided to gather the dispersed lubricating oil together, the amount of lubricating oil circulating in the lubrication system will increase, the lubrication effect will be better, and the oil temperature between the two boxes will be more stable.

[0058] Preferably, the oil collecting mechanism 32 includes a first oil guiding rib 321. The first oil guiding rib 321 is a plate-shaped structure, which is arranged on the first box wall 3. The end of the first oil guiding rib 321 in the vertical direction is arranged on one side of the second oil hole 31 and contacts the edge of the second oil hole 31. In this embodiment, the first oil guiding rib 321 is vertically arranged from top to bottom in the vertical direction, the upper part is the head end, and the lower part is the end end. The head end is seamlessly connected to the first box wall 3 and the top wall of the main gearbox 1. During the rotation of the first gear pair 10, the splashing lubricating oil will be blocked by the first oil guiding rib 321. After the splashing lubricating oil hits the first oil guiding rib 321, it will adhere to the first oil guiding rib 321. Under the action of gravity, it will flow from top to bottom along the plate surface of the first oil guiding rib 321. Due to the end of the first oil guiding rib 321, the splashing lubricating oil will be blocked by the first oil guiding rib 321. The end is arranged on one side of the second oil hole 31, and the attached lubricating oil will eventually flow to the end of the first oil guide rib 321 and flow into the second oil hole 31. In this way, within a certain period of time, the amount of lubricating oil in the second oil hole 31 depends on the amount of lubricating oil attached to the first oil guide rib 321. The larger the surface area of ​​the first oil guide rib 321, the more lubricating oil is attached thereto, the more lubricating oil circulates in the gearbox lubrication system within a certain period of time, the better the lubrication effect of the lubrication system, and the oil temperature between the two boxes will be more stable. In this embodiment, the structure of the first oil guide rib 321 is not limited to a plate shape, and can be a columnar or curved surface shape, etc. Generally speaking, the larger the surface area of ​​the first oil guide rib 321, the better the lubrication effect of the gearbox lubrication system.

[0059] In this embodiment, the specific structure of the oil collecting mechanism 32 includes but is not limited to the first oil guide rib 321, and can also be a groove-shaped structure, such as opening a groove on the first box wall 3, the four walls of the groove are inclined surfaces, and the groove mouth is connected to the second oil hole 31. The splashing lubricating oil will adhere to the four walls of the groove and gather together to flow into the second oil hole 31.

[0060] 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 connected to the second oil hole, and the second oil guiding rib 322 is arranged obliquely, extending upward along the intersection with the first oil guiding rib 321, so as to effectively collect the splashed lubricating oil into the oil collecting groove 323. Furthermore, in the vertical direction, 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, so as to prevent the lubricating oil in the oil collecting groove 323 from flowing out.

[0061] See also Figure 3The 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 rear meshing portion. Because the first gear 101 and the second gear 102 are both helical gears, the lubricating oil aroused by the two gears will not only perform centrifugal motion, but also diverge along the rotation direction of the gear rack. In this embodiment, the gear meshing portion close to the oil collecting mechanism 32 is the first meshing portion, and the gear meshing portion away from the oil collecting mechanism 32 is the rear meshing portion. The meshing portion, the rack of the first gear 101 is right-handed, and the rack of the second gear 102 is left-handed. The rotation direction of the first gear 101 and the second gear 102 is toward the meshing portion thereof. The oil collecting mechanism 32 of the main gearbox 1 is close to the middle 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 will throw the agitated lubricating oil to one side of the oil collecting mechanism 32, and the left-handed second gear 102 will throw the agitated lubricating oil to the other side of the oil collecting mechanism 32. In this way, the divergent lubricating oil can be fully gathered.

[0062] Example 2

[0063] Embodiment 2 of the present invention discloses a transmission which adopts the aforementioned transmission lubrication system, has low cost, good lubrication effect, and is convenient for monitoring and controlling oil temperature.

[0064] In addition, the present embodiment further provides a transmission four-speed shifting device, which is used for performing four-speed gear shifting operations and can also be applied to the transmission in Embodiment 1. For ease of description, the four gears are divided into two groups, namely, a first gear group and a second gear group, each of which includes two gears. The transmission four-speed shifting 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.

[0065] like Figure 5 and Figure 6 As shown, the shift drum 100 is provided with a guide groove 110 extending along its circumferential direction, and the guide groove 110 includes a shift area 111 that rotates to different angular positions with the shift drum 100;

[0066] like Figure 6 As shown, the shift drum 100 can be set to a cylindrical shape, and the aforementioned guide groove 110 can be set on the cylindrical circumferential wall of the shift drum 100. The shift area 111 is a part of the entire guide groove 110. The shift drum 100 can rotate around its own axis, and the shift area 111 also rotates to different positions as the shift drum 100 rotates.

[0067] like Figure 7As shown, the first synchronizer is used to participate in the gear shifting operation of the first group of gears. The first synchronizer can be connected to the input shaft or the output shaft in synchronous rotation; the first synchronizer is provided with a gear shifting component, which can move along the axial direction of the first synchronizer under the action of external force (for example, under the shifting of the shift fork), and when the gear shifting component of the first synchronizer moves to fully engage with the gear of a certain gear, the first synchronizer rotates synchronously with the gear, and the power of the input shaft can be transmitted to the gear through the first synchronizer, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the first synchronizer and the input shaft or the output shaft rotate synchronously.

[0068] The first driving mechanism 300 is slidably connected to the guide groove 110 at the first angular position 120 of the shift drum 100, and the first driving mechanism 300 is used to push the first synchronizer's gear engaging component to move along the axial direction of the first synchronizer to the first axial position to engage in gear, or to push the first synchronizer's gear engaging component to move along the axial direction of the first synchronizer to the second axial position to engage in gear, wherein the first axial position is different from the second axial position;

[0069] The first axial position refers to the position where the gear engaging component of the first synchronizer is fully engaged with the gear of one of the first gear positions and the gear rotates synchronously with it. The second axial position refers to the position where the gear engaging component of the first synchronizer is fully engaged with the gear of another gear position in the first gear position and the gear rotates synchronously with it. The aforementioned gear engaging component may be a synchronizing ring of the first synchronizer.

[0070] As the shift drum 100 rotates, the shift area 111 domain can rotate to an angular position range in which it is slidably connected to the first drive mechanism 300. Within this angular position range, as the shift drum 100 rotates, the position of the shift area 111 domain connected to the first drive also changes continuously. Since the distances between the various positions of the shift area 111 domain and the first synchronizer in the axial direction are different, the shift area 111 can drive the first drive mechanism 300 to move in the axial direction during the rotation process, and the first drive mechanism 300 moves in the axial direction while pushing the first synchronizer's gear engaging component to move in the axial direction.

[0071] In this embodiment, the first driving mechanism 300 includes a first sliding member 310 , a first shift fork 320 and a first connecting member 330 . The first connecting member 330 is connected to the first sliding member 310 and the first shift fork 320 , respectively. The first sliding member 310 slides along the guiding groove 110 .

[0072] The width of the guide groove is slightly larger than the width of the first sliding member 310, and the movement direction of the first connecting member 330 is constrained, and it can only move in the axial direction. Looking along the axial direction of the shift drum 100, in some areas, the distances of the guide groove 110 from the first synchronizer or the second synchronizer 4 at different circumferential positions are different. When the shift drum 100 rotates, different positions of the guide groove 110 contact the first sliding member 310, and the sliding member slides relative to the guide groove 110 in the circumferential direction while moving back and forth in the axial direction under the drive of the guide groove 110. Since the first connecting member 330 connects the first sliding member 310 and the first shift fork 320 together, the first shift fork 320 also moves synchronously with the first sliding member 310 in the axial direction. The first connecting member 330 can be arranged on the radial side of the shift drum 100 , the first sliding member 310 is arranged along the radial direction of the shift drum 100 , one end of the first sliding member 310 is connected to the first connecting member 330 , and the other end opposite is embedded in the guide groove 110 .

[0073] like Figure 4 and Figure 8 As shown, the second synchronizer 4 is used to participate in the gear operation of the second group of gears, and the second synchronizer 4 can be connected to the input shaft or the output shaft for synchronous rotation; the second synchronizer 4 is provided with a gear engaging component, and the gear engaging component can move along the axial direction of the second synchronizer 4 under the action of an external force (for example, under the shifting of a shift fork), and when the gear engaging component of the second synchronizer 4 moves to fully engage with a gear of a certain gear, the second synchronizer 4 rotates synchronously with the gear, and at this time, the power of the input shaft can be transmitted to the gear through the second synchronizer 4, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the second synchronizer 4 and the input shaft or the output shaft rotate synchronously.

[0074] The second driving mechanism 5 is slidably connected to the guide groove 110 at the second angular position 130 of the shift drum 100, and the second driving mechanism 5 is used to push the gear engaging component of the second synchronizer 4 to move to the third axial position to engage in gear along the axial direction of the second synchronizer 4 under the drive of the shift zone 111, or to push the gear engaging component of the second synchronizer 4 to move to the fourth axial position to engage in gear along the axial direction of the second synchronizer 4, wherein the third axial position is different from the fourth axial position, and the second angular position 130 is different from the first angular position 120;

[0075] The third axial position refers to the position where the gear engaging component of the second synchronizer 4 is fully engaged with the gear of one of the second gear positions and the gear rotates synchronously with it. The fourth axial position refers to the position where the gear engaging component of the second synchronizer 4 is fully engaged with the gear of another gear position in the second gear position and the gear rotates synchronously with it. The aforementioned gear engaging component may be a synchronizer ring of the second synchronizer 4.

[0076] As the shift drum 100 rotates, the shift area 111 domain can rotate to an angular position range in which it is slidably connected to the second drive mechanism 5. Within this angular position range, as the shift drum 100 rotates, the position of the shift area 111 domain connected to the second drive also changes continuously. Since the distances between the various positions of the shift area 111 domain and the second synchronizer 4 in the axial direction are different, the shift area 111 can drive the second drive mechanism 5 to move in the axial direction during the rotation process, and the second drive mechanism 5 moves in the axial direction while pushing the gear engaging component of the second synchronizer 4 to move in the axial direction.

[0077] In this embodiment, the second driving mechanism 5 includes a second sliding member 51 , a second shift fork 52 and a second connecting member 53 . The second connecting member 53 is connected to the second sliding member 51 and the second shift fork 52 , respectively. The second sliding member 51 slides along the guiding groove 110 .

[0078] The width of the guide groove is slightly larger than the width of the second sliding member 51, and the movement direction of the second connecting member 53 is constrained, and it can only move in the axial direction. Looking along the axial direction of the shift drum 100, the distances of the guide groove 110 from the first synchronizer or the second synchronizer 4 at different circumferential positions in some areas are different. When the shift drum 100 rotates, different positions of the guide groove 110 contact the second sliding member 51, and the sliding member slides relative to the guide groove 110 in the circumferential direction, and also moves back and forth in the axial direction under the drive of the guide groove 110. Since the second connecting member 53 connects the second sliding member 51 and the second shift fork 52 together, the second shift fork 52 also moves synchronously with the second sliding member 51 in the axial direction. The second connecting member 53 can be arranged on the radial side of the shift drum 100, and the second sliding member 51 is arranged along the radial direction of the shift drum 100. One end of the second sliding member 51 is connected to the second connecting member 53, and the other end opposite to the second sliding member 51 is embedded in the guide groove 110.

[0079] like Figure 4 As shown, the motor 6 is used to drive the shift drum 100 to rotate so that the shift area 111 drives the first drive mechanism 300 and the second drive mechanism 5 to move back and forth along the axial direction of the shift drum 100. The motor 6 and the first synchronizer and the second synchronizer 4 are located on both sides of the axial direction of the shift drum 100, and the motor 6 is coaxially arranged with the shift drum 100.

[0080] In this embodiment, the motor 6 and the two driving mechanisms are separated in the axial direction so that they are located on both sides of the shift drum 100. In this way, the actions of the motor 6 and the driving mechanisms do not affect each other, and the coaxial arrangement of the motor 6 and the shift drum 100 can make the structure more compact and also utilize the power transmission between the motor 6 and the shift drum 100.

[0081] As a preferred implementation, in this embodiment, the transmission four-speed shifting device further includes a rotating shaft 7, the shift drum 100 is interference fit with the rotating shaft 7, and the motor 6 drives the rotating shaft 7 to rotate to drive the shift drum 100 to rotate. The transmission is directly carried out by using the interference fit between the rotating shaft and the shift drum 100, and the transmission process is simpler and more reliable. The motor 6 is installed on the assembly housing, the shift drum 100 is positioned on the housing through the rotating shaft 7, the shift drum 100 and the shift drum 100 shaft rotating shaft 7 are relatively fixed, and the rotating shaft 7 can rotate on the housing.

[0082] like Fig. 9 As shown, in the present embodiment, an annular limiting groove 210 is provided on the peripheral wall of the first synchronizer and / or the second synchronizer 4, and a shifting member 325 is provided at the end of the first shift fork 320 and / or the second shift fork 52, and the shifting member 325 shifts the gear engaging component of the first synchronizer and / or the second synchronizer 4 by shifting the side wall of the limiting groove 210.

[0083] In this embodiment, the width of the limit 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 limit 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 limit groove 210. With the above structure, after the toggle member 325 is inserted into the limit groove 210 and the gear engaging component of the synchronizer is toggled to the gear engaging position, one side of the toggle member 325 contacts one side wall of the limit groove 210, and a sufficient gap is left between the other side of the toggle member 325 and the other side wall of the limit groove 210. In this way, when an unexpected small vibration causes a relative displacement between the toggle member 325 and the limit slot 210, the other side of the toggle member 325 will not contact the other side wall of the limit slot 210, thus preventing the toggle member 325 from toggling the limit slot 210 due to unexpected vibration, causing the gear engaging component to disengage from the current gear position, thereby making gear engaging more reliable. When normally engaging a gear, the distance that the toggle member 325 moves in the axial direction must exceed the axial clearance between the toggle member 325 and the limit slot 210, so during the toggle movement, the other side of the toggle member 325 can also push the gear engaging component to move by contacting the other side wall of the limit slot 210.

[0084] When the toggle member 325 toggles the synchronizer to shift gears, the toggle member 325 contacts the synchronizer, and the synchronizer is in high-speed rotation, and relative motion occurs between the toggle member 325 and the synchronizer. Therefore, there is continuous sliding friction between the toggle member 325 and the synchronizer. Both the toggle member 325 and the synchronizer are prone to wear and deformation, and the heat generated by friction will also affect the gearbox. For this purpose, replaceable wear-resistant parts can be set on the toggle member 325 to allow the wear-resistant parts to contact the synchronizer. When the wear-resistant parts are worn to a certain extent, new wear-resistant parts can be replaced. When this method is used, the gearbox needs to be disassembled and assembled to replace the wear-resistant parts, so it is very inconvenient in actual use.

[0085] To this end, an oil guide groove can be set on the first shift fork 320, and the outlet of the oil guide groove can be set on the surface where the shifting member 325 contacts the synchronizer. The lubricating oil flows along the oil guide groove to the surface of the shifting member 325, forming an oil film between the shifting member 325 and the synchronizer to reduce the friction between the two.

[0086] In addition, rollers or needle rollers may be provided on the shifting member 325 to reduce friction. However, since the rollers are in point contact with the synchronizer and the needle rollers are in line contact with the synchronizer, the contact areas of these two contact modes are very small, which may easily cause excessive concentration of force on the synchronizer and the shift fork.

[0087] In this regard, this embodiment adopts a structure that allows the toggle member 325 to rotate synchronously with the synchronizer to avoid friction. Fig.12As shown, the first shift fork 320 of the present embodiment further includes a cylindrical first rotating member 321, a second rotating member 322, a third rotating member 323 and a fourth rotating member 324, the first rotating member 321, the second rotating member 322, the third rotating member 323 and the fourth rotating member 324 are rotatably connected to the first shift fork 320, and the extension lines of the rotation axes of the first rotating member 321, the second rotating member 322, the third rotating member 323 and the fourth rotating member 324 intersect at the same intersection, and the same intersection is located on the rotation axis of the first synchronizer, the rotation axis of the first rotating member 321 and the rotation axis of the second rotating member 322 are located in a first plane, the rotation axis of the third rotating member 323 and the rotation axis of the fourth rotating member 324 are located in a second plane different from the first plane, and the first plane and the second plane are arranged along the axial direction of the first synchronizer. The toggle member 325 is a rotating belt 326, one end of which is passed around the outer walls of the first rotating member 321, the second rotating member 322, the third rotating member 323 and the fourth rotating member 324 in sequence and then connected to the other end opposite thereto. The rotating belt 326 may be a steel belt or a belt. In the specific implementation, the rotating belt 326 is tightened and then wound around the outer walls of the aforementioned four rotating members, and the rotating belt 326 is connected end to end to form a ring. The rotating belt 326 is in an arc shape after being unfolded. When the distance between the first rotating member 321 and the second rotating member 322 is too long, a fifth rotating member may be arranged between the first rotating member 321 and the second rotating member 322, and the fifth rotating member may be used to provide support for the rotating belt 326 in the middle; when the distance between the third rotating member 323 and the fourth rotating member 324 is too long, a fifth rotating member may be arranged between the first rotating member 321 and the second rotating member 322, and the sixth rotating member may be used to provide support for the rotating belt 326 in the middle. The fifth rotating member and the sixth rotating member may be provided in plurality, and the number of the fifth rotating member and the sixth rotating member 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 rotating members may be rotatably connected to the first shift fork 320 via a rotating shaft with a smooth surface.

[0088] After adopting the above structure, when the rotating belt 326 moves with the first shift fork 320 to the position in contact with the synchronizer, the rotating belt 326 rotates under the drive of the synchronizer. The rotating direction of the rotating belt 326 is as follows: Figures 8 to 10As shown in the direction of the arrow in . When the rotating belt 326 just contacts with the synchronizer at the beginning, there will be sliding friction between the rotating belt 326 and the synchronizer. When the rotating belt 326 and the synchronizer have the same rotation speed, there will be no relative sliding between the rotating belt 326 and the synchronizer, and no sliding friction will be generated to cause the rotating belt 326 and the synchronizer to wear. At this time, the rotating belt 326 rotates around the four rotating parts in sequence under the drive of the synchronizer, and the rotating belt 326 contacts the synchronizer in a surface contact manner, which is not easy to cause excessive concentration of force, and the rotating belt 326 can always rotate synchronously with the synchronizer.

[0089] This embodiment also provides another implementation method for solving the aforementioned sliding friction problem. The first shift fork 320 also includes multiple groups of rotating components, each group of rotating components includes a seventh rotating member, an eighth rotating member and a rotating belt 326, the seventh rotating member and the eighth rotating member are rotatably connected to the first shift fork 320, and one end of the rotating belt 326 successively passes around the outer walls of the seventh rotating member and the eighth rotating member and then connects to the other opposite end. The seventh rotating member and the eighth rotating member shafts 7 are parallel to each other. The eighth rotating member and the ninth rotating member are axially symmetrically arranged, and their symmetry axes serve as the symmetry axes of the rotating components. The extension lines of the symmetry axes of each group of rotating components are compared to the same intersection, and the intersection is located on the rotation axis of the first synchronizer.

[0090] Each group of rotating components forms a small rotating unit, and the rotating belt 326 of each group of rotating components can rotate cyclically around four rotating parts. Since the extension line of the axis of symmetry of the rotating components is located on the rotation axis of the first synchronizer, when the rotating belt 326 moves with the first shift fork 320 to the position in contact with the synchronizer, the rotation direction of the rotating belt 326 of each rotating component is almost the same as the rotation direction of the corresponding position on the synchronizer, and the sliding friction between the rotating belt 326 of each rotating component and the synchronizer is very small. The above-mentioned method has a simple structure, and each rotating component can be arranged in parallel, which is convenient for installation, and both surface contact and reduced sliding friction are achieved.

[0091] The four-speed gear shifting device of the transmission of this embodiment can utilize the motor 6 to drive the shift drum 100 to rotate. When the shift area 111 of the shift drum 100 rotates to a position connected to the first drive mechanism 300, the shift area 111 can rotate with the shift drum 100 and push the first synchronizer through the first drive mechanism 300 to perform gear shifting operations of two of the gears; when the shift area 111 of the shift drum 100 rotates to a position connected to the second drive mechanism 5, the shift area 111 can rotate with the shift drum 100 and push the second synchronizer 4 through the second drive mechanism 5 to perform gear shifting operations of the other two gears; since the areas where the first drive mechanism 300 and the second drive mechanism 5 are connected to the shift drum 100 are at different angular positions, only one shift drum 100 and two drive mechanisms are needed to respectively perform gear shifting of two gears. The gear shifting operations of the aforementioned four gears can be completed by only one motor 6 driving one shift drum 100 to rotate. Therefore, there are fewer actuators for shifting, the gear shifting action is simple, and the operation is more reliable.

[0092] Example 3

[0093] like Fig.13 As shown, this embodiment further provides a transmission flange, which mainly includes a flange body 410, a first transmission structure 420, a first connection structure 430 and a second transmission structure 440:

[0094] The first transmission structure 420 is disposed on the flange body 410, and the first transmission structure 420 is used to connect with the transmission output shaft and transmit the torque of the transmission output shaft to the flange body 410;

[0095] like Fig.14 and Fig.16 As shown, 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 drives the flange body 410 to rotate together through the first transmission structure 420, so that the rotation and torque of the output shaft are transmitted to the flange body 410.

[0096] The first connection structure 430 is disposed on the flange body 410, and the first connection structure 430 is used to connect the flange body 410 with the transmission shaft;

[0097] In this embodiment, the first connection structure 430 only plays a connecting role. The first connection structure 430 prevents the transmission shaft and the flange body 410 from being loosened by connecting the flange body 410 to the transmission shaft.

[0098] The second transmission structure 440 is disposed at one end of the flange body 410 facing the transmission shaft, and the second transmission structure 440 is used to transmit the torque of the flange body 410 to the transmission shaft and prevent the torque from being transmitted to the first connection structure 430 .

[0099] When the flange body 410 rotates under the drive of the gearbox output shaft, the torque of the flange body 410 is transmitted to the transmission shaft through the second transmission structure 440. In the process of the flange body 410 driving the transmission shaft to rotate, the second transmission structure 440 is responsible for bearing the torque of the transmission. In addition, the second transmission structure 440 is also used to prevent the torque from being transmitted to the first connection structure 430, so that in the process of the flange transmitting the torque to the transmission shaft, the first connection structure 430 will not be affected by the torque, so it is not easy to be damaged, and the first connection structure 430 can always be guaranteed to connect the flange body 410 and the transmission shaft, thereby improving the safety of the flange connection, and the number of the first connection structure 430 can be appropriately reduced to simplify the structure and reduce costs.

[0100] As a preferred implementation, in this embodiment, the second transmission structure 440 is a rectangular tooth, which is arranged on the end face where the flange body 410 is connected to the transmission shaft, and the rectangular teeth on the flange body 410 are used to cooperate with the rectangular teeth on the transmission shaft to transmit torque.

[0101] The rectangular teeth are in the shape of long strips, and the cross section of the rectangular teeth is rectangular. In this embodiment, rectangular teeth that match the rectangular teeth on the flange body 410 can be provided on the transmission shaft. After the flange body 410 is installed and connected with the transmission shaft, the end face of the flange body 410 matches the transmission shaft, and the rectangular teeth on the flange 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 transmission shaft, and the rectangular teeth on the flange body 410 push the rectangular teeth on the adjacent transmission shaft, so that the transmission shaft rotates with the flange body 410. The rectangular teeth can be directly processed on 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 torque, the rectangular teeth are formed by two adjacent tooth grooves, and the tooth grooves are formed by the end face of the flange body 410 being recessed in the direction away from the transmission shaft. The use of the above structure to form the rectangular teeth can make the top of the rectangular teeth flush with the end surface of the flange body 410, so it does not take up extra space, and only needs to directly remove material from the original flange body 410 to form the tooth groove. The rectangular teeth formed in this way are an integrated structure with the flange body 410, which has little impact on the original flange body 410. The overall structure is simple and has a strong bearing capacity.

[0102] In this embodiment, the first connecting structure 430 is connected to the transmission shaft through a first connecting member; in the rotation direction of the flange, the fitting clearance between the first connecting member and the first connecting structure 430 is greater than the fitting clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the transmission shaft.

[0103] Since the matching clearance between the first connecting member and the first connecting structure 430 is larger than the matching clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the transmission shaft in the rotation direction of the flange, when the flange is driven, before the first connecting member contacts and receives force from the first connecting structure 430, the rectangular teeth on the flange body 410 first contact with the rectangular teeth on the transmission shaft. Due to the obstruction of the rectangular teeth on the transmission shaft, the first connecting member and the first connecting structure 430 always have a matching clearance, which can effectively avoid the torque effect between the first connecting structure 430 and the first connecting member during transmission. The aforementioned first connecting member can be a bolt, and the first connecting structure 430 can be a bolt hole. When the flange body 410 is connected to the transmission shaft, the bolt passes through the bolt hole.

[0104] In this embodiment, a plurality of transmission structure groups are arranged on the flange body 410, each transmission structure group includes a plurality of first transmission structures 420 arranged in parallel with each other, the number of the first connection structures 430 is the same as the number of the transmission structure groups, and the first connection structures 430 correspond one-to-one to the transmission structure groups, and the transmission structure groups are used to prevent torque from being transmitted to the first connection structures 430 corresponding thereto.

[0105] like Fig.17 As shown, in this embodiment, a plurality of first connection structures 430 can be arranged along the circumferential direction of the flange body 410 to improve the reliability of the connection. In addition, in this embodiment, a one-to-one corresponding arrangement of the transmission structure group and the first connection structure 430 is adopted. Each first connection structure 430 is protected by a corresponding transmission structure group, and it is ensured that in the corresponding first connection structure 430 and the transmission structure group, the transmission structure group is preferably better than the first connection structure 430 in bearing torque, thereby avoiding the problem that when multiple first connection structures 430 are arranged, it is impossible to ensure that all first connection structures 430 will not be subjected to torque. Each group of transmission structure groups can be provided with a plurality of first transmission structures 420 arranged in parallel with each other. During transmission, each first transmission structure 420 in the same group can bear torque together. In this way, the torque acting on the flange is dispersed to each transmission structure group and then further dispersed to each first transmission structure 420, so that the torque borne by each first transmission mechanism becomes smaller, while the torque that can be borne by the whole becomes larger.

[0106] In addition, in the rotation direction, the first connection structure 430 is located at the center of the transmission structure group to which it corresponds. The above-mentioned method can make each first transmission structure 420 in the transmission structure group be subjected to torque before the first connection structure 430 contacts the first connection member, regardless of whether the flange body 410 rotates forward or reversely, thereby ensuring that the torque is not transmitted to the first connection structure 430.

[0107] For example, six transmission structure groups can be arranged on the flange body 410, and each transmission structure group is provided with four rectangular teeth. The four 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 the symmetry axis. The first transmission structure 420 corresponding to the group of rectangular teeth is arranged on the symmetry axis of the group. The six transmission structure groups are evenly distributed along the circumferential direction of the flange body 410, that is, the angle of interval between any two adjacent transmission structure groups in the six transmission structure groups is the same, and the interval between the two adjacent groups is 60 degrees. It can be understood that the number of the aforementioned transmission groups and the number of the first connecting structures 430 in each transmission structure group can also adopt other numbers, which are not limited here.

[0108] In this embodiment, a plurality of parallel rectangular teeth can be used in a transmission structure group, and the length of each rectangular tooth is the same as the radial dimension of the end face of the flange body 410. The above method can further increase the torque bearing capacity of each transmission structure group without increasing the number of rectangular teeth in each group.

[0109] like Fig.16 As shown, in this embodiment, the flange body 410 includes a cylindrical first connecting portion 411 and a disc-shaped second connecting portion 412, the first connecting portion 411 and the second connecting portion 412 are arranged along the axial direction of the flange body 410, the first connecting portion 411 is provided with a through hole penetrating the connecting portion, the first transmission structure 420 is a spline, and the spline is arranged on the through hole of the first connecting portion 411, and the first connecting structure 430 is arranged on the second connecting portion 412.

[0110] When the first connection structure 430 adopts rectangular teeth, the rectangular teeth are arranged on the disc surface of the second connection portion 412 facing the transmission shaft.

[0111] In this embodiment, the first connection portion 411 is used to realize the connection between the flange body 410 and the transmission output shaft, and the second connection portion 412 is used to realize the connection between the flange body 410 and the transmission shaft. In this embodiment, the first connection portion 411 and the second connection portion 412 are arranged along the axial direction of the flange body 410, so that the transmission output shaft and the transmission shaft are compactly distributed on both sides of the axial direction of the flange, so that the mutual influence between the power input side and the power output side can be avoided.

[0112] In this embodiment, a spline is used for transmission at the power input side, and the transmission has a strong load-bearing capacity. A through hole can be processed in the first connecting portion 411 first, and then a spline can be processed on the inner wall of the through hole.

[0113] In this embodiment, the second transmission structure 440 extends from the inner wall of the through hole to the outer wall of the second connecting portion 412 along the radial direction of the second connecting portion 412. This method can fully utilize the radial size of the disk of the second connecting portion 412 to maximize the length of the rectangular teeth that can withstand torque.

[0114] When the rectangular tooth is longer, the deformation of the rectangular tooth under the action of torque will increase. When the deformation exceeds a certain level, the same rectangular tooth will not be in sufficient contact with its matching rectangular tooth, which will reduce the load-bearing capacity of the rectangular tooth. In this regard, in the present embodiment, each rectangular tooth is composed of a plurality of sub-rectangular teeth of smaller lengths, and two adjacent sub-rectangular teeth are disconnected. After adopting the above-mentioned method, the deformation of each sub-rectangular tooth will not be 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 will not exceed the level that can cause insufficient contact of the rectangular teeth. The gap between adjacent sub-rectangular teeth can be very small, so the above-mentioned structure will not significantly reduce the length of the part of the rectangular tooth that can withstand torque.

[0115] like Fig.19 As shown, in this embodiment, each transmission structure group is composed of two sub-transmission structure groups, namely the first sub-transmission structure group 441 and the second sub-transmission structure group 442. The number, cross-sectional shape, and arrangement interval of the rectangular teeth in the two sub-transmission structure groups are equal, but the two sub-transmission structure groups are staggered in the circumferential direction, and each rectangular tooth is also divided into two disconnected parts, and belongs to the two sub-transmission structure groups. The above-mentioned method can reduce the deformation of the rectangular teeth without reducing the total length of the rectangular teeth used to bear the torque. After the two sub-transmission structure groups are staggered in the circumferential direction, the force on the flange body 410 will not be concentrated on the same circumferential position of the flange body 410, and the deformation of the flange body 410 will also be dispersed to various positions of the flange body 410 in the circumferential direction.

[0116] One end of each rectangular tooth in the first sub-transmission structure group 441 extends to the outer wall of the flange body 410, so that the milling cutter can remove material from the outer side of the flange body 410 to the inner side at one time to complete the processing of the rectangular teeth, which can significantly improve the processing efficiency.

[0117] The first sub-transmission structure group 441 and the second sub-transmission structure group 442 may be completely staggered or partially staggered in the circumferential direction. When the completely staggered method is adopted, the first sub-transmission structure group 441 and the second sub-transmission structure group 442 partially overlap in the radial direction. The portion where the first sub-transmission structure group 441 and the second sub-transmission structure group 442 are disconnected on the flange body 410 cannot withstand torque, and the force on the portion of the first sub-transmission structure group 441 and the second sub-transmission structure group 442 near the disconnected position will also change abruptly, which will affect the service life of the flange. After the first sub-transmission structure group 441 and the second sub-transmission structure group 442 partially overlap in the radial direction, the portion of the original flange body 410 that cannot withstand torque due to the disconnection of the radial teeth in the radial direction is eliminated, and the force on the portion of the first sub-transmission structure group 441 and the second sub-transmission structure group 442 near the disconnected position is avoided.

[0118] When the incomplete staggered method is adopted, the tooth grooves 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. The above method can make the portion of the flange body 410 used for bearing torque in the circumferential direction of the same transmission structure group the largest, so that the flange body 410 can withstand more torque.

[0119] like Fig.18 As shown, in this 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 body 410 to the inside. The rectangular teeth of each transmission structure group are disconnected from each other, and the length of the rectangular teeth of the third sub-transmission structure group 443 is less than that of the fourth sub-transmission structure group 444, and the length of the rectangular teeth of the fourth sub-transmission structure group 444 is less than that of the fifth sub-transmission structure group 445. Under the condition of bearing the same torque, the outer side of the flange body 410 is deformed more than the inner side thereof. This embodiment adopts the aforementioned structure in which the length of the rectangular teeth becomes shorter from the inside to the outside, so that the variance of the deformation of the rectangular teeth at each radial position of the flange body 410 can be reduced, so as to avoid excessive deformation of the rectangular teeth at a local position in the radial direction of the flange body 410, which affects the service life of the flange.

[0120] like Fig.15 As shown, in this embodiment, a limiting hole 4121 cooperating with the transmission shaft is provided on the second connection part 412, and a stop 4122 for limiting the axial position of the transmission shaft is provided at one end of the limiting hole 4121 facing the first connection part 411, and the spline extends to the position of the stop 4122.

[0121] During installation, the end of the transmission shaft can be inserted into the limiting hole 4121 of the second connecting portion 412 until the end of the transmission shaft abuts against the stop 4122. The output shaft of the gearbox can be inserted into the through hole. Since the spline in the through hole extends to the stop 4122, the distance between the position where the input end transmits torque and the end of the transmission shaft is shorter. The above method can shorten the distance between the position where the input end transmits torque and the position where the output end transmits torque, thereby reducing the deformation of the transmission component between the input end and the output end under the action of torque.

[0122] Example 4

[0123] Embodiment 4 of the present invention discloses a vehicle, including all the aforementioned systems or structures, with low cost, convenient monitoring and control of oil temperature, and good system stability. The vehicle also includes the aforementioned transmission flange.

[0124] The vehicle in the fourth embodiment of the invention may be a traditional fuel vehicle such as a gasoline vehicle, a diesel vehicle, etc., or a new energy vehicle, wherein the new energy vehicle includes but is not limited to a pure electric vehicle (BEV / EV), a hybrid vehicle (HEV, PHEV and REEV), a fuel cell vehicle (FCEV), and a solar cell vehicle.

[0125] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein by equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A gearbox lubrication system, characterized in that: include: A main gearbox and an auxiliary gearbox, wherein the main gearbox is provided with a first gear pair; a first oil hole and a second oil hole, wherein the first oil hole and the second oil hole are both connected to the main gearbox and the auxiliary gearbox; Wherein, along the vertical direction, the position of the first oil hole is lower than the position of the second oil hole, the first gear pair is used to deliver the lubricating oil in the main gearbox to the auxiliary gearbox through the second oil hole, and the excess lubricating oil in the auxiliary gearbox will flow back to the main gearbox through the first oil hole; The first gear pair includes a first gear and a second gear, the first gear and the second gear are helical gears, the first gear and the second gear are close to the second oil hole at the front meshing portion, and far away from the second oil hole at the rear meshing portion, the first gear rack is right-handed, the second gear rack is left-handed, and the first gear and the second gear rotate toward the meshing portion thereof; The main gearbox comprises a first box wall, the first oil hole and the second oil hole penetrate the first box wall, and an oil collecting mechanism is arranged on the first box wall; The oil collecting mechanism comprises a first oil guiding rib, wherein the end of the first oil guiding rib in the vertical direction is arranged at one side of the second oil hole; The oil collecting mechanism further includes a second oil guide rib, an oil collecting groove is formed between the second oil guide rib and the first oil guide rib, and the oil collecting groove is connected to the second oil hole; An end of the oil collecting groove away from the second oil hole is higher than an end of the oil collecting groove close to the second oil hole; The first gear and the second gear have an earlier meshing portion that is closer to the oil collecting mechanism than a later meshing portion.

2. The gearbox lubrication system according to claim 1, characterized in that: When the lubricating oil in the auxiliary gearbox accumulates to the first liquid level, the lubricating oil in the auxiliary gearbox flows into the main gearbox through the first oil hole, and the lubricating oil liquid level in the main gearbox is the second liquid level. The first liquid level height is consistent with the lowest point height of the first oil hole, and the second liquid level height is lower than the first liquid level height.

3. The gearbox lubrication system according to claim 1, characterized in that: The maximum flow rate of the first oil hole is greater than or equal to the maximum flow rate of the second oil hole.

4. A transmission, characterized in that: Comprising a gearbox lubrication system as described in any one of claims 1-3.

5. A vehicle, characterized in that: It comprises the gearbox lubrication system according to any one of claims 1 to 3 or the transmission according to claim 4.

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