Main and auxiliary gearbox transmission and vehicle

Abstract

The present invention belongs to the technical field of automobile transmission, and provides a main and auxiliary transmission and a vehicle. The main and auxiliary transmission of the present invention comprises: a main transmission, comprising an input shaft assembly, an output shaft assembly and a shift mechanism, wherein the input shaft assembly is used to transmit the power of the vehicle power unit to the output shaft assembly, and the shift mechanism is used to switch the gear of the main transmission; an auxiliary transmission, which is connected to the output shaft assembly through a clutch device, and the clutch device is used to connect or disconnect the power transmission between the auxiliary transmission and the output shaft assembly; when the output shaft assembly and the auxiliary transmission are in a disconnected state, the power output by the output shaft assembly is output to the drive shaft, and when the output shaft assembly and the auxiliary transmission are in a connected state, the power output by the output shaft assembly is output to the drive shaft after being decelerated by the auxiliary transmission. The vehicle of the present invention comprises the above-mentioned main and auxiliary transmission. The present invention can be applied to vehicle models with different torque requirements.

Description

Technical Field

[0001] The invention belongs to the technical field of automobile transmission, in particular to a main and auxiliary box transmission and a vehicle. Background Art

[0002] With the increasing prevalence of automobiles in our daily lives, they have become an indispensable tool for travel and work. The automotive transmission is a crucial component for power transmission. The power generated by the vehicle's power unit is reduced in speed by the transmission and then transmitted to the drive shaft. However, different vehicles require different output torques. For example, family cars and small sedans require lower torque and higher speeds, while heavy-duty trucks, commercial vehicles, and buses require higher torque and lower speeds. Currently, reducers utilize a gearbox. While the shift mechanism can be used to achieve different torque outputs, the torque output range is limited and cannot be adapted to different vehicle types. Summary of the Invention

[0003] In view of this, the present invention provides a main and auxiliary box transmission and a vehicle to solve the technical problem that the existing transmission cannot match vehicle models with different torque requirements.

[0004] The technical solution adopted in the present invention is:

[0005] In a first aspect, the present invention provides a main and auxiliary box transmission, comprising:

[0006] The main gearbox transmission includes an input shaft assembly, an output shaft assembly, and a shift mechanism. The input shaft assembly is used to transmit power from the vehicle power unit to the output shaft assembly, and the shift mechanism is used to switch the gear position of the main gearbox.

[0007] Auxiliary gearbox, connected to the output shaft assembly via a clutch device, the clutch device is used to connect or disconnect the power transmission between the auxiliary gearbox and the output shaft assembly;

[0008] When the output shaft assembly and the auxiliary transmission are in a disconnected state, the power output by the output shaft assembly is output to the transmission shaft. When the output shaft assembly and the auxiliary transmission are in a connected state, the power output by the output shaft assembly is decelerated by the auxiliary transmission and output to the transmission shaft.

[0009] Preferably, the auxiliary transmission includes an auxiliary transmission input shaft, an auxiliary transmission input gear, an auxiliary transmission output shaft and an auxiliary transmission output gear, the auxiliary transmission input shaft drives the auxiliary transmission input gear to rotate, the auxiliary transmission input gear is engaged with the auxiliary transmission output gear, and the auxiliary transmission output gear drives the auxiliary transmission output shaft to rotate.

[0010] Preferably, the auxiliary box input gear and the auxiliary box input shaft are an integrated structure, and the auxiliary box output gear and the auxiliary box output shaft are an integrated structure.

[0011] Preferably, the auxiliary box input gear is fixedly connected to the auxiliary box input shaft, and the auxiliary box output gear is fixedly connected to the auxiliary box output shaft.

[0012] Preferably, a keyway is provided on the auxiliary box input shaft, and the auxiliary box input shaft is connected to the clutch device through the keyway.

[0013] Preferably, ball bearings are provided at both ends of the auxiliary gearbox input shaft, and the auxiliary gearbox input shaft is rotatably connected to the housing of the auxiliary gearbox via the ball bearings.

[0014] Preferably, tapered bearings are provided at both ends of the auxiliary gearbox output shaft, and the tapered surfaces of the tapered bearings at both ends are in opposite directions. The auxiliary gearbox output shaft is rotatably connected to the housing of the auxiliary gearbox via the tapered bearings.

[0015] Preferably, the input shaft assembly is provided with an input shaft, a first gear input gear, a second gear input gear, a third gear input gear, and a fourth gear input gear, wherein the first gear input gear, the third gear input gear, the fourth gear input gear, and the second gear input gear are sequentially arranged along the axial direction of the input shaft, and the output shaft assembly is provided with an output shaft, a first gear output gear meshing with the first gear input gear, a second gear output gear meshing with the second gear input gear, a third gear output gear meshing with the third gear input gear, and a fourth gear output gear meshing with the fourth gear input gear;

[0016] Preferably, the shifting mechanism includes a first synchronizer and a second synchronizer, the first synchronizer is arranged on the input shaft, and the second synchronizer is arranged on the output shaft, the first synchronizer is used to make the input shaft of the transmission rotate synchronously with the second gear input gear or the fourth gear input gear, and the second synchronizer is used to make the output shaft of the transmission rotate synchronously with the first gear output gear or the third gear output gear.

[0017] In a second aspect, the present invention provides a vehicle comprising the main and auxiliary box transmission described in the first aspect.

[0018] Beneficial Effects: The main and auxiliary transmissions and vehicles of the present invention can provide two different torque output modes, which can be selected by the clutch state of the clutch device. One mode is that the power of the vehicle's power unit is transmitted to the main transmission, which is then decelerated by the main transmission and directly transmitted to the vehicle's drive shaft. The other mode is that the power of the vehicle's power unit is first transmitted to the main transmission, which is then decelerated by the main transmission and transmitted to the auxiliary transmission through the clutch device. The auxiliary transmission is further decelerated and torque-increased by the transmission and then output to the vehicle's drive shaft. Since two different torque outputs can be achieved, the present invention is applicable to vehicles with different torque requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work, and these are all within the scope of protection of the present invention.

[0020] Figure 1 A three-dimensional structural diagram of the four-speed shifting device of the transmission of the present invention;

[0021] Figure 2 A diagram showing the relationship between the shifting area of ​​the shift drum and the angular positions of the first drive mechanism and the second drive mechanism of the present invention;

[0022] Figure 3 A three-dimensional structural diagram of the shift drum of the present invention;

[0023] Figure 4 is a diagram showing the relationship between the axial position of the guide groove and the axial position of the present invention;

[0024] Figure 5 A three-dimensional structural diagram of the cooperation between the first drive mechanism and the shift drum of the present invention;

[0025] Figure 6 A three-dimensional structural diagram of the cooperation between the first drive mechanism and the shift drum of the present invention;

[0026] Figure 7 A three-dimensional structural diagram of the cooperation between the first drive mechanism and the first synchronizer of the present invention;

[0027] Figure 8 A top view of the structure of the present invention that enables the rotating belt to rotate with the synchronizer;

[0028] Figure 9 A side view of a structure of the present invention that enables a rotating belt to rotate with a synchronizer;

[0029] Figure 10 A diagram showing the positional relationship of the four rotating parts of the present invention;

[0030] Figure 11 It is a schematic diagram of the transmission principle of the main and auxiliary box transmission of the present invention;

[0031] Figure 12 Schematic diagram of the transmission principle of the main gearbox of the present invention;

[0032] Figure 13 It is a structural schematic diagram of the auxiliary transmission input shaft assembly of the present invention;

[0033] Figure 14 It is a structural schematic diagram of the auxiliary transmission output shaft assembly of the present invention;

[0034] Figure 15It is a schematic diagram of the transmission principle of the main gearbox of the main and auxiliary gearbox transmission of the present invention;

[0035] Figure 16 It is a structural schematic diagram of the input shaft assembly of the main gearbox of the present invention;

[0036] Figure 17 Schematic diagram of the structure of the output shaft assembly of the auxiliary transmission of the present invention;

[0037] Figure 18 A three-dimensional structural diagram of the transmission flange of the present invention;

[0038] Figure 19 A three-dimensional structural diagram of the transmission flange of the present invention from another perspective;

[0039] Figure 20 A three-dimensional view of a structure of a transmission flange of the present invention for connection with a transmission shaft;

[0040] Figure 21 It is a side view of the transmission flange of the present invention;

[0041] Figure 22 This is a front view of the transmission flange of the present invention;

[0042] Figure 23 This is a schematic diagram of the structure of the three groups of sub-transmission structure groups disconnected in the present invention;

[0043] Figure 24 This is a schematic structural diagram of the two groups of sub-transmission structures of the transmission flange of the present invention being staggered in the circumferential direction;

[0044] Description of reference numerals:

[0045] Auxiliary gearbox output 100, auxiliary gearbox input shaft 110, auxiliary gearbox input gear 120, auxiliary gearbox output shaft 130, auxiliary gearbox output gear 140, ball bearing 150, tapered bearing 160, main gearbox 200, power unit 300, first synchronizer 2, second synchronizer 4, input shaft assembly 80, first gear input gear 81, second gear input gear 82, third gear input gear 83, fourth gear input gear 84, input shaft 85, second bearing 86, fourth bearing 87, output shaft assembly 90, first gear output gear 91, second gear output gear 92, third gear output gear 93, fourth gear output gear 94, output shaft 95, first bearing 96, third bearing 97.

[0046] Shift drum 1, guide groove 11, shift area 111, neutral area 112; first guide section 113, second guide section 114, third guide section 115, first angular position 12, second angular position 13;

[0047] Limiting groove 21, first driving mechanism 3, first sliding member 31, first shift fork 32, first connecting member 33, first rotating member 321, second rotating member 322, third rotating member 323, fourth rotating member 324, shifting member 325, rotating belt 326, second driving mechanism 5, second sliding member 51, second shift fork 52, second connecting member 53; motor 6, rotating shaft 7;

[0048] Flange body 410, first connecting part 411, second connecting part 412, limiting hole 4121, stop 4122, first transmission structure 420, first connecting structure 430, second transmission structure 440, first sub-transmission structure group 441, second sub-transmission structure group 442, third sub-transmission structure group 443, fourth sub-transmission structure group 444, and fifth sub-transmission structure group 445. DETAILED DESCRIPTION

[0049] In order to make the purpose, 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 in conjunction with the embodiments 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 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" and the like is based on the orientation or position relationship shown in the accompanying drawings, and 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 operate in a specific orientation, and therefore cannot be understood as limiting the present invention. Moreover, the term "comprises", "includes" 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 process, method, article or device. In the absence of further limitations, elements defined by the phrase "comprising..." do not preclude the presence of additional identical elements in the process, method, article, or apparatus comprising the elements. The embodiments of the present invention and the features thereof may be combined with each other if there is no conflict, and all are within the scope of protection of the present invention.

[0050] A vehicle is a commonly used means of transportation, primarily consisting of a powertrain, transmission system, body, and chassis. The transmission system includes a transmission, drive shaft, and differential. When the vehicle is moving, the power from the powertrain is transmitted to the transmission. The transmission converts the power from the powertrain and outputs power with appropriate torque and speed. The converted power is then transmitted to the drive shaft, which transmits the power to the differential. The differential then transmits the power to the wheels on both sides. The converted power can also be transmitted directly to the differential. To achieve parking and shifting, the transmission is also equipped with a shifting device and a parking device. To lubricate the transmission, differential, and other devices, a lubrication system is also provided for the transmission, differential, and other devices.

[0051] Example 1

[0052] like Figure 11 As shown, this embodiment provides a main-and-sub-box transmission, which includes a main gearbox 200 and a sub-gearbox 100, wherein the sub-gearbox 100 is located on one side of the axial direction of the main gearbox 200. The main gearbox 200 and the sub-gearbox 100 can achieve outputs of different torques and speeds.

[0053] The main gearbox 200 includes an input shaft assembly 80, an output shaft assembly 90 and a shift mechanism. The input shaft assembly 80 is used to transmit the power of the vehicle power unit 300 to the output shaft assembly 90, and the shift mechanism is used to switch the gear position of the main gearbox 200.

[0054] The input shaft assembly 80 and the output shaft assembly 90 cooperate to transmit power. In this embodiment, the input shaft assembly 80 and the output shaft assembly 90 cooperate to reduce power at the input end of the main transmission 200 before outputting it at the output end. Furthermore, the main transmission 200 of this embodiment can be configured with multiple gears having different transmission ratios, and a shift mechanism can be used to achieve switching between these gears.

[0055] The auxiliary transmission case 100 is connected to the output shaft assembly 90 via a clutch mechanism, which is used to connect or disconnect power transmission between the auxiliary transmission case 100 and the output shaft assembly 90. A keyway is provided on the auxiliary transmission case input shaft 110, which is connected to the clutch mechanism via the keyway. The clutch mechanism can be a clutch. One end of the clutch is connected to the output shaft of the main transmission case 200, and the other end is connected to the output shaft of the auxiliary transmission case 100 via a spline.

[0056] like Figure 12As shown, the auxiliary transmission case 100 includes an auxiliary transmission case input shaft 110, an auxiliary transmission case input gear 120, an auxiliary transmission case output shaft 130 and an auxiliary transmission case output gear 140. During the transmission process, the auxiliary transmission case input shaft 110 drives the auxiliary transmission case input gear 120 to rotate, the auxiliary transmission case input gear 120 engages with the auxiliary transmission case output gear 140, and the auxiliary transmission case output gear 140 drives the auxiliary transmission case output shaft 130 to rotate.

[0057] During the transmission process, the auxiliary box input gear 120 rotates synchronously with the auxiliary box input shaft 110, and the auxiliary box output gear 140 rotates synchronously with the auxiliary box output shaft 130. To this end, this embodiment provides two methods for achieving synchronous rotation of the auxiliary box input gear 120 and the auxiliary box input shaft 110, and synchronous rotation of the auxiliary box output gear 140 and the auxiliary box output shaft 130.

[0058] In one embodiment, the auxiliary box input gear 120 and the auxiliary box input shaft 110 are integrally formed, and the auxiliary box output gear 140 and the auxiliary box output shaft 130 are integrally formed. In this embodiment, the auxiliary box input gear 120 is directly formed on the auxiliary box input shaft 110, and the auxiliary box output gear 140 is directly formed on the auxiliary box output shaft 130.

[0059] Another way is that the auxiliary box input gear 120 is fixedly connected to the auxiliary box input shaft 110, and the auxiliary box output gear 140 is fixedly connected to the auxiliary box output shaft 130. The fixed connection can be a key or spline connection.

[0060] like Figure 13 As shown, the auxiliary box input shaft 110 is installed in the auxiliary box, and ball bearings 150 are provided at both ends of the auxiliary box input shaft 110. The auxiliary box input shaft 110 is rotatably connected to the housing of the auxiliary transmission case 100 through the ball bearings 150.

[0061] like Figure 14 As shown, the auxiliary transmission output shaft 130 is installed in the auxiliary transmission. Tapered bearings 160 are provided at both ends of the auxiliary transmission output shaft 130. The auxiliary transmission output shaft 130 is rotatably connected to the housing of the auxiliary transmission case 100 via the tapered bearings 160. The tapered surfaces of the tapered bearings 160 at both ends face opposite directions. The use of tapered bearings 160 can help the auxiliary transmission output shaft 130 withstand axial impacts caused by loads. The tapered surfaces at both ends face opposite directions, allowing the tapered bearings 160 to withstand bidirectional axial impacts.

[0062] When the output shaft assembly 90 and the auxiliary transmission 100 are in a disconnected state, the power output by the output shaft assembly 90 is output to the transmission shaft. When the output shaft assembly 90 and the auxiliary transmission 100 are in a connected state, the power output by the output shaft assembly 90 is output to the transmission shaft after being decelerated by the auxiliary transmission 100.

[0063] The transmission of this embodiment offers two output modes. One is that the power from the vehicle's power unit 300 is transmitted to the main transmission 200, where it is decelerated and directly transferred to the vehicle's drive shaft. The other is that the power from the vehicle's power unit 300 is first transmitted to the main transmission 200, where it is decelerated and then transferred to the auxiliary transmission 100 via a clutch device. After further deceleration and torque increase, the transmission is then output to the vehicle's drive shaft. In the first transmission mode, the output shaft of the main transmission 200 is in driving connection with the vehicle's drive shaft. In the second transmission mode, the auxiliary transmission output shaft 130 is in driving connection with the drive shaft.

[0064] The first transmission mode outputs a higher speed and lower torque, making it suitable for vehicles such as family cars and sedans. The second transmission mode, after two reductions in speed by the main transmission 200 and the auxiliary transmission 100, outputs a lower speed and higher torque. Therefore, it is suitable for vehicles such as heavy-duty trucks, commercial vehicles, buses, and electric vehicles. The two aforementioned modes can be selected based on the clutch state of the clutch device. Because the main transmission 200 utilizes a shift mechanism to output a variety of gear ratios, and because this embodiment utilizes a detachable connection between the main transmission 200 and the auxiliary transmission 100 shaft system, various gear ratios can be flexibly configured, achieving a variety of output gear ratios.

[0065] In this embodiment, the power generated by the vehicle's power unit is transmitted to input shaft assembly 80. The input shaft assembly 80 and the output shaft assembly 90 work together to transmit the power from input shaft assembly 80 to output shaft assembly 90. Finally, the output shaft assembly 90 transmits the power to the drive shaft. The vehicle's power unit includes, but is not limited to, an engine and an electric motor.

[0066] like Figure 16 As shown, the input shaft assembly 80 includes an input shaft 85, a first gear input gear 81, a second gear input gear, a third gear input gear 83, and a fourth gear input gear. The first gear input gear 81, the third gear input gear, the fourth gear input gear 84, and the second gear input gear are arranged in sequence along the axial direction of the input shaft 85;

[0067] The transmission of this embodiment further includes input shaft bearings, which are arranged at both ends of the input shaft 85 . The input shaft bearings are interference fit with the input shaft, and the outer diameter of the input shaft 85 cooperates with the housing to support the input shaft assembly 80 .

[0068] The output shaft assembly 90 is provided with an output shaft 95, a first gear output gear 91 meshing with the first gear input gear 81, a second gear output gear meshing with the second gear input gear 82, a third gear output gear meshing with the third gear input gear 83, and a fourth gear output gear meshing with the fourth gear input gear 84;

[0069] The transmission of this embodiment further includes output shaft bearings, which are arranged at both ends of the output shaft 95 and are interference fit with the output shaft 95 . The outer diameter of the bearings cooperates with the housing to support the output shaft assembly 90 .

[0070] The output shaft 95 can be connected to the output shaft of the engine or motor through a coupling, a spline, or the like, so that the power of the engine or the motor can be transmitted to the output shaft 95. The output shaft 95 can be connected to the transmission shaft through a coupling, a flange, a spline, or the like, so that the power of the output shaft 95 can be transmitted to the transmission shaft.

[0071] In this embodiment, the transmission can be shifted into four different gears: first gear, second gear, third gear, and fourth gear. The gears on the output shaft 95 used to achieve these four gears correspond to the first gear input gear 81, the second gear input gear, the third gear input gear 83, and the fourth gear input gear, respectively. The gears on the output shaft 95 used to achieve these four gears correspond to the first gear output gear 91, the second gear output gear 92, the third gear output gear, and the fourth gear output gear 94, respectively. Gears on the output shaft 95 that are in the same gear mesh with each other.

[0072] In this embodiment, the input gears for the four gears are arranged axially along the output shaft 95 in the following order: first gear input gear 81, third gear input gear, fourth gear input gear 84, and second gear input gear. The output gears for the four gears are arranged axially along the output shaft 95 in the following order: first gear output gear 91, third gear output gear 93, fourth gear output gear, and second gear output gear 92. The gears are not arranged in a sequential order of first, second, third, and fourth gears. Instead, they are arranged in an alternating pattern, with first and second gears separated by third gear, and third and fourth gears separated by second gear. Third and fourth gears are located in the middle of the shaft system. This embodiment utilizes a shift mechanism to switch gears within the transmission. Because first and second gears are separated, first and second gears can be engaged independently without interfering with each other, improving gear engagement comfort. Similarly, the second gear and the third gear can also be shifted separately without interfering with or affecting each other, thus improving the comfort of shifting gears.

[0073] In this embodiment, the shifting mechanism includes a first synchronizer 2 and a second synchronizer 4. The first synchronizer 2 is arranged on the output shaft 95, and the second synchronizer 4 is arranged on the output shaft 95. The first synchronizer 2 is used to make the output shaft 95 of the transmission rotate synchronously with the second gear input gear 82 or the fourth gear input gear 84, and the second synchronizer 4 is used to make the output shaft 95 of the transmission rotate synchronously with the first gear output gear 91 or the third gear output gear 93.

[0074] In this embodiment, the first synchronizer 2 and the second synchronizer 4 are arranged on different shaft systems, resulting in a staggered arrangement of the first synchronizer 2 and the second synchronizer 4. This prevents the two synchronizers from interfering with each other during gear shifting. Since first and second gears are staggered, with the second synchronizer 4 being used for first gear engagement and the first synchronizer 2 for second gear engagement, first and second gear engagements can be performed independently without interfering with each other. Since second and third gears are staggered, with the first synchronizer 2 being used for second gear engagement and the second synchronizer 4 for third gear engagement, second and third gear engagements can be performed independently without interfering with each other. Since third gear engagements are performed using the second synchronizer 4 and fourth gear engagements using the first synchronizer 2, third and fourth gear engagements can be performed independently without interfering with each other. The aforementioned gear arrangement and synchronizer layout in this embodiment allows for the use of different synchronizers for each adjacent gear during stepwise gear engagement, ensuring that the gear engagement processes of each gear do not interfere with each other.

[0075] In this embodiment, the first synchronizer 2 is located between the second gear input gear 82 and the fourth gear input gear. Thus, when the first synchronizer 2 is moved toward one side in the axial direction, it engages with the second gear input gear, and when it is moved toward the other side in the axial direction, it engages with the fourth gear input gear. Therefore, it is very convenient to engage in either second or fourth gear. The distance that the gear engaging component needs to move is also relatively short.

[0076] In this embodiment, the second gear input gear is rotationally connected to the output shaft 95, the fourth gear input gear is rotationally connected to the output shaft 95, and the first synchronizer 2 is synchronously transmitted to the output shaft 95. When the first synchronizer 2 is in a state of being engaged with the second gear input gear, the power of the output shaft 95 is transmitted to the second gear input gear through the first synchronizer 2. When the first synchronizer 2 is in a state of being engaged with the fourth gear input gear, the power of the output shaft 95 is transmitted to the fourth gear input gear through the first synchronizer 2.

[0077] The aforementioned synchronous transmission connection refers to a connection method that can make the first synchronizer 2 and the output shaft 95 rotate synchronously.

[0078] The aforementioned second-gear input gear is rotatably connected to the output shaft 95, and the fourth-gear input gear is rotatably connected to the output shaft 95 means that the second-gear gear can rotate relative to the output shaft 95 after being connected to the output shaft 95, and the fourth-gear gear can rotate relative to the output shaft 95 after being connected to the output shaft 95. The second-gear input gear and the fourth-gear input gear can be loosely mounted on the output shaft 95 so that the second-gear input gear and the fourth-gear input gear can rotate relative to the output shaft 95.

[0079] The input shaft assembly 80 of this embodiment further includes a second bearing 86 and a fourth bearing 87. The second bearing 86 is disposed on the output shaft 95, and the second gear input gear is rotatably connected to the output shaft 95 via the second bearing 86. The fourth bearing 87 is disposed on the output shaft 95, and the fourth gear input gear is rotatably connected to the output shaft 95 via the fourth bearing 87. The second bearing 86 and the fourth bearing 87 are preferably needle roller bearings. Of course, other types of bearings may also be used in other embodiments, and this is not a limitation here.

[0080] The first synchronizer 2 can be connected to the output shaft 95 through a spline for synchronous transmission. For example, a spline is provided on the outer diameter of the output shaft 95, and a keyway that cooperates with the spline is provided on the inner wall of the first synchronizer 2. The spline on the output shaft 95 is inserted into the keyway of the first synchronizer 2 along the axial direction to form a connection between the first synchronizer 2 and the output shaft 95. The first synchronizer 2 can rotate synchronously with the output shaft 95 by virtue of the cooperation between the spline and the keyway.

[0081] Since the first synchronizer 2 rotates synchronously with the output shaft 95, when the first synchronizer 2 is engaged with the second gear input gear, the second gear input gear rotates synchronously with the first synchronizer 2 under the drive of the first synchronizer 2. When the first synchronizer 2 is engaged with the fourth gear input gear, the fourth gear input gear rotates synchronously with the first synchronizer 2 under the drive of the first synchronizer 2.

[0082] like Figure 15 and Figure 17 As shown, in this embodiment, the first-gear output gear is rotationally connected to the output shaft 95, the third-gear output gear 93 is rotationally connected to the output shaft 95, and the second synchronizer 4 is synchronously transmitted to the output shaft 95. When the second synchronizer 4 is in a state of being combined with the first-gear output gear, the power of the first-gear output gear is transmitted to the output shaft 95 through the second synchronizer 4. When the second synchronizer 4 is in a state of being combined with the third-gear output gear 93, the power of the third-gear output gear 93 is transmitted to the output shaft 95 through the second synchronizer 4.

[0083] The aforementioned synchronous transmission connection refers to a connection method that enables synchronous rotation of the second synchronizer 4 and the output shaft 95. The aforementioned first-gear output gear is rotationally connected to the output shaft 95, and the third-gear output gear 93 is rotationally connected to the output shaft 95. This means that the first-gear output gear can rotate relative to the output shaft 95 after being connected to the output shaft 95, and the third-gear output gear can rotate relative to the output shaft 95 after being connected to the output shaft 95. The first-gear output gear and the third-gear output gear 93 can be loosely mounted on the output shaft 95 to enable the first-gear output gear and the third-gear output gear 93 to rotate relative to the output shaft 95.

[0084] like Figure 15 and Figure 17 As shown, the output shaft assembly 90 of this embodiment further includes a first bearing 96 and a third bearing 97. The first bearing 96 is disposed on the output shaft 95, and the first gear output gear is rotatably connected to the output shaft 95 via the first bearing 96. The third bearing 97 is disposed on the output shaft 95, and the third gear output gear 93 is rotatably connected to the output shaft 95 via the third bearing 97. The first bearing 96 and the third bearing 97 are preferably needle roller bearings. Of course, other types of bearings may also be used in other embodiments, and this is not a limitation here.

[0085] Through the above design, the third and fourth gears are arranged in the middle when the shaft system is arranged, and the first and second gears are arranged on both sides, which is conducive to the spatial arrangement of the needle rollers and reduces other parts. The synchronizer used to combine with the second and fourth gears is arranged on the output shaft 95, which can greatly reduce the demand for synchronizer capacity and reduce the cost of the synchronizer.

[0086] The second synchronizer 4 can be connected to the output shaft 95 through a spline for synchronous transmission. For example, a spline is provided on the outer diameter of the output shaft 95, and a keyway that cooperates with the spline is provided on the inner wall of the first synchronizer 2. The spline on the output shaft 95 is inserted into the keyway of the first synchronizer 2 along the axial direction to form a connection between the second synchronizer 4 and the output shaft 95. The second synchronizer 4 can rotate synchronously with the output shaft 95 by virtue of the cooperation between the spline and the keyway.

[0087] Since the second synchronizer 4 rotates synchronously with the output shaft 95, when the second synchronizer 4 is engaged with the third gear output gear 93, the third gear output gear 93 rotates synchronously with the second synchronizer 4 under the drive of the second synchronizer 4. When the second synchronizer 4 is engaged with the fourth gear input gear, the fourth gear input gear rotates synchronously with the second synchronizer 4 under the drive of the second synchronizer 4.

[0088] like Figure 17As shown, in this embodiment, the second synchronizer 4 is located between the first gear output gear 91 and the third gear output gear 93, so that the second synchronizer 4 can be combined with the first gear output gear 91 when the component used to engage the gear moves toward one side in the axial direction, and can be combined with the third gear output gear 93 when it moves toward the other side in the axial direction. Therefore, it is very convenient to engage the first gear or the third gear, and the distance that the component used to engage the gear needs to move is relatively short.

[0089] The first gear input gear and the third gear input gear can be connected to the output shaft 95 through splines and rotate synchronously with the output shaft 95, while the second gear output gear 92 and the fourth gear output gear 94 can be connected to the output shaft 95 through splines and rotate synchronously with the output shaft 95.

[0090] The method for performing gear shift control using the transmission of this embodiment is as follows:

[0091] The first synchronizer 2 is controlled to be in a state of being separated from both the fourth gear input gear and the second gear input gear, while the second synchronizer 4 is in a state of being engaged with the first gear output gear and separated from the third gear output gear 93, and the gear position of the transmission is switched to first gear;

[0092] The first synchronizer 2 is controlled to be in a state of being engaged with the second gear input gear and separated from the fourth gear input gear, while the second synchronizer 4 is in a state of being separated from both the first gear output gear and the third gear output gear 93, and the gear position of the transmission is switched to second gear;

[0093] The first synchronizer 2 is controlled to be in a state of being separated from both the fourth gear input gear and the second gear input gear, while the second synchronizer 4 is in a state of being engaged with the third gear output gear 93 and separated from the first gear output gear, and the gear position of the transmission is switched to third gear;

[0094] The first synchronizer 2 is controlled to be in a state of being engaged with the fourth gear input gear and separated from the second gear input gear. At the same time, the second synchronizer 4 is in a state of being separated from both the first gear output gear and the third gear output gear 93. The gear position of the transmission is switched to fourth gear.

[0095] The specific operation process is as follows:

[0096] When engaging first gear, the second synchronizer 4 is shifted to the left, the first gear output gear is connected to the output shaft 95, and power is transmitted from the output shaft 95 through the spline, and the output shaft 95 is transmitted to the first gear output gear on the output shaft 95 through the first gear input gear on the output shaft 95. The first gear output gear transmits power to the output shaft 95, and the power is transmitted to the transmission shaft through the spline on the output shaft 95;

[0097] When engaging the second gear, the first synchronizer 2 is shifted to the right, the second gear input gear is connected to the output shaft 95, the power is transmitted to the output shaft 95 through the spline connection, the output shaft 95 is transmitted to the second gear input gear through the spline connection, the second gear input gear transmits the power to the second gear output gear 92, the second gear output gear 92 transmits the power to the output shaft 95 through the spline, and the second gear output shaft 95 transmits the power to the transmission shaft through the spline;

[0098] When the third gear is engaged, the second synchronizer 4 is shifted to the right, the third gear output gear 93 is connected to the output shaft 95, the power is transmitted to the output shaft 95 through the spline, the output shaft 95 is transmitted to the third gear output gear 93 through the third gear input gear, the third gear output gear 93 is transmitted to the output shaft 95, and the power is transmitted to the transmission shaft through the spline on the output shaft 95.

[0099] When engaging the fourth gear, the first synchronizer 2 is shifted to the left, the fourth input gear and the output shaft 95 are connected, the power is transmitted to the output shaft 95 through the spline, the output shaft 95 is transmitted to the fourth input gear through the spline connection, the fourth input gear is transmitted to the fourth output gear on the output shaft 95, and the output shaft 95 is transmitted to the transmission shaft through the spline.

[0100] Example 2

[0101] like Figure 1 This embodiment provides a four-speed transmission shifting device for engaging four gears. This device can also be used in the transmission of Example 1. For ease of description, these four gears are divided into two groups: a first group and a second group, each group consisting of two gears. The four-speed transmission shifting device of this embodiment includes a shift drum 1, a motor 6, a first synchronizer, a first drive mechanism 3, a second synchronizer 4, and a second drive mechanism 5.

[0102] like Figure 2 and Figure 3 As shown, the shift drum 1 is provided with a guide groove 11 extending along its circumferential direction, and the guide groove 11 includes a shift area 111 that rotates to different angular positions as the shift drum 1 rotates;

[0103] like Figure 1 As shown, the shift drum 1 can be set to a cylindrical shape, and the aforementioned guide groove 11 can be set on the cylindrical peripheral wall of the shift drum 1. The shift area 111 is a part of the entire guide groove 11. The shift drum 1 can rotate around its own axis, and the shift area 111 also rotates to different positions as the shift drum 1 rotates.

[0104] like Figure 5As shown, the first synchronizer is used to participate in the gear shifting operation of the first group of gears. The first synchronizer can be connected to the input shaft or the output shaft in synchronous rotation; the first synchronizer is provided with a gear shifting component, which can move along the axial direction of the first synchronizer under the action of an external force (for example, under the shifting of a shift fork). When the gear shifting component of the first synchronizer moves to fully engage with the gear of a certain gear, the first synchronizer rotates synchronously with the gear. At this time, the power of the input shaft can be transmitted to the gear through the first synchronizer, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the first synchronizer and the input shaft or the output shaft rotate synchronously.

[0105] The first driving mechanism 3 is slidably connected to the guide groove 11 at the first angular position 12 of the shift drum 1. The first driving mechanism 3 is used to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to a first axial position to engage a gear, or to push the shifting component of the first synchronizer to move along the axial direction of the first synchronizer to a second axial position to engage a gear, wherein the first axial position and the second axial position are different.

[0106] The first axial position refers to the position at which the first synchronizer's shifting component is fully engaged with a gear of one of the first gear positions and rotates synchronously therewith. The second axial position refers to the position at which the first synchronizer's shifting component is fully engaged with a gear of another gear position in the first gear position and rotates synchronously therewith. The shifting component may be a synchronizer ring of the first synchronizer.

[0107] As the shift drum 1 rotates, the shift zone 111 can rotate to a range of angular positions where it is in sliding connection with the first drive mechanism 3. Within this angular position range, the position of the shift zone 111 in contact with the first drive mechanism 3 continuously changes as the shift drum 1 rotates. Because the axial distances between the shift zone 111 and the first synchronizer vary at different positions, the shift zone 111 can drive the first drive mechanism 3 to move axially during rotation. This axial movement of the first drive mechanism 3 simultaneously pushes the first synchronizer's shifting components to move axially.

[0108] In this embodiment, the first driving mechanism 3 includes a first sliding member 31 , a first shift fork 32 and a first connecting member 33 . The first connecting member 33 is connected to the first sliding member 31 and the first shift fork 32 , respectively. The first sliding member 31 slides along the guide groove 11 .

[0109] The width of the guide groove is slightly larger than that of the first slider 31, constraining the movement of the first connecting member 33 to axial movement. Viewed along the axial direction of the shift drum 1, the guide groove 11 has varying distances from the first synchronizer or the second synchronizer 4 at different circumferential locations in some areas. As the shift drum 1 rotates, the guide groove 11 contacts the first slider 31 at different locations. While sliding circumferentially relative to the guide groove 11, the slider also moves back and forth axially, driven by the guide groove 11. Because the first connecting member 33 connects the first slider 31 and the first shift fork 32, the first shift fork 32 also moves axially in sync with the first slider 31. The first connecting member 33 can be positioned on a radially lateral surface of the shift drum 1. The first slider 31 is positioned radially along the shift drum 1, with one end of the first slider 31 connected to the first connecting member 33 and the other end embedded in the guide groove 11.

[0110] like Figure 1 and Figure 6 As shown, the second synchronizer 4 is used to participate in the gear operation of the second group of gears. The second synchronizer 4 can be connected to the input shaft or the output shaft for synchronous rotation. The second synchronizer 4 is provided with a gear engaging component, which can move along the axial direction of the second synchronizer 4 under the action of an external force (for example, under the shifting of a shift fork). When the gear engaging component of the second synchronizer 4 moves to fully engage with the gear of a certain gear, the second synchronizer 4 rotates synchronously with the gear. At this time, the power of the input shaft can be transmitted to the gear through the second synchronizer 4, or the power of the gear can be transmitted to the output shaft. The aforementioned synchronous transmission connection refers to a connection method that can make the second synchronizer 4 and the input shaft or the output shaft rotate synchronously.

[0111] The second driving mechanism 5 is slidably connected to the guide groove 11 at the second angular position 13 of the shift drum 1. The second driving mechanism 5 is used to push the gear engaging component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the third axial position to engage gear, or push the gear engaging component of the second synchronizer 4 to move along the axial direction of the second synchronizer 4 to the fourth axial position to engage gear, under the drive of the shift zone 111. The third axial position is different from the fourth axial position, and the second angular position 13 is different from the first angular position 12.

[0112] The third axial position refers to the position at which the shifting component of the second synchronizer 4 is fully engaged with the gear of one of the second gear positions and rotates synchronously therewith. The fourth axial position refers to the position at which the shifting component of the second synchronizer 4 is fully engaged with the gear of another gear position in the second gear position and rotates synchronously therewith. The shifting component may be a synchronizer ring of the second synchronizer 4.

[0113] As the shift drum 1 rotates, the shift zone 111 can rotate to a range of angular positions where it is slidably connected to the second drive mechanism 5. Within this angular position range, the position of the shift zone 111 in contact with the second drive mechanism 5 continuously changes as the shift drum 1 rotates. Because the axial distances between the shift zone 111 and the second synchronizer 4 vary at different positions, the shift zone 111 can drive the second drive mechanism 5 to move axially during rotation. This axial movement of the second drive mechanism 5 simultaneously pushes the engaging components of the second synchronizer 4 to move axially.

[0114] In this embodiment, the second driving mechanism 5 includes a second sliding member 51 , a second shift fork 52 and a second connecting member 53 . The second connecting member 53 is connected to the second sliding member 51 and the second shift fork 52 , respectively. The second sliding member 51 slides along the guide groove 11 .

[0115] The width of the guide groove is slightly larger than that of the second slider 51, constraining the movement of the second connecting member 53 to axial movement. Viewed along the axial direction of the shift drum 1, the guide groove 11 has varying distances from the first synchronizer or the second synchronizer 4 at different circumferential locations in some areas. As the shift drum 1 rotates, the guide groove 11 contacts the second slider 51 at different locations. While sliding circumferentially relative to the guide groove 11, the slider also moves back and forth axially, driven by the guide groove 11. Because the second connecting member 53 connects the second slider 51 and the second shift fork 52, the second shift fork 52 also moves axially in sync with the second slider 51. The second connecting member 53 can be positioned on a radially lateral surface of the shift drum 1. The second slider 51 is positioned radially along the shift drum 1, with one end of the second slider 51 connected to the second connecting member 53 and the other end embedded in the guide groove 11.

[0116] like Figure 1 As shown, the motor 6 is used to drive the shift drum 1 to rotate so that the shift area 111 drives the first drive mechanism 3 and the second drive mechanism 5 to move back and forth in the axial direction of the shift drum 1. The motor 6 and the first synchronizer and the second synchronizer 4 are located on both sides of the shift drum 1 in the axial direction, and the motor 6 is coaxially arranged with the shift drum 1.

[0117] In this embodiment, the motor 6 and the two drive mechanisms are separated in the axial direction so that they are located on both sides of the shift drum 1. In this way, the actions of the motor 6 and the drive mechanisms do not affect each other, and the coaxial arrangement of the motor 6 and the shift drum 1 can make the structure more compact and also utilize the power transmission between the motor 6 and the shift drum 1.

[0118] As a preferred embodiment, in this embodiment, the four-speed transmission shifting device further includes a rotating shaft 7. The shift drum 1 has an interference fit with the rotating shaft 7. The motor 6 drives the rotating shaft 7 to rotate, thereby driving the shift drum 1. The direct interference fit between the rotating shaft and the shift drum 1 facilitates transmission, making the transmission process simpler and more reliable. The motor 6 is mounted on the assembly housing, and the shift drum 1 is positioned on the housing via the rotating shaft 7. The shift drum 1 and the rotating shaft 7 are relatively fixed, and the rotating shaft 7 is rotatable on the housing.

[0119] like Figure 7 As shown, in this embodiment, an annular limiting groove is provided on the peripheral wall of the first synchronizer and / or the second synchronizer 4, and a shifting member 325 is provided at the end of the first shift fork 32 and / or the second shift fork 52. The shifting member 325 shifts the gear engaging component of the first synchronizer and / or the second synchronizer 4 by shifting the side wall of the limiting groove.

[0120] In this embodiment, the width of the limiting groove is greater than 1.1 times the width of the toggle member 325, and the distance between the first axial position and the second axial position is greater than twice the axial clearance between the toggle member 325 and the limiting groove. With the aforementioned structure, after the toggle member 325 is inserted into the limiting groove and the synchronizer's gear engaging component is toggled to the gear engaging position, one side of the toggle member 325 contacts one sidewall of the limiting groove, while a sufficient clearance is left between the other side of the toggle member 325 and the other sidewall of the limiting groove. This prevents the toggle member 325 from shifting the limiting groove due to unexpected small vibrations, causing the gear engaging component to disengage from the current gear position, thereby making gear engagement more reliable. When shifting gears normally, the distance that the toggle member 325 moves in the axial direction must exceed the axial gap between the toggle member 325 and the limiting groove. Therefore, during the shifting movement, the other side of the toggle member 325 can also push the shifting component to move by contacting the other side wall of the limiting groove.

[0121] When the toggle 325 toggles the synchronizer to shift gears, the toggle 325 contacts the synchronizer, and the synchronizer is in high-speed rotation, and relative motion occurs between the toggle 325 and the synchronizer. Therefore, there is continuous sliding friction between the toggle 325 and the synchronizer. Both the toggle 325 and the synchronizer are prone to wear and deformation, and the heat generated by friction will also affect the gearbox. To this end, replaceable wear-resistant parts can be set on the toggle 325 to allow the wear-resistant parts to contact the synchronizer. When the wear-resistant parts are worn to a certain extent, new wear-resistant parts can be replaced. When this method is used, the gearbox needs to be disassembled and assembled before the wear-resistant parts can be replaced, so it is very inconvenient during actual use.

[0122] To this end, an oil guide groove can be set on the first shift fork 32, and the outlet of the oil guide groove can be set on the surface where the shift member 325 contacts the synchronizer. The lubricating oil flows along the oil guide groove to the surface of the shift member 325, forming an oil film between the shift member 325 and the synchronizer to reduce the friction between the two.

[0123] In addition, rollers or needle rollers can be set on the shifting member 325 to reduce friction. However, since the roller contacts the synchronizer in point contact and the needle roller contacts the synchronizer in line contact, the contact areas of these two contact methods are very small, which can easily cause the synchronizer and the shift fork to be subjected to excessive force.

[0124] In this regard, this embodiment adopts a structure that can make the toggle member 325 rotate synchronously with the synchronizer to avoid friction. Figure 10As shown, the first shift fork 32 of this embodiment also includes a cylindrical first rotating member 321, a second rotating member 322, a third rotating member 323 and a fourth rotating member 324, and the first rotating member 321, the second rotating member 322, the third rotating member 323 and the fourth rotating member 324 are rotatably connected to the first shift fork 32, and the extension lines of the rotation axes of the first rotating member 321, the second rotating member 322, the third rotating member 323 and the fourth rotating member 324 intersect at the same intersection, and the same intersection is located on the rotation axis of the first synchronizer, the rotation axis of the first rotating member 321 and the rotation axis of the second rotating member 322 are located in a first plane, and the rotation axis of the third rotating member 323 and the rotation axis of the fourth rotating member 324 are located in a second plane different from the first plane, and the first plane and the second plane are arranged along the axial direction of the first synchronizer. The shifting member 325 is a rotating belt 326. One end of the rotating belt 326 passes sequentially around the outer walls of the first rotating member 321, the second rotating member 322, the third rotating member 323, and the fourth rotating member 324 before connecting to the opposite end. The rotating belt 326 may be a steel belt or a leather belt. In practice, the rotating belt 326 is tightened and wrapped around the outer walls of the four rotating members, connecting end to end to form a ring. When unfolded, the rotating belt 326 has an arc shape. If the distance between the first rotating member 321 and the second rotating member 322 is too long, a fifth rotating member may be provided between the first rotating member 321 and the second rotating member 322 to provide support for the rotating belt 326 in the middle. If the distance between the third rotating member 323 and the fourth rotating member 324 is too long, a fifth rotating member may be provided between the first rotating member 321 and the second rotating member 322 to provide support for the rotating belt 326 in the middle. The fifth and sixth rotating members may be provided in plurality, and their number may be determined by the distance between the first rotating member 321 and the second rotating member 322 or the distance between the third rotating member 323 and the fourth rotating member 324. Each of the aforementioned rotating members may be rotatably connected to the first shift fork 32 via a smooth rotating shaft.

[0125] After adopting the above structure, when the rotating belt 326 moves with the first shift fork 32 to the position of contacting the synchronizer, the rotating belt 326 rotates under the drive of the synchronizer. The rotation direction of the rotating belt 326 is as follows: Figures 8 to 10As shown by the arrow in the figure, when the rotating belt 326 first contacts the synchronizer, there is sliding friction between the rotating belt 326 and the synchronizer. When the rotating belt 326 and the synchronizer have the same rotational speed, there is no relative sliding between the rotating belt 326 and the synchronizer, and no sliding friction will occur to cause wear of the rotating belt 326 and the synchronizer. At this time, the rotating belt 326, driven by the synchronizer, rotates around the four rotating parts in a circular manner. The contact between the rotating belt 326 and the synchronizer is surface contact, which is less likely to cause excessive force concentration, and the rotating belt 326 can always rotate synchronously with the synchronizer.

[0126] This embodiment also provides another implementation method for solving the aforementioned sliding friction problem. The first shift fork 32 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 32, and one end of the rotating belt 326 passes around the outer walls of the seventh rotating member and the eighth rotating member in turn and then connects to the other opposite end. The rotating axes of the seventh rotating member and the eighth rotating member 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.

[0127] Each rotating assembly forms a small rotating unit, and the rotating belt 326 of each rotating assembly can circulate around four rotating members. Because the extension of the rotating assembly's axis of symmetry lies on the rotation axis of the first synchronizer, when the rotating belt 326 moves with the first shift fork 32 to a position of contact with the synchronizer, the rotation direction of the rotating belt 326 of each rotating assembly is nearly identical to that of the corresponding position on the synchronizer, resulting in minimal sliding friction between the rotating belt 326 of each rotating assembly and the synchronizer. This approach simplifies the structure, allows the rotating assemblies to be arranged in parallel, and facilitates installation, achieving both surface contact and reduced sliding friction.

[0128] The four-speed shifting device of the transmission of this embodiment can use the motor 6 to drive the shift drum 1 to rotate. When the shift area 111 of the shift drum 1 rotates to the position connected to the first drive mechanism 3, the shift area 111 can rotate with the shift drum 1 and push the first synchronizer through the first drive mechanism 3 to perform the gear shifting operation of two of the gears; when the shift area 111 of the shift drum 1 rotates to the position connected to the second drive mechanism 5, the shift area 111 can rotate with the shift drum 1 and push the second synchronizer 4 through the second drive mechanism 5 to perform the gear shifting operation of the other two gears; since the areas where the first drive mechanism 3 and the second drive mechanism 5 are connected to the shift drum 1 are at different angular positions, only one shift drum 1 and two drive mechanisms are needed to respectively shift two gears. The gear shifting operation of the aforementioned four gears can be completed by only one motor 6 driving one shift drum 1 to rotate. Therefore, there are fewer actuators for shifting, the gear shifting action is simple, and the operation is more reliable.

[0129] Example 3

[0130] like Figure 2 and Figure 3 As shown, this embodiment is further improved on the basis of embodiment 1. In this embodiment, the area outside the shift zone 111 in the guide groove 11 is the neutral zone 112. When the first drive mechanism 3 is connected to the neutral zone 112, the first synchronizer is in a neutral state; when the second drive mechanism is connected to the neutral zone 112, the second synchronizer 4 is in a neutral state, and the angle between the first angular position 12 and the second angular position 13 is greater than the central angle corresponding to the shift zone 111.

[0131] In this embodiment, the guide groove 11 is composed of a shift zone 111 and a neutral zone 112. Since the angle between the first angular position 12 and the second angular position 13 is greater than the central angle corresponding to the shift zone 111, the first drive mechanism 3 and the second drive mechanism 5 will not both be connected to the shift zone 111 when the shift drum 1 rotates to any angular position. In this way, when one synchronizer is in gear, the other synchronizer is in neutral, or both synchronizers are in neutral, and there will be no situation where both synchronizers are in gear. This avoids conflicts between gears, thereby further improving the reliability of gear shifting. Using the aforementioned method, only one guide groove 11 is required to achieve four gears, resulting in a simpler structure.

[0132] like Figure 3As shown, in this embodiment, the shifting area 111 includes a first guide section 113 and a second guide section 114. When the first drive mechanism 3 is connected to the first guide section 113, the gear engaging component of the first synchronizer is pushed to the first axial position, and when the first drive mechanism 3 is connected to the second guide section 114, the gear engaging component of the first synchronizer is pushed to the second axial position; when the second drive mechanism 5 is connected to the first guide section 113, the gear engaging component of the second synchronizer 4 is pushed to the third axial position, and when the second drive mechanism 5 is connected to the second guide section 114, the gear engaging component of the second synchronizer 4 is pushed to the fourth axial position.

[0133] like Figure 3 and Figure 4 As shown, Figure 4 The x-axis represents the position of the guide groove 11 in the axial direction, and the y-axis represents the position in the circumferential direction, wherein the first guide section 113 and the second guide section 114 correspond to the height ( Figure 4 The part indicated by H in the middle) is low ( Figure 4 Since the first and second synchronizers 4 are also used to engage two gears, the two guide sections of the shift area 111 also correspond to the two gears of each synchronizer. Since the first drive mechanism 3 and the second drive mechanism 5 are located at different angular positions, when the shift area 111 rotates to the angular position corresponding to the first drive mechanism 3 or the second drive mechanism 5, the corresponding drive mechanism can be shifted. Therefore, in this embodiment, only two high and low gears need to be set in the shift area 111 of the guide groove 11 to achieve the engagement of the four gears of the transmission.

[0134] In this embodiment, in the axial direction of the shift drum 1, the distance between the first guide section 113 and the first axial position is smaller than the distance between the neutral area 112 and the first axial position, and the distance between the neutral area 112 and the first axial position is smaller than the distance between the second guide section 114 and the first axial position.

[0135] In this embodiment, the first guide section 113 and the second guide section 114 are staggered in the axial direction to achieve driving the first drive mechanism 3 or the second drive mechanism 5 to engage in high and low gears. The above-mentioned method can make the high and low gear engagement positions be in neutral ( Figure 4 In this way, the distance from the neutral position to any of the high and low gear positions is relatively short, making gear shifting faster and more reliable.

[0136] As a preferred embodiment, in this embodiment, the shift area 111 also includes a third guide section 115. When the first drive mechanism 3 is connected to the third guide section 115, the gear engaging component of the first synchronizer is pushed to the neutral position; when the second drive mechanism 5 is connected to the third guide section 115, the gear engaging component of the second synchronizer 4 is pushed to the neutral position; in the axial direction of the shift drum 1, the distance between the third guide section 115 and the first axial position is equal to the distance between the neutral area 112 and the first axial position, and in the circumferential direction of the shift drum 1, the first guide section 113, the third guide section 115 and the second guide section 114 are arranged in sequence.

[0137] The axial position of the third guide section 115 of the shift zone 111 is the same as the axial position of the neutral zone 112. When the first drive mechanism 3 or the second drive mechanism 5 is connected to the guide groove 11 in the third guide section 115, the first synchronizer 4 or the second synchronizer 4 is in neutral. This method allows the shift drum 1 to be shifted into neutral even when it rotates into the shift zone 111, without having to wait until the first drive mechanism 3 or the second drive mechanism 5 is completely out of the shift zone 111, making the neutral shifting process simpler and faster. In addition, the aforementioned method is adopted to make the two sides adjacent to the high gear area (first guide section 113) on the guide groove 11 both areas corresponding to the neutral position (neutral area 112 and third guide section 115), so that no matter which direction the shift drum 1 rotates, the synchronizer will first exit to the neutral position. Similarly, the two sides adjacent to the low gear area (second guide section 114) on the guide groove 11 are both areas corresponding to the neutral position (neutral area 112 and third guide section 115), so that no matter which direction the shift drum 1 rotates, the synchronizer will first exit to the neutral position, thereby effectively avoiding conflicts between high and low gears.

[0138] The specific process of shifting is as follows:

[0139] The first driving mechanism 3 shifts: the motor 6 rotates clockwise ( Figure 1 Looking from the motor 6 toward the shift drum 1, power is transmitted to the shift drum 1 via the rotating shaft 7. The shift drum 1 rotates clockwise, driving the first shift fork 32 upward, and the first synchronizer engages an upward gear. The motor 6 rotates counterclockwise, and power is transmitted to the shift drum 1 via the rotating shaft 7. The shift drum 1 rotates counterclockwise, driving the first shift fork 32 downward, and the first synchronizer engages a downward gear.

[0140] The second drive mechanism 5 shifts: the shift drum 1 rotates counterclockwise by an angle, when Figure 1When the shift area 111 in the shift drum rotates to the position where the second sliding member 51 is connected to the guide groove 11 of the shift drum 1, the motor 6 continues to rotate counterclockwise, and the power is transmitted to the shift drum 1 through the rotating shaft 7. The shift drum 1 rotates counterclockwise to drive the second shift fork 52 to move upward, and the second synchronizer 4 shifts gear upward; the motor 6 continues to rotate counterclockwise, and the power is transmitted to the shift drum 1 through the rotating shaft 7. The shift drum 1 rotates counterclockwise to drive the second shift fork 52 to move downward, and the second synchronizer 4 shifts gear downward.

[0141] Example 4

[0142] like Figure 18 As shown, this embodiment provides a transmission flange, which mainly includes a flange body 410, a first transmission structure 420, a first connection structure 430 and a second transmission structure 440:

[0143] The first transmission structure 420 is provided 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 ;

[0144] like Figure 19 and Figure 21 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.

[0145] The first connecting structure 430 is provided on the flange body 410, and the first connecting structure 430 is used to connect the flange body 410 with the transmission shaft;

[0146] In this embodiment, the first connecting structure 430 only plays a connecting role. The first connecting structure 430 prevents the transmission shaft and the flange body 410 from being loosened by connecting the flange body 410 to the transmission shaft.

[0147] The second transmission structure 440 is arranged at one end of the flange body 410 facing the transmission shaft. The second transmission structure 440 is used to transmit the torque of the flange body 410 to the transmission shaft and prevent the torque from being transmitted to the first connection structure 430.

[0148] When the flange body 410 rotates under the drive of the transmission output shaft, the torque of the flange body 410 is transmitted to the transmission shaft via the second transmission structure 440. During the process of the flange body 410 driving the transmission shaft to rotate, the second transmission structure 440 is responsible for bearing the transmitted torque. Furthermore, the second transmission structure 440 is used to prevent the torque from being transmitted to the first connection structure 430. Thus, during the process of the flange transmitting the torque to the transmission shaft, the first connection structure 430 is not affected by the torque and is therefore not easily damaged. This ensures that the first connection structure 430 can always connect the flange body 410 to the transmission shaft, thereby improving the safety of the flange connection and reducing the number of first connection structures 430, thereby simplifying the structure and reducing costs.

[0149] As a preferred embodiment, 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. The rectangular teeth on the flange body 410 are used to cooperate with the rectangular teeth on the transmission shaft to transmit torque.

[0150] The rectangular teeth are elongated and have a rectangular cross-section. In this embodiment, rectangular teeth that mate with the rectangular teeth on the flange body 410 can be provided on the transmission shaft. After the flange body 410 is installed and connected to the transmission shaft, the end face of the flange body 410 mates with the transmission shaft, and the rectangular teeth on the flange body 410 engage 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, causing the transmission shaft and the flange body 410 to rotate together. The rectangular teeth can be directly machined on the end face of the flange body 410 by milling. In order to simplify the flange structure while allowing the rectangular teeth to withstand torque, the rectangular teeth are formed by two adjacent tooth grooves, which are formed by the end face of the flange body 410 being recessed in the direction away from the transmission shaft. Using the aforementioned structure to form rectangular teeth allows the tops of the teeth to be flush with the end surface of the flange body 410, thus eliminating the need for unnecessary space. The tooth grooves can be formed by simply removing material from the existing flange body 410. The resulting rectangular teeth are integrated with the flange body 410, minimizing impact on the existing flange body 410. The overall structure is simple and provides a strong load-bearing capacity.

[0151] 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.

[0152] Because the clearance between the first connecting member and the first connecting structure 430 in the direction of flange rotation is greater than the clearance between the rectangular teeth on the flange body 410 and the rectangular teeth on the transmission shaft, when the flange is transmitting, before the first connecting member and the first connecting structure 430 come into contact and receive force, the rectangular teeth on the flange body 410 first come into contact with the rectangular teeth on the transmission shaft. Due to the obstruction of the rectangular teeth on the transmission shaft, a clearance is always left between the first connecting member and the first connecting structure 430, thereby effectively avoiding 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.

[0153] In this embodiment, multiple transmission structure groups are provided on the flange body 410, each transmission structure group includes several first transmission structures 420 arranged parallel to 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 group is used to prevent torque from being transmitted to the first connection structure 430 corresponding to it.

[0154] like Figure 22 As shown, this embodiment can be provided with multiple first connection structures 430 along the circumferential direction of the flange body 410 to improve connection reliability. Furthermore, this embodiment employs a one-to-one correspondence between transmission structure groups and first connection structures 430. Each first connection structure 430 is protected by a corresponding transmission structure group, ensuring that, among the corresponding first connection structures 430 and transmission structure groups, the transmission structure group is preferred over the first connection structure 430 in terms of torque resistance. This avoids the problem of multiple first connection structures 430 being unable to guarantee that all first connection structures 430 are immune to torque. Each transmission structure group can include multiple first transmission structures 420 arranged in parallel. During transmission, each first transmission structure 420 in the same group can jointly withstand torque. This distributes the torque acting on the flange to each transmission structure group and then further to each first transmission structure 420, reducing the torque borne by each first transmission mechanism while increasing the overall torque resistance.

[0155] Furthermore, in the direction of rotation, the first connecting structure 430 is located at the center of its corresponding transmission structure group. This approach ensures that, regardless of whether the flange body 410 rotates forward or reverse, each first transmission structure 420 in the transmission structure group is subjected to torque before the first connecting structure 430 contacts the first connector, thereby ensuring that torque is not transmitted to the first connecting structure 430.

[0156] For example, six transmission structure groups can be set on the flange body 410, and each transmission structure group is provided with four rectangular teeth. These 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 group of symmetry axes. The six transmission structure groups are evenly distributed along the circumferential direction of the flange body 410, that is, the angle of the interval between any two adjacent transmission structure groups in the six transmission structure groups is the same, and the interval between adjacent groups is 60 degrees. It is understandable that the number of the aforementioned transmission groups and the number of first connecting structures 430 in each transmission structure group can also adopt other numbers, and are not limited here.

[0157] 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-mentioned method can further increase the torque capacity of each transmission structure group without increasing the number of rectangular teeth in each group.

[0158] like Figure 21 As shown, in this embodiment, the flange body 410 includes a cylindrical first connecting part 411 and a disc-shaped second connecting part 412, and the first connecting part 411 and the second connecting part 412 are arranged along the axial direction of the flange body 410. The first connecting part 411 is provided with a through hole passing through the connecting part, and the first transmission structure 420 is a spline, and the spline is provided on the through hole of the first connecting part 411, and the first connecting structure 430 is provided on the second connecting part 412.

[0159] When the first connection structure 430 adopts rectangular teeth, the rectangular teeth are provided on the disc surface of the second connection portion 412 facing the transmission shaft.

[0160] In this embodiment, the first connection portion 411 is used to connect the flange body 410 to the transmission output shaft, while the second connection portion 412 is used to connect the flange body 410 to the drive shaft. By arranging the first and second connection portions 411, 412 along the axial direction of the flange body 410, this embodiment allows the transmission output shaft and the drive shaft to be compactly distributed on both sides of the flange in the axial direction, thereby preventing mutual interference between the power input side and the power output side.

[0161] This embodiment uses splines for transmission on the power input side, which has a strong load-bearing capacity. A through hole can be machined in the first connecting portion 411 first, and then a spline can be machined on the inner wall of the through hole.

[0162] 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 in the radial direction of the second connecting portion 412. This approach can fully utilize the radial dimension of the second connecting portion 412 disk, maximizing the length of the rectangular teeth that can withstand torque.

[0163] When the rectangular tooth is long, the deformation of the rectangular tooth under torque increases. When the deformation exceeds a certain level, the same rectangular tooth will not be in sufficient contact with its mating rectangular tooth, which will reduce the load-bearing capacity of the rectangular tooth. To this end, in this embodiment, each rectangular tooth is composed of multiple sub-rectangular teeth of smaller lengths, and adjacent sub-rectangular teeth are disconnected. After adopting the above method, the deformation of each sub-rectangular tooth will not be added to the other sub-rectangular teeth, so that the deformation of the rectangular tooth can be dispersed among the sub-rectangular teeth. The deformation of each sub-rectangular tooth is very small and will not exceed the level that would cause insufficient contact between the rectangular teeth. The gap between adjacent sub-rectangular teeth can be very small, so the above structure will not significantly reduce the length of the part of the rectangular tooth that can withstand torque.

[0164] like Figure 24 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, except that 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 torque-bearing part of the rectangular teeth. 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.

[0165] 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.

[0166] In the circumferential direction, the first sub-transmission structure group 441 and the second sub-transmission structure group 442 can be completely staggered or partially staggered. 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 of the flange body 410 where the first sub-transmission structure group 441 and the second sub-transmission structure group 442 are disconnected 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, all of 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 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.

[0167] When using a partially staggered arrangement, the tooth grooves of the rectangular teeth in the first sub-transmission structure group 441 can be aligned with the tooth tops of the rectangular teeth in the second sub-transmission structure group 442. This arrangement maximizes the circumferential portion of the flange body 410 used to carry torque within the same transmission structure group, thereby increasing the torque that the flange body 410 can withstand.

[0168] like Figure 23 As shown, in this embodiment, the same transmission structure group is composed of three sub-transmission structure groups. From the outer wall of the flange body 410 inward, they are the third sub-transmission structure group 443, the fourth sub-transmission structure group 444, and the fifth sub-transmission structure group 445. The rectangular teeth of each transmission structure group are disconnected from each other, and the rectangular teeth of the third sub-transmission structure group 443 are shorter than those of the fourth sub-transmission structure group 444, which in turn are shorter than those of the fifth sub-transmission structure group 445. Under the same torque, the outer side of the flange body 410 deforms more than the inner side. This embodiment utilizes the aforementioned structure where the rectangular teeth shorten from the inside out. This reduces the variance in the deformation of the rectangular teeth at various radial locations on the flange body 410, preventing excessive deformation of the rectangular teeth at local radial locations on the flange body 410, which could affect the flange's service life.

[0169] like Figure 20 As shown, in this embodiment, a limiting hole 4121 cooperating with the transmission shaft is provided on the second connecting portion 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 connecting portion 411, and the spline extends to the position of the stop 4122.

[0170] During installation, the end of the transmission shaft can be inserted into the stop hole 4121 of the second connecting portion 412 until the end of the transmission shaft abuts the stop 4122. The output shaft of the gearbox can then be inserted into the through hole. Because the spline in the through hole extends to the stop 4122, the distance between the input end where torque is transmitted and the end of the transmission shaft is relatively short. This approach shortens the distance between the input end where torque is transmitted and the output end where torque is transmitted, thereby reducing the deformation of the transmission components between the input and output ends under the action of torque.

[0171] Example 5

[0172] This embodiment provides a vehicle, comprising the main and auxiliary transmissions and transmission flanges described in the aforementioned embodiments. The vehicle of this embodiment can be a conventional fuel vehicle, such as a gasoline vehicle or a diesel vehicle, or a new energy vehicle. New energy vehicles include, but are not limited to, pure electric vehicles (BEV / EV), hybrid vehicles (HEV, PHEV, and REEV), fuel cell vehicles (FCEV), and solar cell vehicles.

[0173] 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 above embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the above embodiments, or replace some or all of the technical features therein with 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. Main and auxiliary box transmission, characterized in that: include: The main gearbox includes an input shaft assembly, an output shaft assembly, and a shift mechanism. The input shaft assembly is used to transmit power from the vehicle power unit to the output shaft assembly, and the shift mechanism is used to switch the gear position of the main gearbox. Auxiliary gearbox, connected to the output shaft assembly via a clutch device, the clutch device is used to connect or disconnect the power transmission between the auxiliary gearbox and the output shaft assembly; When the output shaft assembly is disconnected from the auxiliary transmission, the power output by the output shaft assembly is output to the transmission shaft; when the output shaft assembly is connected to the auxiliary transmission, the power output by the output shaft assembly is decelerated by the auxiliary transmission and then output to the transmission shaft; The input shaft assembly is provided with an input shaft, a first gear input gear, a second gear input gear, a third gear input gear, and a fourth gear input gear, wherein the first gear input gear, the third gear input gear, the fourth gear input gear, and the second gear input gear are sequentially arranged along the axial direction of the input shaft; the output shaft assembly is provided with an output shaft, a first gear output gear meshing with the first gear input gear, a second gear output gear meshing with the second gear input gear, a third gear output gear meshing with the third gear input gear, and a fourth gear output gear meshing with the fourth gear input gear. The first transmission structure of the flange body is connected to the output shaft of the transmission and transmits the torque of the output shaft of the transmission to the flange body; The first connecting structure on the flange body is used to connect the flange body to the transmission shaft; The second transmission structure of the flange body is provided at one end of the flange body facing the transmission shaft, and the second transmission structure is used to transmit the torque of the flange body to the transmission shaft and prevent the torque from being transmitted to the first connection structure; The second transmission structure is a rectangular tooth, which is provided on the end surface where the flange body is connected to the transmission shaft, and the rectangular teeth on the flange body are used to cooperate with the rectangular teeth on the transmission shaft to transmit torque; the first connection structure 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 connection structure is greater than the fitting clearance between the rectangular teeth on the flange body and the rectangular teeth on the transmission shaft; The rectangular teeth are formed by two adjacent tooth grooves, and the tooth grooves are formed by the end surface of the flange body being recessed in a direction away from the transmission shaft.

2. The main and auxiliary box transmission according to claim 1, characterized in that: The auxiliary transmission includes an auxiliary transmission input shaft, an auxiliary transmission input gear, an auxiliary transmission output shaft and an auxiliary transmission output gear. The auxiliary transmission input shaft drives the auxiliary transmission input gear to rotate, the auxiliary transmission input gear is engaged with the auxiliary transmission output gear, and the auxiliary transmission output gear drives the auxiliary transmission output shaft to rotate.

3. The main and auxiliary box transmission according to claim 2, characterized in that: The auxiliary box input gear and the auxiliary box input shaft are an integrated structure, and the auxiliary box output gear and the auxiliary box output shaft are an integrated structure.

4. The main and auxiliary box transmission according to claim 2, characterized in that: The auxiliary box input gear is fixedly connected to the auxiliary box input shaft, and the auxiliary box output gear is fixedly connected to the auxiliary box output shaft.

5. The main and auxiliary box transmission according to claim 2, characterized in that: The auxiliary box input shaft is provided with a keyway, and the auxiliary box input shaft is connected to the clutch device through the keyway.

6. The main and auxiliary box transmission according to claim 2, characterized in that: Ball bearings are provided at both ends of the auxiliary box input shaft, and the auxiliary box input shaft is rotatably connected to the box body of the auxiliary transmission through the ball bearings.

7. The main and auxiliary box transmission according to claim 2, characterized in that: Conical bearings are provided at both ends of the auxiliary box output shaft, and the conical surfaces of the conical bearings at both ends are in opposite directions. The auxiliary box output shaft is rotatably connected to the box body of the auxiliary transmission case through the conical bearings.

8. The main and auxiliary box transmission according to any one of claims 1 to 7, characterized in that: The shifting mechanism includes a first synchronizer and a second synchronizer, the first synchronizer is arranged on the input shaft, and the second synchronizer is arranged on the output shaft. The first synchronizer is used to make the input shaft of the transmission rotate synchronously with the second gear input gear or the fourth gear input gear, and the second synchronizer is used to make the output shaft of the transmission rotate synchronously with the first gear output gear or the third gear output gear.

9. A vehicle, characterized in that A main and auxiliary box transmission comprising the one of claims 1 to 8.

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