A multi-gear planetary row power system and vehicle

Abstract

The application provides a multi-gear planetary row power system and a vehicle, and relates to the technical field of vehicles.The multi-gear planetary row power system comprises a driving member, a first planetary row, a second planetary row, a gear shifting mechanism, a brake assembly, a first transmission shaft and a second transmission shaft.The first planetary row has a first input end and at least three first output ends.The second planetary row has a second input end and at least three second output ends.The first input end and the second input end are respectively in transmission connection with the driving member and the gear shifting mechanism.One of the at least three first output ends is in transmission connection with the first transmission shaft, and one of the at least three second output ends is in transmission connection with the second transmission shaft.The gear shifting mechanism is used for being in transmission connection with the remaining first output ends of the at least three first output ends alternatively, and the remaining second output ends of the at least three second output ends are respectively used for being engaged with or separated from the brake assembly.In this way, the structure of the whole power system is more compact, and the occupied space is smaller.

Description

Technical Field

[0001] This invention relates to the field of vehicle technology, and more specifically, to a multi-gear planetary gear system and vehicle. Background Technology

[0002] Currently, the reducers in new energy vehicles are mainly single-speed reducers. However, with the continuous increase in motor speed and the demand for high-efficiency electric drive assemblies, the demand for power systems with two or more speeds will continue to increase.

[0003] In traditional two-speed automotive power systems, the reducer typically uses a combination of a main drive reduction system and an independent differential assembly, which results in a large overall space requirement for the power system, making it difficult or impossible to install. Summary of the Invention

[0004] The problem this invention addresses is: how to reduce the space occupied by a two-speed power system.

[0005] To address the aforementioned problems, this invention provides a multi-gear planetary gear system and vehicle.

[0006] In a first aspect, the present invention provides a multi-gear planetary gearbox power system, including a drive unit, a first planetary gearbox, a second planetary gearbox, a shifting mechanism, a braking assembly, a first drive shaft, and a second drive shaft. The first planetary gearbox has a first input end and at least three first output ends, and the second planetary gearbox has a second input end and at least three second output ends. The first input end and the second input end are respectively drivenly connected to the drive unit and the shifting mechanism. One of the at least three first output ends is drivenly connected to the first drive shaft, and one of the at least three second output ends is drivenly connected to the second drive shaft. The shifting mechanism is used to selectively drively connect to the remaining first output ends among the at least three first output ends, and the remaining second output ends among the at least three second output ends are respectively used to engage or disengage from the braking assembly. When one of the remaining first output terminals is connected to the shift mechanism and at least one of the remaining second output terminals is engaged with the braking assembly, the power output by the drive member is transmitted to the first planetary gear set via the first input terminal and then splits into two paths. One path is transmitted to the first drive shaft via the first output terminal of the first planetary gear set connected to the first drive shaft, and the other path is transmitted to the second planetary gear set via the first output terminal connected to the shift mechanism, the shift mechanism, and the second input terminal, and then to the second drive shaft via the second output terminal of the second planetary gear set connected to the second drive shaft.

[0007] Optionally, the first planetary gear set includes a first sun gear, a first multi-planet gear set, a first planet carrier, a first ring gear, and a second ring gear. The first sun gear constitutes the first input end of the first planetary gear set, and the first planet carrier, the first ring gear, and the second ring gear respectively constitute the first output end of the first planetary gear set. The first planet carrier is connected to the first drive shaft for transmission. The first multi-planetary gear includes a first planetary gear and a second planetary gear that are coaxially arranged and connected in transmission. The first planetary gear and the second planetary gear mesh with the first gear ring and the second gear ring, respectively. The first sun gear meshes with either the first planetary gear or the second planetary gear. The shifting mechanism is located between the first gear ring and the second gear ring and is used to selectively connect in transmission with one of the first gear ring and the second gear ring.

[0008] Optionally, the shifting mechanism is a two-way clutch.

[0009] Optionally, the second planetary gear set includes a second sun gear, a third sun gear, a second planet carrier, a second multi-planet gear set, and a third ring gear set. The first sun gear, the second sun gear, and the third sun gear are coaxially arranged. The second planet carrier forms the second input end of the second planetary gear set, and the second sun gear, the third sun gear, and the third ring gear set constitute the second output end of the second planetary gear set. The second multi-planetary gear set includes a third planetary gear, a fourth planetary gear, and a fifth planetary gear. The third planetary gear and the fourth planetary gear are coaxially arranged and connected in a transmission manner. The third planetary gear and the fourth planetary gear are respectively meshed with the second sun gear and the third sun gear. The fifth planetary gear is meshed with one of the third planetary gear and the fourth planetary gear. The third ring gear meshes with the fifth planetary gear and is used to engage or disengage with the braking assembly. One of the second sun gear and the third sun gear is connected in a transmission manner to the second drive shaft. The other of the second sun gear and the third sun gear is used to engage or disengage with the braking assembly.

[0010] Optionally, the braking assembly includes a first brake and a second brake, the first brake being used to brake the third gear ring, and the second brake being used to brake one of the second sun gear and the third sun gear that is not connected to the second drive shaft.

[0011] Optionally, the second sun gear is connected to the second drive shaft, the second brake is used to brake the third sun gear, the fifth planet gear meshes with the fourth planet gear, and the gear mode of the multi-gear planetary gear power system includes a first gear driving mode and a second gear driving mode; When the gear mode is the first gear driving mode, the shifting mechanism is connected to the first gear ring drive, the first brake is closed, the second brake is open, and part of the power output by the drive component is transmitted to the first drive shaft in sequence through the first sun gear, the first multi-planet gear, and the first planet carrier, while the other part is transmitted to the second drive shaft in sequence through the first sun gear, the first multi-planet gear, the first gear ring, the shifting mechanism, the second planet carrier, the fifth planet gear, the fourth planet gear, the third planet gear, and the second sun gear. When the gear mode is the second gear driving mode, the shifting mechanism is connected to the second ring gear, the first brake is disengaged, the second brake is closed, and part of the power output by the drive component is transmitted to the first drive shaft in sequence through the first sun gear, the first multi-planetary gear, and the first planetary carrier, while the other part is transmitted to the second drive shaft in sequence through the first sun gear, the first multi-planetary gear, the second ring gear, the shifting mechanism, the second planetary carrier, the fourth planetary gear, the third planetary gear, and the second sun gear.

[0012] Optionally, in the first gear driving mode, ,and ; in, i1 is the gear ratio of the multi-gear planetary gear system in the first gear driving mode, i3 is the gear ratio of the first ring gear to the first sun gear, and i3 is the gear ratio of the third ring gear to the second sun gear. In the second-gear driving mode, ,and ; in, i1 represents the transmission ratio of the multi-gear planetary gear system in the second gear driving mode, i2 represents the gear ratio between the second ring gear and the first sun gear, and i4 represents the gear ratio between the third sun gear and the second sun gear.

[0013] Optionally, the outer diameter of the third planetary gear is larger than the outer diameter of the fourth planetary gear, and the fifth planetary gear meshes with the fourth planetary gear.

[0014] Optionally, the drive unit includes either a motor or an engine.

[0015] Secondly, the present invention provides a vehicle including the multi-gear planetary power system as described above.

[0016] The beneficial effects of the multi-gear planetary gearbox power system of the present invention are as follows: By connecting the first input end of the first planetary gearbox to the drive member, the power output by the drive member can be transmitted to the first planetary gearbox; by connecting one of the at least three first output ends of the first planetary gearbox to the first drive shaft, selectively connecting the shift mechanism to the remaining first output ends of the at least three first output ends, connecting the shift mechanism to the second input end of the second planetary gearbox, connecting one of the at least three second output ends of the second planetary gearbox to the second drive shaft, and engaging one of the remaining second output ends of the at least three second output ends of the second planetary gearbox with the braking assembly, a portion of the power output by the drive member is transmitted to the first drive shaft via the first planetary gearbox, and then... The power is delivered to, for example, the left drive wheel connected to the first drive shaft. Another portion is transmitted via the first planetary gear set, the shift mechanism, and the second planetary gear set to the second drive shaft, and then to, for example, the right drive wheel connected to the second drive shaft. This allows the power output from the drive components to be split via a compound planetary gear set structure composed of the first and second planetary gear sets, driving the left and right drive wheels to rotate synchronously. Simultaneously, the compound planetary gear set structure also enables the left and right drive wheels to rotate differentially when the vehicle is turning, thus achieving an integrated design of main reduction transmission and differential function. Compared to related technologies that use a main drive reduction system and an independent differential assembly, this eliminates the need to develop a dedicated differential assembly, making the entire system more compact, occupying less space, and reducing production costs. Furthermore, the multi-gear planetary gear set power system allows the shift mechanism to connect the input end of the second planetary gear set to different output ends of the first planetary gear set to meet different operating conditions. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the multi-gear planetary gear system in an embodiment of the present invention; Figure 2 This is a schematic diagram of the multi-gear planetary gear transmission system in first gear driving mode in an embodiment of the present invention; Figure 3 This is a schematic diagram of the principle of the multi-gear planetary gear system in second gear driving mode in an embodiment of the present invention.

[0018] Explanation of reference numerals in the attached figures: 1. Drive unit; 2. First planetary gear set; 21. First sun gear; 22. First multi-planetary gear set; 221. First planetary gear; 222. Second planetary gear; 23. First planetary carrier; 24. First ring gear; 25. Second ring gear; 3. Second planetary gear set; 31. Second sun gear; 32. Third sun gear; 33. Second planetary carrier; 34. Second multi-planetary gear set; 341. Third planetary gear; 342. Fourth planetary gear; 343. Fifth planetary gear; 35. Third ring gear; 4. Shifting mechanism; 5. Braking assembly; 51. First brake; 52. Second brake; 6. First drive shaft; 7. Second drive shaft; 800. Left drive wheel; 900. Right drive wheel. Detailed Implementation

[0019] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Although some embodiments of the present invention are shown in the drawings, it should be understood that the present invention can be implemented in various forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided to provide a more thorough and complete understanding of the present invention. It should be understood that the accompanying drawings and embodiments of the present invention are for illustrative purposes only and are not intended to limit the scope of protection of the present invention.

[0020] The term "comprising" and its variations as used herein are open-ended, meaning "including but not limited to"; the term "based on" means "at least partially based on"; the term "one embodiment" means "at least one embodiment"; the term "another embodiment" means "at least one additional embodiment"; the term "some embodiments" means "at least some embodiments"; and the term "optionally" means "optional embodiments". Definitions of other terms will be given in the following description. It should be noted that the concepts of "first," "second," etc., mentioned in this invention are used only to distinguish different devices, modules, or units, and are not intended to limit the order of functions performed by these devices, modules, or units or their interdependencies.

[0021] It should be noted that the terms "a" and "a plurality of" used in this invention are illustrative rather than restrictive. Those skilled in the art should understand that, unless otherwise expressly indicated in the context, they should be understood as "one or more".

[0022] In related technologies, the reducers in new energy vehicle models mainly use single-speed reducers. However, with the continuous increase in motor speed and the demand for high-efficiency electric drive assemblies, the demand for two-speed or multi-speed reducer power systems will also continue to increase. However, in traditional automotive two-speed power systems, the reducer usually adopts a combination structure of main drive reduction system + independent differential assembly, which makes the overall space occupied by the power system large, easily leading to layout difficulties or even the inability to install it.

[0023] To address the problems existing in the aforementioned related technologies, the present invention provides a multi-gear planetary gear system and vehicle.

[0024] Combination Figure 1 As shown in the figure, an embodiment of the present invention provides a multi-gear planetary gear power system, including a drive member 1, a first planetary gear 2, a second planetary gear 3, a shifting mechanism 4, a braking assembly 5, a first drive shaft 6, and a second drive shaft 7. The first planetary gear 2 has a first input end and at least three first output ends, and the second planetary gear 3 has a second input end and at least three second output ends. The first input end and the second input end are respectively drivenly connected to the drive member 1 and the shifting mechanism 4. One of the at least three first output ends is drivenly connected to the first drive shaft 6, and one of the at least three second output ends is drivenly connected to the second drive shaft 7. The shifting mechanism 4 is used to selectively drively connect to the remaining first output ends among the at least three first output ends, and the remaining second output ends among the at least three second output ends are respectively used to engage or disengage from the braking assembly 5. When one of the remaining first output terminals is connected to the shift mechanism 4 and at least one of the remaining second output terminals is engaged with the braking assembly 5, the power output by the drive unit 1 is transmitted to the first planetary gear set 2 via the first input terminal and then splits into two paths. One path is transmitted to the first drive shaft 6 via the first output terminal of the first planetary gear set 2 connected to the first drive shaft 6, and the other path is transmitted to the second planetary gear set 3 via the first output terminal connected to the shift mechanism 4, the shift mechanism 4, and the second input terminal in sequence, and then to the second drive shaft 7 via the second output terminal of the second planetary gear set 3 connected to the second drive shaft 7.

[0025] Specifically, the driving component 1 can be a motor, in which case the first input end of the first planetary gear set 2 is connected to the motor shaft. Alternatively, the driving component 1 can be an engine, in which case the first input end of the first planetary gear set 2 is connected to the crankshaft of the engine. Both the first planetary gear set 2 and the second planetary gear set 3 have one input end and at least three output ends, and the number of output ends of the first planetary gear set 2 and the second planetary gear set 3 can be the same. When both the first planetary gear set 2 and the second planetary gear set 3 have three output ends, the shifting mechanism 4 is selectively connected to two output ends of the first planetary gear set 2. That is, the shifting mechanism 4 can be a component capable of switching between two gears, such as a two-way clutch. In this case, the power system has two different gears, enabling two-speed drive. When both the first planetary gear set 2 and the second planetary gear set 3 have four output ends, the shifting mechanism 4 is selectively connected to three output ends of the first planetary gear set 2. That is, the shifting mechanism 4 can be a component capable of switching between three gears. In this case, the power system has three different gears, enabling three-speed drive. One end of the first drive shaft 6 is connected to one of the multiple output ends of the first planetary gear set 2, and one end of the second drive shaft 7 is connected to one of the multiple output ends of the second planetary gear set 3. The other ends of the first drive shaft 6 and the second drive shaft 7 are respectively connected to, for example, the left drive wheel 800 and the right drive wheel 900 of the vehicle to transmit power to the left drive wheel 800 and the right drive wheel 900 to drive the vehicle. A braking assembly 5 is disposed at the output end of the second planetary gear set 3. This can be achieved by engaging or disengaging the multiple output ends of the second planetary gear set 3 (excluding those connected to the second drive shaft 7) through a switchable braking assembly 5, or by disengaging a brake at each of the multiple output ends of the second planetary gear set 3 (excluding those connected to the second drive shaft 7) to constrain certain components of the second planetary gear set 3, allowing the first planetary gear set 2 and the second planetary gear set 3 to transmit power to the first drive shaft 6 and the second drive shaft 7 respectively. Furthermore, when the braking assembly 5 is disengaged from all multiple output ends of the second planetary gear set 3 (excluding those connected to the second drive shaft 7), a neutral function is achieved.

[0026] In this embodiment, the power output by the drive member 1 can be transmitted to the first planetary gear set 2 by connecting the first input terminal of the first planetary gear set 2 to the drive member 1. By connecting one of the at least three first output terminals of the first planetary gear set 2 to the first drive shaft 6, selectively connecting the shift mechanism 4 to the remaining first output terminals of the at least three first output terminals, connecting the shift mechanism 4 to the second input terminal of the second planetary gear set 3, connecting one of the at least three second output terminals of the second planetary gear set 3 to the second drive shaft 7, and engaging one of the remaining second output terminals of the at least three second output terminals of the second planetary gear set 3 with the braking assembly 5, a portion of the power output by the drive member 1 is transmitted to the first drive shaft 6 via the first planetary gear set 2, and then to a device connected to the first drive shaft 6, for example... The left drive wheel 800, and another portion of the power is transmitted to the second drive shaft 7 via the first planetary gear set 2, the shift mechanism 4, and the second planetary gear set 3. This power is then transmitted to, for example, the right drive wheel 900 connected to the second drive shaft 7. This allows the power output from the drive unit 1 to be split via the composite planetary gear set structure formed by the first planetary gear set 2 and the second planetary gear set 3, driving the left drive wheel 800 and the right drive wheel 900 to rotate synchronously. Simultaneously, the composite planetary gear set structure also enables the left drive wheel 800 and the right drive wheel 900 to rotate differentially when the vehicle is turning. This achieves an integrated design of main reduction transmission and differential function. Compared to related technologies that use a main drive reduction system and an independent differential assembly, this eliminates the need to develop a dedicated differential assembly, making the entire system more compact, occupying less space, and reducing production costs. Furthermore, the multi-gear planetary gear system can utilize the shift mechanism 4 to connect the input end of the second planetary gear set 3 to different output ends of the first planetary gear set 2 to meet different operating conditions.

[0027] In other embodiments, the second planetary gear set 3 can be controlled by adding an active control element, such as adding a drive element 1, so that the first planetary gear set 2 and the second planetary gear set 3 can be controlled by the two drive elements 1 respectively, thereby achieving the need for active differential or intelligent drive control.

[0028] Optionally, the drive unit 1 includes either a motor or an engine. When the drive unit 1 is a motor, the first input end (i.e., the first sun gear 21) of the first planetary gear set 2 is connected to the motor shaft to transmit the power of the motor to the first planetary gear set 2. In this case, the multi-gear planetary gear set power system is suitable for electric vehicles. When the drive unit 1 is an engine, the first input end (i.e., the first sun gear 21) of the first planetary gear set 2 is connected to the crankshaft of the engine to transmit the power output of the engine to the first planetary gear set 2. In this case, the multi-gear planetary gear set power system is suitable for gasoline vehicles. This expands the applicability of the multi-gear planetary gear set power system.

[0029] Optionally, combined Figure 1 As shown, the first planetary gear set 2 includes a first sun gear 21, a first multi-planet gear set 22, a first planet carrier 23, a first gear ring 24, and a second gear ring 25. The first sun gear 21 constitutes the first input end of the first planetary gear set 2, and the first planet carrier 23, the first gear ring 24, and the second gear ring 25 respectively constitute the first output end of the first planetary gear set 2. The first planet carrier 23 is connected to the first drive shaft 6 for transmission. The first multi-planetary gear 22 includes a first planetary gear 221 and a second planetary gear 222 coaxially arranged and connected in transmission. The first planetary gear 221 and the second planetary gear 222 mesh with the first gear ring 24 and the second gear ring 25 respectively. The first sun gear 21 meshes with either the first planetary gear 221 or the second planetary gear 222. The shifting mechanism 4 is located between the first gear ring 24 and the second gear ring 25 and is used to selectively connect in transmission with one of the first gear ring 24 and the second gear ring 25.

[0030] Specifically, the first planetary gear set 2 has a first input end, namely the first sun gear 21, and three first output ends, namely the first planet carrier 23, the first ring gear 24, and the second ring gear 25. Furthermore, the first planet carrier 23 and the first drive shaft 6 can be connected via a spline structure. Compared to using the first planet carrier 23 as the input end of the first planetary gear set 2 and the first sun gear 21 as the output end connected to the first drive shaft 6, this simplifies the structure of the first planet carrier 23 and even the first planetary gear set 2, making the structure of the first planetary gear set 2 more compact and thus reducing the overall space occupied by the power system. The first sun gear 21 and the drive component 1 can be connected as a single unit or via a spline structure. The shifting mechanism 4 is located between the first ring gear 24 and the second ring gear 25 and is used to selectively connect with one of the first ring gear 24 and the second ring gear 25, enabling the multi-gear planetary gear set power system to achieve two-gear drive. In other words, the multi-gear planetary gear set power system in this embodiment is a two-gear planetary gear set power system.

[0031] More specifically, there are typically multiple first multi-planetary gears 22, which are spaced apart circumferentially on the first planetary carrier 23. Each first multi-planetary gear 22 includes a first planetary gear 221 and a second planetary gear 222 coaxially arranged and drivenly connected, i.e., the first multi-planetary gear 22 has a double planetary gear structure. This expands the speed ratio range of the multi-speed planetary gear transmission system, thereby allowing the multi-speed planetary gear transmission system to be equipped with a high-speed, low-torque lightweight motor, further reducing the overall weight of the multi-speed planetary gear transmission system. The first sun gear 21 can mesh with either the first planetary gear 221 or the second planetary gear 222. For ease of description, the example of the first sun gear 21 meshing with the second planetary gear 222 will be used.

[0032] When the shift mechanism 4 engages with the first ring gear 24, and the first brake 51 of the braking assembly 5 (described later) brakes the third ring gear 35 of the second planetary gear set 3 (described later), the power system is in first gear driving mode. Part of the power output by the drive unit 1 is transmitted sequentially through the first sun gear 21, the first multi-planetary gear set 22, and the first planetary carrier 23 to the first drive shaft 6, and another part is transmitted through the first sun gear 21, the first multi-planetary gear set 22, the first ring gear 24, and the shift mechanism 4 to the second planetary gear set 3, and then to the second drive shaft 7, thus achieving first gear drive. At this time, the first sun gear 21, the first multi-planet gear 22, the first planet carrier 23, and the first ring gear 24 constitute the NW planetary gear set, that is, the planetary gear set of sun gear-double planet gear-ring gear. In the NW planetary gear set, N represents internal meshing, that is, the meshing between the planet gear and the ring gear, and W represents external meshing, that is, the meshing between the sun gear and the planet gear. Moreover, the first sun gear 21 and the first planet gear 221 in the first multi-planet gear set 22 constitute the first stage gear pair, while the second planet gear 222 and the second ring gear 25 in the first multi-planet gear set 22 constitute the second stage gear pair.

[0033] When the shift mechanism 4 engages with the second ring gear 25, and the second brake 52 (described later) brakes the third sun gear 32 (described later) of the second planetary gear set 3, the power system is in second gear driving mode. Part of the power output from the drive unit 1 is transmitted sequentially through the first sun gear 21, the second planet gear 222, and the first planet carrier 23 to the first drive shaft 6. The other part is transmitted through the first sun gear 21, the second planet gear 222, the second ring gear 25, and the shift mechanism 4 to the second planetary gear set 3, and then to the second drive shaft 7, ensuring that the first drive shaft 6 and the second drive shaft 7 rotate at the same speed, thus achieving second gear drive. At this time, the first sun gear 21, the second planet gear 222, the first planet carrier 23, and the second ring gear 25 constitute an NGW planetary gear set, i.e., a conventional planetary gear set such as sun gear-single set planet gear-ring gear. In the NGW planetary gear set, N indicates internal meshing, G indicates common planet gears (planet gears that mesh with both the sun gear and the ring gear), and W indicates external meshing.

[0034] Furthermore, combined Figure 1 As shown, the outer diameter of the second planetary gear 222 is larger than that of the first planetary gear 221, and the first sun gear 21 meshes with the second planetary gear 222. Compared with meshing the first sun gear 21 with the first planetary gear 221 with a smaller outer diameter, this reduces the radial dimension of the first sun gear 21, making the structure of the first planetary gear set 2 more compact and easier to arrange.

[0035] Optionally, combined Figure 1As shown, the second planetary gear set 3 includes a second sun gear 31, a third sun gear 32, a second planet carrier 33, a second multi-planetary gear set 34, and a third ring gear 35. The first sun gear 21, the second sun gear 31, and the third sun gear 32 are coaxially arranged. The second planet carrier 33 constitutes the second input end of the second planetary gear set 3, and the second sun gear 31, the third sun gear 32, and the third ring gear 35 constitute the second output end of the second planetary gear set 3. The second multi-planetary gear 34 includes a third planetary gear 341, a fourth planetary gear 342, and a fifth planetary gear 343. The third planetary gear 341 and the fourth planetary gear 342 are coaxially arranged and connected in transmission. The third planetary gear 341 and the fourth planetary gear 342 are respectively meshed with the second sun gear 31 and the third sun gear 32. The fifth planetary gear 343 is meshed with one of the third planetary gear 341 and the fourth planetary gear 342. The third gear ring 35 is meshed with the fifth planetary gear 343 and is used to engage or disengage with the braking assembly 5. One of the second sun gear 31 and the third sun gear 32 is connected in transmission to the second drive shaft 7, and the other of the second sun gear 31 and the third sun gear 32 is used to engage or disengage with the braking assembly 5.

[0036] Specifically, the second planetary gear set 3 has a second input end, namely the second planet carrier 33, and three second output ends, namely the second sun gear 31, the third sun gear 32, and the third ring gear 35. Furthermore, the second sun gear 31 can be connected to the second drive shaft 7 via a spline structure. Compared to using the second sun gear 31 as the input end of the second planetary gear set 3 and the second planet carrier 33 as the output end of the second planetary gear set 3 connected to the second drive shaft 7, this design facilitates the connection of the second planetary gear set 3 to the ring gear of the first planetary gear set 2 via the shift mechanism 4, and also makes the structure of the second planetary gear set 3 more compact, thereby reducing the overall space occupied by the power system. One of the second sun gear 31 and the third sun gear 32 is connected to the second drive shaft 7, and the other of the second sun gear 31 and the third sun gear 32 is used to engage or disengage with the braking assembly 5. Moreover, the braking assembly 5 is also used to brake the third ring gear 35.

[0037] More specifically, there are usually multiple second multi-planetary gears 34. These multiple second multi-planetary gears 34 are arranged at intervals along the circumference of the second planetary carrier 33. Each second multi-planetary gear 34 includes a third planetary gear 341, a fourth planetary gear 342, and a fifth planetary gear 343. The third planetary gear 341 and the corresponding fourth planetary gear 342 are coaxially arranged and connected for transmission. The fifth planetary gear 343 is arranged in a one-to-one correspondence with one of the third planetary gear 341 and the fourth planetary gear 342 and meshes with each other. That is, the second multi-planetary gear 34 is a combination structure of double planetary gears and a single set of planetary gears. This approach, on the one hand, further expands the speed ratio range of the multi-gear planetary gear system, enabling the system to be equipped with a lightweight motor that operates at high speed and low torque, thereby reducing the overall weight of the system. On the other hand, by correspondingly arranging and meshing the fifth planetary gear 343 with one of the third planetary gear 341 or the fourth planetary gear 342, it ensures that the first planetary carrier 23 and the second sun gear 31 rotate in the same direction, thus ensuring that the first drive shaft 6 and the second drive shaft 7 rotate in the same direction. The fifth planetary gear 343 can mesh with either the third planetary gear 341 or the fourth planetary gear 342. For ease of description, this example illustrates the connection between the fifth planetary gear 343 and the fourth planetary gear 342, with the second sun gear 31 and the second drive shaft 7 connected.

[0038] When the shift mechanism 4 engages with the first ring gear 24, and the first brake 51 of the braking assembly 5 (described later) brakes the third ring gear 35 of the second planetary gear set 3, the power system is in first gear driving mode. Part of the power output from the drive unit 1 is transmitted sequentially through the first sun gear 21, the first multi-planetary gear set 22, and the first planet carrier 23 to the first drive shaft 6. Another part is transmitted via the first sun gear 21, the first multi-planetary gear set 22, the first ring gear 24, and the shift mechanism 4 to the second planet carrier 33. Under the action of the stationary third ring gear 35, the power is transmitted to the second multi-planetary gear set 34, and then sequentially through the fifth planet gear 343, the fourth planet gear 342, the third planet gear 341, and the second sun gear 31 to the second drive shaft 7. This achieves power splitting under first gear drive. At this time, the second sun gear 31, the second planet carrier 33, the second multi-planetary gear set 34, and the third ring gear 35 constitute the NGGW planetary gear set.

[0039] When the shift mechanism 4 engages with the second ring gear 25, and the second brake 52 of the braking assembly 5 (described later) brakes the third sun gear 32 of the second planetary gear set 3, the power system is in second gear driving mode. Part of the power output from the drive unit 1 is transmitted sequentially through the first sun gear 21, the second planetary gear 222, and the first planetary carrier 23 to the first drive shaft 6. Another part is transmitted via the first sun gear 21, the second planetary gear 222, the second ring gear 25, and the shift mechanism 4 to the second planetary carrier 33. Under the action of the stationary third sun gear 32, the power is then transmitted to the second multi-planetary gear set 34, and then sequentially through the fourth planetary gear 342, the third planetary gear 341, and the second sun gear 31 to the second drive shaft 7. This achieves power splitting under second gear drive. At this time, the second sun gear 31, the third sun gear 32, the second planetary carrier 33, the third planetary gear 341, and the fourth planetary gear 342 constitute the WW planetary gear set.

[0040] In this way, in first gear driving mode, the power system uses a combination structure of NW planetary gear set + NGGW planetary gear set to achieve deceleration transmission and differential function. In second gear driving mode, the power system uses a combination structure of NGW planetary gear set + WW planetary gear set to achieve deceleration transmission and differential function. By utilizing the combination arrangement of NGW planetary gear set + NW planetary gear set + NGGW planetary gear set + WW planetary gear set, the main deceleration transmission and differential function are integrated into one design. This allows each planetary gear set to bear half of the total output torque, i.e., the load of one tire. It ensures that the intermediate connecting component (i.e., shift mechanism 4) connecting the two planetary gear sets receives equal loads in opposite directions. Moreover, the NW planetary gear set and NGW planetary gear set share some parts, and the NGGW planetary gear set and WW planetary gear set also share some parts, thereby reducing the number of parts in the power system and reducing the space occupied by the power system in the radial and axial directions, so as to facilitate the layout on the vehicle.

[0041] Optionally, combined Figure 1 As shown, the braking assembly 5 includes a first brake 51 and a second brake 52. The first brake 51 is used to brake the third ring gear 35, and the second brake 52 is used to brake one of the second sun gear 31 and the third sun gear 32 that is not connected to the second drive shaft 7. In this way, braking is achieved by setting a brake at each of the two output ends of the second planetary gear 3, which simplifies the structure of the braking assembly 5 and allows for flexible setting of the brake positions according to actual needs.

[0042] Optionally, combined Figure 2 and Figure 3 As shown, the second sun gear 31 is connected to the first drive shaft 6, the second brake 52 is used to brake the third sun gear 32, the fifth planet gear 343 meshes with the fourth planet gear 342, and the gear mode of the multi-gear planetary gear power system includes first gear driving mode and second gear driving mode. When the gear mode is first gear driving mode, the shift mechanism 4 is connected to the first gear ring 24, the first brake 51 is closed, the second brake 52 is open, and part of the power output by the drive component 1 is transmitted to the first drive shaft 6 in sequence through the first sun gear 21, the first multi-planet gear 22 and the first planet carrier 23, and the other part is transmitted to the second drive shaft 7 in sequence through the first sun gear 21, the first multi-planet gear 22, the first gear ring 24, the shift mechanism 4, the second planet carrier 33, the fifth planet gear 343, the fourth planet gear 342, the third planet gear 341 and the second sun gear 31. When the gear mode is second gear driving mode, the shift mechanism 4 is connected to the second ring gear 25, the first brake 51 is disengaged, the second brake 52 is closed, and part of the power output by the drive component 1 is transmitted to the first drive shaft 6 in sequence through the first sun gear 21, the first multi-planetary gear 22 and the first planetary carrier 23, and the other part is transmitted to the second drive shaft 7 in sequence through the first sun gear 21, the first multi-planetary gear 22, the second ring gear 25, the shift mechanism 4, the second planetary carrier 33, the fourth planetary gear 342, the third planetary gear 341 and the second sun gear 31.

[0043] This allows for power distribution at different gears when the multi-gear planetary gear system is used as a second-gear planetary gear system. Furthermore, by configuring the second brake 52 to brake the third sun gear 32, the fixation of the third sun gear 32 provides positioning and support for the power system, thereby improving its structural strength. By meshing the fifth planet gear 343 with the fourth planet gear 342, the radial dimension of the second multi-planetary gear 34 can be reduced, thereby reducing the radial dimension of the second planetary gear set 3 and even the entire power system, resulting in a more compact structure and easier arrangement.

[0044] Optionally, combined Figure 2 and Figure 3 As shown, in first gear driving mode, ,and ; in, For the multi-gear planetary gear power system in first gear driving mode, i1 is the gear ratio between the first ring gear 24 and the first sun gear 21, and i3 is the gear ratio between the third ring gear 35 and the second sun gear 31. In second gear driving mode ,and ; in, i2 is the gear ratio of the multi-gear planetary gear system in second gear driving mode, i4 is the gear ratio of the second ring gear 25 to the first sun gear 21, and i4 is the gear ratio of the third sun gear 32 to the second sun gear 31.

[0045] Specifically, in first gear driving mode, since the first planetary gear set 2 is equivalent to the NW planetary gear set and the second planetary gear set 3 is equivalent to the NGGW planetary gear set, i1 is also the gear ratio of the NW planetary gear set and i3 is also the gear ratio of the NGGW planetary gear set. In second gear driving mode, since the first planetary gear set 2 is equivalent to the NGW planetary gear set and the second planetary gear set 3 is equivalent to the WW planetary gear set, i2 is also the gear ratio of the NGW planetary gear set and i4 is also the gear ratio of the WW planetary gear set.

[0046] In this optional embodiment, it can be based on the formula To calculate the gear ratio of a multi-gear planetary transmission system in first gear driving mode, and according to the formula... This is used to calculate the gear ratio of the multi-gear planetary gearbox powertrain in second gear driving mode. Furthermore, the gear ratio of the first planetary gearbox 2 and the second planetary gearbox 3 in first gear driving mode is set to... The gear ratio of the first planetary gear set 2 and the second planetary gear set 3 in second gear driving mode is set as follows: This ensures that when the vehicle is turning, the upward speed of the first planetary carrier 23 is equal to the downward speed of the second sun gear 31, or the downward speed of the first planetary carrier 23 is equal to the upward speed of the second sun gear 31, so that the multi-gear planetary power system meets the differential speed conditions for vehicle turning.

[0047] Optionally, combined Figure 1 As shown, the shifting mechanism 4 is a two-way clutch. Essentially, a two-way clutch is a sliding sleeve with internal and external teeth. Shifting is achieved by axially moving the sliding sleeve on a shaft via a shift fork mechanism. Furthermore, due to its advantages of simple and compact structure, low cost, high reliability, durability, and ability to transmit large torques, a two-way clutch is particularly suitable for vehicles with high requirements for cost, space, and weight. Therefore, in this optional embodiment, using a two-way clutch as the shifting mechanism 4 to switch between first and second gear simplifies the powertrain structure, making the overall layout of the powertrain more compact, and saving space, weight, and cost, facilitating lightweight vehicle design.

[0048] Optionally, combined Figure 1 As shown, the outer diameter of the third planetary gear 341 is larger than that of the fourth planetary gear 342, and the fifth planetary gear 343 meshes with the fourth planetary gear 342. Compared with meshing the fifth planetary gear 343 with the third planetary gear 341, which has a larger outer diameter, this not only reduces the radial dimension of the second multi-planetary gear 34, but also reduces the radial dimension of the third gear ring 35 that meshes with the fifth planetary gear 343, further making the structure of the second planetary gear set 3 more compact and easier to arrange.

[0049] Furthermore, combined Figure 1As shown, the second sun gear 31 is connected to the second drive shaft 7, and the second brake 52 is used to brake the third sun gear 32. Since the outer diameter of the third planetary gear 341 is larger than that of the fourth planetary gear 342, and the second sun gear 31 and the third sun gear 32 are coaxially arranged, the outer diameter of the third sun gear 32, which meshes with the larger outer diameter third planetary gear 341, is larger than that of the second sun gear 31, which meshes with the smaller outer diameter fourth planetary gear 342. At this time, by connecting the second drive shaft 7 to the smaller outer diameter second sun gear 31 and using the second brake 52 to brake the larger outer diameter third sun gear 32, the output torque of the second planetary gear set 3 can be reduced, and the output speed can be increased. This makes the power system more energy-efficient and can achieve high-speed operation. At the same time, it can also reduce the rotational inertia of the output end of the power system and improve the dynamic response performance of the power system.

[0050] The present invention provides a vehicle including the multi-gear planetary power system described above.

[0051] The beneficial effects of the vehicle in this embodiment are the same as those of the multi-gear planetary gear system described above, and will not be repeated here.

[0052] While the present invention has been disclosed above, its scope of protection is not limited thereto. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention, and all such changes and modifications will fall within the scope of protection of the present invention.

Claims

1. A multi-gear planetary transmission power system, characterized in that, The system includes a drive unit (1), a first planetary gear set (2), a second planetary gear set (3), a shifting mechanism (4), a braking assembly (5), a first drive shaft (6), and a second drive shaft (7). The first planetary gear set (2) has a first input end and at least three first output ends. The second planetary gear set (3) has a second input end and at least three second output ends. The first input end and the second input end are respectively connected to the drive unit (1) and the shifting mechanism (4). One of the at least three first output ends is connected to the first drive shaft (6). One of the at least three second output ends is connected to the second drive shaft (7). The shifting mechanism (4) is used to selectively connect to the remaining first output ends among the at least three first output ends. The remaining second output ends among the at least three second output ends are respectively used to engage or disengage from the braking assembly (5). When one of the remaining first output terminals is connected to the shift mechanism (4) and at least one of the remaining second output terminals is engaged with the brake assembly (5), the power output by the drive member (1) is transmitted to the first planetary gearbox (2) via the first input terminal of the first planetary gearbox (2) and then splits into two paths. One path is transmitted to the first drive shaft (6) via the first output terminal of the first planetary gearbox (2) connected to the first drive shaft (6), and the other path is transmitted to the second planetary gearbox (3) via the first output terminal connected to the shift mechanism (4), the shift mechanism (4), and the second input terminal in sequence, and then transmitted to the second drive shaft (7) via the second output terminal of the second planetary gearbox (3) connected to the second drive shaft (7). The first planetary gear set (2) includes a first sun gear (21), a first multi-planetary gear set (22), a first planet carrier (23), a first gear ring (24), and a second gear ring (25). The first sun gear (21) constitutes the first input end of the first planetary gear set (2). The first planet carrier (23), the first gear ring (24), and the second gear ring (25) respectively constitute the first output end of the first planetary gear set (2). The first planet carrier (23) is connected to the first drive shaft (6) in a transmission connection. The first multi-planetary gear set (22) includes a first planetary gear (221) and a second planetary gear (222) that are coaxially arranged and connected in a transmission connection. The first planetary gear (221) and the second planetary gear (222) mesh with the first gear ring (24) and the second gear ring (25) respectively. The first sun gear (21) meshes with either the first planetary gear (221) or the second planetary gear (222). The shifting mechanism (4) is located between the first gear ring (24) and the second gear ring (25) and is used to selectively drive one of the first gear ring (24) and the second gear ring (25). The second planetary gear set (3) includes a second sun gear (31), a third sun gear (32), a second planet carrier (33), a second multi-link planetary gear set (34), and a third gear ring (222). 35), the first sun gear (21), the second sun gear (31) and the third sun gear (32) are coaxially arranged, the second planet carrier (33) constitutes the second input end of the second planetary gear set (3), and the second sun gear (31), the third sun gear (32) and the third ring gear (35) constitute the second output end of the second planetary gear set (3); the second multi-planetary gear set (34) includes a third planetary gear (341), a fourth planetary gear (342) and a fifth planetary gear (343), the third planetary gear (341) and the fourth planetary gear (342) are coaxially arranged and connected in transmission, the third planetary gear (341) The third planetary gear (341) and the fourth planetary gear (342) are respectively engaged with the second sun gear (31) and the third sun gear (32), the fifth planetary gear (343) is engaged with one of the third planetary gear (341) and the fourth planetary gear (342), the third ring gear (35) is engaged with the fifth planetary gear (343) and is used to engage or disengage with the brake assembly (5), one of the second sun gear (31) and the third sun gear (32) is connected to the second drive shaft (7), and the other of the second sun gear (31) and the third sun gear (32) is used to engage or disengage with the brake assembly (5);The braking assembly (5) includes a first brake (51) and a second brake (52). The first brake (51) is used to brake the third gear ring (35), and the second brake (52) is used to brake one of the second sun gear (31) and the third sun gear (32) that is not connected to the second drive shaft (7). The second sun gear (31) is connected to the second drive shaft (7) for transmission, the second brake (52) is used to brake the third sun gear (32), the fifth planet gear (343) meshes with the fourth planet gear (342), and the gear mode of the multi-gear planetary gear power system includes first gear driving mode and second gear driving mode; When the gear mode is the first gear driving mode, the shifting mechanism (4) is connected to the first gear ring (24) in a transmission connection, the first brake (51) is closed, and the second brake (52) is open; when the gear mode is the second gear driving mode, the shifting mechanism (4) is connected to the second gear ring (25) in a transmission connection, the first brake (51) is open, and the second brake (52) is closed; In the first gear driving mode, ; Wherein, i1 is the ratio of the number of teeth of the first gear ring (24) to the number of teeth of the first sun gear (21), and i3 is the ratio of the number of teeth of the third gear ring (35) to the number of teeth of the second sun gear (31); In the second-gear driving mode, ; Wherein, i2 is the ratio of the number of teeth of the second gear ring (25) to the number of teeth of the first sun gear (21), and i4 is the ratio of the number of teeth of the third sun gear (32) to the number of teeth of the second sun gear (31).

2. The multi-gear planetary power system according to claim 1, characterized in that, The shifting mechanism (4) is a two-way clutch.

3. The multi-gear planetary power system according to claim 1, characterized in that, When the gear mode is the first gear driving mode, part of the power output by the drive unit (1) is transmitted to the first drive shaft (6) in sequence through the first sun gear (21), the first multi-planetary gear (22) and the first planetary carrier (23), and another part is transmitted to the second drive shaft (7) in sequence through the first sun gear (21), the first multi-planetary gear (22), the first gear ring (24), the shifting mechanism (4), the second planetary carrier (33), the fifth planetary gear (343), the fourth planetary gear (342), the third planetary gear (341) and the second sun gear (31). When the gear mode is the second gear driving mode, part of the power output by the drive unit (1) is transmitted to the first drive shaft (6) in sequence through the first sun gear (21), the first multi-planetary gear (22) and the first planetary carrier (23), and another part is transmitted to the second drive shaft (7) in sequence through the first sun gear (21), the first multi-planetary gear (22), the second ring gear (25), the shifting mechanism (4), the second planetary carrier (33), the fourth planetary gear (342), the third planetary gear (341) and the second sun gear (31).

4. The multi-gear planetary power system according to claim 1, characterized in that, In the first gear driving mode, ; in, The transmission ratio of the multi-gear planetary gear system in the first gear driving mode; In the second-gear driving mode, ; in, This refers to the transmission ratio of the multi-gear planetary powertrain system in the second gear driving mode.

5. The multi-gear planetary power system according to claim 1, characterized in that, The outer diameter of the third planetary gear (341) is larger than that of the fourth planetary gear (342), and the fifth planetary gear (343) meshes with the fourth planetary gear (342).

6. The multi-gear planetary power system according to claim 1, characterized in that, The drive unit (1) includes either a motor or an engine.

7. A vehicle, characterized in that, Including the multi-gear planetary power system as described in any one of claims 1-6.

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