Multi-gear planet row power system and vehicle

Abstract

The invention provides a multi-gear planet row power system and a vehicle, and relates to the technical field of vehicles, the multi-gear planet row power system comprises a driving part, a first planet row, a second planet row, a gear shifting mechanism, a braking assembly, a first transmission shaft and a second transmission shaft, the first planet row is provided with a first input end and at least three first output ends, and the second planet row is provided with a second input end and at least three second output ends; the first planet row is provided with a first input end and at least three first output ends, the second planet row is provided with a second input end and at least three second output ends, the first input end and the second input ends are in transmission connection with the driving part and the gear shifting mechanism respectively, 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 selectively in transmission connection with the other first output ends in the at least three first output ends, and the other second output ends in the at least three second output ends are used for being connected with or separated from the braking assembly. Therefore, the whole power system is more compact in structure and smaller in occupied space.

Description

Technical Field

[0001] The present invention relates to the field of vehicle technology, and in particular to a multi-gear planetary gear power system and a vehicle. Background Art

[0002] At present, the reducers of new energy vehicles mainly use single-speed reducers, but with the continuous increase in motor speed and the demand for high-efficiency electric drive assemblies, the demand for two-speed or more reducer power systems will continue to increase.

[0003] In traditional two-speed automotive power systems, the reducer usually adopts a combination structure of a main drive reduction system + an independent differential assembly, which makes the overall space occupied by the power system larger and easily leads to difficulties or impossibility of layout. Summary of the Invention

[0004] The problem solved by the present invention is how to reduce the occupied space of a two-speed power system.

[0005] In order to solve the above problems, the present invention provides a multi-gear planetary gear power system and a vehicle.

[0006] In a first aspect, the present invention provides a multi-gear planetary gear power system, comprising a drive member, a first planetary gear, a second planetary gear, a shifting mechanism, a brake assembly, a first transmission shaft, and a second transmission shaft, wherein the first planetary gear has a first input end and at least three first output ends, the second planetary gear has a second input end and at least three second output ends, the first input end and the second input end are respectively transmission-connected to the drive member and the shifting mechanism, one of the at least three first output ends is transmission-connected to the first transmission shaft, and one of the at least three second output ends is transmission-connected to the second transmission shaft, the shifting mechanism is configured to selectively transmission-connect to the remaining first output ends of the at least three first output ends, and the remaining second output ends of the at least three second output ends are respectively configured to engage or disengage with the brake assembly; When one of the remaining first output ends is transmission-connected to the shift mechanism, and at least one of the remaining second output ends is engaged with the brake assembly, the power output by the driving member is transmitted to the first planetary gear through the first input end of the first planetary gear and then divided into two paths. One path is transmitted to the first transmission shaft through the first output end of the first planetary gear transmission-connected to the first transmission shaft, and the other path is transmitted to the second planetary gear in sequence through the first output end connected to the shift mechanism, the shift mechanism, and the second input end, and then transmitted to the second transmission shaft through the second output end of the second planetary gear transmission-connected to the second transmission shaft.

[0007] Optionally, the first planetary gear comprises a first sun gear, a first multi-linked planetary gear, a first planet carrier, a first ring gear, and a second ring gear, wherein the first sun gear constitutes the first input end of the first planetary gear, the first planet carrier, the first ring gear, and the second ring gear respectively constitute the first output end of the first planetary gear, and the first planet carrier is in driving connection with the first transmission shaft; The first multi-linked planetary gear includes a first planetary gear and a second planetary gear that are coaxially arranged and transmission-connected. The first planetary gear and the second planetary gear are respectively meshed with the first ring gear and the second ring gear. The first sun gear is meshed with the first planetary gear or the second planetary gear. The shift mechanism is located between the first ring gear and the second ring gear, and is used to selectively be transmission-connected to one of the first ring gear and the second ring gear.

[0008] Optionally, the shifting mechanism is a bidirectional clutch.

[0009] Optionally, the second planetary gear comprises a second sun gear, a third sun gear, a second planet carrier, a second multi-linked planetary gear, and a third ring gear, the first sun gear, the second sun gear, and the third sun gear are coaxially arranged, the second planet carrier constitutes the second input end of the second planetary gear, and the second sun gear, the third sun gear, and the third ring gear constitute the second output end of the second planetary gear; The second multi-linked planetary gear 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 transmission-connected. 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 is meshed with the fifth planetary gear and is used to engage or disengage with the brake assembly. One of the second sun gear and the third sun gear is transmission-connected to the second transmission shaft, and the other of the second sun gear and the third sun gear is used to engage or disengage with the brake assembly.

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

[0011] Optionally, the second sun gear is in driving connection with the second transmission shaft, the second brake is used to brake the third sun gear, the fifth planetary gear is meshed with the fourth planetary 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 shift mechanism is in transmission connection with the first ring gear, the first brake is engaged, and the second brake is disengaged. A portion of the power output by the driving member is transmitted to the first transmission shaft via the first sun gear, the first multi-linked planetary gear, and the first planet carrier in sequence, and another portion of the power is transmitted to the second transmission shaft via the first sun gear, the first multi-linked planetary gear, the first ring gear, the shift mechanism, the second planet carrier, the fifth planetary gear, the fourth planetary gear, the third planetary gear, and the second sun gear in sequence. When the gear mode is the second gear driving mode, the shift mechanism is connected to the second ring gear, the first brake is disconnected, and the second brake is closed. A part of the power output by the driving member is transmitted to the first transmission shaft via the first sun gear, the first multi-linked planetary gear and the first planetary carrier in sequence, and the other part is transmitted to the second transmission shaft via the first sun gear, the first multi-linked planetary gear, the second ring gear, the shift mechanism, the second planetary carrier, the fourth planetary gear, the third planetary gear and the second sun gear in sequence.

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

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

[0014] Optionally, the driving member includes one of a motor and a generator.

[0015] In a second aspect, the present invention provides a vehicle comprising the multi-speed planetary gear power system as described above.

[0016] The multi-gear planetary gear power system of the present invention has the following beneficial effects: the first input end of the first planetary gear is connected to the driving member in a transmission manner, so that the power output by the driving member can be transmitted to the first planetary gear; by connecting one of the at least three first output ends of the first planetary gear to the first transmission shaft in a transmission manner, connecting the shift mechanism to the other first output ends of the at least three first output ends in a selective manner, and connecting the shift mechanism to the second input end of the second planetary gear, connecting one of the at least three second output ends of the second planetary gear to the second transmission shaft, and engaging one of the other second output ends of the at least three second output ends of the second planetary gear with the brake assembly, so that a part of the power output by the driving member is transmitted to the first transmission shaft through the first planetary gear, and then transmitted to the first planetary gear. The power output of the drive element is transmitted to, for example, the left drive wheel connected to the first transmission shaft, while the remaining power is transmitted to the second transmission shaft via the first planetary gear, the shift mechanism, and the second planetary gear, and then to, for example, the right drive wheel connected to the second transmission shaft. This allows the power output of the drive element to be divided via the composite planetary gear structure formed by the first and second planetary gears to drive the left and right drive wheels to rotate synchronously. Furthermore, the composite planetary gear structure formed by the first and second planetary gears also enables the left and right drive wheels to achieve differential rotation when the vehicle turns, thereby achieving an integrated design of the main reduction transmission and differential functions. Compared with the related art that uses a main transmission reduction system and an independent differential assembly structure, this eliminates the need for a dedicated differential assembly, making the entire system more compact, occupying less space, and having lower production costs. Furthermore, a multi-speed planetary gear power system can utilize the shift mechanism to connect the input end of the second planetary gear with different output ends of the first planetary gear to achieve shifting requirements to meet different operating conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 A schematic diagram of the principle of a multi-gear planetary gear power system according to an embodiment of the present invention; Figure 2 Schematic diagram of the principle of a multi-gear planetary gear power system in a first gear driving mode according to an embodiment of the present invention; Figure 3 Schematic diagram of the principle of a multi-gear planetary gear power system in a second gear driving mode according to an embodiment of the present invention.

[0018] Description of reference numerals: 1. Driving member; 2. First planetary row; 21. First sun gear; 22. First multi-linked planetary gear; 221. First planetary gear; 222. Second planetary gear; 23. First planetary carrier; 24. First ring gear; 25. Second ring gear; 3. Second planetary row; 31. Second sun gear; 32. Third sun gear; 33. Second planetary carrier; 34. Second multi-linked planetary gear; 341. Third planetary gear; 342. Fourth planetary gear; 343. Fifth planetary gear; 35. Third ring gear; 4. Shift mechanism; 5. Brake assembly; 51. First brake; 52. Second brake; 6. First transmission shaft; 7. Second transmission shaft; 800. Left drive wheel; 900. Right drive wheel. DETAILED DESCRIPTION

[0019] To make the above-mentioned objects, features, and advantages of the present invention more clearly understood, specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. Although certain embodiments of the present invention are shown in the accompanying drawings, it should be understood that the present invention can be implemented in various forms and should not be construed as being limited to the embodiments described herein. Instead, these embodiments are provided to provide a more thorough and complete understanding of the present invention. It should be understood that the 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 "including" and its variations used in this document are open inclusions, that is, "including but not limited to"; the term "based on" means "based at least in part on"; the term "one embodiment" means "at least one embodiment"; the term "another embodiment" means "at least one other embodiment"; the term "some embodiments" means "at least some embodiments"; the term "optionally" means "optional embodiments". The relevant definitions of other terms will be given in the following description. It should be noted that the concepts of "first", "second", etc. mentioned in the present invention are only used to distinguish different devices, modules or units, and are not used to limit the order or interdependence of the functions performed by these devices, modules or units.

[0021] It should be noted that the modifications of "one" and "multiple" mentioned in the present invention are illustrative rather than restrictive. Those skilled in the art should understand that unless otherwise clearly indicated in the context, it should be understood as "one or more".

[0022] In related technologies, reducers for new energy vehicles primarily utilize single-speed reducers. However, with the continuous increase in motor speed and the demand for efficient electric drive assemblies, the demand for two-speed or multi-speed reducer power systems will continue to increase. However, in traditional automotive two-speed power systems, the reducer typically utilizes a combination of a main drive reduction system and an independent differential assembly, resulting in a larger overall power system footprint and making layout difficult or impossible.

[0023] In response to the problems existing in the above-mentioned related technologies, the present invention provides a multi-gear planetary gear power system and a vehicle.

[0024] Combine Figure 1 As shown, an embodiment of the present invention provides a multi-gear planetary gear power system, including a driving member 1, a first planetary gear 2, a second planetary gear 3, a shifting mechanism 4, a brake assembly 5, a first transmission shaft 6, and a second transmission 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 transmission-connected to the driving member 1 and the shifting mechanism 4. One of the at least three first output ends is transmission-connected to the first transmission shaft 6, and one of the at least three second output ends is transmission-connected to the second transmission shaft 7. The shifting mechanism 4 is configured to selectively transmission-connect to the remaining first output ends of the at least three first output ends, and the remaining second output ends of the at least three second output ends are respectively configured to engage with or disengage from the brake assembly 5. When one of the remaining first output ends is transmission-connected to the shift mechanism 4, and at least one of the remaining second output ends is engaged with the brake assembly 5, the power output by the driving member 1 is transmitted to the first planetary gear row 2 via the first input end of the first planetary gear row 2 and then divided into two paths. One path is transmitted to the first transmission shaft 6 via the first output end of the first planetary gear row 2 transmission-connected to the first transmission shaft 6, and the other path is transmitted to the second planetary gear row 3 via the first output end connected to the shift mechanism 4, the shift mechanism 4, and the second input end in sequence, and is then transmitted to the second transmission shaft 7 via the second output end of the second planetary gear row 3 connection to the second transmission shaft 7.

[0025] Specifically, the driving member 1 can be a motor, in which case the first input end of the first planetary gear 2 is connected to the motor shaft of the motor. The driving member 1 can also be an engine, in which case the first input end of the first planetary gear 2 is connected to the crankshaft of the engine. The first planetary gear 2 and the second planetary gear 3 each have one input end and at least three output ends, and the number of output ends of the first planetary gear 2 and the second planetary gear 3 can be the same. When the first planetary gear 2 and the second planetary gear 3 each have three output ends, the shift mechanism 4 is selectively connected to the two output ends of the first planetary gear 2, that is, the shift 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 the first planetary gear 2 and the second planetary gear 3 each have four output ends, the shift mechanism 4 is selectively connected to the three output ends of the first planetary gear 2, that is, the shift 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 transmission shaft 6 is drivingly connected to one of the multiple output ends of the first planetary gear set 2, and one end of the second transmission shaft 7 is drivingly connected to one of the multiple output ends of the second planetary gear set 3. The other ends of the first transmission shaft 6 and the second transmission shaft 7 are respectively drivingly 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, thereby driving the vehicle. A brake assembly 5 is provided at the output end of the second planetary gear set 3. The multiple output ends of the second planetary gear set 3, excluding those connected to the second transmission shaft 7, can be engaged or disengaged by a single switchable brake assembly 5. Alternatively, a brake can be provided at each of the multiple output ends of the second planetary gear set 3, excluding those connected to the second transmission shaft 7, to engage or disengage the brakes. This restraint of the brakes constrains some 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 transmission shaft 6 and the second transmission shaft 7, respectively. Furthermore, when the brake assembly 5 is disengaged from all the output ends of the second planetary gear set 3, excluding those connected to the second transmission shaft 7, a neutral gear function can be achieved.

[0026] In this embodiment, the first input end of the first planetary gear 2 can be transmission-connected to the driving member 1 so that the power output by the driving member 1 can be transmitted to the first planetary gear 2; by transmission-connecting one of the at least three first output ends of the first planetary gear 2 to the first transmission shaft 6, transmission-connecting the shift mechanism 4 to the other first output ends of the at least three first output ends in a selective manner, and transmission-connecting the shift mechanism 4 to the second input end of the second planetary gear 3, transmission-connecting one of the at least three second output ends of the second planetary gear 3 to the second transmission shaft 7, and engaging one of the other second output ends of the at least three second output ends of the second planetary gear 3 with the brake assembly 5, so that a portion of the power output by the driving member 1 is transmitted to the first transmission shaft 6 through the first planetary gear 2, and then transmitted to, for example, the first transmission shaft 6 connected to the first transmission shaft 6. The left drive wheel 800 is driven by a second portion of the power, while the remaining portion is transmitted to the second transmission shaft 7 via the first planetary gear set 2, the shift mechanism 4, and the second planetary gear set 3, and then to, for example, the right drive wheel 900 connected to the second transmission shaft 7. This allows the power output by the drive element 1 to be divided through 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. Furthermore, the composite planetary gear set structure formed by the first planetary gear set 2 and the second planetary gear set 3 also enables differential rotation of the left drive wheel 800 and the right drive wheel 900 when the vehicle turns, thereby achieving an integrated design of the main reduction transmission and differential functions. Compared with the related art that uses a main drive reduction system and an independent differential assembly structure, this eliminates the need for a dedicated differential assembly, making the overall system more compact, occupying less space, and having lower production costs. Furthermore, a multi-speed planetary gear set power system can utilize the shift mechanism 4 to connect the input end of the second planetary gear set 3 with different output ends of the first planetary gear set 2 to achieve gear shifting requirements to meet different operating conditions.

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

[0028] Optionally, the driving element 1 includes either a motor or an engine. When the driving element 1 is a motor, the first input end of the first planetary gear 2 (i.e., the first sun gear 21) is connected to the motor shaft of the motor to transmit the motor's power to the first planetary gear 2. In this case, the multi-speed planetary gear powertrain is suitable for electric vehicles. When the driving element 1 is an engine, the first input end of the first planetary gear 2 (i.e., the first sun gear 21) is connected to the engine's crankshaft to transmit the engine's output power to the first planetary gear 2. In this case, the multi-speed planetary gear powertrain is suitable for fuel-powered vehicles. This can expand the applicability of the multi-speed planetary gear powertrain.

[0029] Optionally, combined Figure 1 As shown, the first planetary gear 2 includes a first sun gear 21, a first multi-linked planetary gear 22, a first planetary carrier 23, a first ring gear 24, and a second ring gear 25. The first sun gear 21 constitutes a first input end of the first planetary gear 2, and the first planetary carrier 23, the first ring gear 24, and the second ring gear 25 respectively constitute a first output end of the first planetary gear 2, and the first planetary carrier 23 is in driving connection with the first transmission shaft 6. The first multi-connected planetary gear 22 includes a first planetary gear 221 and a second planetary gear 222 which are coaxially arranged and transmission-connected. The first planetary gear 221 and the second planetary gear 222 are respectively meshed with the first ring gear 24 and the second ring gear 25. The first sun gear 21 is meshed with the first planetary gear 221 or the second planetary gear 222. The shift mechanism 4 is located between the first ring gear 24 and the second ring gear 25 and is used to selectively be transmission-connected with one of the first ring gear 24 and the second ring gear 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 planetary carrier 23, the first ring gear 24, and the second ring gear 25. Furthermore, a spline structure can be used to achieve a transmission connection between the first planetary carrier 23 and the first transmission shaft 6. Compared to a system in which the first planetary carrier 23 serves as the input end of the first planetary gear set 2 and the first sun gear 21 serves as the output end connected to the first transmission shaft 6, this simplifies the structure of the first planetary carrier 23 and, consequently, 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 transmission connection between the first sun gear 21 and the drive element 1 can be achieved through an integral connection or a spline structure. The shift mechanism 4 is disposed between the first ring gear 24 and the second ring gear 25 and is configured to selectively connect to one of the first ring gear 24 and the second ring gear 25, enabling the multi-speed planetary gear set power system to achieve two-speed drive. In other words, the multi-speed planetary gear set power system in this embodiment is a two-speed planetary gear set power system.

[0031] More specifically, a plurality of first multi-linked planetary gears 22 are typically provided, spaced apart circumferentially on the first planet carrier 23. Each first multi-linked planetary gear 22 comprises a first planetary gear 221 and a second planetary gear 222 coaxially disposed and drivingly connected thereto, i.e., the first multi-linked planetary gears 22 form a double-linked planetary gear structure. This expands the speed ratio range of the multi-speed planetary gear system, thereby allowing the multi-speed planetary gear system to be equipped with a lightweight motor with high speed and low torque, further reducing the overall weight of the multi-speed planetary gear 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 meshing of the first sun gear 21 and the second planetary gear 222 is used as an example.

[0032] When the shift mechanism 4 is engaged with the first ring gear 24 and the first brake 51 (described later) of the brake assembly 5 brakes the third ring gear 35 (described later) of the second planetary gear row 3, the power system is in the first gear driving mode. Part of the power output by the driving member 1 is transmitted to the first transmission shaft 6 via the first sun gear 21, the first multi-linked planetary gear 22, and the first planet carrier 23 in sequence, and the other part is transmitted to the second planetary gear row 3 via the first sun gear 21, the first multi-linked planetary gear 22, the first ring gear 24, and the shift mechanism 4, and then transmitted to the second transmission shaft 7, thereby realizing first gear drive. At this time, the first sun gear 21, the first multi-linked planetary gear 22, the first planet carrier 23 and the first ring gear 24 constitute an NW planetary row, that is, a planetary row of sun gear-double-linked planetary gear-ring gear, wherein N in the NW planetary row represents internal meshing, that is, the meshing between the planetary gear and the ring gear, and W represents external meshing, that is, the meshing between the sun gear and the planetary gear. Moreover, the first sun gear 21 and the first planetary gear 221 in the first multi-linked planetary gear 22 constitute a first-stage gear pair, and the second planetary gear 222 in the first multi-linked planetary gear 22 and the second ring gear 25 constitute a second-stage gear pair.

[0033] When the shift mechanism 4 engages 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 enters second gear driving mode. A portion of the power output from the driving element 1 is transmitted sequentially through the first sun gear 21, the second planetary gears 222, and the first planet carrier 23 to the first transmission shaft 6. The remaining portion is transmitted through the first sun gear 21, the second planetary gears 222, the second ring gear 25, and the shift mechanism 4 to the second planetary gear set 3, and then to the second transmission shaft 7. This ensures that the rotational speeds of the first and second transmission shafts 6 and 7 are the same, thus achieving second gear drive. At this point, the first sun gear 21, the second planetary gears 222, the first planet carrier 23, and the second ring gear 25 form an NGW planetary set, i.e., a conventional planetary set consisting of a sun gear, a single set of planetary gears, and a ring gear. In the NGW planetary set, N represents internal meshing, G represents a shared planetary gear (i.e., a planetary gear meshing with both the sun gear and the ring gear), and W represents external meshing.

[0034] Further, combined with Figure 1 As shown, the outer diameter of the second planetary gear 222 is larger than the outer diameter 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 having a smaller outer diameter, this can reduce the radial size of the first sun gear 21, making the structure of the first planetary gear 2 more compact and easier to arrange.

[0035] Optionally, combined Figure 1As shown, the second planetary gear 3 includes a second sun gear 31, a third sun gear 32, a second planet carrier 33, a second multi-linked planetary gear 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 a second input end of the second planetary gear 3, and the second sun gear 31, the third sun gear 32 and the third ring gear 35 constitute a second output end of the second planetary gear 3. The second multi-linked 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 transmission-connected. 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 ring gear 35 is meshed 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 transmission-connected to the second transmission shaft 7. 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.

[0036] Specifically, the second planetary gear set 3 has a second input end, namely the second planetary 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, a spline structure can be used to achieve a transmission connection between the second sun gear 31 and the second transmission shaft 7. Compared to using the second sun gear 31 as the input end of the second planetary gear set 3 and the second planetary carrier 33 as the output end of the second planetary gear set 3 connected to the second transmission shaft 7, this not only facilitates connecting the second planetary gear set 3 to the ring gear of the first planetary gear set 2 via the shift mechanism 4, but 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 transmission-connected to the second transmission shaft 7, while the other of the second sun gear 31 and the third sun gear 32 is configured to engage or disengage with the brake assembly 5. Furthermore, the brake assembly 5 is also configured to brake the third ring gear 35.

[0037] More specifically, a plurality of second multi-linked planetary gears 34 are typically provided, and the plurality of second multi-linked planetary gears 34 are arranged on the second planetary carrier 33 at intervals along the circumference of the second planetary carrier 33. Each second multi-linked 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 transmission-connected. 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-linked planetary gear 34 is a combination structure of a double-linked planetary gear and a single set of planetary gears. This, on the one hand, further expands the speed ratio range of the multi-speed planetary gear set power system, allowing the multi-speed planetary gear set power system to be equipped with a high-speed, low-torque, lightweight motor, thereby reducing the overall weight of the multi-speed planetary gear set power system. On the other hand, by providing a one-to-one correspondence between the fifth planetary gear 343 and one of the third planetary gear 341 and the fourth planetary gear 342 and engaging them with each other, the first planet carrier 23 and the second sun gear 31 are ensured to rotate in the same direction, thereby ensuring that the first transmission shaft 6 and the second transmission shaft 7 rotate in the same direction. The fifth planetary gear 343 can mesh with the third planetary gear 341 or the fourth planetary gear 342. For ease of description, the following example is used to illustrate the meshing of the fifth planetary gear 343 with the fourth planetary gear 342 and the transmission connection between the second sun gear 31 and the second transmission shaft 7.

[0038] When the shift mechanism 4 engages the first ring gear 24 and the first brake 51 of the brake assembly 5 (described later) brakes the third ring gear 35 of the second planetary gear set 3, the power system enters first gear driving mode. A portion of the power output from the driving element 1 is transmitted sequentially through the first sun gear 21, the first multi-linked planetary gears 22, and the first planet carrier 23 to the first transmission shaft 6. The remaining portion is transmitted through the first sun gear 21, the first multi-linked planetary gears 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-linked planetary gears 34. The power is then transmitted sequentially through the fifth planetary gear 343, the fourth planetary gear 342, the third planetary gear 341, and the second sun gear 31 to the second transmission shaft 7, thus achieving power splitting in first gear. At this point, the second sun gear 31, the second planet carrier 33, the second multi-linked planetary gears 34, and the third ring gear 35 constitute the NGGW planetary gear set.

[0039] When the shift mechanism 4 engages the second ring gear 25 and the second brake 52 (described later) of the brake assembly 5 brakes the third sun gear 32 of the second planetary gear set 3, the power system enters the second gear driving mode. A portion of the power output from the driving element 1 is transmitted sequentially through the first sun gear 21, the second planetary gear 222, and the first planet carrier 23 to the first transmission shaft 6. The remaining portion is transmitted through the first sun gear 21, the second planetary gear 222, the second ring gear 25, and the shift mechanism 4 to the second planet carrier 33. Under the action of the stationary third sun gear 32, the power is transmitted to the second multi-linked planetary gear 34. Then, the power is transmitted sequentially through the fourth planetary gear 342, the third planetary gear 341, and the second sun gear 31 to the second transmission shaft 7. This achieves power splitting in second gear driving. At this point, the second sun gear 31, the third sun gear 32, the second planet carrier 33, the third planetary gear 341, and the fourth planetary gear 342 form the WW planetary gear set.

[0040] In this way, in the first gear driving mode, the power system adopts the combined structure of NW planetary gear + NGGW planetary gear to realize the reduction transmission and differential function. In the second gear driving mode, the power system adopts the combined structure of NGW planetary gear + WW planetary gear to realize the reduction transmission and differential function. The main reduction transmission and differential function are integrated into one design by utilizing the combined arrangement of NGW planetary gear + NW planetary gear + NGGW planetary gear + WW planetary gear, so that each set of planetary gears can bear half of the total output torque, that is, the load of one tire, to ensure that the loads on the intermediate connecting member connecting the two planetary gears (that is, the shift mechanism 4) are equal in magnitude and opposite in direction. Moreover, the NW planetary gear and the NGW planetary gear share some parts, and the NGGW planetary gear and the WW planetary gear also share some parts, so as to reduce the number of parts of the power system and reduce the space occupied by the power system in the radial and axial directions, so as to facilitate layout on the whole vehicle.

[0041] Optionally, combined Figure 1 As shown, the brake 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 the one of the second sun gear 31 and the third sun gear 32 that is not drivingly connected to the second transmission shaft 7. In this way, by providing a brake at each of the two output ends of the second planetary gear 3 for braking, the structure of the brake assembly 5 is simplified and the position of the brake can be flexibly set according to actual needs.

[0042] Optionally, combined Figure 2 and Figure 3 As shown, the second sun gear 31 is in driving connection with the first transmission shaft 6, the second brake 52 is used to brake the third sun gear 32, the fifth planetary gear 343 is meshed with the fourth planetary gear 342, and the gear modes of the multi-gear planetary gear power system include a first gear driving mode and a second gear driving mode; When the gear mode is the first gear driving mode, the shift mechanism 4 is in transmission connection with the first ring gear 24, the first brake 51 is closed, and the second brake 52 is released. Part of the power output by the driving member 1 is transmitted to the first transmission shaft 6 via the first sun gear 21, the first multi-linked planetary gear 22, and the first planet carrier 23 in sequence, and the other part is transmitted to the second transmission shaft 7 via the first sun gear 21, the first multi-linked planetary gear 22, the first ring gear 24, the shift mechanism 4, the second planet carrier 33, the fifth planetary gear 343, the fourth planetary gear 342, the third planetary gear 341, and the second sun gear 31 in sequence. When the gear mode is the second gear driving mode, the shift mechanism 4 is connected to the second ring gear 25, the first brake 51 is disconnected, and the second brake 52 is closed. Part of the power output by the driving member 1 is transmitted to the first transmission shaft 6 through the first sun gear 21, the first multi-linked planetary gear 22 and the first planetary carrier 23 in sequence, and the other part is transmitted to the second transmission shaft 7 through the first sun gear 21, the first multi-linked 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 in sequence.

[0043] This allows for power splitting at different gears when the multi-gear planetary gear system is used as a two-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 enhancing its structural strength. By meshing the fifth planetary gear 343 with the fourth planetary gear 342, the radial dimensions of the second multi-linked planetary gear 34 are reduced, thereby reducing the radial dimensions of the second planetary gear 3 and, consequently, the entire power system, making the power system more compact and easier to deploy.

[0044] Optionally, combined Figure 2 and Figure 3 As shown, in the first gear driving mode, ,and ; in, is the transmission ratio of the multi-speed planetary gear system in the first gear driving mode, i1 is the gear ratio of the first ring gear 24 to the first sun gear 21, and i3 is the gear ratio of the third ring gear 35 to the second sun gear 31; In the second gear driving mode, ,and ; in, is the transmission ratio of the multi-speed planetary gear power system in the second gear driving mode, i2 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 the first gear driving mode, since the first planetary gear row 2 is equivalent to the NW planetary gear row and the second planetary gear row 3 is equivalent to the NGGW planetary gear row, i1 is also the transmission ratio of the NW planetary gear row and i3 is also the transmission ratio of the NGGW planetary gear row. In the second gear driving mode, since the first planetary gear row 2 is equivalent to the NGW planetary gear row and the second planetary gear row 3 is equivalent to the WW planetary gear row, i2 is also the transmission ratio of the NGW planetary gear row and i4 is also the transmission ratio of the WW planetary gear row.

[0046] In this optional embodiment, the formula To calculate the transmission ratio of the multi-speed planetary gear power system in the first gear driving mode, and according to the formula To calculate the transmission ratio of the multi-gear planetary gear power system in the second gear driving mode. Moreover, by setting the gear ratio relationship of the first planetary gear 2 and the second planetary gear 3 in the first gear driving mode to , set the gear ratio of the first planetary gear 2 and the second planetary gear 3 in the second gear driving mode to , to ensure that when the vehicle turns, the rising speed value of the first planetary carrier 23 is equal to the falling speed value of the second sun gear 31, or the falling speed value of the first planetary carrier 23 is equal to the rising speed value of the second sun gear 31, so that the multi-speed planetary gear power system meets the differential conditions for vehicle turning.

[0047] Optionally, combined Figure 1 As shown, the shift mechanism 4 is a two-way clutch. The two-way clutch is essentially a sliding sleeve with internal and external teeth. The shift fork mechanism pushes the sliding sleeve axially on the shaft to achieve gear shifting. Furthermore, due to its advantages such as simple and compact structure, low cost, high reliability, strong durability, and ability to transmit high torque, the two-way clutch is particularly suitable for vehicles with high requirements on cost, layout space, and weight. Therefore, in this optional embodiment, the use of a two-way clutch as the shift mechanism 4 to achieve switching between first and second gears can simplify the structure of the power system, making the overall layout of the power system more compact, saving space, weight, and cost, and facilitating a lightweight design for the entire vehicle.

[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 having a larger outer diameter, this not only reduces the radial size of the second multi-linked planetary gear 34, but also reduces the radial size of the third ring gear 35 meshing with the fifth planetary gear 343, further making the structure of the second planetary gear row 3 more compact and easier to arrange.

[0049] Further, combined with Figure 1As shown, the second sun gear 31 is drivingly connected to the second transmission shaft 7, and the second brake 52 is used to brake the third sun gear 32. Because the outer diameter of the third planetary gear 341 is larger than the outer diameter 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 third planetary gear 341 with the larger outer diameter, is larger than the outer diameter of the second sun gear 31, which meshes with the fourth planetary gear 342 with the smaller outer diameter. In this case, by drivingly connecting the second transmission shaft 7 to the second sun gear 31 with the smaller outer diameter and using the second brake 52 to brake the third sun gear 32 with the larger outer diameter, the output torque of the second planetary gear 3 can be reduced and the output speed can be increased, making the power system more labor-saving while achieving high-speed operation. At the same time, the rotational inertia of the output end of the power system can be reduced, thereby improving the dynamic response performance of the power system.

[0050] An embodiment of the present invention provides a vehicle comprising the multi-gear planetary gear power system as described above.

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

[0052] Although the present invention is disclosed as above, the protection scope of the present invention is not limited thereto. Those skilled in the art may make various changes and modifications without departing from the spirit and scope of the present invention, and these changes and modifications will fall within the protection scope of the present invention.

Claims

1. A multi-gear planetary gear power system, characterized in that: The invention comprises a driving member (1), a first planetary gear (2), a second planetary gear (3), a shift mechanism (4), a brake assembly (5), a first transmission shaft (6) and a second transmission shaft (7), wherein the first planetary gear (2) has a first input end and at least three first output ends, 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 connected to the driving member (1) and the shift mechanism (4), one of the at least three first output ends is connected to the first transmission shaft (6), and one of the at least three second output ends is connected to the second transmission shaft (7), the shift mechanism (4) is used to selectively connect to the other first output ends of the at least three first output ends, and the other second output ends of the at least three second output ends are respectively used to engage with or disengage from the brake assembly (5); When one of the remaining first output ends is transmission-connected to the shift mechanism (4), and at least one of the remaining second output ends is engaged with the brake assembly (5), the power output by the driving member (1) is transmitted to the first planetary gear (2) via the first input end of the first planetary gear (2) and then divided into two paths. One path is transmitted to the first transmission shaft (6) via the first output end of the first planetary gear (2) transmission-connected to the first transmission shaft (6), and the other path is transmitted to the second planetary gear (3) via the first output end connected to the shift mechanism (4), the shift mechanism (4), and the second input end in sequence, and is then transmitted to the second transmission shaft (7) via the second output end of the second planetary gear (3) transmission-connected to the second transmission shaft (7).

2. The multi-gear planetary gear power system according to claim 1, characterized in that: The first planetary gear (2) comprises a first sun gear (21), a first multi-linked planetary gear (22), a first planetary carrier (23), a first ring gear (24) and a second ring gear (25), wherein the first sun gear (21) constitutes the first input end of the first planetary gear (2), the first planetary carrier (23), the first ring gear (24) and the second ring gear (25) respectively constitute the first output end of the first planetary gear (2), and the first planetary carrier (23) is in transmission connection with the first transmission shaft (6); The first multi-linked planetary gear (22) comprises a first planetary gear (221) and a second planetary gear (222) which are coaxially arranged and transmission-connected. The first planetary gear (221) and the second planetary gear (222) are respectively meshed with the first ring gear (24) and the second ring gear (25). The first sun gear (21) is meshed with the first planetary gear (221) or the second planetary gear (222). The shift mechanism (4) is located between the first ring gear (24) and the second ring gear (25) and is used to selectively be transmission-connected with one of the first ring gear (24) and the second ring gear (25).

3. The multi-gear planetary gear power system according to claim 2, characterized in that: The shift mechanism (4) is a bidirectional clutch.

4. The multi-gear planetary gear power system according to claim 2, characterized in that: The second planetary gear (3) comprises a second sun gear (31), a third sun gear (32), a second planet carrier (33), a second multi-linked planetary gear (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 (3); 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 (3); The second multi-linked 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 transmission-connected. 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 ring gear (35) is meshed with the fifth planetary gear (343) and is used to engage with or disengage from the brake assembly (5). One of the second sun gear (31) and the third sun gear (32) is transmission-connected to the second transmission shaft (7). The other of the second sun gear (31) and the third sun gear (32) is used to engage with or disengage from the brake assembly (5).

5. The multi-gear planetary gear power system according to claim 4, characterized in that: The brake assembly (5) comprises a first brake (51) and a second brake (52), wherein the first brake (51) is used to brake the third ring gear (35), and the second brake (52) is used to brake the one of the second sun gear (31) and the third sun gear (32) that is not in transmission connection with the second transmission shaft (7).

6. The multi-gear planetary gear power system according to claim 5, characterized in that: The second sun gear (31) is in transmission connection with the second transmission shaft (7); the second brake (52) is used to brake the third sun gear (32); the fifth planetary gear (343) is meshed with the fourth planetary gear (342); 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 shift mechanism (4) is in transmission connection with the first ring gear (24), the first brake (51) is closed, and the second brake (52) is disconnected. A portion of the power output by the driving member (1) is sequentially transmitted to the first transmission shaft (6) via the first sun gear (21), the first multi-linked planetary gear (22), and the first planet carrier (23), and the other portion is sequentially transmitted to the second transmission shaft (7) via the first sun gear (21), the first multi-linked planetary gear (22), the first ring gear (24), the shift mechanism (4), the second planet 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, the shift mechanism (4) is in transmission connection with the second ring gear (25), the first brake (51) is disconnected, and the second brake (52) is closed. A portion of the power output by the driving member (1) is sequentially transmitted to the first transmission shaft (6) via the first sun gear (21), the first multi-linked planetary gear (22), and the first planet carrier (23), and the other portion is sequentially transmitted to the second transmission shaft (7) via the first sun gear (21), the first multi-linked planetary gear (22), the second ring gear (25), the shift mechanism (4), the second planet carrier (33), the fourth planetary gear (342), the third planetary gear (341), and the second sun gear (31).

7. The multi-gear planetary gear power system according to claim 6, characterized in that: In the first gear driving mode, ,and ; in, is the transmission ratio of the multi-gear planetary gear power system in the first gear driving mode, i1 is the gear ratio of the first ring gear (24) to the first sun gear (21), and i3 is the gear ratio of the third ring gear (35) to the second sun gear (31); In the second gear driving mode, ,and ; in, is the transmission ratio of the multi-gear planetary gear power system in the second gear driving mode, i2 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).

8. The multi-gear planetary gear power system according to claim 4, characterized in that: The outer diameter of the third planetary gear (341) is greater than the outer diameter of the fourth planetary gear (342), and the fifth planetary gear (343) is meshed with the fourth planetary gear (342).

9. The multi-gear planetary gear power system according to claim 1, characterized in that: The driving member (1) includes one of a motor and a generator.

10. A vehicle, characterized in that: A multi-gear planetary gear power system comprising any one of claims 1-9.

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