Transmission system and vehicle

Abstract

The application provides a transmission system and a vehicle. The transmission system provided by the application comprises an engine, a power transmission assembly and a second output shaft. The power transmission assembly comprises a double clutch, a planetary gear set, a first output shaft and a motor. The double clutch is in transmission connection with the engine. The planetary gear set is in control connection with the double clutch. The motor and the planetary gear set are both connected with the first output shaft. The double clutch and the planetary gear set are both connected with the second output shaft. The first output shaft and the second output shaft are respectively adapted to different gears. The transmission system provided by the application can guarantee the smoothness of gear shifting and improve the NVH performance.

Description

Technical Field

[0001] This application relates to the field of vehicle transmission system technology, and particularly to a transmission system and a vehicle using the transmission system. Background Technology

[0002] As the core transmission component of hybrid vehicles, the smoothness of shifting in a single-motor hybrid transmission directly affects the driving experience, while noise, vibration, and harshness (NVH) performance is related to ride comfort. Both are key factors in measuring the performance of a single-motor hybrid transmission.

[0003] In related technologies, most single-motor hybrid transmissions adopt a "planetary gear set + dual-clutch" structure. Some solutions simplify the structure by directly connecting the engine to a component of the planetary gear set. This type of structure aims to achieve power distribution through the planetary gear set and complete gear shifting with the help of the dual-clutch, in order to adapt to the collaborative work requirements of the single motor and the engine.

[0004] However, the aforementioned "planetary gear set + dual-clutch" structure relies on clutch slippage to avoid power interruption during gear shifting, which can easily lead to a decrease in output torque and disrupt the smoothness of gear shifting; the design of directly connecting the engine to the planetary gear set lacks a buffer adjustment structure, resulting in poor NVH performance and making it difficult to meet users' needs for driving comfort. Utility Model Content

[0005] This application provides a transmission system and vehicle that can not only improve the smoothness of gear shifting, but also improve NVH performance.

[0006] On one hand, this application provides a transmission system including an engine, a power transmission component, and a second output shaft; the power transmission component includes a dual clutch, a planetary gear set, a first output shaft, and a motor, the dual clutch is connected to the engine for transmission, the planetary gear set is connected to the dual clutch for control, and both the motor and the planetary gear set are connected to the first output shaft; both the dual clutch and the planetary gear set are connected to the second output shaft; wherein the first output shaft and the second output shaft are adapted to different gears.

[0007] In this way, during gear shifting, the coordinated control of the dual clutch and planetary gear set allows the motor and engine to independently drive the first and second output shafts respectively. This avoids the problem of output torque reduction caused by clutch slippage in the "planetary gear set + dual clutch" structure of related technologies, which relies on clutch slippage to prevent power interruption. This effectively ensures smooth gear shifting and improves the driving experience. Secondly, the transmission connection between the dual clutch and the engine replaces the design of the engine directly connecting to a single component of the planetary gear set in related technologies. The slippage characteristics of the dual clutch can form a buffer adjustment structure, which can buffer the impact during engine power transmission, solving the problem of poor NVH performance caused by lack of buffering and improving ride comfort. At the same time, the structure in which the planetary gear set is controlled by the dual clutch and both the motor and the planetary gear set are connected to the first output shaft retains the core functions of the planetary gear set in power distribution and the dual clutch in gear shifting. Through the transmission connection of multiple components, it ensures that the motor and engine can work together to adapt to different operating conditions, taking into account the stability of power transmission and adaptability to operating conditions. This makes up for the shortcomings of related technologies in terms of shifting smoothness and NVH performance, and improves the overall performance of the transmission system provided in this application.

[0008] As an alternative implementation, the central axis of the engine, the central axis of the planetary gear set, and the central axis of the electric motor are located on the same straight line.

[0009] The coaxial arrangement of the engine, planetary gear set, and electric motor allows for a more direct power transmission path, reducing power loss during transmission and improving transmission efficiency. Secondly, the coaxial design makes the entire transmission system more compact, which is beneficial for vehicle space layout, especially in hybrid vehicles where space is a major concern, freeing up more installation space for other components.

[0010] As an optional implementation, the planetary gear set includes a ring gear, planet gears, a planet carrier, and a sun gear; the ring gear is connected to a dual-clutch transmission; the planet gears are mounted on the planet carrier and mesh with the ring gear, the planet carrier is connected to a second output shaft, and the planet carrier is connected to a dual-clutch transmission; the sun gear meshes with the planet gears and is connected to a first output shaft.

[0011] The gear ring is connected to the dual-clutch transmission, the planetary carrier is connected to the dual-clutch transmission, and the power of the motor and engine is split through the connection with the planetary gear set to meet the needs of different working conditions.

[0012] As an optional implementation, the dual clutch includes a first sub-clutch and a second sub-clutch, both of which are connected to the engine drive; the first sub-clutch is controlled by the ring gear, and the second output shaft and planetary carrier are both connected to the second sub-clutch.

[0013] As an alternative implementation, the first sub-clutch is located outside the second sub-clutch, and both the first and second sub-clutches are located between the planetary gear set and the engine, with the motor located on the side of the planetary gear set (22) away from the engine.

[0014] In this way, the radial space is fully utilized, avoiding excessive installation area occupied by the axial layout, making the structure of the transmission system provided by this application more compact, and reducing mutual interference between the first sub-clutch and the second sub-clutch, thereby improving control independence and stability.

[0015] As an optional implementation, the first sub-clutch is located in front of the second sub-clutch, and both the first and second sub-clutches are located outside the planetary gear set. The first sub-clutch, the second sub-clutch, and the planetary gear set are all located between the engine and the electric motor.

[0016] The front-to-back arrangement of the first and second sub-clutches makes the spatial layout of the transmission system provided in this embodiment more reasonable and the structure more compact, adapting to the complex installation requirements inside the vehicle.

[0017] As an alternative implementation, the motor is connected to the first output shaft via a gear structure or a sprocket structure.

[0018] Among them, both gear structure and sprocket structure are mature and reliable mechanical transmission forms, with the advantages of high transmission efficiency and low power loss. They can ensure that the power output of the motor is accurately and efficiently transmitted to the first output shaft, avoid energy waste in the power transmission process, and ensure the timeliness of power output.

[0019] As an optional implementation, the planetary gear set includes a ring gear, planet gears, a planet carrier, and a sun gear; the ring gear is connected to a second output shaft and is also connected to a dual-clutch transmission; the planet gears are mounted on the planet carrier, meshing with the ring gear, and the planet carrier is connected to the dual-clutch transmission; the sun gear meshes with the planet gears and is also connected to a first output shaft.

[0020] The gear ring is directly connected to the second output shaft, and the gear ring and planetary carrier receive the engine power transmitted by the dual clutch. The sun gear corresponds to the first output shaft. In this way, the engine power can be transmitted to the gear ring (second output shaft) and the sun gear (first output shaft) respectively after being input through the planetary carrier by the dual clutch control and the motor, ensuring uninterrupted power during gear shifting and improving driving smoothness.

[0021] As an optional implementation, the dual clutch includes a first sub-clutch and a second sub-clutch, with the first sub-clutch located outside the second sub-clutch. Both the first and second sub-clutches are connected to the engine drive. The first sub-clutch is connected to the planetary carrier drive, and the second output shaft and the ring gear are both connected to the second sub-clutch.

[0022] In this embodiment, the first and second sub-clutches are arranged in the inward and outward directions, making full use of the radial space layout and avoiding excessive axial occupation of the installation area, thus further improving the structural compactness of the transmission system and adapting to the limited installation space requirements inside the vehicle. Secondly, the first sub-clutch, through its transmission connection with the planetary carrier, can input engine power into the planetary gear set, while the second sub-clutch directly connects to the second output shaft to transmit power, forming two independent power paths: "planetary gear set split transmission" and "direct transmission," thereby improving the flexibility of power transmission.

[0023] As an alternative implementation, both the first and second sub-clutches are located between the planetary gear set and the engine, with the motor located on the side of the planetary gear set furthest from the engine.

[0024] In this way, the first and second sub-clutches are positioned close to the engine, which shortens the power transmission path from the engine to the dual clutches, reduces power loss and delay during power transmission, and facilitates the first and second sub-clutches to quickly respond to the engine's power on / off needs, thus improving the timeliness of power control.

[0025] As an optional implementation, the first output shaft is fitted with a second output shaft.

[0026] In this way, the hollow structure allows the two output shafts to be nested on the same axis, without occupying additional axial or radial space, which improves the structural compactness of the transmission system provided by this application and adapts to the limited installation space requirements inside the vehicle. Secondly, the hollow design allows the first output shaft and the second output shaft to rotate independently without interfering with each other, which not only ensures that the two can be adapted to the independent transmission function of different gears, but also enables power coordinated output when needed.

[0027] On the other hand, this application provides a vehicle including the aforementioned transmission system.

[0028] The vehicle provided in this embodiment achieves high driving stability by employing the aforementioned transmission system. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of a first structure of a transmission system provided in an embodiment of this application; Figure 2 This is a schematic diagram of a second structure of the transmission system provided in an embodiment of this application; Figure 3 This is a schematic diagram of a third structure of the transmission system provided in an embodiment of this application; Figure 4 This is a schematic diagram of a fourth structure of the transmission system provided in an embodiment of this application.

[0030] Explanation of reference numerals in the attached figures: 1. Engine; 2. Power transmission components; 3. Second output shaft; 4. Gear structure; 10. Transmission system; 21. Dual clutch; 22. Planetary gear set; 23. First output shaft; 24. Motor; 41. First gear; 42. Second gear; 43. Third gear; 211. First sub-clutch; 212. Second sub-clutch; 221. Ring gear; 222. Planet gear; 223. Planet carrier; 224. Sun gear. Detailed Implementation

[0031] The technical solutions in this application will be clearly and thoroughly described below with reference to the accompanying drawings. In the description of the embodiments of this application, unless otherwise stated, " / " means "or," for example, A / B can mean A or B. "And / or" in the text is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Furthermore, in the description of the embodiments of this application, "multiple" refers to two or more than two.

[0032] Hereinafter, the terms "first" and "second" are used for descriptive purposes only and should not be construed as implying or suggesting relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

[0033] In related technologies, many single-motor hybrid transmissions adopt a "planetary gearbox + dual-clutch" structure. Some solutions, to simplify the structure, use a design where the engine is directly connected to a component of the planetary gearbox. This type of structure aims to achieve power distribution through the planetary gearbox and gear shifting through the dual-clutch, adapting to the collaborative work requirements of a single motor and engine. However, the aforementioned "planetary gearbox + dual-clutch" structure relies on clutch slippage to prevent power interruption during gear shifts, which can easily lead to a decrease in output torque and compromise shift smoothness. The design where the engine is directly connected to the planetary gearbox lacks a buffer adjustment structure, resulting in poor NVH performance and failing to meet users' demands for driving comfort.

[0034] Based on this, embodiments of this application provide a transmission system and vehicle that can not only improve the smoothness of gear shifting, but also improve NVH performance.

[0035] The embodiments of this application will be described in detail below with reference to the accompanying drawings and specific implementation details.

[0036] Please see Figure 1 , Figure 1This is a schematic diagram of a first structural embodiment of the transmission system provided in this application. This embodiment provides a transmission system 10, including an engine 1, a power transmission assembly 2, and a second output shaft 3. The power transmission assembly 2 includes a dual clutch 21, a planetary gear set 22, a first output shaft 23, and a motor 24. The dual clutch 21 is drive-connected to the engine 1, and the planetary gear set 22 is control-connected to the dual clutch 21. Both the motor 24 and the planetary gear set 22 are connected to the first output shaft 23. Both the dual clutch 21 and the planetary gear set 22 are connected to the second output shaft 3. The first output shaft 23 and the second output shaft 3 are respectively adapted to different gear positions.

[0037] In this way, during gear shifting, the dual clutch 21 and planetary gear set 22 can work together to allow the motor 24 and engine 1 to independently drive the first output shaft 23 and the second output shaft 3, respectively. This avoids the problem of output torque reduction caused by clutch slippage in the "planetary gear set + dual clutch" structure of related technologies, which relies on clutch slippage to avoid power interruption. This effectively ensures smooth gear shifting and improves the driving experience.

[0038] Secondly, the transmission connection between the dual clutch 21 and the engine 1 replaces the design in the related technology where the engine 1 is directly connected to a certain component of the planetary gear set 22. The slippery friction characteristics of the dual clutch 21 can form a buffer adjustment structure, which can buffer the impact during the power transmission process of the engine, solve the problem of poor NVH performance caused by lack of buffer, and improve driving comfort.

[0039] Meanwhile, the structure in which the planetary gear set 22 is controlled to the dual clutch 21 and both the motor 24 and the planetary gear set 22 are connected to the first output shaft 23 not only retains the core functions of the planetary gear set 22 in power distribution and the dual clutch 21 in gear shifting, but also ensures that the motor 24 and the engine 1 can work together to adapt to different working conditions through the transmission connection of multiple components. This balances the stability of power transmission and the adaptability of working conditions, makes up for the deficiencies of related technologies in shift smoothness and NVH performance, and improves the overall performance of the transmission system 10 provided in this embodiment.

[0040] For example, in some specific embodiments, the first output shaft 23 can be adapted to an odd number of gears, such as 2, 4, 6, or 8; the second output shaft 3 can be adapted to an odd number of gears, such as 1, 3, 5, or 7. It should be noted that in some other embodiments, the first output shaft 23 and the second output shaft 3 can also be adapted to other gears, which are not limited here.

[0041] In this embodiment, the first output shaft 23 is fitted with the second output shaft 3.

[0042] The hollow sleeve structure allows the two output shafts to be nested on the same axis, eliminating the need for additional axial or radial space and improving the structural compactness of the transmission system 10 provided in this embodiment, thus adapting to the limited installation space requirements inside the vehicle. Secondly, the hollow sleeve design allows the first output shaft 23 and the second output shaft 3 to rotate independently without interfering with each other. This ensures that they can each be adapted to the independent transmission function of different gears, and can also achieve power synergy output when needed. For example, in hybrid mode, the two power sources can be independently transmitted through the two shafts and then merged, avoiding power loss or shift jerking caused by transmission interference. Moreover, the coaxial hollow sleeve layout shortens the power transmission path, reduces energy loss during power transmission, and improves transmission efficiency. At the same time, this compact coaxial design can reduce vibration and sway during power transmission, further optimizing NVH performance.

[0043] In some embodiments, the central axis of the engine 1, the central axis of the planetary gear set 22, and the central axis of the motor 24 are located on the same straight line.

[0044] First, the coaxial arrangement of the engine 1, planetary gear set 22, and motor 24 allows for a more direct power transmission path, reducing power loss during transmission and improving transmission efficiency. Second, the coaxial design makes the entire transmission system 10 more compact, which is beneficial for vehicle space layout, especially in hybrid models where space is a major concern, freeing up more installation space for other components.

[0045] Moreover, the coaxial structure can reduce vibration and yaw during power transmission, thereby optimizing NVH performance and improving ride comfort. At the same time, this layout also facilitates the assembly and maintenance of the engine 1, planetary gear set 22 and motor 24, reduces assembly errors, and ensures the stability and reliability of the power system. While achieving efficient power coupling and distribution, it also takes into account structural compactness and smooth operation.

[0046] Please continue to combine Figure 2 , Figure 2 This is a schematic diagram of a second structure of the transmission system provided in an embodiment of this application. As shown in the figure, the connection between the motor 24 and the first output shaft 23 is not limited to a direct connection; it can also be connected through the gear structure 4 or sprocket structure shown in the figure.

[0047] Among them, both the gear structure 4 and the sprocket structure are mature and reliable mechanical transmission forms, with the advantages of high transmission efficiency and low power loss. They can ensure that the power output by the motor 24 is accurately and efficiently transmitted to the first output shaft 23, avoiding energy waste in the power transmission process and ensuring the timeliness of power output. Secondly, both the gear structure 4 and the sprocket structure have good load-bearing capacity and impact resistance, which can be adapted to the power output requirements of the motor 24 under different working conditions (such as starting, acceleration, and climbing), effectively dispersing the load in the transmission process, reducing component wear, and extending the service life of the connection between the motor 24 and the first output shaft 23.

[0048] like Figure 2 As shown, in some specific embodiments, the gear structure 4 may include a first gear 41, a second gear 42, and a third gear 43. The first gear 41 is mounted on the first output shaft 23, the second gear 42 meshes with the first gear 41, the third gear 43 meshes with the second gear 42, and the third gear 43 is connected to the motor shaft of the motor 24. It should be noted that in other embodiments, the gear structure 4 may also have other structural forms, which are not specifically limited here.

[0049] The specific form of the sprocket structure is not described in this embodiment, as long as it can achieve the purpose of this embodiment.

[0050] Please continue to combine Figure 3 , Figure 3 This is a schematic diagram of a third structure of the transmission system provided in an embodiment of this application. (See attached diagram.) Figure 1 and Figure 3 As shown, in one embodiment, a dual clutch 21 is located between the planetary gear set 22 and the engine 1, and a motor 24 is located on the side of the planetary gear set 22 away from the engine 1.

[0051] The dual clutch 21 is positioned close to the engine 1, which can shorten the power transmission path from the engine to the dual clutch 21, reduce power loss and delay during power transmission, and facilitate the dual clutch 21 to quickly respond to the power on / off requirements of the engine 1, thereby improving the timeliness of power control.

[0052] Secondly, the motor 24 is positioned on the side of the planetary gear set 22 furthest from the engine 1, and is located at both ends of the planetary gear set 22, forming a coaxial sequential layout of "engine 1 - dual clutch 21 - planetary gear set 22 - motor 24". This makes the transmission system 10 provided in this embodiment more compact, optimizes space utilization, and adapts to the installation requirements inside the vehicle. In addition, this two-end distribution layout reduces mutual interference between the engine 1 and the motor 24. Vibrations from the engine 1 are less likely to be directly transmitted to the motor 24, and the operating noise of the motor 24 is less likely to diffuse towards the engine 1, indirectly improving the overall NVH performance.

[0053] like Figure 1 As shown, in one specific embodiment, the planetary gear set 22 includes a ring gear 221, planet gears 222, a planet carrier 223, and a sun gear 224; the ring gear 221 is connected to the dual clutch 21 for transmission; the planet gears 222 are mounted on the planet carrier 223 and mesh with the ring gear 221; the planet carrier 223 is connected to the second output shaft 3 and is connected to the dual clutch 21 for transmission; the sun gear 224 meshes with the planet gears 222 and is connected to the first output shaft 23.

[0054] The gear ring 221 and planetary carrier 223 are both connected to the dual clutch 21. The input and output of engine power to the planetary gear set 22 can be controlled by the on and off state of the dual clutch 21. With the meshing relationship between the planetary gear 222 and the gear ring 221 and the sun gear 224 respectively, the planetary gear set 22 has a power splitting function, which can flexibly distribute the power ratio between the engine 1 and the motor 24 to adapt to different working conditions.

[0055] Secondly, the planetary carrier 223 is connected to the second output shaft 3, and the sun gear 224 is connected to the first output shaft 23. The first output shaft 23 and the second output shaft 3 are adapted to different gears, so that the power of the planetary gear set 22 can be accurately transmitted to the corresponding gear through the two output shafts, realizing independent power distribution and gear adaptation. With the control of the dual clutch 21, power interruption during gear shifting can be avoided, ensuring smooth driving.

[0056] like Figure 1 and Figure 2 As shown, the specific structure of the dual clutch 21 can be as follows: the dual clutch 21 includes a first sub-clutch 211 and a second sub-clutch 212, both of which are connected to the engine 1 for transmission; the first sub-clutch 211 is controlled to the ring gear 221, and the second output shaft 3 and the planetary carrier 223 are both connected to the second sub-clutch 212.

[0057] Furthermore, the first sub-clutch 211 is located outside the second sub-clutch 212, and both the first sub-clutch 211 and the second sub-clutch 212 are located between the planetary gear set 22 and the engine 1. The motor 24 is located on the side of the planetary gear set 22 away from the engine 1.

[0058] The first sub-clutch 211 and the second sub-clutch 212 are arranged in the inward and outward directions, which makes full use of the radial space and avoids the axial layout from occupying too much installation area, making the structure of the transmission system 10 provided in this embodiment more compact. It also reduces the mutual interference between the first sub-clutch 211 and the second sub-clutch 212, and improves the control independence and stability.

[0059] In addition, both the first sub-clutch 211 and the second sub-clutch 212 are connected to the engine 1 for transmission, and can independently receive engine power and achieve differentiated control. With the control connection between the first sub-clutch 211 and the gear ring 221, and the direct connection between the second sub-clutch 212 and the second output shaft 3, two independent and cooperative power transmission paths can be formed, avoiding the risk of power interruption caused by single clutch control in related technologies.

[0060] Moreover, the first sub-clutch 211 can adjust the power distribution state of the planetary gear set 22 by controlling the gear ring 221, and the second sub-clutch 212 directly transmits power to the second output shaft 3. The two work together to achieve flexible distribution of engine power. It can achieve the electronically controlled continuously variable transmission (e-CVT) mode through the planetary gear set 22 and the motor 24, and can also directly drive the second output shaft 3 to adapt to the corresponding gear, thus improving the adaptability of working conditions.

[0061] like Figure 3 As shown, in another specific embodiment, the planetary gear set 22 includes a ring gear 221, planet gears 222, a planet carrier 223, and a sun gear 224; the ring gear 221 is connected to the second output shaft 3 and is also connected to the dual clutch 21; the planet gears 222 are mounted on the planet carrier 223 and are meshed with the ring gear 221, and the planet carrier 223 is connected to the dual clutch 21; the sun gear 224 meshes with the planet gears 222 and is also connected to the first output shaft 23.

[0062] Among them, the gear ring 221 is directly connected to the second output shaft 3. The gear ring 221 and the planetary carrier 223 receive the engine power transmitted by the dual clutch 21. The sun gear 224 corresponds to the first output shaft 23. In this way, through the control of the dual clutch 21 and the coordination of the motor, the engine power is input through the planetary carrier 223 and then the power is split through the meshing of the planetary gears 222, and transmitted to the gear ring 221 (second output shaft 3) and the sun gear 224 (first output shaft 23) respectively, ensuring uninterrupted power during gear shifting and improving driving smoothness.

[0063] The structure of the dual clutch 21 is as follows: the dual clutch 21 includes a first sub-clutch 211 and a second sub-clutch 212. The first sub-clutch 211 is located outside the second sub-clutch 212. Both the first sub-clutch 211 and the second sub-clutch 212 are connected to the engine 1 for transmission. The first sub-clutch 211 is connected to the planetary carrier 223 for transmission. The second output shaft 3 and the gear ring 221 are both connected to the second sub-clutch 212.

[0064] The first sub-clutch 211 and the second sub-clutch 212 are arranged in the inward and outward directions, making full use of the radial space layout and avoiding excessive axial occupation of the installation area, thereby further improving the structural compactness of the transmission system 10 provided in this embodiment and adapting to the limited installation space requirements inside the vehicle. Secondly, the first sub-clutch 211, through its transmission connection with the planetary carrier 223, can input engine power into the planetary gear set 22. With the engagement of the planetary gears 222 with the ring gear 221 and the sun gear 224, power is split. The second sub-clutch 212 is directly connected to the second output shaft 3 to transmit power, forming two independent power paths: "planetary gear set split transmission" and "direct transmission," thereby improving the flexibility of power transmission.

[0065] Moreover, this transmission distribution method, combined with the design that the first output shaft 23 and the second output shaft 3 are adapted to different gears respectively, allows the engine power to be seamlessly switched between the two paths by switching the working state of the two sub-clutches during gear shifting, ensuring smooth gear shifting.

[0066] It should be noted that the aforementioned inner and outer directions are radial directions, with the inner side being the side closer to the first output shaft 23 and the outer side being the side farther away from the first output shaft 23.

[0067] Please continue to combine Figure 4 , Figure 4 This is a schematic diagram of a fourth structure of the transmission system provided in an embodiment of this application. In another embodiment, the dual clutch 21 includes a first sub-clutch 211 and a second sub-clutch 212. The first sub-clutch 211 is located in front of the second sub-clutch 212. Both the first sub-clutch 211 and the second sub-clutch 212 are connected to the engine 1. The first sub-clutch 211 is connected to the ring gear 221. The second output shaft 3 and the planetary carrier 223 are both connected to the second sub-clutch 212.

[0068] Furthermore, the first sub-clutch 211 and the second sub-clutch 212 are both located outside the planetary gear set 22, and the first sub-clutch 211, the second sub-clutch 212 and the planetary gear set 22 are all located between the engine 1 and the electric motor 24.

[0069] The dual clutch 21 and planetary gear set 22 are arranged radially to make full use of the radial space and avoid occupying too much installation area axially. Combined with the front and rear arrangement of the first sub-clutch 211 and the second sub-clutch 212, the spatial layout of the transmission system 10 provided in this embodiment is more reasonable and the structure is more compact, which can adapt to the complex installation requirements inside the vehicle.

[0070] It should be noted that the aforementioned front-to-back direction, i.e., the axial direction, refers to the front side being closer to engine 1 and the rear side being farther away from engine 1. Furthermore, in this embodiment, the transmission relationship between the planetary gear set 22 and the first output shaft 23 and the second output shaft 3 is... Figure 1The transmission relationship is the same as in the previous section, and no restrictions are imposed here.

[0071] In this embodiment, the transmission system 10 operates as follows: Engine 1 direct drive mode has two power transmission routes: The first method is to switch the first sub-clutch 211 in the dual clutch 21 to the disengaged state, while switching the second sub-clutch 212 to the engaged state. Under this condition, the motor 24 stops running and does not participate in power transmission. The power output by the engine 1 will be directly transmitted to the second output shaft 3 through the planet carrier 223 of the planetary gear set 22. The second output shaft 3 then drives the transmission structure of the corresponding gear, ultimately achieving effective power output. The second method involves switching both the first sub-clutch 211 and the second sub-clutch 212 in the dual clutch 21 to the engaged state. Under this condition, the motor 24 also stops running and does not participate in power transmission. The power output from the engine 1 is input to the planetary gear set 22. Through the coordinated operation of the internal gear ring 221, planetary gears 222, planet carrier 223 and sun gear 224 of the planetary gear set 22, the overall power output is achieved. The power is transmitted to the first output shaft 23 and the second output shaft 3 respectively. Then, the two output shafts drive the corresponding transmission structure of the appropriate gear to complete the synchronous output of power.

[0072] 24-speed direct drive mode power transmission route of the motor: When the engine 1 is not started and does not participate in power output, the first sub-clutch 211 and the second sub-clutch 212 of the dual clutch 21 are both in the disengaged state to cut off the power connection between the engine 1 and the subsequent transmission components. After the motor 24 starts, the power output will be directly transmitted to the first output shaft 23, and then the first output shaft 23 will drive its corresponding gear transmission structure to achieve stable power output and ensure that the vehicle can drive normally in this mode.

[0073] e-CVT mode power transmission route: The first sub-clutch 211 of the dual-clutch 21 is engaged, while the second sub-clutch 212 is disengaged. Under this condition, the engine 1 and the electric motor 24 start synchronously and jointly contribute to power output. The power output from the engine 1 is directly input to the planet carrier 223 of the planetary gear set 22, and the power output from the electric motor 24 is directly input to the sun gear 224 of the planetary gear set 22. After entering the planetary gear set 22, the power is distributed and speed is adjusted through the meshing and coordinated operation of its internal ring gear 221, planet gears 222, planet carrier 223, and sun gear 224, achieving optimized power matching between the engine 1 and the electric motor 24. The power processed by the planetary gear set 22 can be transmitted to the first output shaft 23 and the second output shaft 3, which then drive their respective gears, ultimately achieving stable power output and ensuring that the vehicle can adapt to different driving conditions in this mode.

[0074] There are two ways to achieve the power transmission route in hybrid mode: The first method involves switching both the first sub-clutch 211 and the second sub-clutch 212 in the dual-clutch 21 to the engaged state. Under this condition, the engine 1 and the motor 24 start synchronously and output power. The power of the two merges to form an overall power flow, which is synchronously transmitted to the first output shaft 23 and the second output shaft 3. The first output shaft 23 and the second output shaft 3 then drive their respective gear transmission structures, ultimately achieving the coordinated output of power from the engine 1 and the motor 24, ensuring that the vehicle's power performance meets driving requirements. The second method involves switching the first sub-clutch 211 of the dual-clutch 21 to the disengaged state while simultaneously switching the second sub-clutch 212 to the engaged state. Under this condition, the engine 1 and the motor 24 start synchronously and output power independently. The power output by the engine 1 is directly transmitted to the second output shaft 3 via the second sub-clutch 212, while the power output by the motor 24 is directly transmitted to the first output shaft 23. By precisely matching the transmission ratios of the gears of the first output shaft 23 and the second output shaft 3, the speed and torque of the two independent power flows are adapted and integrated to form a coordinated and consistent overall power output, ensuring the power stability and smoothness of the vehicle during driving.

[0075] There are two states for starting engine 1: starting engine 1 while parked and starting engine 1 while driving. Specifically, when starting the engine 1 from a stop, the first sub-clutch 211 and the second sub-clutch 212 in the dual clutch 21 are first switched to the engaged state, so that the motor 24 and the engine 1 establish a power connection through the dual clutch 21. In this connected state, the motor 24 starts and outputs power, which is transmitted to the engine 1 through the engaged first sub-clutch 211 and the second sub-clutch 212, driving the crankshaft of the engine 1 to rotate, and finally realizing the smooth start of the engine 1 when the engine is stopped.

[0076] There are two ways to start the engine while driving: The first method involves switching both the first sub-clutch 211 and the second sub-clutch 212 of the dual clutch 21 to the engaged state during vehicle operation, thereby establishing a stable power connection between the motor 24 and the engine 1 through the dual clutch 21. At this time, the motor 24 outputs power, which is transmitted to the engine 1 through the engaged first sub-clutch 211 and second sub-clutch 212, driving the crankshaft of the engine 1 to rotate, thus directly realizing the rapid start of the engine 1 under driving conditions and ensuring timely power connection. The second method involves starting engine 1 in e-CVT mode. During vehicle operation, the first sub-clutch 211 of the dual-clutch 21 is engaged, while the second sub-clutch 212 is disengaged. The system first acquires the input speed of motor 24 and, combined with the transmission ratio parameters of the current gear on the first output shaft 23, calculates the actual speed at the vehicle's wheel ends. Then, based on the meshing transmission characteristics of the internal gear ring 221, planetary gears 222, planetary carrier 223, and sun gear 224 of the planetary gear set 22, the transmission ratio between engine 1 and motor 24 is adjusted to determine the appropriate gear on the second output shaft 3 and complete the matching. Once all parameters are properly matched, the power output of motor 24 is transmitted to engine 1 through the corresponding transmission path, driving engine 1 to start smoothly and ensuring the smoothness and stability of engine 1's power during startup.

[0077] This embodiment also provides a vehicle, including the transmission system 10 described in the above embodiments. The structure of the transmission system 10 has been described in detail in the above embodiments and will not be repeated here.

[0078] It should be noted that the vehicle provided in this embodiment should also include other modules or components, which will not be described in detail here.

[0079] The vehicle provided in this embodiment has good driving stability by adopting the above-described transmission system 10.

[0080] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A transmission system, characterized in that, include: engine; A power transmission assembly includes a dual clutch, a planetary gear set, a first output shaft, and a motor. The dual clutch is drive-connected to the engine, the planetary gear set is control-connected to the dual clutch, and both the motor and the planetary gear set are connected to the first output shaft. The second output shaft is connected to both the dual clutch and the planetary gear set. The first output shaft and the second output shaft are adapted to different gears.

2. The transmission system according to claim 1, characterized in that, The central axis of the engine, the central axis of the planetary gear set, and the central axis of the motor are located on the same straight line.

3. The transmission system according to claim 2, characterized in that, The planetary array includes: The gear ring is connected to the dual clutch drive; Planetary gears and a planet carrier, the planetary gears being mounted on the planet carrier and meshing with the ring gear, the planet carrier being connected to the second output shaft, and the planet carrier being connected to the dual-clutch transmission; and The sun gear meshes with the planet gears, and the sun gear is connected to the first output shaft.

4. The transmission system according to claim 3, characterized in that, The dual clutch includes a first sub-clutch and a second sub-clutch, both of which are connected to the engine drive. The first sub-clutch is connected to the gear ring drive, and the second output shaft and the planetary carrier are both connected to the second sub-clutch; Wherein, the first sub-clutch is located outside the second sub-clutch, both the first and second sub-clutches are located between the planetary gear set and the engine, and the motor is located on the side of the planetary gear set away from the engine; or, The first sub-clutch is located in front of the second sub-clutch. Both the first and second sub-clutches are located outside the planetary gear set. The first sub-clutch, the second sub-clutch, and the planetary gear set are all located between the engine and the electric motor.

5. The transmission system according to claim 3, characterized in that, The motor is connected to the first output shaft via a gear structure or a sprocket structure.

6. The transmission system according to claim 2, characterized in that, The planetary array includes: A gear ring is connected to the second output shaft, and the gear ring is also connected to the dual clutch drive. Planetary gears and a planet carrier, the planetary gears being mounted on the planet carrier and meshing with the ring gear, the planet carrier being connected to the dual-clutch transmission; and The sun gear meshes with the planet gears, and the sun gear is connected to the first output shaft.

7. The transmission system according to claim 6, characterized in that, The dual clutch includes a first sub-clutch and a second sub-clutch, the first sub-clutch being located outside the second sub-clutch, and both the first sub-clutch and the second sub-clutch being connected to the engine drive. The first sub-clutch is connected to the planetary carrier, and the second output shaft and the gear ring are both connected to the second sub-clutch.

8. The transmission system according to claim 7, characterized in that, Both the first sub-clutch and the second sub-clutch are located between the planetary gear set and the engine, and the motor is located on the side of the planetary gear set away from the engine.

9. The transmission system according to any one of claims 1 to 7, wherein the first output shaft is loosely fitted with the second output shaft.

10. A vehicle, characterized in that, Includes the transmission system described in any one of claims 1 to 9.

Images