A multi-gear hybrid power transmission system
Patent Information
- Application Number
- CN202521850878.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-08-29
- Publication Date
- 2026-09-15
- Estimated Expiration
- 2035-08-29
AI Technical Summary
这种设计导致整体传动系统结构复杂度显著增加、零部件数量增多、加工制造难度提升，同时因传动链延长和效率损耗，在一定程度上限制了节能水平的进一步提升
本实用新型通过集成单行星排与拉维纳行星轮系，结合多离合器及制动器的协同控制，实现了结构紧凑性与传动效率的显著提升。相较于现有技术需额外配置多挡变速器导致的复杂传动链问题，本实用新型通过双行星排架构及多挡位设计（四挡发动机驱动、两挡纯电驱动及ECVT模式），有效简化了传动结构、减少了零部件数量，降低了制造难度，同时通过动力源的灵活组合（发动机、发电机、驱动电机三动力源协同驱动及双电机纯电驱动）及工况适配（低速电机驱动、高速发动机直驱、加速时电机增补动力），显著增强了动力性能，避免了发动机过载，提升了加速能力与能效水平。此外，本实用新型还兼具能量回收、停车发电及ECVT无级变速功能，覆盖全速域驾驶需求，兼顾动力性与经济性，解决了现有技术中结构复杂、效率受限及动力性不足的问题。
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Figure CN224752282U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to a multi-gear hybrid powertrain system, belonging to the field of hybrid transmission technology. Background Technology
[0002] With the rapid development and technological innovation of the automotive industry, the application of new energy hybrid powertrains in the transmission field is becoming increasingly widespread. As a highly integrated, high-efficiency power transmission system with multi-mode hybrid power technology, it can effectively match various power combination modes of the engine, generator, and electric motor, and has become a major development direction of new energy vehicle technology.
[0003] However, existing hybrid power transmission structures still face technical bottlenecks. Typical solutions generally employ a pair of long-meshing gears with a fixed speed ratio as the core transmission component. Because the speed ratio of these gears is relatively small, a multi-speed transmission is required to adjust the speed ratio to meet the power demands under different driving conditions. This design significantly increases the overall complexity of the transmission system, the number of parts, and the difficulty of manufacturing. Furthermore, the extended transmission chain and efficiency losses limit further improvements in energy efficiency to some extent. Summary of the Invention
[0004] To address the problems existing in the background technology, this utility model provides a multi-gear hybrid power transmission system.
[0005] To achieve the above objectives, this utility model adopts the following technical solution: a multi-gear hybrid power transmission system, comprising an engine, a hydraulic torque converter, a starting clutch, a generator, an input shaft, a second clutch, a first clutch, a drive motor, an output shaft, a first brake, a second brake, a single planetary gear set, and a Ravina planetary gear system; the output end of the engine is connected to the input end of the hydraulic torque converter, the output end of the hydraulic torque converter is connected to the input end of the input shaft, the output end of the input shaft is connected to the inner hub of the starting clutch, the outer disc of the starting clutch is connected to the single planetary gear set, the single planetary gear set is connected to the inner hub of the second clutch, the inner hub of the first clutch, and the generator, the outer disc of the second clutch is connected to the Ravina planetary gear system, the outer disc of the first clutch is connected to the rotor of the drive motor, and the rotor of the drive motor is connected to the Ravina planetary gear system; the Ravina planetary gear system is connected to the output shaft, the first brake, and the second brake; the first brake, the second brake, and the single planetary gear set are all fixed to a housing.
[0006] Furthermore, the single planetary gear set includes a first sun gear, first planet gears, a first planet carrier, and a first external gear ring; the first sun gear and the first planet carrier are fitted on the outer side of the input shaft, the first planet carrier is connected to the outer disc of the starting clutch, the inner hub of the second clutch, and the inner hub of the first clutch, the first planet gear is mounted on the first planet carrier, the first planet gear is meshed with the first sun gear and the first external gear ring, and the first external gear ring is fixed to the housing; the first sun gear is connected to the rotor of the generator; Furthermore, the Ravina planetary gear train includes a second sun gear, a third sun gear, short planet gears, long planet gears, a second external gear ring, and a second planet carrier; the second planet carrier is connected to the outer disc of the second clutch and the first brake, the second planet carrier is equipped with short planet gears and long planet gears, the outer end of the long planet gears meshes with the second external gear ring, the second external gear ring is connected to the output shaft; the inner end of the long planet gears meshes with both the short planet gears and the second sun gear, the second sun gear is connected to the second brake, the short planet gears mesh with the third sun gear, and the third sun gear is connected to the rotor of the drive motor.
[0007] Compared with the prior art, the beneficial effects of this utility model are: This invention achieves a significant improvement in structural compactness and transmission efficiency by integrating a single planetary gear set and a Ravina planetary gear system, combined with the coordinated control of multiple clutches and brakes. Compared to the complex transmission chain caused by the need for additional multi-speed transmissions in existing technologies, this invention effectively simplifies the transmission structure, reduces the number of parts, and lowers manufacturing difficulty through a dual planetary gear set architecture and multi-speed design (four-speed engine drive, two-speed pure electric drive, and ECVT mode). Simultaneously, through flexible combinations of power sources (coordinated drive of engine, generator, and drive motor, and dual-motor pure electric drive) and adaptation to operating conditions (low-speed motor drive, high-speed engine direct drive, and motor supplementary power during acceleration), it significantly enhances power performance, avoids engine overload, and improves acceleration capability and energy efficiency. Furthermore, this invention also incorporates energy recovery, parking power generation, and ECVT continuously variable transmission functions, covering the full speed range driving needs, balancing power and economy, and solving the problems of complex structure, limited efficiency, and insufficient power in existing technologies. Attached Figure Description
[0008] Figure 1 This is a schematic diagram of the structure of this utility model; Figure 2 This is a schematic diagram of the first gear transmission operation; Figure 3 This is a schematic diagram of the second gear transmission. Figure 4 This is a schematic diagram of the three-speed transmission. Figure 5This is a schematic diagram of the four-speed transmission. Figure 6 This is a schematic diagram of the EV1 gear transmission. Figure 7 This is a schematic diagram of the EV2 gear transmission operation; Figure 8 This is a schematic diagram of the operation of the dual-motor EV1 gear transmission; Figure 9 This is a schematic diagram of the operation of the dual-motor EV2 gear transmission; Figure 10 This is a schematic diagram of the three-power-source drive mode. Figure 11 This is a schematic diagram of the ECVT gear transmission. Detailed Implementation
[0009] The technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of this utility model. Obviously, the described embodiments are only some embodiments of the utility model, not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without creative effort are within the protection scope of this utility model.
[0010] A multi-speed hybrid powertrain system includes an engine 1, a hydraulic torque converter 2, a starting clutch 3, a generator 4, an input shaft 5, a second clutch 10, a first clutch 11, a drive motor 12, an output shaft 19, a first brake 20, a second brake 21, a single planetary gear set, and a Ravenna planetary gear train. The output end of the engine 1 is connected to the input end of the hydraulic torque converter 2, the output end of the hydraulic torque converter 2 is connected to the input end of the input shaft 5, the output end of the input shaft 5 is connected to the inner hub of the starting clutch 3, the outer disc of the starting clutch 3 is connected to the single planetary gear set, and the single planetary gear set is connected to the first... The inner hub of the second clutch 10, the inner hub of the first clutch 11, and the generator 4 are connected. The outer plate of the second clutch 10 is connected to the Ravina planetary gear system, and the outer plate of the first clutch 11 is connected to the rotor of the drive motor 12. The rotor of the drive motor 12 is connected to the Ravina planetary gear system. The Ravina planetary gear system is connected to the output shaft 19, the first brake 20, and the second brake 21. The first brake 20, the second brake 21, and the single planetary gear set are all fixed on the housing 22. The single planetary gear set includes a first sun gear 6, a first planet gear 7, a first planet carrier 8, and a first external gear ring 9. The input shaft 5 is fitted with a first sun gear 6 and a first planetary carrier 8. The first planetary carrier 8 is connected to the outer disc of the starting clutch 3, the inner hub of the second clutch 10, and the inner hub of the first clutch 11. A first planetary gear 7 is mounted on the first planetary carrier 8. The first planetary gear 7 is meshed with the first sun gear 6 and the first external gear ring 9. The first external gear ring 9 is fixed to the housing 22. The first sun gear 6 is connected to the rotor of the generator 4. The Ravina planetary gear train includes a second sun gear 13, a third sun gear 14, short planetary gears 15, long planetary gears 16, and a second external gear ring 17. The second planetary carrier 18 is connected to the outer disc of the second clutch 10 and the first brake 20. The second planetary carrier 18 is equipped with a short planetary gear 15 and a long planetary gear 16. The outer end of the long planetary gear 16 is meshed with the second external gear ring 17, which is connected to the output shaft 19. The inner end of the long planetary gear 16 is meshed with both the short planetary gear 15 and the second sun gear 13. The second sun gear 13 is connected to the second brake 21. The short planetary gear 15 is meshed with the third sun gear 14, which is connected to the rotor of the drive motor 12.
[0011] The output shaft 19 obtains power output from the Ravina planetary gear system. The first brake 20 and the second brake 21 are used to brake the corresponding components to achieve different gears or modes. S1 and S2 are related power transmission nodes. The whole system realizes multiple power transmission and mode switching through the meshing and constraint relationships of various components to meet the needs of different working conditions.
[0012] This utility model discloses a first-gear transmission method for a multi-gear hybrid powertrain system, the method comprising the following steps: S1: The generator 4 and drive motor 12 are put into a non-working state, the second clutch 10 and the second brake 21 are put into a disengaged state, the starting clutch 3, the first clutch 11 and the first brake 20 are put into a engaged state, and the engine 1 and the hydraulic torque converter 2 are put into a working state; the drive motor 12 and the generator 4 can both participate in power generation or driving.
[0013] S2: Start engine 1. The power of engine 1 is output to input shaft 5 through hydraulic torque converter 2. Input shaft 5 engages with starting clutch 3 and first clutch 11 to transmit power to third sun gear 14, causing third sun gear 14 to rotate. S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. In the first gear, the speed is very low, and the rotation of the long planet gear 16 generates a torque in the opposite direction on the second planet carrier 18. S4: Because the second planetary carrier 18 is fixed to the first brake 20 which is in the engagement state, the long planetary gear 16 drives the second external gear ring 17 that meshes with it to rotate. S5: The second external gear ring 17 outputs power through the output shaft 19.
[0014] This utility model discloses a two-speed transmission method for a multi-speed hybrid powertrain system, the method comprising the following steps: S1: The generator 4 and drive motor 12 are put into a non-working state, the second clutch 10 and the first brake 20 are put into a disengaged state, the starting clutch 3, the first clutch 11 and the second brake 21 are put into a engaged state, and the engine 1 and the hydraulic torque converter 2 are put into a working state; the drive motor 12 and the generator 4 can both participate in power generation or driving.
[0015] S2: Start engine 1. The power of engine 1 is output to input shaft 5 through hydraulic torque converter 2. Input shaft 5 engages with starting clutch 3 and first clutch 11 to transmit power to third sun gear 14, causing third sun gear 14 to rotate. S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. At the same time, because the second brake 21 engages and fixes the second sun gear 13, the long planet gear 16 revolves synchronously during its rotation. S4: The long planetary gear 16 drives the second external gear ring 17, which meshes with it, to rotate through the combined motion of revolution and rotation; S5: The second external gear ring 17 outputs power through the output shaft 19.
[0016] This utility model discloses a three-speed transmission method for a multi-speed hybrid powertrain system, the method comprising the following steps: S1: The generator 4 and drive motor 12 are put into a non-working state, the first brake 20 and the second brake 21 are put into a disengaged state, the starting clutch 3, the second clutch 10 and the first clutch 11 are put into a engaged state, and the engine 1 and the hydraulic torque converter 2 are put into a working state; the drive motor 12 and the generator 4 can both participate in power generation or driving.
[0017] S2: Start engine 1. The power of engine 1 is output to input shaft 5 through hydraulic torque converter 2. Input shaft 5 engages starting clutch 3, second clutch 10 and first clutch 11 to transmit power to third sun gear 14 and second planetary carrier 18, so that input shaft 5 is connected to third sun gear 14 and second planetary carrier 18 as a whole, and the three rotate with input shaft 5 at the same speed. S3: The short planetary gear 15 and the long planetary gear 16 are constrained and cannot rotate on their own. They can only revolve together with the third sun gear 14 and the second planet carrier 18. The revolving short planetary gear 15 and the long planetary gear 16 drive the second external gear ring 17 to rotate together. S4: The second external gear ring 17 outputs power through the output shaft 19.
[0018] This utility model discloses a four-speed transmission method for a multi-speed hybrid powertrain system, the method comprising the following steps: S1: The generator 4 and drive motor 12 are put into a non-working state, the first clutch 11 and the first brake 20 are put into a disengaged state, the starting clutch 3, the second clutch 10 and the second brake 21 are put into a engaged state, and the engine 1 and the hydraulic torque converter 2 are put into a working state; the drive motor 12 and the generator 4 can both participate in power generation or driving.
[0019] S2: Start engine 1. The power of engine 1 is output to input shaft 5 through hydraulic torque converter 2. Input shaft 5 engages starting clutch 3 and second clutch 10 to transmit power to second planetary carrier 18, causing second planetary carrier 18 to rotate. S3: The second planetary carrier 18 rotates, driving the long planetary gear 16 and the short planetary gear 15 to rotate. Because the second brake 21 is in working condition, the second sun gear 13 is fixed. The long planetary gear 16 and the short planetary gear 15 rotate on their own axis while revolving around the second sun gear 13, thereby driving the second external gear ring 17 to rotate. S4: The second external gear ring 17 outputs power through the output shaft 19.
[0020] This invention discloses a gear transmission method for a multi-gear hybrid powertrain system with three power source drive modes, primarily applicable to starting or low-torque, high-endurance operating conditions. The method includes the following steps: S1: Disengage the second clutch 10 and the second brake 21, engage the starting clutch 3, the first clutch 11 and the first brake 20, and put the engine 1, generator 4 and drive motor 12 into operation; put the hydraulic torque converter 2 into a non-direct operating condition, working through the direct sliding friction between the pump wheel and the turbine, decoupling the engine from the vehicle speed, and solving the problem of the engine not being able to work below the operating speed.
[0021] S2: Start engine 1. Power from engine 1 is output to input shaft 5 via hydraulic torque converter 2 and coupled to single planetary gear set via starting clutch 3. Power from generator 4 is transmitted to first clutch 11 via single planetary gear set. Input shaft 5 engages with starting clutch 3 and first clutch 11, and merges with the power output from drive motor 12. S3: The power of the generator 4 and the drive motor 12 after they are combined is transmitted to the third sun gear 14. The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. In the first gear, the speed is very low. The rotation of the long planet gear 16 generates a torque in the opposite direction on the second planet carrier 18. S4: Because the second planetary carrier 18 is fixed to the first brake 20 which is in the engagement state, the long planetary gear 16 drives the second external gear ring 17 that meshes with it to rotate. S5: The second external gear ring 17 outputs power through the output shaft 19.
[0022] This utility model discloses a method for EV1 gear transmission in a multi-gear hybrid powertrain system, the method comprising the following steps: S1: Put the engine 1, hydraulic torque converter 2 and generator 4 into a non-working state, put the starting clutch 3, second clutch 10, first clutch 11 and second brake 21 into a disengaged state, put the first brake 20 into an engaged state, and put the drive motor 12 into a working state. S2: Drive motor 12 outputs power and transmits the power to the third sun gear 14, causing the third sun gear 14 to rotate; S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. Because the first brake 20 is in working condition, the second planet carrier 18 is fixed to prevent it from rotating in the opposite direction. Under the constraint, the long planet gear 16 drives the second external gear ring 17 to rotate. S4: The second external gear ring 17 outputs power through the output shaft 19.
[0023] This utility model discloses a method for EV 2-speed transmission in a multi-gear hybrid powertrain system, the method comprising the following steps: S1: Put the engine 1, hydraulic torque converter 2 and generator 4 into a non-working state, put the starting clutch 3, second clutch 10, first clutch 11 and first brake 20 into a disengaged state, put the second brake 21 into an engaged state, and put the drive motor 12 into a working state. S2: Drive motor 12 outputs power and transmits the power to the third sun gear 14, causing the third sun gear 14 to rotate; S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. Because the second brake 21 is in working condition, the second sun gear 13 is fixed, and the long planet gear 16 rotates synchronously around the sun while rotating on its own axis. S4: The long planetary gear 16 drives the second external gear ring 17 to rotate through a compound motion; S5: The second external gear ring 17 outputs power through the output shaft 19.
[0024] This utility model discloses a dual-motor EV1-speed transmission method for a multi-gear hybrid powertrain system, the method comprising the following steps: S1: Put the engine 1 and the hydraulic torque converter 2 into a non-working state, put the starting clutch 3, the second clutch 10 and the second brake 21 into a disengaged state, put the first clutch 11 and the first brake 20 into a engaged state, and put the generator 4 and the drive motor 12 into a working state. S2: Start engine 1. The power of engine 1 is transmitted to the first clutch 11 through the single planetary gear set, and then transmitted to the drive motor 12 through the first clutch 11. The power output by the drive motor 12 and the power transmitted by the generator 4 are combined and transmitted to the third sun gear 14, causing the third sun gear 14 to rotate. S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15. Because the first brake 20 is in working condition, the second planet carrier 18 is fixed to prevent it from rotating in the opposite direction. Under the constraint, the long planet gear 16 drives the second external gear ring 17 to rotate. S4: The second external gear ring 17 outputs power through the output shaft 19.
[0025] This utility model discloses a dual-motor EV 2-speed transmission method for a multi-speed hybrid powertrain system, the method comprising the following steps: S1: Put the engine 1 and the hydraulic torque converter 2 into a non-working state, put the starting clutch 3, the second clutch 10 and the first brake 20 into a disengaged state, put the first clutch 11 and the second brake 21 into a engaged state, and put the generator 4 and the drive motor 12 into a working state. S2: Start engine 1. The power of engine 1 is transmitted to the first clutch 11 through the single planetary gear set. The power is then transmitted to the drive motor 12 through the first clutch 11. The power output by the drive motor 12 and the power transmitted by the generator 4 are combined and transmitted to the third sun gear 14, causing the third sun gear 14 to rotate. S3: The third sun gear 14 drives the long planet gear 16 to rotate through the meshing short planet gear 15; because the second brake 21 is in working condition, the second sun gear 13 is fixed, and the long planet gear 16 rotates synchronously around the sun while rotating on its own axis. S4: The long planetary gear 16 drives the second external gear ring 17 to rotate through the combined motion of rotation and revolution; S5: The second external gear ring 17 outputs power through the output shaft 19.
[0026] This utility model discloses a method for multi-gear hybrid powertrain system (ECVT) gear transmission, the method comprising the following steps: S1: Disengage the first clutch 11, the first brake 20 and the second brake 21, engage the starting clutch 3 and the second clutch 10, and put the engine 1 and the drive motor 12 into operation. S2: Power distribution and transmission under different operating conditions: S201: Low-speed driving condition: The power of engine 1 is transmitted to input shaft 5 via hydraulic torque converter 2, and coupled to single planetary gear set via starting clutch 3 to the generator 4 to realize energy recovery; drive motor 12 is a power source from battery or power distributed by input shaft 5, and transmits power to third sun gear 14. Short planet gear 15 and long planet gear 16 rotate with third sun gear 14, driving second external gear ring 17 to rotate, and outputting power through output shaft 19; S202: Normal driving condition: Part of the power of engine 1 is transmitted to generator 4 via input shaft 5 to supply power or store energy as needed; another part is transmitted to second planetary carrier 18 via input shaft 5 and second clutch 10. The second planetary carrier 18 rotates, which drives the long planetary gear 16 and short planetary gear 15 to rotate, and then drives the second external gear ring 17 to rotate, outputting power via output shaft 19. S203: Full-speed driving / acceleration condition: Engine 1 outputs full power, and the drive motor 12 supplements the power source from the battery or input shaft 5. The two work together to provide the power required for acceleration, driving the second external gear ring 17 to rotate, and outputting the power through the output shaft 19.
[0027] By adjusting the speed of the drive motor 12 and the engine 1, the Ravenna planetary gear mechanism can achieve a continuously variable transmission ratio between the engine and the wheels, matching efficient power combinations under different working conditions.
[0028] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of the equivalents of the claims be included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.
[0029] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.
Claims
1. A multi-gear hybrid powertrain system, characterized in that: The system includes an engine (1), a torque converter (2), a starting clutch (3), a generator (4), an input shaft (5), a second clutch (10), a first clutch (11), a drive motor (12), an output shaft (19), a first brake (20), a second brake (21), a single planetary gear set, and a Ravenna planetary gear train. The output end of the engine (1) is connected to the input end of the torque converter (2), the output end of the torque converter (2) is connected to the input end of the input shaft (5), the output end of the input shaft (5) is connected to the inner hub of the starting clutch (3), and the outer disc of the starting clutch (3) is connected to the torque converter (2). The single planetary gear set is connected to the inner hub of the second clutch (10), the inner hub of the first clutch (11), and the generator motor (4). The outer disk of the second clutch (10) is connected to the Ravina planetary gear system. The outer disk of the first clutch (11) is connected to the rotor of the drive motor (12). The rotor of the drive motor (12) is connected to the Ravina planetary gear system. The Ravina planetary gear system is connected to the output shaft (19), the first brake (20), and the second brake (21). The first brake (20), the second brake (21), and the single planetary gear set are all fixed on the housing (22).
2. The multi-gear hybrid powertrain system according to claim 1, characterized in that: The single planetary gear set includes a first sun gear (6), a first planet gear (7), a first planet carrier (8), and a first external gear ring (9); the input shaft (5) is fitted with the first sun gear (6) and the first planet carrier (8), the first planet carrier (8) is connected to the outer disk of the starting clutch (3), the inner hub of the second clutch (10) and the inner hub of the first clutch (11), the first planet carrier (8) is mounted on the first planet carrier (8), the first planet gear (7) is meshed with the first sun gear (6) and the first external gear ring (9), the first external gear ring (9) is fixed on the housing (22); the first sun gear (6) is connected to the rotor of the generator motor (4).
3. The multi-gear hybrid powertrain system according to claim 1, characterized in that: The Ravina planetary gear system includes a second sun gear (13), a third sun gear (14), short planet gears (15), long planet gears (16), a second external gear ring (17), and a second planet carrier (18). The second planet carrier (18) is connected to the outer disk of the second clutch (10) and the first brake (20). The second planet carrier (18) is equipped with short planet gears (15) and long planet gears (16). The outer end of the long planet gear (16) is meshed with the second external gear ring (17), which is connected to the output shaft (19). The inner end of the long planet gear (16) is meshed with both the short planet gear (15) and the second sun gear (13). The second sun gear (13) is connected to the second brake (21). The short planet gear (15) is meshed with the third sun gear (14), which is connected to the rotor of the drive motor (12).