Dual power source coupling driving system and vehicle

Abstract

This invention belongs to the field of vehicle transmission technology, and particularly relates to a dual-power-source coupled drive system and vehicle, including a fixed part and a first power source, a second power source, a first planetary gear set, and a second planetary gear set disposed within the fixed part; the output shaft of the first power source is coaxially and fixedly connected to the sun gear of the first planetary gear set, and the output shaft of the second power source is coaxially and fixedly connected to the planet carrier of the second planetary gear set; the sun gear of the second planetary gear set serves as the output shaft; the ring gear of the first planetary gear set and the ring gear of the second planetary gear set are coaxially and fixedly connected; the planet carrier of the first planetary gear set and the planet carrier of the second planetary gear set are coaxially and fixedly connected; both the first power source and the second power source have forward and reverse rotation functions; it also includes a one-way clutch, the fixed end of which is fixed to the fixed part, and the movable end of which is coaxially and fixed to the ring gear of the first planetary gear set; the movable end of the one-way clutch rotates forward and locks in reverse; the forward rotation direction of the movable end of the one-way clutch is the same as the forward rotation direction of the first power source.

Description

Technical Field

[0001] This invention belongs to the field of vehicle transmission technology, and particularly relates to a dual-power source coupled drive system and vehicle. Background Technology

[0002] Vehicles require significant driving torque during starting and hill climbing due to their weight, while demanding high speed and efficiency for cruising on flat roads. Traditional vehicles with single drive systems, limited by fixed gear ratios or drive modes, struggle to simultaneously meet these two differentiated needs across all operating conditions.

[0003] Existing technologies have developed solutions employing dual-power-source coupled drive, which adapt to different operating conditions by switching between torque coupling and speed coupling modes. The torque coupling mode superimposes the output torques of the two power sources, providing strong starting and climbing capabilities; the speed coupling mode synthesizes the speeds of the two power sources, ensuring the vehicle's high-speed driving performance and enabling the motor to operate in its efficient range.

[0004] However, existing dual-power-source coupled drive systems generally share a common drawback: to achieve switching between the two modes, they must rely on additional operating mechanisms, such as traditional clutches or synchronizers and their complex electro-hydraulic control systems. These additional actuators not only occupy valuable space within the transmission system, increasing the overall weight, manufacturing cost, and maintenance difficulty, but also cause losses in transmission efficiency. At the same time, the smoothness and responsiveness of the mode switching process are also limited by the performance of these external actuators, affecting the overall vehicle's power and driving quality.

[0005] Therefore, there is an urgent need for a dual-power source coupled drive system and vehicle to solve this problem. Summary of the Invention

[0006] The purpose of this invention is to provide a dual-power source coupled drive system and vehicle to solve the above-mentioned problems.

[0007] To achieve the above objectives, the present invention provides the following solution:

[0008] A dual-power-source coupled drive system includes a fixed part and a first power source, a second power source, a first planetary gear set, and a second planetary gear set disposed within the fixed part.

[0009] Wherein, the output shaft of the first power source is coaxially and fixedly connected to the sun gear of the first planetary gear set, and the output shaft of the second power source is coaxially and fixedly connected to the planet carrier of the second planetary gear set;

[0010] The sun gear of the second planetary array serves as the output shaft;

[0011] The gear rings of the first planetary set and the gear rings of the second planetary set are coaxially fixed.

[0012] The planet carrier of the first planetary set is coaxially fixed with the planet carrier of the second planetary set;

[0013] Both the first power source and the second power source have forward and reverse rotation functions;

[0014] It also includes a one-way clutch, wherein the fixed end of the one-way clutch is fixed to the fixed part, and the movable end of the one-way clutch is coaxially fixed to the ring gear of the first planetary gear set.

[0015] The movable end of the one-way clutch rotates in the forward direction and locks in the reverse direction.

[0016] The forward rotation direction of the movable end of the one-way clutch is the same as the forward rotation direction of the first power source.

[0017] Optionally, when the moving end of the one-way clutch rotates in the forward direction, the drive system is in speed coupling drive mode; when the moving end of the one-way clutch is locked in the reverse direction, the drive system is in torque coupling drive mode.

[0018] Optionally, the first planetary gear set includes a first gear ring, a first planet carrier, a first sun gear, and a first planet gear;

[0019] The first gear ring is fixed coaxially with the movable end of the one-way clutch;

[0020] The first sun gear is fixed coaxially with the output shaft of the first power source;

[0021] The first planetary gear is meshed between the first gear ring and the first sun gear, and the first planetary gear is rotatably engaged with the first planet carrier.

[0022] The first planet carrier and the planet carrier of the second planetary row are coaxially fixed together;

[0023] The first gear ring is fixed coaxially with the gear ring of the second planetary gear set.

[0024] Optionally, the second planetary gear set includes a second ring gear, a second planet carrier, a second sun gear, and second planet gears;

[0025] The second gear ring is fixed coaxially with the first gear ring;

[0026] The second planetary carrier is fixed coaxially with the first planetary carrier;

[0027] The second sun gear is rotatably mounted inside the fixed part, and one end of the output shaft is coaxially fixed to the second sun gear;

[0028] The second planetary gear is meshed between the second ring gear and the second sun gear, and the second planetary gear is rotatably engaged with the second planet carrier.

[0029] Optionally, the first power source is an electric motor.

[0030] Optionally, the second power source is an electric motor.

[0031] Optionally, the fixing part is a housing.

[0032] A vehicle comprising the aforementioned dual-power-source coupled drive system.

[0033] Optionally, the vehicle is a heavy-duty truck.

[0034] Compared with the prior art, the present invention has the following advantages and technical effects:

[0035] This invention achieves autonomous and smooth switching between torque coupling and speed coupling modes simply by controlling the steering of the first and second power sources. This is achieved by coaxially fixing the ring gears of the first and second planetary gear sets, and coaxially fixing the planet carriers of the first and second planetary gear sets, and using a one-way clutch to coaxially connect their moving ends to the ring gear of the first planetary gear set. This eliminates the need for additional mode switching actuators and their control systems, simplifying the system structure, reducing manufacturing costs, weight, and control complexity, and improving reliability. In torque coupling mode, the ring gear assembly is fixed by the reverse locking of the one-way clutch, achieving superimposed output of torque from both power sources, providing huge torque for vehicle starting and hill climbing. In speed coupling mode, the one-way clutch is released in the forward direction, and the system becomes a speed synthesizer, outputting higher speeds to meet the needs of high-speed driving, and allowing both power sources to operate more in their efficient range, effectively improving the vehicle's all-condition power performance, economy, and transmission efficiency. Attached Figure Description

[0036] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly described below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0037] Figure 1 This is a schematic diagram of the structure of the present invention;

[0038] Figure 2 This is a force analysis diagram of the present invention;

[0039] Figure 3 This is a diagram showing the power transmission in the torque coupling mode of this invention.

[0040] Figure 4 This is a power transmission diagram of the rotational speed coupling mode of the present invention;

[0041] The components are: 1. One-way clutch; 2. Housing; 3. First gear ring; 4. First planetary carrier; 5. First sun gear; 6. First planetary gear; 7. Second gear ring; 8. Second planetary carrier; 9. Second sun gear; 10. Second planetary gear; 11. Output shaft. Detailed Implementation

[0042] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0044] Reference Figures 1 to 4 The present invention discloses a dual-power source coupled drive system, including a fixed part and a first power source, a second power source, a first planetary gear set and a second planetary gear set disposed in the fixed part;

[0045] Among them, the output shaft of the first power source is coaxially and fixedly connected to the sun gear of the first planetary gear set, and the output shaft of the second power source is coaxially and fixedly connected to the planet carrier of the second planetary gear set.

[0046] The sun gear of the second planetary gear set serves as the output shaft;

[0047] The gear rings of the first planetary set and the gear rings of the second planetary set are fixed coaxially.

[0048] The planet carriers of the first planetary set and the planet carriers of the second planetary set are fixed coaxially.

[0049] Both the first and second power sources have forward and reverse rotation functions;

[0050] It also includes a one-way clutch 1, the fixed end of which is fixed to the fixed part, and the movable end of which is coaxially fixed to the gear ring of the first planetary gear set.

[0051] The moving end of the one-way clutch 1 rotates in the forward direction and locks in the reverse direction;

[0052] The forward rotation direction of the moving end of the one-way clutch 1 is the same as the forward rotation direction of the first power source.

[0053] As an optional implementation, when the moving end of the one-way clutch 1 rotates in the forward direction, the drive system is in speed coupling drive mode; when the moving end of the one-way clutch 1 is locked in the reverse direction, the drive system is in torque coupling drive mode.

[0054] The core of this device is as follows: the output shaft of the first power source is fixedly connected to the sun gear of the first planetary set to directly input power, while the output shaft of the second power source is fixedly connected to the planet carrier of the second planetary set; the power of the system is ultimately output by the sun gear of the second planetary set; in order to achieve power coupling, the planet carriers of the first planetary set and the planet carriers of the second planetary set are fixedly connected to each other, and at the same time, the gear rings of the first planetary set and the gear rings of the second planetary set are also fixedly connected to each other, thereby connecting the two planetary sets into a whole.

[0055] The key automatic mode switching function is achieved by a one-way clutch 1, whose fixed end is connected to a fixed part, and whose movable end is coaxially fixed with the gear ring of the first planetary gear set. The one-way clutch 1 is defined to be released when the movable end rotates in the forward direction and locked when it rotates in the reverse direction. The forward rotation direction of its movable end is consistent with the forward rotation direction of the first power source.

[0056] The system operates based on the coordinated control of the steering of the first and second power sources, automatically triggering two different operating modes. When the vehicle requires high torque output for starting or climbing, the system enters torque coupling drive mode. In this mode, the first power source is controlled to rotate in reverse, while the second power source rotates forward. Under this power input combination, the ring gear of the first planetary gear set will exhibit a reverse rotational tendency, opposite to the forward rotation direction of the first power source. Since the moving end of the one-way clutch 1 is fixedly connected to the ring gear of the first planetary gear set, this reverse rotational tendency immediately triggers the locking function of the one-way clutch 1, thereby locking the ring gear of the first planetary gear set and even the ring gear of the second planetary gear set fixedly connected to it onto the fixed part, preventing them from rotating. Thus, the power from the first power source is input through the sun gear of the first planetary gear set, amplified under the condition that the ring gear is fixed, and then transmitted through the planet carrier of the first planetary gear set to the planet carrier of the second planetary gear set fixedly connected to it; the power from the second power source is directly input to the planet carrier of the second planetary gear set. The two power sources converge on the second planetary gear set. Since the ring gear of the second planetary gear set is also fixed at this time, the power is combined again through torque and then output by the sun gear of the second planetary gear set, realizing the superposition of torque from the two power sources and providing the vehicle with huge driving torque.

[0057] When the vehicle enters high-speed cruising mode, the system automatically switches to speed-coupled drive mode. At this time, both the first and second power sources rotate forward. Under this power input combination, the ring gear of the first planetary gear set will generate a forward rotational tendency, consistent with the forward rotation direction of the first power source. This tendency causes the moving end of the one-way clutch 1 to enter a forward rotation state, thus disengaging the clutch and no longer constraining the ring gear of the first planetary gear set. The entire system becomes a speed synthesizer. The power from the first and second power sources is input through the sun gear of the first planetary gear set and the planet carrier of the second planetary gear set, respectively, and undergoes complex speed synthesis in the two interconnected planetary gear sets. Finally, the sun gear of the second planetary gear set outputs a higher synthesized speed to meet the vehicle's high-speed driving requirements, while allowing both power sources to operate more within their high-efficiency range.

[0058] This device, through its ingenious mechanical design, achieves automatic and smooth switching between torque coupling and speed coupling operating modes using only a single one-way clutch 1, completely eliminating the need for traditional electronically controlled clutches or synchronizers and their associated control systems. This not only greatly simplifies the system structure, making it more compact and reducing manufacturing costs, weight, and control complexity, but also improves system reliability. Furthermore, the two modes are optimized for the low-speed, high-torque and high-speed, high-efficiency requirements of heavy-duty trucks, respectively, effectively enhancing vehicle power, economy, and the quality of mode switching.

[0059] As an optional implementation, the first planetary gear set includes a first gear ring 3, a first planet carrier 4, a first sun gear 5, and a first planet gear 6;

[0060] The first gear ring 3 is fixed coaxially with the movable end of the one-way clutch 1;

[0061] The first sun gear 5 is fixed coaxially with the output shaft of the first power source;

[0062] The first planetary gear 6 is meshed between the first gear ring 3 and the first sun gear 5, and the first planetary gear 6 is rotatably engaged with the first planet carrier 4.

[0063] The first planet carrier 4 is coaxially fixed to the planet carrier of the second planet row;

[0064] The first gear ring 3 is fixed coaxially with the gear ring of the second planetary gear set.

[0065] The specific configuration of the first planetary gear set is as follows: the first sun gear 5 is fixedly connected to the first power source to input power, the first planet gear 6 is engaged between the first sun gear 5 and the first ring gear 3 and supported on the first planet carrier 4, the first ring gear 3 is fixedly connected to the movable end of the one-way clutch 1, and the first planet carrier 4 is fixedly connected to the planet carrier of the second planetary gear set.

[0066] When the first power source drives the first sun gear 5 to rotate, the power is transmitted to the first planet carrier 4 and the first ring gear 3 through the meshing first planet gear 6. In torque coupling mode, the one-way clutch 1 is locked, forcing the first ring gear 3 to be fixed. At this time, the power is transmitted from the first planet gear 6 to the first planet carrier 4 for output, realizing torque amplification. In speed coupling mode, the one-way clutch 1 is released, and the first ring gear 3 can rotate freely. The input power of the first sun gear 5 and the speed of the first ring gear 3 are combined here. After being adjusted by the first planet gear 6, the speed is output by the first planet carrier 4, realizing speed synthesis.

[0067] This structure ensures a clear power transmission path and smooth, efficient transmission. Furthermore, through the fixed connection between the first gear ring 3 and the one-way clutch 1, and the linkage between the first planetary carrier 4 and the second planetary gear set, it achieves a compact and reliable automatic switching between the two working modes.

[0068] As an optional implementation, the second planetary gear set includes a second gear ring 7, a second planet carrier 8, a second sun gear 9, and a second planet gear 10;

[0069] The second gear ring 7 is fixed coaxially with the first gear ring 3;

[0070] The second planetary carrier 8 is fixed coaxially with the first planetary carrier 4;

[0071] The second sun gear 9 is rotatably mounted in the fixed part, and one end of the output shaft 11 is coaxially fixed to the second sun gear 9.

[0072] The second planetary gear 10 is meshed between the second gear ring 7 and the second sun gear 9, and the second planetary gear 10 is in rotational engagement with the second planetary carrier 8.

[0073] The second planetary gear set achieves deep linkage with the first planetary gear set through the coaxial fixation of the second ring gear 7 and the first ring gear 3, and the coaxial fixation of the second planetary carrier 8 and the first planetary carrier 4, forming the core of power coupling. In torque coupling mode, when the first ring gear 3 is locked by the one-way clutch, the second ring gear 7, which is fixed to it, is also fixed. At this time, the power from the first planetary carrier 4 and the second power source power that directly drives the second planetary carrier 8 are combined at the second planetary gear set, and finally a huge torque is output by the second sun gear 9 through the output shaft 11. In speed coupling mode, the second ring gear 7 can rotate freely, and the second planetary gear set acts as a speed synthesizer, combining the input speed from the second planetary carrier 8 with the speed transmitted through the second ring gear 7, and finally a higher speed is output by the second sun gear 9.

[0074] This structural design ensures that the power is efficiently combined and converted before final output, and its compact connection reduces energy loss, which is the structural basis for achieving efficient dual-mode operation of the system.

[0075] As an alternative implementation, the first power source is an electric motor.

[0076] As an optional implementation, the second power source is an electric motor.

[0077] As an optional implementation, the fixing part is the housing 2.

[0078] The first power source, the second power source, the first planetary gear set, and the second planetary gear set are all connected and installed inside the housing 2.

[0079] The fixed end of the one-way clutch 1 is fixed to the housing 2, and the fixed end of the motor is fixed to the housing 2.

[0080] The first gear ring 3, the first planet carrier 4, the first sun gear 5, the second gear ring 7, the second planet carrier 8, the second sun gear 9, and the output shaft 11 are all rotatably mounted inside the housing 2.

[0081] The specific working principle of this device is as follows:

[0082] Automatic switching between torque coupling mode and speed coupling mode is achieved through a one-way clutch mechanism. The mode switching logic is shown in the table below:

[0083] Table 1 Mode Switching Logic Table

[0084] Operating mode One-way clutch M-A M-B Torque-coupled drive mode Lock-up Reverse rotation Forward rotation Speed-coupled drive mode Release Forward rotation Forward rotation

[0085] Automatic switching between torque coupling drive mode and speed coupling drive mode is achieved by using a one-way clutch 1 through the speed difference direction at both ends of the one-way clutch 1.

[0086] When the first power source rotates in reverse and the second power source rotates in forward, the speed difference between the two ends of the one-way clutch 1 is reversed, and the one-way clutch 1 is locked, realizing the torque coupling drive mode, which provides the vehicle with greater output torque and higher transmission efficiency. When the first power source rotates forward and the second power source rotates forward, the speed difference between the two ends of the one-way clutch 1 is forward, and the one-way clutch 1 is released, realizing the speed coupling drive mode, which provides the vehicle with greater driving speed and higher transmission efficiency. The application of the one-way clutch 1 makes mode switching quick and convenient.

[0087] Kinematic analysis was performed on it based on the mode switching logic:

[0088] When performing kinematic analysis on the designed configuration, a lever graphical model is used to simplify the planetary gear mechanism. This model equates the planetary gear mechanism to a lever, using the nodes of the lever to represent the central rotating component of the planetary gear mechanism, and the lever length relationship to represent the characteristic parameters of the planetary gear mechanism, namely the tooth ratio of the ring gear to the sun gear. This method can accurately and intuitively represent the rotational speed relationship between the sun gear, planet carrier, and ring gear, facilitating the dynamic analysis of complex transmission systems based on planetary gear mechanisms. The lever diagram for this scheme is attached. Figure 2 As shown.

[0089] The kinematic equations for the rotational speed coupling mode can be obtained from the four-point lever diagram:

[0090]

[0091] The kinematic equations for the torque coupling mode can be obtained from the four-point lever diagram:

[0092]

[0093] in, The characteristic coefficients of the left planetary gear mechanism are... The characteristic coefficients of the planetary gear mechanism on the right are... The input speed of the motor is MA. This is the input speed of motor MB. For output speed, This represents the input torque of the motor, MA. This represents the input torque of motor MB. This is the output torque.

[0094] The power flow direction under torque coupling and speed coupling modes is analyzed based on the kinematic equations. The power flow direction under torque coupling mode is shown in the attached figure. Figure 3 As shown, the power of motor MA is input to the sun gear of planetary gear set P1, and outputs through the planet gears of planetary gear set P1, the planet gears of planetary gear set P2, and the sun gear of planetary gear set P2; the power of motor MB is input to the planet carrier of planetary gear set P2, and outputs through the sun gear of planetary gear set P2. There is no power cycle in this process.

[0095] The power flow direction in the speed coupling mode is shown in the attached figure. Figure 4 As shown, the power of motor MA is input to the sun gear of planetary gear set P1, and outputs through the planet gears of planetary gear set P1, the ring gear of planetary gear set P1, the ring gear of planetary gear set P2, the planet gears of planetary gear set P2, and the sun gear of planetary gear set P2; the power of motor MB is input to the planet gears of planetary gear set P2, and outputs through the ring gear of planetary gear set P2 and the sun gear of planetary gear set P2. There is no power circulation in this process.

[0096] A vehicle comprising the aforementioned dual-power-source coupled drive system.

[0097] As an alternative implementation, the vehicle is a heavy-duty truck.

[0098] Compared to conventional vehicles, heavy-duty trucks incorporating the dual-power-source coupled drive system of this invention have the following advantages:

[0099] (1) The dual-motor coupling drive system for heavy trucks described in this invention adopts planetary gear mechanism transmission, which has a compact structure, smooth transmission, high transmission efficiency and a large transmission ratio range; it adopts a one-way clutch structure, which makes the transmission system structure more compact, improves the chassis utilization rate of heavy trucks and facilitates the arrangement of chassis space.

[0100] (2) The dual-motor coupled drive system for heavy trucks described in this invention has two working modes: torque coupling and speed coupling, enabling dual-motor torque coupling drive and dual-motor speed coupling drive. In the dual-motor torque coupling drive mode, the two power sources are torque coupled, which can achieve a larger torque range and output greater torque to improve the starting acceleration and hill-climbing acceleration performance of heavy trucks; in the dual-motor speed coupling drive mode, the two power sources are speed coupled, so that the two power sources work in the optimal working range as much as possible, improving the driving efficiency of the two power sources, achieving higher speed output, and improving the power and economy of heavy trucks.

[0101] (3) The dual-motor coupling drive system for heavy trucks described in this invention can switch modes using only a one-way clutch. It does not require separate operating mechanisms to control the switching between speed coupling and torque coupling modes. It can achieve autonomous mode switching by controlling the steering of the two power sources. Furthermore, the speed of each power component is continuous during switching, which improves the quality of mode switching and the controllability of the entire power system.

[0102] In the description of this invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0103] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Various modifications and improvements made by those skilled in the art to the technical solutions of the present invention without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. A dual-power-source coupled drive system, characterized in that, It includes a fixed part and a first power source, a second power source, a first planetary gear set and a second planetary gear set disposed within the fixed part; Wherein, the output shaft of the first power source is coaxially and fixedly connected to the sun gear of the first planetary gear set, and the output shaft of the second power source is coaxially and fixedly connected to the planet carrier of the second planetary gear set; The sun gear of the second planetary array serves as the output shaft; The gear rings of the first planetary set and the gear rings of the second planetary set are coaxially fixed. The planet carrier of the first planetary set is coaxially fixed with the planet carrier of the second planetary set; Both the first power source and the second power source have forward and reverse rotation functions; It also includes a one-way clutch (1), the fixed end of which is fixed to the fixed part, and the movable end of which is coaxially fixed to the gear ring of the first planetary gear set; The movable end of the one-way clutch (1) rotates in the forward direction and locks in the reverse direction; The forward rotation direction of the movable end of the one-way clutch (1) is consistent with the forward rotation direction of the first power source.

2. The dual-power-source coupled drive system according to claim 1, characterized in that: When the moving end of the one-way clutch (1) rotates in the forward direction, the drive system is in speed coupling drive mode; when the moving end of the one-way clutch (1) is locked in the reverse direction, the drive system is in torque coupling drive mode.

3. The dual-power-source coupled drive system according to claim 1, characterized in that: The first planetary gear set includes a first gear ring (3), a first planet carrier (4), a first sun gear (5), and a first planet gear (6); The first gear ring (3) is coaxially fixed with the movable end of the one-way clutch (1); The first sun gear (5) is fixed coaxially with the output shaft of the first power source; The first planetary gear (6) is meshed between the first gear ring (3) and the first sun gear (5), and the first planetary gear (6) is rotatably engaged with the first planet carrier (4); The first planet carrier (4) is coaxially fixed to the planet carrier of the second planetary row; The first gear ring (3) is fixed coaxially with the gear ring of the second planetary gear set.

4. The dual-power-source coupled drive system according to claim 3, characterized in that, The second planetary gear set includes a second gear ring (7), a second planet carrier (8), a second sun gear (9), and a second planet gear (10); The second gear ring (7) is fixed coaxially with the first gear ring (3); The second planetary carrier (8) is fixed coaxially with the first planetary carrier (4); The second sun gear (9) is rotatably disposed in the fixed part, and one end of the output shaft (11) is coaxially fixed to the second sun gear (9); The second planetary gear (10) is meshed between the second gear ring (7) and the second sun gear (9), and the second planetary gear (10) is rotatably engaged with the second planetary carrier (8).

5. The dual-power-source coupled drive system according to claim 1, characterized in that: The first power source is an electric motor.

6. The dual-power-source coupled drive system according to claim 1, characterized in that: The second power source is an electric motor.

7. The dual-power-source coupled drive system according to claim 1, characterized in that: The fixing part is the housing (2).

8. A vehicle, characterized in that, Includes a dual-power source coupled drive system as described in any one of claims 1-7.

9. A vehicle according to claim 8, characterized in that: The vehicle in question is a heavy-duty truck.

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