Double-planet-row hybrid power system sharing gear ring

Abstract

The invention discloses a double-planet-row hybrid power system sharing a gear ring, and the system comprises a double-row compound planet gear mechanism which comprises a first planet gear mechanism provided with a first planet carrier, a first sun gear and a first inner gear ring, and a second planet gear mechanism provided with a second planet carrier, a second sun gear and a second inner gear ring, the second inner gear ring and the first inner gear ring are fixed into a whole; the engine is in transmission connection with the first planet carrier; the first motor is in transmission connection with the first sun gear; the second motor is in transmission connection with the second sun gear; the brake component is used for controlling locking or releasing of the first inner gear ring and the second inner gear ring; the clutch component is used for controlling combination or separation between the second sun gear and the second planet carrier; the input end of the output mechanism is in transmission connection with the second planet carrier, and the output mechanism is used for transmitting power to wheels; the hybrid power system is simple in structure, and the dynamic property and economical efficiency of the vehicle can be improved.

Description

Technical Field

[0001] The present invention relates to the technical field of hybrid electric vehicles, and in particular to a double planetary gear hybrid electric system with a shared ring gear. Background Art

[0002] In related technologies, automotive hybrid systems achieve power diversion and convergence through single or multiple planetary gears, allowing for greater freedom in adjusting the operating states of the engine and motor, resulting in improved power and economy. However, current power-dividing hybrid systems generally require multiple clutches and / or brakes, as well as transmission structures, to achieve multiple operating modes and ensure the vehicle's adaptability to various driving conditions. Furthermore, to meet dynamic requirements such as hill climbing performance, higher-power motors must be selected, or additional torque-amplifying structures must be installed. These factors inevitably make the hybrid system's overall structure more complex, less compact, and less efficient, hindering overall vehicle manufacturing cost control.

[0003] Therefore, it is necessary to provide a new hybrid power system, hoping to ensure that the vehicle has better adaptability to driving conditions through a relatively simple structure, thereby improving the vehicle's power and economy. Summary of the Invention

[0004] In view of this, an object of the present invention is to provide a dual planetary gear hybrid system with a shared ring gear, which has a simple structure and can ensure that the vehicle has good adaptability to driving conditions, thereby improving the vehicle's power and economy.

[0005] To achieve the above-mentioned objectives, the present invention provides the following technical solutions: a dual-planetary hybrid system with a shared ring gear, comprising: a double-row compound planetary gear mechanism, comprising a first planetary gear mechanism having a first planetary carrier, a first sun gear and a first inner ring gear, and a second planetary gear mechanism having a second planetary carrier, a second sun gear and a second inner ring gear, the second inner ring gear being fixed as a whole with the first inner ring gear; an engine, the output end of the engine being transmission-connected to the first planetary carrier; a first motor, the output end of the first motor being transmission-connected to the first sun gear; a second motor, the output end of the second motor being transmission-connected to the second sun gear; a brake component for operating the locking or releasing of the first inner ring gear and the second inner ring gear; a clutch component for operating the engagement or separation between the second sun gear and the second planetary carrier; an output mechanism, the input end of the output mechanism being transmission-connected to the second planetary carrier and for transmitting power to the wheels.

[0006] Furthermore, the rotation axes of the first motor, the second motor, the first planetary carrier and the second planetary carrier are collinear.

[0007] Furthermore, the first motor is arranged on the front side of the first planetary gear mechanism, and the second motor is arranged on the rear side of the second planetary gear mechanism; a first input shaft is coaxially provided on the first planetary carrier, the first input shaft extends forward and passes through the output shaft of the first motor, the first sun gear is fixedly connected to the output shaft of the first motor, and the first input shaft is transmission-connected to the output end of the engine; the output mechanism includes a power output shaft, the power output shaft is coaxially fixed to the second planetary carrier and extends backward through the output shaft of the second motor, and the second sun gear is fixedly connected to the output shaft of the second motor.

[0008] Furthermore, the first motor is arranged on the front side of the first planetary gear mechanism, and the second motor is arranged on the rear side of the second planetary gear mechanism; a first input shaft is coaxially provided on the first planetary carrier, the first input shaft extends forward and passes through the output shaft of the first motor, the first sun gear is fixedly connected to the output shaft of the first motor, and the first input shaft is transmission-connected to the output end of the engine; the second sun gear is fixedly connected to the output shaft of the second motor; an output gear is fixedly provided on the second planetary carrier, and the output mechanism includes a transmission gear meshing with the output gear.

[0009] Furthermore, the second motor is arranged on the rear side of the second planetary gear mechanism, and the first motor is arranged on the rear side of the second motor; the second sun gear is fixedly connected to the output shaft of the second motor; the output shaft of the first motor extends forward and passes through the output shaft of the second motor, and the first sun gear is fixedly connected to the output shaft of the first motor; an output gear is fixed on the second planetary carrier, and the output mechanism includes a transmission gear meshing with the output gear.

[0010] Furthermore, the output shaft of the engine is coaxially arranged with the axis of the first planet carrier.

[0011] Furthermore, the rotation axes of the first motor, the first planetary carrier and the second planetary carrier are collinear, and the rotation axis of the second motor is parallel to the rotation axis of the first motor; the first motor is arranged on the rear side of the second planetary gear mechanism, and the output shaft of the first motor extends forward and passes through the second planetary carrier and the second sun gear in sequence and is fixedly connected to the first sun gear; the second sun gear is fixedly provided with a second input gear, and the output shaft of the second motor is fixedly connected with a second output gear meshing with the second input gear; the second planetary carrier is fixedly provided with an output gear, and the output mechanism includes a transmission gear meshing with the output gear.

[0012] Furthermore, the output shaft of the engine is coaxially arranged with the axis of the first planet carrier.

[0013] Furthermore, the rotation axes of the second motor, the first planetary carrier and the second planetary carrier are collinear, and the rotation axes of the first motor and the second motor are parallel; the second motor is arranged on the rear side of the first planetary gear mechanism, and the output shaft of the second motor extends forward and passes through the first sun gear and is fixedly connected to the second sun gear; a first input gear is fixedly provided on the first sun gear, and a first output gear meshing with the first input gear is fixedly connected to the output shaft of the first motor; a third input gear is fixedly provided on the first planetary carrier and is transmission-connected to the output end of the engine; and an output gear is fixedly provided on the second planetary carrier.

[0014] Furthermore, the braking component is a brake, and the clutch component is a clutch.

[0015] Compared with the prior art, the present invention has the following beneficial effects:

[0016] The dual-planetary hybrid power system with a shared ring gear provided by the present invention can realize multi-mode operation of the vehicle through only one brake component, one clutch component and a double-row compound planetary gear mechanism. The overall structure is simple, which is conducive to improving the compactness of the vehicle layout and reducing the production and manufacturing costs of the vehicle. At the same time, there are fewer meshing parts in the system, which is conducive to improving power transmission efficiency. At the same time, it can reduce the power level requirement for the motor, which is conducive to vehicle cost control. Multiple operating modes can ensure that the vehicle has good power and economy under various driving conditions such as low and high speeds, thereby helping to improve the comprehensive economy and power of the vehicle.

[0017] Other advantages, objects, and features of the present invention will be described in part in the following description and, in part, will be apparent to those skilled in the art upon examination of the following description or may be learned from practice of the present invention. The objects and other advantages of the present invention may be realized and obtained through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 The structure of the present invention is schematically shown Figure 1

[0019] Figure 2 The structure of the present invention is schematically shown Figure 2

[0020] Figure 3 The structure of the present invention is schematically shown Figure 3

[0021] Figure 4 The structure of the present invention is schematically shown Figure 4

[0022] Figure 5 The structure of the present invention is schematically shown Figure 5

[0023] Figure markings: 1-first planetary gear mechanism; 101-first planetary carrier; 101a-first input shaft; 101b-third input gear; 102-first sun gear; 102a-first input gear; 103-first inner ring gear; 104-first planetary gear I; 105-first planetary gear II; 2-second planetary gear mechanism; 201-second planetary carrier; 201a-output gear; 202-second sun gear; 202a-second input gear; 203-second inner ring gear; 204-first planetary gear II; 205-second planetary gear II; 3-engine; 301-gear I; 4-first motor; 401-first output gear; 5-second motor; 501-second output gear; 6-brake component; 7-clutch component; 8-power output shaft; 9-torsional vibration damper; 10-transmission gear; 11-differential. DETAILED DESCRIPTION

[0024] The following describes the embodiments of the present invention through specific examples, and those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the illustrations provided in the following embodiments are only used to illustrate the basic concept of the present invention. In the absence of conflict, the following embodiments and the features in the embodiments can be combined with each other.

[0025] See also Figure 1-5The present embodiment discloses a dual-planetary hybrid system with a shared ring gear, comprising: a dual-row compound planetary gear mechanism, comprising a first planetary gear mechanism 1 having a first planet carrier 101, a first sun gear 102, and a first inner ring gear 103; and a second planetary gear mechanism 2 having a second planet carrier 201, a second sun gear 202, and a second inner ring gear 203, wherein the second inner ring gear 203 is fixed to the first inner ring gear 103 as a whole; an engine 3, wherein the output end of the engine 3 is transmission-connected to the first planet carrier 101; and a first motor 4, wherein the output end of the first motor 4 is transmission-connected to the first planet carrier 101; and The output end is connected to the first sun gear 102 by transmission; the second motor 5, the output end of the second motor 5 is connected to the second sun gear 202 by transmission; the brake component 6 is used to control the locking or release of the first inner gear 103 and the second inner gear 203, and the brake component 6 is usually a brake; the clutch component 7 is used to control the connection or separation between the second sun gear 202 and the second planetary carrier 201, and the clutch component 7 is usually a clutch; the output mechanism, the input end of the output mechanism is connected to the second planetary carrier 201 by transmission and is used to transmit power to the wheels; here, The second inner ring gear 203 and the first inner ring gear 103 are embedded in a gear ring to form an integrated structure, that is, they share a gear ring, that is, the first inner ring gear 103 and the second inner ring gear 203 can realize synchronous rotation; the output mechanism here is generally a shaft-tooth transmission structure, the input end of the shaft-tooth transmission structure is connected to the second planetary carrier 201, and the output end of the shaft-tooth transmission structure transmits power to the differential 11, and then transmits it to the wheels through the half-shaft. Different layout designs can be adopted according to the layout requirements of the entire vehicle; it can be understood that the first planetary gear mechanism 1 here also includes a first sun gear 1 that is simultaneously meshed with the first sun gear 1 02 and the first inner gear ring 103, the first planetary gears are usually evenly distributed along the circumference of the first sun gear 102 and are provided in a plurality; the second planetary gear mechanism 2 also includes a second planetary gear meshed between the second sun gear 202 and the second inner gear ring 203, and the second planetary gears are evenly distributed along the circumference of the second sun gear 202 and are provided in a plurality; of course, it can also be understood that the hybrid system further includes a battery, a motor driver, etc., and the battery is electrically connected to the motor driver, the first motor 4 and the second motor 5. This part is the same as the existing dual-motor hybrid system and will not be repeated here;

[0026] The hybrid system in the above structure can achieve multi-mode operation of the vehicle through only one brake component 6, one clutch component 7 and a double-row compound planetary gear mechanism. The overall structure is simple, which is conducive to improving the compactness of the vehicle layout and reducing the production and manufacturing costs of the vehicle. At the same time, the system has fewer meshing parts, which is conducive to improving power transmission efficiency. At the same time, it can reduce the power level requirement of the motor, which is conducive to vehicle cost control (specifically: here, since the power of the second motor 5 can be output after deceleration and torque increase by the second planetary gear mechanism 2, thereby meeting the power requirements of climbing performance and acceleration performance on flat roads, at high speeds, the power of the second motor 5 can be directly output by the second planetary carrier 201 to ensure high-speed driving requirements. The second motor 5 can use a motor with a smaller peak torque to reduce dependence on the motor). Multiple operating modes (see below for details) can ensure that the vehicle has good power and economy under various driving conditions such as low and high speeds, thereby improving the comprehensive economy and power of the vehicle.

[0027] See Figure 1 、 Figure 2 and Figure 3 In this embodiment, the rotation axes of the first motor 4, the second motor 5, the first planetary carrier 101 and the second planetary carrier 201 are collinear; by arranging these four coaxially, the overall compactness is improved, especially arranging the first motor 4 and the second motor 5 on the same axis, which can effectively reduce the overall space occupied by the system in the lateral direction of the vehicle, facilitate adaptation to the layout on short-width vehicles, and improve the compactness of the vehicle layout.

[0028] See Figure 1 In this embodiment, the first motor 4 is arranged on the front side of the first planetary gear mechanism 1, and the second motor 5 is arranged on the rear side of the second planetary gear mechanism 2; the first planetary carrier 101 is coaxially provided with a first input shaft 101a, the first input shaft 101a extends forward and passes through the output shaft of the first motor 4, the first sun gear 102 is fixedly connected to the output shaft of the first motor 4, and the first input shaft 101a is transmission-connected to the engine 3; the output mechanism includes a power output shaft 8, the power output shaft 8 is coaxially fixedly provided on the second planetary carrier 201 and extends backward through the output shaft of the second motor 5, the second sun gear 202 is fixedly connected to the output shaft of the second motor 5; attached here Figure 1The left end is the front and the right end is the rear, that is, the side close to the engine is the front; specifically, the first input shaft 101a and the first planetary carrier 101 are of an integrated structure; it can be understood that the output shaft of the first motor 4 is designed as a hollow shaft for the first input shaft 101a to pass through; the first sun gear 102 and the output shaft of the first motor 4 are connected by a spline to achieve relative fixation between the two; the output shaft of the engine 3 is connected to the first input shaft 101a after passing through the torsional vibration damper 9, and can be connected to the first input shaft 101a by a coupling, a spline connection, etc. To achieve transmission connection; it can be understood that the output shaft of the second motor 5 is designed to be a hollow shaft for the power output shaft 8 to pass through, and the power output shaft 8 can be connected to the rear axle of the car to transmit power to the wheels; this structural design, through a reasonable layout, further improves the overall compactness of the system, and at the same time, the overall transmission chain of the system is short and the number of meshing parts is small, which is conducive to further reducing power waste and improving the comprehensive economic performance of the vehicle; this structural layout is particularly suitable for front-engine rear-wheel drive models, and the power output shaft 8 is directly output to the rear, and for front-engine rear-wheel drive models, the compactness is very high.

[0029] See Figure 2 In this embodiment, the first motor 4 is arranged on the front side of the first planetary gear mechanism 1, and the second motor 5 is arranged on the rear side of the second planetary gear mechanism 2; the first planetary carrier 101 is coaxially provided with a first input shaft 101a, the first input shaft 101a extends forward and passes through the output shaft of the first motor 4, the first sun gear 102 is fixedly connected to the output shaft of the first motor 4, and the first input shaft 101a is transmission-connected to the engine 3; the second sun gear 202 is fixedly connected to the output shaft of the second motor 5; the second planetary carrier 201 is fixedly provided with an output gear 201a, and the output mechanism includes a transmission gear 10 meshing with the output gear 201a; Here, the attached Figure 2The left end is the front and the right end is the rear, that is, the side close to the engine is the front; specifically, the first input shaft 101a and the first planetary carrier 101 are of an integrated structure; it can be understood that the output shaft of the first motor 4 is designed as a hollow shaft for the first input shaft 101a to pass through; the first sun gear 102 and the output shaft of the first motor 4 are relatively fixed by a spline connection; the output shaft of the engine 3 is connected to the first input shaft 101a after passing through the torsional vibration damper 8, and the transmission connection with the first input shaft 101a can be achieved by a coupling, a spline connection, etc.; the second sun gear 202 is connected to the first sun gear 203 and the second sun gear 204. The output shafts of the two motors 5 are relatively fixed by spline connection; the output gear 201a and the second planetary carrier 201 adopt an integrated structure; the transmission gear 10 is externally connected to the differential 11, and then transmits power to the wheels through the half-shaft; this structural design, through reasonable layout, further improves the overall compactness of the system. At the same time, the overall transmission chain of the system is short and the number of meshing parts is small, which is conducive to further reducing power waste and improving the comprehensive economic performance of the vehicle; this structural layout is particularly suitable for front-engine, front-wheel drive models, and the transmission gear 10 can output directly forward. For front-engine, front-wheel drive models, the compactness is very high.

[0030] See Figure 3 In this embodiment, the second motor 5 is arranged at the rear side of the second planetary gear mechanism 2, and the first motor 4 is arranged at the rear side of the second motor 5; the second sun gear 202 is fixedly connected to the output shaft of the second motor 5; the output shaft of the first motor 4 extends forward and passes through the output shaft of the second motor 5, and the first sun gear 102 is fixedly connected to the output shaft of the first motor 4; the second planetary carrier 201 is fixedly provided with an output gear 201a, and the output mechanism includes a transmission gear 10 meshing with the output gear 201a; Here, the attached Figure 3 The left end is the front and the right end is the rear, that is, the side close to the engine is the front; the second sun gear 202 and the output shaft of the second motor 5 are relatively fixed by a spline connection; it can be understood that the output shaft of the second motor 5 is designed to be a hollow shaft for the output shaft of the first motor 4 to pass through; the first sun gear 102 and the output shaft of the first motor 4 are relatively fixed by a spline connection; the output gear 201a and the second planetary carrier 201 adopt an integrated structure; the transmission gear 10 is externally connected to the differential 11, and then transmits power to the wheels through the half shaft; this structural design, through reasonable layout, further improves the overall compactness of the system, and at the same time, the overall transmission chain of the system is short and the number of meshing parts is small, which is conducive to further reducing power waste and improving the comprehensive economic performance of the vehicle; this structural layout is particularly suitable for front-engine front-wheel drive models, and the transmission gear 10 can output directly forward. For front-engine front-wheel drive models, the compactness is very high.

[0031] See Figure 1 , Figure 2 and Figure 3 In this embodiment, the output shaft of the engine 3 is coaxially arranged with the axis of the first planetary carrier 101; by arranging the engine 3 coaxially with the axis of the first planetary carrier 101, the compactness of the overall structural arrangement is further improved and the space occupied is reduced; in particular, the first motor 4, the first planetary gear mechanism 1, the second motor 5 and the second planetary gear mechanism 2 are coaxially arranged, and the overall arrangement is extremely compact, which greatly reduces the overall lateral arrangement space occupied.

[0032] See Figure 4 In this embodiment, the rotation axes of the first motor 4, the first planetary carrier 101 and the second planetary carrier 201 are collinear, and the second motor 5 is parallel to the rotation axis of the first motor 4; the first motor 4 is arranged on the rear side of the second planetary gear mechanism 2, and the output shaft of the first motor 4 extends forward and passes through the second planetary carrier 201 and the second sun gear 202 in sequence and is fixedly connected to the first sun gear 102; the second sun gear 202 is fixedly provided with a second input gear 202a, and the output shaft of the second motor 5 is fixedly connected with a second output gear 501 meshing with the second input gear 202a; the second planetary carrier 201 is fixedly provided with an output gear 201a, and the output mechanism includes a transmission gear 10 meshing with the output gear 201a; Here, the attached Figure 4 The left end is the front and the right end is the rear, that is, the side close to the engine 3 is the front; it is conceivable that the central axis of the second planetary carrier 201 and the second sun gear 202 is designed as a hollow shaft structure for the output shaft of the first motor 4 to pass through; the first sun gear 102 and the output shaft of the first motor 4 can be relatively fixed by spline connection; the second input gear 202a and the second sun gear 202 adopt an integrated structure; the output gear 201a and the second planetary carrier 201 adopt an integrated structure; the transmission gear 10 is externally connected to the differential 11, and then the power is transmitted to the wheels through the half shaft; this structure The structural design further improves the overall compactness of the system through reasonable layout. At the same time, the overall transmission chain of the system is short and the number of meshing parts is small, which is conducive to further reducing power waste and improving the overall economic performance of the vehicle. This structural layout is particularly suitable for front-engine, front-wheel drive vehicles. The transmission gear 10 can be externally connected to the differential 11 for forward output. For front-engine, front-wheel drive vehicles, the compactness is very high. At the same time, since the second motor 5 is parallel to the rotation axis of the first motor 4, it can be beneficial to reduce the layout size of the vehicle in the longitudinal direction, that is, the length of the second motor 5 is omitted; thus, it can be suitable for layout on shorter vehicles.

[0033] See Figure 4 In this embodiment, the output shaft of the engine 3 is coaxially arranged with the axis of the first planetary carrier 101; by arranging the engine 3 coaxially with the axis of the first planetary carrier 101, the compactness of the overall structural arrangement is further improved and the space occupied is reduced.

[0034] See Figure 5 In this embodiment, the rotation axes of the second motor 4, the first planetary carrier 101 and the second planetary carrier 201 are collinear, and the rotation axes of the first motor 4 and the second motor 5 are parallel; the second motor 5 is arranged on the rear side of the first planetary gear mechanism 2, and the output shaft of the second motor 5 extends forward and passes through the first sun gear 102 and is fixedly connected to the second sun gear 202; the first sun gear 102 is fixedly provided with a first input gear 102a, and the output shaft of the first motor 4 is fixedly connected with a first output gear 401 that meshes with the first input gear 102a; the first planetary carrier 101 is fixedly provided with a third input gear 101b that is transmission-connected to the output end of the engine 3; the second planetary carrier 201 is fixedly provided with an output gear 201a; Here, the attached Figure 5 The right end is the rear, that is, the side away from the engine is the rear; it can be thought that the central axis of the first sun gear 102 is designed to be a hollow structure for the output shaft of the second motor 5 to pass through; the first input gear 102a and the first sun gear 102 adopt an integrated structure; here, the output shaft of the engine 3 passes through the torque damper 9, and then passes through the gear I 301 to engage with the third input gear 101b; this structural design, through reasonable layout, further improves the overall compactness of the system, and at the same time, the overall transmission chain of the system is short and the number of meshing parts is small, which is conducive to further reducing power waste and improving the comprehensive economic performance of the vehicle; this structural layout is particularly suitable for front-engine front-wheel drive models, and the output gear 201a can be directly connected to the external differential 11 for forward output. For front-engine front-wheel drive models, the compactness is very high; at the same time, since the second motor 5 is parallel to the rotation axis of the first motor 4, it can be beneficial to reduce the layout size of the vehicle in the longitudinal direction, that is, the length of the first motor 4 is omitted; this can be suitable for the layout on models with shorter lengths.

[0035] See Figure 1-5 In this embodiment, the braking component 6 is a brake, and the clutch component 7 is a clutch; specifically, the clutch 7 can adopt a multi-plate wet clutch, the active part of the clutch, that is, the input end of the clutch 7 is arranged on the second sun gear 202, and the driven part of the clutch 7 is arranged on the second planetary carrier 201, and the engagement or separation between the second sun gear 202 and the second planetary carrier 201 is achieved by controlling the engagement or separation of the active part and the driven part of the clutch; the brake 6 is connected to the first inner gear 103 or the second inner gear 203, and the brake 6 can adopt a disc brake, the brake disc of the brake 6 is fixed on the first inner gear 103 or the second inner gear 203, and the brake caliper part of the brake 6 is arranged on the vehicle frame or other fixed structure, and the brake caliper clamps the brake disc through the brake pad to achieve braking; by adopting the brake and the clutch, the structure is mature and the structural reliability is good.

[0036] Figures 1 to 5 The structures in the table can all work in the following working modes:

[0037] Pure electric working mode: the brake component 6 is engaged, the clutch component 7 is disengaged, the battery is discharged to the second motor 5, and the second motor 5 is in an electric state; in this mode, it can meet the use of working conditions such as congested urban roads, low-speed driving, and frequent braking, thereby ensuring the power economy in this mode; at the same time, in this mode, the power of the second motor 5 is decelerated and torque-increased by the second planetary gear mechanism 2, and then directly output to the transmission mechanism by the second planetary carrier 201, and then transmitted to the wheels, which can meet the use requirements of climbing performance and starting acceleration, and can improve the power performance of the pure electric mode; at the same time, the engagement of the brake component 6 can prevent power from being transmitted to the first planetary mechanism, thereby avoiding large weak magnetic losses in the first motor 4.

[0038] Extended-range mode: the brake component 6 is engaged, the clutch component 7 is disengaged, the engine 3 works and outputs power to the first motor 4, the first motor 4 is in a power generation state, the first motor 4 transmits electrical energy to the second motor 5 and the battery, and the second motor 5 is in an electric state; in this mode, the first inner ring gear 103 and the second inner ring gear 203 are both locked, the second motor 5 directly drives the second sun gear 202 to rotate, and the power is transmitted to the second planetary carrier 201 to obtain a deceleration torque, and then the power is transmitted to the wheels by the output mechanism; in this mode, when the battery is insufficient, the engine 3 can work to supplement the power supply to ensure the long-distance driving needs of the vehicle.

[0039] In this embodiment, a hybrid mode is also included, and in the hybrid mode: the brake component 6 is disengaged, the clutch component 7 is engaged, the engine 3 is working, the first motor 4 is in a power generation or electric state, and the second motor 5 is in a power generation or electric state; the output power of the engine 3 and the first motor 4 is coupled in the first planetary mechanism 1 and transmitted to the second inner ring gear 203 through the first inner ring gear 103; the output power of the second motor 5 is coupled with the output power of the engine 3 and the first motor 4 in the second planetary mechanism 2, and finally output through the second planetary carrier 201; in this mode, according to the output power demand of the vehicle, the engine 3, the first motor 4, the second motor 5 and the first planetary mechanism are used to generate the power. The coordinated work of the planetary gear mechanism 1 ensures that the engine is always in a high-efficiency working range. The coordinated adjustment principle here is the same as that of the existing single-row planetary gear power split system, that is, by adjusting the torque of the second motor 5 and the speed of the first motor 4, the engine is always in a high-efficiency working range. It will not be repeated here; in this way, the fuel economy in the hybrid mode is guaranteed, and the comprehensive power and economy of the whole vehicle are improved; and because the second motor 5 does not slow down through the second planetary gear mechanism 2 at this time, it directly drives the wheels to travel, which is suitable for the vehicle's high-speed cruising mode. The engine 3 can have better fuel economy, which is conducive to reducing battery usage and increasing battery life, thereby improving the comprehensive economy of the whole vehicle.

[0040] This embodiment also includes a parking mode, in which: the brake component 6 is engaged, the clutch component 7 is engaged, and the engine 3 can optionally drive the first motor to generate power while the vehicle is parked. In this mode, the vehicle is stationary, and depending on the power reserve, the engine 3 can be started to complete charging, or not started to charge, and only the parking function can be achieved. It is also applicable to plug-in hybrid systems, which use an external charging station for charging. In this mode, due to the engagement of the clutch component 7, brake energy recovery can be better achieved. If the vehicle is in a non-emergency braking situation, the vehicle speed is above a certain limit, and the required torque at this time is less than the maximum braking torque that the second motor 5 can provide, the braking force is entirely provided by the second motor 5, converting mechanical energy into electrical energy and storing it in the battery. If the vehicle is in a non-emergency braking situation, the vehicle speed is above a certain limit, and the required torque at this time is greater than the maximum braking torque that the second motor 5 can provide, a portion of the braking force is provided by the second motor 5, converting mechanical energy into electrical energy and storing it in the battery, while the remaining portion of the braking force is provided by traditional mechanical braking.

[0041] The combination of the above modes effectively improves the vehicle's overall economy and power.

[0042] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not limiting. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the purpose and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A double planetary gear hybrid system with a shared ring gear, characterized in that: include: A double-row compound planetary gear mechanism, comprising a first planetary gear mechanism (1) having a first planet carrier (101), a first sun gear (102) and a first inner gear ring (103), and a second planetary gear mechanism (2) having a second planet carrier (201), a second sun gear (202) and a second inner gear ring (203), wherein the second inner gear ring (203) is fixed to the first inner gear ring (103) as a whole; An engine (3), wherein an output end of the engine (3) is drivingly connected to the first planet carrier (101); A first motor (4), wherein an output end of the first motor (4) is drivingly connected to a first sun gear (102); A second motor (5), wherein an output end of the second motor (5) is drivingly connected to a second sun gear (202); A braking component (6) for operating the locking or releasing of the first inner gear ring (103) and the second inner gear ring (203); A clutch component (7) for controlling the coupling or separation between the second sun gear (202) and the second planet carrier (201); An output mechanism, wherein an input end of the output mechanism is drivingly connected to the second planet carrier (201) and is used to transmit power to wheels.

2. The double planetary gear hybrid system with a common ring gear according to claim 1, characterized in that: The rotation axes of the first motor (4), the second motor (5), the first planet carrier (101) and the second planet carrier (201) are collinear.

3. The double planetary gear hybrid system with a common ring gear according to claim 2, characterized in that: The first motor (4) is arranged on the front side of the first planetary gear mechanism (1), and the second motor (5) is arranged on the rear side of the second planetary gear mechanism (2); a first input shaft (101a) is coaxially arranged on the first planetary carrier (101), the first input shaft (101a) extends forward and passes through the output shaft of the first motor (4), the first sun gear (102) is fixedly connected to the output shaft of the first motor (4), and the first input shaft (101a) is transmission-connected to the output end of the engine (3); the output mechanism comprises a power output shaft (8), the power output shaft (8) is coaxially fixedly arranged on the second planetary carrier (201) and extends backward through the output shaft of the second motor (5), and the second sun gear (202) is fixedly connected to the output shaft of the second motor (5).

4. The double planetary gear hybrid system with a common ring gear according to claim 2, characterized in that: The first motor (4) is arranged at the front side of the first planetary gear mechanism (1), and the second motor (5) is arranged at the rear side of the second planetary gear mechanism (2); a first input shaft (101a) is coaxially arranged on the first planetary carrier (101), the first input shaft (101a) extends forward and passes through the output shaft of the first motor (4), the first sun gear (102) is fixedly connected to the output shaft of the first motor (4), and the first input shaft (101a) is transmission-connected to the output end of the engine (3); the second sun gear (202) is fixedly connected to the output shaft of the second motor (5); an output gear (201a) is fixedly arranged on the second planetary carrier (201), and the output mechanism comprises a transmission gear (10) meshing with the output gear (201a).

5. The double planetary gear hybrid system with a common ring gear according to claim 2, characterized in that: The second motor (5) is arranged at the rear side of the second planetary gear mechanism (2), and the first motor (4) is arranged at the rear side of the second motor (5); the second sun gear (202) is fixedly connected to the output shaft of the second motor (5); the output shaft of the first motor (4) extends forward and passes through the output shaft of the second motor (5), and the first sun gear (102) is fixedly connected to the output shaft of the first motor (4); an output gear (201a) is fixedly provided on the second planetary carrier (201), and the output mechanism comprises a transmission gear (10) meshing with the output gear (201a).

6. The double planetary gear hybrid system with a common ring gear according to any one of claims 1 to 5, characterized in that: The output shaft of the engine (3) is coaxially arranged with the axis of the first planet carrier (101).

7. The double planetary gear hybrid system with a common ring gear according to claim 1, characterized in that: The rotation axes of the first motor (4), the first planetary carrier (101) and the second planetary carrier (201) are collinear, and the second motor (5) is parallel to the rotation axis of the first motor (4); the first motor (4) is arranged at the rear side of the second planetary gear mechanism (2), and the output shaft of the first motor (4) extends forward and passes through the second planetary carrier (201) and the second sun gear (202) in sequence and is then fixedly connected to the first sun gear (102); the second sun gear (202) is fixedly provided with a second input gear (202a), and the output shaft of the second motor (5) is fixedly connected with a second output gear (501) meshing with the second input gear (202a); the second planetary carrier (201) is fixedly provided with an output gear (201a), and the output mechanism comprises a transmission gear (10) meshing with the output gear (201a).

8. The double planetary gear hybrid system with a common ring gear according to claim 7, characterized in that: The output shaft of the engine (3) is coaxially arranged with the axis of the first planet carrier (101).

9. The double planetary gear hybrid power system with a common ring gear according to claim 1, characterized in that: The rotation axes of the second motor (5), the first planetary carrier (101) and the second planetary carrier (201) are collinear, and the rotation axes of the first motor (4) and the second motor (5) are parallel; the second motor (5) is arranged at the rear side of the first planetary gear mechanism (2), and the output shaft of the second motor (5) extends forward and passes through the first sun gear (102) and is fixedly connected to the second sun gear (202); the first sun gear (102) is fixedly provided with a first input gear (102a), and the output shaft of the first motor (4) is fixedly connected with a first output gear (401) meshing with the first input gear (102a); the first planetary carrier (101) is fixedly provided with a third input gear (101b) drivingly connected to the output end of the engine (3); and the second planetary carrier (201) is fixedly provided with an output gear (201a).

10. The double planetary gear hybrid system with a common ring gear according to any one of claims 1 to 9, characterized in that: The braking component (6) is a brake, and the clutch component (7) is a clutch.

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