Planet row hybrid transmission system and vehicle

Abstract

The invention provides a planet row hybrid transmission system and a vehicle. The planet row hybrid transmission system comprises an engine, a first motor and a transmission. The transmission comprises an input shaft, an output shaft and a planet row, the input shaft is arranged on a planet carrier of the planet row and used for receiving power input of an engine. The first motor is in transmission connection with a sun gear of the planet row; a speed change mechanism is arranged between a gear ring of the planet row and the output shaft, and the speed change mechanism can change the transmission ratio between the gear ring and the output shaft under the control of the power switching device. According to the planet row hybrid transmission system, transmission among the input shaft, the output shaft and the first motor is formed through the planet row, power input to the input shaft by the engine can be flexibly distributed to the output shaft and the first motor through the planet row, and the engine can be kept in an efficient operation state; and favorable conditions are provided for efficient operation of the engine.

Description

Technical Field

[0001] The present invention relates to the technical field of new energy vehicles, and in particular to a planetary gearbox hybrid transmission system. In addition, the present invention also relates to a vehicle. Background Art

[0002] Vehicles powered by fuel engines cause a lot of air pollution, so people have developed pure electric vehicles. However, due to factors such as battery performance and vehicle mileage, the development of pure electric vehicles has been greatly restricted. In view of this, hybrid vehicles are developing rapidly because they can better solve the above problems. A hybrid vehicle is a vehicle that uses multiple energy sources, usually a conventional engine that uses liquid fuel and an electric motor that uses electrical energy to drive the vehicle.

[0003] In existing hybrid vehicles, the hybrid transmission needs to be connected to the engine and the motor at the same time, and connected to the front or rear axle drive of the vehicle. The power of the engine is generally connected to the single shaft and the dual shaft through a dual clutch, part of the power is output by the single shaft, and part of the power is output by the dual shaft. The power output of the matching motor also needs to be transmitted to the single shaft or the dual shaft. In order to realize the four-wheel drive function of the vehicle, it is generally equipped with multiple motors or a complex transmission structure, resulting in the power system occupying a large space.

[0004] When the entire power system is applied to a vehicle, due to the setting of multiple drive components and multiple sets of speed transmission mechanisms, the hybrid transmission, engine and motor need to occupy a large amount of space in the vehicle cabin. Due to the complexity of the structure and the diversity of the transmission paths, the entire hybrid transmission system occupies a large space in the front and rear and left and right directions of the vehicle, while the space inside the vehicle cabin is limited, and air-conditioning systems, batteries, shock absorbers and other components need to be arranged.

[0005] Moreover, the existing hybrid transmissions mostly adopt the transmission form of gear sets, especially in the multi-speed transmission structure, which requires multiple sets of transmission gears, resulting in a relatively complex overall setting of the transmission structure and requiring a larger layout space, which further increases the difficulty of arranging the power system in the cabin. At the same time, the existing hybrid transmissions mostly adopt the transmission form of gear sets, and the transmission performance is relatively simple. The engine needs to adjust its power output according to the power demand of the vehicle. When the vehicle is at a low speed, if you want to keep the engine in an efficient power output state, you must switch the cumbersome power transmission path to distribute the engine's power transmission to the engine. Not only does it increase the manufacturing cost of the transmission, but the transmission efficiency will also decrease. Summary of the invention

[0006] In view of this, the present invention aims to propose a planetary gear hybrid transmission system to provide favorable conditions for the efficient operation of the engine.

[0007] To achieve the above object, the technical solution of the present invention is achieved as follows:

[0008] A planetary gear hybrid transmission system includes an engine, a first motor, and a transmission;

[0009] The transmission comprises an input shaft and an output shaft arranged in parallel, and a planetary gear;

[0010] The input shaft is arranged on the planetary carrier of the planetary gear set, and is used to receive the power input of the engine; the first motor is connected to the sun gear of the planetary gear set; a speed change mechanism is provided between the ring gear of the planetary gear set and the output shaft, and the speed change mechanism can change the transmission ratio between the ring gear and the output shaft under the control of the power switching device.

[0011] Furthermore, the planetary hybrid transmission system also includes a second motor transmission-connected to the output shaft.

[0012] Furthermore, the second motor is drivingly connected to the output shaft via a transmission gear set, and / or the sun gear is directly fixed on the shaft of the first motor.

[0013] Furthermore, the driving shafts of the second motor and the wheels are respectively connected to the two ends of the output shaft.

[0014] Furthermore, the power output shaft of the engine is connected to the input shaft through a clutch transmission.

[0015] Furthermore, the speed change mechanism adopts a gear transmission structure.

[0016] Furthermore, the speed change mechanism includes a first gear set and a second gear set; the power switching device is arranged between the first gear set and the second gear set, and the power switching device is used to selectively connect the first gear set or the second gear set between the ring gear and the output shaft.

[0017] Furthermore, the power switching device adopts a synchronizer.

[0018] Furthermore, the first gear set includes a first driving gear fixed on the ring gear, and a first driven gear sleeved on the output shaft, the second gear set includes a second driving gear fixed on the ring gear, and a second driven gear sleeved on the output shaft, and the synchronizer is arranged on the output shaft between the first driven gear and the second driven gear.

[0019] Compared with the prior art, the present invention has the following advantages:

[0020] The planetary gear hybrid transmission system of the present invention forms a transmission between an input shaft, an output shaft and a first motor through a planetary gear. The power input to the input shaft by the engine can be flexibly distributed to the output shaft and the first motor through the planetary gear. The power distributed to the output shaft by the ring gear of the planetary gear is used to drive the wheels to operate. The power distributed to the first motor by the sun gear of the planetary gear can drive the first motor to operate and generate electricity to replenish the battery pack of the vehicle. In this case, the engine can be maintained in a state of efficient operation, and the transmission can flexibly adjust the distribution of power according to the power demand of the drive shaft of the wheels, thereby providing favorable conditions for the efficient operation of the engine.

[0021] At the same time, the transmission ratio from the ring gear to the output shaft can be changed by the speed change mechanism and power switching device arranged between the ring gear and the output shaft, so that the transmission has a multi-speed regulation function in the engine drive mode.

[0022] Another object of the present invention is to provide a vehicle, which is equipped with the planetary hybrid transmission system and the auxiliary power system described in the present invention, and the planetary hybrid transmission system and the auxiliary power system can interchangeably drive the wheels of the front axle and the rear axle of the vehicle respectively.

[0023] The vehicle of the present invention has the technical advantages possessed by the above-mentioned vehicles, and also has good four-wheel drive performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The accompanying drawings, which constitute part of the present invention, are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention. The directional terms such as front and back, up and down, etc. involved therein are only used to indicate relative positional relationships and do not constitute improper limitations on the present invention. In the accompanying drawings:

[0025] Figure 1 A schematic diagram of the system structure of a planetary gear hybrid transmission system according to Embodiment 1 of the present invention;

[0026] Figure 2 A schematic diagram of the system configuration of another configuration of the planetary gear hybrid transmission system according to the first embodiment of the present invention;

[0027] Figure 3 It is a schematic diagram of the power transmission path of the planetary gear hybrid transmission system in the engine I gear direct drive mode according to the first embodiment of the present invention;

[0028] Figure 4 A schematic diagram of the power transmission path of the planetary gear hybrid transmission system in the engine II gear direct drive mode according to the first embodiment of the present invention;

[0029] Figure 5 A schematic diagram of a power transmission path of a planetary gear hybrid transmission system in pure electric mode according to Embodiment 1 of the present invention;

[0030] Figure 6 A schematic diagram of a power transmission path of a planetary gear hybrid transmission system in series mode according to Embodiment 1 of the present invention;

[0031] Figure 7 A schematic diagram of a power transmission path of a planetary gear hybrid transmission system in a hybrid mode according to a first embodiment of the present invention;

[0032] Figure 8 It is a structural schematic diagram of a single motor configuration of an auxiliary power system of a vehicle according to a second embodiment of the present invention;

[0033] Fig. 9 It is a structural schematic diagram of another single motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0034] Fig.10 It is a structural schematic diagram of another single motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0035] Fig.11 It is a structural schematic diagram of a dual-motor configuration of an auxiliary power system according to a second embodiment of the present invention;

[0036] Fig.12 It is a structural schematic diagram of another dual-motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0037] Fig.13 It is a structural schematic diagram of another dual-motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0038] Fig.14 It is a structural schematic diagram of another dual-motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0039] Fig.15 It is a structural schematic diagram of another dual-motor configuration of the auxiliary power system according to the second embodiment of the present invention;

[0040] Fig.16 This is a structural schematic diagram of another dual-motor configuration of the auxiliary power system described in the second embodiment of the present invention.

[0041] Description of reference numerals:

[0042] 1. Engine; 10. Power output shaft;

[0043] 21. first motor; 22. second motor; 220. transmission gear set;

[0044] 30. Clutch; 31. Synchronizer;

[0045] 4. Input shaft; 5. Output shaft; 501. First driven gear; 502. Second driven gear;

[0046] 6. Battery pack; 70. Sun gear; 71. Planet carrier; 711. Planet gear; 72. Ring gear; 721. First driving gear; 722. Second driving gear;

[0047] 8. Auxiliary drive motor; 800. Intermediate shaft; 81. Motor shaft gear; 811. First motor shaft gear; 812. Second motor shaft gear;

[0048] 82, driving shaft gear; 821, first driving shaft gear; 822, second driving shaft gear;

[0049] 831, first intermediate shaft gear; 832, second intermediate shaft gear; 833, third intermediate shaft gear;

[0050] 841, parallel synchronizer; 842, gear shift synchronizer; 85, auxiliary differential;

[0051] 9. Wheel; 90. Drive shaft; 91. Differential. DETAILED DESCRIPTION

[0052] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments may be combined with each other.

[0053] In the description of the present invention, it should be stated that if terms indicating directions or positional relationships such as "up, down, left, right, front, back, inside, outside" appear, they are based on the directions or positional relationships shown in the drawings and are only for the convenience of describing the present invention. They do not indicate or imply that the device or element referred to must have a specific direction, be constructed or operate in a specific direction. Therefore, they cannot be understood as limitations on the present invention.

[0054] In addition, in the description of the present invention, unless otherwise clearly defined, the terms "installed", "connected", "connection", and "connector" should be understood in a broad sense. For example, the connection can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediate medium, or a connection between the two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood in combination with specific circumstances. The limiting terms such as "first, second, A, B, C, D" that appear in the description of the present invention are only for distinguishing similar features of different positions, affiliations or uses, so as to achieve the purpose of avoiding ambiguity and confusion in the description, and cannot be understood as indicating or implying relative importance.

[0055] The present invention will be described in detail below with reference to the accompanying drawings and in conjunction with embodiments.

[0056] Embodiment 1

[0057] This embodiment relates to a planetary gear hybrid transmission system, which can provide favorable conditions for the efficient operation of the engine 1; an exemplary system structure is as follows Figure 1 or Figure 2 shown.

[0058] In general, the planetary gearbox hybrid transmission system includes an engine 1, a first motor 21, and a transmission; the transmission includes an input shaft 4 and an output shaft 5 arranged in parallel, and a planetary gearbox. The input shaft 4 is arranged on a planetary gearbox carrier 71 for receiving power input from the engine 1; the first motor 21 is connected to the sun gear 70 of the planetary gearbox; a speed change mechanism is arranged between the ring gear 72 of the planetary gearbox and the output shaft 5, and the speed change mechanism can change the transmission ratio between the ring gear 72 and the output shaft 5 under the control of the power switching device.

[0059] At the same time, in addition to using Figure 1 In addition to the configuration shown, Figure 2 As shown, the planetary gearbox hybrid transmission system is equipped with a second motor 22. It should be noted that when the second motor 22 is not equipped, the first motor 21 can be used as a drive motor to output power, or receive power input from the engine 1 and be used as a generator; after the second motor 22 is equipped, the second motor 22 can be used as a drive motor to be connected to the output shaft 5 to provide power, and the first motor 21 can only be used as a generator.

[0060] When the first motor 21 and the second motor 22 are specifically configured, the transmission mode of the first motor 21 and the sun gear 70, and the transmission mode of the second motor 22 and the output shaft 5 can of course be flexibly set. For example, the second motor 22 can be directly set on the output shaft 5, or the shaft body of the second motor 22 and the output shaft 5 can be connected through a transmission structure. In this embodiment, the second motor 22 is connected to the output shaft 5 through a transmission gear set 220; the sun gear 70 is directly fixed on the shaft body of the first motor 21. The second motor 22 and the output shaft 5 adopt the form of gear transmission, which can not only obtain the required transmission ratio by setting a suitable gear size and number of teeth; but also has reliable transmission performance and high transmission efficiency. The sun gear 70 of the planetary gear is directly fixed on the motor shaft of the first motor 21, which can shorten the length of the transmission path, reduce mechanical loss, and improve power generation efficiency.

[0061] Furthermore, the arrangement of the components on the output shaft 5 of the present embodiment is preferably in the following form: the second motor 22 and the drive shaft 90 of the wheel 9 are respectively connected to the two ends of the output shaft 5; the speed change mechanism (i.e., the first driven gear 501 and the second driven gear 502 described below) for transmission with the ring gear 72 is arranged in the middle of the output shaft 5. When the speed change mechanism is arranged on the output shaft 5, the power output end of the output shaft 5 is connected to the differential 91 of the drive shaft 90, and the second motor 22 is arranged at the other end of the output shaft 5, so that the arrangement of the components on the output shaft 5 can be more reasonable, and the mutual influence between the components during assembly and arrangement can be avoided.

[0062] Still Figure 2 As shown, in order to achieve good power on-off control between the power output shaft 10 and the input shaft 4, a power cut-off control mechanism should be provided between the power output shaft 10 and the input shaft 4. In this embodiment, the power output shaft 10 of the engine 1 is connected to the input shaft 4 through a clutch 30. The clutch 30 is used as the power cut-off control mechanism between the power output shaft 10 and the input shaft 4, which has the advantages of mature and reliable technology and easy configuration.

[0063] There are of course many design schemes for the speed change mechanism between the planetary gear and the output shaft 5. In this embodiment, the speed change mechanism adopts a gear transmission structure. The speed change mechanism adopts the form of gear transmission, which can not only obtain the required transmission ratio by setting a suitable gear size and number of teeth, but also has reliable transmission performance and high transmission efficiency.

[0064] Specifically, the speed change mechanism includes a first gear set and a second gear set; a power switching device is provided between the first gear set and the second gear set, and the power switching device is used to selectively connect the first gear set or the second gear set between the ring gear 72 and the output shaft 5. By providing two sets of gear structures with different transmission ratios and providing a power switching device between the two sets of gear structures, a certain set of gear structures (the first gear set or the second gear set) can be timely connected between the planetary gear and the output shaft 5 to achieve the transmission of the required gear, so that the vehicle can achieve different gears in the engine drive mode.

[0065] The power switching device preferably adopts a synchronizer 31 ; the synchronizer 31 is mature and reliable in technology and has good shift controllability.

[0066] Based on the above arrangement, the first gear set of the present embodiment includes a first driving gear 721 fixed on the gear ring 72, and a first driven gear 501 sleeved on the output shaft 5, the first driving gear 721 is meshed and connected with the first driven gear 501; the second gear set includes a second driving gear 722 fixed on the gear ring 72, and a second driven gear 502 sleeved on the output shaft 5, the second driving gear 722 is meshed and connected with the second driven gear 502. Correspondingly, the synchronizer 31 is arranged on the output shaft 5 between the first driven gear 501 and the second driven gear 502.

[0067] The first driven gear 501 and the second driven gear 502 on the output shaft 5 are in a set form, and the synchronizer 31 is set on the output shaft 5, which can selectively engage the first driven gear 501 or the second driven gear 502, so that the access control of the first gear set or the second gear set can be smoothly realized to complete the gear shifting operation; it has the advantages of simple structure and reliable performance.

[0068] Through the above configuration, the planetary gear hybrid transmission system of this embodiment can drive the vehicle in multiple driving modes such as engine I gear direct drive mode, engine II gear direct drive mode, pure electric mode, series mode, hybrid mode, idle power generation mode, energy recovery mode, etc. Figure 2 Based on the planetary hybrid transmission system shown, the power transmission in each drive mode is explained.

[0069] Specifically, in the engine 1st gear direct drive mode, if Figure 3 As shown, the clutch 30 is in the engaged state, the engine 1 is running, and the power output from the power output shaft 10 reaches the input shaft 4 and the planetary carrier 71 through the clutch 30. Under the coupling transmission of the planetary gear 711 of the planetary gear row, the sun gear 70 and the ring gear 72 are driven to transmit at the same time. A part of the power drives the first motor 21 to operate and generate electricity through the sun gear 70 to replenish the battery pack 6 of the vehicle; the other part of the power reaches the output shaft 5 through the first driving gear 721 and the first driven gear 501, driving the output shaft 5 to operate; the power is then passed from the output shaft 5 through the differential 91 and the drive shaft 90 in sequence to drive the wheels 9 to rotate, thereby driving the vehicle to move. At this moment, the second motor 22 is not running, and the vehicle is driven only by the engine 1.

[0070] In the engine Ⅱ gear direct drive mode, if Figure 4As shown, the clutch 30 is in the engaged state, the engine 1 is running, and the power output from the power output shaft 10 reaches the input shaft 4 and the planetary carrier 71 through the clutch 30. Under the coupling transmission of the planetary gear 711 of the planetary gear row, the sun gear 70 and the ring gear 72 are driven to transmit at the same time. A part of the power drives the first motor 21 to operate and generate electricity through the sun gear 70 to replenish the battery pack 6 of the vehicle; the other part of the power reaches the output shaft 5 through the second driving gear 722 and the second driven gear 502, driving the output shaft 5 to operate; the power then passes through the differential 91 and the drive shaft 90 in sequence from the output shaft 5 to drive the wheels 9 to rotate, thereby driving the vehicle to move. At this moment, the second motor 22 is not running, and the vehicle is driven only by the engine 1.

[0071] In pure electric mode, Figure 5 As shown, the clutch 30 is in a disconnected state, the engine 1 and the first motor 21 are not running, the second motor 22 is running, and the transmission gear set 220 transmits power to the output shaft 5, and the power is then transmitted from the output shaft 5 through the differential 91 and the drive shaft 90 in sequence to drive the wheels 9 to rotate, thereby driving the vehicle to move.

[0072] In series mode, if Figure 6 As shown, the clutch 30 is in the engaged state, the engine 1 is running, and the power output from the power output shaft 10 reaches the input shaft 4 and the planetary carrier 71 through the clutch 30. Under the coupling transmission of the planetary gear 711 of the planetary row, the sun gear 70 is driven to drive. The power drives the first motor 21 to operate and generate electricity through the sun gear 70 to replenish the battery pack 6 of the vehicle; at the same time, the battery pack 6 supplies power to the first motor 21, and the first motor 21 operates and transmits power to the output shaft 5 through the transmission gear set 220. The power is then passed from the output shaft 5 to the differential 91 and the drive shaft 90 in sequence to drive the wheels 9 to rotate, thereby driving the vehicle to move. This mode is equivalent to the operation mode of the extended-range vehicle.

[0073] In hybrid mode, Figure 7 As shown, the clutch 30 is in the engaged state, the engine 1 and the second motor 22 are both running, and the power output shaft 10 drives the first motor 21 to operate and generate electricity to replenish the battery pack 6 of the vehicle through the clutch 30, the input shaft 4 and the sun gear 70 of the planetary gear, while the power output shaft 10 also drives the output shaft 5 to operate through the first gear set or the second gear set. At the same time, the power provided by the second motor 22 reaches the output shaft 5 through the transmission gear set 220, and the power is then passed from the output shaft 5 through the differential 91 and the drive shaft 90 in sequence to drive the wheels 9 to rotate, thereby driving the vehicle to move. At this moment, the engine 1 and the second motor 22 jointly provide power to the vehicle to drive the vehicle to move.

[0074] The power transmission conditions in the idle power generation mode and the energy recovery mode can be learned by referring to the power transmission principles of the above-mentioned driving modes, which will not be elaborated here.

[0075] In summary, the planetary gear hybrid transmission system of this embodiment forms transmission between the input shaft 4, the output shaft 5 and the first motor 21 through the planetary gear. The power input to the input shaft 4 by the engine 1 can be flexibly distributed to the output shaft 5 and the first motor 21 through the planetary gear. The power distributed to the output shaft 5 by the ring gear 72 of the planetary gear is used to drive the wheels 9 to operate, and the power distributed to the first motor 21 by the sun gear 70 of the planetary gear can drive the first motor 21 to operate and generate electricity to replenish the battery pack 6 of the vehicle; in this case, the engine 1 can be maintained in a state of efficient operation, and the transmission can flexibly allocate the power distribution according to the power demand of the drive shaft 90 of the wheel 9, which provides favorable conditions for the efficient operation of the engine 1. At the same time, through the speed change mechanism and power switching device set between the ring gear 72 and the output shaft 5, the transmission ratio from the ring gear 72 to the output shaft 5 can be changed, so that the transmission has a multi-speed regulation function in the engine drive mode.

[0076] Embodiment 2

[0077] This embodiment relates to a vehicle, which is equipped with the planetary gearbox hybrid transmission system and the auxiliary power system provided in the first embodiment. The planetary gearbox hybrid transmission system is used as the main power system of the vehicle in conjunction with the auxiliary power system to interchangeably drive the front and rear axle wheels 9 of the vehicle. The various exemplary structures of the auxiliary power system are as follows: Figures 8 to 16 shown.

[0078] It should be noted that the planetary gear hybrid transmission system and the auxiliary power system mentioned above can interchangeably drive the wheels 9 of the front axle and the rear axle of the vehicle respectively, which means that the planetary gear hybrid transmission system can be used to drive the front axle, and the auxiliary power system can be used to drive the rear axle; or the two can be swapped, and the planetary gear hybrid transmission system can be used to drive the rear axle, and the auxiliary power system can be used to drive the front axle. The vehicle of this embodiment has the technical advantages of the two-speed planetary gear, two-speed planetary gear, two-speed planetary gear hybrid transmission and the planetary gear hybrid transmission system, and can make the vehicle have the performance of four-wheel drive.

[0079] Furthermore, the auxiliary power system may be configured with only one motor or two motors; the motor configured in the auxiliary power system may be powered by the vehicle battery pack 6. When configured with one motor, the auxiliary power system includes an auxiliary drive motor 8 and an auxiliary differential 85 disposed between the drive shafts 90 of the left and right wheels 9, and the auxiliary drive motor 8 is connected to the auxiliary differential 85 directly or through a transmission mechanism having a plurality of gears.

[0080] When a secondary drive motor 8 is configured, Figure 8 As shown, the auxiliary drive motor 8 and the auxiliary differential 85 can be integrated, and the auxiliary drive motor 8 drives the auxiliary differential 85 to drive the drive shafts 90 on both sides to rotate. Fig.10 , Fig.11 As shown, the auxiliary drive motor 8 is connected to the auxiliary differential 85 between the two side drive shafts 90 through a set of speed change mechanisms. The specific configuration of the speed change mechanism can be flexibly set according to the transmission and speed change requirements between the auxiliary drive motor 8 and the wheels 9. The auxiliary power system adopts a driving mode of a single motor and an auxiliary differential 85, which has the advantages of simple structure, small number of motors, etc., and can reduce the configuration cost of the auxiliary power system.

[0081] For example, see Fig. 9 A secondary intermediate shaft 800 is arranged between the motor shaft of the secondary drive motor 8 and the secondary differential 85, a motor shaft gear 81 is arranged on the motor shaft of the secondary drive motor 8, a first intermediate shaft gear 831 and a second intermediate shaft gear 832 are arranged at intervals on the secondary intermediate shaft 800, and a drive shaft gear 82 is arranged on the secondary differential 85; wherein, the motor shaft gear 81 is meshed and connected with the first intermediate shaft gear 831, and the second intermediate shaft gear 832 is meshed and connected with the drive shaft gear 82, forming a speed transmission path, which can achieve a stable speed transmission effect.

[0082] For example, you can refer to Fig.10 A secondary intermediate shaft 800 is arranged between the motor shaft of the secondary drive motor 8 and the secondary differential 85, a first motor shaft gear 811 and a second motor shaft gear 812 are arranged on the motor shaft of the secondary drive motor 8 at intervals, a first intermediate shaft gear 831, a second intermediate shaft gear 832 and a third intermediate shaft gear 833 are arranged on the secondary intermediate shaft 800 at intervals, and a driving shaft gear 82 is arranged on the secondary differential 85; wherein, the first motor shaft gear 811 is meshed and connected with the first intermediate shaft gear 831, the second motor shaft gear 812 is meshed and connected with the second intermediate shaft gear 832, and the third intermediate shaft gear 833 is meshed and connected with the driving shaft gear 82. At this moment, a gear shift synchronizer 842 is arranged on the secondary intermediate shaft 800 between the first intermediate shaft gear 831 and the second intermediate shaft gear 832, which can switch gears, form two speed transmission paths with different transmission ratios of the speed change mechanism, and can perform two-speed speed regulation drive on the wheels 9 to achieve a stable speed transmission effect.

[0083] When two auxiliary drive motors 8 are configured, the structure of the auxiliary power system of this embodiment is as follows: Figures 11 to 16As shown, the auxiliary power system has two auxiliary drive motors 8, and the two auxiliary drive motors 8 are respectively arranged corresponding to the drive shafts 90 of the wheels 9 on the left and right sides. The two auxiliary drive motors 8 are respectively directly arranged on the drive shafts 90 on the corresponding sides, and a parallel synchronizer 841 is arranged between the two drive shafts 90. Alternatively, the two auxiliary drive motors 8 are respectively connected to the drive shafts 90 on the corresponding sides through a set of speed change mechanisms, and a parallel synchronizer 841 is arranged between the two sets of speed change mechanisms; the specific configuration of the speed change mechanism of each group and the setting position of the parallel synchronizer 841 can be flexibly arranged according to the transmission and speed change requirements between the auxiliary drive motors 8 and the wheels 9. The speed change mechanism can be set to a single gear, two gears or multiple gears according to the requirements of the gear change, and the switching between the gears is realized by the synchronizer.

[0084] For example, see Fig.11 , the auxiliary drive motor 8 is directly arranged on the drive shaft 90 on the corresponding side, and a parallel synchronizer 841 is arranged between the two drive shafts 90. Fig.13 A motor shaft gear 81 is provided on the motor shaft of the auxiliary drive motor 8, and a drive shaft gear 82 is provided on the drive shaft 90 on the corresponding side. The motor shaft gear 81 and the drive shaft gear 82 are meshed and transmitted to form a speed change mechanism; a parallel synchronizer 841 is provided between the two sets of speed change mechanisms. Of course, the parallel synchronizer 841 can be provided between the two drive shafts 90, or between the motor shafts of the two auxiliary drive motors 8.

[0085] For example, you can refer to Fig.13 A secondary intermediate shaft 800 is arranged between the motor shaft of the secondary drive motor 8 and the drive shaft 90 on the corresponding side, a motor shaft gear 81 is arranged on the motor shaft of the secondary drive motor 8, a first intermediate shaft gear 831 and a second intermediate shaft gear 832 are arranged on the secondary intermediate shaft 800 at intervals, and a drive shaft gear 82 is arranged on the drive shaft 90; wherein the motor shaft gear 81 is meshed and connected with the first intermediate shaft gear 831, and the second intermediate shaft gear 832 is meshed and connected with the drive shaft gear 82, forming a speed transmission path, which can achieve a stable speed transmission effect. The parallel synchronizer 841 can be arranged at multiple positions on the two sets of speed change mechanisms, such as between the motor shafts of the two secondary drive motors 8 shown in the figure; of course, the parallel synchronizer 841 can also be arranged between the two drive shafts 90 or between the two secondary intermediate shafts 800.

[0086] or reference Fig.14, the first motor shaft gear 811 and the second motor shaft gear 812 are arranged at intervals on the motor shaft of the auxiliary drive motor 8, and the first drive shaft gear 821 and the second drive shaft gear 822 are arranged at intervals on the corresponding side drive shaft 90. The first motor shaft gear 811 is meshed and connected with the first drive shaft gear 821, and the second motor shaft gear 812 is meshed and connected with the second drive shaft gear 822. The parallel synchronizer 841 is arranged between the motor shafts of the auxiliary drive motors 8 on both sides; of course, the parallel synchronizer 841 can also be arranged between the two drive shafts 90.

[0087] Or, refer to Fig.15 As shown, a secondary intermediate shaft 800 is added between the motor shaft of the secondary drive motor 8 and the corresponding drive shaft 90. The motor shaft of the secondary drive motor 8 is provided with a first motor shaft gear 811 and a second motor shaft gear 812 at intervals, the secondary intermediate shaft 800 is provided with a first intermediate shaft gear 831, a third intermediate shaft gear 833 and a second intermediate shaft gear 832 at intervals, and the drive shaft gear 82 is provided on the drive shaft 90. Among them, the first motor shaft gear 811 is meshed and connected with the first intermediate shaft gear 831, the second motor shaft gear 812 is meshed and connected with the second intermediate shaft gear 832, and the third intermediate shaft gear 833 is meshed and connected with the drive shaft gear 82; at the same time, a gear shift synchronizer 842 is provided on the secondary intermediate shaft 800 between the first intermediate shaft gear 831 and the second intermediate shaft gear 832, which can switch gears to form two speed transmission paths with different transmission ratios of the speed change mechanism. The parallel synchronizer 841 may be disposed between the drive shafts 90 on both sides; of course, the parallel synchronizer 841 may also be disposed between the motor shafts of the two auxiliary drive motors 8 or between the two auxiliary intermediate shafts 800 .

[0088] Or, refer to Fig.16 As shown, a secondary intermediate shaft 800 is added between the motor shaft of the secondary drive motor 8 and the corresponding drive shaft 90. A motor shaft gear 81 is provided on the motor shaft of the secondary drive motor 8, a first intermediate shaft gear 831, a third intermediate shaft gear 833 and a second intermediate shaft gear 832 are arranged at intervals on the secondary intermediate shaft 800, and a first drive shaft gear 821 and a second drive shaft gear 822 are arranged at intervals on the drive shaft 90. Among them, the motor shaft gear 81 is meshed and connected with the third intermediate shaft gear 833, the first intermediate shaft gear 831 is meshed and connected with the first drive shaft gear 821, and the second intermediate shaft gear 832 is meshed and connected with the second drive shaft gear 822; at the same time, a gear shift synchronizer 842 is provided on the drive shaft 90 between the first drive shaft gear 821 and the second drive shaft gear 822, which can switch gears and form two speed transmission paths with different transmission ratios of the speed change mechanism. The parallel synchronizer 841 may be disposed between the auxiliary intermediate shafts 800 on both sides; of course, the parallel synchronizer 841 may also be disposed between the motor shafts of the two auxiliary drive motors 8 or between the two drive shafts 90 .

[0089] In general, by using two auxiliary drive motors 8 to drive the wheels 9 on the left and right sides respectively, the configuration of the auxiliary differential 85 can be omitted; moreover, by providing a parallel synchronizer 841 between the drive shafts 90 on the left and right sides or the speed change mechanism, not only can the driving forces on both sides be disengaged to achieve a differential effect, but when the wheel 9 on one side encounters bad road conditions and is difficult to get out of trouble, the parallel synchronizer 841 can also promptly engage the drive shafts 90 on both sides, thereby combining the power of the two auxiliary drive motors 8 to transmit to the wheel 9 to be freed, thereby improving the vehicle's ability to get out of trouble.

[0090] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A planetary gearbox hybrid transmission system, comprising an engine (1), a first motor (21), a second motor and a transmission; characterized in that: The transmission comprises an input shaft (4) and an output shaft (5) arranged in parallel, and a planetary gear; The input shaft (4) is arranged on the planet carrier (71) of the planetary gear, and is used to receive power input from the engine (1); The second motor and the first motor (21) are drivingly connected to the sun gear (70) of the planetary gear; A speed change mechanism is provided between the ring gear (72) of the planetary gear set and the output shaft (5), and the speed change mechanism can change the transmission ratio between the ring gear (72) and the output shaft (5) under the control of a power switching device.

2. The planetary gear hybrid transmission system according to claim 1, characterized in that: The planetary hybrid transmission system also includes a second motor (22) drivingly connected to the output shaft (5).

3. The planetary gear hybrid transmission system according to claim 2, characterized in that: The second motor (22) is connected to the output shaft (5) via a transmission gear set (220), and / or the sun gear (70) is directly fixed on the shaft of the first motor (21).

4. The planetary gear hybrid transmission system according to claim 2, characterized in that: The second motor (22) and the driving shaft (90) of the wheel (9) are respectively connected to the two ends of the output shaft (5) in a transmission manner.

5. The planetary gear hybrid transmission system according to claim 1, characterized in that: The power output shaft (10) of the engine (1) is transmission-connected to the input shaft (4) via a clutch (30).

6. The planetary gear hybrid transmission system according to any one of claims 1 to 5, characterized in that: The speed change mechanism adopts a gear transmission structure.

7. The planetary gear hybrid transmission system according to claim 6, characterized in that: The speed change mechanism comprises a first gear set and a second gear set; the power switching device is arranged between the first gear set and the second gear set, and the power switching device is used to selectively connect the first gear set or the second gear set between the ring gear (72) and the output shaft (5).

8. The planetary gear hybrid transmission system according to claim 7, characterized in that: The power switching device adopts a synchronizer (31).

9. The planetary gear hybrid transmission system according to claim 8, characterized in that: The first gear set comprises a first driving gear (721) fixedly mounted on the gear ring (72) and a first driven gear (501) sleeved on the output shaft (5); the second gear set comprises a second driving gear (722) fixedly mounted on the gear ring (72) and a second driven gear (502) sleeved on the output shaft (5); the synchronizer (31) is arranged on the output shaft (5) between the first driven gear (501) and the second driven gear (502).

10. A vehicle, characterized in that: The vehicle is equipped with a planetary gearbox hybrid transmission system and an auxiliary power system according to any one of claims 1 to 9, and the planetary gearbox hybrid transmission system and the auxiliary power system can interchangeably drive the wheels (9) of the front axle and the rear axle of the vehicle respectively.

Images