Driving device for coaxial planet row vehicle

Abstract

The invention discloses a coaxial planet row driving device for a vehicle. The coaxial planet row driving device comprises a shell, a power motor, a planetary reducer gear mechanism and a planet row differential mechanism. The power motor comprises a rotor assembly, a stator assembly and a rotor shaft; the planetary reducer gear mechanism comprises a first sun gear connected with the rotor shaft, a first planet carrier and a gear ring which are arranged in the shell, and a first duplex planetary gear set arranged on the first planet carrier; the rotor shaft, the planetary reducer gear mechanism and the planet row differential mechanism are coaxially arranged, a first output part and a second output part at the two ends of the rotor shaft are connected to the driving wheel, and the first sun wheel is in meshed connection with the first duplex planetary gear set. By designing the planetary reducer gear mechanism with coaxial input and output and the planetary row differential mechanism with parallel axis design, the axial and radial sizes of the driving device are shortened to the maximum extent on the basis of ensuring the gear performance, the miniaturization and light weight of the driving device are facilitated, and the applicability is greatly improved.

Description

Technical Field

[0001] The present invention relates to the technical field of drive devices for new energy vehicles, and in particular to a drive device for a coaxial planetary gear vehicle. Background Art

[0002] As the automotive industry develops in the direction of low carbon and intelligence, new energy vehicles have gradually become the new favorite of major automakers, and there are more stringent requirements on the weight, size, efficiency and other performance of the drive devices used in new energy vehicles.

[0003] Coaxial planetary reducer gear mechanisms are often used as reducers for electric vehicles due to their compact structure and coaxial input and output characteristics. Existing drive devices generally have two typical structures. The first typical structure is a combination of a planetary reducer gear mechanism and a bevel gear differential; the second typical structure is a combination of a planetary reducer gear mechanism and a spur gear planetary differential mechanism. This combination has the advantages of light weight and small size.

[0004] However, in the first structure, the planet carrier of the planetary reducer gear mechanism and the planet carrier of the bevel gear differential are arranged along the axle direction, which increases the axial length of the overall drive device and is not conducive to the miniaturization of the drive device. The second structure has low overall strength and is prone to noise. All planetary gears in existing spur gear planetary differentials are generally designed with the same modulus and the same pressure angle, which affects the load-bearing, layout flexibility and NVH performance of the drive device. Summary of the invention

[0005] Based on this, the purpose of the present invention is to provide a coaxial planetary gear vehicle drive device, aiming to solve the problems that the current two types of drives have a larger axial length, which is not conducive to the miniaturization of the drive device, and the overall strength is not strong and it is easy to generate noise, and all the planetary gears in the existing spur gear planetary gear differential are generally designed with the same module and the same pressure angle, which affects the load-bearing, layout flexibility and NVH performance of the drive device.

[0006] To achieve the above object, the present invention is implemented through the following technical solutions: a coaxial planetary gear vehicle drive device, comprising a housing, a power motor arranged in the housing, a planetary reducer gear mechanism arranged along the rotation path of the power motor, and a planetary gear differential mechanism;

[0007] A power motor comprises a rotor assembly, a stator assembly arranged on the outer periphery of the rotor assembly, and a rotor shaft passing through the rotor assembly;

[0008] a planetary reducer gear mechanism, comprising a first sun gear connected to the rotor shaft, a first planet carrier and a ring gear disposed in the housing, and a first double planetary gear set disposed in the first planet carrier;

[0009] Among them, the rotor shaft, the planetary reducer gear mechanism, and the planetary differential mechanism are coaxially arranged, the first output part and the second output part at both ends of the rotor shaft are connected to the drive wheel, and the first sun gear and the first double planetary gear set are meshed and connected.

[0010] In summary, according to a coaxial planetary gearbox vehicle drive device proposed by the present invention, by designing a planetary reducer gear mechanism with coaxial input and output and a planetary gearbox differential mechanism with parallel axis design, the axial and radial dimensions of the drive device are shortened to the maximum extent on the basis of ensuring the gear performance, which is conducive to the miniaturization and lightweight of the drive device, and the applicability is greatly improved. Specifically, by designing the planetary reducer gear mechanism and the planetary gearbox differential mechanism to share the first planet carrier, the axial length of the overall drive device is preliminarily reduced. It is conducive to achieving the design purpose of miniaturization and lightweight of the drive device. Furthermore, by using the same number of planetary gear sets in the planetary reducer gear mechanism and the planetary gearbox differential mechanism, the first double planetary gear and the second double planetary gear are staggered and overlapped in the circumferential and radial directions, the miniaturization of the drive device is achieved, and the planetary gearbox differential can maintain good NVH performance and load-bearing capacity. Finally, by designing the corresponding gear tooth number of the positive planetary gear set, the vehicle can have the same power performance when turning left and right, so that the speed difference between the left and right wheel ends of the whole vehicle under various driving environments can be kept within a smaller speed difference range, ensuring the driving performance of the whole vehicle, and greatly improving the driving experience of the user.

[0011] According to one aspect of the above technical solution, a plurality of first planetary gear shafts are provided on the first planetary carrier in a direction parallel to the rotor shaft, and a first double planetary gear set is provided on any of the first planetary gear shafts.

[0012] According to one aspect of the above technical solution, the first double planetary gear set includes a first planetary gear meshing with the first sun gear, and a second planetary gear meshing with the ring gear, and the first planetary gear and the second planetary gear are installed on the first planetary gear shaft through bearings.

[0013] According to one aspect of the above technical solution, the diameter of the first planetary gear is greater than the diameter of the second planetary gear.

[0014] According to one aspect of the above technical solution, the inner tooth surface of the output end of the first planet carrier is connected to the power input end of the planetary gear differential mechanism.

[0015] According to one aspect of the above technical solution, the planetary differential mechanism includes a second sun gear connected to the first output part, a third planetary gear meshingly connected to the second sun gear, and a second double planetary gear meshingly connected to the third planetary gear, and the second double planetary gear is meshingly connected to the internal tooth surface.

[0016] According to one aspect of the above technical solution, the second double planetary gear comprises a fourth planetary gear and a fifth planetary gear fixed as one, and the inner tooth surface of the fifth planetary gear is meshingly connected.

[0017] According to one aspect of the above technical solution, the diameter of the fourth planetary gear is smaller than the diameter of the fifth planetary gear.

[0018] According to one aspect of the above technical solution, the first output part and the first driving wheel are combined into a first output line, and the second output part and the second driving wheel are combined into a second output line, and the first output line and the second output line are used to output power and torque.

[0019] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 is a schematic diagram of an electric vehicle in a first embodiment of the present invention;

[0021] Figure 2 is a schematic structural diagram of a driving device in a first embodiment of the present invention;

[0022] Figure 3 is a schematic plan view of a driving device in a first embodiment of the present invention;

[0023] Figure 4 is a schematic structural diagram of a first shaft body in a first embodiment of the present invention;

[0024] Figure 5 It is a schematic axial projection diagram of a planetary gear differential mechanism in the first embodiment of the present invention;

[0025] Figure 6 It is a partial structural diagram of the planetary gear differential mechanism in the first embodiment of the present invention;

[0026] Figure 7 It is a schematic diagram of the power flow of the driving device in the first embodiment of the present invention;

[0027] Figure 8 FIG. 1 is a schematic structural diagram of a driving device according to a second embodiment of the present invention.

[0028] Component symbol description:

[0029]

[0030] DETAILED DESCRIPTION

[0031] In order to facilitate the understanding of the present invention, the present invention will be described more fully below with reference to the relevant drawings. Several embodiments of the present invention are given in the drawings. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present invention more thorough and comprehensive.

[0032] It should be noted that when an element is referred to as being "fixed to" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only.

[0033] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more related listed items.

[0034] Embodiment 1

[0035] Figure 1 This is a schematic diagram of an electric vehicle in the first embodiment of the invention. The electric vehicle has an electrically driven vehicle drive shaft 100, wherein the first drive wheel 1 and the second drive wheel 9 can be driven by the drive device 300 through the first output unit 14 and the second output unit 16. The vehicle axle 200 is the front axle of the electric vehicle, and the vehicle drive shaft 100 is the rear axle of the electric vehicle. However, as a substitute or supplement to the motor vehicle drive shaft 100, the vehicle axle 200 can also be designed to have the same structure as the vehicle drive shaft 100 or be equipped with a traditional engine structure to drive the third drive wheel 17 and the fourth drive wheel 18 to meet the needs of pure electric or hybrid vehicles.

[0036] Figure 2 : is a schematic diagram of the structure of the driving device in the first embodiment of the present invention. The driving device 300 has a power motor 2, a planetary reducer gear mechanism 3, and a planetary differential mechanism 21. The driving device 300 also has a first output part 14, a second output part 16 and a housing 19, wherein the planetary reducer gear mechanism 3 is used for reducing speed and increasing torque, and the planetary differential mechanism 21 realizes the differential function.

[0037] In the driving device 300, a planetary reducer gear mechanism 3, a planetary differential mechanism 21, a first output part 14 and a second output part 16 are arranged along the rotation path of the power motor 2. The power motor comprises a rotor shaft 22 connected to the first sun gear 4, a rotor assembly 2a and a stator assembly 2b, wherein the stator assembly 2b is fixed on the housing 19; the rotor shaft 22, the planetary reducer gear mechanism 3, the planetary differential mechanism 21, the first output part 14, the second output part 16 and the first sun gear 4 are coaxially arranged, the first output part 14 is independently arranged from the rotor shaft 22 and passes through the center of the rotating shaft 22, in other words, the first output part 14 or the transmission shaft connected to the first output part 14 passes through the center of the rotating shaft 22 of the power motor 2 and does not contact the inner wall of the rotating shaft 22.

[0038] Furthermore, one side of the first output unit 14 and the second output unit 16 are connected to the wheels 1 and 9 on both sides of the vehicle, wherein the other side of the first output unit 14 is connected to the second sun gear 15 , and the other side of the second output unit 16 is connected to the second planet carrier 8 .

[0039] In the drive device 300 , the output rotation of the power motor 2 is decelerated and torque-increased by the planetary reducer gear mechanism 4 and then input into the planetary differential mechanism 21 , and transmitted to the left and right drive wheels 1 , 9 of the vehicle equipped with the drive device 300 via the first output unit 14 and the second output unit 16 .

[0040] See also Figures 2 to 7 The above-mentioned planetary reducer gear mechanism 3 includes a first sun gear 4, a first planetary gear 5, a second planetary gear 12, a first planetary shaft 20, a first planetary carrier 7 and a ring gear 6. The first planetary gear 5 is meshed with the first sun gear 4, the second planetary gear 12 is meshed with the ring gear 6, and the ring gear 6 is fixedly connected to the housing 19. Compared with the 'sun gear-single planetary gear-ring gear' structure in the existing reducer, the speed ratio variation range of the planetary gear structure in the present invention is larger. In actual application, the number of teeth of the first sun gear 4, the first planetary gear 5 and the second planetary gear 12, and the ring gear 6 can be adjusted to form different speed ratios, thereby improving applicability.

[0041] Furthermore, the first planetary gear 5 is fixedly connected to the second planetary gear 12 to form a first double-linked planetary gear, and the first double-linked planetary gear is connected to the first planetary carrier 7 through the first planetary gear shaft 20, and the first planetary gear shaft 20 is fixed on the first planetary carrier 7. Specifically, the first double-linked planetary gear is equipped with the first planetary gear shaft 20 in the inner hole, and the first double-linked planetary gear is rotatably mounted on the first planetary gear shaft 20 on the planetary carrier 7 through the bearing 26.

[0042] Furthermore, the above-mentioned first planetary carrier 7 serves as a power output element of the planetary reducer gear mechanism 3, and is also a power input element of the planetary gear differential 21. The power input of the planetary gear differential 21 is connected through the internal tooth structure 23 set at the output end of the first planetary carrier 7, and the internal tooth 23 can be a spur gear or a helical gear.

[0043] Furthermore, the planetary reducer gear mechanism 3 in the present invention includes at least one of the above-mentioned first double-coupled planetary gears. In a preferred embodiment, the planetary gear reducer includes three first double-coupled planetary gears, and the three first double-coupled planetary gears are evenly arranged along the circumferential direction of the first sun gear 4.

[0044] Furthermore, the individual first planetary gears 5 of the first double planetary gear have a larger diameter than the individual second planetary gears 12 .

[0045] It should be noted that the first planetary gear 5 and the second planetary gear 12 can be made into an integral structure to form the first double planetary gear. Figure 4 As shown, the first planetary gear 5, the second planetary gear 12 and the first planetary gear shaft 20 can be made into an integral structure to form a first shaft body 3a, and both ends of the first shaft body 3a are connected to the first planetary carrier 7 through a bearing 26 respectively.

[0046] As an example, the planetary gear differential 21 is arranged side by side with the above-mentioned planetary reducer gear mechanism 3 in the axle direction, and in this case is formed by a positive planetary gear set, which is composed of a second sun gear 15, a third planetary gear 10, a fourth planetary gear 11, a fifth planetary gear 13, and a second planet carrier 8. The second planet carrier 8 carries multiple pairs of planetary gears 10, 11 and 13 in a load-bearing manner, wherein the fifth planetary gear 13 is meshed with an internal tooth structure 23 provided at the output end of the first planet carrier 7. It should be noted that the third planetary gear 10 is not meshed with the internal tooth structure 23 provided at the output end of the first planet carrier 7, and the above-mentioned planetary gears are all designed as straight tooth structures. The transmission axis of the planetary gear differential of the present invention is a parallel two-line coaxial output structure design, and such a structural design facilitates reducing the overall size of the planetary gear differential, thereby achieving the purpose of miniaturization and lightweight design of the drive device.

[0047] Further, the two-line output structure in this embodiment includes a first output line 101 and a second output line 102 for outputting power and torque to the wheels on both sides respectively. Specifically, the inner tooth structure 23 is meshed with the fifth planetary gear 13, the fourth planetary gear 11 is fixedly connected with the fifth planetary gear 13 and rotates therewith, and the fifth planetary gear 13 drives the second planetary carrier 8 to rotate. On the one hand, the fourth planetary gear 11 is meshed with the third planetary gear 10, and the third planetary gear 10 is meshed with the second sun gear 15. The second sun gear 15 is connected to the first output part 14 in a rotationally fixed manner, and the other side of the first output part 14 is connected to the driving wheel 1 to form the first output line 101 for outputting power and torque to the wheels on one side. On the other hand, the second planetary carrier 8 is connected to the second output part 16 in a non-rotatable manner, and part of it is designed as a whole with the second output part 16, and the other side of the second output part 16 is connected to the driving wheel 9 to form the second output line 102 for outputting power and torque to the wheels on the other side.

[0048] Furthermore, the connection between the planetary reducer gear 3 and the planetary differential 21 is achieved in the following manner: the output end of the first planet carrier 7 is non-rotatably connected to the internal gear structure 23 , and the internal gear structure 23 is meshingly connected to the fifth planetary gear 13 .

[0049] As a specific example, in the first embodiment, the fourth planetary gear 11 and the fifth planetary gear 13 are fixedly connected to form a second double-linked planetary gear, and the second double-linked planetary gear is connected to the planet carrier 8 through the core shaft of the second double-linked planetary gear, and the core shaft of the second double-linked planetary gear is fixed on the planet carrier 8. Specifically, the second double-linked planetary gear is connected to the core shaft of the second double-linked planetary gear through a bearing 26, and the core shaft of the second double-linked planetary gear is fixedly installed on the planet carrier 8.

[0050] Furthermore, the fourth planetary gear 11 and the fifth planetary gear 13 are arranged side by side and have different numbers of teeth, different modules and pressure angles, and the diameter of the fourth planetary gear 11 is smaller than the diameter of the fifth planetary gear 13. On the one hand, by designing corresponding gears with different modules and pressure angles, it is possible to avoid using an excessively large displacement coefficient for the differential, and the differential can maintain good NVH performance; on the other hand, by designing the fourth planetary gear 11 and the fifth planetary gear 13 with different numbers of teeth and side-by-side arrangement, the gear matching and arrangement flexibility are improved, while reducing the radial size.

[0051] Furthermore, in order to achieve a 1:1 distribution of torque between the left and right wheels of the vehicle, the number of teeth of each gear needs to satisfy the relationship: (Z22*Z11) / (Z15*Z13)=2, and the total speed ratio of the planetary differential satisfies 1-(Z22*Z11) / (Z15*Z13); by designing the corresponding number of gear teeth, the vehicle can have the same dynamic performance when turning left and right. In other words, a 1:1 distribution of torque between the left and right wheels of the vehicle can effectively improve the vehicle's handling performance.

[0052] Furthermore, the planetary gear differential 21 in the present invention includes at least one of the above-mentioned second double-coupled planetary gears and the third planetary gear 10. In a preferred embodiment, the planetary gear differential includes three second double-coupled planetary gears and the third planetary gear 10, and the three second double-coupled planetary gears and the third planetary gear 10 are evenly arranged along the circumferential direction of the second output portion 16 to ensure the dynamic balance of the system, share the torque, and reduce the load of a single component.

[0053] It should be noted that the fourth planetary gear 11 and the fifth planetary gear 13 can be made into an integral structure to form the second double planetary gear. Figure 4 As shown, the fourth planetary gear 11, the fifth planetary gear 13 and the core shaft of the second double planetary gear can be made into an integral structure to form a second shaft body 4a, and both ends of the second shaft body 4a are connected to the second planetary carrier 8 through a bearing 26 respectively.

[0054] It should be noted that, in order to further reduce the overall dimensions of the drive device, the planetary gear reducer 3 and the planetary gear differential 21 in the vehicle drive device of the present invention use the same number of planetary gear sets. Specifically, the number of the first double-linked planetary gears in the planetary gear reducer 3 is consistent with the number of the second double-linked planetary gears and the third planetary gear 10 in the planetary gear differential 21, and in the circumferential direction of the second planetary carrier 8, the first double-linked planetary gears and the second double-linked planetary gears are staggered; in the axial direction of the second planetary carrier 8, the first double-linked planetary gears and the second double-linked planetary gears are overlapping, thereby making the drive device have a smaller cross-sectional radius and a smaller axial length, thereby achieving the purpose of miniaturization of the drive device.

[0055] Furthermore, the housing 19 is used to install the above structure and the parts required to realize the transmission function, and an oil pool is also provided therein, which is used to contain lubricating oil for lubricating and cooling the moving components. The housing 19 is also provided with an oil channel, which is used to guide the oil into the parts that need lubrication and cooling or the positions that need lubrication and cooling. In some embodiments, an oil pump is also installed on the housing 19. In order to further improve the reliability of the present invention, each gear and bearing 26 in the vehicle drive device should be fully lubricated, and the lubrication forms include various forms such as stirring oil lubrication and forced lubrication.

[0056] In actual use, the working principle of the vehicle drive device of the present invention can be:

[0057] When there is no speed difference between the left and right wheel ends of the vehicle, in other words, when the vehicle is traveling in a straight line, the first output unit 14 and the second output unit 16 rotate at the same speed, and the second sun gear 15 and the second planetary carrier 8 fixedly connected to the first output unit 114 and the second output unit 16 respectively will also rotate at the same speed, so that the second sun gear 15 and the second planetary carrier 8 will not rotate relative to each other. At the same time, since the third planetary gear 10 is used as an idler gear, during the straight-line driving of the vehicle, the third planetary gear 10 will only revolve, and there will be no self-rotation. The power output path in the above process is as follows: the power and torque output by the power motor 2 are first input into the planetary gear reducer 3, and then output to the planetary gear differential 21 through the first planetary carrier 7. Specifically, the power and torque output by the power motor 2 enter the planetary gear differential 21 through the rotating shaft 22, the sun gear 4, the first planetary gear 5, the second planetary gear 12, the first planetary carrier 7 and the inner teeth 23. Under the action of the parallel axis in the planetary gear differential, the first planetary carrier 7 The input power and torque are output to the left and right wheels of the vehicle through the first output line 101 and the second output line 102 respectively, wherein the first output line 101 is transmitted by the inner teeth 23, the fifth planetary gear 13, the fourth planetary gear 11, the third planetary gear 10 and the second sun gear 15 and output through the first output part 14, while the second output line 102 is transmitted by the inner teeth 23, the fifth planetary gear 13, the fourth planetary gear 11 and the second planetary carrier 8 and output through the second output part 16, thereby achieving the purpose of transmitting the driving torque input from the power motor 22 to the left and right wheels of the vehicle without generating a rotation difference between the left and right wheels.

[0058] When the vehicle turns, the road surface under the left and right wheels is different, or the actual rolling radius of the wheels is different, there is a speed difference between the left and right wheels, and the speeds of the first output unit 14 and the second output unit 16 fixedly connected to the left and right wheels are also different. In other words, a differential is generated between the first output unit 14 and the second output unit 116. In this case, the second sun gear 15 and the second planetary carrier 8 will rotate and form a speed difference, and the third planetary gear 10 meshing with the second sun gear 15 will also rotate. The corresponding number of gear teeth in the planetary gear differential of the present invention satisfies (Z22*Z11) / (Z15*Z13)=2, which can ensure that the speed ratio from the fifth planetary gear 13 to the first output unit 14 is equal to the speed ratio from the fifth planetary gear 13 to the second output unit 16, thereby making the vehicle have the same power performance when turning left and right, making the speed difference between the left and right wheel ends of the vehicle smaller, thereby improving the driving performance of the vehicle.

[0059] In summary, the beneficial effects of the vehicle drive device of the present invention are: by designing a planetary gear reducer with coaxial input and output and a planetary gear differential with parallel axes, the axial and radial dimensions of the drive device are shortened to the greatest extent while ensuring the gear performance, which is beneficial to the miniaturization and lightweight of the drive device and greatly improves the applicability. Specifically, by designing the planetary gear reducer and the planetary gear differential to share a planetary carrier, the axial length of the overall drive device is preliminarily reduced. Furthermore, by designing the fifth and fourth planetary gears arranged in parallel in the planetary gear differential, and adding the third planetary gear and the second sun gear to form a parallel axis output structure, the differential structure design with parallel axis design can further reduce the overall size of the drive device, which is conducive to achieving the design purpose of miniaturization and lightweight of the drive device. Furthermore, by using the same number of planetary gear sets in the planetary gear reducer and the planetary gear differential, the first double planetary gear and the second double planetary gear are staggered and overlapped in the circumferential and radial directions, so that the drive device has a smaller cross-sectional radius and a smaller axial length, and the purpose of miniaturization of the drive device is achieved; in addition, by designing the fifth and fourth planetary gears with different numbers of teeth, modules and pressure angles of corresponding gears, it is possible to avoid using an excessively large displacement coefficient for the differential, and the planetary gear differential can maintain good NVH performance and load-bearing capacity. Finally, by designing the corresponding number of gear teeth of the positive planetary gear set, the vehicle can have the same dynamic performance when turning left and right. In other words, the speed difference between the left and right wheel ends of the vehicle under various driving environments can be kept within a smaller speed difference range, ensuring the driving performance of the vehicle and greatly improving the user's driving experience.

[0060] Embodiment 2

[0061] Please refer to Figure 8 , which is a transmission principle diagram and a power transmission route diagram of the driving device in the second embodiment of the present invention. The difference between the vehicle driving device in this embodiment and the vehicle driving device in the first embodiment is that the power transmission between the structures of the planetary gear reducer and the planetary gear differential does not have an internal tooth structure, but is transmitted through external meshing. Specifically, the planetary differential 21 is arranged side by side with the above-mentioned planetary reducer gear mechanism 3 in the direction of the axle, and in this case is formed by a positive planetary gear set, which is composed of a second sun gear 15, a third planetary gear 10, a fourth planetary gear 11, a fifth planetary gear 13, a sixth planetary gear 24, an external tooth structure 25 and a second planet carrier 8. The second planet carrier 8 carries multiple pairs of planetary gears 10, 11, 13 and 24 in a load-bearing manner. The above-mentioned planetary gears are all designed as straight tooth structures. The output end of the first planet carrier 7 is connected to the above-mentioned external tooth structure 25 in a non-rotatable manner, and the external tooth structure 25 is externally meshed with the sixth planetary gear 24, and the sixth planetary gear 24 is externally meshed with the fifth planetary gear 13.

[0062] In summary, according to a coaxial planetary gearbox vehicle drive device proposed by the present invention, by designing a planetary reducer gear mechanism with coaxial input and output and a planetary gearbox differential mechanism with parallel axis design, the axial and radial dimensions of the drive device are shortened to the maximum extent on the basis of ensuring the gear performance, which is conducive to the miniaturization and lightweight of the drive device, and the applicability is greatly improved. Specifically, by designing the planetary reducer gear mechanism and the planetary gearbox differential mechanism to share the first planet carrier, the axial length of the overall drive device is preliminarily reduced. It is conducive to achieving the design purpose of miniaturization and lightweight of the drive device. Furthermore, by using the same number of planetary gear sets in the planetary reducer gear mechanism and the planetary gearbox differential mechanism, the first double planetary gear and the second double planetary gear are staggered and overlapped in the circumferential and radial directions, the miniaturization of the drive device is achieved, and the planetary gearbox differential can maintain good NVH performance and load-bearing capacity. Finally, by designing the corresponding gear tooth number of the positive planetary gear set, the vehicle can have the same power performance when turning left and right, so that the speed difference between the left and right wheel ends of the whole vehicle under various driving environments can be kept within a smaller speed difference range, ensuring the driving performance of the whole vehicle, and greatly improving the driving experience of the user.

[0063] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0064] The above-mentioned embodiments only express several implementation methods of the present invention, and the description thereof is relatively specific and detailed, but it cannot be understood as limiting the scope of the patent of the present invention. It should be pointed out that, for ordinary technicians in this field, several variations and improvements can be made without departing from the concept of the present invention, which all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A coaxial planetary gear vehicle drive device, characterized in that: It includes a housing, a power motor arranged in the housing, a planetary reducer gear mechanism arranged along the rotation path of the power motor, and a planetary gear differential mechanism; A power motor comprises a rotor assembly, a stator assembly arranged on the outer periphery of the rotor assembly, and a rotor shaft passing through the rotor assembly; a planetary reducer gear mechanism, comprising a first sun gear connected to the rotor shaft, a first planet carrier and a ring gear disposed in the housing, and a first double planetary gear set disposed in the first planet carrier; Among them, the rotor shaft, the planetary reducer gear mechanism, and the planetary differential mechanism are coaxially arranged, the first output part and the second output part at both ends of the rotor shaft are connected to the drive wheel, and the first sun gear and the first double planetary gear set are meshed and connected.

2. The coaxial planetary gear vehicle drive device according to claim 1, characterized in that: A plurality of first planetary gear shafts are arranged on the first planet carrier in a direction parallel to the rotor shaft, and a first double planetary gear set is arranged on any of the first planetary gear shafts.

3. The coaxial planetary gear vehicle drive device according to claim 2, characterized in that: The first double planetary gear set includes a first planetary gear meshingly connected to the first sun gear, and a second planetary gear meshingly connected to the ring gear, and the first planetary gear and the second planetary gear are installed on the first planetary gear shaft through bearings.

4. The coaxial planetary gear vehicle drive device according to claim 3, characterized in that: The diameter of the first planetary gear is greater than the diameter of the second planetary gear.

5. The coaxial planetary gear vehicle drive device according to claim 4, characterized in that: The inner tooth surface of the output end of the first planet carrier is connected to the power input end of the planetary gear differential mechanism.

6. The coaxial planetary gear vehicle drive device according to claim 1, characterized in that: The planetary differential mechanism includes a second sun gear connected to the first output portion, a third planet gear meshingly connected to the second sun gear, a second double planet gear meshingly connected to the third planet gear, and the second double planet gear meshingly connected to the internal tooth surface.

7. The coaxial planetary gear vehicle drive device according to claim 6, characterized in that: The second double planetary gear comprises a fourth planetary gear and a fifth planetary gear fixed as one, and the inner tooth surface of the fifth planetary gear is meshingly connected.

8. The coaxial planetary gear vehicle drive device according to claim 7, characterized in that: The diameter of the fourth planetary gear is smaller than the diameter of the fifth planetary gear.

9. The coaxial planetary gear vehicle drive device according to claim 1, characterized in that: The first output part and the first driving wheel are combined into a first output line, and the second output part and the second driving wheel are combined into a second output line. The first output line and the second output line are used to output power and torque.

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