Vehicle driving device

Abstract

The utility model provides a vehicle driving device which comprises a shell, a planetary gear reducer and a planetary gear differential mechanism, the planetary gear reducer and the planetary gear differential mechanism are arranged in the shell, and the planetary gear reducer and the planetary gear differential mechanism share a planet carrier. The planetary gear differential mechanism comprises a third planetary gear, a fourth planetary gear, a fifth planetary gear, a first half axle gear, a second half axle gear, a second planetary gear shaft and a third planetary gear shaft, the first half axle gear and the second half axle gear are arranged in parallel, and the fifth planetary gear is meshed with the third planetary gear and the first half axle gear. The third planet gear is meshed with the first half axle gear, the fourth planet gear is meshed with the second half axle gear, the third planet gear and the fourth planet gear are connected to form a second duplex planet gear, the second duplex planet gear is connected with the planet carrier through a second planet gear shaft, and the fifth planet gear is connected with the planet carrier through a third planet gear shaft. According to the utility model, the overall axial length of the device can be reduced on the basis of ensuring the gear performance, and the design purposes of miniaturization and light weight can be realized.

Description

Technical Field

[0001] The utility model relates to the technical field of drive devices for new energy vehicles, in particular to a vehicle drive device. 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 and axial length of the drive devices used in new energy vehicles.

[0003] The existing drive device generally has two typical structures. The first typical structure is a combination of a planetary gear reducer and a bevel gear differential. However, in this combination, the planet carrier of the planetary gear reducer and the planet carrier of the bevel gear differential are arranged along the axle direction, which makes the axial length of the overall drive device larger, which is not conducive to the miniaturization of the drive device. The second typical structure is a combination of a double pinion planetary reducer and a spur gear planetary differential. Although this combination has the advantages of light weight and small size, the overall strength is not large and it is easy to generate noise. In addition, all the planetary gears in the existing spur gear planetary differential are generally designed to have the same module and the same pressure angle, which affects the load, layout flexibility and NVH performance of the drive device. The improvement measures for the second typical structure are mainly to design the number of teeth of the left and right half-shaft output gears in the spur gear planetary differential to be different, but it also leads to different resistance torques of the left and right wheels, which affects the driving performance of the vehicle. Therefore, it is urgent to develop a vehicle drive device that can shorten the overall axial size while ensuring the gear performance to meet the development trend of existing new energy vehicles. Utility Model Content

[0004] Based on this, the purpose of the utility model is to provide a vehicle drive device, aiming to solve the technical problem that the axial length of the vehicle drive device in the prior art is shortened while the driving performance of the vehicle cannot be guaranteed and it is not conducive to the miniaturization and lightweight of the drive device.

[0005] The utility model aims to provide a vehicle drive device, comprising a housing, a planetary gear reducer and a planetary gear differential arranged inside the housing, wherein the planetary gear reducer and the planetary gear differential share a planet carrier;

[0006] The planetary gear differential includes a third planetary gear, a fourth planetary gear, a fifth planetary gear, a first half-shaft gear, a second half-shaft gear, a second planetary gear shaft and a third planetary gear shaft, the first half-shaft gear and the second half-shaft gear are coaxially arranged, the fifth planetary gear is respectively meshed with the third planetary gear and the first half-shaft gear, the fourth planetary gear is meshed with the second half-shaft gear, the third planetary gear is connected with the fourth planetary gear to form a second double-coupled planetary gear, the second double-coupled planetary gear is connected to the planet carrier through the second planetary gear shaft, and the fifth planetary gear is connected to the planet carrier through the third planetary gear shaft.

[0007] Compared with the prior art, the beneficial effect of the vehicle drive device of the utility model is that by designing a planetary gear reducer with coaxial input and output and a planetary gear differential with parallel axis design, the axial size of the drive device is 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 gear reducer and the planetary gear differential to share a planet carrier, the axial length of the overall drive device is initially reduced. Further, by designing the first half-shaft gear and the second half-shaft gear arranged in parallel in the planetary gear differential, and adding the third planetary gear, the fourth planetary gear and the fifth planetary 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. In addition, it can also keep the speed difference between the left and right wheel ends of the whole vehicle in various driving environments within a smaller speed difference range, ensure the driving performance of the whole vehicle, and greatly improve the driving experience of the user.

[0008] In addition, the vehicle drive device according to the utility model may also have the following additional technical features:

[0009] Furthermore, the third planetary gear and the fourth planetary gear have the same number of teeth, and the diameter of the third planetary gear is smaller than the diameter of the fourth planetary gear.

[0010] Further, the first side shaft gear and the second side shaft gear have the same number of teeth, and the diameter of the first side shaft gear is smaller than the diameter of the second side shaft gear.

[0011] Further, the planetary gear differential includes at least one of the second double-coupled planetary gears and a fifth planetary gear, and the second double-coupled planetary gears and the fifth planetary gear are evenly arranged along the circumference of the second side gear.

[0012] Further, the planetary gear reducer includes a sun gear, a first planetary gear, a second planetary gear, a first planetary gear shaft and a ring gear, the first planetary gear is meshed with the sun gear, the second planetary gear is meshed with the ring gear, and the ring gear is connected to the housing, wherein the first planetary gear is connected to the second planetary gear to form a first double-coupled planetary gear, and the first double-coupled planetary gear is connected to the planet carrier through the first planetary gear shaft.

[0013] Furthermore, the planetary gear reducer includes at least one of the first double-coupled planetary gears, and the first double-coupled planetary gears are evenly arranged along the circumference of the sun gear.

[0014] Furthermore, the number of the first double-linked planetary gears is consistent with that of the second double-linked planetary gears, and in the circumferential direction of the planet carrier, the first double-linked planetary gears and the second double-linked planetary gears are staggered; in the axial direction of the planet carrier, the first double-linked planetary gears and the second double-linked planetary gears are overlapping.

[0015] Furthermore, the vehicle drive device also includes a first output unit and a second output unit, and the vehicle drive device is connected to the wheels on both sides of the vehicle through the first output unit and the second output unit respectively, wherein the first output unit is connected to the first half-shaft gear, and the second output unit is connected to the second half-shaft gear.

[0016] Furthermore, the vehicle drive device also includes a power motor, which is detachably connected to the housing, and the power motor includes a rotating shaft connected to the sun gear, the rotating shaft, the first output part, the second output part and the sun gear are coaxially arranged, and the second output part is independently arranged from the rotating shaft and passes through the center of the rotating shaft.

[0017] Furthermore, a retaining ring is provided at the connection position between the rotating shaft and the sun gear to limit the axial movement of the sun gear; a plurality of pins are provided on the circumference of the ring gear, and the ring gear is connected to the housing through the plurality of pins. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a transmission principle diagram of the vehicle drive device in the first embodiment of the utility model;

[0019] Figure 2 A power transmission route diagram of the vehicle driving device in the first embodiment of the utility model;

[0020] Figure 3 It is a three-dimensional structural schematic diagram of the planetary gear differential in the first embodiment of the utility model;

[0021] Figure 4It is a schematic structural diagram of the planetary gear differential in the first embodiment of the utility model at a first viewing angle;

[0022] Figure 5 It is a schematic structural diagram of the planetary gear differential in the first embodiment of the utility model at a second viewing angle;

[0023] Figure 6 This is a schematic structural diagram of the first shaft body in the first embodiment of the utility model;

[0024] Figure 7 This is a schematic structural diagram of the second shaft body in the first embodiment of the utility model;

[0025] Figure 8 This is a schematic diagram of the structure of the floating sun gear in the first embodiment of the utility model;

[0026] Fig. 9 This is a schematic diagram of the structure of the floating gear ring in the first embodiment of the utility model;

[0027] Fig.10 It is a transmission principle diagram of the vehicle drive device in the second embodiment of the utility model;

[0028] Fig.11 This is a power transmission route diagram of the vehicle driving device in the second embodiment of the utility model.

[0029] The above drawings include the following reference numerals: 10-housing; 11-keyway; 12-mounting hole; 20-planet carrier; 31-sun gear; 32-first planetary gear; 33-second planetary gear; 34-first planetary gear shaft; 35-gear ring; 351-external spline; 352-reinforcement ring; 353-inner hole; 36-pin; 3a-first shaft; 41-third planetary gear; 42-fourth planetary gear; 43-fifth planetary gear; 44-first half-shaft gear; 45-second half-shaft gear; 46-second planetary gear shaft; 47-third planetary gear shaft; 4a-second shaft; 51-first output part; 52-second output part; 60-power motor; 61-rotating shaft; 70-retaining ring; 101-first output line; 102-second output line;

[0030] The following specific implementation manner will further illustrate the present utility model in conjunction with the above-mentioned drawings. 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 in the technical field 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] The vehicle drive device of the utility model includes a housing 10, a planetary gear reducer and a planetary gear differential arranged inside the housing 10. In the present embodiment, the planetary gear reducer and the planetary gear differential share a planet carrier 20. The planet carrier 20 is the power output component of the planetary gear reducer and also the power input component of the planetary gear differential, thereby achieving the purpose of reducing the axial length of the drive device, which is conducive to the miniaturization of the drive device.

[0035] In order to facilitate the understanding of the present invention, several embodiments of the present invention are given below. 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.

[0036] Embodiment 1

[0037] See also Figures 1 to 9, shown is a vehicle drive device in the first embodiment of the utility model. Specifically, the planetary gear reducer includes a sun gear 31, a first planetary gear 32, a second planetary gear 33, a first planetary gear shaft 34 and a ring gear 35. The first planetary gear 32 is meshed with the sun gear 31, the second planetary gear 33 is meshed with the ring gear 35, and the ring gear 35 is fixedly connected to the housing 10. Compared with the 'sun gear-single planetary gear-ring gear' structure in the existing reducer, the planetary gear structure in the utility model has a larger speed ratio variation range. In actual use, the number of teeth of the sun gear 31, the first planetary gear 32, the second planetary gear 33, and the ring gear 35 can be adjusted to form different speed ratios to improve applicability. Furthermore, the first planetary gear 32 and the second planetary gear 33 are fixedly connected to form a first double-coupled planetary gear, and the first double-coupled planetary gear is connected to the planet carrier 20 through the first planetary gear shaft 34, and the core shaft of the first double-coupled planetary gear is fixed on the planet carrier 20. Specifically, the first planetary gear 32 and the second planetary gear 33 are respectively connected to the first planetary gear shaft 34 through bearings, and the first planetary gear shaft 34 is fixedly installed on the planet carrier 20.

[0038] Furthermore, the planetary gear reducer in the utility model 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 sun gear 31.

[0039] It should be noted that the first planetary gear 32 and the second planetary gear 33 can be made into an integral structure to form the first double planetary gear. Figure 6 As shown, the first planetary gear 32, the second planetary gear 33 and the first planetary gear shaft 34 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 planet carrier 20 through a bearing respectively.

[0040] As an example, Figures 3 to 5 As shown, the planetary gear differential includes a third planetary gear 41, a fourth planetary gear 42, a fifth planetary gear 43, a first half-shaft gear 44, a second half-shaft gear 45, a second planetary gear shaft 46 and a third planetary gear shaft 47. The first half-shaft gear 44 is coaxially arranged with the second half-shaft gear 45. In other words, the transmission axis of the planetary gear differential of the utility model is a parallel two-line coaxial output structure design. 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.

[0041] As a specific example, in this embodiment, the third planetary gear 41 and the fourth planetary gear 42 are fixedly connected to form a second double planetary gear, and the second double planetary gear is connected to the planet carrier 20 through the second planetary gear shaft 46, and the mandrel of the second double planetary gear is fixed on the planet carrier 20. Specifically, the third planetary gear 41 and the fourth planetary gear 42 are respectively connected to the second planetary gear shaft 46 through bearings, and the second planetary gear shaft 46 is fixedly mounted on the planet carrier 20. The fifth planetary gear 45 is connected to the third planetary gear shaft 47 through a bearing, and the third planetary gear shaft 47 is fixedly mounted on the planet carrier 20.

[0042] Furthermore, the planetary gear differential in the utility model includes at least one of the above-mentioned second double-coupled planetary gears and the fifth planetary gear 43. In a preferred embodiment, the planetary gear differential includes three second double-coupled planetary gears and the fifth planetary gear 43, and the three second double-coupled planetary gears and the fifth planetary gear 43 are evenly arranged along the circumferential direction of the second half-shaft gear 45 to ensure the dynamic balance of the system, share the torque, and reduce the load of a single component.

[0043] Furthermore, if Figure 2 As shown, 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, specifically, the third planetary gear 41 is meshed with the fifth planetary gear 43, and the fifth planetary gear 43 is meshed with the first side gear 44. In other words, the fifth planetary gear 43 is meshed with the third planetary gear 41 and the first side gear 44, respectively, to form the first output line 101 for outputting power and torque to the wheels on one side. The fourth planetary gear 42 is meshed with the second side gear 45 to form the second output line 102 for outputting power and torque to the wheels on the other side.

[0044] It should be noted that the third planetary gear 41 and the fourth planetary gear 42 can be made into an integral structure to form the second double planetary gear. Figure 7 As shown, the third planetary gear 41, the fourth planetary gear 42 and the second planetary gear shaft 46 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 planet carrier 20 through a bearing. Similarly, the fifth planetary gear 43 and the third planetary gear shaft 47 can be made into an integral structure and connected to the planet carrier 20 through a bearing.

[0045] Furthermore, in the planetary gear differential in this embodiment, the third planetary gear 41 and the fourth planetary gear 42 have the same number of teeth, different modules and pressure angles, and the diameter of the third planetary gear 41 is smaller than the diameter of the fourth planetary gear 43. The first half-shaft gear 44 and the second half-shaft gear 45 have the same number of teeth, different modules and pressure angles, and the diameter of the first half-shaft gear 44 is smaller than the diameter of the second half-shaft gear 45. The design of the same number of teeth of the corresponding gears can make the vehicle have the same power performance when turning left and right. In other words, the 1:1 distribution of the left and right wheel torque of the vehicle can effectively improve the vehicle handling performance. On the other hand, by designing the different modules and pressure angles of the corresponding gears, it is possible to avoid using an excessively large displacement coefficient for the differential, so that the differential can maintain good NVH performance.

[0046] It should be noted that, in order to further reduce the overall dimensions of the drive device, the planetary gear reducer and the planetary gear differential in the vehicle drive device of the utility model use the same number of planetary gear sets. Specifically, the number of the first double-linked planetary gears in the planetary gear reducer is consistent with the number of the second double-linked planetary gears in the planetary gear differential, and in the circumferential direction of the planetary carrier 20, the first double-linked planetary gears and the second double-linked planetary gears are staggered; in the axial direction of the planetary carrier 20, 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.

[0047] Furthermore, the vehicle drive device of the utility model further includes a first output part 51 and a second output part 52, and the vehicle drive device is connected to the wheels on the left and right sides of the vehicle through the first output part 51 and the second output part 52 respectively. In this embodiment, the first output part 51 is connected to the first side gear 44, and transmits power and torque to the wheel on one side through the transmission shaft of the vehicle; the second output part 52 is connected to the second side gear 45, and transmits power and torque to the wheel on the other side through another transmission shaft of the vehicle. In some embodiments, the first output part can be designed as a part of the first side gear, and the second output part can be designed as a part of the second side gear.

[0048] Furthermore, the vehicle drive device of the utility model also includes a power motor 60, which is detachably connected to the housing 10, and the power motor 60 includes a rotating shaft 61 connected to the sun gear 31. In the present embodiment, the rotating shaft 61, the first output part 51, the second output part 52 and the sun gear 31 are coaxially arranged, wherein the second output part 52 is independently arranged from the rotating shaft 61 and passes through the center of the rotating shaft 61. In other words, the second output part 52 or the transmission shaft connected to the second output part 52 passes through the center of the rotating shaft 61 of the power motor 60 and does not contact the inner wall of the rotating shaft 61.

[0049] In order to further improve the NVH performance and load-bearing capacity of the vehicle drive device of the utility model, a load-balancing structure is provided in the planetary gear reducer of the utility model. In this embodiment, a double floating load-balancing structure design is adopted, specifically a sun gear floating structure and a ring gear floating structure. In other words, a load-balancing structure is provided between the sun gear 31 and the rotating shaft and between the ring gear 35 and the housing 10. Specifically, as Figure 8 As shown, in this embodiment, the sun gear 31 and the rotating shaft 61 of the power motor 60 are designed in sections. In some embodiments, the sun gear 31 and the rotating shaft 61 can be designed as an integral structure. Furthermore, the rotating shaft 61 is provided with an internal spline structure, and the sun gear 31 is provided with an external spline structure. A retaining ring groove is provided on the internal and external spline positions of the rotating shaft 61 and the sun gear 31. The retaining ring groove is used to install a retaining ring 70, and the axial movement of the sun gear 31 is limited by the adaptation design of the retaining ring 70 and the retaining ring groove. In some embodiments, the rotating shaft 61 can also be designed as an external spline structure, and the corresponding sun gear 31 is designed as an internal spline structure.

[0050] Furthermore, if Fig. 9 As shown, the floating gear ring adopts a thin-walled flexible inner gear ring design, and the loads of each planetary gear are uniformly reduced by relying on the elastic deformation of the gear itself to reduce vibration. Specifically, the outer ring of the gear ring 35 is provided with an external spline 351, and the housing 10 is correspondingly provided with a keyway 11 adapted to the external spline on the gear ring 35. The support connection design of the two can limit the rotation of the gear ring 35. Further, in order to avoid the occurrence of the unbalanced load phenomenon of the tooth surface load caused by this support method, a reinforcement ring 352 is provided on the upper end face of the rim of the gear ring 35, and the rim of the reinforcement ring 352 is uniformly provided with a plurality of inner holes 353 in the circumferential direction. The inner holes 353 are used to install the pins 36, and the housing 10 is correspondingly provided with mounting holes 12 adapted to the pins 36. In a preferred embodiment, the gear ring 35 is provided with 6 inner holes 353, and the pins 36 are correspondingly inserted into the inner holes 353 and the mounting holes. The housing 10 is also provided with a hole snap ring groove, which is engaged with a large snap ring to limit the position of the gear ring 35 in the axial direction. It should be noted that the load-balancing structure in the planetary gear reducer of the present invention is not limited to the structural combination in the above-mentioned embodiment, and may also be other structural designs that can achieve the purpose of load-balancing.

[0051] Furthermore, the housing 10 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 10 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 10. In order to further improve the reliability of the utility model, each gear and bearing in the vehicle drive device should be fully lubricated, and the lubrication forms include various forms such as stirring oil lubrication and forced lubrication.

[0052] In actual use, the working principle of the vehicle drive device of the utility model can be:

[0053] 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 part 51 and the second output part 52 rotate at the same speed, and the first half-shaft gear 44 and the second half-shaft gear 45 fixedly connected to the first output part 51 and the second output part 52 respectively rotate at the same speed. In this way, the first half-shaft gear 44 and the second half-shaft gear 45 will not rotate relative to the planetary carrier 20. At the same time, since the fifth planetary gear 43 is used as an idler gear, during the straight-line driving of the vehicle, the fifth planetary gear 2 will only revolve and will not rotate on its own. The power output path in the above process is as follows: the power and torque output by the power motor 60 are first input into the planetary gear reducer, and then output to the planetary gear differential through the planetary carrier 20. Specifically, the power and torque output by the power motor 60 enter the planetary gear differential through the rotating shaft 61, the sun gear 31, the first planetary gear 32, the second planetary gear 33 and the planetary carrier 20. Under the action of the parallel axis in the planetary gear differential, The power and torque input by the planetary carrier 20 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 third planetary gear 41, the fifth planetary gear 43 and the first half-shaft gear 44 and output through the first output part 51, and the second output line 102 is transmitted by the fourth planetary gear 42 and the second half-shaft gear 45 and output through the second output part 52, thereby achieving the purpose of transmitting the driving torque input from the power motor 60 to the left and right wheels of the vehicle without generating a rotation difference between the left and right wheels.

[0054] 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 51 and the second output unit 52 fixedly connected to the left and right wheels are also different. In other words, a differential is generated between the first output unit 51 and the second output unit 52. In this case, the third planetary gear 41 and the fourth planetary gear 42 will rotate, and the fifth planetary gear 43 meshing with the third planetary gear 41 will also rotate. The design of the same number of teeth of the corresponding gears in the planetary gear differential of the utility model can ensure that the speed ratio from the third planetary gear 41 to the first output unit 51 is equal to the speed ratio from the fourth planetary gear 42 to the second output unit 52, so that the vehicle has the same power performance when turning left and right, and the speed difference between the left and right wheel ends of the vehicle is small, thereby improving the driving performance of the vehicle.

[0055] In summary, the beneficial effects of the vehicle drive device of the utility model are: by designing a planetary gear reducer with coaxial input and output and a planetary gear differential with parallel axis design, the axial size of the drive device is 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 gear reducer and the planetary gear differential to share a planet carrier, the axial length of the overall drive device is initially reduced. Further, by designing the first half-shaft gear and the second half-shaft gear arranged in parallel in the planetary gear differential, and adding the third planetary gear, the fourth planetary gear and the fifth planetary 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. In addition, it can also keep the speed difference between the left and right wheel ends of the whole vehicle in various driving environments within a smaller speed difference range, ensure the driving performance of the whole vehicle, and greatly improve the driving experience of the user.

[0056] Embodiment 2

[0057] Please refer to Figure 10 to Figure 11 , shown is a transmission principle diagram and a power transmission route diagram of the vehicle drive device in the second embodiment of the utility model. The difference between the vehicle drive device in this embodiment and the vehicle drive device in the first embodiment is that the structures of the planetary gear reducer and the planetary gear differential are arranged side by side.

[0058] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", 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 utility model. 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 can be combined in any one or more embodiments or examples in a suitable manner.

[0059] The above-mentioned embodiments only express several implementation methods of the utility model, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent of the utility model. 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 utility model, and these all belong to the protection scope of the utility model. Therefore, the protection scope of the utility model patent shall be based on the attached claims.

Claims

1. A vehicle drive device, characterized in that: It comprises a housing, a planetary gear reducer and a planetary gear differential arranged inside the housing, wherein the planetary gear reducer and the planetary gear differential share a planet carrier; The planetary gear differential includes a third planetary gear, a fourth planetary gear, a fifth planetary gear, a first half-shaft gear, a second half-shaft gear, a second planetary gear shaft and a third planetary gear shaft, the first half-shaft gear and the second half-shaft gear are coaxially arranged, the fifth planetary gear is respectively meshed with the third planetary gear and the first half-shaft gear, the fourth planetary gear is meshed with the second half-shaft gear, the third planetary gear is connected with the fourth planetary gear to form a second double-coupled planetary gear, the second double-coupled planetary gear is connected to the planet carrier through the second planetary gear shaft, and the fifth planetary gear is connected to the planet carrier through the third planetary gear shaft.

2. The vehicle drive device according to claim 1, characterized in that: The third planetary gear has the same number of teeth as the fourth planetary gear, and the diameter of the third planetary gear is smaller than the diameter of the fourth planetary gear.

3. The vehicle drive device according to claim 1, characterized in that: The first side shaft gear and the second side shaft gear have the same number of teeth, and the diameter of the first side shaft gear is smaller than the diameter of the second side shaft gear.

4. The vehicle drive device according to claim 1, characterized in that: The planetary gear differential includes at least one of the second double planetary gears and the fifth planetary gear, and the second double planetary gears and the fifth planetary gear are evenly arranged along the circumference of the second side gear.

5. The vehicle drive device according to claim 1, characterized in that: The planetary gear reducer includes a sun gear, a first planetary gear, a second planetary gear, a first planetary gear shaft and a ring gear, wherein the first planetary gear is meshed with the sun gear, the second planetary gear is meshed with the ring gear, and the ring gear is connected to the housing, wherein the first planetary gear is connected to the second planetary gear to form a first double-coupled planetary gear, and the first double-coupled planetary gear is connected to the planet carrier through the first planetary gear shaft.

6. The vehicle drive device according to claim 5, characterized in that: The planetary gear reducer includes at least one of the first double planetary gears, and the first double planetary gears are evenly arranged along the circumference of the sun gear.

7. The vehicle drive device according to claim 5, characterized in that: The number of the first double-linked planetary gears is the same as that of the second double-linked planetary gears, and the first double-linked planetary gears and the second double-linked planetary gears are staggered in the circumferential direction of the planet carrier; The first double planetary gear and the second double planetary gear are overlapped in the axial direction of the planet carrier.

8. The vehicle driving device according to claim 5, characterized in that: The vehicle drive device also includes a first output unit and a second output unit, and the vehicle drive device is connected to the wheels on both sides of the vehicle through the first output unit and the second output unit respectively, wherein the first output unit is connected to the first half-shaft gear, and the second output unit is connected to the second half-shaft gear.

9. The vehicle drive device according to claim 8, characterized in that: The vehicle drive device also includes a power motor, which is detachably connected to the housing. The power motor includes a rotating shaft connected to the sun gear. The rotating shaft, the first output part, the second output part and the sun gear are coaxially arranged, and the second output part is independently arranged from the rotating shaft and passes through the center of the rotating shaft.

10. The vehicle driving device according to claim 9, characterized in that: A snap ring is provided at the connection position between the rotating shaft and the sun gear to limit the axial movement of the sun gear; a plurality of pins are provided on the circumference of the gear ring, and the gear ring is connected to the housing through the plurality of pins.

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