Electric differential drive axle with planetary gear structure

Abstract

The present invention relates to the technical field of drive axles, specifically an electric differential drive axle with a planetary gear structure, comprising a differential assembly and a drive assembly, wherein the drive assembly comprises a reduction assembly, the reduction assembly being dynamically connected to a first input shaft; and an input gear, the input gear being coaxially fixedly connected to a second input shaft; the differential assembly comprises a first housing and a second housing, a first differential being rotationally connected between a support plate and the first housing, a second differential being rotationally connected between the support plate and the second housing, the first differential being transmission-connected to a first output shaft, and the second differential being transmission-connected to a second output shaft. The first differential and the second differential are transmission-connected via a transmission shaft. The system is capable of switching between different operating modes, taking into account power consumption economy, having a wide range of applicable scenarios, and reducing overall power consumption; there is no need to set up a very complex motor drive control system, nor is there any need to control wheel speed or drive wheel slip rate, thus simplifying the control system, improving operating accuracy, and saving costs.

Description

Technical Field

[0001] The present invention relates to the technical field of drive axles, and in particular to an electric differential drive axle with a planetary gear structure. Background Art

[0002] The drive axle, located at the end of the drivetrain, converts the speed and torque from the transmission and transmits them to the drive wheels. It withstands vertical, longitudinal, and lateral forces acting between the road surface and the vehicle frame or body, as well as braking torque and reaction forces. A drive axle typically consists of a final drive, differential, wheel drive system, and drive axle housing. Steering drive axles also include constant velocity joints. With the development of automobiles, integrated motor drive axles are becoming increasingly common.

[0003] There are two main types of existing electric drive axles: the first is a single-motor drive axle, and the second is a dual-motor drive axle. This type of drive axle can achieve distributed drive, control the speed and torque of each drive wheel, and realize electronic differential performance.

[0004] As the pace of commercial vehicle new energy gradually accelerates, the multi-axle drive medium and heavy truck form has gradually changed from the traditional structure to the integrated electric drive axle structure. The electric drive axle generally adopts the operation mode of dual motor simultaneous drive. For load-carrying and towing vehicles, the dual-motor drive operation mode is undoubtedly more superior for operation guarantee in full load and climbing states; but it cannot take into account the economic efficiency of power consumption. For example, for operation in an empty state, since its own weight may be about one-third of the full-load gross weight (empty weight ratio), the dual-motor drive mode is not flexible enough and has the problem of huge power consumption. It has the defects of limited applicable application scenarios and high overall power consumption.

[0005] At the same time, the dual-motor drive system involves very complex motor drive control, especially the electronic differential and drive anti-skid control technology between the wheels. It mainly uses wheel speed or drive wheel slip rate as the control target, resulting in a complex control system, large size, low precision, and inability to adapt to different road surfaces.

[0006] Therefore, an electric differential drive axle with a planetary gear structure is needed to solve the above technical problems. Summary of the Invention

[0007] The purpose of the present invention is to solve the above problems and provide an electric differential drive axle with a planetary gear structure.

[0008] An electric differential drive axle with a planetary gear structure is provided, comprising a differential assembly and a drive assembly. The drive assembly comprises a housing, a partition is provided in the middle of the housing, one side of the partition is rotatably connected to a reduction assembly, and the reduction assembly is dynamically connected to a first input shaft; the other side of the partition is rotatably connected to an input gear, and the input gear is coaxially fixedly connected to a second input shaft;

[0009] The differential assembly includes a first housing and a second housing, the first housing and the second housing are symmetrically arranged, the first housing and the second housing are fixedly connected by a support plate, the first differential is rotationally connected between the support plate and the first housing, the second differential is rotationally connected between the support plate and the second housing, the first differential is drivingly connected to the first output shaft, and the second differential is drivingly connected to the second output shaft.

[0010] The first differential and the second differential are connected via a transmission shaft.

[0011] Furthermore, the reduction assembly includes an inner gear ring fixedly connected to the inner wall of the housing, and three third planetary gears are evenly distributed on the inner side of the inner gear ring and are meshed with each other. The three third planetary gears are all meshed with the same center gear, and the center gear is coaxially fixedly connected to the first input shaft.

[0012] The three third planetary gears are rotatably sleeved on the three planetary rods respectively. The three planetary rods are fixed on the side of the planetary carrier. A rotating shaft is fixed on the other side of the planetary carrier. The rotating shaft is rotatably set on the partition. The planetary carrier is coaxially bolted to the output ring gear. The number of teeth and module of the output ring gear are the same as those of the input gear.

[0013] Furthermore, the first differential includes a first differential ring gear, which is coaxially connected to the fixed frame with bolts, and the second sleeve and the first sleeve are respectively bolted to the sides of the first differential ring gear and the fixed frame away from each other, the second sleeve and the support plate are rotatably connected through a bearing, the first sleeve and the first housing are rotatably connected through a bearing, and the first differential ring gear is meshed with the output ring gear of the reduction assembly.

[0014] Furthermore, a second center tooth is rotatably provided at the center of the fixed frame, the second center tooth is coaxially fixedly connected to the first output shaft, a side of the second center tooth away from the fixed frame is adjacent to the first center tooth, the first center tooth is meshedly connected to three first planetary gears uniformly distributed outside the first center tooth, each of the first planetary gears is meshedly connected to one second planetary gear, each of the second planetary gears is meshedly connected to the second center tooth, and the first planetary gears and the second planetary gears are both rotatably connected between the fixed frame and the first differential ring gear;

[0015] The outer diameter of the first central tooth is smaller than the outer diameter of the second central tooth, and the outer diameter of the first planetary teeth is larger than the outer diameter of the second planetary teeth.

[0016] Furthermore, the first center tooth is coaxially fixedly connected to the transmission shaft, the other end of the transmission shaft is coaxially fixedly connected to the third center tooth of the second differential, and the transmission shaft is rotatably connected between the first differential ring gear and the second differential ring gear of the second differential via a bearing;

[0017] The fourth center tooth of the second differential is coaxially fixedly connected to the second output shaft; the second differential ring gear is meshed with the input gear.

[0018] Furthermore, the first shell and the second shell are both slidably connected to the sliding gear ring, and the outer side of the sliding gear ring is provided with a plurality of sliding strips.

[0019] The end of the sliding gear ring is provided with a plurality of second engaging teeth evenly distributed circumferentially, and the second engaging teeth are engaged with the first engaging teeth provided at the end of the locking gear ring. The locking gear ring is coaxially fixedly connected to the outer sides of the fixing frames of the first differential and the second differential.

[0020] Furthermore, a waist-shaped groove is circumferentially provided on the outer side of one end of the sliding gear ring away from the second engaging tooth, and the eccentric shaft is slidably connected in the waist-shaped groove;

[0021] The eccentric shaft is fixedly arranged at the lower end of the driving pin. The eccentric shaft and the driving pin are eccentrically arranged with respect to each other. The driving pin is rotatably arranged and passes through the first shell and the second shell.

[0022] Furthermore, the first output shaft and the first housing are rotatably connected via a bearing, and the second output shaft and the second housing are rotatably connected via a bearing.

[0023] The present invention has the following beneficial effects: it can switch between different operating modes, taking into account power economy, has a wide range of applicable scenarios, and reduces overall power consumption. By providing a first differential and a second differential, and connecting the first and second differentials via a drive shaft, differential connection is achieved between the wheels at both ends of the differential assembly. This eliminates the need for a complex motor drive control system and the need to control wheel speed or drive wheel slip rate, thus simplifying the control system, improving operational accuracy, and saving costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Various other advantages and benefits will become apparent to those skilled in the art by reading the following detailed description of the preferred embodiment.The accompanying drawings are only for the purpose of illustrating the preferred embodiment and are not to be considered as limiting the present invention.

[0025] Figure 1 It is a schematic diagram of the overall three-dimensional structure of the present invention;

[0026] Figure 2 This is a schematic diagram of the internal structure of the drive assembly of the present invention;

[0027] Figure 3 This is a schematic diagram of the structure of the deceleration assembly of the present invention;

[0028] Figure 4 This is a schematic structural diagram of the deceleration assembly of the present invention in an exploded state;

[0029] Figure 5 This is a schematic diagram of the input gear structure of the present invention;

[0030] Figure 6 Schematic diagram of the differential assembly structure of the present invention;

[0031] Figure 7 Schematic diagram of the structure of the first differential of the present invention;

[0032] Figure 8 This is a schematic structural diagram of the first differential of the present invention from another perspective;

[0033] Figure 9 This is a schematic structural diagram of the first differential in the exploded state of the present invention;

[0034] Figure 10 This is a schematic structural diagram of another explosion state of the first differential of the present invention;

[0035] Figure 11 This is a schematic cross-sectional view of the differential assembly of the present invention;

[0036] Figure 12 This is a schematic diagram of the partial internal structure of the differential assembly of the present invention;

[0037] Figure 13 Schematic diagram of the structure of the driving pin of the present invention.

[0038] Reference numerals:

[0039] 1 differential assembly, 11 first output shaft, 111 second output shaft, 12 first housing, 13 second housing, 14 support plate, 4 first differential, 41 first differential ring gear, 411 fixing bracket, 412 first sleeve, 413 second sleeve, 42 first center gear, 43 first planetary gear, 44 second planetary gear, 45 second center gear;

[0040] 5 second differential, 51 drive shaft, 52 second differential ring gear, 53 third center gear, 54 fourth center gear;

[0041] 2 drive assembly, 21 housing, 211 partition, 22 first input shaft, 23 second input shaft, 231 input gear;

[0042] 3 reduction assembly, 31 inner ring gear, 32 output ring gear, 33 third planetary gear, 34 center gear, 35 planet carrier, 351 planet rod, 352 rotating shaft;

[0043] 61 locking gear ring, 611 first engaging tooth, 62 sliding gear ring, 621 second engaging tooth, 623 waist groove, 624 slide bar, 63 driving pin, 631 eccentric shaft. DETAILED DESCRIPTION

[0044] The present invention will be described in detail below with reference to the accompanying drawings. Figures 1-10As shown, the electric differential drive axle with a planetary gear structure includes a differential assembly 1 and a drive assembly 2. The drive assembly 2 is fixedly connected to the side of the differential assembly 1 and is in driving connection with the differential assembly 1. The drive assembly 2 transmits the power of the two motors to the differential assembly 1, and the differential assembly 1 transmits the power to the wheels, driving the wheels to rotate.

[0045] The drive assembly 2 includes a housing 21, a partition 211 is provided in the middle of the housing 21, one side of the partition 211 is rotatably connected to the reduction assembly 3, and the reduction assembly 3 is power-connected to the first input shaft 22; the other side of the partition 211 is rotatably connected to the input gear 231, and the input gear 231 is coaxially fixedly connected to the second input shaft 23. The first input shaft 22 is connected to a motor in a transmission manner, and the second input shaft 23 is connected to another motor in a transmission manner. The two motors transmit power to the drive assembly 2 through the first input shaft 22 and the second input shaft 23 respectively, and then transmit power to the wheels through the differential assembly 1.

[0046] See also Figure 6 The differential assembly 1 includes a first housing 12 and a second housing 13. The first and second housings 12 and 13 are symmetrically arranged and fixedly connected by a support plate 14. The first differential 4 is rotationally connected between the support plate 14 and the first housing 12, and the second differential 5 is rotationally connected between the support plate 14 and the second housing 13. The first and second differentials 4 and 5 have identical structures and are symmetrically arranged. The first differential 4 is drivingly connected to the first output shaft 11, and the second differential 5 is drivingly connected to the second output shaft 111. The first and second output shafts 111 transmit power to the two wheels, respectively.

[0047] See also Figure 11 The first differential 4 and the second differential 5 are connected to each other via a transmission shaft 51. The transmission shaft 51 can realize power transmission between the first differential 4 and the second differential 5.

[0048] See also Figure 3 and Figure 4 The reduction assembly 3 includes an inner gear ring 31 fixedly connected to the inner wall of the housing 21. Three third planetary gears 33 are evenly distributed on the inner side of the inner gear ring 31 and are meshed with each other. The three third planetary gears 33 are all meshed with the same center gear 34. The center gear 34 is coaxially fixedly connected to the first input shaft 22.

[0049] The three third planetary gears 33 are rotatably sleeved on the three planetary rods 351 respectively. The three planetary rods 351 are fixedly set on the side of the planetary carrier 35. The other side of the planetary carrier 35 is fixedly set with a rotating shaft 352. The rotating shaft 352 is rotatably set on the partition 211. The planetary carrier 35 is coaxially bolted with the output ring gear 32. The number of teeth and module of the output ring gear 32 and the input gear 231 are the same.

[0050] By setting up the reduction assembly 3, the power of the motor is transmitted to the reduction assembly 3 through the first input shaft 22, and the power is transmitted to the planetary carrier 35 through the center gear 34 and the third planetary gear 33 in turn. The planetary carrier 35 drives the output ring gear 32 to rotate to achieve reduced output.

[0051] The output ring gear 32 and the input gear 231 have the same number of teeth and module. After passing through the reduction assembly 3, the rotational speed of the output ring gear 32 is much lower than the rotational speed of the input gear 231. When the rotational speeds of the two motors are the same, power output at different speeds is achieved, and different working conditions can be achieved. For example, when the second input shaft 23 rotates and the first input shaft 22 does not rotate, single-motor high-speed light-load cruising can be achieved. When the second input shaft 23 does not rotate and the first input shaft 22 rotates, low-speed light-load cruising can be achieved, which can adapt to poor road conditions and achieve low-speed travel. When the second input shaft 23 and the first input shaft 22 rotate simultaneously, they adapt to heavy-load conditions, and the wheel speed is adjusted by adjusting the rotational speeds of the two motors.

[0052] See also Figure 7-10 The first differential 4 includes a first differential ring gear 41, which is coaxially bolted to a mounting bracket 411. A second sleeve 413 and a first sleeve 412 are bolted to the sides of the first differential ring gear 41 and mounting bracket 411 facing away from each other. The second sleeve 413 and the support plate 14 are rotationally connected via a bearing, while the first sleeve 412 and the first housing 12 are rotationally connected via a bearing. The second sleeve 413 and the first sleeve 412 rotationally connect the first differential ring gear 41 and the mounting bracket 411 between the first housing 12 and the support plate 14. The first differential ring gear 41 is meshed with the output ring gear 32 of the reduction gear assembly 3. The output ring gear 32 drives the first differential ring gear 41 to rotate, achieving power transmission.

[0053] A second center tooth 45 is provided for rotation at the center of the fixed frame 411. The second center tooth 45 is coaxially fixedly connected to the first output shaft 11. The first output shaft 11 and the fixed frame 411 are rotationally connected via a bearing. The second center tooth 45 is adjacent to the first center tooth 42 on the side away from the fixed frame 411. The first center tooth 42 is meshed with three first planetary gears 43 evenly distributed on the outside of the first center tooth 42. The first planetary gears 43 are each meshed with one second planetary gear 44. The second planetary gears 44 are each meshed with the second center tooth 45. The first planetary gears 43 and the second planetary gears 44 are both rotationally connected between the fixed frame 411 and the first differential ring gear 41. The fixed frame 411 and the first differential ring gear 41 can drive the first planetary gears 43 and the second planetary gears 44 to revolve.

[0054] The outer diameter of the first center tooth 42 is smaller than the outer diameter of the second center tooth 45 , and the outer diameter of the first planetary teeth 43 is larger than the outer diameter of the second planetary teeth 44 .

[0055] See also Figure 11 The first center tooth 42 is coaxially fixedly connected to the transmission shaft 51, and the other end of the transmission shaft 51 is coaxially fixedly connected to the third center tooth 53 of the second differential 5. The transmission shaft 51 is rotatably connected between the first differential ring gear 41 and the second differential ring gear 52 of the second differential 5 through a bearing. The first center tooth 42 is rotatably connected to the first differential 4 through the transmission shaft 51, and the third center tooth 53 is rotatably set on the second differential 5 by the transmission shaft 51.

[0056] The second differential 5 has the same structure as the first differential 4. The fourth center tooth 54 of the second differential 5 is coaxially fixedly connected to the second output shaft 111; the outer side of the fourth center tooth 54 is meshed with the fourth planetary gear identical to the second planetary gear 44, and the outer side of the third center tooth 53 is meshed with the fifth planetary gear identical to the first planetary gear 43. The fourth planetary gear and the fifth planetary gear are rotatably connected to the second differential ring gear 52, and the second differential ring gear 52 drives the fourth planetary gear and the fifth planetary gear to revolve.

[0057] The second differential ring gear 52 is meshed with the input gear 231 , and the input gear 231 drives the second differential ring gear 52 to rotate.

[0058] See also Figure 11-13 The first shell 12 and the second shell 13 are both slidably connected to the sliding ring gear 62, and there are multiple sliding bars 624 on the outside of the sliding ring gear 62. The sliding bars 624 realize the circumferential relative fixation between the sliding ring gear 62 and the first shell 12 and the second shell 13, and provide a guiding function for the axial movement of the sliding ring gear 62.

[0059] A plurality of second engaging teeth 621 are evenly distributed circumferentially at the end of the sliding gear ring 62. The second engaging teeth 621 are engaged with the first engaging teeth 611 arranged at the end of the locking gear ring 61. The locking gear ring 61 is coaxially fixedly connected to the outside of the fixing frame 411 of the first differential 4 and the second differential 5 respectively.

[0060] When the sliding ring gear 62 moves toward the locking ring gear 61, the first engaging tooth 611 and the second engaging tooth 621 engage with each other. At this time, the locking ring gear 61 and the sliding ring gear 62 are relatively fixed, and the fixing frames 411 of the first differential 4 and the second differential 5 are fixed relative to the first housing 12 and the second housing 13 respectively, that is, the first differential ring gear 41 and the second differential ring gear 52 are fixed relative to the first housing 12 and the second housing 13 respectively, thereby realizing the locking of the first differential ring gear 41 and the second differential ring gear 52.

[0061] When the sliding gear ring 62 moves away from the locking gear ring 61, the first engaging teeth 611 and the second engaging teeth 621 are disengaged from each other. At this time, the locking gear ring 61 and the sliding gear ring 62 can rotate relative to each other, and the first differential gear ring 41 and the second differential gear ring 52 are unlocked.

[0062] A waist-shaped groove 623 is circumferentially provided on the outer side of one end of the sliding gear ring 62 away from the second engaging teeth 621 . An eccentric shaft 631 is slidably connected in the waist-shaped groove 623 . The outer diameter of the eccentric shaft 631 is the same as the width of the waist-shaped groove 623 .

[0063] The eccentric shaft 631 is fixedly disposed at the lower end of the driving pin 63 . The eccentric shaft 631 and the driving pin 63 are eccentrically disposed relative to each other. The driving pin 63 is rotatably disposed and respectively penetrates the first housing 12 and the second housing 13 .

[0064] A driving device is provided at one end of the driving pin 63 away from the eccentric shaft 631, and the driving pin 63 is driven to rotate by the driving device, and the position of the driving pin 63 is locked. This belongs to the existing technology and will not be described here. By rotating the eccentric shaft 631, the sliding gear ring 62 is driven away from or close to the locking gear ring 61, and the position of the sliding gear ring 62 is locked.

[0065] See also Figure 11 The first output shaft 11 and the first housing 12 are rotatably connected via a bearing, and the second output shaft 111 and the second housing 13 are rotatably connected via a bearing.

[0066] Working mode: 1. The two motors work at the same time. The sliding ring gear 62 and the locking ring gear 61 at both ends of the first differential 4 and the second differential 5 are in a disengaged state. The locking ring gear 61 and the sliding ring gear 62 can rotate relative to each other. At this time, the first differential ring gear 41 and the second differential ring gear 52 are unlocked. This situation is suitable for heavy loads, and the vehicle speed can be adjusted by controlling the speed of the two motors.

[0067] The motor connected to the reduction assembly 3 is working, and the first differential ring gear 41 of the first differential 4 is in a free rotation state; the motor connected to the input gear 231 is not working, and the second differential ring gear 52 of the second differential 5 is in a locked state.

[0068] At this time, the motor connected to the deceleration component 3 drives the vehicle forward at a low speed, which is suitable for low-speed and light-load situations and adapts to situations with poor road conditions.

[0069] The motor connected to the reduction assembly 3 is not working, and the first differential ring gear 41 of the first differential 4 is in a free and locked state; the motor connected to the input gear 231 is working, and the second differential ring gear 52 of the second differential 5 is in a free rotation state. At this time, the motor drives the vehicle to cruise at high speed, which is suitable for light-load and high-speed movement.

[0070] The present invention can switch between different working modes, taking into account the economic efficiency of power consumption, has a wide range of applicable scenarios, and reduces overall power consumption.

[0071] By providing a first differential 4 and a second differential 5, and connecting the first differential 4 and the second differential 5 via a drive shaft 51, a differential connection of the wheels at both ends of the differential assembly 1 is achieved. There is no need to provide a very complex motor drive control system, nor is there any need to control the wheel speed or drive wheel slip rate, which simplifies the control system, improves operating accuracy, and saves costs.

[0072] The above shows and describes the basic principles, main features, and advantages of the present invention. It should be understood by those skilled in the art that the present invention is not limited to the above embodiments. The above embodiments and descriptions are merely preferred examples of the present invention and are not intended to limit the present invention. Various changes and improvements may be made to the present invention without departing from the spirit and scope of the present invention, and such changes and improvements fall within the scope of the present invention. The scope of protection claimed in the present invention is defined by the appended claims and their equivalents.

Claims

1. An electric differential drive axle with a planetary gear structure, comprising a differential assembly (1) and a drive assembly (2), characterized in that: The driving assembly (2) includes a box body (21), a partition (211) is provided in the middle of the box body (21), and the partition One side of the (211) is rotatably connected to the reduction assembly (3), and the reduction assembly (3) is dynamically connected to the first input shaft (22); the other side of the partition (211) is rotatably connected to the input gear (231), and the input gear (231) is coaxially fixedly connected to the second input shaft (23); The differential assembly (1) includes a first housing (12) and a second housing (13), the first housing (12) and the second housing (13) are symmetrically arranged, the first housing (12) and the second housing (13) are fixedly connected via a support plate (14), the support plate (14) and the first housing (12) are rotatably connected to the first differential (4), the support plate (14) and the second housing (13) are rotatably connected to the second differential (5), the first differential (4) and the first output shaft (11) a transmission connection, wherein the second differential (5) and the second output shaft (111) are in transmission connection; The first differential (4) and the second differential (5) are connected in transmission via a transmission shaft (51); The first differential (4) includes a first differential gear ring (41), the first differential gear ring (41) is coaxially connected to a fixing frame (411) by bolts, the first differential gear ring (41) and the fixing frame (411) are respectively connected to a second sleeve (413) and a first sleeve (412) by bolts on sides away from each other, the second sleeve (413) and the support plate (14) are rotatably connected via a bearing, the first sleeve (412) and the first housing (12) are rotatably connected via a bearing, and the first differential gear ring (41) and the output gear ring (32) of the reduction assembly (3) are meshed and connected; The fixed frame (411) is centrally rotatably provided with a second center tooth (45), the second center tooth (45) and the first output shaft (11) are coaxially fixedly connected, the second center tooth (45) is adjacent to the first center tooth (42) on a side away from the fixed frame (411), the first center tooth (42) is meshedly connected to three first planetary teeth (43) uniformly distributed outside the first center tooth (42), the first planetary teeth (43) are each meshedly connected to a second planetary tooth (44), the second planetary teeth (44) are each meshedly connected to the second center tooth (45), and the first planetary teeth (43) and the second planetary teeth (44) are both rotatably connected between the fixed frame (411) and the first differential gear ring (41); The outer diameter of the first center tooth (42) is smaller than the outer diameter of the second center tooth (45), and the outer diameter of the first planetary tooth (43) is larger than the outer diameter of the second planetary tooth (44); The first center tooth (42) is coaxially fixedly connected to the transmission shaft (51), the other end of the transmission shaft (51) is coaxially fixedly connected to the third center tooth (53) of the second differential (5), and the transmission shaft (51) is rotatably connected between the first differential gear ring (41) and the second differential gear ring (52) of the second differential (5) through a bearing; The fourth center tooth (54) of the second differential (5) is coaxially fixedly connected to the second output shaft (111); The second differential ring gear (52) and the input gear (231) are meshed and connected.

2. The electric differential drive axle with a planetary gear structure according to claim 1, characterized in that: The reduction assembly (3) includes an inner gear ring (31) fixedly connected to the inner wall of the housing (21), three third planetary gears (33) meshing with each other are evenly distributed on the inner side of the inner gear ring (31), the three third planetary gears (33) are all meshingly connected to the same center gear (34), and the center gear (34) is coaxially fixedly connected to the first input shaft (22); The three third planetary gears (33) are respectively rotatably sleeved on the three planetary rods (351). The three planetary rods (351) are all fixedly arranged on the side of the planetary frame (35). The other side of the planetary frame (35) is fixedly arranged with a rotating shaft (352). The rotating shaft (352) is rotatably arranged on the partition (211). The planetary frame (35) is coaxially bolted to the output ring gear (32). The number of teeth and module of the output ring gear (32) and the input gear (231) are the same.

3. The electric differential drive axle with a planetary gear structure according to claim 2, characterized in that: The first shell (12) and the second shell (13) are both slidably connected to the sliding ring gear (62), and the outer side of the sliding ring gear (62) is provided with a plurality of sliding strips (624). A plurality of second engaging teeth (621) uniformly distributed circumferentially are provided at the end of the sliding gear ring (62), and the second engaging teeth (621) are engaged with first engaging teeth (611) provided at the end of the locking gear ring (61), and the locking gear ring (61) is coaxially fixedly connected to the outside of the fixing frame (411) of the first differential (4) and the second differential (5).

4. The electric differential drive axle with a planetary gear structure according to claim 3, characterized in that: A waist-shaped groove (623) is circumferentially provided on the outer side of one end of the sliding gear ring (62) away from the second engaging tooth (621), and the waist-shaped groove (623) is slidably connected to the eccentric shaft (631); The eccentric shaft (631) is fixedly arranged at the lower end of the driving pin (63). The eccentric shaft (631) and the driving pin (63) are eccentrically arranged with respect to each other. The driving pin (63) is rotatably arranged and respectively passes through the first housing (12) and the second housing (13).

5. The electric differential drive axle with a planetary gear structure according to claim 4, characterized in that: The first output shaft (11) and the first housing (12) are rotatably connected via a bearing, and the second output shaft (111) and the second housing (13) are rotatably connected via a bearing.

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