A high-strength, highly responsive front and rear axle electronic differential lock

Abstract

This invention relates to the field of vehicle transmission technology, and more particularly to a high-strength, highly responsive front and rear axle electronic differential lock, comprising a differential housing assembly, a differential gear mechanism, and a differential lock thrust actuator. The rear end of the differential housing mount and the front end of the differential housing cover of the differential housing assembly are connected by differential housing connecting bolts. The differential gear mechanism includes a left half-shaft gear, an embedded cross shaft, planetary gears, and a right locking half-shaft gear. The left half-shaft gear, planetary gears, and right locking half-shaft gear are sequentially meshing bevel gears. A differential lock thrust actuator is located on the rear side of the right locking half-shaft gear to prevent its rotation. In this invention, the differential lock thrust actuator, the embedded cross shaft, and the sliding track plate are all arranged on the differential housing cover, which not only improves the structural compactness of the differential lock but also significantly enhances the differential lock's response speed and locking stability, while reducing the complexity of installation and maintenance.

Description

Technical Field

[0001] This invention relates to the field of vehicle transmission technology, and in particular to a high-strength, highly responsive electronic differential lock for the front and rear axles. Background Technology

[0002] In vehicle drive systems, differential locks are a crucial component. They enable wheel locking during vehicle operation, especially in complex road conditions, thereby improving vehicle passability and stability. Differential locks are used for vehicle extrication. When one wheel slips, many domestic automotive drive axles utilize logic commands to control an electromagnetic coil, generating magnetic force to drive a locking gear that engages with the half-shaft gear, locking the differential housing and half-shaft together. This disables the differential's differential function, transferring torque to one wheel and allowing the vehicle to escape the predicament.

[0003] Then, when the differential is locked, the differential lock will be subjected to a large impact, especially when going off-road over potholes. The severity of the locking conditions will directly affect the impact on the electronically controlled differential. This puts a great strain on the strength of the locking structure inside the differential lock. Such structures often fail due to excessive impact, such as tooth breakage, pin breakage, and pin failure to return to its original position, which in turn leads to the failure of the differential lock function. Moreover, this structure has high requirements for materials and precision, which increases the processing cost.

[0004] While existing electronic differential lock technologies have achieved differential lock functionality to some extent, and some employ a cross-shaft structure, they still have shortcomings in terms of structural strength, response speed, and adaptability. For example, CN116951077A discloses an electronically controlled differential lock device for vehicle extrication; although it involves electromagnetic control, its structure is relatively simple and lacks sufficient strength and response speed to meet the demands of harsh road conditions. CN111677837A describes a jaw-locking differential that achieves the differential's locking function through mechanical locking, but it lacks electromagnetic control and cannot achieve rapid response.

[0005] Furthermore, while CN214367581U is also an electronic differential lock, its structural design and locking mechanism differ significantly from this invention, particularly in the design of the thrust actuator and the embedded cross shaft. CN112918189A proposes a coaxial electric drive axle with a differential lock; although it involves electromagnetic control, its application scenario and structural design are inconsistent with this invention. CN207278827U provides an electromagnetic automotive differential lock, but its locking mechanism is relatively simple and lacks sufficient strength and response speed.

[0006] To address the problems existing in the current technology, it is necessary to propose a high-strength, responsive front and rear axle electronic differential lock structure. By optimizing the differential lock design and adopting innovative solutions such as electromagnetically controlled thrust actuators and embedded cross shafts, the aim is to improve the structural strength, response speed, and overall performance of the differential lock to meet the driving needs of vehicles under different road conditions. Summary of the Invention

[0007] The purpose of this invention is to overcome the shortcomings of the prior art and provide a high-strength, responsive front and rear axle electronic differential lock. The differential lock thrust actuator, embedded cross shaft, and sliding track plate are all arranged on the differential housing cover. The optimized differential lock thrust actuator design not only improves the structural compactness of the differential lock, but also significantly enhances the reaction speed and locking stability of the differential lock. The highly integrated structure also reduces the complexity of installation and maintenance.

[0008] To achieve the objectives of this invention, the technical solution adopted is as follows:

[0009] This invention discloses a high-strength, highly responsive front and rear axle electronic differential lock, comprising a differential housing assembly, a differential gear mechanism, and a differential lock thrust actuator. The differential housing assembly includes a differential housing base, a differential housing cover, and differential housing connecting bolts. The differential housing base has a hollow structure with an open rear end, and the differential housing cover has a hollow structure with an open front end. The rear end of the differential housing base and the front end of the differential housing cover are connected by the differential housing connecting bolts. The differential gear mechanism includes a left half-shaft gear, an embedded cross shaft, and planetary gears. The differential housing includes a gear and a right locking half-shaft gear. The embedded cross shaft has a cross-shaped structure, and its four ends are fitted onto the outer wall of the differential housing assembly. The shaft holes of the four planetary gears are fitted onto the outer wall of the embedded cross shaft. The left half-shaft gear and the right locking half-shaft gear are respectively disposed in the inner cavities of the differential housing seat and the differential housing cover. The left half-shaft gear, the planetary gears, and the right locking half-shaft gear are sequentially matched and meshed bevel gears. The rear side of the right locking half-shaft gear is provided with a differential locking thrust actuator that can prevent its rotation.

[0010] The rear end face of the differential housing and the front end face of the differential housing cover are arranged in a ring with four semi-circular grooves on the housing and the housing cover. The semi-circular grooves on the housing and the housing cover are joined together to form cross shaft holes for fitting the four ends of the embedded cross shaft.

[0011] The embedded cross shaft includes an integrally formed intermediate part and a half shaft. The intermediate part has a square structure with an embedded hole in its middle. The middle part of the outer wall of the intermediate part is connected to the inner end of a half shaft. The outer end of the half shaft is fitted into the cross shaft hole. The rear wall of the left half shaft gear has an embedded ring for fitting into the embedded hole. The rear end of the differential housing cover has an axially arranged annular bushing. The rear end of the right locking half shaft gear has an axially arranged right embedded ring for fitting into the bushing.

[0012] The differential lock thrust actuator includes a serpentine spring, end face pressing teeth, a sliding top pin, a sliding track plate, and a planar thrust bearing. The end face pressing teeth are arranged in a ring structure on the rear side of the inner cavity of the differential housing cover. The outer wall of the end face pressing teeth has a plurality of limiting blocks arranged in a ring. The inner wall of the differential housing cover has a limiting groove that slides with the limiting blocks. The front wall of the end face pressing teeth has an annular groove for placing the serpentine spring. The inner side of the annular groove has a plurality of rear pressing teeth arranged in a ring, with rear pressing tooth grooves formed between adjacent rear pressing teeth. The right lock... The rear wall of the stop half-shaft gear has a ring array of front engagement teeth for meshing with the rear engagement tooth groove; the rear end face of the differential housing has a ring array of four pin holes for the rear end of the sliding pin to pass through, and the front end of the sliding pin is connected to the middle of the rear wall of the limiting block; the sliding track disk is sleeved on the outside of the bushing through the planar thrust bearing, the front wall of the sliding track disk is provided with a spiral sliding track that slides in cooperation with the rear end of the sliding pin, and the rear side of the sliding track disk is provided with an electromagnetic coil assembly for driving the rotation of the sliding track disk.

[0013] The rear end of the sliding pin forms a hemispherical sliding pin spherical surface; the spiral sliding track is a cylindrical spiral structure composed of four spiral track grooves connected end to end, the cross-section of the spiral track groove is an arc-shaped structure equal to the outer diameter of the sliding pin spherical surface, the depth d of the spiral sliding track is 40%~60% of the diameter of the sliding pin spherical surface; the spiral track groove has a "V" shaped structure along its axial direction, the rotation angle θ of the spiral track groove is 15°~25°, and the spiral spacing a is 65mm~75mm.

[0014] The surface roughness of the spiral sliding track is Ra0.8 to Ra1.6, and its surface is treated with nickel plating.

[0015] The electromagnetic coil assembly includes an electromagnetic coil, a coil pressure plate, and a double-layer spiral retaining ring for the shaft. The electromagnetic coil is arranged in a ring structure on the rear side of the sliding track disk. The coil pressure plate is located on the rear side of the electromagnetic coil. The outer diameter of the coil pressure plate is larger than its inner diameter, and the inner diameter of the coil pressure plate is smaller than the double-layer spiral retaining ring for the shaft. The double-layer spiral retaining ring for the shaft is located on the rear side of the coil pressure plate, and the inner ring of the double-layer spiral retaining ring for the shaft is fixed to the outside of the bushing.

[0016] A plurality of differential housing connecting threaded holes are provided between the adjacent semi-circular grooves of the housing cover for threaded connection with the differential housing connecting bolts; a differential housing connecting bolt hole is provided on the front wall of the differential housing seat for the screw of the differential housing connecting bolt to pass through; a plurality of lubrication holes are provided on the front wall of the differential housing seat and the side wall of the differential housing cover.

[0017] The mating area between the embedded cross shaft and the planetary gear is provided with a non-metallic anti-friction coating; the front side of the left half-shaft gear, the outer side of the planetary gear, and the rear side of the right locking half-shaft gear are respectively provided with half-shaft gear shims, planetary gear shims, and right half-shaft gear shims.

[0018] The beneficial effects of this invention are as follows:

[0019] (1) The differential lock thrust actuator, embedded cross shaft and sliding track disk of the present invention are all arranged on the differential housing cover. The optimized differential lock thrust actuator design not only improves the structural compactness of the differential lock, but also significantly improves the reaction speed and locking stability of the differential lock. The highly integrated structure also reduces the complexity of installation and maintenance.

[0020] (2) The electromagnetic coil assembly of the present invention is combined with the differential lock thrust actuator. The sliding top pin is moved by the spiral sliding track, which realizes the rapid locking and unlocking of the differential lock. Compared with the prior art, the present invention has a faster response speed and can adapt to changes in road conditions more quickly, thereby improving the driving stability and safety of the vehicle.

[0021] (3) The present invention provides a non-metallic anti-friction coating at the mating point of the embedded cross shaft and the planetary gear; and provides half-shaft gear shims, planetary gear shims and right half-shaft gear shims to protect the components of the differential gear mechanism, reduce wear between moving parts, and extend the service life of the differential lock.

[0022] (4) The present invention drives the differential lock thrust actuator to lock through the electromagnetic coil assembly, which has a fast response speed, thereby realizing the fast response and precise control of differential lock locking, with higher efficiency and reliability, and meeting the needs of different driving scenarios;

[0023] (5) This invention reduces production costs and manufacturing cycle by optimizing structural design and adopting reasonable manufacturing processes. At the same time, the highly integrated structure also reduces the number of parts and assembly steps, thereby improving production efficiency. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the structure of the present invention;

[0025] Figure 2 This is an exploded view of the differential housing assembly in this invention;

[0026] Figure 3 This is an exploded view of the differential gear mechanism in this invention;

[0027] Figure 4 This is an exploded view of the differential lock thrust actuator in this invention;

[0028] Figure 5 This is an exploded view of the present invention;

[0029] Figure 6 This is a schematic diagram of the sliding track disk in the present invention;

[0030] Figure 7 This is a top view of the sliding track disk in this invention;

[0031] Figure 8 for Figure 7 View A in the middle;

[0032] Figure 9 This is a schematic diagram showing the connection between the differential housing cover and the end face pressing teeth in this invention;

[0033] Figure 10 This is a schematic diagram of the right locking half-shaft gear in this invention.

[0034] In the diagram: 1. Differential housing, 101. Semi-circular groove of housing, 2. Differential housing cover, 201. Semi-circular groove of housing cover, 202. Bushing, 203. Limiting groove, 204. Top pin hole, 205. Threaded hole, 3. Differential housing connecting bolt, 4. Half-shaft gear washer, 5. Left half-shaft gear, 51. Inset ring, 6. Inset cross shaft, 61. Intermediate component, 62. Half-shaft, 63. Inset hole, 7. Planetary gear washer, 8. Planetary gear, 9. Right locking half-shaft gear, 91. Right Embedded ring, 92 front insert tooth, 10 right half-shaft gear washer, 11 serpentine spring, 12 end face pressing insert tooth, 121 limiting block, 122 annular groove, 123 rear insert tooth, 124 rear insert tooth groove, 13 sliding top pin, 131 sliding top pin spherical surface, 14 sliding track disk, 15 flat thrust bearing, 16 electromagnetic coil, 17 coil pressure plate, 18 double-layer spiral retaining ring for shaft, 19 spiral sliding track, 191 spiral track groove, 21 lubrication hole. Detailed Implementation

[0035] The present invention will be further described below:

[0036] Please see Figure 1-10 ,

[0037] This invention discloses a high-strength, highly responsive front and rear axle electronic differential lock, comprising a differential housing assembly, a differential gear mechanism, and a differential lock thrust actuator. The differential housing assembly includes a differential housing base 1, a differential housing cover 2, and differential housing connecting bolts 3. The differential housing base 1 is a hollow structure with an open rear end, and the differential housing cover 2 is a hollow structure with an open front end. The rear end of the differential housing base 1 and the front end of the differential housing cover 2 are joined together and connected by the differential housing connecting bolts 3. The differential gear mechanism includes a left half-shaft gear 5, an embedded cross shaft 6, planetary gears 8, and a right locking half-shaft gear 9. The embedded cross shaft 6 has a cross-shaped structure, and its four ends are fitted onto the outer wall of the differential housing assembly. The shaft holes of the four planetary gears 8 are fitted onto the outer wall of the embedded cross shaft 6. The left half-shaft gear 5 and the right locking half-shaft gear 9 are respectively disposed in the inner cavities of the differential housing 1 and the differential housing cover 2. Planetary gear 8 and right locking half-shaft gear 9 are bevel gears that mesh sequentially. The rear side of the right locking half-shaft gear 9 is provided with a differential lock thrust actuator that can prevent its rotation. The differential lock thrust actuator, embedded cross shaft 6, and sliding track disk 14 are all arranged on the differential housing cover 2. The optimized differential lock thrust actuator design not only improves the structural compactness of the differential lock, but also significantly improves the reaction speed and locking stability of the differential lock. The highly integrated structure also reduces the complexity of installation and maintenance. The differential housing 1 and differential housing cover 2 form a complete differential lock housing assembly. The two are fitted together and connected by differential housing connecting bolts 3. Preferably, four lubrication holes 21 are evenly distributed on the front wall of the differential housing 1 and the side wall of the differential housing cover 2 to ensure the lubrication effect of the differential gear mechanism and the differential lock thrust actuator, while ensuring the transmission of power and impact force of the whole vehicle in the locked / unlocked state. The housing is made of high-strength material and special heat treatment process.

[0038] Furthermore, the rear end face of the differential housing 1 and the front end face of the differential housing cover 2 are arranged in a ring with four semi-circular grooves 101 on the housing and semi-circular grooves 201 on the housing. The semi-circular grooves 101 on the housing and semi-circular grooves 201 on the housing are connected to form cross shaft holes for fitting the four ends of the embedded cross shaft 6, which can play a positioning role and make it easier to install the embedded cross shaft 6 into the differential housing cover 2.

[0039] Furthermore, the embedded cross shaft 6 includes an integrally formed intermediate part 61 and a half shaft 62. The intermediate part 61 has a square structure with an embedded hole 63 in its middle. The middle part of the outer wall of the intermediate part 61 is connected to the inner end of a half shaft 62, and the outer end of the half shaft 62 is fitted into the cross shaft hole. The rear wall of the left half shaft gear 5 is provided with an embedded ring 51 for fitting into the embedded hole 63. The rear end of the differential housing cover 2 is axially provided with an annular bushing 202, and the rear end of the right locking half shaft gear 9 is axially provided with a bushing 202 for fitting into the cross shaft hole. The right inner ring 91 inside the bushing 202, the inner cross shaft 6 is integrally set, replacing the traditional method of splicing two long shafts and two short shafts, which improves the stability of the cross shaft when the differential is running. At the same time, the inner ring 51 on the left half shaft gear 5 side is embedded in the inner hole 63 to limit and avoid the left half shaft gear 5. The structure of the inner cross shaft 6 can ensure that the two half shafts will not form two design states due to different spline positions, making the overall structure of the differential lock very compact and able to meet the needs of different vehicles.

[0040] Furthermore, the differential locking thrust actuator includes a serpentine spring 11, end face pressing teeth 12, a sliding top pin 13, a sliding track disk 14, and a planar thrust bearing 15. The end face pressing teeth 12 are arranged in an annular structure on the rear side of the inner cavity of the differential housing 2. The outer wall of the end face pressing teeth 12 has a plurality of limiting blocks 121 arranged in an annular array. The inner wall of the differential housing 2 is provided with a limiting groove 203 that slides with the limiting blocks 121. The front wall of the end face pressing teeth 12 is provided with an annular groove 122 for placing the serpentine spring 11. The inner side of the annular groove 122 has a plurality of rear teeth 123 arranged in an annular array, and a rear tooth groove 124 is formed between adjacent rear teeth 123. The rear wall of the right locking half-shaft gear 9 has a circular array of front engagement teeth 92 for meshing with the rear engagement tooth groove 124; the rear end face of the differential housing 2 has a circular array of four pin holes 204 for the rear end of the sliding pin 13 to pass through, and the front end of the sliding pin 13 is connected to the middle of the rear wall of the limiting block 121; the sliding track disk 14 is sleeved on the outside of the bushing 202 through the planar thrust bearing 15, the front wall of the sliding track disk 14 is provided with a spiral sliding track 19 that slides with the rear end of the sliding pin 13, and the rear side of the sliding track disk 14 is provided with an electromagnetic coil assembly for driving the sliding track disk 14 to rotate, and the engagement teeth are pressed by the end face. The outer wall of the differential cover 2 has a series of limiting blocks 121 arranged in a ring and the limiting grooves 203 on the inner wall of the differential cover 2. The rear end face of the differential cover 2 has four pin holes 204 arranged in a ring for the rear end of the sliding pin 13 to pass through. This ensures that the end face pressing teeth 12 and the sliding pin 13 can slide back and forth stably, so that the end face pressing teeth 12 can mesh and lock with the right locking half shaft gear 9. Specifically, in the initial state, the sliding pin 13 is located at the lowest point of the spiral track groove 19. When the electromagnetic coil assembly drives the sliding track disk 14 to rotate, the sliding pin 13 moves along the sliding track groove 19 to the highest point. The sliding pin 13 can push the end face pressing teeth 12 connected to its front end forward. When the differential lock is engaged, the serpentine spring 11 is compressed, and the rear tooth groove 124 on the front wall of the end face tooth 12 can mesh with the front tooth 92 on the rear wall of the right locking half shaft gear 9, thereby locking the differential. When the differential lock is to be released, the electromagnetic coil assembly is de-energized, and the serpentine spring 11 resets to provide a reverse thrust, disengaging the end face tooth 12 from the right locking half shaft gear 9. The sliding top pin 13 causes the sliding track disk 14 to return to its original position, thereby releasing the differential lock. The differential lock thrust actuator is mounted on the differential housing cover 2. The locking actuator has a short stroke and a compact overall structure, improving the stability of the differential when performing the locking action and the overall structural strength of the differential lock.

[0041] Further, such as Figure 6-8As shown, the rear end of the sliding pin 13 forms a hemispherical sliding pin spherical surface 131. The spiral sliding track 19 is a cylindrical spiral structure composed of four spiral track grooves 191 connected end to end. The cross-section of the spiral track groove 191 is an arc-shaped structure with the same outer diameter as the sliding pin spherical surface 131, so that the sliding pin spherical surface 131 can completely fit with the spiral track groove 191 and is not easy to derail. The track radius R is determined according to the distribution circle of the sliding pin, and the depth d of the spiral sliding track 19 is used to limit the movement of the sliding pin. The movement can be set according to 40%~60% of the diameter of the spherical surface 131 of the sliding top pin; the spiral track groove 191 has a "V" shaped structure along its axial direction, the rotation angle of the spiral track groove 191 is θ=15°~25°, the spiral spacing a=65mm~75mm, the surface roughness of the spiral sliding track 19 is Ra0.8~Ra1.6, and its surface is treated with nickel plating process to make the spiral sliding track 19 smooth and wear-resistant, thereby guiding the sliding top pin 13 to slide smoothly along the spiral path on the spiral sliding track 19.

[0042] The cylindrical helix shape of the helical sliding track 19 is described by the following parametric equation: In a three-dimensional rectangular coordinate system, the parametric equation of the helix can be expressed as:

[0043] x = r * cos(θ)

[0044] y = r * sin(θ)

[0045] Z=a*θ

[0046] in:

[0047] r is the helix radius.

[0048] θ is the rotation angle of the helix.

[0049] 'a' is the helical pitch, which represents the distance the helical spiral rises along the z-axis with each revolution.

[0050] The spiral sliding track 19 is composed of four spiral track grooves 191 connected end to end. The spiral track grooves 191 are cylindrical spiral grooves. Each spiral track groove 191 is composed of a left cylindrical spiral groove (for locking the vehicle forward) and a right cylindrical spiral groove (for locking the vehicle backward). The intersection is chamfered to form a complete "V" shaped spiral track groove 191.

[0051] Furthermore, the electromagnetic coil assembly includes an electromagnetic coil 16, a coil pressure plate 17, and a double-layer spiral retaining ring 18 for the shaft. The electromagnetic coil 16 is arranged in a ring structure on the rear side of the sliding track disk 14. The coil pressure plate 17 is located on the rear side of the electromagnetic coil 16. The outer diameter of the coil pressure plate 17 is larger than its inner diameter, and the inner diameter of the coil pressure plate 17 is smaller than that of the double-layer spiral retaining ring 18 for the shaft. The double-layer spiral retaining ring 18 for the shaft is located on the rear side of the coil pressure plate 17. The inner ring of the double-layer spiral retaining ring 18 for the shaft is fixed to the outside of the bushing 202. The electromagnetic coil 16 is fixed to the outside of the bushing 202 by the coil pressure plate 17 and the double-layer spiral retaining ring 18 for the shaft, ensuring that the electromagnetic coil 16 can rotate. When the electromagnetic coil 16 is energized by a conducting current, the electromagnetic coil 16 generates magnetism, attracting the sliding track disk 14 on its front side and causing the sliding track disk 14 to rotate around the bushing 202. In the initial state, the sliding top pin 13 is located at the lowest point of the spiral track groove 19. When the sliding track disk 14 rotates, the sliding top pin 13 moves along the sliding track groove 19 to the highest point. The sliding top pin 13 can push the end face pressing tooth 12 connected to its front end forward. At this time, the serpentine spring 11 is in a compressed state, and the rear tooth groove 124 on the front wall of the end face pressing tooth 12 can match and mesh with the front tooth 92 on the rear wall of the right locking half shaft gear 9, thereby locking the differential. When the differential locking effect is to be released, the electromagnetic coil 16 is de-energized and no longer provides the attraction force. The serpentine spring 11 resets and provides the reverse thrust, disengaging the end face tooth 12 from the right locking half shaft gear 9. The sliding top pin 13 causes the sliding track disk 14 to return to its original position, thereby releasing the differential lock. The electromagnetic coil 16 control technology has a fast response speed, thereby achieving rapid response and precise control of the differential lock, with higher efficiency and reliability.

[0052] Furthermore, a plurality of differential housing connecting threaded holes 205 are provided between adjacent semi-circular grooves 201 of the housing cover for threaded connection with differential housing connecting bolts 3; the front wall of the differential housing seat 1 is provided with differential housing connecting bolt holes through which the screw of the differential housing connecting bolt 3 passes, so that the threaded holes 205 and the semi-circular grooves 201 of the housing cover are staggered to improve the connection strength.

[0053] Furthermore, a non-metallic anti-friction coating is provided at the mating point between the embedded cross shaft 6 and the planetary gear 8; half-shaft gear shims 4, planetary gear shims 7 and right half-shaft gear shims 10 are respectively provided on the front side of the left half-shaft gear 5, the outer side of the planetary gear 8 and the rear side of the right locking half-shaft gear 9, to protect the components of the differential gear mechanism, reduce wear between moving parts and extend the service life of the differential lock.

[0054] The above description is merely an embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent modifications made based on the content of the present invention specification and drawings, or direct or indirect applications in related technical fields, are similarly included within the patent protection scope of the present invention.

Claims

1. A high-strength, highly responsive front and rear axle electronic differential lock, characterized in that: This includes the differential housing assembly, the differential gear mechanism, and the differential lock thrust actuator. The differential housing assembly includes a differential housing base (1), a differential housing cover (2), and differential housing connecting bolts (3). The differential housing base (1) has a hollow structure with an open rear end, and the differential housing cover (2) has a hollow structure with an open front end. The rear end of the differential housing base (1) and the front end of the differential housing cover (2) are connected by the differential housing connecting bolts (3). The differential gear mechanism includes a left half-shaft gear (5), an embedded cross shaft (6), planetary gears (8), and a right locking half-shaft gear (9). The embedded cross shaft (6) has a cross-shaped structure, and the four ends of the embedded cross shaft (6) are fitted onto the outer wall of the differential housing assembly. The shaft holes of the four planetary gears (8) are fitted onto the outer wall of the embedded cross shaft (6). The left half-shaft gear (5) and the right locking half-shaft gear (9) are respectively disposed in the inner cavities of the differential housing seat (1) and the differential housing cover (2). The left half-shaft gear (5), the planetary gears (8), and the right locking half-shaft gear (9) are bevel gears that mesh sequentially. The rear side of the right locking half-shaft gear (9) is provided with a differential locking thrust actuator that can prevent its rotation; the rear end of the differential housing (2) is axially provided with an annular bushing (202), and the rear end of the right locking half-shaft gear (9) is axially provided with a right inner ring (91) for fitting inside the bushing (202); the differential locking thrust actuator includes a serpentine spring (11), an end face pressing tooth (12), a sliding top pin (13), a sliding track disk (14), and a planar thrust bearing (15). The end face pressing tooth (12) is arranged in an annular structure on the rear side of the inner cavity of the differential housing (2), and the end face pressing tooth (12) is externally... The differential cover (2) has a plurality of limiting blocks (121) arranged in a ring on the wall. The inner wall of the differential cover (2) is provided with a limiting groove (203) that slides with the limiting blocks (121). The front wall of the end face pressing tooth (12) is provided with an annular groove (122) for placing the serpentine spring (11). The inner side of the annular groove (122) has a plurality of rear insert teeth (123) arranged in a ring on the inner side. A rear insert tooth groove (124) is formed between adjacent rear insert teeth (123). The rear wall of the right locking half shaft gear (9) has a front insert teeth (92) arranged in a ring on the rear wall for matching and meshing with the rear insert tooth groove (124). The rear end face of the differential cover (2) is annular. The array has four pin holes (204) through which the rear end of the sliding pin (13) passes. The front end of the sliding pin (13) is connected to the middle of the rear wall of the limiting block (121). The sliding track disk (14) is sleeved on the outside of the bushing (202) through the planar thrust bearing (15). The front wall of the sliding track disk (14) is provided with a spiral sliding track (19) that slides in cooperation with the rear end of the sliding pin (13). The rear side of the sliding track disk (14) is provided with an electromagnetic coil assembly for driving the sliding track disk (14) to rotate. The rear end of the sliding pin (13) forms a hemispherical sliding pin spherical surface (131).The spiral sliding track (19) is a cylindrical helical structure composed of four spiral track grooves (191) connected end to end. The cross-section of the spiral track groove (191) is an arc-shaped structure with the same outer diameter as the sliding pin spherical surface (131). The depth d of the spiral sliding track (19) is 40% to 60% of the diameter of the sliding pin spherical surface (131). The spiral track groove (191) has a "V" shape along its axial direction. The rotation angle θ of the spiral track groove (191) is 15° to 25°, and the spiral spacing a is 65mm to 75mm.

2. The high-strength, highly responsive front and rear axle electronic differential lock according to claim 1, characterized in that: The rear end face of the differential housing (1) and the front end face of the differential housing cover (2) are arranged in a ring with four housing semicircular grooves (101) and housing cover semicircular grooves (201). The housing semicircular grooves (101) and housing cover semicircular grooves (201) are connected to form cross shaft holes for fitting the four ends of the embedded cross shaft (6).

3. A high-strength, highly responsive front and rear axle electronic differential lock according to claim 2, characterized in that: The embedded cross shaft (6) includes an integrally formed intermediate part (61) and a half shaft (62). The intermediate part (61) has a square structure and an embedded hole (63) in its middle. The middle part of the outer wall of the intermediate part (61) is connected to the inner end of a half shaft (62). The outer end of the half shaft (62) is fitted into the cross shaft hole. The rear wall of the left half shaft gear (5) is provided with an embedded ring (51) for fitting into the embedded hole (63).

4. A high-strength, highly responsive front and rear axle electronic differential lock according to claim 1, characterized in that: The surface roughness of the spiral sliding track (19) is Ra0.8 to Ra1.6, and its surface is treated with nickel plating.

5. A high-strength, highly responsive front and rear axle electronic differential lock according to claim 1, characterized in that: The electromagnetic coil assembly includes an electromagnetic coil (16), a coil pressure plate (17), and a double-layer spiral retaining ring (18) for shaft. The electromagnetic coil (16) is arranged in a ring structure on the rear side of the sliding track disk (14). The coil pressure plate (17) is arranged on the rear side of the electromagnetic coil (16). The outer diameter of the coil pressure plate (17) is larger than the inner diameter of the coil pressure plate (17). The inner diameter of the coil pressure plate (17) is smaller than the double-layer spiral retaining ring (18) for shaft. The double-layer spiral retaining ring (18) for shaft is arranged on the rear side of the coil pressure plate (17). The inner ring of the double-layer spiral retaining ring (18) for shaft is fixed to the outside of the bushing (202).

6. A high-strength, highly responsive front and rear axle electronic differential lock according to claim 2, characterized in that: A plurality of differential housing connection threaded holes (205) for threaded connection with differential housing connection bolts (3) are provided between adjacent semi-circular grooves (201) of the housing cover; a differential housing connection bolt hole for the screw of the differential housing connection bolt (3) to pass through is provided on the front wall of the differential housing seat (1); a plurality of lubrication holes (21) are provided on the front wall of the differential housing seat (1) and the side wall of the differential housing cover (2).

7. A high-strength, highly responsive front and rear axle electronic differential lock according to claim 1, characterized in that: The embedded cross shaft (6) and the planetary gear (8) are provided with a non-metallic anti-friction coating; the front side of the left half shaft gear (5), the outer side of the planetary gear (8) and the rear side of the right locking half shaft gear (9) are respectively provided with half shaft gear shims (4), planetary gear shims (7) and right half shaft gear shims (10).

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