Front and rear axle electronic differential lock with high strength and sensitive response

Abstract

The invention relates to the technical field of vehicle transmission, in particular to a high-strength and sensitive-response electronic differential lock for a front axle and a rear axle, which comprises a differential shell assembly, a differential gear mechanism and a differential lock thrust actuating mechanism, the rear end of a differential case seat of the differential case assembly is connected with the front end of a differential case cover through the differential case connecting bolt after being butted; the differential mechanism gear mechanism comprises a left half axle gear, an embedded cross axle, a planetary gear and a right locking half axle gear, and the left half axle gear, the planetary gear and the right locking half axle gear are bevel gears which are sequentially matched and meshed; a differential locking thrust executing mechanism capable of preventing the right locking half axle gear from rotating is arranged on the rear side of the right locking half axle gear. According to the differential lock, the thrust executing mechanism, the embedded cross shaft and the sliding rail disc are all arranged on the differential shell cover, so that the structural compactness of the differential lock is improved, the response speed and the locking stability of the differential lock are remarkably improved, and the complexity of installation and maintenance is reduced.

Description

Technical Field

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

[0002] In the vehicle drive system, the differential lock is an important component. It can realize the locking function between the wheels during the vehicle driving process, especially under complex road conditions, so as to improve the vehicle's passability and driving stability. The differential lock is used to get the whole vehicle out of trouble. When the wheels on one side of the vehicle slip, the domestic automobile drive axle mostly uses the use of logic instructions to control the electromagnetic coil to generate magnetic force, push the tooth gear to connect with the half-axle gear, lock the differential case and the half-axle into one, make the differential lose the differential function, and transmit the torque to one side of the wheel, so as to get the vehicle out of trouble.

[0003] Then when the differential is locked, the differential lock will be subjected to a greater impact, especially when off-roading over a pit. The severity of the locking conditions will directly affect the magnitude of the impact on the electronically controlled differential, which puts a greater test on the strength of the locking structure in the differential lock. This type of structure often fails due to excessive impact, resulting in faults such as tooth chipping, ejector pin breakage, and ejector pin failure to return to its original position, which in turn leads to the failure of the differential lock function. In addition, the structure has high requirements on materials and precision, which increases the processing cost.

[0004] Although the existing electronic differential lock technology has achieved the function of differential lock to a certain extent and also adopts a cross-axis structure, it still has deficiencies in structural strength, reaction speed and adaptability. For example, CN116951077A discloses an electronically controlled differential lock device for vehicle escape. Although it involves electromagnetic control, its structure is relatively simple and lacks sufficient strength and reaction speed to cope with the needs under harsh road conditions. CN111677837A describes a tooth-locking differential that realizes the locking function of the differential through mechanical locking, but it lacks electromagnetic control and cannot achieve rapid response.

[0005] In addition, although CN214367581U is also an electronic differential lock, its structural design and locking mechanism are significantly different from the present invention, especially 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 the present invention. CN207278827U provides an electromagnetic automobile differential lock, whose locking mechanism is relatively simple and lacks sufficient strength and reaction speed.

[0006] In view of the problems existing in the prior art, it is necessary to propose a high-strength and responsive front and rear axle electronic differential lock structure. By optimizing the design of the differential lock and adopting innovative solutions such as electromagnetically controlled thrust actuators and embedded cross shafts, the structural strength, response speed and overall performance of the differential lock are improved to meet the driving needs of the vehicle under different road conditions. Summary of the invention

[0007] The purpose of the present 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, the embedded cross shaft and the sliding track plate are all arranged on the differential case 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.

[0008] In order to achieve the purpose of the present invention, the technical solution adopted by the present invention is: The present invention discloses a high-strength and responsive front and rear axle electronic differential lock, comprising a differential case assembly, a differential gear mechanism and a differential lock thrust actuator, wherein the differential case assembly comprises a differential case seat, a differential case cover and differential case connecting bolts, wherein the differential case seat is a hollow structure with a rear end opening, and the differential case cover is a hollow structure with a front end opening, wherein the rear end of the differential case seat and the front end of the differential case cover are butted and connected by the differential case connecting bolts; the differential gear mechanism comprises a left half-shaft gear, an embedded cross shaft, a planetary gear ... gear and right locking half-shaft gear, the embedded cross shaft is in a "cross" shape, and the four ends of the embedded cross shaft are sleeved on the outer wall of the differential case assembly; the shaft holes of the four planetary gears are sleeved on the outer wall of the embedded cross shaft; the left half-shaft gear and the right locking half-shaft gear are respectively arranged in the inner cavity of the differential case seat and the differential case cover, and the left half-shaft gear, the planetary gear and the right locking half-shaft gear are bevel gears that are matched and meshed in sequence; the rear side of the right locking half-shaft gear is provided with the differential locking thrust actuator that can prevent it from rotating.

[0009] The rear end face of the differential case seat and the front end face of the differential case cover are provided with four case seat semicircular grooves and case cover semicircular grooves in an annular array, and the case seat semicircular grooves and the case cover semicircular grooves are butted to form cross shaft holes for fitting the four ends of the embedded cross shaft.

[0010] The embedded cross shaft includes an integrally formed middle piece and a half shaft. The middle piece is a square structure with an embedded hole in the middle. The middle of the outer wall of the middle piece is connected to the inner end of a half shaft respectively, and the outer end of the half shaft is sleeved in the cross shaft hole; the rear wall of the left half shaft gear is provided with an embedded ring for sleeved in the embedded hole; the rear end of the differential cover is axially provided with a ring-shaped sleeve, and the rear end of the right locking half shaft gear is axially provided with a right embedded ring for sleeved in the sleeve.

[0011] The differential lock thrust actuator includes a serpentine spring, an end face pressing cog, a sliding ejector pin, a sliding track plate and a plane thrust bearing. The end face pressing cog is an annular structure arranged on the rear side of the inner cavity of the differential case cover. The outer wall of the end face pressing cog is an annular array with a plurality of limit blocks. The inner wall of the differential case cover is provided with a limit groove that slides with the limit block. The front wall of the end face pressing cog is provided with an annular groove for placing the serpentine spring. The inner side of the annular groove is an annular array with a plurality of rear cogs, and a rear cog groove is formed between adjacent rear cogs. The right lock The rear wall of the half-shaft gear is provided with front cogs in an annular array for matching and meshing with the rear cog groove; the rear end face of the differential case cover is provided with four ejector pin holes in an annular array for the rear end of the sliding ejector pin to pass through, and the front end of the sliding ejector pin is connected to the middle part of the rear wall of the limit block; the sliding track plate is sleeved on the outside of the sleeve through the planar thrust bearing, and the front wall of the sliding track plate is provided with a spiral sliding track that slides with the rear end of the sliding ejector pin, and the rear side of the sliding track plate is provided with an electromagnetic coil assembly for driving the sliding track plate to rotate.

[0012] The rear end of the sliding ejector pin forms a sliding ejector pin spherical surface with a hemispherical structure; the spiral sliding track is a cylindrical spiral line 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 ejector pin spherical surface, and the depth d of the spiral sliding track is 40%~60% of the diameter of the sliding ejector pin spherical surface; the spiral track groove is a "V"-shaped structure along its axial direction, the rotation angle of the spiral track groove is θ=15°~25°, and the spiral pitch a=65mm~75mm.

[0013] The surface roughness of the spiral sliding track is Ra0.8-Ra1.6, and the surface is treated by nickel plating process.

[0014] The electromagnetic coil assembly includes an electromagnetic coil, a coil pressure plate and a double-layer spiral retaining ring for a shaft. The electromagnetic coil is in an annular structure and is arranged on the rear side of the sliding track plate. The coil pressure plate is arranged on the rear side of the electromagnetic coil. The outer diameter of the coil pressure plate is larger than the inner diameter of the coil pressure plate. 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 arranged on the rear side of the coil pressure plate. The inner ring of the double-layer spiral retaining ring for the shaft is fixed to the outside of the shaft sleeve.

[0015] A plurality of differential case connecting threaded holes for threaded connection with the differential case connecting bolts are arranged between adjacent semicircular grooves of the case cover; a differential case connecting bolt hole for the screw rod of the differential case connecting bolt to pass through is arranged on the front wall of the differential case seat; a plurality of lubrication holes are arranged on the front wall of the differential case seat and the side wall of the differential case cover.

[0016] The mating position of the embedded cross shaft and the planetary gear is provided with a non-metallic friction-reducing 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 a half-shaft gear gasket, a planetary gear gasket and a right half-shaft gear gasket.

[0017] The beneficial effects of the present invention are: (1) The differential lock thrust actuator, the embedded cross shaft and the sliding track plate of the present invention are all arranged on the differential case cover. The optimized design of the differential lock thrust actuator not only improves the compactness of the differential lock structure, 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. (2) The electromagnetic coil assembly of the present invention is combined with the differential lock thrust actuator, and the sliding pin is pushed to move by the spiral sliding track, thereby realizing the rapid locking and unlocking of the differential lock. Compared with the prior art, the present invention has a faster response speed, can adapt to changes in road conditions more quickly, and improves the driving stability and safety of the vehicle; (3) The present invention provides a non-metallic anti-friction coating at the mating point between the embedded cross shaft and the planetary gear; and provides a half-shaft gear gasket, a planetary gear gasket and a right half-shaft gear gasket to protect the various components of the differential gear mechanism, reduce the wear between the moving parts, and extend the service life of the differential lock; (4) The present invention drives the differential lock thrust actuator to lock through the electromagnetic coil assembly, and has a fast response speed, thereby achieving fast response and precise control of the differential lock, with higher efficiency and reliability, meeting the needs of different driving scenarios; (5) The present invention reduces production costs and manufacturing cycles 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 processes, thereby improving production efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a structural schematic diagram of the present invention; Figure 2 is an exploded schematic diagram of the differential case assembly of the present invention; Figure 3 is an exploded schematic diagram of the differential gear mechanism of the present invention; Figure 4 It is an exploded schematic diagram of the differential lock thrust actuator of the present invention; Figure 5 It is a schematic diagram of the decomposition of the present invention; Figure 6 It is a schematic diagram of the structure of the sliding track plate in the present invention; Figure 7 A top view of the sliding track plate of the present invention; Figure 8 for Figure 7 A-direction view in the figure; Fig. 9 It is a schematic diagram of the connection between the differential case cover and the end face pressing cog in the present invention; Fig.10 It is a schematic structural diagram of the right locking half-shaft gear in the present invention.

[0019] In the figure: 1 differential case seat, 101 case seat semicircular groove, 2 differential case cover, 201 case cover semicircular groove, 202 shaft sleeve, 203 limit groove, 204 top pin hole, 205 threaded hole, 3 differential case connecting bolt, 4 half shaft gear gasket, 5 left half shaft gear, 51 embedded ring, 6 embedded cross shaft, 61 middle piece, 62 half shaft, 63 embedded hole, 7 planetary gear gasket, 8 planetary gear, 9 right locking half shaft gear, 91 right Inner ring, 92 front cog, 10 right half shaft gear gasket, 11 serpentine spring, 12 end face cog, 121 limit block, 122 annular groove, 123 rear cog, 124 rear cog groove, 13 sliding ejector pin, 131 sliding ejector pin spherical surface, 14 sliding track plate, 15 plane 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 DESCRIPTION

[0020] The present invention is further described below: See also Figure 1-10 , The present invention discloses a high-strength, responsive front and rear axle electronic differential lock, comprising a differential case assembly, a differential gear mechanism and a differential lock thrust actuator, wherein the differential case assembly comprises a differential case seat 1, a differential case cover 2 and a differential case connecting bolt 3, wherein the differential case seat 1 is a hollow structure with a rear end opening, and the differential case cover 2 is a hollow structure with a front end opening, and the rear end of the differential case seat 1 and the front end of the differential case cover 2 are connected by the differential case connecting bolt 3 after being butted against each other. The differential gear mechanism includes a left half-shaft gear 5, an embedded cross shaft 6, a planetary gear 8 and a right locking half-shaft gear 9. The embedded cross shaft 6 is in a "cross" shape. The four ends of the embedded cross shaft 6 are sleeved on the outer wall of the differential case assembly; the shaft holes of the four planetary gears 8 are sleeved on 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 arranged in the inner cavity of the differential case seat 1 and the differential case cover 2. The planetary gear 8 and the right locking half-shaft gear 9 are bevel gears that are matched and meshed in sequence; the rear side of the right locking half-shaft gear 9 is provided with the differential lock thrust actuator that can prevent it from rotating. The differential lock thrust actuator, the embedded cross shaft 6 and the sliding track plate 14 of the present invention are all arranged on the differential case cover 2. The optimized design of the differential lock thrust actuator not only improves the compactness of the structure 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 case seat 1 and the differential case cover 2 form a complete differential lock case assembly, and the two stoppers are matched and connected together through the differential case connecting bolts 3. Preferably, four lubrication holes 21 are evenly distributed on the front wall of the differential case seat 1 and the side wall of the differential case cover 2 to ensure the lubrication effect of the differential gear mechanism and the differential lock thrust actuator, and at the same time ensure the transmission of the power and impact force of the whole vehicle in the locked / unlocked state. The shell is made of high-strength material and a special heat treatment process.

[0021] Furthermore, the rear end face of the differential case seat 1 and the front end face of the differential case cover 2 are provided with four case seat semicircular grooves 101 and case cover semicircular grooves 201 in a circular array, and the case seat semicircular grooves 101 and the case cover semicircular grooves 201 are butted against each other to form cross shaft holes for fitting the four ends of the embedded cross shaft 6, which can play a positioning role, making it easier for the embedded cross shaft 6 to be installed in the differential case cover 2.

[0022] Furthermore, the embedded cross shaft 6 includes an integrally formed middle piece 61 and a half shaft 62. The middle piece 61 is a square structure, and an embedded hole 63 is provided in the middle of the middle piece 61. The middle of the outer wall of the middle piece 61 is connected to the inner end of a half shaft 62, and the outer end of the half shaft 62 is sleeved in the cross shaft hole; the rear wall of the left half shaft gear 5 is provided with an embedded ring 51 for sleeved in the embedded hole 63; the rear end of the differential cover 2 is axially provided with a ring-shaped shaft sleeve 202, and the rear end of the right locking half shaft gear 9 is axially provided with a sleeve for sleeved in the left half shaft gear 5. The right embedded ring 91 inside the shaft sleeve 202, the embedded cross shaft 6 is set in an integrated manner, replacing the traditional method of splicing two long shafts and two short shafts, thereby improving the stability of the cross shaft when the differential is in operation. At the same time, the embedded ring 51 on one side of the left half-shaft gear 5 is embedded in the embedded hole 63 to limit and avoid the left half-shaft gear 5; the structural scheme of the embedded cross shaft 6 can ensure that the half shafts on both sides will not form two design states due to different spline positions, so that the overall structure of the differential lock is very compact and can meet the use requirements of different vehicles.

[0023] Furthermore, the differential locking thrust actuator includes a serpentine spring 11, an end face pressing cog 12, a sliding ejector pin 13, a sliding track plate 14 and a plane thrust bearing 15, wherein the end face pressing cog 12 is annularly arranged on the rear side of the inner cavity of the differential case cover 2, and the outer wall of the end face pressing cog 12 is annularly arrayed with a plurality of limit blocks 121, and the inner wall of the differential case cover 2 is provided with a limit groove 203 that slides with the limit block 121; the front wall of the end face pressing cog 12 is provided with an annular groove 122 for accommodating the serpentine spring 11, and the inner side of the annular groove 122 is annularly arrayed with a plurality of rear cogs 123, and a rear cog groove 124 is formed between adjacent rear cogs 123; The rear wall of the right locking half-shaft gear 9 is provided with front cogs 92 in an annular array for matching and meshing with the rear cog groove 124; the rear end face of the differential case cover 2 is provided with four ejector pin holes 204 in an annular array for the rear end of the sliding ejector pin 13 to pass through, and the front end of the sliding ejector pin 13 is connected to the middle of the rear wall of the limit block 121; the sliding track plate 14 is sleeved on the outside of the shaft sleeve 202 through the plane thrust bearing 15, and the front wall of the sliding track plate 14 is provided with a spiral sliding track 19 that slides with the rear end of the sliding ejector pin 13, and the rear side of the sliding track plate 14 is provided with an electromagnetic coil assembly for driving the sliding track plate 14 to rotate, which is driven by the end face cogs. The plurality of limit blocks 121 on the outer wall of the differential case cover 2 in an annular array cooperate with the limit grooves 203 on the inner wall of the differential case cover 2 to slide, and the rear end face of the differential case cover 2 has four push pin holes 204 in an annular array for the rear end of the sliding push pin 13 to pass through, ensuring that the end face pressing cog 12 and the sliding push pin 13 can slide forward and backward stably, so that the end face pressing cog 12 is meshed and locked with the right locking half-shaft gear 9. Specifically, in the initial state, the sliding push pin 13 is located at the lowest point of the spiral track groove 19. When the electromagnetic coil assembly drives the sliding track plate 14 to rotate, the sliding push pin 13 moves to the highest point along the sliding track groove 19, and the sliding push pin 13 can push the end face pressing cog 12 connected to its front end forward. When the gear 12 is in motion, the serpentine spring 11 is in a compressed state, and the rear cog groove 124 on the front wall of the end face cog 12 can match and mesh with the front cog 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 assembly is powered off, and the serpentine spring 11 is reset to provide reverse thrust, so that the end face tooth cog 12 is disengaged from the right locking half-shaft gear 9, and the sliding ejector pin 13 returns the sliding track plate 14 to its original position, thereby releasing the differential lock; the differential lock thrust actuators are all assembled on the differential case cover 2, the locking actuator has a short stroke and a compact overall structure, which improves the stability of the differential when performing the locking action and the overall structural strength of the differential lock.

[0024] Further, such as Figure 6-8As shown in the figure, the rear end of the sliding ejector pin 13 forms a sliding ejector pin spherical surface 131 of a hemispherical structure, and the spiral sliding track 19 is a cylindrical spiral line 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 equal to the outer diameter of the sliding ejector pin spherical surface 131, so that the sliding ejector pin spherical surface 131 can be completely fitted 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 ejector pin, and the depth d of the spiral sliding track 19 is used to limit the movement of the sliding ejector pin. The spiral track groove 191 is V-shaped along its axial direction, and the rotation angle θ of the spiral track groove 191 is 15°~25°, the spiral pitch a is 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 pin 13 to slide smoothly along the spiral path on the spiral sliding track 19.

[0025] The cylindrical helix shape of the spiral sliding track 19 is described by the following parametric equation: In a three-dimensional rectangular coordinate system, the parametric equation of the spiral can be expressed as: x=r* cos(θ) y=r* sin(θ) Z=a*θ in: r is the spiral radius, θ is the rotation angle of the helix, a is the spiral pitch, which represents the distance the spiral rises on the z-axis for each rotation.

[0026] The spiral sliding track 19 is composed of four spiral track grooves 191 connected end to end. The spiral track groove 191 is in the form of a cylindrical spiral groove. A single 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.

[0027] 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 annularly structured and is arranged on the rear side of the sliding track plate 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 greater 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 the shaft. The double-layer spiral retaining ring 18 for the 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 the shaft is fixed to the outside of the shaft sleeve 202. The electromagnetic coil 16 is fixed to the outside of the shaft sleeve 202 through the coil pressure plate 17 and the double-layer spiral retaining ring 18 for the shaft to ensure that the electromagnetic coil 16 can rotate. When the electromagnetic coil 16 is energized by conducting current, the electromagnetic coil 16 generates magnetism, attracts the sliding track plate 14 in front of it, and drives the sliding track plate 14 to rotate around the shaft sleeve 202. When the sliding track plate 14 rotates, the sliding push pin 13 moves to the highest point along the sliding track groove 19, and the sliding push pin 13 can push the end face pressing cog 12 connected to its front end forward. At this time, the serpentine spring 11 is in a compressed state, and the rear cog groove 124 on the front wall of the end face pressing cog 12 can match and mesh with the front cog 92 on the rear wall of the right locking half-shaft gear 9, thereby achieving the locking of the differential; when the effect of locking the differential is to be released, the electromagnetic coil 16 is powered off and no longer provides the suction force. The serpentine spring 11 is reset to provide reverse thrust, so that the end face tooth cog 12 is disengaged from the right locking half-shaft gear 9, and the sliding push pin 13 makes the sliding track plate 14 return to its original position, thereby achieving the effect of unlocking the differential; the electromagnetic coil 16 control technology has a fast response speed, thereby achieving a fast response and precise control of the differential lock, with higher efficiency and reliability.

[0028] Furthermore, a plurality of differential case connecting threaded holes 205 for threaded connection with the differential case connecting bolts 3 are provided between adjacent semicircular grooves 201 of the housing cover; differential case connecting bolt holes for the screw rods of the differential case connecting bolts 3 to pass through are provided on the front wall of the differential case seat 1, so that the threaded holes 205 and the semicircular grooves 201 of the housing cover are staggered to improve the connection strength.

[0029] Furthermore, a non-metallic friction-reducing coating is provided at the mating position of the embedded cross shaft 6 and the planetary gear 8; 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 a half-shaft gear gasket 4, a planetary gear gasket 7 and a right half-shaft gear gasket 10, which protect the components of the differential gear mechanism, reduce the wear between the moving parts, and extend the service life of the differential lock.

[0030] The above descriptions are merely embodiments of the present invention and are not intended to limit the patent scope of the present invention. Any equivalent transformations made using the contents of the present invention's specification and drawings or directly or indirectly applied in related technical fields are also included in the patent protection scope of the present invention.

Claims

1. A high-strength, responsive front and rear axle electronic differential lock, characterized by: It includes a differential case assembly, a differential gear mechanism and a differential lock thrust actuator. The differential case assembly comprises a differential case seat (1), a differential case cover (2) and differential case connecting bolts (3); the differential case seat (1) is a hollow structure with an opening at the rear end, the differential case cover (2) is a hollow structure with an opening at the front end, and the rear end of the differential case seat (1) and the front end of the differential case cover (2) are butted against each other and connected via the differential case connecting bolts (3); The differential gear mechanism comprises a left half-shaft gear (5), an embedded cross shaft (6), a planetary gear (8) and a right locking half-shaft gear (9); the embedded cross shaft (6) is in a "cross"-shaped structure; the four ends of the embedded cross shaft (6) are sleeved on the outer wall of the differential case assembly; the shaft holes of the four planetary gears (8) are sleeved on 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 arranged in the inner cavity of the differential case seat (1) and the differential case cover (2); the left half-shaft gear (5), the planetary gear (8) and the right locking half-shaft gear (9) are bevel gears that are matched and meshed in sequence; the rear side of the right locking half-shaft gear (9) is provided with the differential locking thrust actuator that can prevent the right locking half-shaft gear (9) from rotating.

2. A high-strength, responsive front and rear axle electronic differential lock according to claim 1, characterized in that: The rear end face of the differential case seat (1) and the front end face of the differential case cover (2) are provided with four case seat semicircular grooves (101) and case cover semicircular grooves (201) in an annular array, and the case seat semicircular grooves (101) and case cover semicircular grooves (201) are butted against each other to form cross shaft holes for fitting the four ends of the embedded cross shaft (6).

3. A high-strength, responsive front and rear axle electronic differential lock according to claim 2, characterized in that: The embedded cross shaft (6) comprises an integrally formed middle piece (61) and a half shaft (62); the middle piece (61) is of a square structure and is provided with an embedded hole (63) in the middle thereof; the middle of the outer wall of the middle piece (61) is connected to the inner end of a half shaft (62) respectively, and the outer end of the half shaft (62) is sleeved in the cross shaft hole; the rear wall of the left half shaft gear (5) is provided with an embedded ring (51) for sleeved in the embedded hole (63); the rear end of the differential case cover (2) is axially provided with an annular shaft sleeve (202); the rear end of the right locking half shaft gear (9) is axially provided with a right embedded ring (91) for sleeved in the shaft sleeve (202).

4. A high-strength, responsive front and rear axle electronic differential lock according to claim 3, characterized in that: The differential locking thrust actuator comprises a serpentine spring (11), an end face pressing cog (12), a sliding ejector pin (13), a sliding track plate (14) and a planar thrust bearing (15); the end face pressing cog (12) is arranged in an annular structure at the rear side of the inner cavity of the differential case cover (2); the outer wall of the end face pressing cog (12) is provided with a plurality of limit blocks (121) in an annular array; the inner wall of the differential case cover (2) is provided with a limit groove (203) which cooperates with the limit block (121) for sliding; the front wall of the end face pressing cog (12) is provided with an annular groove (122) for accommodating the serpentine spring (11); the inner side of the annular groove (122) is provided with a plurality of rear cogs (123) in an annular array; a rear cog groove (123) is formed between adjacent rear cogs (123). 24); the rear wall of the right locking half-shaft gear (9) has a front cog (92) in an annular array for matching and meshing with the rear cog groove (124); the rear end face of the differential case cover (2) has four ejector pin holes (204) in an annular array for the rear end of the sliding ejector pin (13) to pass through, and the front end of the sliding ejector pin (13) is connected to the middle of the rear wall of the limit block (121); the sliding track plate (14) is sleeved on the outside of the shaft sleeve (202) through the planar thrust bearing (15), the front wall of the sliding track plate (14) is provided with a spiral sliding track (19) that slides with the rear end of the sliding ejector pin (13), and the rear side of the sliding track plate (14) is provided with an electromagnetic coil assembly for driving the sliding track plate (14) to rotate.

5. A high-strength, responsive front and rear axle electronic differential lock according to claim 4, characterized in that: The rear end of the sliding ejector pin (13) forms a sliding ejector pin spherical surface (131) with a hemispherical structure; the spiral sliding track (19) is a cylindrical spiral line structure composed of four spiral track grooves (191) connected end to end, the cross section of the spiral track groove (191) is an arc structure equal to the outer diameter of the sliding ejector pin spherical surface (131), and the depth d of the spiral sliding track (19) is 40% to 60% of the diameter of the sliding ejector pin spherical surface (131); the spiral track groove (191) is a "V"-shaped structure along its axial direction, the rotation angle θ of the spiral track groove (191) is 15° to 25°, and the spiral pitch a is 65 mm to 75 mm.

6. A high-strength, responsive front and rear axle electronic differential lock according to claim 5, characterized in that: The surface roughness of the spiral sliding track (19) is Ra0.8-Ra1.6, and its surface is processed by nickel plating process.

7. A high-strength, responsive front and rear axle electronic differential lock according to claim 4, characterized in that: The electromagnetic coil assembly comprises an electromagnetic coil (16), a coil pressure plate (17) and a double-layer spiral retaining ring (18) for a shaft. The electromagnetic coil (16) is arranged in an annular structure at the rear side of the sliding track plate (14). The coil pressure plate (17) is arranged at the rear side of the electromagnetic coil (16). The outer diameter of the coil pressure plate (17) is greater 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 the shaft. The double-layer spiral retaining ring (18) for the shaft is arranged at 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 shaft sleeve (202).

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

9. The high-strength and responsive front and rear axle electronic differential lock according to claim 1, characterized in that: A non-metallic anti-friction coating is provided at the mating position of the embedded cross shaft (6) and the planetary gear (8); a half-shaft gear gasket (4), a planetary gear gasket (7) and a right half-shaft gear gasket (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).

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