Front and rear axle electronic differential lock thrust actuating mechanism

Abstract

The utility model relates to the technical field of vehicle transmission, in particular to a front and rear axle electronic differential lock thrust actuating mechanism, which comprises a differential case cover, a right locking half axle gear and end face embedded teeth, the differential case cover is of a hollow structure with an opening at the front end, an annular shaft sleeve is axially arranged at the rear end of the differential case cover, and the right locking half axle gear and the end face embedded teeth are arranged on the shaft sleeve. The rear end of the right locking half axle gear is axially provided with a right embedded ring used for being arranged in the shaft sleeve in a sleeved mode, and a plurality of front embedded teeth are arranged on the end face of the right end of the right locking half axle gear in an annular array mode. Rear embedded tooth grooves clamped with the front embedded teeth in a matched mode are formed in the left end faces of the end face pressing embedded teeth in an annular array mode, and the side walls of the end face pressing embedded teeth are driven by a driving mechanism to slide along the inner wall of the differential mechanism shell cover. Rapid locking and unlocking of the differential lock are achieved, the differential lock can more rapidly adapt to road condition changes, and the running stability and safety of a vehicle are improved.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicle transmission, in particular to a front and rear axle electronic differential locking thrust actuator. Background Art

[0002] The differential lock is a crucial component of a vehicle's drive system. It locks the wheels during driving, especially in complex road conditions, improving the vehicle's maneuverability and stability. Differential locks are used to help the vehicle escape from a jam. When one wheel slips, domestic automotive drive axles often utilize logic instructions to control the electromagnetic coils to generate magnetic force, pushing the teeth of the gears to connect with the axle gears, locking the differential case and axle shafts together. This deactivates the differential's differential function and transfers torque to one wheel, freeing the vehicle.

[0003] Then when the differential is locked, the differential lock will be subjected to a greater impact, especially when off-roading through 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, pin breakage, and 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 processing costs.

[0004] In response to the problems existing in the existing technology, it is necessary to propose a front and rear axle electronic differential lock thrust actuator structure. By optimizing the design of the differential lock and adopting an innovative electromagnetic control thrust actuator solution, the reaction speed and overall performance of the differential lock are improved to meet the driving needs of the vehicle under different road conditions. Utility Model Content

[0005] The purpose of the present invention is to overcome the shortcomings of the existing technology and provide a front and rear axle electronic differential lock thrust actuator, which uses an electromagnetic coil assembly as a driving mechanism and pushes the sliding push pin to move through a spiral sliding track to achieve rapid locking and unlocking of the differential lock. Compared with the existing technology, the present invention has a faster response speed, can adapt to changes in road conditions more quickly, and improve the driving stability and safety of the vehicle.

[0006] In order to achieve the purpose of this utility model, the technical solution adopted by this utility model is:

[0007] The utility model discloses a front and rear axle electronic differential lock thrust actuator, comprising a differential case cover, a right locking half-shaft gear and an end face pressing cog, wherein the differential case cover is a hollow structure with an open front end, the rear end of the differential case cover is axially provided with an annular shaft sleeve, the rear end of the right locking half-shaft gear is axially provided with a right inner ring for being sleeved inside the shaft sleeve, the right end face of the right locking half-shaft gear is in an annular array with a plurality of front cogs; the left end face of the end face pressing cog is in an annular array with rear cog grooves matching and engaging with the front cogs, and the side wall of the end face pressing cog is driven by a driving mechanism to slide along the inner wall of the differential case cover.

[0008] A plurality of limiting blocks are arranged in an annular array on the side wall of the end face pressing cog, and a limiting groove which slides with the limiting blocks is provided on the inner wall of the differential housing cover.

[0009] The driving mechanism includes a serpentine spring, a sliding ejector pin, a sliding track plate, a planar thrust bearing and an electromagnetic coil assembly. The front wall of the end face cog is provided with an annular groove for placing the serpentine spring, and the rear cog groove is arranged on the inner side of the annular groove. The rear end face of the differential case cover is in an annular array with four ejector pin holes for the rear end of the sliding ejector pin to pass through. 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 shaft sleeve through the planar thrust bearing, 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.

[0010] 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 linear 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% to 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.

[0011] The surface roughness of the spiral sliding track is Ra0.8-Ra1.6, and the surface is processed by nickel plating process.

[0012] 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 a ring 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 a shaft. The double-layer spiral retaining ring for a shaft is arranged on the rear side of the coil pressure plate. The inner ring of the double-layer spiral retaining ring for a shaft is fixed to the outside of the shaft sleeve.

[0013] The beneficial effects of the present invention are:

[0014] The utility model uses an electromagnetic coil assembly as a driving mechanism and pushes the sliding ejector pin to move via a spiral sliding track, thereby achieving rapid locking and unlocking of the differential lock. Compared with the existing technology, the utility model has a faster response speed, can more quickly adapt to changes in road conditions, and improves the driving stability and safety of the vehicle.

[0015] The utility model drives the differential lock thrust actuator to lock through the electromagnetic coil assembly, and has a fast response speed, thereby achieving rapid response and precise control of the differential lock, with higher efficiency and reliability, and meeting the needs of different driving scenarios. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is an exploded schematic diagram of the utility model;

[0017] Figure 2 This is a schematic diagram of the structure of the present invention without the right locking half-shaft gear;

[0018] Figure 3 This is a partial structural exploded diagram of the driving mechanism of the present invention;

[0019] Figure 4 This is a schematic structural diagram of the sliding track plate in the present utility model;

[0020] Figure 5 This is a top view of the sliding track plate in the present utility model;

[0021] Figure 6 for Figure 5 A-direction view in.

[0022] In the figure: 2 differential case cover, 203 limiting groove, 204 ejector pin hole, 9 right locking half-shaft gear, 91 right inner ring, 92 front cog, 12 end face pressing cog, 121 limiting block, 122 annular groove, 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. DETAILED DESCRIPTION

[0023] The utility model is further described below:

[0024] See also Figure 1-6 ,

[0025] The utility model discloses a front and rear axle electronic differential locking thrust actuator, such as Figure 1 and 2 As shown, it includes a differential case cover 2, a right locking half-shaft gear 9 and an end face pressing cog 12. The differential case cover 2 is a hollow structure with an open front end. The rear end of the differential case cover 2 is axially provided with an annular shaft sleeve. The rear end of the right locking half-shaft gear 9 is axially provided with a right inner ring 91 for being sleeved inside the shaft sleeve. The right end face of the right locking half-shaft gear 9 is annularly arrayed with a plurality of front cogs 92; the left end face of the end face pressing cog 12 is annularly arrayed with rear cog grooves 124 that match and engage with the front cogs 92. The side wall of the end face pressing cog 12 is driven by a driving mechanism to slide along the inner wall of the differential case cover 2.

[0026] Further, such as Figure 2 As shown, a plurality of limit blocks 121 are provided in an annular array on the side wall of the end face pressing cog 12, and a limit groove 203 is provided on the inner wall of the differential case cover 2 for sliding with the limit blocks 121. By sliding in cooperation with the limit blocks 121 in an annular array on the outer wall of the end face pressing cog 12 and the limit groove 203 on the inner wall of the differential case cover 2, it is ensured that the end face pressing cog 12 and the sliding ejector pin 13 can slide stably back and forth, so that the end face pressing cog 12 and the right locking half-shaft gear 9 can be engaged and locked.

[0027] Further, such as Figure 3As shown, the driving mechanism includes a serpentine spring 11, a sliding ejector pin 13, a sliding track plate 14, a planar thrust bearing 15 and an electromagnetic coil assembly. The front wall of the end face cog 12 is provided with an annular groove 122 for placing the serpentine spring 11, and the rear cog groove 124 is arranged on the inner side of the annular groove 122. The rear end face of the differential case cover 2 is in an annular array with four ejector pin holes 204 for the rear end of the sliding ejector pin 13 to pass through. The front end of the sliding ejector pin 13 is connected to the middle part of the rear wall of the limit block 121; the sliding track plate 14 is sleeved on the outside of the shaft sleeve through the planar 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. 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. Specifically, in the initial state, the sliding ejector pin 13 is located in the spiral track groove 1 When the cam 13 is in the lowest position, the electromagnetic coil assembly drives the sliding track plate 14 to rotate, and the sliding ejector pin 13 moves to the highest point along the sliding track groove 19, and the sliding ejector 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 differential lock effect is to be released, the electromagnetic coil assembly is de-energized, and the serpentine spring 11 is reset to provide reverse thrust, disengaging the end face tooth cog 12 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 achieving the effect of 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.

[0028] Further, such as Figure 4-6As shown, the rear end of the sliding ejector pin 13 forms a hemispherical sliding ejector pin spherical surface 131, and 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 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° to 25°, the spiral pitch a is 65mm to 75mm, and the surface roughness of the spiral sliding track 19 is Ra0.8 to Ra1.6. The surface is nickel-plated 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.

[0029] 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:

[0030] x=r* cos(θ)

[0031] y=r* sin(θ)

[0032] Z=a*θ

[0033] in:

[0034] r is the spiral radius,

[0035] θ is the rotation angle of the helix,

[0036] a is the helical pitch, which represents the distance the helix rises on the z-axis per rotation.

[0037] 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.

[0038] Further, such as Figure 1As shown, 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 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 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. The electromagnetic coil 16 is fixed to the outside of the shaft sleeve 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 together. The initial state When the gear shift lever 14 is in the locked position, the cam 13 is in the locked position, and the gear shift lever 14 is in the locked position, so that the gear shift lever 14 can be locked directly to the gear shift lever 14.

[0039] The above description is merely an embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent transformation made using the contents of the present invention specification and drawings or directly or indirectly applied in the relevant technical field shall be included in the patent protection scope of the present invention.

Claims

1. A front and rear axle electronic differential lock thrust actuator, characterized by: The invention comprises a differential case cover (2), a right locking half-axle gear (9) and an end face pressing cog (12), wherein the differential case cover (2) is a hollow structure with an open front end, the rear end of the differential case cover (2) is axially provided with an annular shaft sleeve, the rear end of the right locking half-axle gear (9) is axially provided with a right inner ring (91) for being fitted inside the shaft sleeve, the right end face of the right locking half-axle gear (9) is annularly arrayed with a plurality of front cogs (92); the left end face of the end face pressing cog (12) is annularly arrayed with rear cog grooves (124) that match and engage with the front cogs (92), and the side wall of the end face pressing cog (12) is driven by a driving mechanism to slide along the inner wall of the differential case cover (2).

2. The front and rear axle electronic differential lock thrust actuator according to claim 1, characterized in that: A plurality of limiting blocks (121) are provided in an annular array on the side wall of the end face pressing tooth (12), and a limiting groove (203) is provided on the inner wall of the differential case cover (2) for slidingly cooperating with the limiting blocks (121).

3. The front and rear axle electronic differential lock thrust actuator according to claim 2, characterized in that: The driving mechanism comprises a serpentine spring (11), a sliding ejector pin (13), a sliding track disc (14), a planar thrust bearing (15) and an electromagnetic coil assembly. The front wall of the end face cog (12) is provided with an annular groove (122) for accommodating the serpentine spring (11). The rear cog groove (124) is provided on the inner side of the annular groove (122). 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. The front end of the sliding ejector pin (13) is connected to the middle part of the rear wall of the limit block (121). The sliding track disc (14) is sleeved on the outside of the shaft sleeve through the planar thrust bearing (15). The front wall of the sliding track disc (14) is provided with a spiral sliding track (19) that slides with the rear end of the sliding ejector pin (13). The rear side of the sliding track disc (14) is provided with an electromagnetic coil assembly for driving the sliding track disc (14) to rotate.

4. The front and rear axle electronic differential lock thrust actuator according to claim 3, 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 65mm to 75mm.

5. The front and rear axle electronic differential lock thrust actuator according to claim 4, 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.

6. The front and rear axle electronic differential lock thrust actuator according to claim 3, 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 the shaft, wherein the electromagnetic coil (16) is annularly structured and arranged on the rear side of the sliding track plate (14), and 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), and the inner diameter of the coil pressure plate (17) is smaller than the double-layer spiral retaining ring (18) for the shaft, and the double-layer spiral retaining ring (18) for the shaft is arranged on the rear side of the coil pressure plate (17), and the inner ring of the double-layer spiral retaining ring (18) for the shaft is fixed to the outside of the shaft sleeve.

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