Passive magnetic differential lock device and control method

Abstract

This application discloses a passive magnetic differential lock device and control method, relating to the field of vehicle transmission system technology. It includes left and right drive structures. The left side has a movable toothed sleeve pushed by a drive fork, and the right side has a engaged toothed ring installed on its exterior. Strong magnetic modules with the same magnetic poles are installed at corresponding positions on the movable toothed sleeve and the engaged toothed ring. When the padlock approaches and the spline faces the top teeth, a repulsive force is generated between the strong magnetic modules. Utilizing the circumferential clearance reserved in the spline fit of the movable toothed sleeve, the movable toothed sleeve undergoes a slight circumferential rotation, causing the inner spline groove to automatically align with the outer spline teeth. Furthermore, an external magnetic sliding unit combined with a spring can be used to achieve axial buffering and reset. The control method determines whether to engage the padlock or actively intervene based on the wheel end speed difference. This invention avoids rigid top tooth collisions during differential lock engagement by guiding phase adaptive adjustment through passive magnetic repulsion, reducing wear on transmission components and improving meshing smoothness.

Description

Technical Field

[0001] This application relates to the field of vehicle transmission system technology, and in particular to a passive magnetic differential lock device and control method. Background Technology

[0002] A differential lock is a crucial component of a vehicle's transmission system. It is primarily used when a vehicle is traveling on muddy, slippery, or off-road surfaces to lock the drive structures on both sides, causing them to rotate synchronously and thus improving the vehicle's traction and ability to get out of trouble. Currently, most common differential locks employ mechanical jaw locks or splined sleeve structures. They rely on external actuators such as shift forks to push a movable gear sleeve along the axial direction, causing it to physically engage with the opposite gear ring, thereby completing the transmission locking.

[0003] In the operation of this traditional structure, due to the randomness of the circumferential phase of the movable gear sleeve and the engaged gear ring at the moment of engagement, when the movable gear sleeve is subjected to axial thrust and approaches the engaged gear ring, the spline tooth end face of the movable gear sleeve often happens to be exactly at the same circumferential position as the spline tooth end face of the engaged gear ring. This end face alignment leads to mechanical tooth interference, preventing the movable gear sleeve from smoothly sliding into the corresponding tooth groove. At this time, the thrust continuously applied by the external actuator will be directly converted into rigid extrusion and collision between the tooth surfaces, causing significant mechanical noise and severe wear on the spline tooth end face metal. Frequent tooth interference accelerates the aging of transmission components and may even lead to tooth deformation or breakage, affecting the reliability and service life of the differential lock.

[0004] To alleviate the aforementioned gear engagement problem, current conventional methods often rely on the driver slightly moving the vehicle when the differential lock fails, using the wheel rotation to randomly change the phase of the internal gear sleeve. This method is not only cumbersome but also difficult to implement in harsh road conditions. Some technologies attempt to add active phase synchronization devices or complex mechanical damping components inside the differential lock, but these additional structures are usually large, significantly increasing the overall size and manufacturing cost of the differential lock, making it difficult to adapt to the increasingly compact assembly space requirements within modern vehicle axles. Summary of the Invention

[0005] The purpose of this invention is to provide a passive magnetic differential lock device and control method, which at least solves a technical problem in traditional mechanical differential locks where the random alignment of spline tooth end faces easily causes rigid top tooth interference, resulting in wear of transmission components and difficulty in smooth meshing.

[0006] This invention provides the following solution:

[0007] According to one aspect of the present invention, a passive magnetic differential lock device and control method are provided, comprising a left drive structure and a right drive structure. A movable toothed sleeve is disposed externally on the left drive structure, and a engaged toothed ring is mounted externally on the right drive structure. A drive fork is disposed externally on the left drive structure, and the drive fork pushes the movable toothed sleeve to slide towards the engaged toothed ring. A strong magnetic module is mounted externally on the end face of the movable toothed sleeve facing the engaged toothed ring, and a second strong magnetic module is mounted externally on the end face of the engaged toothed ring facing the movable toothed sleeve. The first and second strong magnetic modules are arranged opposite to each other and have the same magnetic poles.

[0008] Preferably, the left drive structure has an external spline, and the movable tooth sleeve has an internal spline. The internal spline of the movable tooth sleeve and the external spline of the left drive structure are configured to cooperate. The tooth width of the internal spline of the movable tooth sleeve is smaller than the groove width of the external spline of the left drive structure, allowing the movable tooth sleeve to rotate circumferentially on the left drive structure.

[0009] Preferably, the inner spline teeth of the movable tooth sleeve one are provided with grooves, the strong magnetic module one is installed in the groove of the movable tooth sleeve one, the outer spline teeth of the engaged tooth ring one are provided with grooves, and the strong magnetic module two is installed in the groove of the engaged tooth ring one.

[0010] Preferably, when the movable tooth sleeve one and the engaged tooth ring one approach each other, the strong magnetic module one and the strong magnetic module two repel each other with the same pole, generating a repulsive force, which drives the movable tooth sleeve one to rotate, aligning the inner spline groove of the movable tooth sleeve one with the outer spline teeth of the engaged tooth ring one.

[0011] Preferably, the movable toothed sleeve one and the engaged toothed ring one can be replaced by the movable toothed sleeve two and the engaged toothed ring two, respectively. The movable toothed sleeve two is provided on the left drive structure, and the engaged toothed ring two is installed on the right drive structure. The drive fork pushes the movable toothed sleeve two to slide towards the engaged toothed ring two. A strong magnetic module four is installed on the outside of the movable toothed sleeve two. A magnetic sliding unit is installed on the outside of the engaged toothed ring two. A strong magnetic module three is installed on the outside of the magnetic sliding unit. The strong magnetic module three and the strong magnetic module four are arranged opposite to each other and have the same magnetic poles.

[0012] Preferably, the magnetic sliding unit and the second gear ring to be joined are configured by a spline connection, allowing the magnetic sliding unit to slide back and forth along the axial direction outside the second gear ring to be joined. A groove is machined on the outer side of the tail of the second gear ring to be joined, and a spring and a trapezoidal slider are installed in the groove of the second gear ring to be joined. The spring pushes the trapezoidal slider to abut the tail end of the magnetic sliding unit.

[0013] Preferably, the strong magnetic force module three corresponds to the radial direction phase of the outer spline of the engaged gear ring two, and the strong magnetic force module four corresponds to the radial direction phase of the inner spline of the movable gear sleeve two.

[0014] Preferably, when the movable toothed sleeve 2 and the engaged toothed ring 2 approach each other, the strong magnetic module 4 and the strong magnetic module 3 generate a repulsive force due to the repulsion of their like poles, which drives the movable toothed sleeve 2 to rotate, aligning the inner spline groove of the movable toothed sleeve 2 with the outer spline teeth of the engaged toothed ring 2. At the same time, the magnetic sliding unit retracts and compresses the spring.

[0015] Preferably, when the drive fork drives the movable toothed sleeve two away from the engaged toothed ring two to separate, the spring pushes the trapezoidal slider to generate an axial force, restoring the magnetic sliding unit to its initial position.

[0016] Preferably, it includes the following steps:

[0017] Obtain the difference in wheel-end rotational speed between the left and right wheels;

[0018] Determine whether the wheel end speed difference exceeds the critical speed difference;

[0019] If the wheel end speed difference exceeds the critical speed difference, the vehicle controller actively controls the speed of the left wheel and the right wheel, or controls the vehicle to resume normal straight driving, or controls the vehicle to stop.

[0020] Once it is determined that the speed difference at the wheel ends does not exceed the critical speed difference and the speed difference condition is met, the linear padlock action continues.

[0021] The above solution achieves the following beneficial technical effects:

[0022] This invention arranges strong magnetic modules with the same magnetic poles at corresponding positions on the opposite end faces or the outside of the engaged gear ring of the movable gear sleeve. When the two components approach each other and the spline teeth face each other, the repulsive force between the same poles generated between the magnets drives the movable gear sleeve to rotate circumferentially, guiding the inner spline groove to automatically align with the outer spline teeth. This avoids the rigid top tooth collision that is easy to occur when the traditional differential lock is engaged, and reduces the wear rate of the transmission end face.

[0023] This invention designs the inner spline tooth width of the movable tooth sleeve to be smaller than the outer spline groove width of the left drive structure. While maintaining the basic axial sliding guide function, it reserves an appropriate circumferential movement clearance on the mating tooth side, providing the necessary micro-rotational degree of freedom for the movable tooth sleeve under the action of magnetic repulsion. This ensures that the tooth sleeve has enough space to complete the self-correction of the meshing phase without leaving the guide constraint, thus ensuring the effective implementation of the anti-tooth alignment action.

[0024] This invention features a magnetic sliding unit on the outside of the gear ring to be engaged, which can slide axially along the spline. In conjunction with a spring and trapezoidal slider in the groove, the magnetic repulsion component is externally mounted to maintain the structural strength of the main drive spline. When encountering axial pushing caused by misalignment of the end faces, the magnetic sliding unit can retract to compress the spring to absorb the impact load. When the components separate, the spring releases elastic potential energy to smoothly push them back to their original position, providing flexible buffering and automatic reset capability for the mechanical structure. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the first differential lock structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0026] Figure 2 This is a schematic diagram of the movable gear sleeve structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0027] Figure 3 This is a schematic diagram of the engaged gear ring structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0028] Figure 4 This is a schematic diagram of a second differential lock structure provided by one or more embodiments of the present invention, which is a passive magnetic differential lock device and control method.

[0029] Among them, 1. Left-side drive structure; 2. Right-side drive structure; 3. Drive fork; 4. Movable toothed sleeve one; 41. Strong magnetic module one; 5. Engaged toothed ring one; 51. Strong magnetic module two; 6. Magnetic sliding unit; 61. Strong magnetic module three; 7. Movable toothed sleeve two; 71. Strong magnetic module four; 8. Engaged toothed ring two; 81. Spring; 82. Trapezoidal slider. Detailed Implementation

[0030] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0031] Figure 1 This is a schematic diagram of the first differential lock structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0032] When the vehicle encounters specific road conditions requiring differential lock engagement, the external actuator responds to the command, causing the drive fork 3 located outside the left drive structure 1 to move axially. During this movement, the drive fork 3 exerts a mechanical pushing force, compelling the movable toothed sleeve 4, fitted outside the left drive structure 1, to slide axially towards the engaged gear ring 5, fixedly mounted outside the right drive structure 2. As the distance between the movable toothed sleeve 4 and the engaged gear ring 5 gradually decreases, the strong magnetic module 41 mounted on the outer face of the movable toothed sleeve 4 facing the engaged gear ring 5 and the strong magnetic module 51 mounted on the outer face of the engaged gear ring 5 facing the movable toothed sleeve 4 also approach each other. If at this moment the splines of both are axially aligned at the top teeth, about to collide head-on, due to the strong magnetic module... Block 1 41 and strong magnetic module 2 51 are arranged opposite each other and have the same magnetic poles. Based on the principle of like poles repulsion, they will instantly generate a significant magnetic repulsion force. This repulsion force is converted into a circumferential rotational torque that acts on the movable gear sleeve 4, causing the movable gear sleeve 4 to rotate slightly within a certain range on the left drive structure 1. This transforms the passive collision resistance into an automatic phase adaptive adjustment, allowing the inner spline groove of the movable gear sleeve 4 to align with the outer spline teeth of the engaged gear ring 5. This effectively avoids direct impact on the metal tooth end face and reduces wear, ensuring that the movable gear sleeve 4 can smoothly and quietly slide into the engaged gear ring 5 to achieve a gentle engagement. Finally, the left drive structure 1 and the right drive structure 2 are smoothly locked together, and the synchronous and reliable transmission of power is achieved.

[0033] Figure 2 This is a schematic diagram of the movable gear sleeve structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0034] To facilitate the adaptive alignment process generated by magnetic repulsion, the external spline machined on the outer surface of the left drive structure 1 and the internal spline machined on the inner surface of the movable gear sleeve 4 are fitted together to provide a basic axial sliding guide and torque transmission basis. Based on this conventional fit, the width of the internal spline tooth of the movable gear sleeve 4 is intentionally designed to be slightly smaller than the width of the corresponding external spline groove of the left drive structure 1, thereby reserving an appropriate circumferential movement clearance between the mating tooth sides of the two. When the movable gear sleeve 4 approaches the engaged gear ring and there is a risk of direct interference between the end face spline teeth, the circumferential repulsive torque caused by the repulsion of the like poles of the strong magnet module will guide the movable gear sleeve 4 to make full use of the reserved clearance, and generate a small circumferential rotational offset without deviating from the guiding constraint of the left drive structure 1. This ingenious design that gives the component micro-rotational freedom not only maintains the compactness of the overall structure, but also provides the key physical rotation space and action prerequisite for the movable gear sleeve 4 to automatically correct the meshing phase, effectively avoid hard connection of the top tooth, and facilitate the smooth sliding of the spline teeth into the opposite keyway.

[0035] Figure 3 This is a schematic diagram of the engaged gear ring structure of a passive magnetic differential lock device and control method provided in one or more embodiments of the present invention.

[0036] To introduce a passive alignment mechanism without significantly increasing the overall internal space of the differential lock and while ensuring the strength of the normal transmission structure, a groove of appropriate depth is pre-machined into the internal spline tooth of the movable gear sleeve 4, which participates in the initial engagement, as a receiving cavity. The strong magnetic module 41 is then securely embedded and installed inside this groove, ensuring that its magnetic field end face maintains a suitable proximity to the spline tooth end face. Correspondingly, a similar groove is also provided on the external spline tooth of the engaged gear ring 5, which is prepared to receive power input. This allows the strong magnetic module 51 to be discreetly embedded and properly installed within the groove of the engaged gear ring 5. The ingenious arrangement of directly integrating the magnetic element that generates the same polarity repulsion force into the spline tooth end, where physical tooth interference is most likely to occur, not only maintains the original compact mechanical form of the transmission component, but also ensures that at the critical moment when the movable tooth sleeve 4 is forced to move towards the engaged tooth ring 5 and the spline teeth of both face the risk of direct end-face collision, the built-in strong magnetic force module 41 and strong magnetic force module 51 can reach the closest distance and face each other in space. This allows for the timely and concentrated generation of the same polarity repulsion torque sufficient to push the movable tooth sleeve 4 to produce a circumferential retraction displacement, providing a timely and targeted force basis for smoothly overcoming end-face contact obstacles and smoothly sliding into the corresponding keyway.

[0037] When the differential lock is in the padlock operation phase and the movable gear sleeve 4 is pushed by the shift fork and moves axially towards the engaged gear ring 5, if the end faces of the spline teeth of the two happen to be directly opposite each other in circumferential phase, and mechanical tooth interference is imminent, the strong magnetic force module 41 and strong magnetic force module 51, which are respectively arranged at the ends of the two and spatially opposite, are also pulled closer to the effective range of magnetic field interaction. Based on the physical property of like poles repelling each other caused by the same magnetic pole arrangement, a non-contact magnetic field repulsion force will be rapidly generated between the magnets, which gradually increases as the distance decreases. This repulsion force, combined with the movable gear sleeve 41, is then applied to the gear ring 5. After the circumferential degree of freedom reserved by the spline fit clearance of the movable gear sleeve 4 is cleverly transformed into rotational force that causes the movable gear sleeve 4 to make a slight circumferential angular offset. This causes the movable gear sleeve 4 to rotate flexibly on the support structure, automatically changing the initial circumferential phase of its spline part. This avoids the position of the inner spline teeth of the movable gear sleeve 4 that would have faced collision interference, and guides its inner spline groove to more accurately align with the outer spline teeth of the gear ring 5 being engaged. In this way, the risk of frontal collision of the tooth surfaces is resolved in a purely passive manner, providing suitable phase alignment conditions for the subsequent smooth and low-noise sliding of the spline part into the keyway to complete the meshing and locking.

[0038] Figure 4 This is a schematic diagram of a second differential lock structure provided by one or more embodiments of the present invention, which is a passive magnetic differential lock device and control method.

[0039] To avoid the technological challenges and potential structural strength loss caused by directly machining and placing the magnetic components that generate adaptive repulsive forces inside the spline entity, after replacing the original structure with movable toothed sleeve 2 7 and engaged toothed ring 2 8, when the actuator guides the drive fork 3 to push movable toothed sleeve 2 7 to slide continuously along the left drive structure 1 towards engaged toothed ring 2 8, the strong magnetic module 4 71 fixedly placed on the outer side of movable toothed sleeve 2 7 also moves forward and gradually approaches the strong magnetic module 3 61 placed outside the magnetic sliding unit 6 responsible for the alignment function outside the engaged toothed ring 2 8. At this time, if the spline of these two components... The key tooth end face is at the critical point of collision where face-to-face interference is about to occur. Given the pre-set opposite arrangement of the same magnetic poles between the strong magnetic module 3 61 and the strong magnetic module 4 71, the two modules will immediately generate a significant repulsive force between the same poles when they approach each other within an effective distance. This repulsive torque transmitted from the external components can play a smooth role, so that the design idea of ​​moving the synchronous repulsion functional area outward not only effectively ensures the integrity of the internal structure of the main drive spline, but also gives the movable tooth sleeve 2 7 a small deflection kinetic energy through the magnetic repulsion, prompting the spline groove to find the right angle in advance in the direction that can slide in smoothly.

[0040] To endow the component subjected to the external magnetic field with flexible axial retraction and buffer reset capabilities, a splined fit is used for guiding and constraining between the outer side of the engaged gear ring 2 8 and the magnetic sliding unit 6. This allows the magnetic sliding unit 6 to maintain circumferential positioning to ensure accurate magnetic pole phase while smoothly sliding axially along the outer contour of the engaged gear ring 2 8. To complement this sliding mechanism, a groove is specially machined on the outer surface of the tail of the engaged gear ring 2 8 to accommodate the elastic avoidance structure. Inside this groove, a spring 81, serving as a mechanical energy storage element, and a trapezoidal slider 82 for transmitting gentle and smooth thrust are properly installed. During normal standby or initial padlock approach phases, the spring 81, with a certain preload, continuously releases appropriate axial thrust, which acts on the trapezoidal slider 82, causing the trapezoidal slider... The slider 82 is firmly pressed against the tail end of the magnetic sliding unit 6, maintaining it in the optimal working position for triggering magnetic repulsion interaction. Once a strong repulsive force between like poles is generated during the approach of the front component or axial compression is caused by the spline tooth end faces not being fully aligned, the magnetic sliding unit 6 can use the spline sliding characteristic to move backward and simultaneously compress the bottom spring 81. This operation mode, which transforms rigid resistance into flexible yielding, can effectively buffer and absorb axial impact energy, protecting the transmission components from potential damage caused by hard impacts. At the same time, this displacement energy is temporarily converted into the elastic potential energy of the spring 81 and stored, providing sufficient power for the spring 81 to relax again and push the trapezoidal slider 82 to guide the magnetic sliding unit 6 to smoothly return to the initial working position when the working conditions change.

[0041] To ensure that the repulsive torque generated by the external magnetic field can more accurately and promptly intervene in the avoidance adjustment action of the internal spline end face, the spatial layout deliberately positions the installation position of the strong magnetic force module three 61 so that it maintains the same circumferential phase in the radial direction as the physical teeth of the outer spline of the engaged gear ring two 8. Simultaneously, the arrangement position of the strong magnetic force module four 71 is also set to maintain the same circumferential phase in the radial direction as the physical teeth of the inner spline of the movable gear sleeve two 7. This structural design, which synchronously binds the external magnetic excitation point and the potential internal mechanical interference point in circumferential phase, ensures that when the differential lock performs the closing and approaching action, the inner spline teeth of the movable gear sleeve two 7 and the... In a specific working condition where the external spline teeth of the engaged gear ring 2 8 happen to be facing each other at the end face and are at risk of collision interference from the top tooth, the strong magnetic force module 3 61 and strong magnetic force module 4 71 located outside the two components can also achieve a relatively close spatial position and face-to-face alignment. Before the internal mechanical tooth surfaces make substantial hard contact, they can concentrate and release a relatively obvious like-pole repulsive force. This repulsive force drives the movable gear sleeve 2 7 to make a moderate circumferential deflection to offset the original tooth surface collision area, guide the teeth to align and slide into the tooth groove on the opposite side, and improve the triggering accuracy of the anti-top tooth adaptive adjustment mechanism and the smoothness of the overall meshing process.

[0042] During the padlock operation of the differential lock, as the movable gear sleeve 7 approaches the engaged gear ring 8 under the thrust of the external actuator, if the spline teeth on their end faces happen to be radially aligned, potentially leading to mechanical tooth interference, the strong magnetic modules 71 and 61, located on their outer sides and pulled closer together, will generate a significant non-contact magnetic repulsion force based on their opposing polarities. This repulsion force can be smoothly converted into a circumferential driving torque, causing the movable gear sleeve 7 to rotate slightly in the transmission structure. This guides the spline groove on its inner side to adjust its angle and align with the outer spline teeth of the engaged gear ring 8 to avoid direct frontal interference. Simultaneously, facing the gradually increasing... When the axial pushing force generated by the mutual squeezing force or the tooth surface not being fully aligned occurs, the magnetic sliding unit 6, which carries the strong magnetic force module 61, will follow the axial force by retracting backward according to the internal spline guide. During the backward sliding process, it will simultaneously compress the spring 81 located in the tail groove. This dynamic operation mechanism, which combines circumferential rotation adaptive alignment with axial elastic retraction buffer, not only ensures that the spline structure can gently find a suitable meshing and sliding point, but also effectively absorbs and reduces the axial impact load generated when the transmission components are squeezed together by the compression of the spring 81. This makes the entire component's approach and alignment action smoother and provides better mechanical protection.

[0043] When the vehicle's road conditions change and the differential lock needs to be disengaged, the control mechanism guides the drive fork 3 to move in the opposite direction, causing the movable toothed sleeve 7 to gradually move away from the engaged toothed ring 8 along the axial direction to disengage the transmission. As the distance between the two continues to increase, the strong magnetic module 71 on the outside of the movable toothed sleeve 7 also moves away from the strong magnetic module 61 on the outside of the magnetic sliding unit 6. This causes the forward axial pushing and squeezing action and the magnetic field repulsion force applied to the magnetic sliding unit 6 during the initial padlock and approach phases to gradually weaken and dissipate. At this time, the spring 81, which was previously in a compressed state, loses the resistance pressure at the front and begins to release naturally. The elastic potential energy stored inside generates a forward axial extension force, which directly pushes the trapezoidal slider 82 located in front of it forward. The trapezoidal slider 82 then transmits a relatively smooth axial thrust to the tail end face of the magnetic sliding unit 6, guiding the magnetic sliding unit 6 to slide smoothly forward along the spline guide structure outside the engaged toothed ring 8 until it is completely pushed back and stops at the initial working position in front of the padlock. Thus, the entire axial avoidance buffer assembly is reset by relying on a purely mechanical elastic release method, providing the basic structural form and position preparation for the next padlock engagement cycle.

Claims

1. A passive magnetic differential lock device and control method, comprising a left side drive structure (1) and a right side drive structure (2), characterized in that, The left drive structure (1) is provided with a movable tooth sleeve (4) on the outside, the right drive structure (2) is provided with a engaged tooth ring (5) on the outside, the left drive structure (1) is provided with a drive fork (3) on the outside, the drive fork (3) pushes the movable tooth sleeve (4) to slide towards the engaged tooth ring (5), the movable tooth sleeve (4) is provided with a strong magnetic module (41) on the outside of the end face of the movable tooth sleeve (4) facing the engaged tooth ring (5), the engaged tooth ring (5) is provided with a strong magnetic module (51) on the outside of the end face of the movable tooth sleeve (4), the strong magnetic module (41) and the strong magnetic module (51) are arranged opposite to each other and have the same magnetic poles.

2. A passive magnetic differential lock device according to claim 1, characterized in that The left drive structure (1) has an external spline, and the movable tooth sleeve (4) has an internal spline. The internal spline of the movable tooth sleeve (4) and the external spline of the left drive structure (1) are configured to cooperate. The tooth width of the internal spline of the movable tooth sleeve (4) is smaller than the groove width of the external spline of the left drive structure (1), allowing the movable tooth sleeve (4) to rotate circumferentially on the left drive structure (1).

3. The passive magnetic differential lock device according to claim 1, characterized in that, The inner spline teeth of the movable tooth sleeve (4) have grooves, and the strong magnetic module (41) is installed in the groove of the movable tooth sleeve (4). The outer spline teeth of the engaged tooth ring (5) have grooves, and the strong magnetic module (51) is installed in the groove of the engaged tooth ring (5).

4. A passive magnetic differential lock device according to claim 1, characterized in that, When the movable tooth sleeve one (4) and the engaged tooth ring one (5) approach each other, the strong magnetic module one (41) and the strong magnetic module two (51) repel each other with the same pole, generating a repulsive force, which drives the movable tooth sleeve one (4) to rotate, aligning the inner spline groove of the movable tooth sleeve one (4) with the outer spline teeth of the engaged tooth ring one (5).

5. A passive magnetic differential lock device according to claim 1, characterized in that, The movable tooth sleeve 1 (4) and the engaged tooth ring 1 (5) can be replaced by the movable tooth sleeve 2 (7) and the engaged tooth ring 2 (8) respectively. The movable tooth sleeve 2 (7) is provided on the left drive structure (1), and the engaged tooth ring 2 (8) is installed on the right drive structure (2). The drive fork (3) pushes the movable tooth sleeve 2 (7) to slide towards the engaged tooth ring 2 (8). A strong magnetic module 4 (71) is installed on the outside of the movable tooth sleeve 2 (7). A magnetic sliding unit (6) is installed on the outside of the engaged tooth ring 2 (8). A strong magnetic module 3 (61) is installed on the outside of the magnetic sliding unit (6). The strong magnetic module 3 (61) and the strong magnetic module 4 (71) are arranged opposite each other and have the same magnetic poles.

6. A passive magnetic differential lock device according to claim 5, characterized in that, The magnetic sliding unit (6) and the second gear ring (8) are configured by spline connection, allowing the magnetic sliding unit (6) to slide back and forth along the axial direction outside the second gear ring (8). A groove is machined on the outer side of the tail of the second gear ring (8). A spring (81) and a trapezoidal slider (82) are installed in the groove of the second gear ring (8). The spring (81) pushes the trapezoidal slider (82) to abut against the tail end of the magnetic sliding unit (6).

7. A passive magnetic differential lock device according to claim 5, characterized in that, The strong magnetic module three (61) corresponds to the radial direction phase of the outer spline of the engaged gear ring two (8), and the strong magnetic module four (71) corresponds to the radial direction phase of the inner spline of the movable gear sleeve two (7).

8. A passive magnetic differential lock device according to claim 6, characterized in that, When the movable tooth sleeve 2 (7) and the engaged tooth ring 2 (8) approach each other, the strong magnetic module 4 (71) and the strong magnetic module 3 (61) repel each other with the same pole, generating a repulsive force, which drives the movable tooth sleeve 2 (7) to rotate, aligning the inner spline groove of the movable tooth sleeve 2 (7) with the outer spline tooth of the engaged tooth ring 2 (8), while the magnetic sliding unit (6) moves backward and compresses the spring (81).

9. A passive magnetic differential lock device according to claim 8, characterized in that, When the drive fork (3) drives the movable tooth sleeve (7) away from the engaged tooth ring (8), the spring (81) pushes the trapezoidal slider (82) to generate axial force, restoring the magnetic sliding unit (6) to its initial position.

10. A control method for a passive magnetic differential lock device, applied to any one of claims 1-9, characterized in that, Includes the following steps: Obtain the difference in wheel-end rotational speed between the left and right wheels; Determine whether the wheel end speed difference exceeds the critical speed difference; If the wheel end speed difference exceeds the critical speed difference, the vehicle controller actively controls the speed of the left wheel and the right wheel, or controls the vehicle to resume normal straight driving, or controls the vehicle to stop. Once it is determined that the speed difference at the wheel ends does not exceed the critical speed difference and the speed difference condition is met, the linear padlock action continues.

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