Gear shifting trend sensor for radial bearing seat

Abstract

A gear shifting trend sensor of a radial bearing seat comprises a shell, a push-pull shaft, a reset spring and a magnet fixed on the push-pull shaft are arranged in the shell, the initial state of the magnet corresponds to that of a sensor outside the shell, the radial bearing seat is arranged at one end of the shell, an electric appliance box is arranged outside the radial bearing seat, and the push-pull shaft is reset by compressing the same reset spring when pushed in and pulled out. And the two strokes are consistent. The utility model has the beneficial effects that the technical scheme provides an angle fault-tolerant capability through the design of the radial bearing seat, and allows the push-pull shaft to smoothly perform linear displacement when bearing external angle deviation, thereby avoiding the problem of clamping stagnation caused by deviation of a stress direction. Meanwhile, the same reset spring is compressed in the push-in operation and the pull-out operation, it is guaranteed that the magnet accurately returns to the initial position after reset through the consistent stroke, the stability and reliability of sensor signal detection are guaranteed, and position errors are reduced.

Description

Technical Field

[0001] The utility model relates to a vehicle accessory, in particular to a gear shifting trend sensor of a centripetal bearing seat. Background Art

[0002] In motorcycle shifting systems, shift trend sensors are primarily used to monitor the rider's shifting intentions in real time to support intelligent control of automatic transmissions or assist manual shifting operations. This sensor is typically mounted on the push-pull shaft of the shift mechanism, and its application scenarios include the need for rapid shifting during urban commuting or high-speed riding. During use, when the rider operates the shift lever, the push-pull shaft is pushed in (for upshifting) or pulled out (for downshifting), causing the magnet attached to it to move; a sensor (such as a Hall effect sensor) detects the change in magnet position, generating an electrical signal that is transmitted to the control unit to determine the shifting trend (e.g., acceleration for upshifting or deceleration for downshifting). This process involves the reciprocating motion of the push-pull shaft, and a return spring returns the push-pull shaft to its initial position after the operation, ensuring that the sensor can accurately capture the next operation. This technology is widely used in modern motorcycle electronic shifting systems to improve shifting efficiency and riding comfort.

[0003] However, the reset mechanisms in existing technologies have significant flaws. Common solutions include using two independent springs to handle push-in and pull-out resets, or using the same spring to achieve bidirectional reset through tension and compression. In the dual-spring design, spring manufacturing tolerances and installation deviations make it difficult to ensure consistent reset force. In the single-spring solution, processing accuracy issues (such as material unevenness or dimensional errors) lead to asymmetric spring forces in the tension and compression phases. These flaws all result in inconsistent reset force, making it impossible for the magnet to accurately return to its initial position during reset. This in turn causes sensor detection errors, affecting shift accuracy and system reliability, and increasing the risk of misoperation. Utility Model Content

[0004] In view of the deficiencies in the prior art, the present invention provides a centripetal bearing seat shift trend sensor that ensures that a magnet can be reset to an initial position by ensuring that the reset force of a reset spring is consistent.

[0005] To achieve the above-mentioned purpose, the technical solution of the utility model is as follows: a radial bearing seat shift trend sensor, including a shell, a push-pull shaft, a reset spring for driving the push-pull shaft to reset, and a magnet fixed on the push-pull shaft and displaced with the push-pull shaft. The magnet is arranged corresponding to the sensor position outside the shell in the initial state. One end of the shell is a radial bearing seat, and an electrical box for placing the sensor is arranged on the outside of the radial bearing seat. When the push-pull shaft is pushed in and pulled out, the spring force obtained by compressing the same reset spring is used to reset the push-pull shaft, and the pushing-in and pulling-out strokes of the push-pull shaft are consistent.

[0006] The beneficial effects of the present invention are as follows: the technical solution provides angular fault tolerance through the design of the radial bearing seat, allowing the push-pull shaft to smoothly move linearly when subjected to external angular deviations, thereby avoiding the problem of jamming caused by force direction deviation. At the same time, the same return spring is compressed during both the pushing and pulling operations, and the consistent stroke ensures that the magnet accurately returns to its initial position after reset, which ensures the stability and reliability of sensor signal detection and reduces position error. As a preferred embodiment, the radial bearing seat can be designed as a spherical joint structure, with a spherical mating surface connected to the push-pull shaft. When the push-pull shaft is subjected to an inclined external force, the spherical mating surface allows the shaft to deflect freely within a predetermined angle range without hindering linear motion, thereby effectively achieving angular fault tolerance. Another preferred embodiment is that the return spring adopts a symmetrically arranged bidirectional compression design, with both ends of the spring fixed to a movable limit element. When the push-pull shaft is pushed in or pulled out, the limit element synchronously moves the compression spring, so that the spring generates equal return force under equal compression, ensuring stroke consistency and avoiding position drift. These structural optimizations not only improve the durability of the sensor but also reduce assembly complexity.

[0007] Furthermore, a first retaining ring and a second retaining ring are provided on the push-pull shaft, and the return spring is provided between the first retaining ring and the second retaining ring. When the push-pull shaft is pushed in or pulled out, the first retaining ring and the second retaining ring move toward each other to compress the return spring.

[0008] This technical solution, by providing a first and second retaining ring as a stopper for the return spring, ensures efficient spring compression during both the push-pull shaft's insertion and extraction movements, preventing spring twisting or deflection and thus providing a stable return force. This simplifies the mechanical design and reduces the number of components, while also improving the system's reliability and lifespan because the spring's compression path is precisely controlled, reducing the risk of wear. As a preferred embodiment, the retaining ring can be designed as an annular flange structure, with its inner diameter interfering with the push-pull shaft and its outer diameter slidingly connected to a guide groove on the inner wall of the housing. When the push-pull shaft moves, the guide groove guides the retaining ring in its opposite direction, directly compressing the spring without the need for an additional transmission mechanism. Another preferred embodiment utilizes a helical compression spring for the return spring, with its ends welded or clipped to the retaining ring. The relative displacement of the retaining rings applies uniform compression force, ensuring a linear response in both insertion and extraction modes. These implementations not only meet functional requirements but also enhance overall compactness.

[0009] Furthermore, when the push-pull shaft is pulled out, the first retaining ring remains in a relative position, and the second retaining ring moves toward the first retaining ring to compress the return spring; when the push-pull shaft is pushed in, the second retaining ring remains in a relative position, and the first retaining ring moves toward the second retaining ring to compress the return spring.

[0010] This solution clarifies the movement of the retaining ring under different operating modes of the push-pull shaft, ensuring that the reset spring is only compressed on one side, avoiding unnecessary friction and energy loss, thereby improving reset accuracy and response speed. This helps the magnet always return to its initial position, reduces sensor drift error, and extends the service life of the spring. As a preferred method, the first retaining ring can be integrated with a fixed pin structure that cooperates with the positioning hole on the housing. The fixed pin locks the retaining ring position when the push-pull shaft is pulled out, while the second retaining ring directly pushes the compression spring through the axial force of the push-pull shaft. Another preferred method is to design the second retaining ring as a floating ring with an elastic clip on its outer side. During the push-in operation, the clip engages with the housing groove to fix the position, while the first retaining ring is driven to move by the push-pull shaft. These structures achieve the relative stillness of the retaining rings through a mechanical locking mechanism, ensuring that the compression process is efficient and controllable.

[0011] Furthermore, a reset groove is provided in the shell for the first retaining ring and the second retaining ring to move therein, and the first retaining ring abuts against one side of the reset groove toward the pulling direction of the push-pull shaft when the magnet is in the initial position, and the second retaining ring abuts against the other side of the reset groove toward the pushing direction of the push-pull shaft when the magnet is in the initial position; the first drive ring and the second drive ring are provided at both ends of the corresponding reset groove on the push-pull shaft, which respectively abut against the first retaining ring and the second retaining ring when the magnet is in the initial position.

[0012] This technical solution provides precise guidance and positioning for the retaining ring through the cooperation of the reset groove and the drive ring, ensuring that the retaining ring is in close contact with the side wall of the groove in the initial position, thereby achieving orderly movement of the retaining ring during the push-pull shaft movement and preventing radial deviation when the spring is compressed. This enhances the stability of the system, reduces the impact of vibration, and ensures the consistency of the magnet reset. As a preferred method, the reset groove can be designed as a U-shaped cross-section groove, with limiting bosses on its two side walls. The first and second retaining rings are embedded in the boss recesses in the initial position and fixed, while the drive ring adopts a stepped design. When the push-pull shaft moves, the stepped surface pushes the retaining ring out of the recess and moves. Another preferred method is to use an inclined surface between the drive ring and the retaining ring. When the push-pull shaft moves, the inclined surface generates a component force that drives the retaining ring to slide into the deep reset groove to compress the spring. These structures optimize the force transmission path and avoid jamming.

[0013] Furthermore, the shell also includes a connecting cover, and the corresponding end faces of the radial bearing seat and the connecting cover are connected by threads. After the connection, the radial bearing seat is partially wrapped in the connecting cover and the part wrapped in the connecting cover is arranged on the radial outside of the reset spring, and the reset groove is arranged at the connecting part of the connecting cover and the radial bearing seat.

[0014] This solution achieves compact assembly of the housing through threaded connections, reducing the axial dimensions. At the same time, the connecting cover wraps around the radial bearing seat, providing radial support for the reset spring, preventing the spring from twisting or radially deforming during compression, and ensuring a stable and reliable reset force. This improves the overall structural strength and sealing, making disassembly and maintenance easier. As a preferred method, an annular guide rib can be provided on the inner wall of the connecting cover to cooperate with the groove on the outer wall of the radial bearing seat. After the threaded connection, the guide rib is embedded in the groove to form a radial constraint, and the outer side of the reset spring contacts the guide rib to prevent radial displacement. Another preferred method is to integrate the reset groove into the threaded connection, and the groove adopts a segmented design. The connecting cover and the radial bearing seat each contribute half of the groove wall, and a complete groove body is formed after assembly. These structures simplify the manufacturing process and enhance the torsional resistance.

[0015] Furthermore, the connecting cover and the radial bearing seat are respectively provided with a first driving groove and a second driving groove for the first driving ring and the second driving ring to slide therein, and the moving distance of the first driving ring in the first driving groove is equivalent to the moving distance of the second driving ring in the second driving groove.

[0016] This technical solution accurately limits the stroke of the push-pull shaft through the design of the drive groove, ensuring that the push-in and pull-out operations have equal moving distances, thereby ensuring the symmetry of the magnet displacement and the reset accuracy, and avoiding over-travel damage. At the same time, the drive groove provides a smooth sliding guide, reducing friction and wear. As a preferred embodiment, the first drive groove and the second drive groove can be designed as a linear guide structure, the inner wall of which is provided with a low-friction coating, the drive ring adopts a cylindrical slider to cooperate with the groove, and hard limit blocks are provided at both ends of the groove to define the end point of the stroke; another preferred embodiment is to use a ball bearing mechanism between the drive ring and the drive groove, and the ball is embedded in the ring groove gap, rolling to reduce resistance during movement. These implementation plans optimize motion control and improve response efficiency.

[0017] Furthermore, the first retaining ring is arranged in the connecting cover, the second retaining ring is arranged in the radial bearing seat, the axial width of the first drive ring is greater than the axial width of the second drive ring, and the distance between the end faces of the first retaining ring and the radial bearing seat in the reset groove, the moving distance of the first drive ring in the first drive groove, and the moving distance of the second drive ring in the second drive groove are equivalent.

[0018] This solution realizes a multiple limiting mechanism by optimizing the arrangement and dimensional relationship of the retaining ring and the drive ring. In the push-in operation, the end faces of the second drive ring and the first retaining ring are matched to form a more reliable stroke end protection to prevent overload, while simplifying the structure of the second drive ring to save space. This enhances the safety and compactness of the system. As a preferred method, the first retaining ring can be designed as an L-shaped cross-section, with its vertical arm contacting the end face of the radial bearing seat for position limiting, while the first drive ring adopts a thickened ring body to increase strength; another preferred method is that the second drive ring integrates a thin flange, the thickness of which is compensated by the groove depth to ensure consistent movement distance. These structures balance the limiting function and lightweight requirements.

[0019] Furthermore, first limiting planes are symmetrically arranged on both sides of the radial direction of the first drive ring, circumferential limiting grooves are arranged in the first drive groove corresponding to the two first limiting planes, a second limiting plane is arranged at the center of the circumferential limiting groove corresponding to the first limiting plane, and both ends of the second limiting plane are provided with a clearance arc groove, the first limiting plane and the second limiting plane coincide with each other at the center, and at least part of the two ends of the first limiting plane are located in the clearance arc groove.

[0020] This technical solution effectively prevents the first drive ring from circumferential rotation during movement through the cooperation of the limiting plane and the clearance arc groove, ensuring that the push-pull shaft maintains a straight trajectory and avoids jamming or offset. At the same time, the clearance arc groove reduces the contact area, reduces friction resistance, and improves the smoothness of movement. As a preferred embodiment, the first limiting plane can be designed as a rectangular protrusion embedded in the rectangular recess of the circumferential limiting groove, and the clearance arc groove is a semicircular recess. When the drive ring moves, the edge of the protrusion slides in the arc groove to reduce interference; another preferred embodiment is that the second limiting plane adopts an adjustable slider, which is kept aligned with the center of the first limiting plane by the spring preload. These structures optimize the guiding accuracy and durability.

[0021] Furthermore, a magnet is provided at one end of the push-pull shaft, and an oil seal and an oil sealing ring for preventing relative axial movement between the oil seal and the push-pull shaft are provided at the other end of the push-pull shaft.

[0022] This technical solution significantly improves sealing performance by adding an oil seal and oil seal ring to the non-magnet end of the push-pull shaft. The oil seal effectively isolates external contaminants (such as dust and moisture) and protects internal components. The oil seal prevents axial movement of the oil seal, ensuring sealing stability, extending sensor life, and improving reliability in harsh environments (such as motorcycle shifting systems). As a preferred option, the oil seal utilizes a lip seal ring structure with an inner lip that forms an interference fit with the push-pull shaft. The oil seal ring is a C-shaped retaining ring that fits into the push-pull shaft groove. The lip seal adaptively deforms as the shaft moves, blocking foreign matter, while the retaining ring secures the oil seal in place through elastic engagement. Another preferred option is to design the oil seal ring as a threaded ring that connects to the push-pull shaft. During assembly, tightening the ring squeezes the oil seal to form a secondary seal, enhancing leak prevention. This solution optimizes maintenance ease and environmental adaptability. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 This is a schematic diagram of the overall structure of an embodiment of the utility model;

[0024] Figure 2 This is a disassembled diagram of the housing of an embodiment of the present utility model;

[0025] Figure 3 This is a front view of the connection cover of an embodiment of the utility model;

[0026] Figure 4 This is an axonometric view of the connection cover of an embodiment of the utility model;

[0027] Figure 5 This is a disassembled diagram of the push-pull shaft of an embodiment of the utility model;

[0028] Figure 6 A partial cross-sectional view of the magnet assembly portion of an embodiment of the present utility model;

[0029] Figure 7 This is a partial cross-sectional view of the push-pull shaft movement limiting structure according to an embodiment of the present utility model;

[0030] Figure 8 This is a partial cross-sectional view of the oil seal of an embodiment of the present utility model. DETAILED DESCRIPTION

[0031] The utility model embodiment of a centripetal bearing seat shift trend sensor is as follows Figure 1-8As shown: It includes a shell 1, in which a push-pull shaft 2, a reset spring 3 for driving the push-pull shaft 2 to reset, and a magnet 21 fixed to the push-pull shaft 2 and displaced along with the push-pull shaft 2 are arranged. One end of the shell 1 is a radial bearing seat 11, and an electrical box 112 for placing a sensor 1121 is arranged outside the radial bearing seat 11. The magnet 21 is arranged in a corresponding position to the sensor 1121 in the electrical box 112 in the initial state. A first retaining ring 22 and a second retaining ring 23 are provided on the push-pull shaft 2, and the reset spring 3 is provided between the first retaining ring 22 and the second retaining ring 23. When the push-pull shaft 2 is pushed in or pulled out, the first retaining ring 22 and the second retaining ring 23 move toward each other to compress the reset spring 3, so that the push-pull shaft 2 is reset by the spring force obtained by compressing the same reset spring 3 when it is pushed in and pulled out, and the push-pull shaft 2 has the same pushing and pulling stroke.

[0032] A reset groove 4 is provided in the housing 1 for the movement of a first retaining ring 22 and a second retaining ring 23. When the magnet 21 is in the initial position, the first retaining ring 22 abuts against one side of the reset groove 4 in the direction of pulling out the push-pull shaft 2, and when the magnet 21 is in the initial position, the second retaining ring 23 abuts against the other side of the reset groove 4 in the direction of pushing in the push-pull shaft 2. A first drive ring 24 and a second drive ring 25 are provided at both ends of the push-pull shaft 2 corresponding to the reset groove 4, respectively abutting against the first retaining ring 22 and the second retaining ring 23 when the magnet 21 is in the initial position, so that the first retaining ring 22 and the second retaining ring 23 can move toward each other when the push-pull shaft 2 is pushed in and pulled out, respectively. Specifically, when the push-pull shaft 2 is pulled out, the first retaining ring 22 remains in a relative position, and the second retaining ring 23 moves toward the first retaining ring 22 driven by the second drive ring 25 to compress the return spring 3; when the push-pull shaft 2 is pushed in, the second retaining ring 23 remains in a relative position, and the first retaining ring 22 moves toward the second retaining ring 23 driven by the first drive ring 24 to compress the return spring 3.

[0033] The housing 1 also includes a connecting cover 12. The corresponding end surfaces of the radial bearing seat 11 and the connecting cover 12 are connected by threads. After the connection, the radial bearing seat 11 is partially wrapped within the connecting cover 12, and the portion wrapped within the connecting cover 12 is sleeved radially outward of the return spring 3. The return groove 4 is provided at the connection portion between the connecting cover 12 and the radial bearing seat 11. A first drive groove 121 and a second drive groove 111 are provided in the connecting cover 12 and the radial bearing seat 11, respectively corresponding to the first drive ring 24 and the second drive ring 25, for the first drive ring 24 and the second drive ring 25 to slide therein. The movement distance of the first drive ring 24 in the first drive groove 121 is equivalent to the movement distance of the second drive ring 25 in the second drive groove 111. The first retaining ring 22 is arranged in the connecting cover 12, the second retaining ring 23 is arranged in the radial bearing seat 11, the axial width of the first drive ring 24 is greater than the axial width of the second drive ring 25, and the distance between the end faces of the first retaining ring 22 and the radial bearing seat 11 in the reset groove 4, the moving distance of the first drive ring 24 in the first drive groove 121, and the moving distance of the second drive ring 25 in the second drive groove 111 are equivalent.

[0034] The first drive ring 24 is symmetrically provided with first limiting planes 241 on both sides of the radial direction. A circumferential limiting groove 1211 is provided in the first drive groove 121 corresponding to the two first limiting planes 241. A second limiting plane 12111 is provided at the center of the circumferential limiting groove 1211 corresponding to the first limiting plane 241. Both ends of the second limiting plane 12111 are provided with a clearance arc groove 12112. The first limiting plane 241 and the second limiting plane 12111 coincide at their centers, and at least part of the ends of the first limiting plane 241 are located within the clearance arc groove 12112. The magnet 21 is provided at one end of the push-pull shaft 2, and the other end of the push-pull shaft 2 is sleeved with an oil seal 26 and an oil sealing ring 27 for preventing relative axial movement between the oil seal 26 and the push-pull shaft 2.

[0035] When the push-pull shaft 2 needs to be pulled out, external force acts on the push-pull shaft 2 to make it move in the pulling direction inside the shell 1. At this time, the first drive ring 24 moves synchronously with the push-pull shaft 2. Since the first retaining ring 22 abuts against the side of the reset groove 4 facing the pulling direction in the initial position, and the first drive ring 24 abuts against the first retaining ring 22 in the initial position, the first retaining ring 22 maintains a relative position; at the same time, the second drive ring 25 moves synchronously with the push-pull shaft 2 in the pulling direction, and then drives the second retaining ring 23 to move toward the first retaining ring 22, so that the first retaining ring 22 and the second retaining ring 23 move toward each other to compress the reset spring 3. During this process, the second drive ring 25 slides in the second drive groove 111 until the second drive ring 25 abuts against the end of the second drive groove 111, realizing the stroke limit when the push-pull shaft 2 is pulled out. At this time, the reset spring 3 stores elastic potential energy. When the external force is removed, the reset spring 3 releases its elastic potential energy, pushing the second retaining ring 23 to move away from the first retaining ring 22, and then driving the push-pull shaft 2 to move in the opposite direction through the second drive ring 25 until the first retaining ring 22 and the second retaining ring 23 respectively abut against the two sides of the reset groove 4, and the magnet 21 returns to its initial position.

[0036] When the push-pull shaft 2 needs to be pushed in, external force acts on the push-pull shaft 2 to make it move in the pushing direction in the shell 1. At this time, the second driving ring 25 moves synchronously with the push-pull shaft 2. Since the second retaining ring 23 abuts against the side of the reset groove 4 facing the pushing direction in the initial position, and the second driving ring 25 abuts against the second retaining ring 23 in the initial position, the second retaining ring 23 maintains a relative position. At the same time, the first driving ring 24 moves synchronously with the push-pull shaft 2 in the pushing direction, thereby driving the first retaining ring 22 to move toward the second retaining ring 23, so that the first retaining ring 22 and the second retaining ring 23 move toward each other to compress the reset spring 3. In this process, the first driving ring 24 slides in the first driving groove 121 until the first retaining ring 22 abuts against the end face of the radial bearing seat 11 in the reset groove 4, and the first driving ring 24 abuts against the end of the first driving groove 121. The two work together to realize the stroke limit when the push-pull shaft 2 is pushed in. At this time, the reset spring 3 also stores elastic potential energy. When the external force is removed, the reset spring 3 releases its elastic potential energy, pushing the first retaining ring 22 to move away from the second retaining ring 23, and then driving the push-pull shaft 2 to move in the opposite direction through the first drive ring 24 until the first retaining ring 22 and the second retaining ring 23 respectively abut against the two sides of the reset groove 4, and the magnet 21 returns to its initial position.

[0037] The above embodiment is only one preferred embodiment of the present invention. Common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included in the protection scope of the present invention.

Claims

1. A centripetal bearing seat shift trend sensor, comprising a housing, a push-pull shaft disposed within the housing, a return spring for returning the push-pull shaft to its original position, and a magnet fixed to the push-pull shaft and displaced along with the shaft, wherein the magnet is initially positioned relative to the sensor outside the housing, and characterized in that: One end of the shell is a radial bearing seat, and an electrical box for placing the sensor is provided outside the radial bearing seat. The push-pull shaft is reset by compressing the spring force obtained by the same reset spring when the push-pull shaft is pushed in and pulled out, and the push-pull shaft has the same push-in and pull-out strokes.

2. The centripetal bearing seat shift trend sensor according to claim 1, characterized in that: The push-pull shaft is provided with a first retaining ring and a second retaining ring, and the return spring is provided between the first retaining ring and the second retaining ring. When the push-pull shaft is pushed in or pulled out, the first retaining ring and the second retaining ring move toward each other to compress the return spring.

3. The centripetal bearing seat shift trend sensor according to claim 2, characterized in that: When the push-pull shaft is pulled out, the first retaining ring remains in a relative position and the second retaining ring moves toward the first retaining ring to compress the return spring; when the push-pull shaft is pushed in, the second retaining ring remains in a relative position and the first retaining ring moves toward the second retaining ring to compress the return spring.

4. The centripetal bearing seat shift trend sensor according to claim 3, characterized in that: The shell is provided with a reset groove for the first retaining ring and the second retaining ring to move therein, the first retaining ring abuts against one side of the reset groove toward the pulling direction of the push-pull shaft when the magnet is in the initial position, and the second retaining ring abuts against the other side of the reset groove toward the pushing direction of the push-pull shaft when the magnet is in the initial position; the two ends of the corresponding reset groove on the push-pull shaft are provided with a first driving ring and a second driving ring, which respectively abut against the first retaining ring and the second retaining ring when the magnet is in the initial position.

5. The centripetal bearing seat shift trend sensor according to claim 4, characterized in that: The shell also includes a connecting cover, and the corresponding end faces of the radial bearing seat and the connecting cover are connected by threads. After the connection, the radial bearing seat is partially wrapped in the connecting cover and the part wrapped in the connecting cover is sleeved on the radial outside of the reset spring, and the reset groove is arranged at the connecting part of the connecting cover and the radial bearing seat.

6. The centripetal bearing seat shift trend sensor according to claim 5, characterized in that: The connecting cover and the radial bearing seat are respectively provided with a first driving groove and a second driving groove corresponding to the first driving ring and the second driving ring, and the first driving ring and the second driving ring are respectively provided with a first driving groove and a second driving groove for the first driving ring and the second driving ring to slide therein. The moving distance of the first driving ring in the first driving groove is equivalent to the moving distance of the second driving ring in the second driving groove.

7. The centripetal bearing seat shift trend sensor according to claim 6, characterized in that: The first retaining ring is arranged in the connecting cover, the second retaining ring is arranged in the radial bearing seat, the axial width of the first drive ring is greater than the axial width of the second drive ring, and the distance between the end faces of the first retaining ring and the radial bearing seat in the reset groove, the moving distance of the first drive ring in the first drive groove, and the moving distance of the second drive ring in the second drive groove are equivalent.

8. The centripetal bearing seat shift trend sensor according to claim 6, characterized in that: The first limiting planes are symmetrically arranged on both sides of the radial direction of the first driving ring, a circumferential limiting groove is arranged in the first driving groove corresponding to the two first limiting planes, a second limiting plane is arranged at the center of the circumferential limiting groove corresponding to the first limiting plane, and a clearance arc groove is arranged at both ends of the second limiting plane, the first limiting plane and the second limiting plane coincide with each other at the center, and at least part of the two ends of the first limiting plane are located in the clearance arc groove.

9. The centripetal bearing seat shift trend sensor according to claim 1, characterized in that: One end of the push-pull shaft is provided with a magnet, and the other end of the push-pull shaft is sleeved with an oil seal and an oil sealing ring for preventing relative axial movement between the oil seal and the push-pull shaft.

Images