One-way clutch and two-wheeler

Abstract

The present invention discloses an overrunning clutch and a two-wheeled vehicle. The overrunning clutch includes: a ratchet member, which includes a tower base and an end cover. The tower base is provided with a rotating shaft and first ratchet teeth surrounding the rotating shaft. The rotating shaft is fixedly connected to the end cover. The end cover is provided with second ratchet teeth facing the first ratchet teeth. Along the circumferential direction of the rotating shaft, the first ratchet teeth and the second ratchet teeth are arranged staggeredly; a sleeve, which is sleeved outside the rotating shaft. The sleeve is provided with a guiding groove, and the guiding groove is arranged along the axial direction of the sleeve; a slider, which includes a connected guiding block and a bearing bush. The inner wall of the bearing bush abuts against the rotating shaft and is located between the first ratchet teeth and the second ratchet teeth. One end of the bearing bush is provided with a first pawl. The guiding block is located in the guiding groove and can slide along the axial direction of the sleeve; wherein, when the sleeve rotates in the first direction, the first pawl can engage with the first ratchet teeth; when the sleeve rotates in the second direction, the bearing bush reciprocates between the first ratchet teeth and the second ratchet teeth to achieve disengagement. The present invention does not require the use of a spring and has a reliable structure.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicles, and particularly relates to a one-way clutch and a two-wheeled vehicle. Background Art

[0002] In common two-wheeled vehicles, a one-way clutch mechanism is usually installed to achieve the functions of one-way torque output and reverse clutch. In related technologies, a hub and a freewheel body form a one-way clutch mechanism, which is most commonly composed of ratchet teeth and pawls, and a return spring is provided to provide elastic force for the pawl, so that the pawl opens outward toward the ratchet teeth in the normal pressing state. When the hub rotates forward, the ratchet teeth engage with the pawl to drive the freewheel body to rotate. When the hub rotates backward, the ratchet teeth are separated from the pawl, and the hub rotates idly. However, in this ratchet tooth and pawl structure, the return spring may become loose or fatigue-fail during installation and operation, resulting in the failure of the engagement between the ratchet teeth and the pawl, the slipping of the two-wheeled vehicle, and low structural reliability. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. For this purpose, the present invention provides a one-way clutch that does not require the use of a spring and has a reliable structure.

[0004] The present invention also provides a two-wheeled vehicle having the above one-way clutch.

[0005] The one-way clutch according to the first aspect embodiment of the present invention includes: a ratchet member, including a freewheel body and an end cover, the freewheel body is provided with a rotating shaft and first ratchet teeth around the rotating shaft, the rotating shaft is fixedly connected to the end cover, the end cover is provided with second ratchet teeth facing the first ratchet teeth, along the circumferential direction of the rotating shaft, the first ratchet teeth and the second ratchet teeth are arranged staggeredly; a sleeve, sleeved outside the rotating shaft, the sleeve is provided with a guiding groove, and the guiding groove is arranged along the axial direction of the sleeve; a slider, including a guiding block and a bearing bush connected together, the inner wall of the bearing bush abuts against the rotating shaft and is located between the first ratchet teeth and the second ratchet teeth, one end of the bearing bush is provided with a first pawl, the guiding block is located in the guiding groove and can slide along the axial direction of the sleeve; wherein, when the sleeve rotates in the first direction, the first pawl can engage with the first ratchet teeth; when the sleeve rotates in the second direction, the bearing bush reciprocates between the first ratchet teeth and the second ratchet teeth to achieve disengagement.

[0006] The one-way clutch according to the first aspect of the present invention has at least the following beneficial effects: when the sleeve rotates along the first direction, the first pawl engages with the first ratchet tooth, the bearing drives the ratchet part to rotate, and the force on the sleeve can be transmitted to the ratchet part; when the sleeve rotates along the second direction, the bearing slides back and forth between the first ratchet tooth and the second ratchet tooth, the bearing cannot drive the ratchet part to rotate, and the force on the sleeve will not be transmitted to the ratchet part, thereby realizing one-way clutch between the sleeve and the ratchet part. No spring is required in this process, and the structure is reliable.

[0007] According to some embodiments of the first aspect of the present invention, a second pawl for engaging with a second ratchet tooth is provided at one end of the bearing shell away from the first pawl, and the first ratchet tooth and the second ratchet tooth have the same tooth shape and the same number of teeth.

[0008] According to some embodiments of the first aspect of the present invention, the number of teeth of the first ratchet is set to N, and along the circumference of the rotating shaft, the staggered angle between the first ratchet and the second ratchet is α, and α is equal to 180° divided by N.

[0009] According to some embodiments of the first aspect of the present invention, the inner wall surface of the bearing shell is an arc surface matching the outer wall of the rotating shaft, the central angle occupied by the bearing shell is β, and β is equal to 180° divided by N.

[0010] According to some embodiments of the first aspect of the present invention, along the axial direction of the rotating shaft, the maximum length of the bearing shell is equal to the minimum distance between the first ratchet tooth and the second ratchet tooth.

[0011] According to some embodiments of the first aspect of the present invention, along the radial direction of the rotating shaft, the outer diameter of the first ratchet tooth and the second ratchet tooth is D, the tooth thickness of the first ratchet tooth and the second ratchet tooth is d, d is greater than or equal to 0.05D, and d is less than or equal to 0.1D.

[0012] According to some embodiments of the first aspect of the present invention, along the radial direction of the rotating shaft, the thickness of the bearing bush is equal to the tooth thickness of the first ratchet tooth.

[0013] According to some embodiments of the first aspect of the present invention, a mounting column is provided at the end of the rotating shaft, the mounting column is consistent with the axis of the rotating shaft, and the end cover is sleeved on the outside of the mounting column and fixed.

[0014] According to some embodiments of the first aspect of the present invention, a pin hole is provided on the end surface of the rotating shaft, and a pin shaft is provided on the end cover, and the pin shaft is located in the pin hole to fix the end cover.

[0015] According to some embodiments of the first aspect of the present invention, the one-way clutch further comprises a thrust plate, wherein the thrust plate is fixedly connected to the mounting column to limit the sleeve along the axial direction of the mounting column.

[0016] According to some embodiments of the first aspect of the present invention, a plurality of guiding grooves are provided, and the plurality of guiding grooves are uniformly arranged along the circumferential direction of the sleeve. A plurality of sliders are provided, and the sliders correspond to the guiding grooves one by one.

[0017] A two-wheeled vehicle according to an embodiment of the second aspect of the present invention includes the one-way clutch according to the embodiment of the first aspect of the present invention.

[0018] The two-wheeled vehicle according to the embodiment of the second aspect of the present invention has at least the following beneficial effects: when the sleeve rotates in the first direction, the first pawl engages with the first ratchet teeth, and the bearing shell drives the ratchet member to rotate, and the force on the sleeve can be transmitted to the ratchet member; when the sleeve rotates in the second direction, the bearing shell reciprocates between the first ratchet teeth and the second ratchet teeth, and the bearing shell cannot drive the ratchet member to rotate, and the force on the sleeve will not be transmitted to the ratchet member, so as to realize the one-way clutch between the sleeve and the ratchet member. In this process, no spring is required, and the structure is reliable.

[0019] The additional aspects and advantages of the present invention will be partially given in the following description, partially become apparent from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The additional aspects and advantages of the present invention will become apparent and be easily understood in conjunction with the following description of the embodiments with reference to the accompanying drawings, wherein:

[0021] Figure 1 is a schematic diagram of the overall structure of the one-way clutch according to the embodiment of the first aspect of the present invention;

[0022] Figure 2 is an exploded view of the one-way clutch according to the embodiment of the first aspect of the present invention;

[0023] Figure 3 is a schematic diagram of the structure of the ratchet member according to the embodiment of the first aspect of the present invention;

[0024] Figure 4 is Figure 3 a stepped sectional view taken along A-A in

[0025] Figure 5 is a schematic diagram of the structure of the slider according to the embodiment of the first aspect of the present invention;

[0026] Figure 6 is Figure 5 a schematic diagram of the structure from another perspective;

[0027] Figure 7 is a schematic diagram of the position of the slider between the first ratchet teeth and the second ratchet teeth according to the embodiment of the first aspect of the present invention;

[0028] Figure 8Schematic diagram II of the position of the slider between the first ratchet tooth and the second ratchet tooth in the first aspect embodiment of the present invention;

[0029] Figure 9 Schematic diagram III of the position of the slider between the first ratchet tooth and the second ratchet tooth in the first aspect embodiment of the present invention.

[0030] The reference numerals in the attached drawings are as follows:

[0031] Ratchet member 100, tower base 110, rotating shaft 111, first ratchet tooth 112, mounting post 113, pin hole 114, mounting portion 115, end cap 120, second ratchet tooth 121, pin shaft 122;

[0032] Sleeve 200, guide groove 201;

[0033] Slider 300, guide block 310, bearing bush 320, first pawl 321, second pawl 322;

[0034] Thrust washer 400. Detailed implementation manners

[0035] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals represent the same or similar elements or elements with the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation to the present invention.

[0036] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by terms such as up, down, front, back, left, right, etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0037] In the description of the present invention, if the first and second are described only for the purpose of distinguishing technical features, they should not be construed as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence of the indicated technical features.

[0038] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installation, connection, etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific content of the technical solution.

[0039] The one-way clutch is an extremely important component in the rear-wheel drive of a two-wheeled vehicle. The one-way clutch can only transmit torque in one direction and cannot transmit torque in the reverse direction, enabling the two-wheeled vehicle to have normal functions and preventing it from driving backward.

[0040] Referring to Figures 1 to 9 , an embodiment of the first aspect of the present invention provides a one-way clutch applied to a two-wheeler. The one-way clutch includes: a ratchet member 100, including a tower base 110 and an end cover 120. The tower base 110 is provided with a rotating shaft 111 and a first ratchet tooth 112 surrounding the rotating shaft 111. The rotating shaft 111 is fixedly connected to the end cover 120. The end cover 120 is provided with a second ratchet tooth 121 facing the first ratchet tooth 112. Along the circumferential direction of the rotating shaft 111, the first ratchet tooth 112 and the second ratchet tooth 121 are arranged staggeredly; a sleeve 200, sleeved outside the rotating shaft 111. The sleeve 200 is provided with a guiding groove 201, and the guiding groove 201 is arranged along the axial direction of the sleeve 200; a slider 300, including a connected guiding block 310 and a bearing bush 320. The inner wall of the bearing bush 320 abuts against the rotating shaft 111 and is located between the first ratchet tooth 112 and the second ratchet tooth 121. One end of the bearing bush 320 is provided with a first pawl 321. The guiding block 310 is located in the guiding groove 201 and can slide along the axial direction of the sleeve 200; wherein, when the sleeve 200 rotates in the first direction, the first pawl 321 can engage with the first ratchet tooth 112; when the sleeve 200 rotates in the second direction, the bearing bush 320 reciprocates between the first ratchet tooth 112 and the second ratchet tooth 121 to achieve disengagement.

[0041] Specifically, during the working process, in combination with Figure 1 , Figure 7 and Figure 8 , when the sleeve 200 rotates in the first direction, the sleeve 200 drives the bearing bush 320 to rotate in the same direction. The first pawl 321 of the bearing bush 320 engages with the first ratchet tooth 112, and the bearing bush 320 drives the ratchet member 100 to rotate. At this time, the force on the sleeve 200 can be transmitted to the ratchet member 100. In combination with Figure 1 , Figure 7 and Figure 9 , when the sleeve 200 rotates in the second direction, the sleeve 200 drives the bearing bush 320 to rotate in the same direction. The first pawl 321 at one end of the bearing bush 320 slides along the tooth surface of the first ratchet tooth 112 until the first pawl 321 disengages from the tooth surface of the first ratchet tooth 112. The sleeve 200 continues to rotate, and the other end of the bearing bush 320 abuts against the second ratchet tooth 121. At this time, the second ratchet tooth 121 can exert a reaction force on the bearing bush 320. This reaction force drives the bearing bush 320 to move towards the direction where the first ratchet tooth 112 is located. During the continuous rotation of the sleeve 200 in the second direction, the bearing bush 320 reciprocates between the first ratchet tooth 112 and the second ratchet tooth 121, and the bearing bush 320 cannot drive the ratchet member 100 to rotate. The force on the sleeve 200 will not be transmitted to the ratchet member 100, thereby realizing the one-way clutch between the sleeve 200 and the ratchet member 100. During this process, there is no need to use a spring, and the structure is reliable.

[0042] It should be noted that one end of the bearing shell 320 away from the first pawl 321 can be designed according to the shape of the second ratchet tooth 121, so that when the sleeve 200 rotates in the second direction and the bearing shell 320 abuts against the second ratchet tooth 121, the second ratchet tooth 121 can exert a force on the bearing shell 320 towards the direction where the first ratchet tooth 112 is located, so that the bearing shell 320 slides reciprocally between the first ratchet tooth 112 and the second ratchet tooth 121 to achieve separation. The specific shape of the second ratchet tooth 121 is not specifically limited here.

[0043] It should be noted that in combination with Figure 1 and Figure 2 , along the axial direction of the sleeve 200, the guide groove 201 guides the guide block 310, making the movement of the bearing shell 320 between the first ratchet tooth 112 and the second ratchet tooth 121 smoother. In addition, along the circumferential direction of the sleeve 200, the guide groove 201 can limit the guide block 310, so that when the sleeve 200 rotates, the bearing shell 320 can rotate in the same direction as the sleeve 200. Preferably, along the circumferential direction of the sleeve 200, the width of the guide groove 201 is the same as the width of the guide block 310, so that when the rotation direction of the sleeve 200 changes, the guide block 310 can respond quickly, and the guide block 310 can be prevented from hitting the inner wall of the guide groove 201 to generate noise or deform the guide block 310, thereby reducing noise and extending the service life.

[0044] It should be noted that along the axial direction of the sleeve 200, the slidable distance of the guide block 310 in the guide groove 201 should be greater than or equal to the axial sliding distance of the bearing shell 320 along the rotating shaft 111, so that when the sleeve 200 rotates in the first direction, the bearing shell 320 can be fully engaged with the first ratchet tooth 112, and when the sleeve 200 rotates in the second direction, the bearing shell 320 slides reciprocally between the first ratchet tooth 112 and the second ratchet tooth 121 to successively disengage from the first ratchet tooth 112 and the second ratchet tooth 121.

[0045] Preferably, during actual use, lubricating grease can be added to the sleeve 200 to reduce frictional losses, facilitate the movement of the sleeve 200 and the bearing shell 320, extend the service life, and reduce noise.

[0046] Preferably, during actual use, the inner wall of the sleeve 200 should abut against the outer wall of the first ratchet tooth 112 and the outer surface of the second ratchet tooth 121, so that the sleeve 200 is not prone to shaking during rotation.

[0047] It can be understood that with reference to Figure 2 , a second pawl 322 for engaging the second ratchet tooth 121 is provided at one end of the bearing shell 320 away from the first pawl 321, and the tooth shapes of the first ratchet tooth 112 and the second ratchet tooth 121 are the same and the number of teeth is equal.

[0048] It should be noted that the first ratchet tooth 112 and the second ratchet tooth 121 have the same tooth shape, which means that the first ratchet tooth 112 and the second ratchet tooth 121 have the same tooth shape, and are not limited to changes in their positions, such as mirror images, rotation, translation, etc. Figure 3 The first ratchet tooth 112 and the second ratchet tooth 121 have substantially the same appearance. The second ratchet tooth 121 is obtained by rotating the first ratchet tooth 112 along the circumferential direction of the rotating shaft 111 at a set angle after being mirrored.

[0049] Specifically, after the first ratchet teeth 112 and the second ratchet teeth 121 are staggered along the circumferential direction of the rotating shaft 111, when the sleeve 200 changes from the second rotation direction to the first rotation direction, the bearing bush 320 can cooperate with the first ratchet teeth 112 or the second ratchet teeth 121 that are closest to it, so as to reduce the idle travel of the bearing bush 320, so that the power on the sleeve 200 can be quickly transmitted to the ratchet member 100, thereby improving the working efficiency. In addition, the first ratchet teeth 112 and the second ratchet teeth 121 have the same tooth shape and the same number of teeth, so that when the sleeve 200 rotates in the second direction, the bearing bush 320 can reciprocate between the first ratchet teeth 112 and the second ratchet teeth 121 more smoothly.

[0050] It is easy for a person skilled in the art to think of that the tooth shape of the second ratchet tooth 121 can be different from the tooth shape of the first ratchet tooth 112, and the second ratchet pawl 322 is designed according to the shape of the second ratchet tooth 121, so that when the sleeve 200 rotates along the first direction, the second ratchet pawl 322 can engage with the second ratchet tooth 121, and when the sleeve 200 rotates along the second direction, the bearing 320 slides back and forth between the first ratchet tooth 112 and the second ratchet tooth 121, and the bearing 320 will not drive the ratchet wheel 100 to rotate, and no specific limitation is made here.

[0051] It is understandable that, referring to Figure 3 and Figure 4 , the number of teeth of the first ratchet teeth 112 is set to N, and along the circumference of the rotating shaft 111, the staggered angle between the first ratchet teeth 112 and the second ratchet teeth 121 is α, and α is equal to 180° divided by N. It should be understood that, in combination Figure 3 Along the circumference of the rotating shaft 111, the arc length distance between the first ratchet teeth 112 and the first ratchet teeth 112 is half of the circumferential arc length width of the first ratchet teeth 112, so that when the sleeve 200 changes from the second rotation direction to the first rotation direction, the bearing 320 can cooperate with the nearest first ratchet tooth 112 or the second ratchet tooth 121. When the number of teeth of the first ratchet teeth 112 and the second ratchet teeth 121 remains unchanged, half of the idle travel of the bearing 320 can be reduced, thereby improving work efficiency.

[0052] It is easy for a person skilled in the art to think that, while ensuring that the bearing 320 can have a one-way clutch effect, the staggered angle between the first ratchet tooth 112 and the second ratchet tooth 121 along the circumference of the rotating shaft 111 can be any angle other than α, which can also play a role in reducing the idle travel of the bearing 320. No specific limitation is made here.

[0053] Those skilled in the art can understand that the number of teeth of the first ratchet tooth 112 can be set according to the outer diameter of the first ratchet tooth 112. The larger the outer diameter of the first ratchet tooth 112, the more teeth of the first ratchet tooth 112 can be set, so that the idle travel of the bearing 320 when sliding to the engagement of the first ratchet tooth 112 or the second ratchet tooth 121 is appropriate, making the movement smoother and meeting actual usage requirements.

[0054] It is understandable that, referring to Figure 6 The inner wall surface of the bearing bush 320 is an arc surface matching the outer wall of the rotating shaft 111, and the central angle of the bearing bush 320 is β, and β is equal to 180° divided by N. It should be noted that, in combination Figures 7 to 9 Along the circumference of the rotating shaft 111, the circumferential arc length width of the bearing 320 is equal to the arc length distance between the first ratchet tooth 112 and the second ratchet tooth 121. When the sleeve 200 changes from rotating in the first direction to rotating in the second direction, the first pawl 321 slides along the tooth surface of the first ratchet tooth 112 to half of the circumferential arc length width of the first ratchet tooth 112. The second pawl 322 is not blocked by the second ratchet tooth 121. At this time, the first pawl 321 continues to slide along the tooth surface of the first ratchet tooth 112, and the bearing 320 can slide to the right along the axial direction of the rotating shaft 111, so that the first pawl 321 can smoothly disengage from the first ratchet tooth 112. Similarly, when the second pawl 322 slides along the tooth surface of the second ratchet tooth 121, the bearing 320 can slide to the left along the axial direction of the rotating shaft 111, so that the second pawl 322 can smoothly disengage from the second ratchet tooth 121, so that when the sleeve 200 continues to rotate in the second direction, the movement of the bearing 320 between the first ratchet tooth 112 and the second ratchet tooth 121 is smoother.

[0055] It is understandable that, combined with Figures 7 to 9 Along the axial direction of the rotating shaft 111 , the maximum length of the bearing bush 320 is equal to the minimum distance between the first ratchet tooth 112 and the second ratchet tooth 121 .

[0056] It should be noted that, combined with Figure 7 , the minimum distance between the first ratchet tooth 112 and the second ratchet tooth 121 is the distance between the top of the first ratchet tooth 112 and the second ratchet tooth 121 on the same horizontal straight line along the axial direction of the rotating shaft 111. Specifically, Figure 8As shown, when the sleeve 200 rotates in the first direction, the first pawl 321 engages with the first ratchet tooth 112; when the sleeve 200 rotates in the second direction, one end of the bearing shell 320 first abuts against the first ratchet tooth 112 (as shown in Figure 7 ), when the bearing shell 320 disengages from the first ratchet tooth 112, the other end of the bearing shell 320 just abuts against the second ratchet tooth 121 (as shown in Figure 9 ). One end of the bearing shell 320 always abuts against the first ratchet tooth 112 or the second ratchet tooth 121 during the rotation process, making the reciprocating sliding of the bearing shell 320 between the first ratchet tooth 112 and the second ratchet tooth 121 smoother, and avoiding the bearing shell 320 from hitting the first ratchet tooth 112 or the second ratchet tooth 121 during the rotation process, thereby reducing noise.

[0057] It can be understood that, referring to Figure 3 , along the radial direction of the rotating shaft 111, the outer diameters of the first ratchet tooth 112 and the second ratchet tooth 121 are D, and the tooth thickness of the first ratchet tooth 112 and the second ratchet tooth 121 is d, d is greater than or equal to 0.05D and less than or equal to 0.1D. It should be noted that the outer diameters of the first ratchet tooth 112 and the second ratchet tooth 121 should be set according to the magnitude of the rated load, and the tooth thickness of the first ratchet tooth 112 and the second ratchet tooth 121 can be set according to the outer diameter sizes of the first ratchet tooth 112 and the second ratchet tooth 121, so that the first ratchet tooth 112 and the second ratchet tooth 121 have sufficient structural strength within the rated load range, and are not prone to deformation or damage, so as to ensure that the first ratchet tooth 112 and the second ratchet tooth 121 can work normally.

[0058] It can be understood that, referring to Figure 1 and Figure 2 , along the radial direction of the rotating shaft 111, the thickness of the bearing shell 320 is equal to the tooth thickness of the first ratchet tooth 112. It should be understood that the bearing shell 320 is located between the first ratchet tooth 112 and the second ratchet tooth 121. Along the radial direction of the rotating shaft 111, the outer diameter of the bearing shell 320 is the same as the outer diameter of the first ratchet tooth 112, so that the contact area between the pawl 321 of the bearing shell 320 and the first ratchet tooth 112 is larger, making the engagement between the pawl 321 and the first ratchet tooth 112 smoother. Similarly, it also makes the engagement between the pawl 321 of the bearing shell 320 and the second ratchet tooth 121 smoother.

[0059] Those skilled in the art can understand that the sleeve 200 is sleeved outside the rotating shaft 111, and the inner wall of the sleeve 200 should be fitted with the outer walls of the first ratchet tooth 112 and the second ratchet tooth 121 to ensure the smooth rotation of the sleeve 200. The thickness of the bearing shell 320 is consistent with the tooth thickness of the first ratchet tooth 112, which can make the inner wall of the bearing shell 320 abut against the rotating shaft 111, and then the outer wall of the bearing shell 320 abuts against the inner wall of the sleeve 200, so that during the movement of the sleeve 200 driving the bearing shell 320, the bearing shell 320 is not prone to shaking, and the movement of the bearing shell 320 is smoother.

[0060] It is understandable that, with reference to Figure 2 , an installation post 113 is provided at the end of the rotating shaft 111. The installation post 113 is aligned with the axis of the rotating shaft 111. The end cover 120 is sleeved outside the installation post 113 and fixed. It should be understood that after the end cover 120 is assembled on the installation post 113, it is fixed to the tower base 110 to form an integral structure, so that the pawl 321 of the bearing bush 320 meshes with the first ratchet tooth 112 or the second ratchet tooth 121, and both can drive the tower base 110 to rotate.

[0061] It is understandable that, with reference to Figure 2 , a pin hole 114 is provided on the end face of the rotating shaft 111, and a pin shaft 122 is provided on the end cover 120. The pin shaft 122 is located in the pin hole 114 to fix the end cover 120. It should be noted that the pin hole 114 and the pin shaft 122 are easy to process and convenient to disassemble and assemble.

[0062] Those skilled in the art can understand that the assembly positions of the pin hole 114 and the pin shaft 122 can be correspondingly set, so that the angle by which the first ratchet tooth 112 and the second ratchet tooth 121 are circumferentially offset along the rotating shaft 111 is a preset angle.

[0063] Optionally, the outer shape of the installation post 113 can be set as a square, and a square groove is correspondingly provided on the end cover 120. The installation post 113 is inserted into the square groove, and the end cover 120 can also be fixed to the tower base 110. The fixing method of the end cover 120 to the tower base 110 is not specifically limited herein.

[0064] It is understandable that, with reference to Figure 2 , the one-way clutch further includes a thrust washer 400. The thrust washer 400 is fixedly connected to the installation post 113 to axially limit the sleeve 200 along the installation post 113. It should be understood that the thrust washer 400 is used to limit the position of the sleeve 200 to prevent the sleeve 200 from falling off the rotating shaft 111. Optionally, the thrust washer 400 and the installation post 113 can be fixed by threaded connection for easy disassembly and assembly.

[0065] Optionally, one end of the thrust washer 400 can abut against the end cover 120, so as to axially limit the end cover 120 along the installation post 113.

[0066] It is understandable that, with reference to Figure 1 and Figure 2, there are multiple guiding grooves 201 provided, and the multiple guiding grooves 201 are evenly arranged along the circumferential direction of the sleeve 200. There are multiple sliders 300 provided, and the sliders 300 correspond to the guiding grooves 201 one by one. It should be understood that the multiple sliders 300 can act simultaneously, reducing the bearing capacity borne by a single slider 300, so as to prevent a single slider 300 from deforming or breaking due to excessive force during operation, thereby extending the service life. In addition, the multiple sliders 300 are evenly distributed along the circumferential direction of the sleeve 200, so that when the sleeve 200 drives the sliders 300 to rotate, the force between the sleeve 200 and the sliders 300 is uniform, thus making the rotation of the sleeve 200 and the sliders 300 more stable.

[0067] Optionally, the number of the sliders 300 is set to an odd number, which can make the rotation of the sleeve 200 and the sliders 300 stable, and no specific limitation is made here. Preferably, the number of the sliders 300 is set to three, and the three sliders 300 are evenly distributed along the circumferential direction of the sleeve 200, making the rotation of the sleeve 200 and the sliders 300 more stable.

[0068] In the second aspect embodiment of the present invention, a two-wheeled vehicle is proposed. The two-wheeled vehicle includes the one-way clutch of the first aspect embodiment. The one-way clutch includes: a ratchet member 100, including a hub 110 and an end cover 120. The hub 110 is provided with a rotating shaft 111 and first ratchet teeth 112 surrounding the rotating shaft 111. The rotating shaft 111 is fixedly connected to the end cover 120. The end cover 120 is provided with second ratchet teeth 121 facing the first ratchet teeth 112. Along the circumferential direction of the rotating shaft 111, the first ratchet teeth 112 and the second ratchet teeth 121 are arranged staggeredly; a sleeve 200 is sleeved outside the rotating shaft 111, and the sleeve 200 is provided with a guiding groove 201, and the guiding groove 201 is arranged along the axial direction of the sleeve 200; a slider 300 includes a connected guiding block 310 and a bearing bush 320. The inner wall of the bearing bush 320 abuts against the rotating shaft 111 and is located between the first ratchet teeth 112 and the second ratchet teeth 121. One end of the bearing bush 320 is provided with a first pawl 321, and the guiding block 310 is located in the guiding groove 201 and can slide along the axial direction of the sleeve 200; wherein, when the sleeve 200 rotates in the first direction, the first pawl 321 can engage with the first ratchet teeth 112; when the sleeve 200 rotates in the second direction, the bearing bush 320 reciprocates between the first ratchet teeth 112 and the second ratchet teeth 121 to achieve disengagement.

[0069] It should be noted that in the present invention, the two-wheeled vehicle can only transmit power in one direction and cannot transmit power in the other direction, that is, it has the function of one-way clutch. The two-wheeled vehicle can be a bicycle, an electric vehicle, or other types of two-wheeled vehicles, and no specific limitation is made here.

[0070] Taking a bicycle as an example for illustration, in the related art, the bicycle is driven by the rear wheel, and the rear wheel is driven by pedaling the pedals manually and through a chain. To achieve the functions of one-way output torque and reverse clutch, a one-way clutch needs to be installed. When the pedals are pedaled forward, the rear wheel is driven to rotate, enabling the bicycle to move forward normally. When the pedals are pedaled backward, the force on the pedals is not transmitted to the rear wheel to make the rear wheel reverse, avoiding potential safety hazards caused by the bicycle moving backward. In some embodiments of the present invention, the two-wheeled vehicle further includes a rear wheel (not shown in the figure), pedals (not shown in the figure), and a chain (not shown in the figure). One end of the chain is connected to the pedals, and the other end is connected to the sleeve 200. The freehub body 110 is provided with an installation portion 115 fixedly connected to the rim of the rear wheel (not shown in the figure). When the pedals are pedaled forward, the chain drives the sleeve 200 to rotate in the first direction. The sleeve 200 drives the bearing shell 320 to rotate in the same direction. The first pawl 321 of the bearing shell 320 engages with the first ratchet tooth 112. The bearing shell 320 drives the ratchet member 100 to rotate. At this time, the force on the sleeve 200 can be transmitted to the ratchet member 100 to drive the rear wheel to rotate forward. When the pedals are pedaled backward, the chain drives the sleeve 200 to rotate in the second direction. The sleeve 200 drives the bearing shell 320 to rotate in the same direction. The first pawl 321 at one end of the bearing shell 320 slides along the tooth surface of the first ratchet tooth 112 until the first pawl 321 disengages from the tooth surface of the first ratchet tooth 112. The sleeve 200 continues to rotate, and the other end of the bearing shell 320 abuts against the second ratchet tooth 121. At this time, the second ratchet tooth 121 can exert a reaction force on the bearing shell 320. This reaction force drives the bearing shell 320 to move toward the direction where the first ratchet tooth 112 is located. During the continuous rotation of the sleeve 200 in the second direction, the bearing shell 320 reciprocally slides between the first ratchet tooth 112 and the second ratchet tooth 121. The bearing shell 320 cannot drive the ratchet member 100 to rotate, and the force on the sleeve 200 is not transmitted to the ratchet member 100, so that the rear wheel is not driven to reverse. During this process, the one-way clutch does not need to use a spring, and the structure is reliable.

[0071] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those of ordinary skill in the art, various changes can be made without departing from the purpose of the present invention.

Claims

1. One-way clutch, characterized in that, Comprising: A ratchet member, including a base and an end cover. The base is provided with a rotating shaft and first ratchet teeth around the rotating shaft. The rotating shaft is fixedly connected to the end cover. The end cover is provided with second ratchet teeth facing the first ratchet teeth. Along the circumferential direction of the rotating shaft, the first ratchet teeth and the second ratchet teeth are arranged staggeredly. A sleeve, sleeved outside the rotating shaft. The sleeve is provided with a guiding groove, and the guiding groove is arranged along the axial direction of the sleeve. A slider, including a connected guiding block and a bearing bush. The inner wall of the bearing bush abuts against the rotating shaft and is located between the first ratchet teeth and the second ratchet teeth. One end of the bearing bush is provided with a first pawl, and the guiding block is located in the guiding groove and can slide along the axial direction of the sleeve. Wherein, when the sleeve rotates in the first direction, the first pawl can engage with the first ratchet teeth; when the sleeve rotates in the second direction, the bearing bush reciprocally slides between the first ratchet teeth and the second ratchet teeth to achieve disengagement.

2. The one-way clutch according to claim 1, wherein A second pawl for engaging the second ratchet teeth is provided at one end of the bearing bush away from the first pawl. The tooth profiles of the first ratchet teeth and the second ratchet teeth are the same and the number of teeth is equal.

3. The one-way clutch according to claim 2, wherein The number of teeth of the first ratchet teeth is set as N. Along the circumferential direction of the rotating shaft, the stagger angle between the first ratchet teeth and the second ratchet teeth is α, and α is equal to the value of 180° divided by N.

4. The one-way clutch according to claim 3, characterized in that, The inner wall surface of the bearing bush is an arc surface matching the outer wall of the rotating shaft. The central angle occupied by the bearing bush is β, and β is equal to the value of 180° divided by N.

5. The one-way clutch according to claim 1, wherein Along the axial direction of the rotating shaft, the maximum length of the bearing bush is equal to the minimum distance between the first ratchet teeth and the second ratchet teeth.

6. The one-way clutch according to claim 1, wherein Along the radial direction of the rotating shaft, the outer diameters of the first ratchet teeth and the second ratchet teeth are D, and the tooth thickness of the first ratchet teeth and the second ratchet teeth is d. d is greater than or equal to 0.05D and less than or equal to 0.1D.

7. The one-way clutch according to claim 6, characterized in that, Along the radial direction of the rotating shaft, the thickness of the bearing bush is equal to the tooth thickness of the first ratchet teeth.

8. The one-way clutch according to claim 1, wherein, An installation post is provided at the end of the rotating shaft. The installation post is aligned with the axis of the rotating shaft. The end cover is sleeved outside the installation post and fixed.

9. The one-way clutch according to claim 8, wherein, A pin hole is provided on the end face of the rotating shaft, and a pin shaft is provided on the end cover. The pin shaft is located in the pin hole to fix the end cover.

10. The one-way clutch according to claim 8, wherein, The one-way clutch further includes a thrust washer, and the thrust washer is fixedly connected to the installation post to axially limit the sleeve along the installation post.

11. The one-way clutch according to claim 1, characterized in that, A plurality of the guiding grooves are provided, and the plurality of guiding grooves are evenly arranged along the circumferential direction of the sleeve. A plurality of the sliders are provided, and the sliders correspond to the guiding grooves one by one.

12. Two-wheeler, characterized in that, Comprising the one-way clutch according to any one of claims 1 to 11.

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