CN222141837U - An overrunning clutch and an internal speed-changing hub - Google Patents

Abstract

The utility model belongs to the technical field of overrunning clutches, and particularly relates to an overrunning clutch and an internal speed hub. The application provides an overrunning clutch, comprising a first clutch assembly and a second clutch assembly, wherein the first clutch assembly is provided with a first ratchet, and the second clutch assembly is provided with a second ratchet, and when the rotation speed of the first clutch assembly is higher than that of the second clutch assembly, the first ratchet and the second ratchet engage, and when the rotation speed of the first clutch assembly is not higher than that of the second clutch assembly, the first ratchet and the second ratchet separate. The overrunning clutch adopts a ratchet structure, and a plurality of first ratchets and second ratchets transmit torque together, the engagement speed is extremely short, the response speed is fast, and the torque that can be carried is large. During sliding, the first ratchet and the second ratchet collide with each other to produce dense, crisp, and loud sounds.

Description

Overrunning clutch and internal speed-changing hub

Technical Field

The utility model belongs to the technical field of overrunning clutches, and particularly relates to an overrunning clutch and an inner speed-changing hub.

Background

The bicycle is a common commuter, a rider drives the bicycle to advance by stepping on the pedal, and when the bicycle is not stepped on, the bicycle depends on the self-freewheeling of the bicycle without the rotation of a sprocket, a chain and the pedal, and the function is realized by arranging a clutch in a hub of the bicycle.

Chinese patent document CN219256947U discloses a bicycle rear hub assembly, which adopts a mode that a tower base body is meshed with an inner tooth of a hub body in a unidirectional rotation manner through pawls, then the number of the pawls is small, a rider suddenly tramples and the torque response speed transferred to the hub is slow, and the noise in the sliding process is low.

Accordingly, the prior art is subject to improvement and development.

Disclosure of utility model

The application aims to provide an overrunning clutch and an internal variable speed hub, which have extremely short engagement speed, high response speed and large bearing torque. Can make dense, crisp and bright sounds during sliding.

In order to solve the technical problems, the overrunning clutch provided by the application comprises a first clutch component and a second clutch component, wherein the first clutch component is provided with a first ratchet, the second clutch component is provided with a second ratchet, the first ratchet is engaged with the second ratchet when the rotating speed of the first clutch component is higher than that of the second clutch component, and the first ratchet is separated from the second ratchet when the rotating speed of the first clutch component is not higher than that of the second clutch component.

Further, the first ratchet of the first clutch assembly is disposed opposite the second ratchet of the second clutch assembly.

Further, the second clutch assembly is linearly movable along an axial direction thereof to be away from or close to the first clutch assembly.

Further, a pretensioner is included that is coupled to and acts on the second clutch assembly to bias the first ratchet and the second ratchet toward engagement.

Further, the pretension piece is a compression spring, one end of the compression spring abuts against the fixed end, and the other end of the compression spring abuts against the first clutch assembly or the second clutch assembly.

Further, the pretension piece is a magnet assembly, the magnet assembly comprises a first magnet and a second magnet which are opposite in polarity, the second magnet is connected with the fixed end, and the first magnet is connected with the first clutch assembly or the second clutch assembly.

Further, the tooth shapes of the first ratchet and the second ratchet are triangular.

The application also provides an internal speed-changing hub, which comprises the overrun clutch, and comprises an input part for inputting torque, an output part for outputting torque and a transmission mechanism with at least two transmission ratios, wherein the input part is fixedly connected to the transmission mechanism, the overrun clutch is arranged between the transmission mechanism and the output part, the first clutch component is fixedly connected to the output part, the second clutch component is movably connected to the transmission mechanism, the overrun clutch is connected to transmit torque of the transmission mechanism to the output part when the rotating speed of the output part is not higher than that of the transmission mechanism, and the overrun clutch is separated to interrupt torque transmission when the rotating speed of the output part is higher than that of the transmission mechanism.

Further, the transmission mechanism is a planetary gear mechanism, the transmission mechanism comprises a gear ring, a planet carrier, a planetary gear and a sun gear, the first clutch assembly is fixedly connected to the output piece, the second clutch assembly is provided with a second connecting portion, the gear ring is provided with a first connecting portion, and the second connecting portion of the second clutch assembly is slidably connected with the first connecting portion of the gear ring.

Further, the first connecting portion has a split surface inclined to an axis of the ring gear, and torque of the ring gear is split to the second ratchet by the split surface to keep the first ratchet and the second ratchet engaged.

Further, a sound amplifying cavity is formed between the gear ring and the output piece.

From the above, the overrunning clutch adopts a ratchet structure, a plurality of first ratchets and second ratchets jointly transmit torque, the joint speed is extremely short, the response speed is high, and the torque which can be borne is large. The first ratchet and the second ratchet collide with each other to make dense, crisp and bright sounds during sliding.

Additional features and advantages of the application will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the application. The objectives and other advantages of the application will be realized and attained by the structure particularly pointed out in the written description and claims thereof as well as the appended drawings.

Drawings

Fig. 1 is a perspective view of the shift drum in example 1.

Fig. 2 is a longitudinal sectional view of the shift drum in example 1.

Fig. 3 is an exploded view of the shift drum in example 1.

Fig. 4 is a perspective view of the first clutch assembly of embodiment 1.

Fig. 5 is a perspective view of the second clutch assembly of embodiment 1.

Fig. 6 is a schematic structural view (engaged state) of the overrunning clutch of embodiment 1.

Fig. 7 is a schematic view of the structure of the overrunning clutch of embodiment 1 (disengaged state).

Fig. 8 is a schematic structural view (engaged state) of the overrunning clutch of example 2.

Fig. 9 is a schematic view of the structure of the overrunning clutch of embodiment 2 (disengaged state).

Fig. 10 is a perspective view of the ring gear of embodiment 3.

Fig. 11 is a top view of the ring gear of embodiment 3.

The reference numerals indicate 1-input member, 2-output member, 3-transmission mechanism, 31-gear ring, 311-first connection, 3111-break-down face, 4-overrunning clutch, 41-first clutch assembly, 411-first ratchet, 412-side wall, 42-second clutch assembly, 421-second ratchet, 422-second connection, 43-pretensioner, 431-compression spring, 432-magnet assembly, 4321-first magnet, 4322-second magnet, 5-amplifying chamber.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary only for explaining the present utility model and are not to be construed as limiting the present utility model.

In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more of the described features. In the description of the present utility model, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.

In the description of the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected, mechanically connected, electrically connected, or communicable with each other, directly connected, indirectly connected via an intermediary, or in communication between two elements or in an interaction relationship between two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present utility model, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.

The following disclosure provides many different embodiments, or examples, for implementing different features of the utility model. In order to simplify the present disclosure, components and arrangements of specific examples are described below. They are, of course, merely examples and are not intended to limit the utility model. Furthermore, the present utility model may repeat reference numerals and/or letters in the various examples, which are for the purpose of brevity and clarity, and which do not themselves indicate the relationship between the various embodiments and/or arrangements discussed. In addition, the present utility model provides examples of various specific processes and materials, but one of ordinary skill in the art will recognize the application of other processes and/or the use of other materials.

Example 1

Fig. 1 is a perspective view of an inner shift drum. Fig. 2 is a longitudinal sectional view of the inner shift drum. The inner shift drum comprises an input part 1 for inputting torque, an output part 2 for outputting torque and a transmission mechanism 3 with at least two transmission ratios, wherein the input part 1 is fixedly connected to the transmission mechanism 3. In this embodiment, the transmission mechanism 3 is a planetary gear mechanism, the transmission mechanism 3 includes a gear ring 31, a planet carrier, a planetary gear, and a sun gear, the input member 1 is fixedly connected to the planet carrier, and the transmission mechanism 3 of the inner shift hub can refer to the chinese patent document CN116353248a, which is not described herein.

In order that the rider can transfer power to the output member 2 when stepping on the bicycle, and the output member 2 does not rotate with a sprocket, a chain and a pedal when sliding, an overrunning clutch 4 is arranged between the transmission mechanism 3 and the output member 2.

Fig. 3 is an exploded view of the inner shift drum. The overrunning clutch 4 includes a first clutch assembly 41 and a second clutch assembly 42. Fig. 4 is a perspective view of the first clutch assembly 41. The first clutch assembly 41 is provided with a first ratchet 411, and the first clutch assembly 41 is further provided with a side wall 412, the side wall 412 being for fastening connection with the inner wall of the output member 2. Fig. 5 is a perspective view of the second clutch assembly 42. The second clutch assembly 42 is provided with a second ratchet 421, the first ratchet 411 of the first clutch assembly 41 is arranged opposite to the second ratchet 421 of the second clutch assembly 42 and has the same tooth shape, and the tooth shape of the first ratchet 411 is triangular, but the tooth shape of the second ratchet 421 faces opposite to the tooth shape of the second ratchet 421. Preferably, the tooth shapes of the first ratchet 411 and the second ratchet 421 may be right triangle shapes. The first ratchet 411 and the second ratchet 421 are engaged when the rotational speed of the first clutch assembly 41 is higher than the rotational speed of the second clutch assembly 42, and the first ratchet 411 and the second ratchet 421 are disengaged when the rotational speed of the first clutch assembly 41 is not higher than the rotational speed of the second clutch assembly 42.

In order to have a tendency for the first ratchet 411 and the second ratchet 421 to engage, a pretensioner 43 is also included, the pretensioner 43 being connected with the second clutch assembly 42 and acting on the second clutch assembly 42.

The pre-tightening member 43 may be a compression spring 431 or a magnet assembly 432, and in this embodiment, the pre-tightening member 43 is a compression spring 431, one end of the compression spring 431 abuts against the fixed end, and the other end of the compression spring 431 abuts against the first clutch assembly 41 or the second clutch assembly 42. The fixed end can be any part which does not axially move in the inner variable speed hub and can be the gear ring 31 of the transmission mechanism 3.

The first clutch assembly 41 is fixedly connected to the output member 2, the second clutch assembly 42 is movably connected to the transmission mechanism 3, as shown in fig. 5, a second connection portion 422 is disposed on an inner circumferential surface of the second clutch assembly 42, and correspondingly, a first connection portion 311 is disposed on the gear ring 31 of the transmission mechanism 3, and the second connection portion 422 of the second clutch assembly 42 is slidably connected to the first connection portion 311 of the gear ring 31. The first connection portion 311 may be a spline, the second connection portion 422 may be a spline groove, and the second clutch assembly 42 may be linearly movable along its axial direction to be away from or close to the first clutch assembly 41.

Fig. 6 is a schematic structural view (engaged state) of the overrunning clutch 4.

When the bicycle is pedaled, torque is input to the input member 1, torque is output by the gear ring 31 transmitted to the transmission mechanism 3, and because the gear ring 31 and the second clutch assembly 42 are in slip connection, the rotation speed is the same and the rotation speed is in the direction D2, at this time, the rotation speed of the output member 2 is not higher than the rotation speed of the transmission mechanism 3, i.e. the rotation speed of the output member 2 is zero, or the rotation speed is in the direction D1 but not higher than the rotation speed of the gear ring 31. The second clutch assembly 42 is engaged by the pretensioner 43, the first ratchet 411 of the first clutch assembly 41 and the second ratchet 421 of the second clutch assembly 42 are engaged, i.e. the overrunning clutch 4 is engaged, and after the overrunning clutch 4 is engaged, the rotational speed of the first clutch assembly 41 and the rotational speed of the second clutch assembly 42 are the same, so as to transmit the torque of the transmission mechanism 3 to the output member 2.

When the overrunning clutch 4 is engaged, the plurality of first ratchet teeth 411 and the plurality of second ratchet teeth 421 transmit torque together, the speed of engagement is extremely short, the response speed is high, and the torque that can be carried is large.

Fig. 7 is a schematic structural view (disengaged state) of the overrunning clutch 4.

When the bicycle is in sliding, the input member 1 has no torque input, the rotation speed of the gear ring 31 is zero, the output member 2 drives the first clutch assembly 41 to rotate along the direction D1, the tooth profile of the first ratchet 411 of the first clutch assembly 41 has an inclined surface, the second ratchet 421 of the second clutch assembly 42 can be pushed away against the elastic force of the compression spring 431 to separate the first ratchet 411 from the second ratchet 421, i.e. the overrunning clutch 4 is separated, the torque of the output member 2 is interrupted to be transmitted to the transmission mechanism 3 after the overrunning clutch 4 is separated, and the resistance of the bicycle is small in sliding.

The first ratchet 411 and the second ratchet 421 collide with each other to make a dense, crisp, shiny sound during the sliding.

In order to increase the rattle during coasting, a sound amplifying chamber 5 is formed between the ring gear 31 and the output member 2. A certain gap exists between the outer peripheral surface of the ring gear 31 and the inner peripheral surface of the output member 2, and the ring gear is flared from left to right as shown in fig. 2, so that rattling sounds generated by the collision of the first ratchet 411 and the second ratchet 421 can be increased.

Example 2

Fig. 8 is a schematic structural view (engaged state) of overrunning clutch 4 according to embodiment 2. Fig. 9 is a schematic structural view (disengaged state) of overrunning clutch 4 according to embodiment 2.

Unlike embodiment 1, the pretensioner 43 is a magnet assembly 432, the magnet assembly 432 includes a first magnet 4321 and a second magnet 4322 with opposite polarities, the second magnet 4322 is connected to the fixed end, and the first magnet 4321 is connected to the first clutch assembly 41 or the second clutch assembly 42. As shown in fig. 8 and 9, the opposite polarity means that the S pole of the first magnet 4321 is opposite to the S pole of the second magnet 4322, or the N pole of the first magnet 4321 is opposite to the N pole of the second magnet 4322, and the second magnet 4322 generates a repulsive force to the first magnet 4321 to act on the second clutch assembly 42 according to the distance that the like poles repel each other and the opposite poles attract each other. The operation principle of the overrunning clutch 4 using the magnet assembly 432 is identical to that of the compression spring 431, and will not be described again. Advantageously, the magnet assembly 432 is non-contact and does not suffer from wear degradation.

Example 3

Fig. 10 is a perspective view of a ring gear 31 of embodiment 3. Fig. 11 is a top view of a ring gear 31 of embodiment 3. After the overrun clutch 4 is engaged, in order to increase the engagement force and prevent the first ratchet 411 and the second ratchet 421 from being separated during riding and slipping, a disengagement surface 3111 is provided at the first connection portion 311, the disengagement surface 3111 is inclined to the axis of the ring gear 31, as shown in fig. 11, the inclination angle is α, and the torque of the ring gear 31 is disengaged to the second ratchet 421 through the disengagement surface 3111 to keep the first ratchet 411 and the second ratchet 421 engaged.

In the description of the present specification, reference to the terms "one embodiment," "certain embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

What has been described above is merely some embodiments of the present utility model. It will be apparent to those skilled in the art that several modifications and improvements can be made without departing from the inventive concept, and these are intended to be within the scope of the utility model.

Claims (11)

1. An overrunning clutch, characterized in that it comprises a first clutch assembly (41) and a second clutch assembly (42), wherein the first clutch assembly (41) is provided with a first ratchet tooth (411), and the second clutch assembly (42) is provided with a second ratchet tooth (421), when the rotation speed of the first clutch assembly (41) is higher than the rotation speed of the second clutch assembly (42), the first ratchet tooth (411) and the second ratchet tooth (421) are engaged, and when the rotation speed of the first clutch assembly (41) is not higher than the rotation speed of the second clutch assembly (42), the first ratchet tooth (411) and the second ratchet tooth (421) are separated. 2. The overrunning clutch according to claim 1, characterized in that the first ratchet teeth (411) of the first clutch assembly (41) and the second ratchet teeth (421) of the second clutch assembly (42) are arranged opposite to each other. 3. The overrunning clutch according to claim 1 is characterized in that the second clutch assembly (42) can move linearly along its axial direction to move away from or approach the first clutch assembly (41). 4. The overrunning clutch according to claim 1 is characterized in that it also includes a pre-tightening member (43), wherein the pre-tightening member (43) is connected to the second clutch assembly (42) and acts on the second clutch assembly (42) so that the first ratchet (411) and the second ratchet (421) have a tendency to engage. 5. The overrunning clutch according to claim 4 is characterized in that the preload member (43) is a compression spring (431), one end of the compression spring (431) is against a fixed end, and the other end of the compression spring (431) is against the first clutch assembly (41) or the second clutch assembly (42). 6. The overrunning clutch according to claim 4 is characterized in that the preload member (43) is a magnet assembly (432), the magnet assembly (432) includes a first magnet (4321) and a second magnet (4322) with opposite polarities, the second magnet (4322) is connected to a fixed end, and the first magnet (4321) is connected to the first clutch assembly (41) or the second clutch assembly (42). 7. The overrunning clutch according to claim 1, characterized in that the tooth shapes of the first ratchet tooth (411) and the second ratchet tooth (421) are triangular. 8. An internal speed hub, characterized in that it comprises an overrunning clutch (4) as described in any one of claims 1 to 7, comprising an input member (1) for inputting torque, an output member (2) for outputting torque, and a transmission mechanism (3) having at least two transmission ratios, wherein the input member (1) is fixedly connected to the transmission mechanism (3); the overrunning clutch (4) is arranged between the transmission mechanism (3) and the output member (2), the first clutch assembly (41) is fixedly connected to the output member (2), and the second clutch assembly (42) is movably connected to the transmission mechanism (3), when the rotation speed of the output member (2) is not higher than the rotation speed of the transmission mechanism (3), the overrunning clutch (4) is engaged to transmit the torque of the transmission mechanism (3) to the output member (2), and when the rotation speed of the output member (2) is higher than the rotation speed of the transmission mechanism (3), the overrunning clutch (4) is disengaged to interrupt the torque transmission. 9. The internal gear hub according to claim 8 is characterized in that the transmission mechanism (3) is a planetary gear mechanism, and the transmission mechanism (3) includes a ring gear (31), a planetary carrier, planetary gears, and a sun gear. The first clutch assembly (41) is fixedly connected to the output member (2), the second clutch assembly (42) is provided with a second connecting portion (422), the ring gear (31) is provided with a first connecting portion (311), and the second connecting portion (422) of the second clutch assembly (42) and the first connecting portion (311) of the ring gear (31) are slidingly connected. 10. The internal gear hub according to claim 9 is characterized in that the first connecting portion (311) has a decomposition surface (3111), the decomposition surface (3111) is inclined to the axis of the ring gear (31), and the torque of the ring gear (31) is decomposed to the second ratchet tooth (421) through the decomposition surface (3111) to keep the first ratchet tooth (411) and the second ratchet tooth (421) engaged. 11. The internal gear hub according to claim 9, characterized in that a sound amplification cavity (5) is formed between the ring gear (31) and the output member (2).