Clutch mechanism, transmission and bicycle

Abstract

The application discloses a kind of clutch mechanisms, and discloses the transmission with clutch mechanism and the bicycle with transmission, clutch mechanism includes sun gear and clutch wheel, first ratchet is provided on sun gear, and first engagement surface is provided on first ratchet;Second ratchet is provided on clutch wheel, and second engagement surface is provided on second ratchet;When first engagement surface is abutted on the second separation of second engagement surface, sun gear applies the separation action force along the axial direction of clutch wheel away from sun gear to clutch wheel, or when second engagement surface is abutted on the first separation of first engagement surface, sun gear applies the separation action force along the axial direction of clutch wheel away from sun gear to clutch wheel, can easily drive clutch wheel to move in the direction away from sun gear, reduce the transmission resistance of clutch mechanism, transmission and bicycle.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of bicycles, in particular to a clutch mechanism, a derailleur and a bicycle. BACKGROUND

[0002] The internal derailleur is also called derailleur, which is used for gear shifting of bicycles. For example, the patent with the publication number CN116001967 and the title of gear shifting trigger mechanism of derailleur, and the patent with the publication number CN116161161 and the title of internal two-way derailleur and gear shifting control method. When the derailleur is shifting, the gear shifting lever is driven to rotate, and the gear shifting lever drives the separation or combination of each clutch mechanism. Different combinations of clutch mechanisms achieve different gear positions. At present, a pair of end face ratchet gears are arranged on the clutch wheel and the sun wheel, and the end face ratchet gears generate a component force in the axial direction when meshing and transmitting. This component force provides an axial combination force of the clutch wheel towards the sun wheel to prevent the clutch wheel from automatically separating from the sun wheel when normally transmitting the sun wheel, thereby ensuring the stability of the torque transmission between the sun wheel and the clutch wheel. However, when the clutch wheel and the sun wheel need to be normally separated, the clutch wheel needs to overcome not only the above-mentioned axial combination force, but also the static friction force exerted by the sun wheel, which will cause the gear shifting lever to be subjected to a certain gear shifting resistance when the gear shifting lever is rotating. Especially during the process of pedaling the bicycle pedals, the pressure between the clutch wheel and the sun wheel is large, which increases the axial combination force and the static friction force, resulting in a large gear shifting resistance, and the sun wheel and the clutch wheel cannot be separated or separated smoothly, thereby the gear shifting lever cannot be driven to rotate, and the pedals need to be stopped to continue gear shifting, which reduces the smoothness of gear shifting and the riding experience. SUMMARY

[0003] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application provides a clutch mechanism which can be easily separated and reduces the gear shifting resistance of the derailleur.

[0004] The present application also provides a derailleur with the above-mentioned clutch mechanism.

[0005] The present application also provides a bicycle with the above-mentioned derailleur.

[0006] In a first aspect, embodiments of the present application provide a clutching mechanism, comprising a sun gear and a clutch gear, the sun gear is provided with a first end face ratchet gear, the first end face ratchet gear has a plurality of first ratchets, and each first ratchet is provided with a first engagement surface; the clutch gear is provided with a second end face ratchet gear, the second end face ratchet gear has a plurality of second ratchets, and each second ratchet is provided with a second engagement surface for cooperating with the first engagement surface; the first engagement surface is sequentially provided with a first separation portion, a first turning portion and a first inclined surface portion along a direction from a root of the first ratchet to a top of the first ratchet, the first separation portion gradually extends along an opposite direction of rotation of the clutch gear from the first turning portion to the root of the first ratchet, and the first inclined surface portion gradually extends along the direction of rotation of the clutch gear from the top of the first ratchet to the first turning portion; when the second engagement surface abuts against the first separation portion, the sun gear applies a separation force to the clutch gear along an axial direction of the clutch gear away from the sun gear; when the second engagement surface abuts against the first inclined surface portion, the sun gear applies a combination force to the clutch gear along the axial direction of the clutch gear close to the sun gear; or, the second engagement surface is sequentially provided with a second separation portion, a second turning portion and a second inclined surface portion along a direction from a root of the second ratchet to a top of the second ratchet, the second separation portion gradually extends along the direction of rotation of the clutch gear from the second turning portion to the root of the second ratchet, and the second inclined surface portion gradually extends along the opposite direction of rotation of the clutch gear from the top of the second ratchet to the second turning portion; when the first engagement surface abuts against the second separation portion, the sun gear applies a separation force to the clutch gear along the axial direction of the clutch gear away from the sun gear; and when the first engagement surface abuts against the second inclined surface portion, the sun gear applies a combination force to the clutch gear along the axial direction of the clutch gear close to the sun gear.

[0007] At least has the following beneficial effects: when the second engagement surface abuts against the first separation portion, the sun gear applies a separation force to the clutch gear along an axial direction of the clutch gear away from the sun gear, or when the first engagement surface abuts against the second separation portion, the sun gear applies a separation force to the clutch gear along the axial direction of the clutch gear away from the sun gear. Due to the existence of the separation force, the shift lever only needs to apply a smaller driving force to the clutch gear to drive the clutch gear to move away from the sun gear. Compared with the prior art, the driving force applied by the shift lever to the clutch gear is much smaller than the driving force of the prior art, which can more easily realize gear shifting and operation of the transmission, improve the smoothness of the transmission, and improve the riding experience of the bicycle.

[0008] According to some embodiments of the present application, an included angle between a tangent direction T1 of the first separation portion and an axial direction of the sun gear is an included angle α, and the included angle α is less than 60°.

[0009] According to some embodiments of the present invention, the angle between the tangential direction T2 of the second separation part and the axial direction of the clutch wheel is an angle β, and the angle β is less than 60°.

[0010] Secondly, embodiments of the present invention also provide a transmission, including a main shaft, a clutch mechanism as described in the above embodiments, a planetary gear train, a shift lever, and a pin. A receiving groove is formed on the left end face of the main shaft, and a clearance hole communicating with the receiving groove is formed on the side wall of the main shaft. The length direction of the clearance hole is parallel to the length direction of the main shaft. The sun gear is sleeved on the main shaft, and the clutch gear is sleeved on the main shaft. The planetary gear train includes at least two sun gears, each sleeved on the main shaft. The right end of the shift lever passes through the receiving groove, and the… The shift lever is coaxially arranged with the main shaft. The left end of the shift lever is used to connect with the shift drive mechanism, which is used to drive the shift lever to rotate. A groove is provided on the outer circumferential surface of the shift lever. One end of the pin is located in the groove, which is used to drive the pin to move along the length direction of the main shaft. The other end of the pin extends to the outside of the main shaft through the clearance hole. The other end of the pin is configured to drive the clutch wheel to move on the main shaft so that the first ratchet and the second ratchet engage or disengage with each other.

[0011] It has at least the following beneficial effects: The shift lever is driven to rotate by the shift drive mechanism, which in turn drives the slide groove to rotate. The clearance hole limits the movement of the pin along the length of the main shaft. The rotating slide groove drives the pin to move along the length of the main shaft, and the pin drives the clutch wheel to move on the main shaft, thereby driving the clutch wheel away from or towards the sun gear. In other words, it causes the clutch mechanism formed by the clutch wheel and the sun gear to separate or engage. When the clutch wheel is away from the sun gear, the sun gear exerts a separation force that drives the clutch wheel away from the sun gear, so that a smaller force applied by the shift lever to the pin can also drive the clutch wheel away from the sun gear. This greatly reduces the shift resistance experienced by the shift lever, making gear shifting of the transmission easy.

[0012] According to some embodiments of the present invention, the slide has two opposing inner surfaces in the length direction of the shift lever, one inner surface being used to drive the pin to move in the positive direction along the length direction of the main shaft, and the other inner surface being used to drive the pin to move in the opposite direction along the length direction of the main shaft.

[0013] According to some embodiments of the present invention, a separator ring is provided between two adjacent sun gears.

[0014] According to some embodiments of the present application, a limiting ring is further arranged on the inner wall of the accommodating groove, the limiting ring is movably sleeved on the gear shifting lever, a plurality of gear shifting grooves are arranged in a ring shape on the limiting ring, a gear shifting positioning member is arranged on the gear shifting lever, and the gear shifting positioning member can extend into different gear shifting grooves to position the gear shifting lever in different gear shifting states.

[0015] According to some embodiments of the present application, a guide groove is arranged on the gear shifting lever, the gear shifting positioning member is arranged in the guide groove in a sliding manner, an elastic member is arranged in the guide groove, the gear shifting positioning member abuts against the elastic member, and the elastic member is used to drive the gear shifting positioning member to move in the direction of the slot opening of the guide groove, so that the gear shifting positioning member extends into the gear shifting groove.

[0016] According to some embodiments of the present application, the inner groove wall of the gear shifting groove is arc-shaped, and the gear shifting positioning member is a steel ball which can slide on the inner groove wall of the gear shifting groove.

[0017] According to some embodiments of the present application, a limiting convex stopper is arranged on the limiting ring, and a convex block is arranged on the gear shifting lever, the convex block abuts against the limiting convex stopper to limit the rotation range of the gear shifting lever.

[0018] According to some embodiments of the present application, the inner wall of the accommodating groove is provided with a positioning groove, and the outer circular surface of the limiting ring is provided with a convex, which can extend into the positioning groove to prevent the limiting ring from rotating with the gear shifting lever.

[0019] In a third aspect, the embodiments of the present application further provide a bicycle, comprising a frame, a rear wheel and the above-mentioned gear shifter, the frame is in driving connection with the rear wheel through the gear shifter.

[0020] At least has the following beneficial effects: the gear shifting resistance of the gear shifter is small, so that the force required for the gear shifting operation of the bicycle is small, the smoothness of the gear shifting operation of the bicycle is improved, and the riding experience of the bicycle is also improved.

[0021] Additional aspects and advantages of the present application will be made apparent from the following description, which is given merely by way of non-limiting example, in which reference will be made to the attached drawings and in which: BRIEF DESCRIPTION OF DRAWINGS

[0022] The present application will be further described below in conjunction with the drawings and embodiments, in which:

[0023] Figure 1 is a sectional view of the structure of the embodiment of the present application;

[0024] Figure 2 is a structure schematic view of the main shaft, the sun gear and the clutch wheel of the embodiment of the present application;

[0025] Figure 3 Fig. 6 is a schematic view of a partial cross-sectional structure of a sun gear and a clutch gear according to an embodiment of the present application;

[0026] Figure 4 Fig. 7 is a schematic view of a partial cross-sectional structure of a clutch gear according to an embodiment of the present application;

[0027] Figure 5 Fig. 8 is a schematic view of a partial cross-sectional structure of a sun gear and a clutch gear according to another embodiment of the present application;

[0028] Figure 6 Fig. 9 is a schematic view of a partial cross-sectional structure of a clutch gear according to another embodiment of the present application;

[0029] Figure 7 Fig. 10 is a schematic view of a structure of a shift lever, a detent ring, a gear position positioning member, a resilient member, and a pin according to an embodiment of the present application;

[0030] Figure 8 Fig. 11 is a schematic view of a structure of a shift lever, a detent ring, a gear position positioning member, a resilient member, and a pin according to another embodiment of the present application;

[0031] Figure 9 Fig. 12 is a schematic view of a structure of a detent ring according to an embodiment of the present application;

[0032] Reference Signs List:

[0033] Main shaft 100, receiving groove 110, escape hole 120, bearing 130;

[0034] Sun gear 200, first ratchet 210, first engagement surface 211, first separation portion 2111, first inclined surface portion 2112;

[0035] Clutch gear 300, second ratchet 310, second engagement surface 311, second separation portion 3111, second inclined surface portion 3112;

[0036] Shift lever 400, sliding groove 410, protrusion 420, input gear 430, gear position positioning member 440, resilient member 450;

[0037] Pin 500;

[0038] Partition ring 600;

[0039] Detent ring 700, gear position groove 710, limit protrusion 720, protrusion 730. DETAILED DESCRIPTION

[0040] In the description of the present application, it should be understood that the orientation description, such as the orientation or position relationship indicated by up, down, front, back, left, right and the like, is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and cannot be understood as indicating or implying that the device or element indicated must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present application.

[0041] In the description of the present application, if the first, second, etc. are described, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying the relative importance of the technical features or implicitly indicating the number of technical features indicated or the order of the technical features indicated.

[0042] In the description of the present application, unless otherwise explicitly limited, the words such as arrangement, installation, connection and the like should be broadly understood, and the person skilled in the art can reasonably determine the specific meaning of the above words in the present application in combination with the specific content of the technical solution.

[0043] Referring to Figures 1 to 4 The present application discloses a kind of clutch mechanism, including sun gear 200 and clutch wheel 300, the end surface of sun gear 200 is equipped with first end surface ratchet gear, first end surface ratchet gear includes multiple first ratchet teeth 210, multiple first ratchet teeth 210 are distributed around the axis of sun gear 200, and first ratchet tooth 210 is equipped with first engagement surface 211;The end surface of clutch wheel 300 is equipped with second end surface ratchet gear, and second end surface ratchet gear includes multiple second ratchet teeth 310, multiple second ratchet teeth 310 are distributed around the axis of clutch wheel 300, and second ratchet tooth 310 is equipped with second engagement surface 311 for cooperating with first engagement surface 211.

[0044] Referring to Figure 3 And Figure 4 First engagement surface 211 is sequentially equipped with first separation part 2111, first turning part and first inclined surface part 2112 along the direction from the root of first ratchet tooth 210 to the top of first ratchet tooth 210, first separation part 2111 gradually extends along the reverse direction of rotation of clutch wheel 300 (the direction of arrow V in Fig. Figure 5 And Figure 6 ) from first turning part to the root of first ratchet tooth 210, and first inclined surface part 2112 gradually extends along the direction of rotation of clutch wheel 300 (the direction of arrow V in Fig. Figure 5 And Figure 6 ) from the top of first ratchet tooth 210 to first turning part, when second engagement surface 311 abuts on first separation part 2111, sun gear 200 applies separation action force to clutch wheel 300 along the axial direction of clutch wheel 300 away from sun gear 200, when second engagement surface 311 abuts on first inclined surface part 2112, sun gear 200 applies joint action force to clutch wheel 300 along the axial direction of clutch wheel 300 close to sun gear 200.

[0045] Alternatively, referring to Figure 5 and Figure 6 , the second engagement surface 311 is provided with a second separation portion 3111, a second transition portion and a second inclined surface portion 3112 in order from the root of the second ratchet tooth 310 to the top of the second ratchet tooth 310, the second separation portion 3111 gradually extends from the second transition portion to the root of the second ratchet tooth 310 along the rotation direction of the clutch wheel 300 (the direction of the arrow V in Figure 5 and Figure 6 ), the second inclined surface portion 3112 gradually extends from the top of the second ratchet tooth 310 to the second transition portion along the reverse rotation direction of the clutch wheel 300 (the reverse direction of the arrow V in Figure 5 and Figure 6 ), when the first engagement surface 211 abuts against the second separation portion 3111, the sun gear 200 applies a separation force to the clutch wheel 300 along the axial direction of the clutch wheel 300 away from the sun gear 200, when the first engagement surface 211 abuts against the second inclined surface portion 3112, the sun gear 200 applies a coupling force to the clutch wheel 300 along the axial direction of the clutch wheel 300 close to the sun gear 200.

[0046] Referring to Figure 4 , the first separation portion 2111 is a curved surface, the first inclined surface portion 2112 is a flat surface at an angle to the axial direction of the sun gear 200, and the first transition portion is a region between the first separation portion 2111 and the first inclined surface portion 2112. The first separation portion 2111 can be concave towards the rotation direction of the sun gear 200 or convex towards the reverse rotation direction of the sun gear 200. Referring to Figure 6 , the second separation portion 3111 is a curved surface, the second inclined surface portion 3112 is a flat surface at an angle to the axial direction of the clutch wheel 300, and the second transition portion is a region between the second separation portion 3111 and the second inclined surface portion 3112. The second separation portion 3111 can be concave towards the reverse rotation direction of the clutch wheel 300 or convex towards the rotation direction of the clutch wheel 300.

[0047] Firstly, it needs to be understood that the rotation directions of the clutch wheel 300 and the sun gear 200 are the same, and the gear shifting process of the transmission needs to change the clutch mechanism formed by the clutch wheel 300 and the sun gear 200 from the coupled state to the separated state or change the clutch mechanism formed by the clutch wheel 300 and the sun gear 200 from the separated state to the coupled state, that is, the plurality of first ratchet teeth 210 and the plurality of second ratchet teeth 310 are separated or engaged. The relatively large gear shifting resistance of the transmission mainly refers to the relatively large resistance required to separate the clutch wheel 300 from the sun gear 200, that is, the relatively large gear shifting resistance when the clutch mechanism formed by the clutch wheel 300 and the sun gear 200 changes from the coupled state to the separated state.

[0048] The shift driving mechanism drives the clutch wheel 300 to approach the sun gear 200 through the shift lever 400, and the plurality of first ratchets 210 and the plurality of second ratchets 310 are engaged with each other, at this time, the clutch wheel 300 is subjected to a smaller shift resistance; when the plurality of first ratchets 210 and the plurality of second ratchets 310 are separated, because the plurality of first ratchets 210 and the plurality of second ratchets 310 are in the engaged state, the clutch wheel 300 and the sun gear 200 change from the relatively static state to the relatively moving state, the static friction between the first ratchets 210 and the second ratchets 310 changes to the dynamic friction, the friction resistance of the static friction is much larger than that of the dynamic friction, so a larger force needs to be applied to the clutch wheel 300 by the shift lever 400 to make the clutch wheel 300 start to separate from the sun gear 200, that is, the shift lever 400 is subjected to a larger shift resistance, and the shift resistance of the transmission is also larger.

[0049] With reference to Figure 3 and Figure 4 , when the clutch wheel 300 and the sun gear 200 are engaged with each other, the area on the second engagement surface 311 close to the tooth top of the second ratchet 310 abuts against the first separation part 2111, and the sun gear 200 applies a separation action force to the clutch wheel 300 along the axial direction of the clutch wheel 300 away from the sun gear 200. As Figure 4 indicated by the force F1, F1 is the normal pressure applied by the first separation part 2111 to the second engagement surface 311, that is, the normal pressure applied to the second engagement surface 311, the direction of F1 is perpendicular to the tangent of the first separation part 2111 along the direction T1 from the clutch wheel 300 to the sun gear 200, the direction of F1 deviates to one side of the clutch wheel 300, and the separation action force F applied to the clutch wheel 300 is equal to the component of F1 in the axial direction of the clutch wheel 300 minus the component of the static friction force applied to the clutch wheel 300 in the axial direction of the clutch wheel 300. When the shift lever 400 starts to drive the clutch wheel 300 to move away from the sun gear 200, because of the existence of the separation action force F, the shift lever 400 only needs to apply a smaller driving force to the clutch wheel 300 to drive the clutch wheel 300 to move away from the sun gear 200, so that the area on the second engagement surface 311 close to the tooth top of the second ratchet 310 slides from the first separation part 2111 to the first inclined surface part 2112, and then slides from the first inclined surface part 2112 to the outside of the first engagement surface 211, and the clutch wheel 300 is separated from the sun gear 200. Compared with the prior art, the driving force applied by the shift lever 400 to the clutch wheel 300 is much smaller than the driving force of the prior art, which can more easily realize the gear shifting and operate the transmission, improve the smoothness of the transmission and improve the riding experience of the bicycle.

[0050] When the area on the second engagement surface 311 close to the tooth top of the second ratchet tooth 310 is in abutment with the first inclined surface portion 2112, the sun gear 200 applies a joining force to the clutch gear 300 along the axial direction of the clutch gear 300 close to the sun gear 200, which is conducive to keeping the sun gear 200 and the clutch gear 300 joined together and avoiding the clutch gear 300 from automatically disengaging from the sun gear 200, however, this does not hinder the clutch gear 300 from smoothly disengaging from the sun gear 200, because when the clutch gear 300 moves against the static friction, the clutch gear 300 can smoothly disengage from the sun gear 200 by using its own inertia and the driving of the shift lever 400.

[0051] In this embodiment, the second engagement surface 311 is a plane, and the second engagement surface 311 is parallel to the first inclined surface portion 2112, so that the area on the second engagement surface 311 close to the tooth top of the second ratchet tooth 310 can smoothly slide through the first separation portion 2111 and the first inclined surface portion 2112 in turn, and the area on the second engagement surface 311 far from the sun gear 200 (the area on the second engagement surface 311 close to the tooth root of the second ratchet tooth 310) does not cause interference to the first engagement surface 211. The area on the second engagement surface 311 close to the tooth top of the second ratchet tooth 310 is provided with a chamfer and / or a fillet.

[0052] In another embodiment, referring to Figure 5 and Figure 6 When the clutch gear 300 and the sun gear 200 are in engagement with each other, the area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 is in abutment with the second separation portion 3111, and the sun gear 200 applies a separation force to the clutch gear 300 along the axial direction of the clutch gear 300 away from the sun gear 200. As Figure 6The indicated force F2 is a normal force received by the second separation portion 3111, the direction of F2 is perpendicular to the tangent of the second separation portion 3111 along the direction T2 from the sun gear 200 to the clutch gear 300, the direction of F2 is biased to the side of the clutch gear 300, the separation force F received by the clutch gear 300 is equal to the component of F2 in the axial direction of the clutch gear 300 minus the component of the static friction force received by the clutch gear 300 in the axial direction of the clutch gear 300. When the shift lever 400 starts to drive the clutch gear 300 to move away from the sun gear 200, due to the existence of the separation force F, the shift lever 400 only needs to apply a small driving force to the clutch gear 300 to drive the clutch gear 300 to move away from the sun gear 200, so that the area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 slides from the second separation portion 3111 to the second inclined surface portion 3112, and then the area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 slides from the second inclined surface portion 3112 to the outside of the first engagement surface 211, and the clutch gear 300 is completely separated from the sun gear 200. Compared with the prior art, the driving force applied by the shift lever 400 to the clutch gear 300 is much smaller than the driving force of the prior art, which can more easily realize gear shifting and operate the transmission, improve the smoothness of the transmission and improve the riding experience of the bicycle.

[0053] When the area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 is in abutment with the second inclined surface portion 3112, the sun gear 200 applies a joining force to the clutch gear 300 along the axial direction of the clutch gear 300 close to the sun gear 200, which is beneficial to keep the sun gear 200 and the clutch gear 300 joined together and avoid the clutch gear 300 from automatically separating from the sun gear 200, however, this will not hinder the clutch gear 300 from smoothly separating from the sun gear 200, because when the clutch gear 300 moves against the static friction force, the clutch gear 300 can use its own inertia and the driving of the shift lever 400 to smoothly separate from the sun gear 200.

[0054] The first engagement surface 211 is a plane, the first engagement surface 211 is parallel to the second inclined surface portion 3112, so that the area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 can smoothly slide through the second separation portion 3111 and the second inclined surface portion 3112 in turn, and the area on the first engagement surface 211 away from the clutch gear 300 (the area on the first engagement surface 211 close to the tooth root of the first ratchet tooth 210) will not interfere with the second inclined surface portion 3112. The area on the first engagement surface 211 close to the tooth top of the first ratchet tooth 210 is provided with a chamfer and / or a rounding.

[0055] It should be noted that the clutch wheel 300 is also limited by the spring in the transmission, so that the clutch wheel 300 and the sun gear 200 are kept engaged, thereby avoiding the clutch wheel 300 and the sun gear 200 from being separated automatically. The separation force applied by the sun gear 200 to the clutch wheel 300 cannot make the clutch wheel 300 automatically disengage from the sun gear 200, thereby avoiding the automatic separation of the clutch mechanism during operation, and the axial movement of the clutch wheel 300 is ultimately controlled by the shift lever 400.

[0056] With reference to Figure 4 In some embodiments, the angle between the tangent direction T1 of the first separation portion 2111 and the axial direction of the sun gear 200 is an angle α, and the angle α is less than 60°.

[0057] F1 is the normal pressure applied by the first separation portion 2111 to the second engagement surface 311, f is the friction coefficient, and the friction coefficient f is taken as 0.5. When the angle α is 45°, the separation force F of the open clutch mechanism is F=F1×sinα-F1×f×cosα=0.355F1, that is, in the state that the clutch wheel 300 and the sun gear 200 are engaged, the separation force received by the clutch wheel 300 is 0.355 times the normal pressure, which helps the clutch wheel 300 to overcome the static friction and move away from the sun gear 200. It should be noted that the angle α cannot be too large, otherwise the separation force will be too large, and the sun gear 200 and the clutch wheel 300 cannot be kept together. The angle α cannot be too small, otherwise the separation force will be too small, and the help to the clutch wheel 300 to overcome the static friction and move away from the sun gear 200 will be too small.

[0058] It is conceivable that the first inclined surface portion 2112 can also be a curved surface with the same structure as the first separation portion 2111, and the angle α can be greater than 10°. In another embodiment, the angle between the tangent direction T1 of the first separation portion 2111 and the axial direction of the sun gear 200 gradually decreases from the clutch wheel 300 to the sun gear 200.

[0059] Similarly, with reference to Figure 6 In some embodiments, the angle between the tangent direction T2 of the second separation portion 3111 and the axial direction of the clutch wheel 300 is an angle β, and the angle β is less than 60°.

[0060] It is conceivable that the second inclined surface portion 3112 can also be a curved surface with the same structure as the second separation portion 3111, and the angle β can be greater than 10°. In another embodiment, the angle between the tangent direction T2 of the second separation portion 3111 and the axial direction of the clutch wheel 300.

[0061] With reference to Figure 1 and Figure 2The application further discloses a transmission, which comprises a main shaft 100, the clutching mechanism, a planetary gear train, a shift lever 400 and a pin shaft 500, the left end surface of the main shaft 100 is provided with a receiving groove 110, the side wall of the main shaft 100 is provided with an avoiding hole 120 which is in communication with the receiving groove 110, and the length direction of the avoiding hole 120 is parallel to the length direction of the main shaft 100; the sun gear 200 is sleeved on the main shaft 100, and the clutching wheel 300 is sleeved on the main shaft 100; the planetary gear train comprises at least two sun gears 200 which are all sleeved on the main shaft 100; the right end of the shift lever 400 is arranged in the receiving groove 110, and the shift lever 400 is coaxially arranged on the main shaft 100; the left end of the shift lever 400 is used for being in transmission connection with a shift driving mechanism; the shift driving mechanism is used for driving the shift lever 400 to rotate; and the outer circular surface of the shift lever 400 is provided with a sliding groove 410; one end of the pin shaft 500 is arranged in the sliding groove 410, the sliding groove 410 is used for driving the pin shaft 500 to move along the length direction of the main shaft 100, the other end of the pin shaft 500 extends to the outside of the main shaft 100 through the avoiding hole 120, and the other end of the pin shaft 500 is configured to drive the clutching wheel 300 to move on the main shaft 100, so that the first ratchet 210 and the second ratchet 310 are in meshing or separated from each other.

[0062] The length direction of the main shaft 100 is the left-right direction. During the shift process, the shift driving mechanism drives the shift lever 400 to rotate, the shift lever 400 drives the sliding groove 410 to rotate, the avoiding hole 120 plays a role in limiting the pin shaft 500 to move along the length direction of the main shaft 100, the inner side wall of the rotating sliding groove 410 drives the pin shaft 500 to move along the length direction of the main shaft 100, and the pin shaft 500 drives the clutching wheel 300 to move on the main shaft 100, so that the clutching wheel 300 is driven to move away from or close to the sun gear 200, that is, the clutching mechanism formed by the clutching wheel 300 and the sun gear 200 is separated or combined. When the clutching wheel 300 moves away from the sun gear 200, since the sun gear 200 applies a separating force to drive the clutching wheel 300 to move away from the sun gear 200, the shift lever 400 applies a smaller force to the pin shaft 500, and the clutching wheel 300 can also be driven to move away from the sun gear 200, that is, the shift resistance of the shift lever 400 is greatly reduced, and the shift driving mechanism can drive the shift lever 400 to rotate by applying a smaller force, so that the shift of the transmission can be easily realized.

[0063] Reference Figure 1 It can be understood that the shift lever 400 is installed in the receiving groove 110 of the main shaft 100 through a plurality of bearings 130, the rotating friction resistance of the shift lever 400 is reduced, and the bearings 130 ensure the stability of the rotation of the shift lever 400. In the embodiment, the number of the bearings 130 is two, and the two bearings 130 are respectively connected with the groove bottom of the receiving groove 110 and the groove opening of the receiving groove 110.

[0064] The left end of the shift lever 400 is provided with an input gear 430, and the shift lever 400 is in transmission connection with the shift driving mechanism through the input gear 430. The shift driving mechanism can be a manual cable type driving mechanism or a motor driven type driving mechanism, which is not limited further herein.

[0065] With reference to Figure 7 and Figure 8 In some embodiments, the chute 410 has two opposite inner sides in the length direction of the shift lever 400, one of which is used to drive the pin shaft 500 to move in the positive direction of the length direction of the main shaft 100, and the other of which is used to drive the pin shaft 500 to move in the reverse direction of the length direction of the main shaft 100. The chute 410 can drive the pin shaft 500 to move in the length direction of the main shaft 100 in the positive and reverse directions, and can reset the pin shaft 500 and the clutch wheel 300 in time.

[0066] The chute 410 can be milled directly on the outer circular surface of the shift lever 400 by a milling cutter, which has a relatively simple structure and is easy to process.

[0067] With reference to Figure 2 It can be understood that the planetary gear train includes a plurality of sun gears 200, and there is friction between adjacent two sun gears 200, so that friction interference is generated between the adjacent two sun gears 200.

[0068] In some embodiments, a separation ring 600 is arranged between adjacent two sun gears 200, and the separation ring 600 separates the adjacent two sun gears 200, which can reduce the friction resistance suffered by the sun gear 200 when rotating.

[0069] It can be understood that the separation ring 600 is annular, and the separation ring 600 is sleeved on the main shaft 100. The two sides of the separation ring 600 are relatively smooth, so that the friction between the separation ring 600 and the sun gear 200 is very small.

[0070] With reference to Figure 1 , Figures 7 to 9In some embodiments, the transmission further comprises a fixed gear ring 700 connected to the inner wall of the receiving groove 110, the fixed gear ring 700 movably sleeving the gear shift lever 400 and not rotating with the gear shift lever 400, the fixed gear ring 700 having a plurality of gear slots 710 annularly distributed thereon, the number of gear slots 710 being equal to the number of gears of the transmission. The gear shift lever 400 is provided with a gear position positioning member 440, which can extend into different gear slots 710. When the gear position positioning member 440 extends into the gear slot 710, the gear slot 710 limits the rotation of the gear position positioning member 440 around the central axis of the gear shift lever 400, so that the gear position positioning member 440 limits the rotation of the gear shift lever 400, thereby positioning the gear shift lever 400 at different gear positions, avoiding accidental gear shifting of the transmission caused by accidental rotation of the gear shift lever 400. When the gear shift lever 400 is driven by the gear shifting driving mechanism, the gear shift lever 400 is forcibly driven, and the gear position positioning member 440 will exit the gear slot 710.

[0071] In some embodiments, the inner wall of the receiving groove 110 is provided with a positioning groove, and the outer circular surface of the fixed gear ring 700 is provided with a protrusion 730 protruding from the outer circumferential surface of the fixed gear ring 700. When the fixed gear ring 700 is installed into the receiving groove 110, the protrusion 730 extends into the positioning groove. The cooperation between the positioning groove and the protrusion 730 limits the rotation of the fixed gear ring 700, preventing the fixed gear ring 700 from rotating with the gear shift lever 400, and preventing the gear shift lever 400 from rotating with the fixed gear ring 700.

[0072] Referring to Figure 7 In some embodiments, the gear shift lever 400 is provided with a guide groove, and the gear position positioning member 440 is slidably arranged in the guide groove. The guide groove serves to guide the gear position positioning member 440, and when the gear shift lever 400 rotates, the gear shift lever 400 drives the gear position positioning member 440 to rotate through the inner wall of the guide groove. Specifically, the guide direction of the guide groove is parallel to the length direction of the gear shift lever 400.

[0073] The guide groove is provided with an elastic member 450, and the gear position positioning member 440 abuts against the elastic member 450. The elastic member 450 is used to drive the gear position positioning member 440 to move towards the slot opening of the guide groove, so that the gear position positioning member 440 extends into the gear slot 710. When the gear shift lever 400 rotates with the gear position positioning member 440, the inner groove wall of the gear slot 710 drives the gear position positioning member 440 to move towards the guide groove, and the elastic member 450 is compressed until the gear position positioning member 440 completely exits the gear slot 710. At this time, the gear shift lever 400 can drive the gear position positioning member 440 to rotate to a position directly opposite another gear slot 710, so that the gear position positioning member 440 extends into another gear slot 710. At this time, the gear shift lever 400 rotates to a position where another gear is located, and the transmission realizes gear shifting.

[0074] Referring to Figure 9In some embodiments, the inner groove wall of the gear slot 710 is arc-shaped, so that the inner groove wall of the gear slot 710 can force the gear positioning member 440 to exit the gear slot 710.

[0075] It should be noted that the depth or length or guiding direction of the guide groove is parallel to the axial direction of the main shaft 100 / shift lever 400, the plurality of gear slots 710 are arranged on the end surface of the blocking ring 700, and the plurality of gear slots 710 are distributed around the central axis of the blocking ring 700. The depth direction of the gear slot 710 is parallel to the axial direction of the main shaft 100 / shift lever 400. Of course, the depth or length or guiding direction of the guide groove can be arranged to be parallel to the radial direction of the main shaft 100 / shift lever 400, and the plurality of gear slots 710 are arranged on the inner circular surface of the blocking ring 700.

[0076] Referring to Figures 7 to 9 The gear positioning member 440 is a steel ball, which has an arc surface that cooperates with the inner groove wall of the gear slot 710. The steel ball can slide on the inner groove wall of the gear slot 710, which is more conducive to the inner groove wall of the gear slot 710 forcing the gear positioning member 440 to exit the gear slot 710. Of course, the gear positioning member 440 can also be cylindrical, and one end of the gear positioning member 440 has a spherical surface that cooperates with the gear slot 710, which is also conducive to the inner groove wall of the gear slot 710 forcing the gear positioning member 440 to exit the gear slot 710.

[0077] In some embodiments, the blocking ring 700 is provided with a limiting protrusion 720, and the shift lever 400 is provided with a protrusion 420 that can abut against the limiting protrusion 720. The shift lever 400 carries the protrusion 420 to rotate. When the protrusion 420 abuts against one side of the limiting protrusion 720, the shift lever 400 cannot continue to rotate, but the shift lever 400 can rotate in the opposite direction until the protrusion 420 abuts against the other side of the limiting protrusion 720, thereby limiting the rotation range of the shift lever 400. The shift lever 400 cannot rotate around one direction to 360°, so that the gear positions of the transmission are arranged in an arc shape rather than a circular shape.

[0078] It can be understood that the protruding direction of the limiting protrusion 720 is parallel to the axial direction of the blocking ring 700 / main shaft 100 / shift lever 400, that is, the limiting protrusion 720 is arranged on the end surface of the blocking ring 700.

[0079] In the embodiment, the number of the clutch mechanisms, the pin shafts 500 and the sliding grooves 410 is two, and the clutch mechanisms, the pin shafts 500 and the sliding grooves 410 are arranged one by one. The planetary gear train includes three sun gears 200 arranged side by side, and the sun gear 200 in the middle position is not matched with the clutch wheel 300, and the other two sun gears 200 are matched with the two clutch wheels 300 respectively, forming two clutch mechanisms. Other mechanisms or other structures of the transmission are prior art, and will not be described redundantly here, or refer to the patent with the publication number CN116001967, the invention name is transmission gear shifting trigger mechanism, the patent with the publication number CN116001968B, the invention name is transmission and transmission control method, and the patent with the publication number CN116161161, the invention name is internal two-way transmission and transmission control method.

[0080] The application further discloses a bicycle comprising a frame, a rear wheel and the transmission.

[0081] The transmission has small gear shifting resistance, can easily realize gear shifting, is labor-saving and has high gear shifting smoothness, and further improves the riding experience of the bicycle.

[0082] The technical features of the above embodiments can be combined arbitrarily, and in order to make the description simple, all possible combinations of the technical features in the above embodiments are not described, however, as long as the combination of the technical features does not exist contradictory, it should be considered that the combination is within the scope of the present application.

[0083] Of course, the present application is not limited to the above-mentioned embodiments, and those skilled in the art can make equivalent modifications or replacements without departing from the spirit of the present application, and these equivalent modifications or replacements are all included in the scope defined by the claims of the present application.

Claims

1. A clutching mechanism characterized by, The sun gear is provided with a first end face gear, and the first end face gear has a plurality of first ratchets, and the first ratchets are provided with first engagement surfaces; The clutch gear is provided with a second end face gear, and the second end face gear has a plurality of second ratchets, and the second ratchets are provided with second engagement surfaces for cooperating with the first engagement surfaces; The first engagement surface is sequentially provided with a first separation portion, a first transition portion and a first inclined surface portion along a direction from a dedendum of the first ratchet to a tooth top of the first ratchet, the first separation portion gradually extends along an opposite direction of rotation of the clutch gear from the first transition portion to the dedendum of the first ratchet, the first inclined surface portion gradually extends along a direction of rotation of the clutch gear from the tooth top of the first ratchet to the first transition portion, when the second engagement surface abuts against the first separation portion, the sun gear applies a separation force to the clutch gear along an axial direction of the clutch gear away from the sun gear, when the second engagement surface abuts against the first inclined surface portion, the sun gear applies a combination force to the clutch gear along the axial direction of the clutch gear close to the sun gear, the first separation portion is a curved surface, the first inclined surface portion is a plane with an angle to the axial direction of the sun gear, the first transition portion is a transition region between the first separation portion and the first inclined surface portion, and the first separation portion can be concave towards the direction of rotation of the sun gear or convex towards the opposite direction of rotation of the sun gear; Alternatively, the second engagement surface is sequentially provided with a second separation portion, a second transition portion and a second inclined surface portion along a direction from a dedendum of the second ratchet to a tooth top of the second ratchet, the second separation portion gradually extends along the direction of rotation of the clutch gear from the second transition portion to the dedendum of the second ratchet, the second inclined surface portion gradually extends along the opposite direction of rotation of the clutch gear from the tooth top of the second ratchet to the second transition portion, when the first engagement surface abuts against the second separation portion, the sun gear applies the separation force to the clutch gear along the axial direction of the clutch gear away from the sun gear, when the first engagement surface abuts against the second inclined surface portion, the sun gear applies the combination force to the clutch gear along the axial direction of the clutch gear close to the sun gear, the second separation portion is a curved surface, the second inclined surface portion is a plane with an angle to the axial direction of the clutch gear, the second transition portion is a transition region between the second separation portion and the second inclined surface portion, and the second separation portion can be concave towards the opposite direction of rotation of the clutch gear or convex towards the direction of rotation of the clutch gear. An angle between a tangent direction T1 of the first separation portion and an axial direction of the sun gear is an angle α, and the angle α is less than 60°.

2. The clutching mechanism of claim 1, wherein An angle between a tangent direction T2 of the second separation portion and an axial direction of the clutch gear is an angle β, and the angle β is less than 60°.

3. The clutching mechanism of claim 1, wherein The main shaft is provided with a receiving groove at a left end face, and an avoiding hole is formed in a side wall of the main shaft and communicates with the receiving groove, and a length direction of the avoiding hole is parallel to a length direction of the main shaft; 4. Transmission, characterized in that The clutch mechanism according to any one of claims 1 to 3, the sun gear is sleeved on the main shaft, and the clutch gear is sleeved on the main shaft; The planetary gear train includes at least two sun gears each sleeved on the main shaft; A shift lever is arranged in the receiving groove at a right end, and the shift lever is coaxially arranged with the main shaft, a left end of the shift lever is used for transmission connection with a shift driving mechanism, the shift driving mechanism is used for driving the shift lever to rotate, and a sliding groove is arranged on an outer circular surface of the shift lever. ​ ​ A pin shaft is arranged in the sliding groove, one end of the pin shaft is arranged in the sliding groove, the sliding groove is used to drive the pin shaft to move along the length direction of the main shaft, the other end of the pin shaft extends to the outside of the main shaft through the avoiding hole, and the other end of the pin shaft is configured to drive the clutch wheel to move on the main shaft, so that the first ratchet and the second ratchet are engaged or separated from each other.

5. The transmission of claim 4, wherein, The sliding groove has two opposite inner sides in the length direction of the shift lever, one of the inner sides is used to drive the pin shaft to move in the positive direction of the length direction of the main shaft, and the other of the inner sides is used to drive the pin shaft to move in the negative direction of the length direction of the main shaft.

6. The transmission of claim 5, wherein, A separation ring is arranged between two adjacent sun gears.

7. The transmission of claim 4, wherein, A fixed shift ring connected with the inner wall of the receiving groove is further included, the fixed shift ring is movably sleeved on the shift lever, a plurality of shift grooves are annularly distributed on the fixed shift ring, a shift positioning member is arranged on the shift lever, and the shift positioning member can extend into different shift grooves, so that the shift lever is positioned in different shift states.

8. The transmission of claim 7, wherein, A guide groove is arranged on the shift lever, the shift positioning member is slidably arranged in the guide groove, an elastic member is arranged in the guide groove, the shift positioning member abuts against the elastic member, and the elastic member is used to drive the shift positioning member to move in the direction of the slot opening of the guide groove, so that the shift positioning member extends into the shift groove.

9. The transmission of claim 8, wherein, An inner groove wall of the shift groove is arc-shaped, and the shift positioning member is a steel ball which can slide on the inner groove wall of the shift groove.

10. The transmission of any of claims 7 to 9, characterized in that A limiting protrusion is arranged on the fixed shift ring, and a protruding block is arranged on the shift lever, the protruding block can abut against the limiting protrusion to limit the rotation range of the shift lever.

11. The transmission of any of claims 7 to 9, characterized in that An inner wall of the receiving groove is provided with a positioning groove, and an outer circular surface of the fixed shift ring is provided with a protrusion, the protrusion can extend into the positioning groove to prevent the fixed shift ring from rotating with the shift lever.

12. Bicycle, characterized in that The transmission includes a frame, a rear wheel, and the transmission according to any one of claims 4 to 11, and the frame is in driving connection with the rear wheel through the transmission.

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