Shaft transmission structure and clutch device

Abstract

The utility model discloses a kind of shaft transmission structure and clutch device, wherein, shaft transmission structure includes first shaft piece, second shaft piece, locking member and sliding sleeve. First shaft piece has accommodating cavity and radial through locking hole;Second shaft piece is rotatably inserted in accommodating cavity and is equipped with locking groove. Locking member is slidably arranged in locking hole. Sliding sleeve is sleeved on the outside of first shaft piece, and its inner wall is provided with axially distributed abutting surface and release surface. By the axial movement of sliding sleeve, make abutting surface or release surface correspond locking hole, drive locking member radial movement to embed or come out of locking groove, to realize the circumferential fixation or separation of two shaft pieces. The utility model can realize rigid locking under the premise of not changing shafting axial position, with the advantages of compact structure, shaft end support stability etc.

Description

Technical Field

[0001] This utility model relates to the field of mechanical transmission technology, and in particular to a shaft transmission structure and clutch device. Background Technology

[0002] In power machinery, engineering vehicles, and various automated production equipment, coaxial transmission is the fundamental method for transmitting power from the power source to the actuator. To meet the needs of equipment during operation, such as starting and stopping, speed changing, reversing, or overload protection, a clutch mechanism is usually installed between the drive shaft and the driven shaft to control the engagement and disengagement of power through the action of the mechanical structure.

[0003] Currently, the most widely used rigid clutch structures in existing technology mainly include jaw clutches and splined sliding clutches. These two structures operate on similar principles, both relying on the meshing of teeth or splines at the shaft ends to transmit torque. During clutch operation, the drive mechanism typically needs to push one of the shafts or the sliding gear on the shaft to generate a large axial displacement, thereby achieving tooth engagement or disengagement. This transmission method, heavily reliant on axial movement, has significant limitations in practical applications: firstly, to meet the stroke required for disengagement, sufficient axial space must be reserved inside the equipment, which is often difficult to achieve for modern machinery aiming for miniaturization and compactness; secondly, when the drive shaft retracts to achieve disengagement, the fitting length of the shaft within the bushing or bearing is significantly reduced, leading to a decrease in the support rigidity of the shaft end. Under high-speed rotation or lateral loads, the disengaged shaft end is prone to radial runout or wobble, affecting not only the operational stability of the equipment but also damaging the sealing structure of the shaft system.

[0004] Furthermore, while friction clutches can avoid the impact caused by toothed meshing and do not require significant axial insertion, they primarily rely on friction between contact surfaces to transmit torque. Under high loads and high torque rigid transmission requirements, or in harsh conditions such as oil contamination or dust, friction clutches are prone to slippage, overheating, and even burn-out failure, failing to guarantee the accuracy and reliability of power transmission.

[0005] It is evident that existing clutch transmission technologies struggle to balance structural compactness, connection rigidity, and transmission reliability. Therefore, there is an urgent need to develop a novel clutch structure that can achieve rigid locking with a small operating stroke without altering the axial position of the shaft system, while also being compact and reliable in operation, to address these technical challenges. Utility Model Content

[0006] In view of the shortcomings of the prior art, the technical problem to be solved by this utility model is: how to provide a shaft transmission structure and clutch device that can achieve rigid locking with a small operating stroke without changing the axial position of the shaft system, and has a compact structure and high shaft end support stability.

[0007] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0008] A shaft drive structure includes a first shaft and a second shaft. The first shaft has a coaxially extending axially extending receiving cavity, and the receiving cavity has at least one radially penetrating locking hole. One end of the second shaft is coaxially rotatably inserted into the receiving cavity, and the second shaft has a locking groove corresponding to the locking hole in the circumferential direction. A locking member that can slide radially along the first shaft is provided in the locking hole. An axially movable sliding sleeve is sleeved on the first shaft. The inner wall of the sliding sleeve has a pressing surface and a releasing surface that correspond to the locking hole in the axial direction. The pressing surface and the releasing surface are distributed axially on the sliding sleeve, such that the locking member is embedded in the locking groove when the pressing surface moves to the locking hole, and can be disengaged from the locking groove when the releasing surface moves to the locking hole.

[0009] In the above structure, the locking method of radial movement of the locking element driven by a sliding sleeve replaces the traditional axial movement gear or shaft clutch method. On the one hand, during the clutch switching process, there is no axial relative displacement between the first shaft and the second shaft, which allows the second shaft to always remain deeply inserted into the receiving cavity of the first shaft. This ensures that even in the disengaged state, there is still sufficient mating length between the two shafts, thereby ensuring the coaxiality and support rigidity of the transmission system and avoiding shaft end runout. On the other hand, the sliding sleeve only needs to slide outside the first shaft and does not occupy the axial space inside the shaft system, making the overall structure more compact and suitable for occasions with limited installation space.

[0010] Furthermore, multiple locking members and locking grooves are evenly distributed along the circumference of the corresponding first shaft and second shaft, and the number of locking grooves is an integer multiple of the number of locking members.

[0011] In this way, multiple evenly distributed locking components can achieve multi-point force application, avoiding shaft force eccentricity and wear caused by single-point locking; at the same time, the number of locking grooves is set to an integer multiple of the number of locking components, so that the second shaft only needs to rotate through a small angle during rotation to align the locking components with the locking grooves and achieve engagement, which significantly improves the response speed and alignment success rate of clutch engagement.

[0012] Furthermore, the locking groove is a spline groove that extends axially along the second shaft member.

[0013] Furthermore, the pressing surface and the releasing surface are a first cylindrical surface and a second cylindrical surface coaxially arranged on the inner wall of the sliding sleeve. The inner diameter of the first cylindrical surface matches the diameter of the shaft segment where the locking hole is located and is smaller than the inner diameter of the second cylindrical surface. The difference between the radius of the second cylindrical surface and the radius of the receiving cavity matches the radial dimension of the locking member on the first shaft member. A variable diameter section with a gradually changing inner diameter is connected between the first cylindrical surface and the second cylindrical surface.

[0014] In this way, the first cylindrical surface provides a physical constraint for forced locking, preventing the locking element from coming out under load; the space difference between the second cylindrical surface and the receiving cavity constitutes a clearance space for the locking element to exit, ensuring that the locking element can completely disengage from the locking groove to cut off the power; the variable diameter section with a gradually changing inner diameter plays a wedge-shaped guiding role during the movement of the sliding sleeve, smoothly converting the axial thrust of the sliding sleeve into the radial pressure of the locking element, reducing the operating resistance and preventing the mechanism from jamming.

[0015] Furthermore, the outer peripheral surface of the sliding sleeve is provided with a driving part for receiving external driving force. The driving part is constructed as an annular groove recessed along the circumference of the sliding sleeve, or as an annular flange protruding outward along the circumference of the sliding sleeve.

[0016] This allows for flexible adaptation to different drive mechanisms based on specific application scenarios. The annular groove is suitable for use with a two-way shift fork for forced drive; the annular flange is suitable for use with push rods, cables, or unidirectional force application mechanisms, improving the versatility and adaptability of the structure.

[0017] Furthermore, a reset elastic element that can extend and retract along the axial direction of the first shaft is provided between the first shaft and the sliding sleeve, so that the pressing surface or release surface of the sliding sleeve is located at the locking hole in the initial state of the reset elastic element.

[0018] In this way, by using the reset elastic element to provide axial bias force, the sliding sleeve can automatically remain in the default state of normally closed (normally engaged) or normally open (normally disengaged) when not driven by external force, which simplifies the design of the external operating mechanism and only requires the application of a unidirectional driving force to achieve state switching.

[0019] Furthermore, an annular limiting plate is fixedly provided at the opening end of the receiving cavity, and the outer diameter of the limiting plate is larger than the outer diameter of the shaft segment where the receiving cavity is located; the reset elastic element is located on the side of the sliding sleeve away from the limiting plate, and the other end of the sliding sleeve abuts against the limiting plate in the initial state of the reset elastic element.

[0020] In this way, the large outer diameter structure of the limiting plate forms the axial travel stop of the sliding sleeve, preventing the sliding sleeve from dislodging from the first shaft under the action of spring force; at the same time, the limiting plate also provides the necessary reference position for the spring reset system, ensuring the stability of the initial state.

[0021] Furthermore, the inner diameter of the limiting plate is smaller than the inner diameter of the receiving cavity, and one end of the second shaft passing through the limiting plate is a small-diameter shaft segment. A shoulder is formed between the small-diameter shaft segment and the main body of the second shaft segment. The shoulder is located inside the receiving cavity and can rotatably abut against the side of the limiting plate facing the inside of the receiving cavity.

[0022] In this way, the limiting plate serves a dual function of limiting the sliding sleeve and the second shaft. By utilizing the small inner diameter of the limiting plate in conjunction with the shoulder of the second shaft, axial anti-disengagement limiting of the second shaft is achieved without the need for additional locking nuts or pins, simplifying the assembly structure and realizing the multi-purpose use of the component.

[0023] Furthermore, the locking element is a spherical ball, the locking hole is a circular through hole, and the diameter of the locking hole is adapted to the diameter of the locking element.

[0024] In this way, by using balls as the transmission medium, the sliding friction between the locking component and the sliding sleeve and locking groove is converted into rolling friction, which reduces wear and operating force, and at the same time reduces processing costs. It is suitable for transmission scenarios with small to medium torque.

[0025] A clutch device includes a housing, characterized in that a shaft drive structure as described above is provided inside the housing.

[0026] In summary, this utility model has the advantages of achieving rigid locking with a small operating stroke without changing the axial position of the shaft system, and has a compact structure and high shaft end support stability. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the overall structure of the steering clutch transmission system in this embodiment.

[0028] Figure 2 for Figure 1 A frontal view of the structure.

[0029] Figure 3 for Figure 2 A cross-sectional structural diagram.

[0030] Figure 4 This is a schematic diagram of the axle sectional view of the steering clutch transmission system.

[0031] Figure 5 This is a partial exploded view of the steering clutch transmission system.

[0032] Figure 6 A schematic diagram of the axial sectional structure for driving the spindle.

[0033] Figure 7 This is a schematic diagram of the shaft side sectional view of the output shaft.

[0034] Figure 8 This is a cross-sectional view of the sliding sleeve. Detailed Implementation

[0035] The present invention will be further described in detail below with reference to an embodiment employing the structure of the present invention.

[0036] In practical implementation: such as Figures 1 to 8 As shown, a mini-tiller includes a travel box, and a steering clutch transmission system is installed inside the travel box.

[0037] The steering clutch transmission system includes a drive shaft 1, on which a drive gear 13 for inputting power is coaxially and fixedly mounted. In this embodiment, the drive gear 13 is preferably a spur gear integrally formed (e.g., precision forged) on the drive shaft 1 to obtain optimal structural strength. In specific implementations, spur gears, helical gears, pulleys, or sprockets, etc., that are separately mounted or integrally formed, can also be used according to transmission requirements.

[0038] like Figures 1-6 As shown, the drive spindle 1 has symmetrically arranged clutch structures at both ends. The clutch structure includes a receiving cavity 11 extending axially and coaxially arranged on the drive spindle 1, and an output shaft 2 rotatably inserted into the receiving cavity 11. The receiving cavity 11 has at least one radially penetrating locking hole 12, and the output shaft 2 has a locking groove 21 corresponding to the locking hole 12 in the circumferential direction. A locking member 3 that can slide radially along the drive spindle 1 is provided in the locking hole 12. An axially movable sliding sleeve 4 is sleeved on the drive spindle 1. The inner wall of the sliding sleeve 4 has a pressing surface and a releasing surface that are axially corresponding to the locking hole 12. The pressing surface and the releasing surface are axially distributed on the sliding sleeve 4, so that the locking member 3 is embedded in the locking groove 21 when the pressing surface moves to the locking hole 12, and can be dislodged from the locking groove 21 when the releasing surface moves to the locking hole 12.

[0039] By employing a locking method that uses a sliding sleeve to drive the radial movement of the locking element, the axial movement of the shaft or gear in traditional dog clutches or spline clutches is replaced. This achieves a "shaft stationary, locking element moving" clutch logic. Throughout the clutch engagement and disengagement process, there is no relative axial displacement between the drive shaft and the output shaft, ensuring that the output shaft remains deeply inserted within the drive shaft's receiving cavity. This guarantees sufficient engagement length between the two shafts even in the disengaged state, thus ensuring the coaxiality and support rigidity of the transmission system. Furthermore, the sliding sleeve only needs to slide outside the drive shaft, without occupying axial space within the shaft system, resulting in a more compact overall structure that can adapt to the narrow installation environment at the bottom of the tiller's travel box. Simultaneously, the axial thrust of the sliding sleeve is converted into radial pressure on the locking element, resulting in a large locking force and stable engagement.

[0040] Multiple locking elements 3 and locking grooves 21 are evenly distributed along the circumference of the corresponding drive shaft 1 and output shaft 2, respectively, and the number of locking grooves 21 is an integer multiple of the number of locking elements 3. Multiple evenly distributed locking elements enable multi-point synchronous force application, avoiding shaft force eccentricity and wear caused by single-point locking. Simultaneously, setting the number of locking grooves to an integer multiple of the number of locking elements allows the output shaft to align with the nearest locking groove and engage with it only by rotating a small angle during rotation, significantly improving the response speed and alignment success rate of the steering clutch.

[0041] like Figure 5 and Figure 7 As shown, in this embodiment, the locking groove 21 is a spline groove extending axially along the output shaft 2, the locking member 3 is a spherical ball, and the locking hole 12 is a circular through hole, the diameter of which is adapted to the diameter of the locking member 3. Specifically, the outer surface of the output shaft 2 is provided with a plurality of spline teeth extending axially, and the locking groove 21 is formed between adjacent spline teeth; a transition ring groove is also provided on the spline teeth, which is circumferentially continuous, and the axial position of the transition ring groove corresponds to the axial position of the locking hole 12; the radial depth of the transition ring groove is less than the tooth height of the spline teeth, so that the spline teeth still retain part of the tooth structure at the bottom of the transition ring groove.

[0042] By creating shallow transition grooves at the tips of the spline teeth, when the clutch is in the transitional state between engagement and disengagement, and there is a speed difference between the output shaft and the drive shaft, the locking element (such as a ball) will not violently impact or rub against the sharp edges of the teeth. Instead, it can first fall into this shallow transition groove. Since the groove depth is less than the tooth height, the spline teeth are not cut off. Therefore, the sidewalls of the teeth still exist at the transition groove (although they are shorter). This not only ensures the overall strength of the spline but also serves as a pre-guide for the locking element to slide into the fully locked spline groove, effectively reducing the jerking sensation and the risk of jamming during clutch engagement / disengagement.

[0043] like Figure 8 As shown, the pressing surface and the releasing surface are a first cylindrical surface 42 and a second cylindrical surface 41 coaxially arranged on the inner wall of the sliding sleeve 4. The inner diameter of the first cylindrical surface 42 matches the diameter of the shaft segment where the locking hole 12 is located, and is smaller than the inner diameter of the second cylindrical surface 41. The difference between the radius of the second cylindrical surface 41 and the radius of the receiving cavity 11 matches the radial dimension of the locking member 3 on the driving spindle 1. A variable diameter section with a gradually changing inner diameter is connected between the first cylindrical surface 42 and the second cylindrical surface 41.

[0044] The first cylindrical surface provides a physical constraint for forced locking, preventing the locking element from coming out under the reaction force of the load; the space difference between the second cylindrical surface and the receiving cavity constitutes a clearance space for the locking element to exit, ensuring that the locking element can completely disengage from the locking groove to completely cut off the power; the variable diameter section with a gradually changing inner diameter plays a wedge-shaped guiding role during the movement of the sliding sleeve, smoothly converting the axial thrust of the sliding sleeve into the radial pressure of the locking element, reducing the operating resistance and preventing the mechanism from jamming.

[0045] The outer circumferential surface of the sliding sleeve 4 is provided with a driving part for receiving external driving force. In this embodiment, the driving part is constructed as an annular flange protruding outward along the circumference of the sliding sleeve 4. Simultaneously, a reset elastic element 5, which can extend and retract axially along the driving shaft 1, is provided between the driving spindle 1 and the sliding sleeve 4, so that the pressing surface or release surface of the sliding sleeve 4 is located at the locking hole 12 in the initial state of the reset elastic element 5. The reset elastic element provides an axial biasing force, allowing the sliding sleeve to automatically maintain its default state of normally closed (normally engaged) or normally open (normally disengaged) when not driven by external force. This simplifies the design of the external operating mechanism, requiring only the application of a unidirectional driving force to achieve state switching. In other specific embodiments, the driving part can also be constructed as an annular groove recessed along the circumference of the sliding sleeve 4, allowing bidirectional switching via a shift fork.

[0046] like Figure 3 and Figure 4 As shown, an annular limiting plate 6 is fixedly provided at the opening end of the receiving cavity 11. The outer diameter of the limiting plate 6 is larger than the outer diameter of the shaft segment where the receiving cavity 11 is located. The reset elastic member 5 is located on the side of the sliding sleeve 4 away from the limiting plate 6, and the other end of the sliding sleeve 4 abuts against the limiting plate 6 in the initial state of the reset elastic member 5. At the same time, the inner diameter of the limiting plate 6 is smaller than the inner diameter of the receiving cavity 11. One end of the output shaft 2 passing through the limiting plate 6 is a small-diameter shaft segment 22. A shoulder is formed between the small-diameter shaft segment 22 and the main body of the output shaft 2. The shoulder is located inside the receiving cavity 11 and can rotatably abut against the side of the limiting plate 6 facing the inside of the receiving cavity 11.

[0047] The large outer diameter of the limiting plate forms the axial travel stop of the sliding sleeve, preventing it from disengaging from the drive shaft under spring force. Simultaneously, the limiting plate provides a necessary reference position for the spring return system, ensuring initial stability. Furthermore, the limiting plate serves a dual limiting function for both the sliding sleeve and the output shaft. By utilizing the small inner diameter of the limiting plate in conjunction with the shoulder of the output shaft, the output shaft is physically restricted from disengaging from the receiving cavity without the need for additional locking nuts or pins. Moreover, during clutch operation, this limiting fit consistently fixes the output shaft in its axial position, ensuring that it does not axially move due to clutch disengagement, thus guaranteeing a constant fit depth and support rigidity between the output shaft and the drive shaft.

[0048] In this embodiment, in the steering clutch transmission system, the two accommodating cavities 11 on the drive spindle 1 are axially connected; the opposite ends of the two output shafts 2 are connected through a rotatable shaft hole fitting structure to form a load-bearing beam; the outer ends of the two output shafts 2 are equipped with travel bearings, which are rotatably supported on the wall of the travel box, and the drive spindle 1 is rotatably mounted on the load-bearing beam formed by the two output shafts 2. This overturns the traditional force-bearing mode of micro-tillers, where the box supports the spindle and the spindle cantilever supports the wheel axle. This solution interconnects the two output shafts to form an integral load-bearing beam spanning the travel box, and directly supports this load-bearing beam on the box wall through travel bearings, allowing the huge bending moment load from the wheels to be directly transmitted to the box. The drive spindle, in a "floating" state, is mounted on the load-bearing beam formed by the output shafts, only responsible for transmitting torque and no longer bearing the bending moment load from the wheels. This structure greatly improves the overall rigidity and bending resistance of the shaft system without increasing the size of the box, fundamentally solving the risk of axle breakage during heavy-load tillage.

[0049] Specifically, such as Figure 3 and Figure 4 As shown, the shaft-hole mating structure includes an inner support shaft 9 and inner support holes 23 respectively opened at opposite ends of the two output shafts 2. The inner support holes 23 are coaxially arranged on the output shafts 2, and both ends of the inner support shaft 9 are rotatably inserted into the two inner support holes 23. By using the inner support shaft as an intermediate connector, the two independent output shafts on the left and right are precisely aligned and connected at their geometric centers, forming the physical basis of the aforementioned load-bearing beam, while ensuring that the left and right output shafts can rotate independently to achieve differential speed or unilateral parking steering.

[0050] To prevent the two output shafts from pushing against each other, a retaining ring is provided between the two output shafts 2. The retaining ring is protrudingly disposed on the inner wall of the receiving cavity 11 of the drive main shaft 1 or in the middle of the inner support shaft 9. In this embodiment, the retaining ring is located in the middle of the inner support shaft 9. This provides an axial thrust reference between the two output shafts, preventing excessive inward movement of the two output shafts under the action of lateral force from the wheel, and ensuring the stability of the axial clearance of the internal components of the clutch.

[0051] Furthermore, each of the two output shafts 2 has a support shaft section 24 formed at its opposite end. The outer diameter of the support shaft section 24 matches the inner diameter of the receiving cavity 11. The drive spindle 1 is rotatably supported on the support shaft sections 24 of the two output shafts 2 through the inner wall of the receiving cavity 11. This provides a specific physical interface for the "floating" installation of the drive spindle. By using the support shaft section at the inner end of the output shaft as a sliding bearing surface, the coaxiality between the drive spindle and the output shaft is ensured, achieving smooth operation of the floating support.

[0052] When the micro-tiller of this embodiment is in operation, after the micro-tiller engine is started, the power is transmitted to the drive gear 13 through the gearbox, which drives the drive shaft 1 to rotate.

[0053] 1. Straight-line driving state (normally closed mode): When no steering operation is performed, both sliding sleeves 4 on the left and right sides are held at their extreme positions near the limit plate 6 under the elastic force of the reset elastic element 5. At this time, the first cylindrical surface (pressing surface) of the inner wall of the sliding sleeve 4 covers the locking hole 12, forcibly pressing the locking element 3 (ball) into the spline locking groove 21 of the output shaft 2. The torque of the drive shaft 1 is simultaneously transmitted to the left and right output shafts 2 through the locking element 3, driving the two walking wheels on both sides to rotate synchronously, and the tiller moves forward in a straight line. During this process, the left and right output shafts 2 are connected into a whole beam through the inner support shaft 9, which jointly bears the bending moment load from the ground, while the drive shaft 1 only floats to transmit torque.

[0054] 2. Steering Operation (Taking Left Turn as an Example): When the operator squeezes the left steering handle, the resistance of the reset elastic element 5 is overcome by the cable or push rod mechanism, pulling the left sliding sleeve 4 inward (away from the limit plate 6). After the sliding sleeve 4 moves a certain distance, the second cylindrical surface (release surface) of its inner wall aligns with the locking hole 12, and the locking element 3 loses the radial forced constraint from the inner wall of the sliding sleeve 4. At this time, under the centrifugal force generated by the high-speed rotation of the drive shaft 1, and under the relative rotation (rolling) squeezing action between the output shaft 2 and the drive shaft 1 due to the load difference, the locking element 3 (ball) will automatically move outward radially, quickly disengage from the locking groove 21 of the output shaft 2, and fall into the clearance space formed between the second cylindrical surface and the receiving cavity 11. The power on the left side is then cut off, the left output shaft 2 loses driving force (or stops rotating with the brake), while the right output shaft 2 continues to maintain drive, and the tiller uses the speed difference between the left and right wheels to achieve left turn.

[0055] 3. Reset State: After the steering is completed, the operator releases the handle, and the reset elastic element 5 pushes the left sliding sleeve 4 to reset. The variable diameter section of the inner wall of the sliding sleeve 4 contacts and pushes the locking element 3. If the locking element 3 is aligned with the spline tooth tip at this time, it will first fall into the shallower transition ring groove; as the output shaft 2 rotates relative to it, once the locking element 3 is aligned with the locking groove 21, it will be quickly pressed into the groove under the wedge force of the variable diameter section, restoring power transmission.

[0056] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A shaft drive structure, characterized in that, The assembly includes a first shaft (1) and a second shaft (2). The first shaft (1) has a coaxially extending axially extending receiving cavity (11) with at least one radially penetrating locking hole (12). One end of the second shaft (2) is coaxially rotatably inserted into the receiving cavity (11), and the second shaft (2) has a locking groove (21) corresponding to the locking hole (12) in the circumferential direction. The locking hole (12) contains a groove that can slide radially along the first shaft (1). The locking member (3) is provided with a sliding sleeve (4) that can move axially on the first shaft member (1). The inner wall of the sliding sleeve (4) has a pressing surface and a releasing surface that are axially corresponding to the locking hole (12). The pressing surface and the releasing surface are distributed on the sliding sleeve (4) along the axial direction, so that the locking member (3) can be embedded in the locking groove (21) when the pressing surface moves to the locking hole (12), and can be dislodged from the locking groove (21) when the releasing surface moves to the locking hole (12).

2. The shaft drive structure as described in claim 1, characterized in that, The locking member (3) and the locking groove (21) are provided in multiple ways along the circumference of the corresponding first shaft (1) and second shaft (2), and the number of the locking groove (21) is an integer multiple of the locking member (3).

3. The shaft drive structure as described in claim 2, characterized in that, The locking groove (21) is a spline groove that extends axially along the second shaft (2).

4. The shaft transmission structure as described in claim 1, characterized in that, The pressing surface and the releasing surface are a first cylindrical surface and a second cylindrical surface coaxially arranged on the inner wall of the sliding sleeve (4). The inner diameter of the first cylindrical surface matches the diameter of the shaft segment where the locking hole (12) is located, and is smaller than the inner diameter of the second cylindrical surface. The difference between the radius of the second cylindrical surface and the radius of the receiving cavity (11) matches the size of the locking member (3) in the radial direction of the first shaft member (1). A variable diameter section with a gradually changing inner diameter is connected between the first cylindrical surface and the second cylindrical surface.

5. The shaft drive structure as described in claim 1, characterized in that, The outer peripheral surface of the sliding sleeve (4) is provided with a driving part for receiving external driving force. The driving part is constructed as an annular groove recessed along the circumference of the sliding sleeve (4), or as an annular flange protruding outward along the circumference of the sliding sleeve (4).

6. The shaft drive structure as described in claim 5, characterized in that, A reset elastic element (5) that can extend and retract along the axial direction of the first shaft (1) is provided between the first shaft (1) and the sliding sleeve (4), so that the pressing surface or the release surface of the sliding sleeve (4) is located at the locking hole (12) in the initial state of the reset elastic element (5).

7. The shaft drive structure as described in claim 6, characterized in that, The opening end of the receiving cavity (11) is fixedly provided with an annular limiting plate (6), the outer diameter of the limiting plate (6) is larger than the outer diameter of the shaft segment where the receiving cavity (11) is located; the reset elastic member (5) is located on the side of the sliding sleeve (4) away from the limiting plate (6), and the other end of the sliding sleeve (4) abuts against the limiting plate (6) in the initial state of the reset elastic member (5).

8. The shaft transmission structure as described in claim 7, characterized in that, The inner diameter of the limiting plate (6) is smaller than the inner diameter of the receiving cavity (11). The end of the second shaft (2) that passes through the limiting plate (6) is a small diameter shaft section (22). A shoulder is formed between the small diameter shaft section (22) and the body of the second shaft (2). The shoulder is located inside the receiving cavity (11) and can rotate relative to the side of the limiting plate (6) facing the inside of the receiving cavity (11).

9. The shaft transmission structure according to any one of claims 1 to 8, characterized in that, The locking element (3) is a spherical ball, and the locking hole (12) is a circular through hole. The diameter of the locking hole (12) is adapted to the diameter of the locking element (3).

10. A clutch device, comprising a housing, characterized in that, The housing (7) is provided with a shaft transmission structure as described in any one of claims 1 to 9.

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