Switching mechanism

Abstract

This utility model relates to a switching mechanism, comprising: a first shaft, a second shaft, a coupling sleeve, an actuating unit, an actuating pin, and a mating part. The coupling sleeve is axially movable and fitted onto the second shaft to control the connection and disconnection between the first and second shafts; the outer periphery of the coupling sleeve has a helical line portion, which has a helical line contact surface extending both circumferentially and axially; the actuating pin is controlled by the actuating unit to be movable in the radial direction; the mating part is disposed at the end of the actuating pin near the second shaft and has a mating surface; the actuating unit controls the radial movement of the mating part via the actuating pin and controls the abutment engagement of the mating surface with the helical line contact surface, thereby converting the radial movement of the mating part into axial movement of the coupling sleeve. The helical line contact surface has a tooth flank angle greater than 0 degrees and less than 90 degrees, and the mating surface has an inclined surface corresponding to the helical line contact surface.

Description

Technical Field

[0001] This utility model relates to the field of torque transmission mechanism technology. Specifically, this utility model relates to a switching mechanism for torque transmission disconnection and connection. Background Technology

[0002] In the vehicle's drive control unit, the switching mechanism is used to disconnect and connect the half-shaft power and the electric axle power during the switching process between two-wheel drive and four-wheel drive in pure electric four-wheel drive vehicles or hybrid four-wheel drive vehicles.

[0003] In a conventional switching mechanism, a first shaft, a second shaft, and a connecting sleeve are included. The outer periphery of the connecting sleeve has a helical line and is axially movable relative to the second shaft, thereby enabling the switching of disconnection and connection between the first and second shafts. The switching mechanism also includes an actuating unit, which controls the radial extension and retraction of an actuating pin relative to the second shaft. The end of the actuating pin is provided with a mating part. When the switching mechanism switches from a connected state to a disconnected state, the mating part abuts against the helical line on the connecting sleeve as the actuating pin extends radially, so that the radial movement of the mating part is converted into the axial movement of the connecting sleeve, thereby controlling the disconnection of the second shaft from the first shaft. When the switching mechanism switches from a disconnected state to a connected state, the actuating unit controls the actuating pin to drive the mating part to retract, the mating part disengages from the connecting sleeve, and the connecting sleeve returns to its axial position to connect the second shaft to the first shaft.

[0004] In the current design, the spiral profile of the engaging sleeve and the outer surface of the mating part are both perpendicular to the plane of the axis. When the engaging sleeve receives excessive torque from the second shaft, the engaging sleeve will generate a very large axial force on the mating part, which can easily cause the actuator pin to be subjected to excessive axial shear force, resulting in deformation or even breakage.

[0005] Therefore, there is an urgent need for a switching mechanism that can reduce the axial force between the engaging sleeve and the mating part, thereby effectively protecting the various components of the switching mechanism and improving its service life. Utility Model Content

[0006] To solve the above technical problems, this utility model provides a switching mechanism.

[0007] An embodiment of this utility model provides a switching mechanism, including: a first shaft, a second shaft, a coupling sleeve, an actuating unit, an actuating pin, and a mating part. The coupling sleeve is movably fitted onto the second shaft along the axial direction to control the connection and disconnection between the first shaft and the second shaft; and the outer periphery of the coupling sleeve has a helical line portion, the helical line portion having a helical line contact surface extending simultaneously in both the circumferential and axial directions. The actuating pin is controlled by the actuating unit to be movable in the radial direction. The mating part is disposed at the end of the actuating pin near the second shaft and has a mating surface; the actuating unit controls the movement of the mating part in the radial direction of the second shaft via the actuating pin, and controls the abutment engagement of the mating surface with the helical line contact surface, so as to convert the movement of the mating part in the radial direction of the second shaft into the movement of the coupling sleeve in the axial direction. The helical line contact surface has a tooth flank angle greater than 0 degrees and less than 90 degrees, and the mating surface has an inclined surface corresponding to the helical line contact surface between the radial and axial directions.

[0008] According to some optional embodiments of the present invention, the switching mechanism further includes: a reset spring, which is sleeved on the second shaft and disposed on the axial side of the engaging sleeve away from the first shaft.

[0009] According to some optional embodiments of this utility model, the engaging sleeve further includes a mating portion receiving groove; the mating portion receiving groove is located on the axial side of the end of the helical contact surface of the helical portion, and the bottom surface of the mating portion receiving groove is closer to the central axis of the second shaft in the radial direction relative to the helical portion. In the engaged state, the mating portion is located radially outside the helical portion; in the disengaged state, the mating portion is located within the mating portion receiving groove.

[0010] According to some optional embodiments of the present invention, the mating portion receiving groove is closer to the first shaft in the axial direction relative to the helical line portion; the end of the helical line contact surface is closer to the mating portion receiving groove in the axial direction relative to the starting end of the helical line contact surface.

[0011] According to some optional embodiments of this utility model, the spiral line contact surface and the mating surface are arranged in parallel.

[0012] According to some optional embodiments of the present invention, the spiral line contact surface and the outer peripheral surface of the spiral line portion have a profile fillet, and the mating surface and the radial inner surface of the mating portion have a mating fillet.

[0013] According to some optional embodiments of this utility model, the mating part is a bearing, and the inner ring of the bearing is fixedly sleeved on the radial inner end of the actuating pin.

[0014] According to some optional embodiments of the present invention, the mating part is an annular piece, sleeved on the radial inner end of the actuating pin, and is rotatable relative to the actuating pin.

[0015] According to some optional embodiments of the present invention, the mating part and the actuating pin are an integral structure.

[0016] According to some optional embodiments of the present invention, the actuating pin is rotatable relative to the actuating unit, so that the mating part, which is integrally formed with the actuating pin, is rotatable relative to the actuating unit.

[0017] In the switching mechanism of this utility model, the spiral line contact surface has a tooth flank angle greater than 0 degrees and less than 90 degrees, and the mating surface has an inclined surface corresponding to the spiral line contact surface in the radial and axial directions. That is, the contact surface between the spiral line part and the mating part is chamfered. While realizing the retraction function of the engaging sleeve, it effectively reduces the excessive axial force generated on the mating part and the actuator pin under excessive torque. Furthermore, it can also generate an axial component force to separate the mating part from the spiral line part when the torque is too large, avoiding damage to the actuator pin, effectively protecting the various components of the switching mechanism, and improving the service life of the switching mechanism. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the description of the embodiments of this utility model will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A schematic diagram of a switching mechanism according to some embodiments of the present invention is shown; Figure 2 A schematic diagram of a switching mechanism for a disconnected state according to some embodiments of the present invention is shown; Figure 3 A cross-sectional view showing the engagement of a first shaft and a second shaft according to some embodiments of the present invention is shown; Figure 4 A partial cross-sectional view of the switching mechanism when the mating part and the spiral line part are mated according to some embodiments of the present invention is shown; Figure 5A partial cross-sectional view of the switching mechanism is shown when the mating part and the spiral line part are not mated according to some embodiments of the present invention; Figure 6 This invention provides a partially enlarged schematic diagram of the mating portion and the spiral line portion according to some embodiments of the present invention. Figure 7 A partial cross-sectional view of a switching mechanism according to some embodiments of the present invention, wherein the mating part is an annular member, is shown; and Figure 8 A partial cross-sectional view of a switching mechanism according to some embodiments of the present invention, in which the mating part and the actuator are integrated, is shown. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the described embodiments of this utility model are within the protection scope of this utility model.

[0021] In the vehicle's drive control unit, the switching mechanism can be used to disconnect and connect the half-shaft power and the electric axle power during the switching process between two-wheel drive and four-wheel drive in pure electric four-wheel drive vehicles or hybrid four-wheel drive vehicles.

[0022] This invention provides a switching mechanism for switching control of the torsion-transmitting connection and disconnection between a first shaft and a second shaft, which can be applied to, but is not limited to, the drive control unit of a vehicle.

[0023] According to an embodiment of the present invention, a switching mechanism is provided. Figure 1 A schematic diagram of a switching mechanism according to some embodiments of the present invention is shown; Figure 2 A schematic diagram of a switching mechanism for a disconnected state according to some embodiments of the present invention is shown. For example... Figure 1 and Figure 2 As shown, the switching mechanism includes: a first shaft 1, a second shaft 2, a coupling sleeve 3, an execution unit 4, an execution pin 5, and a mating part 6. In some embodiments, the first shaft 1 can be an input shaft and the second shaft 2 can be an output shaft; in other embodiments, the first shaft 1 can also be an output shaft and the second shaft 2 can be an input shaft. This invention does not limit the input and output of the first shaft 1 and the second shaft 2. The following description uses only the example of the first shaft 1 as the input shaft and the second shaft 2 as the output shaft.

[0024] More specifically, Figure 3A cross-sectional view showing the engagement of a first shaft and a second shaft according to some embodiments of the present invention is shown. Figure 4 A partial cross-sectional view of the switching mechanism when the mating part and the spiral line part are mated according to some embodiments of the present invention is shown; Figure 5 A partial cross-sectional view of the switching mechanism according to some embodiments of the present invention is shown when the mating part and the helical line part are not mated. (In conjunction with...) Figures 1 to 5 As shown, the coupling sleeve 3 is torsionally fitted onto the outer periphery of the second shaft 2 so as to rotate with the second shaft 2 and is movable relative to the second shaft 2 in the axial direction to control the connection and disconnection between the first shaft 1 and the second shaft 2.

[0025] Specifically, such as Figure 3 As shown, the first shaft 1 has an input engagement end 11 for engaging with the second shaft 2 at one axial end near the second shaft 2, and the second shaft 2 has an output engagement end 21 for engaging with the first shaft 1 at one axial end. The engagement sleeve 3 has multiple connecting pins 33 extending in the axial direction L at the axial ends of the input engagement end 11 and the output engagement end 21. Correspondingly, the output engagement end 21 has multiple through holes 211, each corresponding to one of the connecting pins 33. The output engagement end 21 and the connecting pins 33 have multiple structures for torque transmission with the input engagement end 11, such as pawls 212. Each pawl 212 has a pivot end 212a pivotally fixed to the output engagement end 21, and a mating end 212b located away from the pivot end 212a and facing radially outward. The mating end 212b is used to engage with the connecting pins 33. Specifically, the through hole 211 is located radially outward and close to the mating end 212b relative to it. The connecting pin 33 can be designed with a gradually increasing end diameter in the axial direction L, so that when the connecting pin 33 moves axially toward the output engagement end 21 and enters the through hole 211, the connecting pin 33 can abut against the mating end 212b of the pawl 212, gradually pressing the mating end 212b radially inward. At this time, the mating end 212b rotates around the pivot end 212a and moves radially inward. Continuing as... Figure 3 As shown, a torsion-resistant protrusion 212c is provided on the radially inner side of the end of the pawl 212 away from the pivot end 212a; correspondingly, the outer peripheral side of the input engagement end 11 is formed as a gear structure; when the end of the pawl 212 away from the pivot end 212a rotates radially inward, the torsion-resistant protrusion 212c engages with the tooth groove 111 of the input engagement end 11 to form a torsion-resistant fit. In this way, the switching mechanism is in the connected state, and torque can be transmitted between the first shaft 1 and the second shaft 2.

[0026] When the engaging sleeve 3 moves axially away from the input engaging end 11 and the output engaging end 21, the connecting pin 33 leaves the through hole 211 and no longer abuts against the mating end 212b of the pawl 212. Under the elastic force of the return spring 213, the end of the pawl 212 away from the pivot 212a rotates radially outward to rebound, causing the anti-torsion protrusion 212c to disengage from the tooth groove 111 of the input engaging end 11. In this way, the switching mechanism is in the disengaged state, and no torque is transmitted between the first shaft 1 and the second shaft 2.

[0027] Furthermore, a helical section 31 is formed on the outer periphery of the engaging sleeve 3, and the helical section 31 has a helical contact surface 311 extending simultaneously in the circumferential direction C and the axial direction L; the actuating pin 5 is controlled by the actuating unit 4 to move in the radial direction R of the second shaft 2; wherein, the actuating unit 4 can be a solenoid valve, and the actuating pin 5 can be a solenoid pin. A mating part 6 is provided at the end of the actuating pin 5 near the second shaft 2, and a mating surface 61 is formed thereon; the actuating unit 4 controls the movement of the mating part 6 in the radial direction R of the second shaft 2 via the actuating pin 5, and controls the contact engagement or disengagement of the mating surface 61 with the helical contact surface 311, so as to convert the movement of the mating part 6 in the radial direction R of the second shaft into the movement of the engaging sleeve 3 in the axial direction L.

[0028] like Figure 1 The diagram shows the initial engagement of the mating part 6 with the spiral section 31 of the engaging sleeve 3. (See also...) Figure 1 and Figure 4 As shown, at this time, the first shaft 1 and the second shaft 2 are still in a torsion-transmitting connection state. As the second shaft 2, along with the engaging sleeve 3, rotates relative to the mating part 6, the helical contact surface 311 extending in the circumferential direction C and the axial direction L continuously abuts against the mating surface 61, causing relative movement between the mating part 6 and the engaging sleeve 3 in the axial direction L. Since the mating part 6 is fixed in the axial direction L, the relative movement between the engaging sleeve 3 and the mating part 6 in the axial direction L causes relative movement between the engaging sleeve 3 and the second shaft 2 in the axial direction L.

[0029] like Figure 2 As shown, the mating part 6 moves the engaging sleeve 3 axially away from the first shaft 1 until the connecting pin of the engaging sleeve 3 is completely disengaged from the input engaging end of the first shaft 1; at this time, the first shaft 1 and the second shaft 2 are in a disconnected state.

[0030] Among them, such as Figure 4 and Figure 5As shown, the helical line contact surface 311 has a flank angle α greater than 0 degrees and less than 90 degrees, and the mating surface 61 has an inclined surface corresponding to the helical line contact surface 311 between the radial direction R and the axial direction L. The flank angle refers to the angle between the flank (i.e., the helical line contact surface 311) and the perpendicular line to the thread axis on the thread profile of the helical line portion 31.

[0031] It is understandable that if the helical thread 31 is a rectangular thread, that is, the flank angle of the helical thread contact surface 311 is 0 degrees, and the mating surface 61 is a plane perpendicular to the axial direction L, during the rotation of the helical thread contact surface 311 against the mating surface 61, the mating surface 61 will be subjected to axial force and tangential force from the helical thread contact surface 311. When the torque is too large, it will result in a large axial force, which will easily cause a large axial impact force on the mating part 6. In particular, for the actuator pin 5 with a smaller diameter, it will be subjected to a large axial shear force, which will make the actuator pin 5 prone to breakage.

[0032] In the switching mechanism of this utility model, see Figure 4 and Figure 5 As shown, the helical thread contact surface 311 has a flank angle α greater than 0 degrees and less than 90 degrees. For example, the helical thread portion 31 can be a trapezoidal thread or a triangular thread, etc., with a thread flank angle inclined at a certain angle. Furthermore, the mating surface 61 has an inclined surface between the radial direction R and the axial direction L at a position corresponding to the helical thread contact surface 311, such that the contact surface between the helical thread portion 31 and the mating portion 6 is chamfered. Thus, as... Figure 4 As shown, during the rotation of the helical contact surface 311 against the mating surface 61, the mating surface 61 is subjected to a tangential force F from the helical contact surface 311. T In addition, the supporting force of the spiral line contact surface 311 on the mating surface 61 can be decomposed into an axial component F along the axial direction L. A and the radial component F along the radial direction v When encountering a torsional impact, when the radial component F v When the radial component F exceeds a certain threshold, v This will cause the mating part 6 to spring upward, thus protecting the axial component force F acting on the mating part 6. A It is confined within a safe range to avoid damage to the actuator pin 5, effectively protecting all components of the switching mechanism and extending the service life of the switching mechanism.

[0033] See also Figures 1 to 5 As shown, in some embodiments, the switching mechanism further includes a return spring 7, which is sleeved on the second shaft 2 and disposed on the axial side of the engaging sleeve 3 away from the first shaft 1.

[0034] The return spring 7 provides an axial elastic force to the engaging sleeve 3 toward the first shaft 1. Therefore, the normal state of the switching mechanism is a torque-transmitting connection. When the mating part 6 moves radially inward, causing the engaging sleeve 3 to move axially away from the first shaft 1, the elastic force of the return spring 7 needs to be overcome to disconnect the first shaft 1 from the second shaft 2; when the mating part 6 moves radially outward, disengaging from the engaging sleeve 3, the return spring 7 pushes the engaging sleeve 3 axially toward the first shaft 1 to make the first shaft 1 and the second shaft 2 torque-transmittingly connected.

[0035] See Figure 4 and Figure 5 As shown, in some embodiments, the engaging sleeve 3 further includes a mating portion receiving groove 32; the mating portion receiving groove 32 is located on the axial side of the end of the helical contact surface 311 of the helical portion 31, and the bottom surface of the mating portion receiving groove 32 is closer to the central axis A of the second shaft 2 in the radial direction R relative to the helical portion 31. In the engaged state, the mating portion 6 is located radially outside the helical portion 31; in the disengaged state, the mating portion 6 is located within the mating portion receiving groove 32.

[0036] By providing a mating part receiving groove 32, the mating part 6 can be stably contained within the mating part receiving groove 32 in the disconnected state, thereby stably limiting the axial position of the engaging sleeve 3.

[0037] Furthermore, the mating portion receiving groove 32 is closer to the first shaft 1 in the axial direction L relative to the spiral line portion 31; the end of the spiral line contact surface 311 is closer to the mating portion receiving groove 32 in the axial direction L relative to the starting end of the spiral line contact surface 311.

[0038] Thus, during the transition from the torque connection state to the disconnection state, the mating part 6 abuts against the spiral line part 31. From the starting end of the spiral line contact surface 311 to the end of the spiral line contact surface 311, the mating part 6 gradually moves radially inward and is finally pushed into the mating part receiving groove 32, completing the switch from the torque connection state to the disconnection state.

[0039] See also Figure 4 and Figure 5 As shown, in some embodiments, the helical line contact surface 311 and the mating surface 61 are arranged in parallel. For example, the flank angle α of the helical line contact surface 311 and the inclination angle of the mating surface 61 are the same. The larger the flank angle α, the greater the radial component force F. v and axial component F A The larger the ratio, the more effectively the impact force L in the axial direction on the mating part 6 and the actuator pin 5 can be reduced. However, at the same time, the actuator unit 4 needs to provide a greater force to overcome the elastic force of the return spring 7; the smaller the tooth flank angle α, the greater the radial component force F. v and axial component F AThe smaller the ratio, the less force the actuator 4 needs to provide to overcome the elastic force of the return spring 7, but the impact force in the axial direction L on the mating part 6 and the actuator pin 5 will also increase.

[0040] Figure 6 A partially enlarged schematic diagram of the mating portion and the spiral line portion according to some embodiments of the present invention is shown. See also Figure 6 As shown, in some embodiments, the spiral line contact surface 311 and the outer peripheral surface of the spiral line portion 31 have a profile fillet R3, and the mating surface 61 and the radial inner surface of the mating portion 6 have a mating fillet R6.

[0041] During the switching mechanism's transition from a torque-connected state to a disconnected state, the area between the spiral-shaped contact surface 311 and the outer peripheral surface of the spiral-shaped section 31, and the area between the mating surface 61 and the radially inner surface of the mating section 6, are the first to come into contact. Therefore, by providing a profile fillet R3 in the initial contact area of ​​the spiral-shaped section 31 and a mating fillet R6 in the initial contact area of ​​the mating section 6, the impact between the mating section 6 and the spiral-shaped section 31 can be further reduced, allowing for a smoother transition between the spiral-shaped contact surface 311 and the mating surface 61, thereby improving the service life of each component of the switching mechanism.

[0042] The mating part 6 can take various forms of components. Optionally, the mating part 6 can be configured to be rotatable relative to the spiral line contact surface 311 of the engaging sleeve 3, so that during the state switching process, the sliding friction between the spiral line contact surface 311 and the mating surface 61 is converted into rolling friction, thereby reducing the friction between the mating part 6 and the spiral line part 31 and improving the service life of each component of the switching mechanism.

[0043] Specifically, in such Figures 4 to 6 In the illustrated embodiment, the mating part 6 can be a bearing, with the inner ring of the bearing fixedly fitted onto the radially inner end of the actuating pin 5. In this embodiment, the mating surface 61 is provided on the outer ring of the bearing, which has a conical mating surface 61. During the state switching process, the outer ring of the bearing can rotate relative to the inner ring. The conical mating surface 61 always has an inclined surface that mates with the helical contact surface 311 at the position corresponding to it. Therefore, the mating surface 61 and the helical contact surface 311 form rolling friction, thereby reducing the frictional force between the mating surface 61 and the helical contact surface 311.

[0044] In another embodiment, Figure 7 A partial cross-sectional view of a switching mechanism according to some embodiments of the present invention, wherein the mating part is a ring-shaped component, is shown. For example... Figure 7As shown, the mating part 6 is a ring-shaped component, sleeved on the radially inner end of the actuating pin 5, and is rotatable relative to the actuating pin 5. Figure 6 Similar to the embodiment, a conical mating surface 61 is provided on the outer surface of the annular member. During the state switching process, the annular member can rotate relative to the actuating pin 5, so the mating surface 61 forms rolling friction with the helical contact surface 311 to reduce the frictional force between the mating surface 61 and the helical contact surface 311.

[0045] In yet another embodiment, Figure 8 A partial cross-sectional view of a switching mechanism according to some embodiments of the present invention, in which the mating part 6 and the actuating pin are integrally formed, is shown. The mating part 6 and the actuating pin 5 are integrally formed.

[0046] In this embodiment, the mating part 6 and the actuator pin 5 are an integral structure, and... Figure 6 , Figure 7 Similar to the embodiment, a conical mating surface 61 is provided on the outer surface of the mating part 6. Although the mating part 6 cannot rotate relative to the actuating pin 5, it can be configured such that the integral structure of the mating part 6 and the actuating pin 5 is rotatable relative to the actuating unit 4. During the state switching process, the integral structure of the mating part 6 and the actuating pin 5 can roll relative to the helical contact surface 311, thus forming rolling friction between the mating surface 61 and the helical contact surface 311, thereby reducing the frictional force between the mating surface 61 and the helical contact surface 311.

[0047] In the switching mechanism of this utility model, the spiral line contact surface 311 has a tooth flank angle greater than 0 degrees and less than 90 degrees, and the mating surface 61 has an inclined surface corresponding to the spiral line contact surface 311 between the radial direction R and the axial direction L. That is, the contact surface between the spiral line part 31 and the mating part 6 is chamfered. While realizing the retraction function of the engaging sleeve 3, it effectively reduces the excessive axial force generated on the mating part 6 and the actuating pin 5 when the torque is too large. Furthermore, when the torque is too large, it can also generate an axial component force to separate the mating part 6 from the spiral line part 31, avoid damage to the actuating pin 5, effectively protect the various components of the switching mechanism, and improve the service life of the switching mechanism.

[0048] While possible embodiments have been described exemplarily in the foregoing description, it should be understood that numerous variations of the embodiments exist through combinations of all known and readily conceived technical features and implementation methods. Furthermore, it should be understood that the exemplary embodiments are merely examples and do not in any way limit the scope, application, or construction of this invention. The foregoing description is more intended to provide those skilled in the art with technical guidance for transforming at least one exemplary embodiment, wherein various changes, particularly regarding the function and structure of the components, can be made without departing from the scope of the claims.

[0049] Appendix Label Table 1. First shaft; 11. Input engagement end; 111. Tooth groove; 2. Second shaft; 21. Output engagement end; 211. Through hole; 212. Pawl; 212a. Pivot end; 212b. Mating end; 212c. Anti-torsion protrusion; 213. Return spring; 3. Engaging sleeve; 31. Spiral line section; 311. Spiral line contact surface; 32. Mating part receiving groove; 33. Connecting pin; R3. Profile fillet; 4. Execution unit; 5. Execute the sale; 6. Mating part; 61. Mating surface; R6. Mating fillet; 7. Return spring; A. Central axis; R. Radial direction; L. Axial direction; C. Circumferential direction; a. Tooth flank angle; F T : Tangential force; F A Radial component; F V : Axial component force.

Claims

1. A switching mechanism, characterized by include: First axis (1); Second axis (2); A coupling sleeve (3) is movably fitted onto the second shaft (2) in the axial direction (L) to control the connection and disconnection between the first shaft (1) and the second shaft (2); and the outer periphery of the coupling sleeve (3) is formed with a helical line portion (31), the helical line portion (31) having a helical line contact surface (311) extending simultaneously in the circumferential direction (C) and the axial direction (L). Execution unit (4); The actuator pin (5), which is controlled by the actuator unit (4) to be movable in the radial direction (R) of the second shaft (2); and The mating part (6) is provided at the end of the actuating pin (5) near the second shaft (2) and has a mating surface (61); the actuating unit (4) controls the movement of the mating part (6) in the radial direction (R) of the second shaft (2) via the actuating pin (5) and controls the abutment of the mating surface (61) with the spiral line contact surface (311) to convert the movement of the mating part (6) in the radial direction (R) of the second shaft (2) into the movement of the engaging sleeve (3) in the axial direction (L); The spiral line contact surface (311) has a tooth flank angle (a) greater than 0 degrees and less than 90 degrees, and the mating surface (61) has an inclined surface corresponding to the spiral line contact surface (311) between the radial direction (R) and the axial direction (L).

2. The switching mechanism of claim 1, wherein Also includes: A return spring (7) is sleeved on the second shaft (2) and located on the axial side of the engaging sleeve (3) away from the first shaft (1).

3. The switching mechanism according to claim 1, characterized in that, The coupling sleeve (3) also includes a mating portion receiving groove (32); the mating portion receiving groove (32) is located on the axial side of the end of the spiral line contact surface (311) of the spiral line portion (31), and the bottom surface of the mating portion receiving groove (32) is closer to the central axis (A) of the second shaft (2) in the radial direction (R) relative to the spiral line portion (31). In the engaged state, the mating part (6) is located radially outside the spiral line part (31); in the disengaged state, the mating part (6) is located inside the mating part receiving groove (32).

4. The switching mechanism according to claim 3, characterized in that, The mating portion receiving groove (32) is closer to the first shaft (1) in the axial direction (L) relative to the spiral line portion (31); the end of the spiral line contact surface (311) is closer to the mating portion receiving groove (32) in the axial direction (L) relative to the starting end of the spiral line contact surface (311).

5. The switching mechanism according to claim 1, characterized in that, The spiral line contact surface (311) and the mating surface (61) are arranged in parallel.

6. The switching mechanism according to claim 1, characterized in that, The spiral line contact surface (311) has a profile fillet (R3) between it and the outer peripheral surface of the spiral line portion (31), and the mating surface (61) has a mating fillet (R6) between it and the radial inner surface of the mating portion (6).

7. The switching mechanism according to claim 1, characterized in that, The mating part (6) is a bearing, and the inner ring of the bearing is fixedly sleeved on the radial inner end of the actuating pin (5).

8. The switching mechanism according to claim 1, characterized in that, The mating part (6) is an annular part, which is sleeved on the radial inner end of the actuating pin (5) and can rotate relative to the actuating pin (5).

9. The switching mechanism according to claim 1, characterized in that, The mating part (6) and the actuator (5) are an integral structure.

10. The switching mechanism according to claim 9, characterized in that, The actuator pin (5) is rotatable relative to the actuator unit (4) so ​​that the mating part (6), which is integrally formed with the actuator pin (5), is rotatable relative to the actuator unit (4).

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