Clutch actuator, clutch and vehicle

Abstract

The present invention relates to a clutch actuator, a clutch and a car, wherein the clutch actuator comprises: a housing; a worm, one end of which is rotatably connected to an output shaft on a motor on the housing; a worm shaft assembly, the worm meshing with a worm wheel in the worm shaft assembly; a secondary fan gear shaft assembly, the secondary fan gear in the secondary fan gear shaft assembly meshing with a secondary driving gear in the worm shaft assembly; a tappet, one end of which is hinged to a crank rocker arm in a crank rocker arm mechanism in the secondary fan gear shaft assembly, and the other end is connected to a piston in a master cylinder on the housing. The above scheme provided by the present application amplifies the torque transmitted by the motor in the first stage by meshing the worm with the worm wheel in the worm shaft assembly, and then amplifies the torque transmitted by the motor in the second stage by meshing the secondary driving gear with the secondary fan gear, thereby realizing two-stage deceleration, so that the clutch has a larger speed ratio and a larger driving force, and is more practical.

Description

Technical Field

[0001] The present invention relates to the technical field of clutches, and particularly to a clutch actuator, a clutch and an automobile. Background Art

[0002] With the rapid development of China's automobile industry, the market share of traditional manual transmissions is getting lower and lower. The trend of reducing driver fatigue and completely liberating the left foot is becoming more and more obvious. AMT: fully electronic controlled mechanical automatic transmission (hereinafter referred to as AMT) is upgraded from the existing manual transmission by adding a shift selecting and shifting mechanism, a clutch actuator and a transmission control unit (TCU). It has the high efficiency and reliability of traditional manual transmissions, and at the same time takes into account advantages such as fuel economy and good maintainability. It is the first choice for automatic transmissions supporting commercial vehicles.

[0003] The automatic clutch actuator is the core component of AMT and plays an important role in AMT. For a long time, how to accurately control the engagement and separation actions of the clutch has become the key to evaluating the shifting quality of AMT. It not only requires the automatic clutch mechanism to have fast engagement and separation actions with small impact, but also requires it to work safely and reliably within the whole vehicle life cycle. At present, most automatic clutch actuators adopt hydraulic operating mechanisms, which are composed of oil solenoid valves, oil cylinders, etc. This kind of structure is complex and the cost is relatively high. There are also those that adopt electric cross-axis helical gear self-locking mechanisms, which have low efficiency. In the field of heavy commercial vehicles, pneumatic clutch actuators are also used, which are generally composed of cylinders, pistons and solenoid valves. Due to being restricted by the air source and volume, their applications in passenger cars and light commercial vehicles are relatively small.

[0004] At present, most of the existing AMT automatic clutch mechanisms in the market adopt a structure where a motor is connected to a worm and worm gear. Through speed reduction and torque increase, the rotational motion of the worm gear is converted into an axial thrust through a crank rocker arm to push the release fork to complete the forward and backward movement of the release bearing. In order to prevent the backward movement during the forward movement from bringing pressure to the motor, this kind of mechanism generally adopts a self-locking mechanism with low efficiency. Therefore, it is difficult to achieve the current goal of rapid separation in a short time. At the same time, the single-stage worm and worm gear speed reduction and torque increase without a boost clutch solution are difficult to be realized in the field of large-torque commercial vehicles. Summary of the Invention

[0005] Based on this, in view of the problem that the transmission torque of a general clutch actuator with single-stage reduction is small, it is necessary to provide a clutch actuator, a clutch and an automobile.

[0006] The present invention provides a clutch actuator, comprising:

[0007] A housing;

[0008] A worm, the worm is rotatably arranged in the housing along its axial direction, and one end of the worm is rotatably connected to the output shaft of the motor on the housing;

[0009] A worm gear shaft assembly, which is fixedly arranged in the housing, and the worm is meshed with the worm gear in the worm gear shaft assembly;

[0010] A secondary sector gear shaft assembly, which is fixedly arranged in the housing, and the secondary sector gear in the secondary sector gear shaft assembly is meshed with the secondary driving gear in the worm gear shaft assembly;

[0011] A tappet, which is arranged in the housing. One end of the tappet is hinged to a crank rocker in a crank rocker mechanism in the secondary sector gear shaft assembly, and the other end is connected to a piston in a master cylinder on the housing.

[0012] For the above clutch actuator, the torque transmitted by the motor is amplified at the first stage through the meshing of the worm and the worm gear in the worm gear shaft assembly, and then the torque transmitted by the motor is amplified at the second stage through the meshing of the secondary driving gear and the secondary sector gear, thereby realizing two-stage deceleration, enabling the clutch to have a larger speed ratio and a greater driving force, and the matching AMT torque platform is also wider, with more extensive practicability.

[0013] In one embodiment, the worm gear shaft assembly further includes a worm gear shaft, which is rotatably arranged in the housing along its axial direction, and the axial direction of the worm gear shaft is perpendicular to the axial direction of the worm;

[0014] The shaft hole on the worm gear and the shaft hole on the secondary driving gear are both in interference fit with the worm gear shaft, and the diameter of the secondary driving gear is smaller than the diameter of the worm gear.

[0015] In one embodiment, the secondary sector gear shaft assembly further includes a secondary sector gear shaft, which is rotatably arranged in the housing along its axial direction, and the axial direction of the secondary sector gear shaft is parallel to the axial direction of the worm gear; the shaft hole on the crank rocker and the sixth shaft sleeve hole on the secondary sector gear are both in interference fit with the secondary sector gear shaft.

[0016] In one embodiment, the secondary sector gear shaft is provided with a protrusion along its radial direction, and the protrusion divides the secondary sector gear shaft into a spaced first rotating shaft and a second rotating shaft;

[0017] The sixth shaft sleeve hole on the secondary sector gear is matched with the first rotating shaft, and the second shaft sleeve hole on the crank rocker is matched with the second rotating shaft.

[0018] In one embodiment, the crank rocker mechanism further includes a connecting pin and a cylindrical pin. One end of the connecting pin is connected to a fifth shaft sleeve hole circumferentially arranged on the second shaft sleeve hole through the cylindrical pin, and the other end is threadedly connected to the tappet.

[0019] In one embodiment, two coaxial fifth bushing holes are provided in the circumferential direction of the second bushing hole on the crank rocker arm, and the two fifth bushing holes are spaced apart along the axial direction of the second bushing hole;

[0020] One end of the connecting pin close to the fifth bushing hole is provided with a first bushing hole, the first bushing hole is located between the two fifth bushing holes, and after the cylindrical pin passes through the fifth bushing hole, it is connected to the first bushing hole.

[0021] In one embodiment, a third bushing hole is further provided in the circumferential direction of the second bushing hole, and the third bushing hole is spaced from the fifth bushing hole;

[0022] It further includes an assisting component, one end of the assisting component is connected to the housing, and the other end is connected to the third bushing hole.

[0023] In one embodiment, the assisting component includes a spring and a spring connecting pin; one end of the spring is connected to the inner wall of the housing, and the other end is connected to the third bushing hole through the spring connecting pin.

[0024] In one embodiment, a fourth bushing hole is further provided in the circumferential direction of the second bushing hole, and the fourth bushing hole, the third bushing hole and the fifth bushing hole are respectively spaced apart;

[0025] It further includes an angle detection component, and the angle detection component passes through the fourth bushing hole and is connected to the secondary sector gear.

[0026] In one embodiment, the angle detection component includes an angle sensor, a connecting rod and a sensor fixing piece;

[0027] The angle sensor is arranged on the housing;

[0028] One end of the sensor fixing piece is rotatably connected to the bottom surface of the angle sensor, and the other end can rotate along the axial direction of the connecting rod;

[0029] One end of the connecting rod is fixed on the secondary sector gear, and the other end passes through the fourth bushing hole and is rotatably connected to the sensor fixing piece.

[0030] In one embodiment, a sensor rotating shaft is provided at one end of the sensor fixing piece, and the sensor fixing piece is rotatably connected to the bottom surface of the angle sensor through the sensor rotating shaft;

[0031] The end of the connecting rod far from the secondary sector gear passes through the fourth bushing hole and is located inside the open end, and is in close contact with the upper arm of the sensor fixing piece.

[0032] The present invention also provides a clutch, comprising a clutch body and a clutch actuator as described in any one of the embodiments of the present application, and the clutch actuator is mounted on the clutch body.

[0033] The present invention also provides a vehicle, comprising a vehicle body and the clutch as described in the embodiments of the present application, and the clutch is mounted on the vehicle body. Description of the Drawings

[0034] Figure 1 Schematic diagram of the clutch actuator in an embodiment of the present invention;

[0035] Figure 2 is Figure 1 Schematic diagram of the structure of the worm shaft assembly in

[0036] Figure 3 is Figure 1 Schematic diagram of the structure of the secondary sector gear shaft assembly in

[0037] Figure 4 is Figure 3 Exploded view of

[0038] Figure 5 is Figure 1 Schematic diagram of the structure of the sensor fixing piece in Detailed Description of the Invention

[0039] For the convenience of understanding the present invention, the present invention will be described more comprehensively below with reference to the relevant drawings. The preferred embodiments of the present invention are shown in the drawings. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, these embodiments are provided so that the understanding of the disclosure of the present invention is more thorough and comprehensive.

[0040] It should be noted that when an element is referred to as being "fixed to" another element, it can be directly on the other element or there may also be an intermediate element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or there may be an intermediate element at the same time.

[0041] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the technical field to which the present invention belongs. The terms used in the description of the present invention herein are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0042] Such as Figure 1As shown in the figure, in an embodiment of the present invention, a clutch actuator is provided, which includes a housing 3, a worm 5, a worm gear shaft assembly 4, a secondary sector gear shaft assembly 8, and a tappet 18. The worm 5 is rotatably arranged in the housing 3 along its axial direction. One end of the worm 5 is rotatably connected to the output shaft of the motor 6 on the housing 3. The worm gear shaft assembly 4 is fixedly arranged in the housing 3. The worm 5 meshes with the worm gear 11 in the worm gear shaft assembly 4. The secondary sector gear shaft assembly 8 is fixedly arranged in the housing 3. The secondary sector gear 17 in the secondary sector gear shaft assembly 8 meshes with the secondary driving gear 12 in the worm gear shaft assembly 4. The tappet 18 is arranged in the housing 3. One end of the tappet 18 is hinged to the crank rocker 15 in the crank rocker mechanism 2 in the secondary sector gear shaft assembly 8, and the other end is connected to the piston in the master cylinder 9 on the housing 3.

[0043] Specifically, as Figure 1-3 shown, the worm gear shaft assembly 4 in this embodiment further includes a worm gear shaft 13. The worm gear shaft 13 is rotatably arranged in the housing 3 along its axial direction, that is, both ends of the worm gear shaft 13 are connected to the housing 3 through bearings, and the axial direction of the worm gear shaft 13 is perpendicular to the axial direction of the worm 5. The worm gear 11 and the secondary driving gear 12 are both installed on the worm gear shaft 13, and the shaft holes on the worm gear 11 and the shaft holes on the secondary driving gear 12 are both in interference fit with the worm gear shaft 13. At the same time, the diameter of the secondary driving gear 12 is smaller than the diameter of the worm gear 11.

[0044] The secondary sector gear shaft assembly 8 further includes a secondary sector gear shaft 16. The secondary sector gear shaft 16 is rotatably arranged in the housing 3 along its axial direction, that is, both ends of the secondary sector gear shaft 16 are connected to the housing 3 through bearings, and the axial direction of the secondary sector gear shaft 16 is parallel to the axial direction of the worm gear 11. The crank rocker 15 and the secondary sector gear 17 are both installed on the secondary sector gear shaft 16, and the shaft holes on the crank rocker 15 and the sixth bushing holes 1702 on the secondary sector gear 17 are both in interference fit with the secondary sector gear shaft 16. At the same time, the secondary sector gear 17 meshes with the secondary driving gear 12.

[0045] The motor 6 is fixed to the housing 3 by bolts. Further, the motor 6 can be a DC brushed motor. After the motor 6 is fixed, the output shaft of the motor 6 passes through the housing 3 and is rotatably connected to a worm 5 provided in the housing 3. One end of the worm 5 away from the output shaft of the motor 6 is rotatably provided in the housing 3 through a bearing. When the motor 6 rotates forward (in the counterclockwise rotation direction facing the motor shaft), the output shaft of the motor 6 drives the worm 5 to rotate. Since the worm 5 meshes with a worm gear 11 in a worm gear shaft assembly 4 fixedly provided in the housing 3, when the worm 5 rotates, it will also drive the worm gear 11 to rotate. Since the worm gear 11 is in interference fit with the worm gear shaft 13, when the worm gear 11 rotates, the worm gear shaft 13 will also rotate synchronously. Further, since a secondary driving gear 12 is also in interference fit with the worm gear shaft 13, when the worm gear shaft 13 rotates, the secondary driving gear 12 will also rotate synchronously. Since a secondary sector gear 17 meshes with the secondary driving gear 12, when the secondary driving gear 12 rotates, it will also drive the secondary sector gear 17 to rotate. Since the secondary sector gear 17 is in interference fit with a secondary sector gear shaft 16, when the secondary sector gear 17 rotates, the secondary sector gear shaft 16 will also rotate synchronously. Since a crank rocker 15 is also in interference fit with the secondary sector gear shaft 16, when the secondary sector gear shaft 16 rotates, the crank rocker 15 will also rotate synchronously. The crank rocker 15 then converts the rotational motion into a horizontal motion to push a tappet 18 to reciprocate linearly. The tappet 18 then pushes a piston inside a master cylinder 9 to form a high-pressure oil chamber. The high-pressure oil is injected into a transmission release bearing through a metal pipe 10, and finally pushes a diaphragm spring of a dry clutch on an engine flywheel to complete a separation action.

[0046] It should be noted that the fitting relationships between the worm gear and the worm gear shaft, between the secondary driving gear and the worm gear shaft, between the crank rocker and the secondary sector gear shaft, and between the secondary sector gear and the secondary sector gear shaft are only examples. In other alternative solutions, other connection structures can also be adopted. For example, the worm gear and the worm gear shaft, the secondary driving gear and the worm gear shaft, the crank rocker and the secondary sector gear shaft, and the secondary sector gear and the secondary sector gear shaft are all connected by welding. This application does not impose special restrictions on the fitting relationships between the worm gear and the worm gear shaft, between the secondary driving gear and the worm gear shaft, between the crank rocker and the secondary sector gear shaft, and between the secondary sector gear and the secondary sector gear shaft, as long as the above structures can achieve the purpose of this application.

[0047] In some embodiments, in order to enable the worm gear 11 and the worm 5 to be self-locking, the developed helix angle (not indicated in the figure) of the worm 5 in this application is smaller than the friction angle (not indicated in the figure) of the contact between the worm gear and the worm. Since the worm gear 11 and the worm 5 can be self-locking, when the motor 6 has no power supply, it can also stop at any position, thereby reducing the load on the motor 6 and increasing the service life of the motor 6.

[0048] In some embodiments, such asFigure 4 As shown, in order to arrange the secondary sector gear 17 and the crank rocker arm 15 at intervals on the secondary sector gear shaft 16, a protrusion 1601 is provided on the secondary sector gear shaft 16 along its radial direction. The protrusion 1601 divides the secondary sector gear shaft 16 into a spaced first rotating shaft 1602 and a second rotating shaft 1603; among them, the sixth bushing hole 1702 on the secondary sector gear 17 is in interference fit with the first rotating shaft 1602, and the second bushing hole 1501 on the crank rocker arm 15 is in interference fit with the second rotating shaft 1603.

[0049] In some embodiments, as Figure 3 and Figure 4 shown, the crank rocker arm mechanism 2 in the present application further includes a connecting pin 14 and a cylindrical pin 19. One end of the connecting pin 14 is connected to a fifth bushing hole 1504 circumferentially provided on the second bushing hole 1501 through the cylindrical pin 19, and the other end is threadedly connected to the tappet 18.

[0050] Furthermore, two coaxial fifth bushing holes 1504 are circumferentially provided on the second bushing hole 1501 of the above-mentioned crank rocker arm 15. The two fifth bushing holes 1504 are spaced along the axial direction of the second bushing hole 1501. A first bushing hole 1401 is provided at one end of the connecting pin 14 close to the fifth bushing hole 1504. During assembly, the first bushing hole 1401 at one end of the connecting pin 14 is placed between the two fifth bushing holes 1504, and then the cylindrical pin 19 passes through the fifth bushing hole 1504 and is connected to the first bushing hole 1401; at the same time, an internal thread (not indicated in the figure) is provided at the end of the connecting pin 14 away from the first bushing hole 1401, and an external thread is provided at the end of the tappet 18 close to the connecting pin 14. The connecting pin 14 is threadedly connected to the external thread on the tappet 18 through the internal thread on it.

[0051] When the crank rocker arm 15 rotates, the fifth bushing hole 1504 on the crank rocker arm 15 drives the connecting pin 14 to move through the cylindrical pin 19. Furthermore, the connecting pin 14 can drive the tappet 18 to move, thus realizing that the crank rocker arm 15 changes the rotational motion into a horizontal motion to push the tappet 18 to reciprocate linearly. The tappet 18 then pushes the piston inside the master cylinder 9 to form a high-pressure oil chamber. The high-pressure oil is injected into the transmission release bearing through the metal pipe 10, and finally the dry clutch diaphragm spring on the engine flywheel is pushed to complete the separation action.

[0052] Furthermore, as Figure 4 shown, in order to prevent the first bushing hole 1401 on the connecting pin 14 from falling off between the two fifth bushing holes 1504, a retaining piece 1901 is provided at one end of the cylindrical pin 19. The diameter of the retaining piece 1901 is larger than the diameter of the fifth bushing hole 1504. The other end of the cylindrical pin 19 is engaged with a snap ring 20, and the outer diameter of the snap ring 20 is also larger than the diameter of the fifth bushing hole 1504.

[0053] Specifically, when reassembling the connecting pin 14 and the crank rocker arm 15, first place the first bushing hole 1401 on the connecting pin 14 between the two fifth bushing holes 1504. Then, pass the cylindrical pin 19 through one of the fifth bushing holes 1504, the first bushing hole 1401, and the other fifth bushing hole 1504 in sequence, and then use a snap ring 20 to clamp one end of the cylindrical pin 19 away from the retaining plate 1901. Since the diameter of the retaining plate 1901 at one end of the cylindrical pin 19 is larger than the diameter of the fifth bushing hole 1504, and the diameter after clamping at the other end by the snap ring 20 is also larger than the diameter of the fifth bushing hole 1504, therefore, the cylindrical pin 19 can be stably connected to the first bushing hole 1401 and the fifth bushing hole 1504, thereby preventing the connecting pin 14 from falling off the crank rocker arm 15.

[0054] In some embodiments, such as Figure 1 , Figure 3 and Figure 4 shown, since the power required during clutch disengagement is generally very large and the motor output power is insufficient, in order to better linearly push the tappet 18, the present application further includes an assist component. One end of the assist component is connected to the housing 3, and the other end is connected to the third bushing hole 1502 circumferentially arranged on the second bushing hole 1501.

[0055] Specifically, the assist component includes a spring 1 and a spring connecting pin 21. One end of the spring 1 is connected to the inner wall of the housing 3, and the other end is connected to the third bushing hole 1502 through the spring connecting pin 21, wherein the third bushing hole 1502 and the fifth bushing hole 1504 are arranged at intervals in the circumferential direction of the second bushing hole 1501. When the power output by the motor 6 is insufficient, the elastic force of the spring 1 can also be transmitted to the connecting pin 14 through the crank rocker arm 15, and then transmitted to the tappet 18, so as to push the clutch to disengage together with the force transmitted by the motor 6.

[0056] In some embodiments, such as Figure 1 , Figure 4 and Figure 5 shown, in order to facilitate detecting the rotation angle of the secondary sector gear 17, the present application further includes an angle detection component. The angle detection component passes through the fourth bushing hole 1503 circumferentially arranged on the second bushing hole 1501 and is then connected to the secondary sector gear 17.

[0057] Specifically, the angle detection component includes an angle sensor 7, a connecting rod 1701, and a sensor fixing piece 22. A screw hole 701 is provided on the angle sensor 7, and the angle sensor 7 is fixed to the housing 3 by a bolt passing through the screw hole 701. One end of the sensor fixing piece 22 is rotatably connected to the bottom surface of the angle sensor 7, and the other end can rotate along the axial direction of the connecting rod 1701. One end of the connecting rod 1701 is fixed to the secondary sector gear 17, and the other end passes through the fourth bushing hole 1503 and is rotatably connected to the sensor fixing piece 22. When the crank rocker 15 rotates, the fourth bushing hole 1503 on the crank rocker 15 rotates synchronously. Since the connecting rod 1701 passes through the fourth bushing hole 1503, when the fourth bushing hole 1503 rotates, it will also drive the connecting rod 1701 to rotate. Since the end of the connecting rod 1701 far from the secondary sector gear 17 is rotatably connected to the sensor fixing piece 22, when the connecting rod 1701 moves left or right, it will also drive the sensor fixing piece 22 to move left or right. Since the sensor fixing piece 22 is rotatably connected to the bottom surface of the angle sensor 7, when the sensor fixing piece 22 rotates, the angle sensor 7 can detect the rotation angle of the sensor fixing piece 22 and further detect the rotation angle of the secondary sector gear 17.

[0058] Furthermore, as Figure 5 shown, a sensor rotating shaft 2201 is provided at one end of the sensor fixing piece 22 in the present application, and the sensor fixing piece 22 is rotatably connected to the bottom surface of the angle sensor 7 through the sensor rotating shaft 2201; after the end of the connecting rod 1701 far from the secondary sector gear 17 passes through the fourth bushing hole 1503, it is located within the open end 2202 and is in close contact with the upper arm 2203 of the sensor fixing piece 22.

[0059] The present invention also provides a clutch, including a clutch body and a clutch actuator according to any one of the embodiments described in the present application, and the clutch actuator is installed on the clutch body.

[0060] The present invention also provides an automobile, including an automobile body and a clutch according to the embodiment described in the present application, and the clutch is installed on the automobile body.

[0061] The technical features of the above-described embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope described in this specification.

[0062] The above-described embodiments merely represent several implementation manners of the present invention. The description thereof is relatively specific and detailed, but it should not be construed as a limitation to the scope of the invention patent. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several modifications and improvements can still be made, and these all fall within the protection scope of the present invention. Therefore, the protection scope of the present invention patent shall be subject to the appended claims.

Claims

1. A clutch actuator, characterized in that, Comprising: A housing (3); A worm (5) which is rotationally arranged in the housing (3) along its axial direction, and one end of the worm (5) is rotationally connected to the output shaft of a motor (6) on the housing (3); A worm gear shaft assembly (4) which is fixedly arranged in the housing (3), and the worm (5) meshes with a worm gear (11) in the worm gear shaft assembly (4); A secondary sector gear shaft assembly (8) which is fixedly arranged in the housing (3), and a secondary sector gear (17) in the secondary sector gear shaft assembly (8) meshes with a secondary driving gear (12) in the worm gear shaft assembly (4); A tappet (18) which is arranged in the housing (3), one end of the tappet (18) is hinged to a crank rocker (15) in a crank rocker mechanism (2) in the secondary sector gear shaft assembly (8), and the other end is connected to a piston in a master cylinder (9) on the housing (3); The secondary sector gear shaft assembly (8) further includes a secondary sector gear shaft (16), and a second bushing hole (1501) on the crank rocker (15) and a sixth bushing hole (1702) on the secondary sector gear (17) are both in interference fit with the secondary sector gear shaft (16); The second bushing hole (1501) of the crank rocker (15) has a fifth bushing hole (1504), a third bushing hole (1502) and a fourth bushing hole (1503) which are arranged at intervals in the circumferential direction. The clutch actuator further includes an angle detection assembly. The angle detection assembly includes an angle sensor (7), a connecting rod (1701) and a sensor fixing piece (22); the angle sensor (7) is arranged on the housing (3); one end of the sensor fixing piece (22) is rotationally connected to the bottom surface of the angle sensor (7), and the other end can rotate along the axial direction of the connecting rod (1701); one end of the connecting rod (1701) is fixed on the secondary sector gear (17), and after passing through the fourth bushing hole (1503), the other end is rotationally connected to the sensor fixing piece (22); The crank rocker mechanism (2) further includes a connecting pin (14) and a cylindrical pin (19). One end of the connecting pin (14) is connected to a fifth bushing hole (1504) arranged in the circumferential direction of the second bushing hole (1501) through the cylindrical pin (19), and the other end is threadedly connected to the tappet (18); It further includes an assisting component, one end of the assisting component is connected to the housing (3), and the other end is connected to the third bushing hole (1502).

2. The clutch actuator according to claim 1, wherein The worm gear shaft assembly (4) further includes a worm gear shaft (13) which is rotationally arranged in the housing (3) along its axial direction, and the axial direction of the worm gear shaft (13) is perpendicular to the axial direction of the worm (5); A shaft hole on the worm gear (11) and a shaft hole on the secondary driving gear (12) are both in interference fit with the worm gear shaft (13), and the diameter of the secondary driving gear (12) is smaller than the diameter of the worm gear (11).

3. The clutch actuator according to claim 2, characterized in that, The secondary sector gear shaft (16) is rotationally arranged in the housing (3) along its axial direction, and the axial direction of the secondary sector gear shaft (16) is parallel to the axial direction of the worm gear (11).

4. The clutch actuator according to claim 3, characterized in that, A protrusion (1601) is arranged on the secondary sector gear shaft (16) along its radial direction, and the protrusion (1601) divides the secondary sector gear shaft (16) into a spaced first rotating shaft (1602) and a second rotating shaft (1603); The sixth bushing hole (1702) on the secondary sector gear (17) cooperates with the first rotating shaft (1602), and the second bushing hole (1501) on the crank rocker arm (15) cooperates with the second rotating shaft (1603).

5. The clutch actuator according to claim 4, characterized in that, Two coaxial fifth bushing holes (1504) are arranged on the circumference of the second bushing hole (1501) on the crank rocker arm (15), and the two fifth bushing holes (1504) are spaced along the axial direction of the second bushing hole (1501); A first bushing hole (1401) is arranged at one end of the connecting pin (14) close to the fifth bushing hole (1504), the first bushing hole (1401) is located between the two fifth bushing holes (1504), and after the cylindrical pin (19) passes through the fifth bushing hole (1504), it is connected to the first bushing hole (1401).

6. The clutch actuator according to claim 1, characterized in that, The boosting assembly includes a spring (1) and a spring connecting pin (21); One end of the spring (1) is connected to the inner wall of the housing (3), and the other end is connected to the third bushing hole (1502) through the spring connecting pin (21).

7. The clutch actuator according to claim 6, characterized in that, A sensor rotating shaft (2201) is arranged at one end of the sensor fixing piece (22), and the sensor fixing piece (22) is rotationally connected to the bottom surface of the angle sensor (7) through the sensor rotating shaft (2201); One end of the connecting rod (1701) far from the secondary sector gear (17) passes through the fourth bushing hole (1503) and is located in the open end (2202), and is in close contact with the upper arm (2203) of the sensor fixing piece (22).

8. A clutch, characterized in that, It includes a clutch body and the clutch actuator according to any one of claims 1-7, and the clutch actuator is installed on the clutch body.

9. A vehicle, characterized in that, It includes an automobile body and the clutch according to claim 8, and the clutch is installed on the automobile body.

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