CN211975707U - Clutch actuators, clutches and automobiles - Google Patents

Abstract

The utility model relates to a clutch actuator, a clutch and an automobile. The clutch actuator comprises a casing; a worm, one end of the worm is rotatably connected with an output shaft of a motor on the casing; a worm shaft assembly, a worm and a worm shaft assembly The worm gear in the secondary sector gear shaft assembly, the secondary sector gear in the secondary sector gear shaft assembly meshes with the secondary driving gear in the worm gear shaft assembly; tappet, one end of the tappet and the secondary sector gear shaft assembly The crank-rocker arm in the crank-rocker mechanism is hinged, and the other end is connected with the piston in the master cylinder on the housing. The above solution provided by the present application, the torque transmitted by the motor is amplified in the first stage through the meshing of the worm with the worm gear in the worm gear shaft assembly, and then the torque transmitted by the motor is amplified by the meshing of the secondary driving gear and the secondary sector gear. The second stage is amplified, which in turn realizes two-stage deceleration, which makes the clutch have a larger speed ratio, a larger driving force, and a wider range of practicability.

Description

Clutch actuators, clutches and automobiles

technical field

The utility model relates to the technical field of clutches, in particular to a clutch actuator, a clutch and an automobile.

Background technique

With the rapid development of my country'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 practical. AMT: fully electronically controlled mechanical automatic transmission (hereinafter referred to as AMT) , which is upgraded by adding gear selector, clutch actuator and transmission control unit (TCU) to the existing manual transmission. It has the high efficiency and reliability of the traditional manual transmission, while taking into account the fuel economy and maintainability. It is the first choice for commercial vehicles to match automatic transmissions.

The automatic clutch actuator is the core component of AMT and plays an important role in AMT. For a long time, how to precisely control the clutch engagement and disengagement actions has become the key to evaluating the quality of AMT shifting. It not only requires the automatic clutch mechanism to engage and disengage quickly, with little impact, but also requires safe and reliable operation within the vehicle life cycle. At present, most automatic clutch actuators use hydraulic control mechanisms, which are composed of oil solenoid valves, oil cylinders, etc., and this structure is complex and costly. There are also electric cross-axis helical gear self-locking mechanisms, which are less efficient. In the field of heavy commercial vehicles, there are also pneumatic clutch actuators, which are generally composed of cylinders, pistons, and solenoid valves. Due to the limitation of air source and volume, they are less used in passenger cars and light commercial vehicles.

At present, most of the existing AMT automatic clutch mechanisms in the market use a motor to connect the worm gear and worm, and through deceleration and torque increase, the rotary motion of the worm gear is converted into an axial thrust through the crank rocker arm, and the release fork is pushed to complete the forward and backward movement of the release bearing. In order to prevent the motor from being put under pressure during the forward process, the self-locking mechanism with low efficiency is generally used, so it is difficult to achieve the current goal of rapid separation in a short time. Realized in the car field.

Utility model content

Based on this, it is necessary to provide a clutch actuator, a clutch and an automobile to solve the problem that the transmission torque of the general clutch actuator is small in single-stage deceleration.

The utility model provides a clutch actuator, comprising:

case;

a worm, which is rotatably arranged in the casing along its axial direction, and one end of the worm is rotatably connected with the output shaft of the motor on the casing;

a worm gear shaft assembly, the worm gear shaft assembly is fixedly arranged in the housing, and the worm is engaged with the worm gear in the worm gear shaft assembly;

The secondary sector gear shaft assembly, the secondary sector gear shaft assembly is fixedly arranged in the housing, and the secondary sector gear in the secondary sector gear shaft assembly meshes with the secondary driving gear in the worm gear shaft assembly ;

A tappet, the tappet is arranged in the housing, one end of the tappet is hinged with the crank rocker arm in the crank rocker mechanism in the secondary sector gear shaft assembly, and the other end is connected to the housing The piston connection inside the master cylinder.

The above clutch actuator, through the meshing of the worm and the worm gear in the worm gear shaft assembly, amplifies the torque transmitted by the motor in the first stage, and then through the meshing of the secondary drive gear and the secondary sector gear, the torque transmitted by the motor is used as the second stage. Stage amplification, and then achieve two-stage deceleration, so that the clutch has a larger speed ratio, and a larger driving force, the matching AMT torque platform is also wider, and the practicability is wider.

In one embodiment, the worm gear shaft assembly further includes a worm gear shaft, the worm gear shaft is rotatably disposed in the housing along its axial direction, and the axial direction of the worm gear shaft and the axial direction of the worm are perpendicular to each other ;

Both the shaft hole on the worm gear and the shaft hole on the secondary drive gear are in interference fit with the worm gear shaft, and the diameter of the secondary drive gear is smaller than the diameter of the worm gear.

In one of the embodiments, the secondary sector gear shaft assembly further includes a secondary sector gear shaft, the secondary sector gear shaft is arranged in the housing to rotate along its axial direction, and the secondary sector gear shaft The axial direction of the worm gear is parallel to the axial direction of the worm gear; both the shaft hole on the crank rocker arm and the shaft hole on the secondary sector gear are in interference fit with the secondary sector gear shaft.

In one of the embodiments, the secondary sector gear shaft is provided with protrusions along its radial direction, and the protrusions divide the secondary sector gear shaft into spaced first and second rotation shafts;

The sixth bushing hole on the secondary sector gear is matched with the first rotating shaft, and the second bushing hole on the crank rocker arm is matched with the second rotating shaft.

In one embodiment, the crank-rocker mechanism further includes a connecting pin and a cylindrical pin, and one end of the connecting pin is connected to a fifth bushing hole provided in the circumferential direction of the second bushing hole through the cylindrical pin , and the other end is threadedly connected with the tappet.

In one embodiment, two coaxial fifth bushing holes are provided in the circumferential direction of the second bushing hole on the crank arm, and the two fifth bushing holes are along the second axis Axial spacing distribution of sleeve holes;

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 the cylindrical pin passes through all the fifth bushing holes. After the fifth bushing hole is described, it is connected with the first bushing hole.

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;

It also includes a booster assembly, one end of the booster assembly is connected with the housing, and the other end is connected with the third bushing hole.

In one embodiment, the booster assembly 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.

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

It also includes an angle detection component, the angle detection component is connected with the secondary sector gear after passing through the fourth bushing hole.

In one of the embodiments, the angle detection assembly includes an angle sensor, a connecting rod and a sensor fixing plate;

the angle sensor is arranged on the casing;

One end of the sensor fixing plate is rotatably connected with the bottom surface of the angle sensor, and the other end can rotate along the axial direction of the connecting rod;

One end of the connecting rod is fixed on the secondary sector gear, and the other end is rotatably connected with the sensor fixing plate after passing through the fourth bushing hole.

In one of the embodiments, one end of the sensor fixing plate is provided with a sensor rotating shaft, and the sensor fixing plate is rotatably connected to the bottom surface of the angle sensor through the sensor rotating shaft;

After the end of the connecting rod away from the secondary sector gear passes through the fourth bushing hole, it is located in the open end, and is in close contact with the upper arm of the sensor fixing plate.

The present invention further provides a clutch, comprising a clutch body and the clutch actuator according to any one of the descriptions of the embodiments of the present application, wherein the clutch actuator is mounted on the clutch body.

The utility model also provides an automobile, comprising an automobile body and the clutch as described in the embodiments of the present application, and the clutch is mounted on the automobile body.

Description of drawings

1 is a schematic diagram of a clutch actuator in an embodiment of the present invention;

Fig. 2 is the structural schematic diagram of the worm gear shaft assembly in Fig. 1;

FIG. 3 is a schematic structural diagram of the secondary sector gear shaft assembly in FIG. 1;

Fig. 4 is the exploded view of Fig. 3;

FIG. 5 is a schematic structural diagram of the sensor fixing sheet in FIG. 1 .

Detailed ways

In order to facilitate the understanding of the present utility model, the present utility model will be more fully described below with reference to the related drawings. The preferred embodiments of the present utility model are shown in the accompanying drawings. However, the present invention may be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided so that a thorough and complete understanding of the present disclosure is provided.

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 intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill 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. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

As shown in FIG. 1 , in an embodiment of the present invention, a clutch actuator is provided, including a housing 3 , a worm 5 , a worm gear shaft assembly 4 , a secondary sector gear shaft assembly 8 and a tappet 18 , wherein the worm 5 It is arranged in the housing 3 to rotate along its axial direction, and 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, and the worm shaft 5 and the worm gear shaft assembly 4 are rotatably connected. The worm gear 11 in the worm gear is meshed, the secondary sector gear shaft assembly 8 is fixedly arranged in the housing 3, and the secondary sector gear 17 in the secondary sector gear shaft assembly 8 is meshed with the secondary driving gear 12 in the worm gear shaft assembly 4. The rod 18 is arranged in the housing 3, one end of the tappet 18 is hinged with the crank arm 15 in the crank arm mechanism 2 in the secondary sector gear shaft assembly 8, and the other end is connected with the crank arm 15 in the master cylinder 9 on the housing 3. Piston connection.

Specifically, as shown in FIGS. 1-3 , the worm gear shaft assembly 4 in this embodiment further includes a worm gear shaft 13 , and 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 The bearing is connected to the housing 3, and the axial direction of the worm gear shaft 13 and the axial direction of the worm shaft 5 are perpendicular to each other. The shaft holes on the gear 12 are all 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 .

The secondary sector gear shaft assembly 8 also includes a secondary sector gear shaft 16, and 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 through bearings. 3 connection, and the axial direction of the secondary sector gear shaft 16 and the axial direction of the worm gear 11 are parallel to each other, the crank rocker arm 15 and the secondary sector gear 17 are both installed on the secondary sector gear shaft 16, and the shaft on the crank rocker arm 15 Both the hole and the shaft hole on the secondary sector gear 17 are in interference fit with the secondary sector gear shaft 16 , while the secondary sector gear 17 meshes with the secondary driving gear 12 .

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

It should be noted that the above-mentioned matching relationship between the worm gear and the worm gear shaft, the matching relationship between the secondary driving gear and the worm gear shaft, the matching relationship between the crank rocker arm and the secondary sector gear shaft, and the matching between the secondary sector gear and the secondary sector gear shaft. The relationship is only an example, in other alternative solutions, other connection structures can also be used, for example, the worm gear and the worm gear shaft, the secondary drive gear and the worm gear shaft, the crank rocker arm and the secondary sector gear shaft, and the secondary sector gear and the shaft. The secondary sector gear shafts are all connected by welding. This application does not make any special reference to the matching relationship between the worm gear and the worm gear shaft, the matching relationship between the secondary driving gear and the worm gear shaft, the matching relationship between the crank rocker arm and the secondary sector gear shaft, and the matching relationship between the secondary sector gear and the secondary sector gear shaft. limitation, as long as the above structure can achieve the purpose of the present application.

In some embodiments, in order to make the worm gear 11 and the worm 5 self-lock, the unfolded helix angle (not shown in the figure) of the worm 5 in the present application is smaller than the friction angle (not shown in the figure) of the contact between the worm gear and the worm. Since the worm gear 11 and the worm 5 can self-lock, the motor 6 can stop at any position when there is no power supply, thereby reducing the load of the motor 6 and increasing the life of the motor 6 .

In some embodiments, as shown in FIG. 4 , in order to dispose the secondary sector gear 17 and the crank rocker arm 15 on the secondary sector gear shaft 16 at intervals, the present application is provided with the secondary sector gear shaft 16 along its radial direction. The protrusion 1601 divides the secondary sector gear shaft 16 into spaced first rotation shafts 1602 and second rotation shafts 1603; wherein the sixth bushing hole 1702 on the secondary sector gear 17 is an interference fit with the first rotation shaft 1602 , the second bushing hole 1501 on the crank arm 15 is in an interference fit with the second rotating shaft 1603 .

In some embodiments, as shown in FIGS. 3 and 4 , the crank arm mechanism 2 in the present application further includes a connecting pin 14 and a cylindrical pin 19 , wherein one end of the connecting pin 14 passes through the cylindrical pin 19 and the second bushing hole 1501 is connected with the fifth bushing hole 1504 provided in the circumferential direction, and the other end is connected with the tappet 18 by thread.

Further, two coaxial fifth bushing holes 1504 are provided in the circumferential direction of the second bushing hole 1501 on the crank arm 15 , and the two fifth bushing holes 1504 are along the axis of the second bushing hole 1501 Distributed at intervals, a first bushing hole 1401 is provided on one end of the connecting pin 14 close to the fifth bushing hole 1504. During assembly, the first bushing hole 1401 on one end of the connecting pin 14 is placed on the two fifth bushing holes 1401. Between the bushing holes 1504, and then use the cylindrical pin 19 to pass through the fifth bushing hole 1504, and connect with the first bushing hole 1401; at the same time, one end of the connecting pin 14 away from the first bushing hole 1401 is provided with an internal thread ( (not indicated in the figure), the end of the tappet 18 close to the connecting pin 14 is provided with an external thread, and the connecting pin 14 is connected with the external thread on the tappet 18 through the internal thread thereon.

When the crank arm 15 is rotating, the fifth bushing hole 1504 on the crank arm 15 drives the connecting pin 14 through the cylindrical pin 19 to move, and then the connecting pin 14 can drive the tappet 18 to move, thereby realizing the crank arm 15 The rotary motion is changed into a horizontal motion to push the tappet 18 to reciprocate linearly, and the tappet 18 pushes the piston inside the master cylinder 9 to form a high-pressure oil chamber. The clutch diaphragm spring completes the separation action.

Further, as shown in FIG. 4 , 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 blocking piece 1901 is provided on one end of the cylindrical pin 19 . The blocking piece The diameter of 1901 is larger than the diameter of the fifth bushing hole 1504 , the other end of the cylindrical pin 19 is matched with the snap ring 20 , and the outer diameter of the snap ring 20 is also larger than the diameter of the fifth bushing hole 1504 .

Specifically, when reassembling the connecting pin 14 and the crank arm 15, first place the first bushing hole 1401 on the connecting pin 14 between the two fifth bushing holes 1504, and then pass the cylindrical pin 19 therethrough in turn After one fifth bushing hole 1504 , the first bushing hole 1401 and the other fifth bushing hole 1504 , the snap ring 20 is clamped to the end of the cylindrical pin 19 away from the blocking piece 1901 . Since the diameter of the blocking piece 1901 on one end of the cylindrical pin 19 is larger than the diameter of the fifth bushing hole 1504, and the diameter of the other end after being clamped by the snap ring 20 is also larger than the diameter of the fifth bushing hole 1504, the cylindrical pin 19 can It is stably connected to the first bushing hole 1401 and the fifth bushing hole 1504 , thereby preventing the connecting pin 14 from falling off from the crank arm 15 .

In some embodiments, as shown in FIG. 1 , FIG. 3 and FIG. 4 , since the power required when the clutch is disengaged is generally large, and the output power of the motor is insufficient, in order to better linearly push the tappet 18 , the present application also includes a booster assembly, One end of the booster assembly is connected with the housing 3 , and the other end is connected with the third bushing hole 1502 provided in the circumferential direction of the second bushing hole 1501 .

Specifically, the booster 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, wherein the third bushing hole 1502 The second bushing hole 1501 is spaced from the fifth bushing hole 1504 in the circumferential direction of the second bushing hole 1501 . When the output power of the motor 6 is insufficient, the elastic force of the spring 1 can also be transmitted to the connecting pin 14 through the crank arm 15, and then to the tappet 18, so that the clutch can be disengaged together with the force transmitted by the motor 6.

In some embodiments, as shown in FIG. 1 , FIG. 4 and FIG. 5 , in order to conveniently detect the rotation angle of the secondary sector gear 17 , the present application further includes an angle detection component, which passes through the second bushing hole 1501 The fourth bushing hole 1503 provided in the circumferential direction is connected to the secondary sector gear 17 afterward.

Specifically, the angle detection assembly includes an angle sensor 7 , a connecting rod 1701 and a sensor fixing plate 22 , wherein the angle sensor 7 is provided with a screw hole 701 , and the angle sensor 7 is fixed on the housing 3 by bolts passing through the screw hole 701 . One end of the fixed 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 on the secondary sector gear 17, and the other end passes through the fourth bushing hole 1503 Then, it is rotatably connected with the sensor fixing piece 22 .

When the crank rocker arm 15 rotates, the fourth bushing hole 1503 on the crank rocker arm 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 away from the secondary sector gear 17 is rotatably connected to the sensor fixing piece 22, when the connecting rod 1701 moves to the left and the right to the right, it will also drive the sensor fixing piece 22. Move to the left and the latter to the right. Since the bottom surface of the sensor fixing piece 22 is rotatably connected to 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 to the rotation angle of the secondary sector gear 17 .

Further, as shown in FIG. 5 , one end of the sensor fixing piece 22 in the present application is provided with a sensor rotating shaft 2201, and the sensor fixing piece 22 is rotatably connected to the bottom surface of the angle sensor 7 through the sensor rotating shaft 2201; the connecting rod 1701 is far away from the secondary One end of the fan gear 17 is located in the open end 2202 after passing through the fourth bushing hole 1503 , and is in close contact with the upper arm 2203 of the sensor fixing plate 22 .

The present invention also provides a clutch, which includes 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.

The utility model also provides an automobile, which includes an automobile body and a clutch as described in the embodiments of the present application, and the clutch is mounted on the automobile body.

The technical features of the above-described embodiments can be combined arbitrarily. For the sake of brevity, all possible combinations of the technical features in the above-described embodiments are not described. However, as long as there is no contradiction between the combinations of these technical features, All should be regarded as the scope described in this specification.

The above-mentioned embodiments only represent several embodiments of the present utility model, and the descriptions thereof are specific and detailed, but should not be construed as a limitation on the scope of the utility model patent. It should be pointed out that for those of ordinary skill in the art, some modifications and improvements can be made without departing from the concept of the present invention, which all belong to the protection scope of the present invention. Therefore, the protection scope of the patent for this utility model shall be subject to the appended claims.

Claims (13)

1. A clutch actuator, comprising:

a housing (3);

the worm (5) is rotationally arranged in the shell (3) along the axial direction of the worm (5), and one end of the worm (5) is rotationally connected with an output shaft on a motor (6) on the shell (3);

the worm gear shaft assembly (4), the worm gear shaft assembly (4) is fixedly arranged in the shell (3), and the worm (5) is meshed with a worm gear (11) in the worm gear shaft assembly (4);

the two-stage sector gear shaft assembly (8) is fixedly arranged in the shell (3), and a two-stage sector gear (17) in the two-stage sector gear shaft assembly (8) is meshed with a two-stage driving gear (12) in the worm gear shaft assembly (4);

a tappet (18), wherein the tappet (18) is arranged in the housing (3), one end of the tappet (18) is hinged with a crank rocker arm (15) in a crank rocker arm mechanism (2) in the two-stage sector gear shaft assembly (8), and the other end of the tappet (18) is connected with a piston in a master pump (9) on the housing (3).

2. The clutch actuator according to claim 1, wherein the worm gear shaft assembly (4) further comprises a worm gear shaft (13), the worm gear shaft (13) is rotatably disposed in the housing (3) along an axial direction thereof, and an axial direction of the worm gear shaft (13) and an axial direction of the worm (5) are perpendicular to each other;

the shaft hole in the worm wheel (11) and the shaft hole in the secondary driving gear (12) are in interference fit with the worm wheel shaft (13), and the diameter of the secondary driving gear (12) is smaller than that of the worm wheel (11).

3. A clutch actuator according to claim 2, characterized in that the secondary sector shaft assembly (8) further comprises a secondary sector shaft (16), the secondary sector shaft (16) is rotatably disposed in the housing (3) along an axial direction thereof, and an axial direction of the secondary sector shaft (16) and an axial direction of the worm wheel (11) are parallel to each other; and the shaft hole on the crank rocker arm (15) and the shaft hole on the secondary sector gear (17) are in interference fit with the secondary sector gear shaft (16).

4. A clutch actuator according to claim 3 characterised in that the secondary sector shaft (16) is provided with a projection (1601) radially thereof, the projection (1601) dividing the secondary sector shaft (16) into first and second spaced shafts (1602, 1603);

and a sixth shaft sleeve hole (1702) on the two-stage sector gear (17) is matched with the first rotating shaft (1602), and a second shaft sleeve hole (1501) on the crank rocker arm (15) is matched with the second rotating shaft (1603).

5. A clutch actuator according to claim 4, characterized in that the crank arm mechanism (2) further comprises a connecting pin (14) and a cylindrical pin (19), one end of the connecting pin (14) is connected with a fifth shaft sleeve hole (1504) circumferentially arranged in the second shaft sleeve hole (1501) through the cylindrical pin (19), and the other end is threadedly connected with the tappet (18).

6. The clutch actuator according to claim 5, characterized in that the second shaft sleeve hole (1501) on the crank rocker arm (15) is circumferentially provided with two coaxial fifth shaft sleeve holes (1504), and the two fifth shaft sleeve holes (1504) are distributed at intervals along the axial direction of the second shaft sleeve hole (1501);

one end of the connecting pin (14) close to the fifth shaft sleeve holes (1504) is provided with a first shaft sleeve hole (1401), the first shaft sleeve hole (1401) is positioned between the two fifth shaft sleeve holes (1504), and the cylindrical pin (19) penetrates through the fifth shaft sleeve holes (1504) and then is connected with the first shaft sleeve hole (1401).

7. The clutch actuator according to claim 5, characterized in that the second shaft sleeve hole (1501) is further provided with a third shaft sleeve hole (1502) in the circumferential direction, and the third shaft sleeve hole (1502) is arranged at a distance from the fifth shaft sleeve hole (1504);

the power assisting device is characterized by further comprising a power assisting assembly, wherein one end of the power assisting assembly is connected with the shell (3), and the other end of the power assisting assembly is connected with the third shaft sleeve hole (1502).

8. Clutch actuator according to claim 7, wherein the booster assembly comprises a spring (1) and a spring connecting pin (21);

one end of the spring (1) is connected with the inner wall of the shell (3), and the other end of the spring is connected with the third shaft sleeve hole (1502) through the spring connecting pin (21).

9. The clutch actuator according to claim 7, characterized in that a fourth shaft sleeve hole (1503) is further arranged on the second shaft sleeve hole (1501) in the circumferential direction, and the fourth shaft sleeve hole (1503), the third shaft sleeve hole (1502) and the fifth shaft sleeve hole (1504) are respectively spaced;

the angle detection assembly penetrates through the fourth shaft sleeve hole (1503) and then is connected with the second-stage sector gear (17).

10. The clutch actuator as claimed in claim 9, characterized in that the angle detection assembly includes an angle sensor (7), a link (1701), and a sensor fixing plate (22);

the angle sensor (7) is arranged on the shell (3);

one end of the sensor fixing piece (22) is rotatably connected with the bottom surface of the angle sensor (7), and the other end of the sensor fixing piece can rotate along the axial direction of the connecting rod (1701);

one end of the connecting rod (1701) is fixed on the second-stage sector gear (17), and the other end of the connecting rod passes through the fourth shaft sleeve hole (1503) and then is rotatably connected with the sensor fixing plate (22).

11. The clutch actuator according to claim 10, wherein a sensor rotating shaft (2201) is provided at one end of the sensor fixing plate (22), and the sensor fixing plate (22) is rotatably connected to the bottom surface of the angle sensor (7) through the sensor rotating shaft (2201);

one end of the connecting rod (1701) far away from the second-stage sector gear (17) penetrates through the fourth shaft sleeve hole (1503) and then is positioned in an opening end (2202) on an upper arm (2203) on the sensor fixing plate (22) and is tightly attached to the upper arm (2203) of the sensor fixing plate (22).

12. A clutch comprising a clutch body and a clutch actuator according to any of claims 1 to 11, said clutch actuator being mounted on said clutch body.

13. An automobile comprising an automobile body and the clutch of claim 12, wherein the clutch is mounted on the automobile body.

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