A high-strength clutch actuator and its manufacturing method

Abstract

This invention discloses a high-strength clutch actuator and its processing method, belonging to the field of transmission technology. The mechanism includes a base plate; a pump body fixed to the base plate, the pump body being hollow and equipped with a return spring; a piston disposed in the cavity of the pump body, with a self-lubricating bearing at the piston end; a guide sleeve, open at both ends and penetrating between the piston and the middle of the pump body; a push ring is engaged with one end of the piston located in the buffer cavity, the push ring being equipped with a push rod, one end of the push rod extending outward from the buffer cavity and having a force-receiving ring at its end, and a rotatable thrust ring being disposed between the force-receiving ring and the base plate. Through this invention, the thrust ring pushes the force-receiving ring, thereby controlling the sliding of the piston, so that the direction of the thrust force on the piston during sliding is parallel to the central axis, thereby reducing the contact pressure between the outer wall of the piston and the inner wall of the pump body, making the force on the entire piston more uniform.

Description

Technical Field

[0001] This invention relates to a high-strength clutch actuator and its processing method, belonging to the field of transmission technology. Background Technology

[0002] The clutch actuator, as the control component of the clutch, changes the contact or disengagement between the friction disc and the drive shaft by controlling the forward and backward displacement of the piston, thereby realizing gear shifting in a car engine. The release bearing, as part of the actuator, is located on the axial side of the clutch diaphragm spring. When the release bearing moves axially, it pushes the diaphragm spring, causing the clutch to switch to the disengaged state.

[0003] Existing displacement control methods for release bearings include pneumatic, hydraulic, and mechanical drives. Among them, mechanical drives generally use levers to push the piston, which has only one force point. This results in uneven force distribution during piston sliding, leading to increased friction between the piston and the pump body in certain areas and affecting service life. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to provide a high-strength clutch actuator and its processing method, which solves the problem of uneven force on the piston under mechanical drive in the prior art.

[0005] The technical problem to be solved by the present invention is achieved by the following technical solution: a high-strength clutch actuator, including a base plate;

[0006] The pump body is fixed to the base plate, and the pump body is hollow inside and equipped with a return spring.

[0007] A piston is disposed in the cavity of the pump body, and the piston and the pump body form a sealed buffer cavity. A self-lubricating bearing is provided at the end of the piston.

[0008] A guide sleeve, open at both ends and extending through the middle of the piston and the pump body;

[0009] A push ring is engaged with one end of the piston located in the buffer cavity. A push rod is provided on the push ring. One end of the push rod extends outward from the buffer cavity and a force-receiving ring is provided at the end. A rotatable thrust ring is provided between the force-receiving ring and the base plate. The thrust ring is used to push the force-receiving ring to slide.

[0010] By adopting the above technical solution, the friction loss between the piston and the pump body can be reduced, and the service life of the piston can be improved. By using the thrust ring to push the force ring and thus control the sliding of the piston, the direction of the thrust force on the piston during sliding can be parallel to the central axis, thereby reducing the contact pressure between the outer wall of the piston and the inner wall of the pump body, and making the force on the entire piston more uniform.

[0011] The present invention is further configured such that: a plurality of force-receiving guide portions and thrust-guiding portions are respectively provided on the surface of the force-receiving ring and the thrust-guiding ring that abut against each other; the surface of the force-receiving guide portions and the thrust-guiding portions that abut against each other smoothly transitions from one end to the other along the circumferential direction and gradually rises to form an inclined surface one and an inclined surface two; the lower end of the inclined surface one abuts against the higher end of the inclined surface two; when the thrust ring rotates, the lower end of the inclined surface one and the higher end of the inclined surface two gradually move away from each other or move closer to each other.

[0012] By adopting the above technical solution, the thrust required for the axial sliding of the force ring is converted into the radial driving force required for the rotation of the thrust ring. This avoids uneven force distribution on the force ring, ensuring that the piston does not produce a large radial deviation when pushed by the force ring, thereby improving the thrust effect of the piston on the self-lubricating bearing.

[0013] The invention is further configured such that: two arc-shaped grooves are symmetrically arranged on the thrust ring, and the push rod slides through the arc-shaped grooves.

[0014] By adopting the above technical solution, interference can be avoided. The push rod slides through the arc groove, so that the thrust ring and the force ring can rotate on the same axis, preventing the thrust ring from deviating during rotation.

[0015] The invention is further configured such that: the outer ring of the thrust ring is provided with meshing teeth for transmission, the meshing teeth are engaged with a power gear, and the power gear is provided with a driver.

[0016] By adopting the above technical solution, the precise meshing of the meshing teeth and the power gear enables efficient transmission of mechanical power, reduces energy loss, and improves transmission efficiency. Integrating the meshing teeth directly into the outer ring of the thrust ring eliminates the need for additional transmission components, simplifies the overall structure, and saves installation space.

[0017] The present invention is further configured such that: the push ring includes an outer ring connected to the push rod and an inner ring disposed on the outer ring, the outer ring having an inner chamfered surface extending inward, and the inner ring having a snap-fit ​​block extending outward.

[0018] By adopting the above technical solution, the thrust ring can be quickly inserted into the piston, thereby facilitating the installation of the entire actuator and bearings.

[0019] The present invention is further configured such that: the inner ring of the inner ring is provided with a thread, the push ring has a reinforcing ring through the threaded knob, and after the reinforcing ring is turned to the inner ring of the inner ring, its knob end is in contact with the inner guide surface.

[0020] By adopting the above technical solution, the reinforcing ring is pre-installed in the cavity formed at the bottom of the piston before the push ring is inserted into the bottom of the piston. After the push ring is snapped onto the piston, the reinforcing ring knob is turned to the inner ring of the inner ring, thereby improving the fit between the inner ring and the inner wall of the piston, preventing separation from the inner ring during piston sliding, and improving the stability of the entire actuator.

[0021] The present invention is further configured such that: a flexible dust cover is provided between the self-lubricating bearing and the piston, one end of the dust cover is sleeved on the end of the guide sleeve, and the other end is pressed onto the piston through the self-lubricating bearing.

[0022] By adopting the above technical solution, external dust, particles or liquids can be prevented from entering the mating gap between the piston and the guide sleeve, avoiding increased friction or component wear caused by contaminants and extending service life.

[0023] The present invention is further configured such that: a bearing claw is provided between the self-lubricating bearing and the piston, the bearing claw comprising a ring and a plurality of claw plates arranged circumferentially on the ring.

[0024] By adopting the above technical solution, the claw plates are evenly distributed on the ring, forming a multi-point clamping structure to ensure axial fixation between the self-lubricating bearing and the piston, preventing radial displacement of the self-lubricating bearing during movement. Simultaneously, the bearing can be quickly fixed by the bearing clamping mechanism, improving installation efficiency.

[0025] The present invention is further configured such that: the outer ring end edge of the piston is bent inward to form an inner curved groove, and a protective sleeve is engaged through the inner curved groove. The protective sleeve is coaxially arranged with the piston, one end of which is engaged in the inner curved groove, and the other end is attached to the outer wall of the pump body.

[0026] By adopting the above technical solution, the inner curved groove at the end of the piston forms a mechanical limit, and one end of the protective sleeve is firmly inserted to prevent axial movement or circumferential rotation, ensuring long-term operational stability. The other end of the protective sleeve is tightly fitted to the outer wall of the pump body to form a dynamic sealing barrier, preventing external dust, liquid or particles from entering the gap between the piston and the pump body, and protecting the cleanliness of the internal lubricating medium.

[0027] This application also relates to a method for processing a high-strength clutch actuator, specifically including the following steps:

[0028] Step 1: Fix the pump body to the base plate and install the return spring onto the pump body;

[0029] Step 2: After assembling the force ring and the thrust ring, insert the push rod on the force ring into the inner cavity of the pump body through the insertion hole between the base plate and the bottom of the pump body, and fix the push ring at the end;

[0030] Step 3: Place a reinforcing ring on the push ring, and at the same time put a protective sleeve on the outer ring of the pump body. Align the piston with the pump body opening and insert it into the inner cavity of the pump body to form a buffer inner cavity with the pump body.

[0031] Step 4: After attaching the push ring to the piston end, tighten the reinforcing ring thread onto the inner ring using the knob for tightening the reinforcing ring.

[0032] Step 5: Install the guide sleeve and dust cover, and at the same time assemble the self-lubricating bearing to the piston end and fix it with the bearing claws;

[0033] Step 6: Slide the sheath along the pump body toward the outlet end so that the end of the sheath is engaged in the inner groove of the piston.

[0034] By adopting the above technical solution, the assembly of the actuator can be realized quickly, the assembly process of each component can be clearly defined, and wear or assembly interference caused by misalignment can be avoided.

[0035] The beneficial effects of this invention are:

[0036] By employing a thrust ring and a force-receiving ring in tandem, the entire piston is subjected to axial force, reducing frictional losses between the piston and the pump body during piston sliding and extending the service life of the actuator. The rotation of the thrust ring, in conjunction with its mating force-receiving and thrust-receiving guides, converts the rotational power of the thrust ring into the sliding force of the force-receiving ring. Through the cooperation of the force-receiving ring and the thrust ring, a thrust can be directly applied to the circumferential surface of the piston, thereby increasing the piston's force-bearing area and ensuring uniform force distribution.

[0037] By using bearing chucks, self-lubricating bearings can be quickly installed onto the piston's push end, thereby improving the overall installation efficiency of the actuator.

[0038] By using a push ring in conjunction with a reinforcing ring, the connection between the push ring and the piston is made more secure, reducing the risk of the push ring and piston detaching from each other. Attached Figure Description

[0039] Figure 1 This is a schematic diagram of the structure of the present invention;

[0040] Figure 2 This is a partial structural diagram of the present invention;

[0041] Figure 3 This is a partial structural diagram of the piston during sliding according to the present invention;

[0042] Figure 4 This is a three-dimensional structural diagram of the present invention;

[0043] Figure 5 This is a three-dimensional structural diagram of the force-bearing ring and thrust ring assembly of the present invention;

[0044] Figure 6 This is a schematic diagram of the three-dimensional structure of the force ring and the thrust ring in another embodiment of the present invention.

[0045] In the diagram: 1. Base plate; 2. Pump body; 2a. First vertical section; 2b. Angled section; 2c. Second vertical section; 2d. Straight section; 3. Return spring; 4. Piston; 4a. Inner curved groove; 4b. Dustproof groove; 4c. Fitting section; 4d. Abutting section; 4e. Force-bearing section; 4f. Locking section; 4g. Locking surface; 5. Buffer cavity; 6. Self-lubricating bearing; 7. Guide sleeve; 8. Push ring; 8a. Outer ring; 8b. Inner ring; 8c. Inner chamfered surface; 9. Push rod; 10. Force-bearing ring; 10a. Force-bearing guide; 10b. Inclined surface one; 11. Thrust ring; 11a. Thrust guide; 11b. Inclined surface two; 11c. Arc groove; 11d. Meshing teeth; 12. Power gear; 13. Detection assembly; 13a. Base; 13b. Sensing block; 13c. Sensing spring; 13d. Slide groove; 14. Dust cover; 15. Bearing claw; 15a. Circular ring; 15b. Claw plate; 16. Protective sleeve; 17. Reinforcing ring; 18. Anti-friction ring; 19. Sealing ring. Detailed Implementation

[0046] To facilitate a clear understanding of the technical means, creative features, objectives, and effects of this invention, the invention will be further described below in conjunction with specific illustrations.

[0047] like Figure 1 As shown, a high-strength clutch actuator includes a base plate 1, which is fixed by bolts.

[0048] Pump body 2 is fixed on base plate 1. Pump body 2 is hollow inside and is equipped with a return spring 3.

[0049] Piston 4 is located in the cavity of pump body 2. Piston 4 and pump body 2 form a closed buffer cavity 5. A self-lubricating bearing 6 is provided at the end of piston 4.

[0050] Guide sleeve 7, open at both ends and inserted through the middle of piston 4 and pump body 2;

[0051] A push ring 8 is attached to one end of the piston 4 located in the buffer cavity 5. A push rod 9 is provided on the push ring 8. One end of the push rod 9 extends outward from the buffer cavity 5 and a force ring 10 is provided at the end. A rotatable thrust ring 11 is provided between the force ring 10 and the base plate 1. The thrust ring 11 is used to push the force ring 10 to slide.

[0052] In this embodiment, as Figure 2 and Figure 3As shown, the center of the base plate 1 has a through hole for connecting the guide sleeve 7, and the hole diameter is larger than the outer diameter of the guide sleeve 7. Multiple protrusions extending towards the pump body 2 are provided on the base plate 1 around the through hole. Simultaneously, multiple recessed grooves are provided on the side of the pump body 2 that fits against the base plate 1, and these grooves engage with the multiple protrusions on the pump body 2. One end of the pump body 2 for inserting the piston 4 is open, and the other end has a through hole equal to the outer diameter of the guide sleeve 7. At this through hole, a first vertical portion 2a, an oblique portion 2b, a second vertical portion 2c, and a straight portion 2d are sequentially bent outwards from the center of the through hole of the pump body 2. The inner wall of the first vertical portion 2a is in contact with the outer wall of the guide sleeve 7, and a sealing ring 19 is provided between the contact surfaces. The first vertical portion 2a, the oblique portion 2b, and the second vertical portion 2c are bent towards the inner cavity of the pump body 2 to form an internal protrusion. One end of the return spring 3 is engaged with the internal protrusion for fixation.

[0053] like Figure 3 As shown, for piston 4, from the center of piston 4 outwards, there are sequentially arranged a fitting part 4c that fits with guide sleeve 7, a contact part 4d that abuts against self-lubricating bearing 6, and a force-bearing part 4e that fits with pump body 2. A dustproof groove 4b with an opening facing self-lubricating bearing 6 is formed between fitting part 4c and contact part 4d, and a dustproof cover 14 is provided in the dustproof groove 4b. One end of the dustproof cover 14 is sleeved on the end of guide sleeve 7, and the other end is pressed onto piston 4 by self-lubricating bearing 6.

[0054] Specifically, one end of the dust cover 14 is fixedly sleeved on the end of the guide sleeve 7, and the other end is attached to the abutment part 4d and the self-lubricating bearing 6, and is fixedly connected to the abutment part 4d. The middle section of the dust cover 14 is flexible and bends down into the dust cover groove 4b. The entire dust cover 14 automatically changes its bending point as the piston 4 rises and falls.

[0055] In this embodiment, multiple sealing rings 19 and friction-reducing rings 18 are provided on the inner wall surface where the fitting part 4c and the guide sleeve 7 are in contact. The multiple sealing rings 19 form a multi-layer sealing structure, and the friction-reducing layer reduces frictional loss between the piston 4 and the guide sleeve 7, thus improving service life. The dust cover 14 prevents external dust, particles, or liquids from entering the mating gap between the piston 4 and the guide sleeve 7, avoiding increased friction or component wear caused by contaminants and extending service life. When the piston 4 retracts, dragging the self-lubricating bearing 6 away from the friction disc, the outer wall of the guide sleeve 7 near the friction disc is exposed. The dust cover 14 prevents dust from contaminating this section of the guide sleeve 7, ensuring smooth operation between the piston 4 and the guide sleeve 7, reducing frictional loss, and improving service life.

[0056] Furthermore, such as Figure 2 , Figure 3 and Figure 4As shown, a locking part 4f extends outward from the contact end of the abutment part 4d and the self-lubricating bearing 6. The outer end of the locking part 4f is a triangular cone surface and extends outward to the locking surface 4g. The self-lubricating bearing 6 is disposed in the inner ring of the locking part 4f, and a bearing claw 15 is engaged with the outer ring of the self-lubricating bearing 6 and the locking surface 4g. The bearing claw 15 includes a ring 15a that is in contact with the end of the self-lubricating bearing 6 and a plurality of claw plates 15b arranged circumferentially on the ring 15a. One end of the claw plate 15b is fixed to the ring 15a, and the other end extends obliquely and bends towards the inner ring of the ring 15a. Furthermore, there is a movable gap between the bent end and the locking surface 4g. When the piston 4 pushes the self-lubricating bearing 6 to fit against the friction disc, the gap is at its maximum. The end of the claw plate 15b that bends towards the inner ring of the ring 15a separates from the locking surface 4g. When the piston 4 pulls the self-lubricating bearing 6 to separate from the friction disc, the end of the claw plate that bends towards the inner ring of the ring 15a abuts against the locking surface 4g.

[0057] Furthermore, at the end of the abutment portion 4d facing the inner cavity of the pump body 2, a groove is formed by an inward recess to engage the return spring 3. Both ends of the return spring 3 are fixedly connected to the groove formed by the inward recess of the abutment portion 4d and the internal protrusion, respectively.

[0058] In this embodiment, the entire self-lubricating bearing 6 is limited to the abutment portion 4d of the piston 4 by the bearing claw 15, and the gap between the end of the claw plate 15b and the locking surface 4g serves as a transition buffer, so that when the piston 4 is pushed or pulled, the self-lubricating bearing 6 will not immediately and directly contact or separate from the friction disc, thus playing a transition role and allowing the user to have a certain adaptation distance when stepping on the clutch pedal.

[0059] Furthermore, such as Figure 5 As shown, a plurality of force-receiving guides 10a and thrust guides 11a are respectively provided on the surface where the force-receiving ring 10 and the thrust ring 11 abut against each other. The surface where the force-receiving guides 10a and the thrust guides 11a abut against each other smoothly transitions from one end to the other along the circumferential direction and gradually rises to form an inclined surface 10b and an inclined surface 11b. The lower end of the inclined surface 10b abuts against the higher end of the inclined surface 11b. When the thrust ring 11 rotates, the lower end of the inclined surface 10b and the higher end of the inclined surface 11b gradually move away from each other or move closer to each other.

[0060] Specifically, the thrust ring 11 has two symmetrically arranged arc-shaped grooves 11c, and the push rod 9 slides through the arc-shaped grooves 11c. The outer ring of the thrust ring 11 is also provided with meshing teeth 11d for transmission, and the meshing teeth 11d are engaged with the power gear 12, which is equipped with a driver.

[0061] In this embodiment, there are four force-receiving guides 10a and four thrust guides 11a. The force-receiving guides 10a are arranged end-to-end on the force-receiving ring 10, and the thrust guides 11a are arranged end-to-end on the thrust ring 11. When the user depresses the clutch pedal, the driver drives the power gear 12 to rotate, which in turn drives the thrust ring 11 to rotate. This causes the thrust guides 11a to rotate relative to the force-receiving guides 10a, thereby causing the first inclined surface 10b and the second inclined surface 11b to slide relative to each other. The higher end of the second inclined surface 11b moves toward the higher end of the first inclined surface 10b, thus pushing the entire force-receiving ring 10 to slide outward. When the clutch pedal is released, under the action of the return spring 3, the entire force-receiving ring 10 moves back toward the base plate 1, and the thrust ring 11 reverses direction until the lowest end of the first inclined surface 10b re-fits with the highest end of the second inclined surface 11b.

[0062] By cooperating with the force ring 10 and the thrust ring 11, the traditional mechanical pushing method is transformed from point-to-surface contact pushing to surface-to-surface contact pushing, making the force on the entire piston 4 more uniform, the radial offset force on the piston 4 during sliding is smaller, the sliding friction between the piston 4 and the guide sleeve 7 is minimized, the friction loss is lower, and the service life of the entire actuator can be improved.

[0063] In this embodiment, by setting two symmetrical arc-shaped grooves 11c on the force ring 10, the push rod 9 slides through the arc-shaped grooves 11c, which not only avoids interference between the push rod 9 and the arc-shaped grooves 11c, but also limits the maximum rotation angle between the push ring 8 and the thrust ring 11 by setting the maximum curvature of the arc-shaped grooves 11c, thereby preventing the meshing teeth 11d from disengaging from the power gear 12 and improving the compactness and stability of the drive mechanism.

[0064] like Figure 6 As shown, in other embodiments, the drive gear is connected to the worm gear via a connecting shaft, and a drive worm meshes on the worm gear. By configuring the worm gear and drive, the entire drive point position and the arrangement direction of the drive unit can be changed to adapt to installations in different vehicle models. Furthermore, using a worm gear and drive for further refined driving can improve the driving accuracy of the clutch.

[0065] Furthermore, the push ring 8 includes an outer ring 8a connected to the push rod 9 and an inner ring 8b disposed on the outer ring 8a. The outer ring 8a has an inner chamfered surface 8c extending inward, and the inner ring 8b has a snap-fit ​​block extending outward. The inner ring 8b has a threaded inner ring, and the push ring 8 has a reinforcing ring 17 via a threaded knob. After the reinforcing ring 17 is turned to the inner ring 8b, its knob end is in contact with the inner chamfered surface 8c.

[0066] Specifically, the push ring 8 is snapped onto the force-bearing part 4e of the piston 4 by a snap-fit ​​block, and the reinforcement ring 17 is tightened by rotating the inner ring 8b inner ring knob, thereby improving the tightness of the connection between the push ring 8 and the piston 4.

[0067] In this embodiment, the push ring 8 is connected to the force-receiving ring 10 via the push rod 9. The thrust or pull force received by the force-receiving ring 10 is transmitted to the push ring 8 through the push rod 9. After the push ring 8 engages with the piston 4, it can drive the piston 4 to move synchronously. Through the surface contact between the push ring 8 and the piston 4, the point thrust of the push rod 9 is converted into a surface thrust on the push ring 8, thereby making the force uniform during the entire sliding process of the piston 4, and the force direction is parallel to the central axis. This can reduce the friction between the piston 4 and the guide sleeve 7, and reduce the power loss caused by friction.

[0068] Furthermore, such as Figure 3 As shown, the outer ring of piston 4 is bent inward at the end edge to form an inner bend groove 4a. A sleeve 16 is engaged through the inner bend groove 4a. The sleeve 16 is coaxial with piston 4, with one end engaged in the inner bend groove 4a and the other end attached to the outer wall of pump body 2.

[0069] Specifically, the extension end forming the inner curved groove 4a extends from the end edge of the force-bearing part 4e toward the clutch friction disc. After multiple bends, it forms an inner recess and an inner curved groove 4a. The opening of the inner recess faces the clutch friction disc and is located in the inner circle of the inner curved groove 4a. The opening of the inner curved groove 4a faces the opposite direction to the inner recess.

[0070] In this embodiment, by snapping a sheath 16 onto the inner curved groove 4a, the sheath 16 can slide synchronously with the piston 4, thereby preventing external dust from contacting the sliding contact surface of the pump body 2 and the piston 4, keeping the contact surface of the two smooth, and further reducing friction loss.

[0071] Furthermore, it also includes a detection component 13, which includes a base 13a fixed to the base plate 1 and a sensing block 13b fixed to the outer ring of the piston 4. A sliding groove 13d is provided on the base 13a, and the sensing block 13b is slidably engaged in the sliding groove 13d. A sensing spring 13c is provided between the sensing block 13b and the bottom of the sliding groove 13d.

[0072] In this embodiment, the sliding state of the piston 4 during the entire clutch actuator transmission process can be measured in real time by the sensing spring 13c and the sensing block 13b, and the position of the piston 4 relative to the clutch friction disc can be detected.

[0073] This application also relates to a method for processing a high-strength clutch actuator, specifically including the following steps:

[0074] Step 1: Fix the pump body 2 onto the base plate 1, and install the return spring 3 onto the pump body 2;

[0075] Step 2: After assembling the force ring 10 and the thrust ring 11, insert the push rod 9 on the force ring 10 into the inner cavity of the pump body 2 through the insertion hole between the base plate 1 and the bottom of the pump body 2, and fix the push ring 8 at the end.

[0076] Step 3: Place the reinforcing ring 17 on the push ring 8, and at the same time, put the protective sleeve 16 on the outer ring of the pump body 2. Align the piston 4 with the opening of the pump body 2 and insert it into the inner cavity of the pump body 2 to form a buffer inner cavity 5 with the pump body 2.

[0077] Step 4: After attaching the push ring 8 to the end of the piston 4, tighten the reinforcing ring 17 by turning the screw knob onto the inner ring 8b.

[0078] Step 5: Install the guide sleeve 7 and dust cover 14, and at the same time assemble the self-lubricating bearing 6 to the end of the piston 4 and fix it with the bearing claw 15.

[0079] Step 6: Slide the sheath 16 along the pump body 2 toward the outlet end so that the end of the sheath 16 is engaged in the inner bend 4a of the piston 4.

[0080] Specifically, during installation, one end of the return spring 3 is fitted onto the inwardly recessed internal protrusion of the pump body 2. The push ring 8 and reinforcing ring 17 are fitted onto the return spring 3 before the piston 4 is installed, and the push ring 8 is connected to the push rod 9. After the piston 4 is installed onto the pump body 2, the reinforcing ring 17 is first turned into the inner ring of the inner ring 8b. Then, the guide sleeve 7 is inserted into the piston 4, and sealing rings 19 are installed at both ends of the guide sleeve 7 for sealing and clamping. When the piston 4 is inserted into the pump body 2, the groove formed by the inwardly recessed abutment part 4d is aligned with the end of the return spring 3, causing the other end of the return spring 3 to engage in the groove.

[0081] Working principle: During the operation of the actuator, the user depresses the clutch pedal, and the car drive system drives the drive gear 12 to rotate, which in turn drives the thrust ring 11 that meshes with it to rotate. During the rotation of the thrust ring 11, when the force ring 10 is pushed, the contact area between the first inclined surface 10b and the second inclined surface 11b gradually decreases, and the higher end of the second inclined surface 11b gradually moves away from the lower end of the first inclined surface 10b. The push rod 9 slides in the arc groove 11c. The push rod 9 drives the piston 4 to slide through the push ring 8, so that the self-lubricating bearing 6 and the clutch friction disc separate from each other. When the user releases the clutch pedal, the piston 4 is pushed outward from the pump body 2 by the return spring 3, dragging the force ring 10 to reset, causing the thrust ring 11 to rotate in the opposite direction. The contact area between the second inclined surface 11b and the first inclined surface 10b gradually increases until the higher end of the second inclined surface 11b re-fits the lower end of the first inclined surface 10b, and the contact area between the second inclined surface 11b and the first inclined surface 10b reaches its maximum again.

[0082] When the second inclined surface 11b and the first inclined surface 10b are fully in contact, the push rod 9 is in contact with one end of the arc groove 11c. When the contact area between the second inclined surface 11b and the first inclined surface 10b reaches its minimum, the push rod 9 is in contact with the other end of the arc groove 11c. That is, the maximum arc angle of the arc groove 11c is the maximum rotation angle of the thrust ring 11. At this time, the piston 4 retracts the greatest distance into the pump body 2.

[0083] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments, and various changes and modifications can be made without departing from the spirit and scope of the invention, all of which fall within the scope of protection claimed by the present invention. The scope of protection of the present invention is defined by the appended claims and their equivalents.

Claims

1. A high-strength clutch actuator, characterized in that, include: Base plate (1); Pump body (2) is fixed on the base plate (1). The pump body (2) is hollow inside and is provided with a return spring (3). Piston (4) is disposed in the cavity of the pump body (2). The piston (4) and the pump body (2) form a closed buffer cavity (5). A self-lubricating bearing (6) is provided at the end of the piston (4). The guide sleeve (7) is open at both ends and is disposed through the middle of the piston (4) and the pump body (2); The piston (4) is fitted with a push ring (8) at one end in the buffer cavity (5). A push rod (9) is provided on the push ring (8). One end of the push rod (9) extends outward from the buffer cavity (5) and a force ring (10) is provided at the end. A rotatable thrust ring (11) is provided between the force ring (10) and the base plate (1). The thrust ring (11) is used to push the force ring (10) to slide. On the side where the force-receiving ring (10) and the thrust ring (11) abut against each other, a plurality of force-receiving guides (10a) and thrust guides (11a) are respectively provided. The side where the force-receiving guides (10a) and the thrust guides (11a) abut against each other smoothly transitions from one end to the other along the circumferential direction and gradually rises to form an inclined surface one (10b) and an inclined surface two (11b). The lower end of the inclined surface one (10b) abuts against the higher end of the inclined surface two (11b). When the thrust ring (11) rotates, the lower end of the inclined surface one (10b) and the higher end of the inclined surface two (11b) gradually move away from each other or move closer to each other. Two arc-shaped grooves (11c) are symmetrically arranged on the thrust ring (11), and the push rod (9) slides through the arc-shaped grooves (11c).

2. The high-strength clutch actuator according to claim 1, characterized in that: The outer ring of the thrust ring (11) is also provided with meshing teeth (11d) for transmission, and the meshing teeth (11d) are engaged with a power gear (12), and the power gear (12) is provided with a driver.

3. The high-strength clutch actuator according to claim 1, characterized in that: The push ring (8) includes an outer ring (8a) connected to the push rod (9) and an inner ring (8b) disposed on the outer ring (8a). The outer ring (8a) has an inner chamfered surface (8c) extending inward, and the inner ring (8b) has a snap-fit ​​block extending outward.

4. The high-strength clutch actuator according to claim 3, characterized in that: The inner ring (8b) has a threaded inner ring, and the push ring (8) has a reinforcing ring (17) through the threaded knob. After the reinforcing ring (17) is turned to the inner ring (8b), its knob end is in contact with the inner guide surface (8c).

5. A high-strength clutch actuator according to claim 1, characterized in that: A flexible dust cover (14) is provided between the self-lubricating bearing (6) and the piston (4). One end of the dust cover (14) is sleeved on the end of the guide sleeve (7), and the other end is pressed onto the piston (4) through the self-lubricating bearing (6).

6. The high-strength clutch actuator according to claim 1, characterized in that: A bearing claw (15) is provided between the self-lubricating bearing (6) and the piston (4). The bearing claw (15) includes a ring (15a) and a plurality of claw plates (15b) arranged circumferentially on the ring (15a).

7. A high-strength clutch actuator according to claim 1, characterized in that: The outer ring of the piston (4) bends inward at the end edge to form an inner bend groove (4a). A sleeve (16) is engaged through the inner bend groove (4a). The sleeve (16) is coaxially arranged with the piston (4), with one end engaged in the inner bend groove (4a) and the other end attached to the outer wall of the pump body (2).

8. A method for processing a high-strength clutch actuator, specifically applied to a high-strength clutch actuator as described in any one of claims 1-7, characterized in that, Includes the following steps: Step 1: Fix the pump body (2) onto the base plate (1) and install the return spring (3) onto the pump body (2); Step 2: After assembling the force ring (10) and the thrust ring (11), insert the push rod (9) on the force ring (10) into the inner cavity of the pump body (2) through the insertion hole at the bottom of the base plate (1) and the pump body (2), and fix the push ring (8) at the end. Step 3: Place a reinforcing ring (17) on the push ring (8), and at the same time, put a protective sleeve (16) on the outer ring of the pump body (2). Align the piston (4) with the opening of the pump body (2) and insert it into the inner cavity of the pump body (2) to form a buffer inner cavity (5) with the pump body (2). Step 4: After snapping the push ring (8) onto the end of the piston (4), tighten the reinforcing ring (17) by turning the screw on the inner ring (8b); Step 5: Install the guide sleeve (7) and dust cover (14), and at the same time assemble the self-lubricating bearing (6) to the end of the piston (4) and fix it by bearing claw (15); Step 6: Slide the sheath (16) along the pump body (2) toward the outlet end so that the end of the sheath (16) is inserted into the inner bend groove (4a) of the piston (4).

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