Clutch system and its clutch actuation device

Abstract

Clutch actuation device comprising: a release bearing (10), a preload spring (11) and a clutch central release bearing (12); The clutch release bearing (12) comprises a slave cylinder housing (13), the release bearing (10) is mounted on an axial end of the slave cylinder housing (13) on the outside and can move axially relative to the slave cylinder housing (13), the preload spring (11) is mounted on the outside of the slave cylinder housing (13) and provides axial preload to the release bearing (10); A sealing cap (14) is attached radially outside the preload spring (11) on the outside of the slave cylinder housing (13) in a ring-like manner; the sealing cap is attached in an axial direction to the release bearing (10) and to the other axial end of the slave cylinder housing (13); characterized in that the sealing cap (14) comprises a movable part (15) and a stationary part (16) which are assembled together as a set, the inner diameter of the part of the movable part (15) and stationary part (16) which is located on the radial outside is larger than the outer diameter of the other part; the movable part (15) is synchronously axially movable on the release bearing (10), the immovable part (16) is attached to the other axial end of the slave cylinder housing (13), the movable part (15) and the immovable part (16) have a continuous sealed overlap section in the radial direction.

Description

field of technology

[0001] This invention relates to the technical field of clutches and, in particular, to a clutch system and its clutch actuation device. State of the art

[0002] Current clutch systems include: a clutch comprising a diaphragm spring; a clutch actuation device for controlling the disengagement and engagement of the clutch. With reference to Fig. 1 and Fig. 2 the clutch actuation device: a release bearing 1 and a clutch concentric slave cylinder (CSC) 2. The clutch concentric slave cylinder 2 comprises a slave cylinder housing 3, the release bearing 1 is mounted externally on an axial end A of the slave cylinder housing 3 and can move axially relative to the slave cylinder housing 3, and the release bearing 1 rests against each other in the axial direction with a diaphragm spring (not shown in the figure). A preload spring 4 is provided between the slave cylinder housing 3 and the release bearing 1, wherein the preload spring 4 provides axial preload for the release bearing 1.

[0003] A seal cap 5 is attached to the outside of the preload spring 4. The seal cap 5 is axially fixed to the release bearing 1 and the other axial end B of the slave cylinder housing 3. The seal cap 5 performs a sealing function for the slave cylinder housing 3 and insulates against external dust and water contamination. The current seal cap 5 is shaped like a corrugated tube, and when the release bearing 1 moves axially away from the diaphragm spring to compress the preload spring 4, the seal cap 5 is compressed and deformed, increasing its outer diameter. As the outer diameter increases, the seal cap 5 may collide with the adjacent clutch housing. Due to prolonged collision, the seal cap 5 wears and may even come off due to collision, resulting in a deterioration in sealing performance and a reduction in service life.

[0004] Further prior art is disclosed in DE 84 22 431 U1, US 4 869 355 A and DE 10 2004 032 038 A1. Subject of the invention

[0005] The problem solved by this invention is that in current clutch actuators, as the outer diameter of the seal cap increases, it may abut against the adjacent clutch housing. The abutment over a long period of time may wear out the seal cap and may even come off due to the abutment, resulting in a deterioration of the sealing performance and a reduction in service life.

[0006] To solve the above problem, this invention provides a clutch actuating device comprising: a release bearing, a preload spring, and a clutch release mechanism; wherein the clutch release mechanism comprises a slave cylinder housing, the release bearing is mounted externally on one axial end of the slave cylinder housing and can move axially relative to the slave cylinder housing, the preload spring is mounted externally on the slave cylinder housing and axially preloads the release bearing; a sealing cap is mounted externally on the slave cylinder housing in a ring-like manner, the sealing cap is fastened in the axial direction to the release bearing and to the other axial end of the slave cylinder housing;the sealing cap comprises a movable part and a stationary part which are mounted together as a set, the inner diameter of the part of the movable part and the stationary part which is located on the radially outer side is larger than the outer diameter of the other part; the movable part is synchronously attached to the release bearing in an axially movable manner, the stationary part is attached to the other axial end of the slave cylinder housing, the movable part and the stationary part have a sealed overlap part continuously in the radial direction;

[0007] Optionally, the movable part serves as a spring support and comprises: a body which is fastened to the release bearing and carries one end of the preload spring, and a sealing part which has an overlap part with the stationary part in the radial direction.

[0008] Optionally, the movable part is placed on the outside of the immovable part.

[0009] Optionally, the sealing part is formed by the body extending in the axial direction.

[0010] Optionally, a radial gap is provided between the sealing cap and the slave cylinder housing to support the preload spring.

[0011] Optionally, a sealing ring is provided between the movable part and the immovable part in the overlap part.

[0012] Optionally, one of the two radially opposite circumferential surfaces of the movable part and the stationary part is provided with an annular groove to accommodate the sealing ring.

[0013] The number of sealing rings can be one or a plurality arranged with a gap in the axial direction.

[0014] This invention also provides a clutch system comprising one of the above-mentioned clutch actuating devices.

[0015] Compared to the prior art, the technical concept of this invention has the following advantages: Since the inner diameter of the radially outer portion of the movable part and the fixed part is larger than the outer diameter of the other part, there is no problem of mutual compression between the movable part and the fixed part when the movable part moves axially relative to the fixed part in the radial direction, and the radially outer portion cannot deform or move outward in the radial direction. This prevents interference between the seal cap and the adjacent coupling housing. The seal cap features good stability, extended service life, and improved sealing performance. Furthermore, the radially sealed overlap portion between the movable part and the fixed part ensures that the seal cap has good sealing performance. Description of the drawings Fig. 1 shows a spatial representation of a clutch actuating device according to the prior art. Fig. 2 shows an axial sectional view of a clutch actuating device according to the prior art. Fig. 3 shows a spatial representation of a clutch actuating device of a concrete embodiment of this invention. Fig. 4 shows an axial sectional view of a clutch actuating device of a concrete embodiment of this invention when the release bearing is in the left limit position. Fig. 5 shows an axial sectional view of a clutch actuating device of a concrete embodiment of this invention when the release bearing is in the right limit position. Concrete embodiments

[0016] For a clearer and easier understanding of the above-described objects, features and advantages of this invention, the specific embodiments of this invention are described in detail below in conjunction with the drawings.

[0017] With reference to Fig. 3 and Fig. 4, this invention provides a clutch actuation device comprising: a release bearing 10, a preload spring 11, and a clutch central releaser 12; wherein the clutch central releaser 12 comprises a slave cylinder housing 13, the release bearing 10 is mounted externally on an axial end C of the slave cylinder housing 13 and can move axially relative to the slave cylinder housing 13, the preload spring 11 is mounted externally on the slave cylinder housing 13 and axially preloads the release bearing 10; a sealing cap 14 is mounted annularly on the outside of the slave cylinder housing 13, the sealing cap 14 is fastened in the axial direction to the other axial end D of the release bearing 10 and the slave cylinder housing 13; wherein the sealing cap 14 comprises a movable part 15 and a fixed part 16 which are assembled together as a set, the inner diameter of the part of the movable part 15 and the fixed part 16 which is located on the radially outer side is larger than the outer diameter of the other part; the movable part 15 is fastened synchronously to the release bearing 10 in an axially movable manner, the immovable part 16 is fastened to the other axial end D of the slave cylinder housing 13, the movable part 15 and the immovable part 16 have a sealed overlap part throughout in the radial direction.

[0018] Compared with the prior art, the present concept has the following advantages: Since the inner diameter of the part of the movable part 15 and the fixed part 16 located on the radially outer side is larger than the outer diameter of the other part, the problem of mutual compression between the movable part 15 and the fixed part 16 does not arise when the movable part 15 moves axially relative to the fixed part 16 in the radial direction, and the part located on the radially outer side cannot deform or move outward in the radial direction. In this way, collisions between the sealing cap 14 and the adjacent clutch housing can be avoided. The sealing cap 14 is characterized by good stability, an extended service life, and improved sealing performance.Furthermore, the radially sealed overlap part between the movable part 15 and the stationary part 16 ensures that the sealing cap 14 has good sealing performance.

[0019] It should be explained that the axial end C of the slave cylinder housing 13 is the end closest to the clutch (not shown in the figure), the other axial end D is the end remote from the clutch, and the release bearing 10 axially abuts the clutch diaphragm spring. The side of the sealing cap 14 remote from the clutch on the release bearing 10 seals the slave cylinder housing 13 radially and axially and insulates it against external dust and water.

[0020] With reference to Fig. 4, when the release bearing 10 is in the left limit position, the length of the preload spring 11 is maximum, and an overlap part E1 is present in the radial direction between the movable part 15 and the stationary part 16. In connection with reference to Fig. 5, when the release bearing 10 is in the right limit position, the preload spring 11 is compressed to its maximum length, and an overlap portion E2 with a relatively large surface area is present in the radial direction between the movable portion 15 and the fixed portion 16. One aspect is that the overlap portions E1 and E2 ensure the sealing performance of the seal cap 14. Another aspect is that, in the process of moving the release bearing 10 between the left limit position and the right limit position, the movable portion 15 moves axially relative to the fixed portion 16, continuously maintaining an overlap portion with an area between E1 and E2 between the two, and effectively maintaining the sealing performance of the seal cap 14.In specific applications, the axial dimensions of the movable part 15 and the fixed part 16 can be adjusted according to requirements to ensure that both maintain an overlap portion throughout.

[0021] In comparison to the prior art, this concept also dispenses with a sealing cap in the form of a corrugated tube, thereby reducing the radial dimensions of the sealing cap 14, thus reducing the collisions that may occur between the sealing cap 14 and the adjacent coupling housing.

[0022] The overlap portion between the movable part 15 and the fixed part 16 includes a seal ring 17. Compared with the contact seal of the movable part 15 and the fixed part 16, the seal ring 17 prevents contact wear from occurring between the movable part 15 and the fixed part 16. The seal ring 17 is compressed and deformed in the radial direction by the movable part 15 and the fixed part 16 and can have closer contact with the movable part 15 and the fixed part 16, resulting in better sealing performance. Of the two radially opposite circumferential surfaces of the movable part 15 and the fixed part 16, one circumferential surface is provided with an annular groove to receive the seal ring 17.For example, an annular groove 18 is provided on the peripheral surface of the stationary part 16, which is radially opposite the movable part 15. The sealing ring 17 is provided in the annular groove 18 and is exposed to the outside to form a contact seal with the movable part 15. The annular groove 18 serves to secure the sealing ring 17 and prevent it from shifting due to the axial movement of the movable part 15.

[0023] In this concept, the movable part 15 is externally fitted onto the stationary part 16, with the inner diameter of the movable part 15 being larger than the outer diameter of the stationary part 16, and the annular groove 18 is provided on the outer peripheral surface 160 of the stationary part 16. Fitting the movable part 15 externally onto the movable part 16 prevents the preload spring 11 from radially contacting the movable part 15 in the overlap portion between the movable part 15 and the stationary part 16, and prevents the movable part 15 from causing the preload spring 11 to axially displace due to friction during axial movement, thereby ensuring that both ends of the preload spring 11 have good stability.

[0024] In other embodiments, it is also possible for an annular groove to be arranged on the inner circumferential surface of the movable part 15. As a further improvement, it is also possible for the stationary part to be mounted externally on the movable part, and then the inner diameter of the stationary part is larger than the outer diameter of the movable part.

[0025] With reference to Fig. 4 and Fig. 5, the number of seal rings 17 is one. As a further improvement, it is also possible for the number of seal rings 17 to be a plurality distributed axially with a gap, and for a seal ring 17 to be provided with a corresponding annular groove, or for some of the seal rings 17 to be secured in an annular groove. A plurality of seal rings 17 can achieve relatively good sealing performance.

[0026] One aspect is that the movable part 15 is used for sealing. Another aspect is that the movable part 15 serves as a spring support and comprises: a body 150 which is fastened to the release bearing 10 and carries one end of the preload spring 11, and a sealing part 151 which has an overlap part with the stationary part 16 continuously in the radial direction, wherein the sealing part 151 has an overlap part with the stationary part 16 continuously in the radial direction. In comparison with the prior art, in this concept, the sealing part 151 is formed by the body 150 extending in the axial direction to the other axial end D, wherein it has relatively large axial dimensions and the overlap part is realized with the stationary part 16.The concept for supporting one end of the preload spring 11 by the body 150 is: The body 150 covers the end surface of one end of an inner ring 100 of the release bearing 10 and is fixed, one end of the preload spring 11 axially abuts the body 150 and is limited in the axial direction by the sealing part 151 and cannot shift.

[0027] The other end of the preload spring 11 is arranged in a gap 20 between the stationary part 16 and the slave cylinder body 13. The stationary part 16 serves to prevent the other end of the preload spring 11 from shifting outward in the axial direction. Therefore, a radial gap is provided between the seal cap 14 and the slave cylinder housing 13 to support the preload spring 11. In specific applications, the thickness of the movable part 15 and the stationary part 16 is appropriately selected to prevent the seal cap 14 from abutting the adjacent clutch housing. In this concept, compared to the prior art, the stationary part 16 extends axially toward the movable part 15 to increase the axial dimensions, and the overlap part between it and the seal part 151 is realized.

[0028] Furthermore, the opening 130 provided in the slave cylinder housing 13 is directed in the axial direction toward an oil chamber 131 of the release bearing 10. A hydraulic control device 19 is mounted in the oil chamber 131. The hydraulic control device 19 serves to control the movement of the release bearing 10 in the axial direction. The hydraulic control device 19 comprises a piston 21 and a piston rod 22, wherein the piston 21 is located in the oil chamber 131, the piston rod 22 protrudes from the oil chamber 131 in the axial direction and bears against the release bearing 10. With reference to Fig. 4, pressure is exerted on the piston 21 by filling the oil chamber 131 with oil. The piston 21 drives the release bearing 10 via the piston rod 22 to move it toward the clutch until it reaches the left limit position. The pressure is then continued to close the clutch. In connection with reference to Fig.5, the oil discharge from the oil chamber 131 to the outside causes the piston 21 to move in the opposite direction in order to disengage the clutch.

[0029] The sealing cap 14 and the preload spring 11 are located outside the oil chamber 131, the sealing cap 14 can prevent external dust and external water from contaminating the piston 21, the piston rod 22 and the oil chamber 131.

[0030] While this invention is disclosed as above, it is by no means limited thereto. Those skilled in the art may make various changes and modifications without departing from the spirit and scope of this invention, and the scope of this invention is to be construed as defined by the claims.

Claims

[1] Clutch actuating device comprising: a release bearing (10), a preload spring (11) and a clutch central releaser (12); the clutch central release mechanism (12) comprises a slave cylinder housing (13), the release bearing (10) is mounted externally on an axial end of the slave cylinder housing (13) and can move axially relative to the slave cylinder housing (13), the preload spring (11) is mounted externally on the slave cylinder housing (13) and axially preloads the release bearing (10); a sealing cap (14) is mounted in a ring-like manner on the outside of the slave cylinder housing (13) radially outside the preload spring (11), the sealing cap is fastened in the axial direction to the release bearing (10) and to the other axial end of the slave cylinder housing (13); characterized bythat the sealing cap (14) comprises a movable part (15) and a fixed part (16) which are mounted together as a set, the inner diameter of the part of the movable part (15) and the fixed part (16) which is located on the radial outside is larger than the outer diameter of the other part; the movable part (15) is fastened synchronously to the release bearing (10) in an axially movable manner, the immovable part (16) is fastened to the other axial end of the slave cylinder housing (13), the movable part (15) and the immovable part (16) have a sealed overlap part throughout in the radial direction. [2] Clutch actuating device according to claim 1, characterized byin that the movable part (15) serves as a spring support and comprises: a body (150) which is fastened to the release bearing (10) and carries one end of the preload spring (11), and a sealing part (151) which has an overlap part continuously in the radial direction with the immovable part (16). [3] Clutch actuating device according to claim 2, characterized by that the movable part (15) is placed on the outside of the immovable part (16). [4] Clutch actuating device according to claim 2, characterized by that the sealing part (151) is formed by the body (150) extending in the axial direction to the other axial end of the slave cylinder housing (13). [5] Clutch actuating device according to claim 1, characterized by that there is a radial gap (20) between the sealing cap (14) and the slave cylinder housing (13) to support the preload spring (11). [6] Clutch actuating device according to claim 1, characterized by that a sealing ring (17) is provided between the movable part (15) and the immovable part (16) in the overlap part. [7] Clutch actuating device according to claim 6, characterized by that of the two radially opposite circumferential surfaces of the movable part (15) and the immovable part (16), one circumferential surface is provided with an annular groove (18) to receive the sealing ring (17). [8] Clutch actuating device according to claim 6, characterized by that the number of sealing rings (17) is one or a plurality arranged with space in the axial direction. [9] Clutch actuating device according to claim 1, characterized bythat an opening (130) provided in the slave cylinder housing (13) is directed in the axial direction towards an oil chamber (131) of the release bearing (1), a hydraulic control device (19) is mounted in the oil chamber (131), the hydraulic control device (19) serves to control the movement of the release bearing (1) in the axial direction. [10] Coupling system, characterized by that it comprises a clutch actuating device according to one of claims 1 to 9.

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