JP2005188596A - Hydraulic clutch cut-off device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic clutch cut-off device which is excellent in durability to enable the prevention of oil leakage in advance. <P>SOLUTION: The hydraulic clutch cut-off device 1 is comprised of an inner cylinder 3 providing a flange 3b at an end, and an outer cylinder 4, which is coaxially arranged with respect to the inner cylinder 3 with space, providing a flange 42d at one end. The flange 3b of the inner cylinder 3 and one end 41b of the outer cylinder 4 are connected with a screw member 10 inserted into the flange 3b of the inner cylinder 3 in the axial direction to block an opening at the end of the outer cylinder 4 with the flange 3b of the inner cylinder 3. An O-ring 15 is arranged in a recessed groove 41d installed in the end 41b of the outer cylinder 4 or the flange 3b of the inner cylinder 3 to hermetically seal the gap between the end 41b of the outer cylinder 4 and the flange 3b of the inner cylinder 3 and to secure the flange 42d of the outer cylinder 4 to a clutch housing 7. Axial clearance L, which is 0.05 or under times the thickness of the O-ring 15, is formed between the flange 3b of the inner flange 3 and the clutch housing 7 to set a depth H of the recessed groove 41d to be 0.65 to 0.9 times the thickness of the O-ring 15. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a hydraulic clutch disconnection device.

The clutch device is a device for transmitting torque from the crankshaft of the engine to the transmission and blocking transmission of torque as necessary. Among clutch disconnection devices that operate in the clutch device, there are hydraulic devices that operate by hydraulic pressure.
The hydraulic clutch breaker has a cylinder and a piston inserted into the cylinder, and introduces hydraulic oil into the cylinder to move the piston. Then, the release bearing is pushed by the movement of the piston, and the release bearing is pressed against a diaphragm spring or the like, whereby the clutch is disengaged.

  As such a clutch disconnection device, the one shown in FIG. 5 is known. The clutch disengagement device 100 has an inner cylinder 101 provided with a flange portion 101a extending radially outward at one end, and is disposed coaxially with a space with respect to the inner cylinder 101, and radially outward at one end. And an outer cylinder 102 provided with a flange portion 102a extending in the direction. An annular hydraulic chamber 103 is formed between the inner cylinder 101 and the outer cylinder 102, and a piston 104 is inserted into the hydraulic chamber 103. The piston 104 is moved in the axial direction by hydraulic pressure, and the contact plate 106 of the release bearing 105 provided at the tip of the piston 104 pushes the diaphragm spring 107 to disengage the clutch. The flange 101a of the inner cylinder 101 and the one end 102b of the outer cylinder 102 are connected by a screw member 108 that passes through the flange 101a of the inner cylinder 101 in the axial direction, and an opening on one end of the outer cylinder 102 is opened. Is closed by the flange portion 101 a of the inner cylinder 101. In addition, an O-ring 110 is disposed in an annular concave groove 109 provided in one end portion 102b of the outer cylinder 102, and the space between the one end portion 102b of the outer cylinder 102 and the flange portion 101a of the inner cylinder 101 is sealed, A flange portion 102 a of the outer cylinder 102 is fixed to the clutch housing 112 with a bolt 111. An axial gap L is formed between the flange portion 101 a of the inner cylinder 101 and the clutch housing 112. By forming the axial gap L, axial dimension errors of the inner cylinder 101 and the outer cylinder 102 are absorbed, and axial adhesion between the flange portion 102a of the outer cylinder 102 and the clutch housing 112 is ensured. ing.

However, in the conventional clutch disconnection device 100, when the screw member 108 is loosened due to vibration or the like, the axial gap L is formed, so that the inner cylinder 101 is axially displaced by the looseness of the screw member 108. There was a movement. As a result, the sealing performance of the O-ring 110 is impaired, and hydraulic oil may leak.
The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a hydraulic clutch breaker excellent in durability that can prevent hydraulic fluid leakage.

The present invention provides an inner cylinder provided with a flange portion extending radially outward at one end portion, and is provided coaxially with a space with respect to the inner tube, and provided with a flange portion extending radially outward at one end portion. And connecting the flange portion of the inner cylinder and one end portion of the outer cylinder with a screw member that passes through the flange portion of the inner cylinder in the axial direction. The opening of the inner cylinder is closed by a flange portion of the inner cylinder, and an O-ring is disposed in an annular groove provided in one end of the outer cylinder or the flange of the inner cylinder, so that the one end of the outer cylinder and the flange of the inner cylinder Between the flange portion of the inner cylinder and the clutch housing, and an O-ring between the flange portion of the inner cylinder and the clutch housing. Forming an axial gap of 0.05 times or less the thickness of the groove Characterized in that it is set to 0.65 to 0.9 times the thickness of said O-ring is.
According to the present invention, when the screw member is loosened, the inner cylinder moves in the axial direction due to the axial gap, but the movement of the inner cylinder is restricted by the one end portion of the outer cylinder and the clutch housing. The amount of movement of the inner cylinder in the axial direction is 0.05 times or less the thickness of the O-ring that is the range of the axial clearance. Here, since the depth of the concave groove is 0.65 to 0.9 times the thickness of the O-ring 15, even when the inner cylinder moves to the maximum extent, The cylinder flange can be kept elastic and in close contact. Accordingly, the sealing performance of the O-ring can be maintained.

  According to the present invention, hydraulic oil leakage can be prevented and durability can be improved.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows a cross section of a clutch disconnection device 1 used in the clutch device. The left side in FIG. 1 is the engine E side, and the right side is the transmission T side. FIG. 2 is a right side view excluding the clutch housing 7 in FIG.
As shown in FIG. 1, the hydraulic clutch breaker 1 includes a substantially cylindrical inner cylinder 3 that surrounds the outer periphery of a transmission shaft 2, and a substantially cylindrical that is provided coaxially with a space with respect to the inner cylinder 3. An annular inner hydraulic chamber 5 is formed between the inner cylinder 3 and the outer cylinder 4.

The outer cylinder 4 includes a substantially cylindrical small outer cylinder 41 provided on the radially inner side, and a substantially cylindrical large outer cylinder 42 provided coaxially with a space with respect to the small outer cylinder 41. An annular outer hydraulic chamber 6 is formed between the small outer cylinder 41 and the large outer cylinder 42.
Each of the cylinders 3 and 4 is fixed to a clutch housing 7 having an annular cross-sectional base portion 7a that protrudes toward the axial engine E side in a state where they are connected. The inner hydraulic chamber 5 and the outer hydraulic chamber 6 include an inner oil supply passage 5a and an outer oil supply from an inner oil supply port 5A and an outer oil supply port 6A connected to a master cylinder (not shown) that is a pressure oil supply source. The pressure oil is supplied independently via the path 6a.

The inner cylinder 3 has a cylindrical inner cylinder main body 3a and an inner cylinder flange portion 3b extending radially outward from one end (the right end in FIG. 1) of the inner cylinder main body 3a.
The small outer cylinder 41 includes a cylindrical small outer cylinder main body 41a, a small outer cylinder extending portion 41b extending radially outward from one end of the small outer cylinder main body 41a, and a small outer cylinder extending portion 41b. And a small outer cylinder skirt portion 41c extending to the axial transmission T side.
The large outer cylinder 42 includes a cylindrical large outer cylinder main body 42a, a large outer cylinder extending part 42b extending radially outward from one end of the large outer cylinder main body 42a, and a large outer cylinder extending part 42b. A large outer cylinder skirt portion 42c extending from the extended end to the axial transmission T side, and a large outer cylinder flange portion 42d extending radially outward from the extended end of the large outer cylinder skirt portion 42c. Have.

In each of the cylinders 3 and 4 configured as described above, the small outer cylinder 41 and the large outer cylinder 42 are arranged coaxially by fitting the small outer cylinder skirt portion 41c and the large outer cylinder skirt portion 42c. It has become so. Further, the inner cylinder flange portion 3b and the small outer cylinder extending portion 41b which is one end portion of the outer cylinder 4 are fastened by a short screw 10 which is a screw member which passes through the inner cylinder flange portion 3b in the axial direction. Thus, the opening on the one end side of the small outer cylinder 41 is closed by the inner cylinder flange portion 3b. Further, the small outer cylinder skirt portion 41c and the large outer cylinder extending portion 42b are fastened by the long screw 11 that passes through the small outer cylinder skirt portion 41c in the axial direction, thereby one end portion of the large outer cylinder 42 The opening on the side is closed by the small outer cylinder extending portion 41b.
A support bearing 13 that supports the clutch cover 12 is provided at a substantially central portion in the axial direction of the outer peripheral surface of the large outer cylinder main body 42a.

  An annular first concave groove 41d is formed in the right end surface 41b1 of the small outer cylinder extending portion 41b so as to be recessed in the axial direction, and the inner cylindrical flange surface 3b1 and the right end surface are formed in the first concave groove 41d. A first O-ring 15 having a circular cross-section that seals between 41b1 is disposed. Similarly, an annular second concave groove 41e is formed in the left end surface 41c1 of the small outer cylinder skirt portion 41c so as to be recessed in the axial direction, and the second concave groove 41e has a large outer surface and the left end surface 41c1. A second O-ring 17 having a circular cross section that seals between the right end surface 42b1 of the tube extending portion 42b is disposed. Each of the O-rings 15 and 17 is made of an elastic member such as acrylic rubber, and the thickness thereof is larger than the axial depth H of each of the concave grooves 41d and 41e. More specifically, the axial depth H of the first concave groove 41 d is formed to be 0.65 to 0.9 times the thickness of the first O-ring 15. The first O-ring 15 is kept in close contact with the bottom surface of the first concave groove 41d and the inner cylinder flange surface 3b1 in an elastic state, and similarly, the second O-ring 17 The sealing performance is maintained in close contact with the bottom surface of the two concave grooves 41e and the large outer cylinder extending portion end surface 42b1 in an elastic state.

In the inner cylinder 3 and the outer cylinder 4 fastened so as to be integrated with each other as described above, the inner peripheral surface 41c2 of the small outer cylinder skirt portion 41c is fitted to the outer peripheral surface 7a1 of the base portion 7a of the clutch housing 7. ing. An axial gap L is formed between the inner cylinder flange portion 3 b and the base portion 7 a of the clutch housing 7. Further, the large outer cylinder flange portion 42 d of the large outer cylinder 42 is fastened to the clutch housing 7 with the fixing bolt 18 inserted in the axial direction.
The axial clearance L is set to be 0.05 times or less the thickness of the first O-ring 15. By forming this axial gap L, the axial dimensional error of each of the cylinders 3 and 4 is absorbed, and the axial adhesion between the large outer cylinder flange portion 42d and the clutch housing 7 is ensured.

  A cylindrical inner piston 19 that moves in the axial direction by hydraulic pressure is inserted in the inner hydraulic chamber 5, and a cylindrical outer piston 20 that moves in the axial direction by hydraulic pressure is inserted in the outer hydraulic chamber 6. Yes. An inner release bearing 21 is provided at the tip of the inner piston 19 on the engine E side, and an outer release bearing 22 is provided at the tip of the outer piston 20 on the engine E side. Inner contacts 21 and 22 of the release bearings 21 and 22 are respectively provided with an inner contact plate 24 and an outer contact plate 25 that are in contact with the diaphragm spring 23 of the clutch mechanism. In addition, an oil seal 26 having a lip that is in sliding contact with the inner surfaces of the hydraulic chambers 2 and 3 is attached to the rear end portions of the pistons 19 and 20. Sealed. Further, a compression coil spring 27 is interposed between the small outer cylinder 41 and the inner piston 19 and between the large outer cylinder 42 and the outer piston 20, and the inner piston 19 and the outer piston 20 are It is biased toward the axial engine E side.

Here, the operation of the hydraulic clutch breaker 1 will be described.
The inner release bearing 21 and the outer release bearing 22 move to the engine E side or the transmission T side by the pressure oil supplied from the master cylinder to the inner hydraulic chamber 5 and the outer hydraulic chamber 6 via the oil supply passage. The contact plates 24 and 25 provided on the inner rings 21a and 22a of the release bearings 21 and 22 press or release the diaphragm spring 23, so that the clutch can be engaged and disengaged. At this time, since the pressure oil can be supplied to the inner hydraulic chamber 5 and the outer hydraulic chamber 6 independently, the operation timing of the pistons 19 and 20 can be shifted. By shifting the operation timings of the pistons 19 and 20, the timing at which the clutch plate (not shown) of the clutch mechanism is brought into and out of contact with the flywheel (not shown) can be shifted, so that smooth power interruption is performed. be able to.

  In the hydraulic clutch breaker 1 configured as described above, the axial gap L that absorbs the axial dimensional error of the inner cylinder 3 and the outer cylinder 4 is formed, so that the short screw 10 is loosened. The inner cylinder 3 moves in the axial direction. However, the movement is restricted between the right end surface 41 b 1 of the small outer cylinder extending portion 41 b that forms the axial gap L and the end surface 7 a 2 on the engine E side of the base portion 7 a of the clutch housing 7. That is, the amount of movement of the inner cylinder 3 in the axial direction is restricted to 0.05 times or less the thickness of the first O-ring 15 that is the range of the axial clearance L. Accordingly, even if the inner cylinder 3 moves to the maximum extent, the depth H of the first concave groove 41d is formed to be 0.65 to 0.9 times the thickness of the first O-ring 15. The ring 15 is elastic and can keep a close contact with the bottom surface of the first concave groove 41d and the inner cylinder flange surface 3b1. For this reason, the sealing performance of the first O-ring 15 can be maintained.

  When the axial gap L is set to be larger than 0.05 times the thickness of the first O-ring 15, the axial depth of the first concave groove 41d is secured in order to ensure the sealing performance of the O-ring 15. The length H needs to be less than 0.65 times the thickness of the first O-ring 15. However, in this case, since the depth H of the first concave groove 41d is too shallow, the inner cylinder flange surface 3b1 and the right end surface 41b1 of the small outer cylinder extending portion 41b can be closely attached and fastened in the axial direction. It becomes difficult. When the depth H of the first concave groove 41 d exceeds 0.9 times the thickness of the first O-ring 15, the amount of movement of the inner cylinder 3 is 0.05 of the thickness of the first O-ring 15. Even if it is less than double, the first O-ring 15 cannot keep the elastic close contact with the bottom surface of the first concave groove 41d and the inner cylinder flange surface 3b1, and the first O-ring 15 15 sealability cannot be maintained.

Here, the result of the evaluation test of the sealing performance of the first O-ring 15 will be described.
FIG. 3 shows the evaluation results of the sealing performance of the first O-ring 15 when the ratio of the axial clearance L to the thickness of the first O-ring 15 is changed, and FIG. 4 shows the shaft of the first concave groove 41d. The evaluation result of the sealing performance of the first O-ring 15 when the ratio of the direction depth H to the thickness of the first O-ring 15 is changed is shown. 3 and 4 indicate that the sealing performance of the first O-ring 15 can be maintained satisfactorily, and the × mark indicates that the sealing performance could not be maintained satisfactorily. Is shown.

From FIG. 3, it can be seen that the axial clearance L can maintain the sealing performance of the first O-ring 15 well when the ratio to the thickness of the first O-ring 15 is 0.05 or less. Further, from FIG. 4, the axial depth H of the first concave groove 41 d is excellent in the sealing performance of the first O-ring 15 when the ratio to the thickness of the first O-ring 15 is 0.65 to 0.9. It can be seen that can be maintained.
That is, the axial gap L is set to 0.05 times or less the thickness of the first O-ring 15, and the axial depth H of the first concave groove 41 d is set to 0.65 to 0. 0 of the thickness of the first O-ring 15. It was confirmed that the sealing performance of the first O-ring 15 can be maintained satisfactorily by setting it to 9 times.
As described above, according to the hydraulic clutch disconnection device 1 of the present embodiment, it is possible to prevent hydraulic fluid leakage and improve the durability of the device 1.

In addition, this invention is not limited to embodiment mentioned above.
For example, the hydraulic clutch disconnection device 1 can be applied to one having only the inner hydraulic chamber 5 and does not limit the number of hydraulic chambers or the number of cylinders constituting the peripheral wall. Further, the outer cylinder 4 may be configured by integrating a small outer cylinder 41 and a large outer cylinder 42. Further, the first concave groove 41d may be formed on the flange surface 3b1 of the inner cylinder 3. Further, the fastening between the inner cylinder flange portion 3b and the small outer cylinder extending portion 41b may be, for example, press-fitting or caulking other than a screw.

It is a fragmentary sectional view of the hydraulic clutch cutoff device of the present invention. FIG. 2 is a right side view excluding a clutch housing in FIG. 1. It is a table | surface which shows the evaluation result of the sealing performance of a 1st O-ring when changing the ratio with respect to the thickness of the 1st O-ring of an axial clearance gap. It is a table | surface which shows the evaluation result of the sealing performance of a 1st O-ring when changing the ratio with respect to the thickness of the 1st O-ring of the axial direction depth of a 1st groove. It is sectional drawing of the conventional clutch interruption | blocking apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic clutch cutoff device 3 Inner cylinder 3b Inner cylinder flange part (flange part of inner cylinder)
4 Outer cylinder 41b Small outer cylinder extension (one end of the outer cylinder)
41d First groove (concave groove)
42d Large outer flange (outer cylinder flange)
7 Clutch housing 15 First O-ring (O-ring)
10 Short screw (screw member)
L Axial gap H Depth groove axial depth

Claims (1)

An inner cylinder provided with a flange portion extending radially outward at one end portion, and an outer cylinder provided with a flange portion extending radially outward at one end portion with a space provided for the inner cylinder, And connecting the flange portion of the inner cylinder and one end portion of the outer cylinder by a screw member that is inserted through the flange portion of the inner cylinder in the axial direction,
An opening on the one end side of the outer cylinder is closed by a flange portion of the inner cylinder, and an O-ring is disposed in an annular groove provided in one end portion of the outer cylinder or the flange portion of the inner cylinder. A hydraulic clutch disconnection device that seals between the flange portion of the inner cylinder and the flange portion of the inner cylinder, and fixes the flange portion of the outer cylinder to the clutch housing,
Between the flange portion of the inner cylinder and the clutch housing, an axial clearance of 0.05 times or less the thickness of the O-ring is formed,
The depth of the concave groove is set to 0.65 to 0.9 times the thickness of the O-ring.

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