JP5125965B2 - Cup seal connection structure - Google Patents

Description

  The present invention relates to a cup seal coupling structure, and more particularly to a cup seal coupling structure applied to a hydraulic clutch release device mounted on a vehicle or the like.

  Patent Document 1 discloses a cup seal coupling structure in which an air escape path is provided in an annular groove of an annular piston into which a cup seal is fitted. Referring to FIG. 1 of Patent Document 1, it is formed in an annular groove formed so as to extend in the circumferential direction at the end of the annular piston so as to extend in the circumferential direction at the end of the cup seal. Further, there is disclosed a cup seal coupling structure in which the annular convex portions are closely contacted with no gaps, and further, an opening of an air escape passage is formed on the bottom surface of the annular concave groove. Referring to FIG. 2 of Patent Document 1, the piston further has air escape grooves formed at several places in the circumferential direction of the annular concave groove, and at the portion where the air escape groove exists, Between the annular convex part and the annular concave part of the piston, a gap is formed on both the outer peripheral side and the inner peripheral side, whereby the cup seal is not tightened from the piston at the part where the air escape groove is present. A cup seal coupling structure is disclosed.

  FIG. No. 21 discloses a coupling structure in which an opening of an annular groove of an annular piston or a jaw part forming the opening presses and holds a fitting protrusion of a cup seal.

FIG. 1, the annular concave groove of the annular piston is in contact with the annular convex portion of the cup seal both at the inner side and at the inner side of the opening portion, and the fitting convex portion is fully tightened. A cup-seal coupling structure for holding is disclosed.
JP 2002-340028 A (FIGS. 1 and 2) US6502682B2 (FIG. 21, c.14, 1.59-65) DE19524312A1 (Fig. 1)

  As disclosed in Patent Documents 1 to 3, according to the coupling structure in which the annular convex portion of the cup seal is in close contact with the annular concave portion of the annular piston, the resistance when inserting the convex portion into the concave portion is large. Therefore, there is a problem that it takes time to assemble the cup seal coupling structure. In addition, since the cup seal is usually made of rubber, inevitably variations in shape or dimensions occur between lots. As described above, when the convex part of the cup seal is designed to be in close contact with the concave part of the piston, for example, when the size of the cup seal is large at either the convex part tip or the convex intermediate part. However, it takes time to assemble, and if it is the same, there is a problem that it is difficult to obtain the expected tension. Therefore, it takes time to manage the production of the cup seal.

  As disclosed in Patent Document 1 or 2, when there are gaps between the outer peripheral surface and inner peripheral surface of the convex portion provided in the cup seal and the concave portion of the piston, the cup seal is partially May twist and interfere with the recess opening edge of the piston.

  An object of the present invention is to provide a cup seal coupling structure that can easily couple a cup seal to a piston and obtain a stable tightening force between lots.

  In a first aspect, the present invention is an annular shape that slides on an inner cylinder surface and an outer cylinder surface of the cylinder chamber when the piston strokes at an end of an annular piston that can freely stroke in an annular cylinder chamber. A cup seal coupling structure in which an elastic cup seal is coupled, wherein the cup seal has a neck portion and a head portion formed on one side of the neck portion, and the neck portion and the head portion are inserted into the piston. The neck portion is loosely fitted to a pair of jaw portions located at the entrance of the annular groove, and the head portion is compressed on the back side of the pair of jaw portions of the front annular groove. Providing a cup seal coupling structure in which the cup seal is coupled to the piston.

  In a second aspect, the present invention is an annular shape that slides on an inner cylinder surface and an outer cylinder surface of the cylinder chamber when the piston strokes at an end of an annular piston that can freely stroke in an annular cylinder chamber. A cup seal coupling structure in which a cup seal having elasticity is coupled, wherein the cup seal is formed from a base portion, a neck portion formed on one side of the base portion, and a neck portion formed on one side of the neck portion. A large-diameter head portion and a pair of lip portions formed on the other side of the base portion and in sliding contact with the inner cylindrical surface and the outer cylindrical surface of the cylinder, respectively, and the piston includes the neck portion and the head An annular groove into which the portion is inserted, a pair of jaws positioned at the entrance of the annular groove, a projection formed on one of the pair of jaws and projecting into the annular groove, and the projection The annular groove than the part A compression portion that is compressible to the head portion that is disposed on the back side and that is inserted into the annular groove, and the other of the pair of jaw portions in a state where the head portion is compressed to the compression portion. A gap is formed between the neck portion and the neck portion, the neck portion is loosely fitted to the pair of jaw portions of the annular groove, and the head portion is compressed by the tightening portion on the back side of the pair of jaw portions. Thus, a cup seal coupling structure is provided in which the cup seal is coupled to the piston.

  According to the present invention, the cup seal is loosely fitted to the piston at the inlet of the annular groove, and is held tightly from the piston side inside or behind the annular groove. In this way, the number of places where the cup seal is tightened is small, that is, the places where the cup seal is tightened are limited, and compared with the case where the cup seal is tightened from the piston side in many places, The tightening force against the cup seal is stabilized. As a result, variation in the tightness of the cup seal between lots is reduced, and production management is facilitated.

  The cup seal is an elastic member such as rubber, and its dimensional variation is inevitably larger than that of the piston. The variation becomes larger as the shape of the cup seal becomes more complicated. If the cup seal is tightened at the inlet of the annular groove and at two locations on the inner side or the rear side, the variation in the tightening force on the cup seal increases due to the variation in the size of the cup seal. For example, the tightening force largely fluctuates depending on how the neck portion of the cup seal and the pair of jaw portions of the piston come into contact. According to the present invention, as described above, by limiting the tightening portion to the inner side or the inner side of the annular groove, the above-described variation in the size of the cup seal is absorbed, and the cup that is easy to fit during assembly and difficult to remove during operation. A seal coupling structure is provided.

  According to a preferred embodiment of the present invention, on the inner surface of the annular groove, the wall surface facing the protrusion is formed straight along the axial direction of the piston on the radial cross section. Alternatively, on the inner surface of the annular groove, the wall surface facing the protrusion is formed on the same diameter along the axial direction. According to such a form, the head part (convex part) of a cup seal becomes easy to insert in the recessed part of a piston at the time of an assembly.

  According to a preferred embodiment of the present invention, the bottom surface of the annular groove includes a straight portion formed on a straight line along the radial direction of the piston, and a first portion formed on a curved surface on both sides of the straight portion. 1 R portion. According to this form, even if there exists a projection part in the opening part of an annular groove, the cutting process of an annular groove becomes easy.

  According to a preferred embodiment of the present invention, the head portion has second R portions each formed in a curved shape on both radial sides of the tip portion. According to this aspect, the contact area between the head portion of the cup seal and the annular groove of the piston is increased, and the tightening force against the cup seal can be increased.

  The cup seal coupling structure according to a preferred embodiment of the present invention allows a space to be formed between the tip of the head of the cup seal and the bottom of the annular groove of the piston.

  In a preferred embodiment of the present invention, the cup seal coupling structure defined by the present invention is formed continuously along the circumferential direction, that is, in an annular shape. In another preferred embodiment of the present invention, the cup seal coupling structure defined by the present invention is formed discontinuously along the circumferential direction, that is, at a plurality of predetermined intervals along the circumferential direction.

  An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view schematically showing a configuration of a hydraulic clutch release device to which a cup seal coupling structure according to an embodiment of the present invention is applied.

  Referring to FIG. 1, a hydraulic clutch release device to which a cup seal coupling structure according to an embodiment of the present invention is applied forms a cylinder chamber 4 between an inner housing 1 and an outer housing 2. This is a device that controls the engagement / disengagement state of a clutch (not shown) by moving the first and second annular pistons 6 and 7 and the release bearing 5 along the axial direction by the internal hydraulic pressure.

  The hydraulic clutch release device includes an inner housing 1, an outer housing 2, a cup seal 3, a cylinder chamber 4, a release bearing 5, a first annular piston 6, a second annular piston 7, and a disc spring 8. The coil spring 9, the sheet member 10, the cover member 11, the retaining ring 12, the seal 13, and the stopper member 14 are included.

  The inner housing 1 is an annular member, and includes a cylindrical portion 1a and a flange portion 1b extending from one end of the cylindrical portion 1a in the outer peripheral direction.

  The outer housing 2 is an annular member, and has an oil port 2a, a mounting flange 2b, and a step portion 2c. The attachment flange 2b is a flange-shaped portion for attaching the present apparatus to a transmission or the like. The step portion 2 c is a recess formed on the surface of the outer housing 2 on the flange portion 1 b side, and is formed in an annular shape on the outer periphery of the cylinder chamber 4.

  The cup seal 3 is an annular seal member that is made of an elastic material and seals the cylinder chamber 4. The cup seal 3 is disposed between the inner housing 1 and the outer housing 2 and is mounted in the annular groove 7 a of the second annular piston 7.

  The cylinder chamber 4 is an annular cylinder chamber surrounded by the inner housing 1, the outer housing 2, and the second annular piston 7. The cylinder chamber 4 is connected to an unillustrated clutch master cylinder or the like via an oil passage between the stepped portion 2c and the flange portion 1b and an oil port 2a, and is supplied with pressure oil.

  The release bearing 5 is a ball bearing attached to the holding member 5c. The inner ring 5a of the release bearing 5 is rotatably supported by the outer ring 5b via a ball, and is always joined to a diaphragm spring (not shown) at the end on the clutch side (right side in FIG. 1). Therefore, the inner ring 5a rotates integrally with a diaphragm spring (not shown). The outer ring 5b of the release bearing 5 is a non-rotating wheel fixed to the first annular piston 6 via a holding member 5c. The holding member 5c of the release bearing 5 is attached to the attachment portion 6a of the first annular piston 6 by a disc spring 8 so that it can be aligned. The urging force of the spring 9 is received. The disc spring 8 supports the release bearing 5 so as to be movable in the radial direction.

  Note that a diaphragm spring (not shown) presses a clutch disk (not shown) to a flywheel (not shown) via a pressure plate (not shown).

  The first annular piston 6 is in contact with the second annular piston 7 at the end on the cylinder chamber 4 side so as to be able to contact and separate. The first annular piston 6 is slidable along the axial direction (left-right direction in FIG. 1) as the second annular piston 7 slides between the inner housing 1 and the outer housing 2.

  The second annular piston 7 is slidable between the inner housing 1 and the outer housing 2 along the axial direction (left-right direction in FIG. 1) by hydraulic pressure. The second annular piston 7 has an annular groove (concave portion) 7a for mounting the cup seal 3 on the end on the cylinder chamber 4 side.

  The disc spring 8 is an annular member having spring elasticity for attaching the holding member 5 c of the release bearing 5 to the attachment portion 6 a of the first annular piston 6.

  The coil spring 9 extends along the axial direction of the apparatus (left-right direction in FIG. 1), and is interposed between the sheet member 10 and the sheet portion 11 a of the cover member 11. The coil spring 9 urges the release bearing 5 via a seat member 10 toward a diaphragm spring (not shown).

  The sheet member 10 is a member for supporting one end of the coil spring 9, and is attached to the holding member 5 c of the release bearing 5.

  The cover member 11 is a cylindrical member that covers the outer periphery of the coil spring 9. The cover member 11 is set so as not to come into contact with the release bearing 5 even when the first and second annular pistons 6 and 7 slide to the cylinder chamber 4 side. The cover member 11 has a seat portion 11a extending to the inner peripheral side at an end portion on the transmission side (left side in FIG. 1). The seat portion 11 a supports the other end of the coil spring 9 and is in contact with the outer housing 2.

  The retaining ring 12 is an annular member that restricts the sliding of the annular pistons 6 and 7 to the clutch side (right side in FIG. 1). The retaining ring 12 is attached to a groove formed in the vicinity of the end of the outer peripheral surface of the inner housing 1 on the clutch side (right side in FIG. 1).

  The seal 13 is an annular member made of an elastic material for sealing the joint surface between the flange portion 1 b of the inner housing 1 and the outer housing 2. The seal 13 is disposed on the outer peripheral side of the cylinder chamber 4 and the oil port 2a.

  The stopper member 14 is an annular member that regulates sliding of the cup seal 3 toward the transmission side (left side in FIG. 1). When the piston member is completely separated in order to prevent the axial vibration caused by the crankshaft (not shown) of the engine (not shown) from propagating to the hydraulic system, the stopper member 14 causes the cup seal 3 to be separated from the stepped portion 2c and the flange. This is to prevent the oil passage between the parts 1b from being damaged. The stopper member 14 is disposed on the outer periphery of the cylindrical portion 1a of the inner housing 1 so as to be rotatable in an oil passage between the step portion 2c and the flange portion 1b from a portion in the vicinity of the flange portion 1b of the cylinder chamber 4. .

  The basic operation of the hydraulic clutch release device described above will be described. When the operator depresses a clutch pedal (not shown), pressure oil is supplied to the cylinder chamber 4 from a clutch master cylinder (not shown), whereby the first and second annular pistons 6 and 7 and the release bearing 5 are moved. The clutch moves to the clutch side (the right side in FIG. 1), and the clutch (not shown) enters the disconnected state.

  When the operator releases a clutch pedal (not shown), the pressure oil in the cylinder chamber 4 moves from the oil port 2a to the cylinder chamber 4 side, and the clutch (not shown) is engaged.

  Next, a cup seal coupling structure according to an embodiment of the present invention will be described in detail. FIG. 2 is an exploded view showing a partial cross section of a cup seal coupling structure according to an embodiment of the present invention. FIG. 3 is an assembly view showing a partial cross section of the cup seal and the piston shown in FIG. 2. FIG. 4 is a diagram schematically showing an entire cross section taken along line IV-IV in FIG. 3. In addition, the center line described in FIG. 2 etc. is for showing that the cup seal is annular, and does not correspond to the dimensions of the cup seal shown in FIG.

  2 and 3, in the cup seal coupling structure according to one embodiment of the present invention, an end portion of a second annular piston (hereinafter simply referred to as “piston”) 7 that can freely stroke in the annular cylinder chamber 4. In addition, an annular and elastic cup seal 3 that slides with the inner cylinder surface 4a and the outer cylinder surface 4b of the cylinder chamber 4 when the piston 7 strokes is coupled. The cup seal 3 provides a liquid-tight seal between the piston 7 and the inner cylindrical surface 4a and the outer cylindrical surface 4b of the cylinder chamber 4.

  The cup seal 3 includes a base portion 3a, a neck portion 3b formed on one side in the axial direction of the base portion 3a, a head portion 3c formed on one side in the axial direction of the neck portion 3b, and having a larger diameter than the neck portion 3b, It has a pair of lip portions 3d and 3e formed on the other axial side or both radial sides of 3a and in sliding contact with the inner cylindrical surface 4a and the outer cylindrical surface 4b of the cylinder chamber 4, respectively.

  The piston 7 is formed in an annular groove 7a into which the neck portion 3b and the head portion 3c are inserted, a pair of jaw portions 7b and 7c positioned at the entrance of the annular groove 7a, and one jaw portion (outer jaw portion) 7c. A projecting portion 7d that protrudes into the annular groove 7a, and a tension portion 7e that is disposed on the deeper side of the annular groove 7a than the projecting portion 7d and that can compress the head portion 3c inserted into the annular groove 7a. ing. The inner peripheral surface of the protrusion 7d is in contact with the radially outer surface of the neck 3b.

  Referring to FIG. 3 and FIG. 4, in the state where the head portion 3c is compressed to the tightening portion 7e, one jaw portion (outer jaw portion) 7c is in contact with the neck portion 3b via the protruding portion 7d. A gap 20 is formed between the other jaw (inner jaw) 7b and the neck 3b. Thus, the neck portion 3b is loosely fitted from the pair of jaw portions 7b, 7c located at the entrance of the annular groove 7a, and the head portion 3c is a tight portion where the head portion 3c is located behind the pair of jaw portions 7b, 7c of the annular groove 7a. The cup seal 3 is coupled to the piston 7 by being compressed by 7e. The protrusion 7d abuts on the neck 3b, so that the cup seal 3 can be easily positioned and the cup seal 3 is prevented from being twisted.

  In this way, the cup seal 3 is tightened from the piston 7 side at a large number of locations by the fact that there are few locations where the cup seal 3 is tightened, that is, the location where the cup seal 3 is tightened is limited to the tightening portion 7e. Compared to the case of being tightened, the tightening force on the cup seal 3 is stabilized. As a result, the variation in tightness between lots is reduced.

  The cup seal 3 is generally formed of an elastic member such as rubber, and dimensional variation due to processing is inevitably larger than that of a piston generally formed of a rigid body. This variation becomes larger as the shape of the cup seal 3 becomes more complicated. If the cup seal 3 is tightened at two locations on the inlet and the inner side or the back side of the annular groove 7a, the variation in the tightening force between the lots of the cup seal 3 increases due to the variation in the size of the cup seal 3. That is, the tension force varies greatly depending on the degree of tension of the pair of jaw portions 7b and 7c with respect to the neck portion 3b.

  According to the present embodiment, the position of the tightening portion 7e is limited to the inner side or the inner side of the annular groove 7a, so that variations in the dimensions of the cup seal 3 are absorbed, and the cup seal coupling that is easy to fit during assembly and difficult to disconnect during operation. A structure is provided.

  Subsequently, further advantages and the like of the cup seal coupling structure according to the present embodiment will be described.

  Referring to FIG. 2, on the inner surface of the annular groove 7a, a wall surface 7f facing the projection 7d is formed straight along the axial direction of the piston 7 on the radial cross section. Alternatively, on the inner surface of the annular groove 7a, a wall surface 7f facing the protrusion is formed on the same diameter along the axial direction. According to such a form, the head part 3c becomes easy to insert in the annular groove 7a at the time of assembly.

  Referring to FIGS. 2 and 3, the bottom surface of the annular groove 7a includes a straight portion 7g formed on a straight line along the radial direction of the piston 7, and a first surface formed on a curved surface on both sides of the straight portion 7g. R portion 7h, 7h. According to this embodiment, even if the projection 7d is present in the opening of the annular groove 7a, the cutting of the annular groove 7a is facilitated.

  Referring to FIGS. 2 and 3, the head portion 3c has second R portions 3f and 3f formed in curved shapes on both sides in the radial direction of the tip portion. According to this embodiment, the contact area between the head portion 3c and the annular groove 7a is increased, and the tightening force on the cup seal 3 can be increased.

  Referring to FIG. 2, the ratio L2 / L1 (%) of the protrusion length L2 along the radial direction of the protrusion 7d to the opening diameter L1 of the annular groove 7a is preferably about 5 to 20%. The protrusion length is usually sufficient if it is 0.1 mm or more.

  In one embodiment of the present invention, a space 21 is allowed to be formed between the tip of the head portion 3c and the bottom of the annular groove 7a.

  The cup seal coupling structure of the present invention is applied to coupling of an annular piston and an annular cup seal, and is particularly preferably applied to a hydraulic clutch release device mounted on a vehicle or the like.

1 is a cross-sectional view schematically illustrating a configuration of a hydraulic clutch release device to which a cup seal coupling structure according to an embodiment of the present invention is applied. It is an exploded view showing a partial cross section of a cup seal coupling structure according to an embodiment of the present invention. FIG. 3 is an assembly view showing a partial cross section of a cup seal and a piston shown in FIG. 2. It is a schematic diagram which shows the whole IV-IV line cross section of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inner housing 1a Tubular part 1b Flange part 2 Outer housing 2a Oil port 2b Mounting flange 2c Step part 3 Cup seal 3a Base part 3b Neck part 3c Head part 3d, 3e A pair of lip part 3f, 3f 2nd R part 4 Cylinder Chamber 4a Inner cylinder surface 4b Outer cylinder surface 5 Release bearing 5a Inner ring 5b Outer ring 5c Holding member 6 First annular piston 6a Mounting portion 7 Second annular piston, piston 7a Concavity, annular groove 7b, 7c A pair of jaws (one jaw Part 7c, the other jaw part 7b)
7d Protruding portion 7e Tightening portion 7f Wall surface facing the protruding portion (inner wall surface in the radial direction)
7g Linear portion 7h, 7h First R portion 8 Belleville spring 9 Coil spring 10 Seat member 11 Cover member 11a Seat portion 12 Retaining ring 13 Seal 14 Stopper member 20 Clearance, clearance 21 space L1 Annular groove opening diameter L2 Protrusion portion Protrusion length along radial direction

Claims (5)

A cup in which an annular and elastic cup seal that slides with the inner cylinder surface and the outer cylinder surface of the cylinder chamber when the piston strokes is coupled to the end of an annular piston that can freely stroke in the annular cylinder chamber A seal coupling structure,
The cup seal has a neck portion and a head portion formed on one side of the neck portion, and the piston has an annular groove into which the neck portion and the head portion are inserted,
The neck is loosely fitted to a pair of jaws located at the inlet of the annular groove, and the head part is compressed on the back side of the pair of jaws of the front annular groove, whereby the cup seal is moved to the piston. Combined with
A cup seal coupling structure characterized by that. A cup in which an annular and elastic cup seal that slides with the inner cylinder surface and the outer cylinder surface of the cylinder chamber when the piston strokes is coupled to the end of an annular piston that can freely stroke in the annular cylinder chamber A seal coupling structure,
The cup seal is formed on a base portion, a neck portion formed on one side of the base portion, a head portion formed on one side of the neck portion and having a diameter larger than the neck portion, and on the other side of the base portion. A pair of lip portions in sliding contact with the inner cylinder surface and the outer cylinder surface of the cylinder chamber,
The piston is formed in one of the annular groove into which the neck part and the head part are inserted, a pair of jaw parts positioned at the inlet of the annular groove, and the pair of jaw parts, and is directed into the annular groove. A protruding portion that protrudes from the protruding portion, and a pressing portion that is arranged on the deeper side of the annular groove than the protruding portion and that can compress the head portion inserted into the annular groove,
A gap is formed between the other of the pair of jaw parts and the neck part in a state where the head part is compressed by the tight part,
The neck portion is loosely fitted to a pair of jaw portions of the annular groove, and the head portion is compressed by the tightening portion on the back side of the pair of jaw portions, whereby the cup seal is coupled to the piston. ,
A cup seal coupling structure characterized by that.   3. The cup seal coupling structure according to claim 2, wherein on the inner surface of the annular groove, a wall surface facing the protrusion is formed on the same diameter along the axial direction. The bottom surface of the annular groove includes a straight portion formed on a straight line along the radial direction of the piston, and a first R portion formed on a curved surface on both sides of the straight portion,
The cup-seal coupling structure according to claim 2 or 3, wherein   The cup seal coupling structure according to any one of claims 2 to 4, wherein the head portion has second R portions formed in curved shapes on both sides in the radial direction of the tip portion.

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