JP2002372073A - Sealing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a sealing device capable of positively preventing the fall and damage to spring members with simple structure easy to manufacture. SOLUTION: This sealing device is provided with a cancel plate 1 supporting a plurality of return springs 13 for energizing a piston onto the high pressure oil chamber side, and forming an oil chamber for oil pressure adjustment on the low pressure oil chamber side of the piston, and a sealing member provided at the outer peripheral part of the cancel plate 1 to seal the oil chamber. The cancel plate 1 has guide faces 1b, 1e provided along the side faces of the return springs 13 to suppress the movement of the return springs 13 to the circumferential direction of the piston, and projections 2 for regulating the positions of the end parts of the return springs 13 so as not to come off the guide faces 1b, 1e.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sealing device used for an automatic transmission for an automobile and the like, and more particularly, to a spring member for biasing a hydraulic piston of the automatic transmission and acting on the hydraulic piston. The present invention relates to a sealing device used to reduce the influence of centrifugal oil pressure.

[0002]

2. Description of the Related Art As an automatic transmission used in an automobile or the like, a CVT (Continuous) that engages a multi-plate clutch by a pressing force of a piston that moves by receiving a hydraulic pressure to control a shift.
ly Variable Transmission) is widely known.

[0003] A schematic configuration of a shift switching portion of the CVT will be briefly described with reference to FIG. FIG. 9 is a schematic half-sectional view of the configuration of the speed changeover unit, showing only one side of the rotation shaft of the drum 11 (the right side is omitted in FIG. 9).

The drum 11 is a substantially cylindrical housing member having a bottom which rotates around a rotating shaft (not shown) by receiving a driving force from the engine side. Drum outer wall 11b and drum bottom 11
An annular piston chamber is formed at c.

In the piston chamber of the drum 11, an annular piston 10 is disposed so as to be able to stroke in the axial direction. The piston 10 is a bonded piston seal having an inner peripheral seal 15 slidably in contact with the drum inner wall 11a and an outer peripheral seal 16 slidably in contact with the drum outer wall 11b. Is divided into

A cylindrical portion 10a extending from the outer peripheral portion of the piston 10 to the low-pressure oil chamber L along the drum outer wall 11b is provided. The cylindrical portion 10a functions as a pressing unit that presses the multi-plate clutch 17.

A canceller seal (sealing device) including a cancel plate 100 and a seal member 3 is disposed at a position facing the piston 10 in the low-pressure oil chamber L.

The cancel plate 100 has a projection 100d near its inner periphery. The projection 100d is engaged with the snap ring 12 fitted on the drum inner wall 11a, whereby the axial movement is restricted. I have.
A contact surface 10 formed substantially parallel to the piston 10
At 0a, a return spring 13 that biases the piston 10 toward the high-pressure oil chamber H is supported.

The contact surface 100 of the cancel plate 100
From the outer peripheral edge of a, a guide surface is provided that rises along the side surface of the return spring 13. The guide surface includes a concave portion 100b formed according to the side shape of the return spring 13 and a convex portion 100e projecting between two adjacent return springs 13, 13.
Are alternately repeated to form an uneven shape (petal shape).

Further, the cancel plate 100 has an outward flange portion 100c extending from the upper end of the guide surface to the vicinity of the inner periphery of the cylindrical portion 10a of the piston 10, and the oil chamber X is provided on the low pressure oil chamber L side of the piston 10. Is formed.

The seal member 3 includes a cancel plate 10
0 is an annular seal made by baking a rubber-like elastic body on the outer peripheral edge of the outward flange portion 100c, and a wedge-shaped seal lip provided on the outer peripheral surface is provided on the inner peripheral surface of the cylindrical portion 10a of the piston 10. The outer peripheral side of the oil chamber X is sealed by sliding contact.

In the above configuration, when hydraulic oil is supplied into the high pressure oil chamber H from the hydraulic oil supply passage provided on the drum inner wall 11a (arrow O), the piston 10 resists the urging force of the return spring 13. And low pressure oil chamber L side (downward in the figure)
And presses the multi-plate clutch 17 at the end of the cylindrical portion 10a of the piston 10. Thereby, the drum 1
The clutch plate provided on one side makes frictional contact with the clutch plate on the output shaft (not shown) side, and the rotational driving force of the drum 11 is transmitted to the output shaft.

In the oil chamber whose outer peripheral side is sealed like the high-pressure oil chamber H, when the drum 11 rotates, centrifugal force acts on the hydraulic oil, and centrifugal oil pressure acts on the piston 10 in addition to the operating oil pressure. The phenomenon of working occurs. This centrifugal oil pressure increases in proportion to the square of the distance from the rotation center of the drum 11, so that a non-uniform force acts on the piston 10 as it increases toward the outer peripheral side. This phenomenon makes it difficult to control the working oil pressure,
And causes damage to the piston 10.

The above-mentioned canceller seal is provided to reduce the influence of the centrifugal oil pressure acting on the piston 10 as described above. That is, by forming an oil chamber X on the low pressure oil chamber L side of the piston 10 by the canceller seal, centrifugal oil pressure is generated in the oil chamber X as the drum 11 rotates. Since the centrifugal oil pressure in the oil chamber X acts as a force for urging the piston 10 toward the high-pressure oil chamber H, the centrifugal oil pressure in the high-pressure oil chamber H can be offset.

[0015]

However, in the speed changeover portion having the above-described structure, the difference in the inertial force and the difference in the friction are caused by the repeated operation of the engagement and disengagement of the piston 10 and the multi-plate clutch 17. As a result, a phenomenon occurs in which a force acting in the circumferential direction of the piston acts on the return spring (spring member) 13. The guide surface (concave portion 100b, convex portion 100e) is provided on the cancel plate 100 to prevent the return spring 13 from rotating and moving in the circumferential direction of the piston when this force acts. is there.

However, depending on the rotational speed of the drum 11 and other operating conditions, an unexpectedly large rotational force may be applied to the return spring 13, and in such a case, the return spring 13 may have a convex shape. There is a risk of falling over the portion 100e and possibly leading to bending damage.

In order to prevent such a problem, it is conceivable to increase the amount of protrusion of the convex portion 100e of the guide surface. However, when the cancel plate 100 is formed by pressing a plate material made of a metal material,
Since the amount of plastic deformation increases as the amount of protrusion of the protruding portion 100e increases, cracking occurs during ring making and strength reduction due to thinning of the plate thickness is undesirable. Further, depending on the type of the metal material, the rigidity is high, so that there is a case where the ring cannot be formed to a target size (amount of protrusion).

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a sealing device capable of reliably preventing a spring member from falling down or being broken by a simple structure which is easy to manufacture. To provide.

[0019]

According to the present invention, in order to achieve the above object, a plurality of spring members for urging a piston toward a high-pressure oil chamber are supported, and a plurality of spring members are provided on the low-pressure oil chamber side of the piston. In a sealing device including: a plate member forming an oil chamber for adjusting hydraulic pressure; and a seal member provided on an outer peripheral portion of the plate member and sealing the oil chamber, the plate member includes a side surface of the spring member. And a guide surface for suppressing the movement of the spring member in the circumferential direction of the piston, and a position regulating portion for regulating the position of the spring member so as not to come off from the guide surface. And

According to this configuration, the guide surface provided on the plate member and the position restricting portion complementarily suppress the movement of the spring member in the circumferential direction of the piston. Can be prevented.

In a structure in which the movement of the spring member is suppressed only by the guide surface (or only the position regulating portion), considerable strictness is required for the shape and dimensional accuracy of the guide surface. In the above configuration, since the guide surface and the position regulating portion act complementarily, the degree of freedom in the shape design of both can be increased and the dimensional accuracy can be relaxed, so that the manufacturing process is facilitated.

Preferably, the position regulating portion is a projection or a ridge provided to face the guide surface.

That is, it is preferable to provide a projection for each of the plurality of spring members, or to provide a ridge for regulating the position of the plurality of spring members collectively. The protrusion may be provided at a position where the spring member is sandwiched between the guide surface and the protrusion, or may be provided between two adjacent spring members.

It is preferable that the projection or the ridge has a height that is at least half the wire diameter of the spring member. If the height is at least about half of the wire diameter of the spring member, an effect of regulating the position so that the end of the spring member does not come off the guide surface can be obtained.

Alternatively, when the end surface of the spring member is processed flat, the height of the projection or the ridge is set to 0.5 mm.
With the above height, a sufficient effect can be obtained.

[0026]

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the dimensions of the components described in this embodiment,
The material, shape, relative arrangement, and the like are not intended to limit the scope of the present invention only to them unless otherwise specified.

The sealing device (canceller seal) according to the present embodiment is used, for example, in an automatic transmission for an automobile such as a CVT, and supports a plurality of spring members for urging a hydraulic piston, and the piston is mounted on the piston. This is to reduce the effect of the centrifugal oil pressure that acts.

The overall structure of the shift changeover portion of the automatic transmission to which the canceller seal is applied is substantially the same as that described in the above-mentioned prior art (FIG. 9), and therefore detailed description thereof will be omitted here. However, in order to facilitate understanding of the present embodiment, the same members as those of the conventional configuration in FIG. 9 will be described using the same member numbers in the following description.

FIG. 1 is a schematic configuration diagram of a cancel plate (plate member) which is a component of a sealing device (canceler seal) according to an embodiment of the present invention. FIG. 2A is a plan view of the cancel plate 1 (only a quarter is shown because of the rotationally symmetric shape), and FIG. 2B is a half sectional view of the cancel plate 1.

The canceller seal supports a plurality of return springs (spring members) 13 for urging the piston 10 toward the high-pressure oil chamber H, and forms an oil chamber X on the low-pressure oil chamber L side of the piston 10. And a seal member provided on the outer peripheral portion of the cancel plate 1 for sealing the outer peripheral portion of the oil chamber X.

The cancel plate 1 is a disk-shaped member formed by pressing a plate made of a metal material by press working or the like, and has a cylindrical portion extending substantially in the axial direction, and an end of the cylindrical portion on the piston 10 side. An outward flange portion 1c extending outward from the front end and an inward flange portion provided inward from the other end portion are integrally formed.

A protrusion 1d is provided near the inner periphery of the inward flange portion.
The projection 1d is engaged with the snap ring 12 fitted on the drum inner wall 11a, whereby the axial movement of the cancel plate 1 is restricted.

A contact surface 1a is formed substantially parallel to the piston 10 on the upper surface of the inward flange portion (the surface facing the piston 10). A return spring (spring member) 13 for urging the piston 10 toward the high-pressure oil chamber H is supported with one end abutting on the abutting surface 1a.

The inner peripheral surface of the cylindrical portion is a guide surface that rises along the side surface of the return spring 13 from the outer peripheral edge of the contact surface 1a. As shown in FIG. 1 (a), the guide surface has a substantially semi-cylindrical concave portion 1b formed in accordance with the side surface shape of the return spring 13 and an adjacent 2b.
The protrusions 1e projecting between the two return springs 13 have an uneven shape (petal shape) that alternately repeats. By arranging the return spring 13 in the concave portion 1b, the return spring 13
Can be suppressed in the circumferential direction of the piston, and the expansion and contraction of the return spring 13 is guided.

Further, in the present embodiment, a structure is provided in which an inward flange portion of the cancel plate 1 is provided with a projection (position regulating portion) 2 projecting from the contact surface 1a.
The protrusion 2 is provided at a position facing the concave portion 1b of the guide surface. At this time, the interval between the concave portion 1b of the guide surface and the projection 2 is provided slightly larger than the coil diameter of the return spring 13, and the interval between the convex portion 1e and the projection 2 is smaller than the coil diameter of the return spring 13. It is good to provide. With this configuration, the movement of the return spring 13 in the piston radial direction (inner circumferential direction) is restricted, and as a result, the end of the return spring 13 can be prevented from coming off the concave portion 1b of the guide surface.

As described above, by restricting the position by sandwiching the return spring 13 between the projection 2 and the guide surface, a force in the circumferential direction of the piston (rotational force) acts on the return spring 13 during driving. Even if you do
The projection 2 and the guide surface complementarily return spring 1
3 can be suppressed, and it is possible to reliably prevent the return spring 13 from climbing over the convex portion 1e of the guide surface and causing the return spring 13 to fall or bend and break.

Further, since the projection 2 and the guide surface act complementarily, the amount of protrusion of the convex portion 1e of the guide surface can be designed to be small. It is possible to secure the thickness and increase the strength of the cancel plate 1. Further, since the dimensional accuracy of both the projection 2 and the guide surface can be relaxed, the processing becomes easy.

The height h of the projection 2 is preferably at least half the diameter d of the return spring 13 as shown in FIG. At least the height h of the projection 2 is set to the wire diameter d.
Of the return spring 13
This is because it is possible to prevent overcoming.

When the end face of the return spring 13 is ground flat as shown in FIG. 3, the height h of the projection 2 is independent of the wire diameter of the return spring 13.
It is sufficient if 2 is 0.5 mm or more. Even in such a configuration,
The return spring 13 can be reliably prevented from getting over, and a sufficient position regulation effect can be obtained.

In the present embodiment, the spring member (return spring 13) is sandwiched between the guide surface and the position regulating portion (projection 2). However, the shape and arrangement of the position regulating portion are not limited. The present invention is not limited to this, and various modifications can be considered. One example is shown in FIGS.

In the cancel plate 1 shown in FIG. 4, a ridge 2a, which is a position regulating portion, is provided all around the position facing the guide surface. Also in this case, the interval between the concave portion 1b of the guide surface and the ridge 2a is provided slightly larger than the coil diameter of the return spring 13, and the convex portion 1e and the ridge 2a are provided.
By providing a distance smaller than the coil diameter of the return spring 13, the same effect as in the above embodiment can be obtained.

In the cancel plate 1 shown in FIG. 5, a triangular prism-shaped projection (position regulating portion) 2b is provided between two adjacent return springs 13, 13. In the case of such a configuration, the distance between the protrusion 1e of the guide surface and the protrusion 2b and the distance between two adjacent protrusions 2b, 2b may both be smaller than the coil diameter. Even with the protrusion 2b having such a configuration, the position can be regulated so that the return spring 13 does not come off the guide surface,
The same effect as the above embodiment can be obtained.

In the cancel plate 1 shown in FIGS. 6 to 8 as well, as in the example of FIG.
A projection as a position regulating portion is provided between the two. 6 shows a semi-cylindrical projection 2c, and FIG. 7 shows a semi-elliptical projection 2
d, FIG. 8 shows an example in which a columnar projection 2e is provided. In any case, by setting the size and the position of the protrusion in the same manner as in FIG. 5, the same effect as in the above embodiment can be obtained.

[0044]

As described above, according to the present invention,
Since the guide surface and the position regulating portion provided on the plate member complementarily suppress the movement of the spring member in the circumferential direction of the piston, it is possible to reliably prevent the spring member from falling down or being damaged, and to provide a sealing device. The reliability of the automatic transmission using the sealing device is improved.

In a structure in which the movement of the spring member is suppressed only by the guide surface (or only the position regulating portion), considerable strictness is required for the shape and dimensional accuracy of the guide surface. According to the present invention, since the guide surface and the position regulating portion act complementarily, the degree of freedom in the shape design of both can be increased, and the dimensional accuracy can be relaxed, so that the manufacturing process is facilitated.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a plate member used in a sealing device according to an embodiment of the present invention.

FIG. 2 is a sectional view of a main part of the plate member of FIG. 1;

FIG. 3 is a sectional view of a main part showing a modification of a plate member.

FIG. 4 is a schematic configuration diagram showing a modified example of a plate member.

FIG. 5 is a schematic configuration diagram showing a modified example of a plate member.

FIG. 6 is a schematic configuration diagram showing a modified example of a plate member.

FIG. 7 is a schematic configuration diagram showing a modified example of a plate member.

FIG. 8 is a schematic configuration diagram showing a modified example of a plate member.

FIG. 9 is a schematic half cross-sectional view of a configuration of a shift switching portion of an automatic transmission including a conventional sealing device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cancel plate (plate member) 1a Contact surface 1b Concave part (guide surface) 1c Outward flange part 1e Convex part (guide surface) 2 Projection (position regulation part) 2a Projection (position regulation part) 2b Projection (position Control part) 2c Projection (position control part) 2d Projection (position control part) 2e Projection (position control part) 3 Seal member 10 Piston 10a Cylindrical part 11 Drum 12 Snap ring 13 Return spring (spring member) 17 Multi-plate clutch H High pressure oil chamber L Low pressure oil chamber X Oil chamber (for hydraulic adjustment)

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Masaki Sato 8th Sugori, Nagaigawa, Fukushima City, Fukushima Prefecture Inside NOK Inc. F term in the company (reference) 3J057 AA04 BB04 CA09 DC01 DC05 GA12 HH02 JJ04

Claims (4)

[Claims] 1. A plate member for supporting a plurality of spring members for urging a piston toward a high-pressure oil chamber, and forming an oil chamber for adjusting hydraulic pressure on a low-pressure oil chamber side of the piston; A sealing member provided on an outer peripheral portion and sealing the oil chamber, wherein the plate member is provided along a side surface of the spring member, and suppresses movement of the spring member in a piston circumferential direction. A sealing device comprising: a guide surface to be formed; and a position regulating portion for regulating a position of the spring member so as not to come off from the guide surface. 2. The sealing device according to claim 1, wherein the position restricting portion is a projection or a ridge provided to face the guide surface. 3. A projection according to claim 2, wherein said projection or ridge has a height of at least half the wire diameter of said spring member.
The sealing device according to claim 1. 4. The sealing device according to claim 2, wherein the projection or the ridge has a height of 0.5 mm or more when an end surface of the spring member is flattened.