JP2596309Y2 - Seal structure for connecting oil passages between relatively rotating members of automatic transmission - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a seal structure for connecting an oil passage between two relatively rotating members.

[0002]

2. Description of the Related Art An automatic transmission for an automobile or the like requires a structure for connecting an oil passage for supplying pressurized oil between a rotating shaft and a fixed cylinder.

Conventionally, as a sealing structure of an oil passage connecting portion between such relatively rotating members, as shown in FIG. Forming three circumferential grooves 23, 24, 25,
In some cases, seal rings 26 and 27 are incorporated in peripheral grooves 24 and 25 on both sides thereof to seal a central peripheral groove 23 to which an oil passage is connected. However, in this structure, it is necessary to provide three circumferential grooves at predetermined intervals on the sliding surface, so that there is a disadvantage that the axial dimension of the oil passage connecting portion becomes large.

On the other hand, assuming that the circumferential groove of the oil passage connecting portion is reduced to one and the dimension of the seal structure in the axial direction is reduced, as shown in FIG. Seal rings 32 and 33 are arranged on both sides, and a backup ring 34 is incorporated between the two seal rings (Japanese Utility Model Laid-Open No. 1-87365). As shown in FIG.
1. Seal rings 42 and 43 are provided on both sides of the seal 1 and the seals 42 and 43 are pressed against the sliding surface and the surface of the circumferential groove 41 by hydraulic pressure received on the tapered surfaces 44 and 45 of the seal ring (Japanese Patent Publication No. 3-51953). Publication).

[0005]

However, the structure shown in FIG. 6 has a drawback that the relatively rotating backup ring 34 and the outer member 35 come into contact with each other, so that the abrasion of the two tends to progress, and noise and vibration are likely to occur. . In addition, the circumferential groove 3
There is also a problem that the work of assembling the two seal rings 32, 33 and the backup ring 34 into one is difficult.

On the other hand, in the structure shown in FIG. 7, when the inner member 46 and the outer member 47 rotate relative to each other in a state where no hydraulic pressure is generated, the inner surfaces of the seal rings 42 and 43 may come into contact with each other and slide. However, at this time, if the edges of the notch 48 formed on the inner surface come into contact with each other, there is a disadvantage that the seal ring is easily chipped or worn.

In view of the above, the present invention solves the above-mentioned problem, and in a seal structure in which a single circumferential groove is provided in an oil passage connecting portion and a seal ring is incorporated in the circumferential groove, the wear and the sealing performance of the seal ring are reduced. It is an object of the present invention to provide a structure that does not cause a decrease in the image quality.

[0008]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides an automatic transmission in which one of a sliding surface of an inner member and a sliding surface of an outer member, which rotates relative to each other coaxially, has a circumferential surface surrounding the sliding surface. A groove is provided, an oil passage formed in the inner member and the outer member is communicated with a central portion of the circumferential groove, and seal rings are provided at both axial ends of the circumferential groove. A relative rotating member of an automatic transmission in which a spacing member disposed at intervals in the direction is provided integrally with one of the seal rings, and the thickness of the spacing member is set to be smaller than the radial thickness of the two seal rings. For connecting oil passages between
It has a rule structure .

In the above structure, the length of the spacing member can be set larger than the diameter of the oil passage communicating with the circumferential groove.

[0010]

In the above structure, since the spacing member positions both seal rings on both sides of the circumferential groove, when pressure oil is supplied to the center of the circumferential groove from one of the oil passages of the inner member and the outer member. The two seal rings are pressed against the side surface of the circumferential groove and one sliding surface to seal the circumferential groove.

On the other hand, when the pressure oil is not supplied or when the oil pressure is low and the two seal rings approach each other, the spacing member stops the movement of the two seal rings and holds them at a predetermined position. Such an oil passage connection seal structure has a
Since the holding material is provided integrally with one seal ring,
Just insert both seal rings into the peripheral groove of the side member,
Both seal rings are positioned on both sides of the circumferential groove by holding material
As a result, there is no need to separately install the spacing material.
Required and easy to assemble. Also,
A spacing material with a constant thickness is provided integrally with the seal ring.
Therefore, wear due to contact of the outer member with the spacing member is prevented.
This stops noise and vibration during rotation .

[0012]

1 and 2 show an embodiment of the present invention. In the figure, reference numeral 1 denotes a rotating inner member, and 2 denotes a cylindrical outer member which is fitted to the outer side of the inner member 1 and relatively rotates. 3 and a pressure oil demand oil passage 4 are provided.

A circumferential groove 7 is formed in the sliding surface 5 of the inner member 1 around the sliding surface 5 with the pressure oil supply oil passage 3 as a center. The peripheral groove 7 forms an annular groove together with the sliding surface 6 of the outer member 2, and the pressure oil demand oil passage 4 communicates with the center of the peripheral groove 7.

On both sides of the circumferential groove 7, seal rings 8 and 9 are respectively incorporated. The two seal rings 8 and 9 are assembled with a gap in the axial direction and the radial direction between them and with the circumferential groove 7. An oil passage 10 connects the oil passage 3 and the hydraulic oil demand oil passage 4. further,
The two seal rings 8 and 9 have one end surfaces 11 and 12 serving as seal surfaces that are in close contact with the sliding surface 6 of the outer member 2.
Reference numerals 3 and 14 are seal surfaces that are in close contact with the side surfaces of the circumferential groove 7.

Further, on the inner surface 15 of the seal ring 8,
A plurality of spacing members 17 are provided integrally at predetermined intervals in the circumferential direction. Each of the spacing members 17 is the same as that shown in FIG.
With the outer surfaces 13 and 14 of the seal rings 8 and 9 in contact with both side surfaces of the circumferential groove 7 as described above, the length is opposed to the center of the inner surface 16 of the seal ring 9 with a small gap 18 therebetween. The end face of the spacing member 17 and the inner face 16 of the seal ring 9 are formed as flat faces facing in parallel. The length L of each of the spacing members 17
Is formed larger than the diameter of the pressure oil supply oil passage 3 and the pressure oil demand oil passage 4, and the thickness d is formed smaller than the radial thickness t of each of the seal rings 8 and 9.

This embodiment has the above-described structure. Just by inserting the seal rings 8 and 9 into the circumferential groove 7 of the inner member 1, both the seal rings 8 and 9 are Since it is positioned on both sides, it can be easily assembled.

When pressure oil is supplied from the pressure oil supply oil passage 3 to the circumferential groove 7 in the assembled state, the two seal rings 8, 9 are separated by the spacing member 17 from the diameter of the pressure oil supply passage 3. Are located at large intervals, so that the hydraulic oil
0, the inner surfaces 15, of both seal rings 8, 9
An outward pressure acts on 16 to move the seal rings 8, 9 outward. For this reason, even when the end face of the spacing member 17 and the inner face 16 of the seal ring 9 are in close contact with each other at the time of assembling , the outer faces 13, 14 and the end faces 11, 12 of the seal rings 8, 9 are respectively supplied at the time of supplying the pressurized oil. Pressure is applied to both sides of the peripheral groove 7 and the sliding surface 6 of the outer member 2 to seal between the peripheral groove 7 and the sliding surfaces 5 and 6.

In this case, even if the spacing member 17 is located at a position where the pressure oil supply oil passage 3 and the pressure oil demand oil passage 4 overlap, the thickness of the spacing member 17 is smaller than the thickness of the seal rings 8 and 9. Since the pressurized oil flows through around the spacing member 17, a sufficient amount of oil can be obtained.

The inner and outer members 1 and 2 rotate relative to each other in a state where the pressure oil does not flow into the circumferential groove 7 or a state where the pressure of the pressure oil is small,
When the two seal rings 8 and 9 approach each other, the spacing member 17 stops the movement of the seal ring 9 and keeps the gap between the two seal rings 8 and 9 substantially constant. In this case, since the spacing member 17 is in contact with the central portion of the inner surface 16 of the seal ring 9 on the flat surfaces, no edge load occurs, and chipping and abnormal wear do not occur on the surfaces of the seal rings 8 and 9. .

FIGS. 3 and 4 show another embodiment.
In this example, the seal rings 8 and 9 incorporated in the circumferential groove 7 are provided with spacing members 17 and 17 ′, respectively.
The inner surfaces 15, 16 of the seal rings 8, 9 facing the respective spacing members 17, 17 'are formed as flat surfaces. By providing the spacing members in both seal rings in this manner, the number of spacing members in one seal ring can be reduced, and the manufacturing cost of each ring can be reduced.

In each of the above embodiments, the peripheral groove 7 and the pressure oil supply oil passage 3 are provided on the inner member 1, but may be provided on the outer member 2 instead.

The spacing members 17 and 17 'have a circular cross section, but may have an oval cross section, an elliptical cross section, or a square cross section.

[0023]

[Effect] As described above, according to the present invention, the two seal rings are positioned on both sides of the circumferential groove by the spacing material.
The pressure oil introduced into the circumferential groove ensures that both seal rings are pressed against both side surfaces of the circumferential groove to achieve stable sealing performance, and prevents the inner surfaces of the seal ring from contacting each other, resulting in chipping or wear of the seal ring. There is an effect that can be prevented.

Further, since only one circumferential groove is provided on the sliding surface of the inner and outer members, the axial length of the seal structure can be reduced, and the size and weight of the device incorporating the seal structure can be reduced. Furthermore, the spacing material should be
It is integrated with the ring, so it can be easily assembled
And wear due to contact of the outer member with the spacing material
Noise and vibration during rotation are prevented.
There are also advantages.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment.

FIG. 2 is a perspective view showing a part of the above seal ring.

FIG. 3 is a sectional view showing another embodiment.

FIG. 4 is a perspective view showing the same seal ring.

FIG. 5 is a sectional view showing a conventional example.

FIG. 6 is a sectional view showing another conventional example.

FIG. 7 is a sectional view showing another conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Inner member 2 Outer member 3 Pressure oil supply oil passage 4 Pressure oil demand oil passage 5, 6 Sliding surface 7 Peripheral groove 8, 9 Seal ring 15, 16 Inner surface 17, 17 'Spacing material

Claims (2)

(57) [Scope of request for utility model registration] A sliding groove is provided on one of the sliding surfaces of an inner member and an outer member which rotate relative to each other coaxially in an automatic transmission, and an oil passage formed in the inner member and the outer member is provided. A seal ring is provided at both ends in the axial direction of the circumferential groove, communicating with the central portion of the circumferential groove, and a spacing member arranged at intervals in the circumferential direction between the two seal rings.
A seal structure for connecting an oil passage between relatively rotating members of an automatic transmission, wherein the seal member is provided integrally with one of the seal rings, and the thickness of the spacing member is set smaller than the radial thickness of the seal rings. . 2. The seal structure between relatively rotating members according to claim 1, wherein the length of the spacing member is set larger than the diameter of an oil passage communicating with the circumferential groove.