JPH0651678U - Seal structure between members that rotate relative to each other - Google Patents

Abstract

(57) [Summary] [PROBLEMS] The present invention provides a structure capable of reliably sealing pressure oil by means of one circumferential groove and two seal rings in an oil passage connecting portion between members that rotate relative to each other. [Structure] Seal rings 8 and 9 are incorporated on both sides of a peripheral groove 7 provided in an inner member 1, and a spacing member 17 is provided on one seal ring 8. The oil passages 3 and 4 are connected to the central portion of the circumferential groove 7, and the length of the spacing member 17 is made larger than the diameter of the oil passages 3 and 4. When pressure oil is supplied to the circumferential groove 7, the seal rings 8 and 9
Is pressed against the peripheral groove 7 and the outer member 2, and the approach of the both rings 8 and 9 is stopped by the spacing member 17.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a seal structure for connecting an oil passage between two members that rotate relative to each other.

[0002]

[Prior art]

 In automatic transmissions of automobiles, it is necessary to have a structure that connects an oil passage for supplying pressure oil between a rotating shaft and a fixed cylinder.

Conventionally, as a sealing structure of an oil passage connecting portion between such members that rotate relative to each other, as shown in FIG. 5, it is arranged in parallel on the peripheral surface of the rotating shaft 21 that rotates relative to the outer member 22. There is one in which three peripheral grooves 23, 24, 25 are formed, and seal rings 26, 27 are incorporated in the peripheral grooves 24, 25 on both sides thereof to seal the central peripheral groove 23 to which the oil passage is connected. However, in this structure, it is necessary to provide three circumferential grooves on the sliding surface at a predetermined interval, so that there is a drawback that the axial dimension of the oil passage connecting portion becomes large.

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

[0005]

[Problems to be solved by the device]

 However, the structure shown in FIG. 6 has a drawback that the relative rotation of the backup ring 34 and the outer member 35 are in contact with each other, so that the wear of both of them easily progresses and noise and vibration are likely to occur. Further, the work of assembling the two seal rings 32 and 33 and the backup ring 34 in the circumferential groove 31 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 side surfaces of both seal rings 42 and 43 may come into contact with each other and slide. However, at this time, if the edge portions of the notch 48 formed on the inner surface are in contact with each other, there is a drawback that the seal ring is likely to be chipped or worn.

In view of the above, the present invention solves the above-mentioned problems, and in the seal structure in which one peripheral groove is provided in the oil passage connecting portion and the seal ring is incorporated in the peripheral groove, wear of the seal ring and sealing performance are improved. The purpose is to provide a structure that does not cause a decrease in

[0008]

[Means for Solving the Problems]

 In order to solve the above problems, the present invention provides a circumferential groove surrounding the sliding surface on one of the sliding surfaces of the inner member and the outer member that rotate relative to each other coaxially, and forms the inner member and the outer member. These oil passages are communicated with the central part of the circumferential groove, and seal rings are provided at both axial ends of the circumferential groove, and are arranged with a circumferential gap between the seal rings. The spacing member is provided, and the thickness of the spacing member is set smaller than the radial thicknesses of the both seal rings.

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]

[Action]

 In the above structure, since the spacing member positions both seal rings on both sides of the circumferential groove, if 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, both seal rings will be sealed. The ring is 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 the oil pressure is low and both seal rings approach each other, the spacing member stops the movement of both seal rings and holds them at a predetermined position.

[0012]

【Example】

 1 and 2 show an embodiment of this invention. In the figure, 1 is a rotating inner member, and 2 is a cylindrical outer member that is fitted to the outside of the inner member 1 and rotates relative to each other. A passage 3 and a pressure oil demand oil passage 4 are provided.

A circumferential groove 7 is formed on the sliding surface 5 of the inner member 1 around the pressure oil supply oil passage 3 and around the sliding surface 5. 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.

Seal rings 8 and 9 are incorporated on both sides of the circumferential groove 7, respectively. The both seal rings 8 and 9 are assembled with a gap between them and the circumferential groove 7 in the axial direction and the radial direction, and the gap formed between the both seal rings 8 and 9 is the pressure oil supply. An oil passage 10 connects the oil passage 3 and the pressure oil demand oil passage 4. Further, both of the seal rings 8 and 9 are such that one end surface 11 and 12 serves as a seal surface that is closely adhered to the sliding surface 6 of the outer member 2, and the outer surfaces 13 and 14 are close to the side surface of the circumferential groove 7. Has become.

A plurality of spacing members 17 are integrally provided on the inner side surface 15 of the seal ring 8 with a predetermined spacing in the circumferential direction. As shown in FIG. 1, each spacing member 17 is smaller than the central portion of the inner side surface 16 of the seal ring 9 when the outer side surfaces 13 and 14 of both seal rings 8 and 9 are in contact with both side surfaces of the circumferential groove 7. The gaps 18 are formed so as to face each other with a gap 18 in between, and the end faces of the spacing member 17 and the inner side face 16 of the seal ring 9 are formed as flat faces facing each other in parallel. Further, the length L of each spacing member 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 the radial thickness t of each seal ring 8, 9. Is formed smaller than.

This embodiment has the structure as described above, and by simply 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 separated from the circumferential groove 7 by the spacing member 17. Since it is positioned on both sides, it can be easily assembled.

When the pressure oil is supplied from the pressure oil supply oil passage 3 to the circumferential groove 7 in the assembled state as described above, both the seal rings 8 and 9 are separated from the diameter of the pressure oil supply passage 3 by the spacing member 17. Since they are positioned at large intervals, outward pressure acts on the inner side surfaces 15 and 16 of both seal rings 8 and 9 while the pressure oil passes through the oil passage 10, so that the seal rings 8 and 9 are removed. Move in the direction. Therefore, even when the end surface of the spacing member 17 and the inner surface 16 of the seal ring 9 are in close contact with each other, the outer surfaces 13 and 14 of the seal rings 8 and 9 and the end surfaces 11 and 12 are located on both sides of the circumferential groove 7, respectively. The surface and the sliding surface 6 of the outer member 2 are crimped to seal between the circumferential groove 7 and the sliding surfaces 5, 6.

In this case, even if the spacing member 17 is positioned to overlap the pressure oil supply oil passage 3 and the pressure oil demand oil passage 4, the thickness of the spacing member 17 is smaller than the thickness of the seal rings 8 and 9. Since the pressure oil flows around the space holding member 17, a sufficient amount of oil can be obtained.

Further, when the inner and outer members 1 and 2 rotate relative to each other when the pressure oil does not flow in the circumferential groove 7 or the pressure of the pressure oil is small, and the seal rings 8 and 9 approach each other, the spacing member 17 stops the movement of the seal ring 9 and keeps the distance between both seal rings 8 and 9 substantially constant. In this case, since the spacing member 17 comes into contact with the central portion of the inner side surface 16 of the seal ring 9 between the flat surfaces, edge loading does not occur and the surface of the seal rings 8 and 9 is not chipped or abnormally worn. Does not happen.

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

Although the circumferential groove 7 and the pressure oil supply oil passage 3 are provided in the inner member 1 in each of the above embodiments, they may be provided in the outer member 2 on the contrary.

Further, although the spacing members 17, 17 ′ have a circular cross section, they may have an elliptical cross section, an ellipse, a quadrangle, or the like.

[0023]

【effect】

 As described above, according to the present invention, since the two seal rings are positioned on both sides of the circumferential groove by the spacing member, the pressure oil introduced into the circumferential groove surely presses both seal rings to both side surfaces of the circumferential groove. In addition to providing stable and stable sealing performance, contact between the inner surfaces of the seal ring is prevented, and chipping and wear of the seal ring can be prevented.

Further, since only one circumferential groove is provided on the sliding surfaces of the inner and outer members, the axial length of the seal structure can be shortened, and the device incorporating the seal structure can be reduced in size and weight.

[Brief description of 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 seal ring of the above.

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]

 1 Inner member 2 Outer member 3 Pressure oil supply oil passage 4 Pressure oil demand oil passage 5, 6 Sliding surface 7 Circumferential groove 8, 9 Seal ring 15, 16 Inner side surface 17, 17 'Interval holding material

Claims (2)

[Scope of utility model registration request] 1. A circumferential groove surrounding the sliding surface is provided on one sliding surface of an inner member and an outer member that rotate relative to each other coaxially, and an oil passage formed in the inner member and the outer member is formed in the circumferential groove. A seal ring is provided at both ends in the axial direction of the circumferential groove, which communicates with the central portion, and a spacing member disposed with a gap in the circumferential direction is provided between both seal rings. A seal structure between relatively rotating members, the thickness of which is set to be smaller than the radial thickness of both seal rings. 2. The seal structure between relative rotating members according to claim 1, wherein the length of the spacing member is set larger than the diameter of the oil passage communicating with the circumferential groove.