Seal device

Abstract: A seal ring (20) fitted into a ring groove (4) provided in the outer peripheral surface of a shaft (2) has side surfaces (21a,b) and an inner circumferential surface which receive hydraulic pressure supplied to the ring groove (4). The side surfaces (21a,b) of the seal ring (2) are tapered surfaces so that the width of the seal ring (2) at its inner circumferential surface is smaller than the width of the seal ring (20) at an outer circumferential surface (22) thereof. The outer circumferential surface (22) of the seal ring (20) is arcuate in cross section. Hydraulic pressure which acts upon one side surface (21b) of the seal ring causes the other side surface (21a) of the seal ring (20) to come into sliding contact with the side wall surface (41) of the ring groove (4). As a result, loss torque due to sliding contact is reduced. The tapered surfaces (21a) of the seal ring (20) contact the edge of the side wall surface (41) of the ring groove (4) at all times so that there is no leakage of oil.

Description: BACKGROUND OF THE INVENTION Field of the Invention This invention relates to a seal ring in which hydraulic pressure acts upon the side surface thereof, as well as to a seal device using this seal ring. Description of the Prior Art An automatic transmission employed in automotive vehicles has a hydraulic circuit which actuates clutches and brakes. A seal ring and seal device which prevent leakage of oil supplied to the hydraulic circuit are widely used. An example of a seal device is disclosed in DE-A-3805735 which shows a brake booster having a seal ring which comprises an O-ring surrounded by a Teflon® ring. As shown in Fig. 5, a seal device indicated at numeral 1 has a hydraulic passageway 3 formed in a shaft 2, a pair of ring grooves 4 provided in the outer circumferential surface of the shaft 2, and seal rings 5, which are made of synthetic resin, fitted into the ring grooves 4. The peripheral surface of each seal ring 5 is brought into sliding contact with the inner peripheral surface of a rotary housing 6 on the drive side. The hydraulic passageway 3 communicates with a working chamber 9 inside the housing 6 via a groove 7 in the outer peripheral surface of the shaft 2 and an inlet 8 provided in the housing 6. A piston 10 delimits the working chamber 9 inside the housing 6. Hydraulic pressure within the working chamber 9 slides the piston 10 to the left in Fig. 5 so as to bring clutch plates 11 on the side of housing 6 and clutch plates 13 on the side of an output shaft 12 into sliding contact, thereby transmitting the rotating motion of the housing 6 to the output shaft 12. Cutting off the supply of hydraulic pressure to the working chamber 9 frees the clutches, thereby halting the transmission of rotating motion to the output shaft 12. The groove 7 in the outer peripheral surface of the shaft 2 communicates with each of the ring grooves 4 so that hydraulic pressure that has been introduced to the ring grooves 4 brings the seal rings 5 into pressured contact with the side surfaces of the ring grooves 4 and brings the seal rings 5 into sliding contact with the inner peripheral surface of the housing 6, thereby preventing leakage of oil. In the example of Fig. 5, the forces which act upon the side surfaces of the seal rings 5 are larger than the forces which act upon the inner peripherals of the seal rings 5. As a result, the seal rings 5 are retained on the side of the shaft 2 and the outer peripheral surfaces of the seal rings 5 are brought into sliding contact with the housing 6. In this case, however, loss torque due to this sliding contact is large. Consequently, the outer circumferential surfaces of the seal rings 5 are held against the housing 6 and the side surfaces of the rings 5 are brought into sliding contact with the side wall surfaces of the ring grooves 4. An example of this is illustrated in Fig. 6. As shown in Fig. 6, seal rings 5' each have circumferentially extending annular grooves 14 in both side surfaces thereof, and a plurality of spaced, diametrically extending grooves 15 which open to the annular grooves 14. Hydraulic pressure is introduced into the grooves 14, 15 so that each seal ring 5' is brought into sliding contact with one side wall of the respective ring groove 4 by a force P1 acting upon the side surface of the seal ring 5' and so that each seal ring 5 ' is held on the side of housing 6 by a force P2 acting upon the inner circumferential surface of the seal ring 5'. In the example of Fig. 6, a sealed surface is assured over a width ℓ 1 between the side surface of each seal ring 5' and the side wall surface of the corresponding ring groove 4. However, the width ℓ 1 is small. Consequently, if the side wall surface of the ring groove 4 has been machined to have an incline (which is caused by the groove being machined at a low precision), the side wall surface wears eccentrically, the shaft 2 comes to be set off center and the rotating housing may wobble. If this occurs, the annular grooves 14 will open to the atmosphere and oil will leak out. SUMMARY OF THE INVENTION The present invention provides a seal device comprising; a shaft having an annular groove in an outer peripheral surface thereof, in which hydraulic pressure is introduced, and ring grooves of rectangular cross section provided on each side of said annular groove, each ring groove having side wall surfaces and communicating with said annular groove; a rotary housing having an inner peripheral surface and a working chamber which communicates with said annular groove; and seal rings arranged in each ring groove, each seal ring having an inner circumferential surface, an outer circumferential surface and side surfaces; wherein hydraulic pressure is applied to said inner circumferential surface and to both of said side surfaces, such that said outer circumferential surface comes into sliding contact with said inner peripheral surface of said rotary housing, and one of said side surfaces comes into sliding contact with a side wall surface of said ring groove; and CHARACTERIZED IN THAT said side surfaces are tapered, such that the width of each seal ring at the inner circumferential surface is smaller than the width of each seal ring at the outer circumferential surface thereof, said outer circumferential surface of each seal ring being arcuate in cross-section. The seal ring is preferably made of synthetic resin and has an angle of inclination of the tapered side surfaces in the range 2 to 10°, preferably 3 to 8° in view of dragging torque and amount of oil leakage. The radius of curvature of the arcuate surface of the seal ring is in the range 2 to 50 mm, preferably between 20 and 40 mm. In operation, hydraulic pressure which acts upon one side surface of the seal ring causes the other side surface of the seal ring to come into sliding contact with the side wall surface of the ring groove. As a result, loss torque due to sliding contact is reduced. One of the tapered surfaces of the seal ring contacts the edge of the side wall surface of the ring groove at all times so that there is no leakage of oil ascribable to causes experienced in the prior art. The seal device using this seal ring is such that hydraulic pressure within the working chamber inside the housing does not decline owing to leakage of oil. As a result, the piston inside the housing is reciprocated the required amount so that the brake and clutch can be operated correctly. The arcuate outer circumferential surface of the seal ring is in contact with the inner peripheral surface of the housing at all times even if there is displacement between the axis of the shaft and the axis of the output shaft. The result is outstanding sealing capability. In terms of its external shape, the sealing ring of the present invention resembles the keystone ring of an internal combustion engine. (For example, the one illustrated in US-A-3727927). The keystone ring has a barrel-shaped outer circumferential surface. However, the keystone ring of an internal combustion engine undergoes reciprocation in the axial direction along with the piston as well as expanding and contracting motion in the diametric direction within the ring groove. In order to force out residual oil between the side surface of the keystone ring and the wall surface of the ring groove at the time of the expanding and contracting motion, the keystone ring adopted is such that the side surface of the piston ring is made a tapered surface. Accordingly, upon taking into consideration the taper angle of the tapered side surfaces of the keystone ring, it is required that the wall surfaces of the ring groove be furnished with a taper angle (the angle at which the wall surfaces of the ring groove taper toward the bottom of the groove) suitable for pushing out the oil residue. Unlike this keystone ring for an internal combustion engine, the seal ring of the present invention is such that the required gap for introducing hydraulic pressure to the space between the seal ring and the side surfaces of the ring groove is assured at all times (even if the side surfaces of the ring groove are machined to maximum tolerance, e.g., even if the tapered side surfaces have an angle of inclination on the order of 0.5 ~ 1.0° ). Since this gap is completely ineffective in pushing out the oil residue, the construction and action of the oil seal according to the invention differ from the construction and action of the keystone ring for an internal combustion engine. Other features and advantages of the present invention will be apparent from the following description taken in conjunction with the accompanying drawings, in which like reference characters designate the same or similar parts throughout the figures thereof. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a sectional view illustratiang an embodiment of a seal ring according to the present invention as well as a portion in which the ring is mounted; Fig. 2 is a graph showing the relationship between hydraulic pressure and dragging torque in a test of dragging torque; Fig. 3 is a graph showing leakage of oil in a test of durability; Fig. 4 is a graph showing the relationship between inclination angle of the tapered face of a seal ring, dragging torque and amount of oil leakage; Fig. 5 is a sectional view showing an example of a sealing device wherein the above-mentioned seal ring is to be used; and Fig. 6 is a sectional view showing a seal ring according to the prior art. DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will now be described in detail with reference to the accompanying drawings. Fig. 1 is a sectional view showing seal rings 20 according to an embodiment of the present invention. The seal device using the seal rings 20 has a construction identical with that shown in Fig. 5 and therefore only the portions that come into contact with the seal rings 20 are shown in Fig. 1; other portions are not shown. The shaft 2 and housing 6 are made of steel (JIS S45C), and the seal rings 20 are made of a synthetic material having a high resistance to heat, such as polyether ether ketone (PEEK), polyphenylene sulfide (PPS) or polyimide, or cast iron. Each seal ring 20 has tapered faces 21a, 21b on both its side surfaces so that the width of the ring is reduced on the inner circumferential side of the ring. The angle of inclination of the tapered faces is made 2 ~ 10° , preferably 5° . If the angle of inclination is less than 2° , hydraulic pressure cannot be introduced to the space between the tapered face 21a and the side wall 41 of the ring groove 4, the axially directed force from the tapered face 21b intensifies and torque loss between the side wall surface of the ring groove 4 and the tapered face 21a is enlarged. This is undesirable. If the angle of inclination is greater than 10° , the width of each seal ring 20 on the inner circumferential side thereof becomes too small, the sliding contact force on the inner peripheral surface of the housing 6 weakens and problems arise in terms of sealing performance. The outer circumferential surface of each seal ring 20 defines an arcuate surface 22 having a radius of curvature of 2 ~ 20 mm, preferably 20 mm, The arcuate surface 22 is effective in that the surface 22 is brought into sliding contact with the inner peripheral surface of housing 6 at all timeseven if the housing 6 or shaft wobbles. Hydraulic pressure introduced to the space between one tapered face 21a of the seal ring 20 and the side wall surface 41 of the ring groove 4 resists the hydraulic force that acts upon the other tapered face 21b of the seal ring 20, thereby reducing the loss torque between the tapered face 21a and the side wall face 41 of the ring groove 4 and assuring a good seal. The results of testing the seal rings 20 according to this embodiment of the invention will now be described. In the test, seal rings 20 were made of synthetic resin and of cast iron. The synthetic resin seal rings were obtained by adding carbon fiber to polyether ether ketone (PEEK). The seal rings had an outer diameter of 52 mm, a width of 2.3 mm and a thickness of 2.3 mm. The radius of curvature of the arcuate surface 22 was 20 mm and the angle of inclination of the tapered faces 21a, 21b was 5°. The conventional seal ring 5, the sectional shape of which is as shown in Fig. 6, was also fabricated from a material and in basic dimensions identical with those of this embodiment of the invention. Both the conventional seal ring 5 and the seal ring 20 of this embodiment were installed in the device of Fig. 5 and tested with regard to dragging torque and durability. The results of the test of dragging torque are shown in Fig. 2, in which the conditions were a rotational speed of 2000 rpm for the housing 6, a hydraulic pressure of 0.4 to 1.2 MPa and an oil temperature of 80°C. Fig. 2 shows that the seal ring of this embodiment exhibits a dragging torque which is 30% lower than that of the prior art. This means a lower loss torque, allowing the fuel efficiency of the device 1 to be improved. Fig. 3 illustrates amount of oil leakage according to the present invention and the prior art. These are the results of a durability test in which the conditions were a rotational speed of 7000 rpm for the housing 6, a hydraulic pressure of 1.2 MPa and an oil temperature of 120°C. Fig. 3 illustrates that whereas the amount of oil leakage increases sharply after 40 hrs in the case of the prior art, the amount of oil leakage according to the present invention is low and constant even with the passage of time. Fig. 4 illustrates how dragging torque and amount of oil leakage are related to the angle of inclination of the tapered faces 21a, 21b of the seal ring 20. It should be evident from Fig. 4 that the amount of oil leakage increases at an inclination angle above 10° and that dragging torque increases at an inclination of less than 2°. Though test results are not particularly shown, it was found that the amount of wear of the housing 6 according to the invention is no different from that of the prior art if the radius of curvature of the arcuate surface 22 is made greater than 50 mm. If the radius of curvature of the arcuate surface 22 is made less than 2 mm, surface pressure increases and wear accelerates sharply. Thus, according to the seal ring of the present invention, the combination of the arcuate surface on the outer circumferential side of the seal ring and the tapered side surface of the seal ring results in balance between the hydraulic pressure that acts upon the side surfaces and the hydraulic pressure that acts upon the inner circumferential surface, thereby reducing dragging torque and minimizing leakage of oil. The seal device using this seal ring exhibits outstanding durability and makes it possible to achieve a constant piston stroke at all times.

Claims: A seal device comprising: a shaft (2) having an annular groove (7) in an outer peripheral surface thereof, in which hydraulic pressure is introduced, and ring grooves (4) of rectangular cross section provided on each side of said annular groove (7), each ring groove (4) having side wall surfaces (41) and communicating with said annular groove (7) ; a rotary housing (6) having an inner peripheral surface and a working chamber (9) which communicates with said annular groove (7); and seal rings (20) arranged in each ring groove (4), each seal ring (20) having an inner circumferential surface, an outer circumferential surface (22) and side surfaces (21a,21b); wherein hydraulic pressure is applied to said inner circumferential surface and to both of said side surfaces (21a,21b), such that said outer circumferential surface (22) comes into sliding contact with said inner peripheral surface of said rotary housing (6), and one of said side surfaces (21a) comes into sliding contact with a side wall surface (41) of said ring groove (4); and CHARACTERIZED IN THAT said side surfaces (21a,21b) are tapered, such that the width of each seal ring (20) at the inner circumferential surface is smaller than the width of each seal ring (20) at the outer circumferential surface (22) thereof, said outer circumferential surface (22) of each seal ring (20) being arcuate in cross-section. A seal device according to claim 1, wherein the angle of inclination of said tapered side surfaces (21a,21b) is in the range 2° to 20°. A seal device according to claim 1, wherein the angle of inclination of said tapered side surfaces (21a,21b) is in the range 3° to 8°. A seal device according to any preceding claim, wherein the radius of curvature of said arcuate cross section of said outer circumferential surface (22) is in the range 2mm to 50mm. A seal device according to any of claim 1 to claim 3, wherein the radius of curvature of said arcuate cross section of said outer circumferential surface (22) is in the range 20mm to 40mm. A seal device according to any preceding claim, wherein said seal ring (4) is made of synthetic resin.

Inventors: OKA TOSHIO, OKA, TOSHIO, Oka, Toshio, c/o K.K. Riken
Applicants: RIKEN KK, KABUSHIKI KAISHA RIKEN
Application year: 1995
Main classification: F16J15
IPC codes: F16J15, C09K3, F16D25