WO2014188616A1 - ピストン一体シール - Google Patents
ピストン一体シール Download PDFInfo
- Publication number
- WO2014188616A1 WO2014188616A1 PCT/JP2013/079187 JP2013079187W WO2014188616A1 WO 2014188616 A1 WO2014188616 A1 WO 2014188616A1 JP 2013079187 W JP2013079187 W JP 2013079187W WO 2014188616 A1 WO2014188616 A1 WO 2014188616A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic chamber
- clutch
- seal
- piston
- edge portion
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
Definitions
- the present invention relates to a piston integrated seal used for a hydraulic clutch of an automatic transmission of a vehicle.
- FIG. 4 shows a hydraulic clutch using a conventional piston integral seal
- FIG. 5 shows a schematic configuration of the conventional piston integral seal.
- reference numeral 1 is an annular clutch cylinder that rotates together with a drive shaft (not shown), and reference numeral 2 is disposed in the clutch cylinder 1 so as to be axially movable.
- a clutch piston defining a hydraulic chamber S1 between the end plate portion 11 and reference numeral 3 is disposed in a space S2 opposite to the hydraulic chamber S1 when viewed from the clutch piston 2 and has an inner diameter within the clutch cylinder 1.
- a spring holder locked to the cylindrical portion 13 reference numeral 4 is a return spring appropriately inserted between the clutch piston 2 and the spring holder 3, and reference numeral 5 is axially moved toward the clutch cylinder 1 side.
- It is a multi-plate clutch comprising a plurality of driven plates 52 which is engaged in the circumferential direction.
- This type of hydraulic clutch applies a hydraulic pressure to the hydraulic chamber S1 via a pressure guide port 14 opened in the inner cylinder portion 13 of the clutch cylinder 1 or releases the hydraulic pressure, whereby the piston 2 is connected to the clutch cylinder 1.
- the inside of the multi-plate clutch 5 is displaced in the axial direction, whereby the drive plate 51 and the driven plate 52 of the multi-plate clutch 5 are frictionally engaged and the frictional engagement is released to perform the clutch intermittent operation.
- packing such as an O-ring has been used as a sealing means for the inner and outer circumferences of the clutch piston 2, but in order to improve fuel efficiency and reduce shift shock (shock generated when clutch friction is engaged), the clutch piston
- pistons having seal lips 101, 101 slidably in close contact with the outer cylinder part 12 and the inner cylinder part 13 of the clutch cylinder 1 facing the hydraulic chamber S 1 side are required.
- the seal 100 has become mainstream. That is, the piston integrated seal 100 is integrally formed on the clutch piston 2 with a rubber-like elastic material (rubber material or synthetic resin material having rubber-like elasticity) (see, for example, Patent Document 1 below).
- the seal lip 101 is generally located closer to the hydraulic chamber S1 than the seal edge portion where the surface pressure P (tightening margin L) with respect to the mating sliding surface indicated by the two-dot chain line in the drawing is the largest.
- the angle ⁇ of the inclined surface is larger than the angle ⁇ of the inclined surface on the opposite side, and the axial length Ha from the seal edge portion to the root portion on the opposite side to the hydraulic chamber S1 is relatively long.
- the seal lip 101 has directionality, so the distribution of the surface pressure P is also asymmetric on both sides of the maximum portion, and the clutch by applying hydraulic pressure to the hydraulic chamber S1.
- the clutch piston 2 strokes to the clutch engagement release side (hydraulic chamber S1 side) by the urging force of the return spring 4 when the hydraulic pressure of the hydraulic chamber S1 is released.
- friction there is a tendency for friction to increase, which makes it difficult to control the hydraulic pressure of the hydraulic clutch, and there is a possibility that a delay in the shift response will occur.
- the present invention has been made in view of the above points, and its technical problem is to reduce the difference in friction caused by the sliding direction due to the directionality of the seal lip, thereby reducing the shift of the hydraulic clutch. It is to improve responsiveness.
- the piston integrated seal according to the invention of claim 1 has a seal lip provided integrally with the clutch piston of the hydraulic clutch and facing the hydraulic chamber side, This seal lip is formed with a main seal edge part on the hydraulic chamber side and a sub seal edge part on the anti-hydraulic chamber side on the sliding part with the mating sliding surface, and these main seal edge part and sub seal edge part are In the unmounted state, the angle of the slope on the hydraulic chamber side is smaller than the angle of the slope on the anti-hydraulic chamber side, and in the mounted state, the angle of the slope on the hydraulic chamber side and the angle of the anti-hydraulic chamber side with respect to the mating sliding surface is approximately It is characterized by being equivalent.
- the piston integrated seal according to the invention of claim 2 is characterized in that, in the configuration of claim 1, the margin of tightening of the sub seal edge portion is smaller than that of the main seal edge portion.
- a piston-integrated seal according to a third aspect of the invention is characterized in that, in the configuration according to the first or second aspect, the secondary seal edge portion is located on the side opposite to the hydraulic chamber from the hydraulic chamber side base surface of the seal lip. It is.
- the sliding portion of the seal lip is formed with the main seal edge portion on the hydraulic chamber side and the sub seal edge portion on the anti-hydraulic chamber side, thereby forming a contact with the mating sliding surface. Since the contact area is small, the friction is reduced, and the angle of the slope on the hydraulic chamber side and the angle on the anti-hydraulic chamber side with respect to the mating sliding surface is approximately the same when mounted (contacted with the mating sliding surface). Therefore, the difference between the friction during the stroke toward the hydraulic chamber and the friction during the stroke toward the anti-hydraulic chamber is reduced. For this reason, the shift response of the hydraulic clutch can be improved.
- the configuration is such that the tightening margin of the sub seal edge portion is smaller than that of the main seal edge portion, deformation of the main seal edge portion is absorbed by the sub seal edge portion.
- the change in the contact load of the main seal edge portion with respect to the sliding surface is suppressed, and this also reduces the difference between the friction during the stroke toward the hydraulic chamber and the friction during the stroke toward the anti-hydraulic chamber.
- the sub seal edge portion is positioned on the side opposite to the hydraulic chamber from the hydraulic chamber side base surface of the seal lip, deformation of the sub seal edge portion due to application of hydraulic pressure is suppressed.
- the effect of suppressing the seal lip deformation is enhanced, and the pressure resistance of the seal lip can be improved.
- FIG. 1 is a side sectional view showing a preferred embodiment of a piston integrated seal according to the present invention by cutting along a plane passing through an axis O together with a part of a hydraulic clutch. It is explanatory drawing which shows the principal part of preferable embodiment of the piston integrated seal which concerns on this invention. It is explanatory drawing which shows the slope angle in the unmounted state in the principal part of preferable embodiment of the piston integrated seal which concerns on this invention, and a mounted state.
- FIG. 6 is a one-side sectional view showing a conventional piston-integrated seal cut along a plane passing through an axis O together with a part of a hydraulic clutch. It is explanatory drawing which shows a part of conventional piston integrated seal.
- FIG. 1 is a one-side sectional view showing a piston integrated seal in this embodiment together with a part of a hydraulic clutch.
- Reference numeral 1 is a clutch cylinder, and reference numeral 2 is arranged in the clutch cylinder 1 so as to be axially movable.
- a clutch piston that defines a hydraulic chamber S1 between the clutch cylinder 1 and reference numeral 1 is disposed in a space S2 opposite to the hydraulic chamber S1 when viewed from the piston 2 (hereinafter referred to as an anti-hydraulic chamber side space) S2.
- a reference numeral 4 is a return spring interposed between the clutch piston 2 and the spring holder 3 in an appropriately compressed state, and a reference numeral. 5 is a multi-plate clutch.
- the clutch cylinder 1 has an end plate part 11, an outer cylinder part 12 and an inner cylinder part 13 extending from an outer diameter and an inner diameter thereof, and is rotated around an axis O together with a drive shaft (not shown). Further, in the inner cylinder portion 13 of the clutch cylinder 1, a pressure introducing port 14 for introducing hydraulic pressure by oil (ATF) into the hydraulic chamber S1 is opened.
- ATF hydraulic pressure by oil
- the clutch piston 2 is a metal press-formed product, and extends from the outer diameter portion of the pressure receiving portion 21 to the counter-hydraulic chamber side space S2 side in the axial direction facing the end plate portion 11 of the clutch cylinder 1.
- the outer cylinder part 22 that opposes the outer cylinder part 12 of the clutch cylinder 1 in the radial direction, and extends from the inner diameter part of the pressure receiving part 21 to the side opposite to the hydraulic chamber S1 and faces the inner cylinder part 13 of the clutch cylinder 1 in the radial direction. It has the inner cylinder part 23 to do.
- a clutch pressing portion 24 is formed at the distal end portion of the outer cylinder portion 22 of the clutch piston 2, and an inward flange portion 25 is formed at the distal end portion of the inner cylinder portion 13 of the clutch piston 2.
- the return spring 4 constantly urges the clutch piston 2 in a direction to reduce the volume of the hydraulic chamber S1, and is composed of a coil spring, and a plurality of return springs 4 are arranged at predetermined intervals in the circumferential direction.
- the multi-plate clutch 5 includes a plurality of drive plates 51 that are engaged with the outer cylinder of the clutch cylinder 1 in a circumferentially movable state and a clutch hub 53 that is provided on the driven shaft side (not shown). It has a structure in which a plurality of driven plates 52 locked in the circumferential direction so as to be movable in the axial direction are alternately arranged in the axial direction.
- the clutch piston 2 is integrally provided with a piston integrated seal 6 made of rubber-like elastic material (rubber material or synthetic resin material having rubber-like elasticity).
- the piston integrated seal 6 extends so as to cover the outer peripheral surface of the outer cylindrical portion 22 of the clutch piston 2, the surface of the pressure receiving portion 21 on the hydraulic chamber S1, the inner peripheral surface of the inner cylindrical portion 23, and the inward flange portion 25.
- a base 61, and seal lips 62, 62 that are located near the outer diameter of the pressure receiving portion 21 and the inner diameter of the inward flange 25 and that extend from the base 61 toward the hydraulic chamber S1.
- the outer peripheral side seal lip 62 is slidably in close contact with the inner peripheral surface of the outer cylindrical portion 12 of the clutch cylinder 1, and the inner peripheral side seal lip 62 is slid with the outer peripheral surface of the inner cylindrical portion 13 of the clutch cylinder 1. It is to be moved closely.
- a plurality of protrusions 63 are formed at equal intervals in the circumferential direction on the portion of the base 61 of the piston integrated seal 6 that is bonded to the pressure receiving portion 21 of the clutch piston 2.
- the protrusion 63 prevents the hydraulic chamber S1 from being closed when the base 61 comes into close contact with the end plate portion 11 of the clutch cylinder 1 when the clutch piston 2 moves to its top dead center position.
- the seal lip 62 has a main seal edge on the hydraulic chamber S ⁇ b> 1 side at a sliding portion with the inner peripheral surface of the outer cylinder portion 12 or the outer peripheral surface of the inner cylinder portion 13 of the clutch cylinder 1.
- a portion 62a and a sub seal edge portion 62b on the counter-hydraulic chamber side space S2 side are formed.
- the raised height of the auxiliary seal edge portion 62b is lower than the raised height of the main seal edge portion 62a.
- the tightening margin L2 of the sub seal edge portion 62b is set smaller than the tightening margin L1 of the main seal edge portion 62a with respect to the 13 outer peripheral surface.
- the raised height of the sub seal edge 62b is formed lower than the inner peripheral surface of the conventional seal lip indicated by the broken line in FIG.
- the length Ha0 from the main seal edge portion 62a to the root portion on the anti-hydraulic chamber side space S2 side is opposite from the seal edge portion of the seal lip 101 according to the prior art shown in FIG. It is shorter than the axial length Ha to the root portion on the hydraulic chamber side space S2 side.
- the axial length Ha1 between the main seal edge portion 62a and the sub seal edge portion 62b is shorter than the axial length Ha2 from the sub seal edge portion 62b to the root portion.
- the main seal edge portion 62a is located on the hydraulic chamber S1 side by an axial distance Hb1 from the base surface 61a on the hydraulic chamber S1 side of the seal lip 62 of the base portion 61, but the sub seal edge portion 62b is pivoted from the base surface 61a.
- the angle ⁇ 1 of the inclined surface on the hydraulic chamber S1 side when not attached is smaller than the angle ⁇ 1 of the inclined surface on the opposite side (space S2 side) to the hydraulic chamber S1 ( ⁇ 1 ⁇ 1), and the sub seal edge portion 62b is also formed so that the angle ⁇ 2 of the inclined surface on the hydraulic chamber S1 side is smaller than the angle ⁇ 2 of the inclined surface on the opposite side (space S2 side) from the hydraulic chamber S1 when not attached. ( ⁇ 2 ⁇ 2). Further, ⁇ 1> ⁇ 2 and ⁇ 1> ⁇ 2.
- the seal lip 62 is bent and deformed with its root as a fulcrum, so that the main seal edge portion 62a is in contact with the inner peripheral surface of the outer cylinder portion 12 of the clutch cylinder or the outer peripheral surface of the inner cylinder portion 13.
- the angle ⁇ 1 ′ formed by the inclined surface on the hydraulic chamber S1 side is slightly larger than ⁇ 1, and the angle ⁇ 1 ′ formed by the inclined surface on the anti-hydraulic chamber side space S2 side is slightly decreased from ⁇ 1, and as a result, ⁇ 1′ ⁇ 1 ′. It will be.
- the angle ⁇ 2 ′ formed by the inclined surface on the hydraulic chamber S1 side is slightly larger than ⁇ 2, and the angle ⁇ 2 ′ formed by the inclined surface on the anti-hydraulic chamber side space S2 side is ⁇ 2 It decreases slightly, and as a result, ⁇ 2′ ⁇ 2 ′.
- the hydraulic clutch having the above configuration applies a hydraulic pressure to the hydraulic chamber S1 via the pressure guide port 14 or releases the hydraulic pressure, whereby the clutch piston 2 is displaced in the axial direction in the clutch cylinder 1 and is The plate clutch 5 is connected or disconnected.
- the clutch piston 2 is displaced downward (the anti-hydraulic chamber side space S2 side) in FIG.
- the second clutch pressing portion 24 presses the multi-plate clutch 5 to frictionally engage the drive plate 51 and the driven plate 52.
- the multi-plate clutch 5 is in a connected state, and drive torque from a drive shaft (not shown) is not shown via the clutch cylinder 1, the drive plate 51, the driven plate 52 and the clutch hub 53 of the multi-plate clutch 5. To the driven shaft.
- the piston integral seal 6 provided integrally with the clutch piston 2 has the inner and outer seal lips 62 of the inner peripheral surface of the outer cylinder portion 12 of the clutch cylinder 1 and the inner cylinder portion 13. It slides in close contact with the outer peripheral surface.
- the sliding portion is formed with a main seal edge portion 62a on the hydraulic chamber S1 side and a sub seal edge portion 62b on the anti-hydraulic chamber side space S2 side, so that the outer cylinder portion 12 of the clutch cylinder 1 and
- the thickness of the seal lip 62 is reduced as a whole compared to the conventional shape shown by the broken line in FIG.
- the surface pressures P1 and P2 due to the main seal edge portion 62a and the sub seal edge portion 62b shown in FIG. 3 are smaller as a whole than the conventional surface pressure shown by the broken lines, and the gap between the seal edge portions 62a and 62b is a lubricating groove. Therefore, friction is effectively reduced.
- the surface pressure P1 of the main seal edge portion 62a and the sub seal edge portion 62b with respect to the inner peripheral surface of the outer cylinder portion 12 or the outer peripheral surface of the inner cylinder portion 13 of the clutch cylinder is substantially equal to the angle ⁇ 2 ′ of the slope on the S2 side.
- P2 are distributed substantially symmetrically on the hydraulic chamber S1 side and the counter-hydraulic chamber side space S2 side, respectively. Accordingly, the friction during the stroke of the clutch piston 2 toward the anti-hydraulic chamber side space S2 (the direction in which the multi-plate clutch 5 is pressed) and the clutch toward the hydraulic chamber S1 side (the direction in which the press on the multi-plate clutch 5 is released) The difference in friction during the stroke of the piston 2 is effectively reduced. For this reason, the shift response of the hydraulic clutch can be improved.
- the fastening margin L2 of the sub seal edge portion 62b is smaller than the fastening margin L1 of the main seal edge portion 62a with respect to the inner peripheral surface of the outer cylinder portion 12 or the outer peripheral surface of the inner cylinder portion 13 of the clutch cylinder. Therefore, the deformation of the main seal edge portion 62a is absorbed by the sub seal edge portion 62b. For this reason, regardless of the change in the hydraulic pressure of the hydraulic chamber S1 acting on the seal lip 62, the change in the contact load of the main seal edge portion 62a is suppressed, and this also reduces the difference in friction described above.
- the sub seal edge portion 62b is positioned on the side opposite to the hydraulic chamber S1 by the axial distance Hb2 from the base surface 61a of the seal lip 62 on the hydraulic chamber S1 side of the base 61, so that the hydraulic pressure to the hydraulic chamber S1 is reduced. Since the deformation of the sub seal edge portion 62b due to the application is suppressed, the effect of suppressing the deformation of the seal lip 62 by the sub seal edge portion 62b is enhanced, and from the main seal edge portion 62a to the root portion on the side of the anti-hydraulic chamber side space S2. Since the length Ha0 itself is shorter than the conventional one shown in FIG. 5, the pressure resistance can be improved even though the thickness of the seal lip 62 is smaller than the conventional one.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
Description
2 クラッチピストン
6 シール
61 基部
62 シールリップ
62a 主シールエッジ部
62b 副シールエッジ部
S1 油圧室
S2 反油圧室側空間
Claims (3)
- 油圧クラッチのクラッチピストンに一体に設けられて油圧室側を向いたシールリップを有し、このシールリップは、相手摺動面との摺動部に、油圧室側の主シールエッジ部と、反油圧室側の副シールエッジ部が形成され、これら主シールエッジ部及び副シールエッジ部は、未装着状態では油圧室側の斜面の角度が反油圧室側の斜面の角度より小さく、装着状態では相手摺動面に対する油圧室側の斜面の角度と反油圧室側の斜面の角度が略同等であることを特徴とするピストン一体シール。
- 主シールエッジ部より副シールエッジ部の締め代が小さいことを特徴とする請求項1に記載のピストン一体シール。
- 副シールエッジ部がシールリップの油圧室側基部表面より反油圧室側に位置することを特徴とする請求項1又は2に記載のピストン一体シール。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/892,305 US9482292B2 (en) | 2013-05-24 | 2013-10-29 | Piston-integrated seal |
CN201380076807.7A CN105247234B (zh) | 2013-05-24 | 2013-10-29 | 活塞一体密封件 |
KR1020157034793A KR102080668B1 (ko) | 2013-05-24 | 2013-10-29 | 피스톤 일체형 시일 |
EP13885064.9A EP3006762B1 (en) | 2013-05-24 | 2013-10-29 | Piston-integrated seal |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-109509 | 2013-05-24 | ||
JP2013109509A JP6117000B2 (ja) | 2013-05-24 | 2013-05-24 | ピストン一体シール |
Publications (1)
Publication Number | Publication Date |
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WO2014188616A1 true WO2014188616A1 (ja) | 2014-11-27 |
Family
ID=51933195
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/079187 WO2014188616A1 (ja) | 2013-05-24 | 2013-10-29 | ピストン一体シール |
Country Status (6)
Country | Link |
---|---|
US (1) | US9482292B2 (ja) |
EP (1) | EP3006762B1 (ja) |
JP (1) | JP6117000B2 (ja) |
KR (1) | KR102080668B1 (ja) |
CN (1) | CN105247234B (ja) |
WO (1) | WO2014188616A1 (ja) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019203524A (ja) * | 2018-05-21 | 2019-11-28 | Nok株式会社 | クラッチピストン |
JP2020076478A (ja) * | 2018-11-09 | 2020-05-21 | Nok株式会社 | 自動変速機用ピストンシール |
IT201900016034A1 (it) | 2019-09-11 | 2021-03-11 | Skf Ab | Dispositivo di tenuta in particolare per steli ammortizzatore |
US11592108B2 (en) * | 2019-09-19 | 2023-02-28 | Aktiebolaget Skf | Seal having a lip optimized for low temperature applications |
FR3129998B1 (fr) * | 2021-12-03 | 2024-03-15 | Valeo Embrayages | Embrayage humide |
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JPH09292031A (ja) * | 1996-04-24 | 1997-11-11 | Nok Corp | 往復動用密封装置 |
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JP4649500B2 (ja) * | 2008-07-31 | 2011-03-09 | トヨタ自動車株式会社 | 密封装置 |
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2013
- 2013-05-24 JP JP2013109509A patent/JP6117000B2/ja active Active
- 2013-10-29 EP EP13885064.9A patent/EP3006762B1/en active Active
- 2013-10-29 KR KR1020157034793A patent/KR102080668B1/ko active IP Right Grant
- 2013-10-29 WO PCT/JP2013/079187 patent/WO2014188616A1/ja active Application Filing
- 2013-10-29 US US14/892,305 patent/US9482292B2/en active Active
- 2013-10-29 CN CN201380076807.7A patent/CN105247234B/zh active Active
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JPH08184377A (ja) * | 1994-11-04 | 1996-07-16 | Nok Corp | 往復動用密封装置 |
JPH09210088A (ja) | 1996-01-29 | 1997-08-12 | Nok Corp | 密封装置 |
JPH09292031A (ja) * | 1996-04-24 | 1997-11-11 | Nok Corp | 往復動用密封装置 |
JP2001241467A (ja) | 2000-02-29 | 2001-09-07 | Mitsubishi Cable Ind Ltd | キャンセルプレート |
WO2004023007A1 (ja) * | 2002-09-09 | 2004-03-18 | Nok Corporation | 密封装置 |
JP2011149512A (ja) * | 2010-01-22 | 2011-08-04 | Koyo Sealing Techno Co Ltd | 流体式変速機用クラッチピストン |
WO2012024470A1 (en) * | 2010-08-18 | 2012-02-23 | Skf Usa Inc. | Seal with pressure-actuatable sealing bead |
JP2013096503A (ja) * | 2011-11-01 | 2013-05-20 | Kyb Co Ltd | 密封装置及びこの密封装置を備える緩衝器 |
Also Published As
Publication number | Publication date |
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EP3006762A4 (en) | 2016-04-20 |
KR102080668B1 (ko) | 2020-02-24 |
US9482292B2 (en) | 2016-11-01 |
KR20160011646A (ko) | 2016-02-01 |
CN105247234B (zh) | 2018-08-31 |
CN105247234A (zh) | 2016-01-13 |
US20160091033A1 (en) | 2016-03-31 |
JP2014228089A (ja) | 2014-12-08 |
JP6117000B2 (ja) | 2017-04-19 |
EP3006762B1 (en) | 2018-07-04 |
EP3006762A1 (en) | 2016-04-13 |
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