JP2006046550A - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
JP2006046550A
JP2006046550A JP2004230194A JP2004230194A JP2006046550A JP 2006046550 A JP2006046550 A JP 2006046550A JP 2004230194 A JP2004230194 A JP 2004230194A JP 2004230194 A JP2004230194 A JP 2004230194A JP 2006046550 A JP2006046550 A JP 2006046550A
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Japan
Prior art keywords
piston member
housing
seal lip
axial direction
parallel
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JP2004230194A
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Japanese (ja)
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Tomoaki Nishimura
智昭 西村
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Nok Corp
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Nok Corp
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Priority to JP2004230194A priority Critical patent/JP2006046550A/en
Publication of JP2006046550A publication Critical patent/JP2006046550A/en
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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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealing device 1 which can improve the operability of a piston member 3 by reducing the sliding resistance of seal lips 7, 8 at the start, the seal lips 7, 8 being arranged on the piston member 3 axially reciprocating in a housing 2 forming an annular bore portion. <P>SOLUTION: Circumferential parallel grooves 11 or parallel projections formed on the sliding surfaces 13 of the seal lips 7, 8, which closely slide on the end faces of the side walls 21, 22 of the housing 2, are separated circumferentially by means of separating portions 12. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、ハウジング内を往復動するピストン部材等に用いられる密封装置に係り、更に詳しくは、自動車の自動変速機におけるクラッチ締結切り替え作動のために使用されるピストン部材等に用いられる密封装置に関する。   The present invention relates to a sealing device used for a piston member or the like that reciprocates in a housing, and more particularly to a sealing device used for a piston member or the like used for clutch engagement switching operation in an automatic transmission of an automobile. .

自動車の自動変速機においては、環状の穴部を形成しているハウジング内に装着しているピストン部材が往復動して、多板クラッチを押したり、または多板クラッチから離れたりして、多板クラッチ締結の切り替え作動を行なっている。このピストン部材は、ピストン部材の軸方向外側とハウジングで形成される圧力室と、ピストン部材の軸方向内側とキャンセラシールとで形成される油室との圧力差によりハウジングの内径側壁及び外径側壁の端面に密接して軸方向に摺動し、ピストン部材がハウジングの内径側壁及び外径側壁の端面と接する部位には、ＢＰＳ（ボンデッドピストンシール）若しくはキャンセラシール等のシールリップが設けられている。   In an automatic transmission of an automobile, a piston member mounted in a housing forming an annular hole reciprocates to push a multi-plate clutch or to move away from a multi-plate clutch. The plate clutch engagement switching operation is performed. The piston member has an inner diameter side wall and an outer diameter side wall of the housing due to a pressure difference between a pressure chamber formed by the outer side in the axial direction of the piston member and the housing, and an oil chamber formed by the inner side in the axial direction of the piston member and the canceller seal. A seal lip such as a BPS (bonded piston seal) or a canceller seal is provided at a portion where the piston member slides in the axial direction in close contact with the end surface of the housing and the piston member contacts the end surfaces of the inner diameter side wall and the outer diameter side wall. Yes.

このシールリップがピストン部材に設けられることで圧力室及び油室の密封性が確保されるが、ピストン部材がハウジングの端面に摺動するときに摺動抵抗が大きくなり、場合によっては、自動変速機の変速時のフィーリング悪化の原因となる可能性があったので、摺動抵抗低減を目的として、下記特許文献１では、シールリップの摺動面に周方向の凹凸部である平行溝若しくは平行突起を形成し、該平行溝若しくは平行突起の間に油を確保することで、摺動時における油膜の形成を補助し、摺動抵抗を低減することが提案されている。   Although the sealing performance of the pressure chamber and the oil chamber is ensured by providing this seal lip on the piston member, the sliding resistance increases when the piston member slides on the end surface of the housing. In order to reduce sliding resistance, in Patent Document 1 below, parallel grooves or uneven portions in the circumferential direction are formed on the sliding surface of the seal lip. It has been proposed to form parallel protrusions and secure oil between the parallel grooves or parallel protrusions to assist the formation of an oil film during sliding and reduce sliding resistance.

しかしながら、シールリップの摺動面に形成された周方向の平行溝若しくは平行突起は、軸方向に作動するピストン部材に対して交差する方向に形成されていることになるので、起動開始時には平行溝若しくは平行突起の間で周方向部分に油が充分に確保されない可能性があり、そのために摺動面の油膜形成が不十分な状態となって、周方向の平行溝若しくは平行突起が抵抗となり、起動開始時に摺動抵抗が大きくなるおそれがあった。   However, since the circumferential parallel grooves or parallel protrusions formed on the sliding surface of the seal lip are formed in a direction crossing the piston member that operates in the axial direction, the parallel grooves or grooves are formed at the start of starting. Alternatively, there is a possibility that sufficient oil is not secured in the circumferential portion between the parallel projections, so that the oil film formation on the sliding surface becomes insufficient, and the circumferential parallel grooves or parallel projections become resistance, There was a risk that the sliding resistance would increase at the start of startup.

特開平０９−２１００８８号公報Japanese Patent Laid-Open No. 09-210088

本発明は以上の点に鑑みて、ピストン部材に設けられたシールリップの起動開始時における摺動抵抗を低減し、これによるピストン部材の作動性の向上を図ることができる密封装置を提供することを目的とする。   In view of the above, the present invention provides a sealing device that can reduce sliding resistance at the start of activation of a seal lip provided on a piston member, thereby improving the operability of the piston member. With the goal.

上記目的を達成するため、本発明の請求項１にかかる密封装置は、円筒状のボア部を形成するハウジング内を軸方向に往復動するピストン部材に前記ハウジングの端面と密接に摺動するシールリップが設けられ、前記シールリップのハウジングの端面と摺動する摺動面には、周方向に凹凸部が形成されており、前記凹凸部は周方向に分離されていることを特徴とするものである。   In order to achieve the above object, a sealing device according to claim 1 of the present invention is a seal that slides in close contact with an end face of the housing on a piston member that reciprocates in the axial direction in a housing forming a cylindrical bore portion. A lip is provided, and an uneven portion is formed in a circumferential direction on a sliding surface that slides with an end surface of the housing of the seal lip, and the uneven portion is separated in the circumferential direction. It is.

本発明は、以下の効果を奏する。   The present invention has the following effects.

すなわち、上記構成を備えた本発明の請求項１の密封装置は、ピストン部材に設けられているシールリップのハウジングの端面と摺動する摺動面に形成されている周方向の凹凸部は、周方向に分離されているので、停止時においてもシールリップの摺動面とハウジングの側壁端面との間に油を介在させ、起動開始時の油膜形成を容易にすることができる。したがって、起動開始時においてもシールリップの摺動抵抗を低減し、これによるピストン部材の作動性の向上を図ることができ、例えば、自動変速機の変速時のフィーリング悪化を防止することができる。   That is, in the sealing device according to claim 1 of the present invention having the above-described configuration, the circumferential unevenness formed on the sliding surface sliding with the end surface of the housing of the seal lip provided on the piston member is: Since they are separated in the circumferential direction, oil can be interposed between the sliding surface of the seal lip and the side wall end surface of the housing even when the vehicle is stopped to facilitate the formation of an oil film at the start of startup. Therefore, the sliding resistance of the seal lip can be reduced even at the start of startup, and the operability of the piston member can be improved thereby, for example, it is possible to prevent feeling deterioration during shifting of the automatic transmission. .

以下に図面を参照して、この発明の好適な実施の形態を例示して説明する。ただし、この発明の範囲は、特に限定的記載がないかぎりは、この実施の形態に記載されている内容に限定する趣旨のものではない。   Preferred embodiments of the present invention will be described below with reference to the drawings. However, the scope of the present invention is not intended to be limited to the contents described in this embodiment unless otherwise specified.

図１は、本発明の実施例に係る密封装置１の断面図であり、図２は、図１におけるシールリップの拡大部分断面図である。   FIG. 1 is a cross-sectional view of a sealing device 1 according to an embodiment of the present invention, and FIG. 2 is an enlarged partial cross-sectional view of a seal lip in FIG.

本発明に係る密封装置１は、図１に示す通り、円筒状のボア部を形成しているハウジング２内に装着されるピストン部材３と、ピストン部材３に対向してハウジング２の開口側に設けられたキャンセルプレート４と、ピストン部材３とキャンセルプレート４の間に設けられたリターンスプリング５と、ピストン部材３の外径円筒部３２側に設けられている多板クラッチ６とにより構成されている。   As shown in FIG. 1, a sealing device 1 according to the present invention includes a piston member 3 mounted in a housing 2 forming a cylindrical bore portion, and an opening side of the housing 2 facing the piston member 3. The cancel plate 4 is provided, the return spring 5 provided between the piston member 3 and the cancel plate 4, and the multi-plate clutch 6 provided on the outer diameter cylindrical portion 32 side of the piston member 3. Yes.

ピストン部材３は、軸方向内側（図上下側）に開口し、内径円筒部３１と外径円筒部３２と径方向部３３とから成っていて、内径円筒部３１は、外径円筒部３２より軸方向内側に延びている。   The piston member 3 opens in the axially inner side (upper and lower sides in the figure), and includes an inner diameter cylindrical portion 31, an outer diameter cylindrical portion 32, and a radial direction portion 33, and the inner diameter cylindrical portion 31 is formed from the outer diameter cylindrical portion 32. It extends inward in the axial direction.

内径円筒部３１は、軸方向に延びる軸方向部３１Ａと、軸方向部３１Ａの軸方向内側端部から径方向内側に広がる傾斜部３１Ｂとから成っていて、傾斜部３１Ｂの先端には、内径方向に若干延びる第一フランジ部３１Ｃが形成されていて、この第一フランジ部３１Ｃの内径方向先端には、ハウジング２の内径側壁２１の端面と摺動するようにゴム状弾性体製の第一シールリップ７が加硫成形により固定されている。   The inner cylindrical portion 31 includes an axial portion 31A extending in the axial direction and an inclined portion 31B extending radially inward from the axial inner end of the axial portion 31A. A first flange portion 31C slightly extending in the direction is formed, and a first end made of a rubber-like elastic body is slid on the end surface of the inner diameter side wall 21 of the housing 2 at the tip end in the inner diameter direction of the first flange portion 31C. The seal lip 7 is fixed by vulcanization molding.

外径円筒部３２は、段つきとなっており、軸方向外側（図上上側）が内径側に位置して、小径軸方向部３２Ａを形成し、小径軸方向部３２Ａの軸方向外側端部から内径方向に向かって径方向部３３が形成されていて、この小径軸方向部３２Ａと径方向部３３の角部に、ハウジング２の外径側壁２２の端面と摺動するようにゴム状弾性体の第二シールリップ８が加硫成形により固定されている。これにより、ピストン部材３の軸方向外側とハウジング２とで囲われた部分に圧力室Ｍが形成される。また、外径円筒部３２の軸方向内側に位置する大径軸方向部３２Ｂの先端には、外径方向に若干延びる第二フランジ部３２Ｃが形成されていて、この第二フランジ部３２Ｃが多板クラッチ６と当接するようになっている。   The outer diameter cylindrical portion 32 is stepped, and the outer side in the axial direction (upper side in the figure) is located on the inner diameter side to form the small diameter axial direction portion 32A, and the axially outer end of the small diameter axial direction portion 32A. A radial portion 33 is formed from the inner diameter direction toward the inner diameter direction, and a rubber-like elasticity is formed so that the corners of the small-diameter axial direction portion 32A and the radial direction portion 33 slide with the end face of the outer diameter side wall 22 of the housing 2. The body second seal lip 8 is fixed by vulcanization molding. Thereby, a pressure chamber M is formed in a portion surrounded by the outer side in the axial direction of the piston member 3 and the housing 2. Further, a second flange portion 32C slightly extending in the outer diameter direction is formed at the tip of the large diameter axial direction portion 32B located on the inner side in the axial direction of the outer diameter cylindrical portion 32. It contacts with the plate clutch 6.

第一シールリップ７と第二シールリップ８の摺動面１３には、図２に示すとおり、周方向に凹凸部としての平行溝１１若しくは平行突起（図示せず）が形成されていて、この摺動面に形成されている平行溝１１若しくは平行突起は分離部１２で周方向に分離されている。なお、平行溝１１若しくは平行突起が周方向に分離される分離部１２は、複数の平行溝１１若しくは平行突起が設けられる場合、互いに周方向同位置でもよいが、それぞれの平行溝１１若しくは平行突起において周方向に異なる位置に設けられていてもよい。   On the sliding surface 13 of the first seal lip 7 and the second seal lip 8, as shown in FIG. 2, parallel grooves 11 or parallel protrusions (not shown) as uneven portions are formed in the circumferential direction. The parallel grooves 11 or parallel protrusions formed on the sliding surface are separated in the circumferential direction by the separation portion 12. In addition, the separation part 12 from which the parallel grooves 11 or the parallel protrusions are separated in the circumferential direction may be at the same position in the circumferential direction when a plurality of parallel grooves 11 or parallel protrusions are provided. May be provided at different positions in the circumferential direction.

ピストン部材３に対向して、ハウジング２の開口部側である軸方向内側に設けられているキャンセルプレート４は、金属製であって、内径側端部４１はハウジング２の内径側壁２１に対して着脱自在に設定してあると共に、外径側端部４２には、ピストン部材３の大径軸方向部３２Ｂの内径端面に摺動するオイルシールリップ４３が加硫接着により固定されていて、これによりピストン部材３とキャンセルプレート４との間に油室Ｎが形成される。   The cancel plate 4 provided on the inner side in the axial direction on the opening side of the housing 2 so as to face the piston member 3 is made of metal, and the inner diameter side end portion 41 is opposed to the inner diameter side wall 21 of the housing 2. An oil seal lip 43 that slides on the inner diameter end surface of the large diameter axial direction portion 32B of the piston member 3 is fixed to the outer diameter side end portion 42 by vulcanization adhesion. Thus, an oil chamber N is formed between the piston member 3 and the cancel plate 4.

ピストン部材３とキャンセルプレート４の間には、ピストン部材３を軸方向外側、すなわち、キャンセルプレート４から離れる方向に付勢する手段としてリターンスプリング５が設けられている。   A return spring 5 is provided between the piston member 3 and the cancel plate 4 as means for urging the piston member 3 outward in the axial direction, that is, in a direction away from the cancel plate 4.

リターンスプリング５は、スプリングバネ状であって、内側端部５１がキャンセルプレート４の径方向部４４の端面に当接し、外側端部５２がピストン部材３の径方向部３３の端面と当接し、ピストン部材３をキャンセルプレート４から離れる方向に付勢している。   The return spring 5 is in the form of a spring spring, the inner end portion 51 abuts on the end surface of the radial portion 44 of the cancel plate 4, the outer end portion 52 abuts on the end surface of the radial portion 33 of the piston member 3, The piston member 3 is urged away from the cancel plate 4.

上記構成において、油室Ｎに油が供給されると圧力室Ｍが相対的に低圧となり、リターンスプリング５の付勢力によりピストン部材３が軸方向外側に移動し、径方向部３３に形成されている突起３３Ａがハウジング２の径方向側壁２３の端面に当接して静止する。   In the above configuration, when oil is supplied to the oil chamber N, the pressure chamber M becomes relatively low pressure, and the piston member 3 moves outward in the axial direction by the urging force of the return spring 5, and is formed in the radial portion 33. The projection 33 </ b> A that is in contact with the end surface of the radial side wall 23 of the housing 2 comes to rest.

また、圧力室Ｍに作動圧が流入して圧力室Ｍの圧力が上昇すると、圧力室Ｍが油室Ｎより相対的に高圧となるので、ピストン部材３がリターンスプリング５の付勢力に抗して軸方向内側の方向に移動し、ピストン部材３の大径軸方向部３２Ｂの先端に形成されている第二フランジ部３２Ｃが多板クラッチ６を押すので、動力を伝達することができる。   Further, when the operating pressure flows into the pressure chamber M and the pressure in the pressure chamber M increases, the pressure chamber M becomes relatively higher than the oil chamber N, so that the piston member 3 resists the urging force of the return spring 5. Thus, the second flange portion 32C formed at the tip of the large-diameter axial direction portion 32B of the piston member 3 pushes the multi-plate clutch 6 so that power can be transmitted.

そして、動力の伝達を解除するときは、上記と同様に、油室Ｎの油を供給して圧力室Ｍの圧力を相対的に低くして、リターンスプリング５の付勢力でピストン部材３を軸方向外側に移動させ、ピストン部材３を元の位置に戻す。   When releasing the transmission of power, the oil in the oil chamber N is supplied to relatively lower the pressure in the pressure chamber M and the piston member 3 is pivoted by the urging force of the return spring 5 in the same manner as described above. The piston member 3 is returned to the original position by moving outward in the direction.

この場合において、第一シールリップ７と第二シールリップ８の摺動面１３には、周方向に凹凸部としての平行溝１１もしくは平行突起が形成されていて、この摺動面１３に形成されている平行溝１１若しくは平行突起は分離部１２で周方向に分離されているので、停止時にも、分離部１２を通った油が平行溝１１若しくは平行突起に供給されるので、起動開始時において、第一シールリップ７と第二シールリップ８の摺動面１３とハウジング２の側壁２１，２２の端面との間に油が介在され、油膜形成を容易にすることが可能となる。   In this case, on the sliding surface 13 of the first seal lip 7 and the second seal lip 8, parallel grooves 11 or parallel protrusions as uneven portions are formed in the circumferential direction, and formed on the sliding surface 13. Since the parallel grooves 11 or parallel protrusions are separated in the circumferential direction by the separation part 12, the oil that has passed through the separation part 12 is supplied to the parallel grooves 11 or parallel protrusions even when stopped. In addition, oil is interposed between the sliding surfaces 13 of the first seal lip 7 and the second seal lip 8 and the end surfaces of the side walls 21 and 22 of the housing 2, so that oil film formation can be facilitated.

なお、凹凸部を分離する分離部１２の形状・個数等については、図面の内容に特に限定されるものではなく、全ての平行溝１１若しくは平行突起に油を供給することができればよい。したがって、複数の周方向に配置された平行溝１１若しくは並行突起のうち、少なくとも一つを周方向に分離されない態様としてもよく、その平行溝１１若しくは平行突起により油を掻き集めることで、他の平行溝１１若しくは平行突起に十分な油を供給できるものとしてもよい。   Note that the shape, number, and the like of the separating portions 12 that separate the uneven portions are not particularly limited to the contents of the drawings, and it is sufficient that oil can be supplied to all the parallel grooves 11 or the parallel protrusions. Accordingly, at least one of the plurality of parallel grooves 11 or parallel protrusions arranged in the circumferential direction may not be separated in the circumferential direction. By collecting oil by the parallel grooves 11 or parallel protrusions, It is good also as what can supply sufficient oil to the parallel groove | channel 11 or a parallel protrusion.

本発明の実施例に係る密封装置の断面図Sectional drawing of the sealing device which concerns on the Example of this invention 図２は、図１におけるシールリップの拡大部分断面図2 is an enlarged partial sectional view of the seal lip in FIG.

符号の説明Explanation of symbols

１ 密封装置
２ ハウジング
３ ピストン部材
４ キャンセルプレート
５ リターンスプリング
６ 多板クラッチ
７，８ シールリップ
１１ 溝
１２ 分離部
１３ 摺動面
２１，２２，２３ 側壁
３１，３２ 円筒部
３１Ａ，３２Ａ，３２Ｂ 軸方向部
３１Ｂ 傾斜部
３１Ｃ，３２Ｃ フランジ部
３３ 径方向部
４１，４２ 端部
４３ オイルシールリップ
５１，５２ 端部
Ｍ 圧力室
Ｎ 油室 DESCRIPTION OF SYMBOLS 1 Sealing device 2 Housing 3 Piston member 4 Cancel plate 5 Return spring 6 Multi-plate clutch 7, 8 Seal lip 11 Groove 12 Separating part 13 Sliding surface 21, 22, 23 Side wall 31, 32 Cylindrical part 31A, 32A, 32B Axial direction Part 31B Inclined part 31C, 32C Flange part 33 Radial part 41, 42 End part 43 Oil seal lip 51, 52 End part M Pressure chamber N Oil chamber

Claims (1)

円筒状のボア部を形成するハウジング内を軸方向に往復動するピストン部材に前記ハウジングの端面と密接に摺動するシールリップが設けられ、前記シールリップのハウジングの端面と摺動する摺動面には、周方向に凹凸部が形成されており、前記凹凸部は周方向に分離されていることを特徴とする密封装置。   A piston member that reciprocates in the axial direction in the housing forming the cylindrical bore portion is provided with a seal lip that slides closely with the end surface of the housing, and a sliding surface that slides with the end surface of the housing of the seal lip Has a concavo-convex portion in the circumferential direction, and the concavo-convex portion is separated in the circumferential direction.
JP2004230194A 2004-08-06 2004-08-06 Sealing device Pending JP2006046550A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004230194A JP2006046550A (en) 2004-08-06 2004-08-06 Sealing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004230194A JP2006046550A (en) 2004-08-06 2004-08-06 Sealing device

Publications (1)

Publication Number Publication Date
JP2006046550A true JP2006046550A (en) 2006-02-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038186A (en) * 2008-07-31 2010-02-18 Toyota Motor Corp Sealing device
WO2011075396A1 (en) 2009-12-18 2011-06-23 Skf Usa Inc. Actuator seal with lubricating gaps
JP2017122486A (en) * 2016-01-08 2017-07-13 Nok株式会社 Bonded piston seal

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6249076A (en) * 1985-08-29 1987-03-03 Nippon Mektron Ltd Dust seal
JPH08121607A (en) * 1994-10-21 1996-05-17 Nok Corp Sealing device
JPH09210213A (en) * 1996-02-02 1997-08-12 Nok Corp Reciprocating sealing device
JPH09210088A (en) * 1996-01-29 1997-08-12 Nok Corp Sealing device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6249076A (en) * 1985-08-29 1987-03-03 Nippon Mektron Ltd Dust seal
JPH08121607A (en) * 1994-10-21 1996-05-17 Nok Corp Sealing device
JPH09210088A (en) * 1996-01-29 1997-08-12 Nok Corp Sealing device
JPH09210213A (en) * 1996-02-02 1997-08-12 Nok Corp Reciprocating sealing device

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038186A (en) * 2008-07-31 2010-02-18 Toyota Motor Corp Sealing device
JP4649500B2 (en) * 2008-07-31 2011-03-09 トヨタ自動車株式会社 Sealing device
US8342536B2 (en) 2008-07-31 2013-01-01 Toyota Jidosha Kabushiki Kaisha Sealing device
WO2011075396A1 (en) 2009-12-18 2011-06-23 Skf Usa Inc. Actuator seal with lubricating gaps
EP2513529A1 (en) * 2009-12-18 2012-10-24 Skf Usa Inc. Actuator seal with lubricating gaps
EP2513529A4 (en) * 2009-12-18 2013-11-06 Skf Usa Inc Actuator seal with lubricating gaps
JP2017122486A (en) * 2016-01-08 2017-07-13 Nok株式会社 Bonded piston seal

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