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WO2005036033A1 - Joint d'etancheite d'arbre - Google Patents

Joint d'etancheite d'arbre Download PDF

Info

Publication number
WO2005036033A1
WO2005036033A1 PCT/JP2004/014652 JP2004014652W WO2005036033A1 WO 2005036033 A1 WO2005036033 A1 WO 2005036033A1 JP 2004014652 W JP2004014652 W JP 2004014652W WO 2005036033 A1 WO2005036033 A1 WO 2005036033A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotary shaft
rubber lip
rubber
axial center
low pressure
Prior art date
Application number
PCT/JP2004/014652
Other languages
English (en)
Japanese (ja)
Inventor
Keizo Morimoto
Original Assignee
Mitsubishi Cable Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Cable Industries, Ltd. filed Critical Mitsubishi Cable Industries, Ltd.
Publication of WO2005036033A1 publication Critical patent/WO2005036033A1/fr

Links

Classifications

    • 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
    • F16J15/3224—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip capable of accommodating changes in distances or misalignment between the surfaces, e.g. able to compensate for defaults of eccentricity or angular deviations
    • 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

Definitions

  • the present invention relates to a rotary shaft seal, and more particularly to a rotary shaft seal used to seal high pressure fluid such as gas.
  • a rotary shaft seal 31 as shown in FIG. 6 has been used (see, for example, JP-A-2003-97723), and the shape of the rubber lip 33 contacting the surface of the rotary shaft 32 is It had a cross-sectional shape extending substantially L-shaped to the sealed fluid chamber side C. That is, in FIGS. 6 and 5 (B) showing the conventional example, this rotary shaft seal 31 interposed between the rotary shaft 32 and the casing 35 is located at the end of the sealed fluid chamber side C.
  • the rubber case 37 is provided with an outer case 36 having an inner ring 36, and the rubber member 37 is integrated by adhesion or baking so as to surround the inner ring 36 of the outer case 34 and to cover the outer peripheral surface of the outer case 34. There is.
  • a support bracket 38 having a substantially L-shaped cross section holds the rubber lip 33 from the low-pressure side E and the inner peripheral surface side (from the back), and the lip tip 33a is a part of the rubber case 34. It is located at an axial position farther to the sealed fluid chamber side C than the axis orthogonal plane Po including the inner weir 36. That is, the sliding contact portion So where the lip tip portion 33a contacts the rotating shaft 32 is present at an axial position far away from the axis orthogonal plane Po including the inner ring 36, and the rubber lip 33 is a support fitting 38 It has a shape having a cylindrical extending portion 33c held by the cylindrical portion 38a.
  • the sealed fluid (the lubricating oil contained therein) infiltrates the interface between the rotary shaft 32 and the sliding contact portion So.
  • the above-mentioned large pressure P makes it difficult to accelerate wear of the sliding contact portion So of the lip tip 33a. After that, the sliding contact portion So wears as it advances, and the sealability (sealability) suddenly deteriorates and an external leak of fluid occurs.
  • the portion which was the smallest inner diameter in the free state is always in sliding contact with the rotary shaft 32 from low pressure to high pressure, and in particular, the smallest inner diameter and its vicinity Force Causes the above-mentioned wear and tear.
  • the present invention has been made in view of a pressing point, and an object of the present invention is to reliably prevent abrasion of the minimum inner diameter portion of a rubber lip portion.
  • the present invention is provided with a rubber lip portion having a rotary shaft contact portion having a convex cross section cut along a plane including the axial center of the rotary shaft, and further, in a free state, the minimum of the rotary shaft slide contact portion.
  • the rotary shaft seenore includes a deformation allowing space for allowing the elastic deformation of the rubber lip portion to the low pressure side so that the inner diameter portion floats up with the rotary shaft force under the mounting pressure load state where the predetermined sealing chamber pressure is received. is there.
  • the present invention is provided with a rubber lip portion having a rotary shaft sliding contact portion having a convex cross-sectional shape cut along a plane including the axial center of the rotary shaft, and a rear surface near the base end of the rubber lip portion.
  • a recessed groove is formed on the side to increase the elastic deformation of the rubber lip toward the low pressure side, and the minimum inner diameter portion of the rotating shaft sliding portion in a free state is subjected to a mounting pressure load state where a predetermined sealing chamber pressure is received.
  • the rotary shaft seal is provided with a deformation allowing space for allowing the elastic deformation of the rubber lip portion to the low pressure side so that the rotary shaft force floats up.
  • the present invention is provided with a rubber lip portion having a rotational shaft sliding contact portion having an arc convex cross-sectional shape cut along a plane including the axial center of the rotary shaft, and a rear surface near the base end of the rubber lip portion.
  • a concave portion is formed on the side to increase the elastic deformation of the rubber lip toward the low pressure side, and a metal support portion inserted into the concave groove to receive a force on the back side near the base end of the rubber lip is provided.
  • the elastic deformation to the low pressure side of the rubber lip portion is made so that, in the free state, the minimum inner diameter portion of the rotary shaft sliding portion also lifts the rotational axial force under a mounting pressure load state where a predetermined sealing chamber pressure is received. It is a rotary shaft seal provided with an allowable deformation allowance space.
  • a metal-made aluminum case having an inner rim portion on the side of the sealed chamber, and an integrated body with the latter.
  • a rotary shaft seal including a rubber seal portion fixed to the inner ring portion and covering the inner flange portion, and a support fitting fixedly held within the water supply case, wherein the rubber seal portion is the inner ring portion described above.
  • the axial center orthogonal wall portion has a rubber lip portion having a rotational shaft sliding contact portion having an arc convex cross section cut along a plane including the axial center of the rotational axis.
  • the axial center orthogonal wall portion has a concave groove on the back side near the base end of the rubber lip portion to increase the elastic deformation to the low pressure side of the rubber lip portion.
  • a metal-made aluminum case having an inner rim on the side of a sealed chamber, a rubber seal integrally fixed to the outer case to cover the inner rim, and fixedly held in the outer case.
  • a rotary shaft seal having a support fitting, wherein the rubber seal portion has an axial center orthogonal wall portion covering the inner flange portion, and the axial center orthogonal wall portion is an axial center of the rotational shaft
  • the rubber lip portion includes a rubber lip portion having a rotational shaft contact portion having a circular arc convex cross section cut at a plane including the above, and the axial center orthogonal wall portion is on the back side near the base end of the rubber lip portion
  • a metal support part is formed on the support fitting, which has a concave groove to increase the elastic deformation to the low pressure side of the rubber, and the force is also inserted into the concave groove to receive the force on the back side near the base end of the rubber lip.
  • the present invention has the following remarkable effects.
  • the sliding contact portion having an arc-convex cross section does not come into contact with the rotating shaft during rotation operation by the minimum inner diameter portion rising (disengaging) from the rotating shaft under the mounting pressure load condition, Within the minimum The diameter does not wear.
  • the rubber lip portion force can also be reliably prevented from causing external fluid leakage, for example, in the stationary state where the pressure is returned to zero and when the rotation from the low pressure is restarted.
  • the thickness of the rubber decreases in the vicinity of the base end of the rubber lip portion due to the recessed groove, and the elastic deformation force S to the deformation allowable space is performed, and the sliding contact portion has an arc convex shape in cross section.
  • the metal support portion inserted into the recessed groove has the concave portion as a fulcrum point (center point), and the swing of the rubber lip portion having a sliding contact portion with an arc convex shape on the smooth (ie, elastic deformation Achieve).
  • the occurrence of excessive phase stress (internal stress) inside the rubber can be prevented by the metal support portion inserted in the recessed groove.
  • the contact surface pressure between the sliding contact portion of the rubber lip portion and the rotation shaft is also reduced by the metal support portion, and the lubrication state is also improved, and the wear can be further suppressed.
  • sealability can be exhibited over a long period of time, and for example, it is suitable for sealing high pressure gas.
  • the force can also reduce the axial dimension of the rotary shaft seal to achieve compactness.
  • FIG. 1 is a sectional view of an essential part showing an embodiment of the present invention.
  • FIG. 2 is a sectional view of an essential part showing another embodiment.
  • FIG. 3 is an enlarged sectional view for explaining the above two embodiments of the present invention.
  • FIG. 5 is a view for explaining the shapes and operations of a comparative example and a conventional example.
  • FIG. 6 is a sectional view of an essential part showing a conventional example.
  • Embodiment 1 of the Invention Hereinafter, the present invention will be described in detail based on the illustrated embodiments.
  • a rubber lip 19 having 23 is provided. Do indicates the minimum inner diameter portion (minimum inner diameter point) of the sliding contact portion 23 in the free state (unmounted state).
  • a metal-made aluminum case 1 having internal flanges 2 and 3 is adhered to the outer peripheral surface of the cylindrical wall 4 of this external case 1 and on both the front and rear surfaces of the internal flange 2 on the sealed fluid chamber side C '.
  • the rubber seal 5 is fixed (held) in a solid state by welding, baking or the like.
  • a seal element 7 with a spiral groove 6 is provided on the low pressure side (non-sealing fluid chamber side or atmosphere side! Z) Z more than the seal portion 5! //.
  • the material of the sealing element 7 is preferably a fluorine-based resin such as PTFE.
  • Reference numeral 8 denotes a support fitting fixedly held in the water case 1, and the support fitting 8 is an intermediate between the outer diameter side annular flat portion 8a, the inner diameter side annular flat portion 8b, and the like.
  • the inner diameter side annular flat plate portion 8b is located on the low pressure side Z (narrowly) than the outer diameter side annular flat plate portion 8a.
  • the outer peripheral edge of the outer diameter side annular flat plate portion 8a is inserted to be in contact with the inner peripheral surface of the cylindrical wall portion 4 of the water supply case 1, and the support fitting 8 is fixedly (fixedly) held in the water supply case 1 Ru.
  • the support fitting 8 is connected by the radially intermediate inclined intermediate connection plate portion 8 c so that the inner diameter side annular flat portion 8 b is unevenly distributed to the low pressure side Z.
  • the support fitting 8, the first inner case 9, the second inner case 10, the seal element 7, and the inner first member 11 are sequentially overlapped with each other, and are held and fixed between the inner collar portions 2 and 3. (Stuck).
  • the rubber seal portion 5 integrally fixed to the outer case 1 has a housing 22 inner circumferential surface A cylindrical portion covering 5a (in the free state) in which the outer peripheral surface of the uneven waveform is formed (in the free state) to form a sealing action by chance and a cross section U-shaped inner covering covering the inner collar 2
  • An axially orthogonal wall portion 5b having the rubber lip portion 19 or the like which has an upper portion 18 and extends in the inner diameter direction is provided.
  • the rubber seal portion 5 is provided with an axial orthogonal wall portion 5 b orthogonal to the axial center L of the rotary shaft 20 (and the rotary shaft seal), and further, the axial orthogonal wall portion 5 b is
  • the cross-sectional shape (shown in FIG. 1) cut along a plane including the axis L of the rotary shaft 20 has a rubber lip 19 having a sliding contact portion 23 with an arc convex (round) shape at the inner peripheral edge,
  • the outer diameter side annular flat plate portion 8a of the support fitting 8 is in pressure contact (support) with the low pressure side annular flat surface of the axial center orthogonal wall portion 5b.
  • the axially orthogonal wall portion 5 b has an annular recessed groove 24 on the back side near the base end of the rubber lip portion 19. That is, the tip of the rubber lip 19 points to the inner diameter end and has the sliding contact portion 23, but the base end of the rubber lip 19 points to the outer diameter end and is a portion continuous with the inner ridge covering 18.
  • a small U-shaped recess 24 is recessed on the back side near the proximal end (ie, the low pressure side Z), which increases the elastic deformation of the rubber lip 19 to the low pressure side Z. Make an action.
  • the root portion (base end portion) of the rubber lip portion 19 serves as the thin neck portion 16 to facilitate elastic deformation of the rubber lip portion 19.
  • the rotary shaft seal according to the present invention is a cutting plane at the cutting plane including the axis L of the rotary shaft 20.
  • the rubber lip 19 is provided with a rotary shaft contact portion 23 whose sectional shape is an arc convex shape, and further, the load which receives the minimum internal diameter Do 1S predetermined (for example, 4 MPa-6 MPa) sealing chamber pressure under free condition
  • the rubber lip portion 19 has a deformation allowance space H which can be elastically deformed to the low pressure side Z so that the surface force of the rotating shaft 20 during rotation rises.
  • the elastic deformation of the rubber lip 19 to the low pressure side Z is increased (promoted) on the back side (low pressure side Z) near the base end (root) of the rubber lip 19
  • the concave groove 24 is formed.
  • the recessed groove 24 also functions to release (absorb) the rubber compressed by pressure receiving, and it is easy to make the contact surface pressure P of the sliding contact portion 23 with respect to the rotation shaft 20 an appropriate value. It also plays a role in exerting excellent sealing performance (sealing performance) for a long time.
  • the sliding contact portion 23 is disposed on the axis orthogonal plane Po including the inner flange portion 2. That is, since the (small) thickness exists in the inner collar portion 2, the axially orthogonal plane Po is displaced in the axial direction by the (small) thickness, and there are only a plurality of sheets, but On at least one orthogonal plane Po, a sliding contact portion V, which is actually in contact with the rotation axis 20, is configured to be present.
  • the shape of the rubber lip portion 19 is such that it has a projecting portion 19 a formed to project like a bird's hook (triangular mountain shape) to the sealed fluid chamber side C, as shown in FIG. 4 (A).
  • the sliding contact portion 23 can always be in contact with the surface of the rotation shaft 20 even when swinging to the deformation allowable space H.
  • FIG. 2 FIG. 3 (B) and FIG. 4 (B).
  • FIG. 1 and the reference numerals have the same configuration as that of the above-described embodiment, and the description thereof will be partially omitted. However, different configurations will be described below.
  • the groove 24 (described above) formed on the back side (that is, the low pressure side Z) near the base end of the rubber lip portion 19. It has a metal support 13 to be inserted.
  • the support portion 13 is a portion that also supports the rubber lip portion 19 on the back side in the vicinity of its base end.
  • a support fitting 8 that receives the axial center orthogonal wall portion 5b from the back side is 2
  • the first metal plate 14 is J-shaped in cross section, and its outer end 14a is in contact with the cylindrical wall 4 of the water supply case 1 and the inner end 14b is It shows a case where it is bent to the sealed fluid chamber side C, and the support portion 13 is configured with the inner end 14b.
  • the first metal plate 14 is press-contacted to the inner ridge covering portion 18, and the inner end 14b (that is, the support portion 13) occupies the outer diameter portion of the recessed groove 24 in a free state.
  • the concave groove 24 shrinks and deforms so as to wrap the support portion 13 from the outer diameter side and the inner diameter side, as shown in FIG. Do. That is, as shown in FIG. 3 (B) to FIG. 4 (B), excessive deformation of the rubber lip 19 (neck 16) is suppressed by elastic deformation of the rubber lip 19 with the support 13 as a fulcrum (FIG. The difference is clear when compared with.
  • the second metal plate 15 has a structure in which the first inner case 9 shown in FIG. 1 is integrally formed, and more specifically, the second metal plate 15
  • the inner case portion 15a having an inverted L-shaped cross section which is fitted to the inner surface of the cylindrical wall portion 4 of the water case 1 and is in pressure contact with the back side of the first metal plate 14; It consists of an intermediate connecting plate portion 15c to be connected.
  • the inner side flat plate portion 15b is biased to the low pressure side Z via the intermediate connection plate portion 15c to form a deformation allowing space H (as in the case of FIG. 1).
  • the first metal plate 14 of FIG. 2 may be added to the structure of FIG. 1, and in this case, the first metal plate 14 having a J-shaped cross section, the support bracket of FIG. It is configured to have the inner case 9.
  • the first support fitting 8 itself may be formed into an annular protrusion to be inserted into the recessed groove 24 by bending, welding, or by mechanical cutting, to thereby form the support portion. It is also free to form 13.
  • the first metal plate 14 and the second metal plate 15 may be integrally configured.
  • the support fitting 8 is provided with a metal support portion 13 which is inserted into the recessed groove 24 and is supported from the back side near the proximal end of the rubber lip portion 19.
  • FIG. 5 an explanatory view of the main parts under pressure load of the comparative example (the same figure (A)) and the conventional example (the same figure (B)) is shown.
  • the rubber moves in the direction of arrow F and the C force on the sealed fluid chamber side in a pressure load state where a high pressure and a predetermined pressure act.
  • the internal stress of the rubber is concentrated just above the sliding contact area So, and the rubber is flexible.
  • a large pressure (contact surface pressure) P shown in FIG. 5 (B) is generated at the sliding contact portion So that is lost and pressed against the rotating shaft 32 via the rubber in the vicinity of the stress concentration.
  • the lubricating oil can not penetrate into the interface between the rotating shaft 32 and the sliding contact portion So, and the wear is promoted accordingly.
  • the wear progresses as the sliding contact portion So is pushed, the sealing performance (sealability) is rapidly deteriorated, and the external leakage of the fluid occurs.
  • the support bracket 38 is an annular flat plate orthogonal to the axis L and the rubber lip 33 is an orthogonal circular plate.
  • the support fitting 38 is formed at the inner peripheral end of an axial center orthogonal rubber wall portion 40 that receives the rear side.
  • the (Point) portion Do always maintains contact from zero pressure (low pressure) to a predetermined high pressure, and the contact surface pressure P of this minimum inner diameter (point) portion is the highest, so the wear of the sliding contact portion So Advance early from the smallest inside diameter (point).
  • the support bracket is provided on the back side of the rubber lip portion 19.
  • the deformation allowable space H is formed as shown in FIG. 3 between 8 and 8.
  • the minimum inner diameter (point) portion under free state Do moves to the low pressure side Z While rising from the rotating shaft 20 (non-contact). Since the minimum inner diameter (point) portion Do is not in contact with the rotary shaft 20 during operation (rotation), no wear occurs. Therefore, when the pressure is subsequently lowered, the minimum inner diameter not worn (point ) Do can reliably contact the rotating shaft 20 to exhibit sealing performance (sealing performance), and it is also possible to effectively prevent fluid leakage when rotation (operation) is resumed.
  • the pressure on the sealed fluid chamber side C is 4 MPa, and a large equivalent stress (internal stress) of 29.8 MPa may be generated.
  • the metal support portion 13 as shown in Fig. 4 (B)
  • the rubber lip portion 19 is deformed so that it swings (swings) to the low pressure side Z with the tip as a fulcrum.
  • the deformation of the concave groove 24 can be prevented. This can prevent cracking of the rubber.
  • the contact surface pressure P can be made smaller than the comparative example of FIG. 5 (A) by the presence of the metal support portion 13.
  • the contact surface pressure P is reduced, the lubricating state between the sliding contact portion 23 and the rotating shaft 20 is also improved, and the wear thereof can be further suppressed, whereby the durability can be remarkably improved.
  • the present invention is not limited to the above-described embodiment.
  • a rubber lip portion separate from the above-described rubber lip portion 19 may be attached to the low pressure side, or the sealing element 7 may be used.
  • the seal element 7 may be omitted, or the number of components of the support bracket 8 may be increased or decreased, or the shape thereof may be changed appropriately. It is also possible to change the shape or change the shape as appropriate.
  • the present invention is useful for rotary shaft seals used to seal high pressure fluid such as gas, and in particular, in the case where the wear of the minimum inner diameter portion of the rubber lip portion is reliably prevented. Suitable for

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention concerne un joint d'étanchéité d'arbre, qui comprend une enveloppe externe (1) à bride interne (2) du côté chambre à fluide étanche C et un joint en caoutchouc (5) à paroi orthogonale (5b) par rapport à son axe, le long d'un plan P0 orthogonal par rapport à l'axe, bride (2) comprise. Une rainure (24) augmentant la déformation élastique d'une lèvre interne (19) du côté pression basse est formée sur le côté face arrière de la lèvre (19) près de l'extrémité de base, un support (13) inséré dans la rainure (24) et soutenant la lèvre (19) depuis la face arrière de celle-ci près de l'extrémité de base est formé sur une fixation métallique de soutien (8), et un espace de déformation H permettant au diamètre interne minimum D0 d'un élément de contact coulissant (23) à l'état libre de se déplacer vers le côté pression basse, de sorte qu'il soit soulevé par rapport à l'arbre (20) au moment de recevoir une pression, est formé entre la fixation (8) et la face arrière de la lèvre (19).
PCT/JP2004/014652 2003-10-08 2004-10-05 Joint d'etancheite d'arbre WO2005036033A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003-349461 2003-10-08
JP2003349461A JP2005114058A (ja) 2003-10-08 2003-10-08 回転軸シール

Publications (1)

Publication Number Publication Date
WO2005036033A1 true WO2005036033A1 (fr) 2005-04-21

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ID=34431005

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2004/014652 WO2005036033A1 (fr) 2003-10-08 2004-10-05 Joint d'etancheite d'arbre

Country Status (2)

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JP (1) JP2005114058A (fr)
WO (1) WO2005036033A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011012129A1 (fr) * 2009-07-30 2011-02-03 Trelleborg Sealing Solutions Germany Gmbh Joint d’étanchéité et ensemble joint d’étanchéité
CN112984116A (zh) * 2021-03-29 2021-06-18 烟台润蚨祥油封有限公司 一种油气密封件

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5967624U (ja) * 1982-10-27 1984-05-08 光洋精工株式会社 ころがり軸受の密封装置
JPS61129967U (fr) * 1985-01-31 1986-08-14
JP2000002254A (ja) * 1998-06-12 2000-01-07 Nippon Seiko Kk 軸受ユニット用密封シール

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3708577B2 (ja) * 1995-03-10 2005-10-19 三菱電線工業株式会社 回転軸シール
JP4035577B2 (ja) * 1999-09-02 2008-01-23 三菱電線工業株式会社 回転軸シール

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5967624U (ja) * 1982-10-27 1984-05-08 光洋精工株式会社 ころがり軸受の密封装置
JPS61129967U (fr) * 1985-01-31 1986-08-14
JP2000002254A (ja) * 1998-06-12 2000-01-07 Nippon Seiko Kk 軸受ユニット用密封シール

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011012129A1 (fr) * 2009-07-30 2011-02-03 Trelleborg Sealing Solutions Germany Gmbh Joint d’étanchéité et ensemble joint d’étanchéité
KR20120034785A (ko) 2009-07-30 2012-04-12 트렐레보르크 씰링 솔루션즈 저머니 게엠베하 밀봉부재 및 밀봉장치
US9068656B2 (en) 2009-07-30 2015-06-30 Trelleborg Sealing Solutions Germany Gmbh Seal and seal arrangement
CN112984116A (zh) * 2021-03-29 2021-06-18 烟台润蚨祥油封有限公司 一种油气密封件

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