WO2016111121A1 - シールリング - Google Patents
シールリング Download PDFInfo
- Publication number
- WO2016111121A1 WO2016111121A1 PCT/JP2015/085056 JP2015085056W WO2016111121A1 WO 2016111121 A1 WO2016111121 A1 WO 2016111121A1 JP 2015085056 W JP2015085056 W JP 2015085056W WO 2016111121 A1 WO2016111121 A1 WO 2016111121A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- seal ring
- angle
- peripheral surface
- housing
- respect
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0887—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by elastic deformation of the packing
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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
- F16J15/44—Free-space packings
- F16J15/441—Free-space packings with floating ring
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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
- F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
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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
- F16J15/44—Free-space packings
- F16J15/441—Free-space packings with floating ring
- F16J15/442—Free-space packings with floating ring segmented
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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
- F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
Definitions
- the present invention relates to a seal ring that can be used for hydraulic equipment.
- a seal ring is used to prevent oil leakage.
- the seal ring seals between the shaft and the housing in, for example, a hydraulic device having a configuration in which the shaft is inserted into the housing.
- the seal ring is attached to the groove portion of the shaft before being inserted into the housing.
- General seal rings have a rectangular cross section (see Patent Document 1).
- the side surface opposite to the pressure-receiving side surface contacts the groove portion of the shaft, and the outer peripheral surface contacts the inner peripheral surface of the housing.
- the seal ring seals between the shaft and the housing by contacting the shaft and the housing.
- the seal ring When the oil pressure applied to the seal ring is increased, the seal ring may be inclined with respect to the shaft and the housing due to the pressing force applied to the pressure receiving side surface and the inner peripheral surface. In such a case, the contact between the outer peripheral surface of the seal ring and the inner peripheral surface of the housing becomes insufficient, and the sealing performance by the seal ring is deteriorated.
- an object of the present invention is to provide a seal ring that can provide excellent sealing performance regardless of the hydraulic pressure.
- a seal ring includes an outer peripheral surface and a side surface formed symmetrically with respect to a plane perpendicular to the central axis.
- the outer peripheral surface has a top portion, a first tapered surface, and a second tapered surface.
- the top is provided along the plane.
- the first tapered surface has a smaller diameter as the distance from the top increases, and forms a first angle with respect to the central axis.
- the second tapered surface is provided closer to the side surface than the first tapered surface, and has a smaller diameter as the distance from the first tapered surface increases.
- the second tapered surface is larger than the first angle with respect to the central axis. Make an angle.
- the first taper surface comes into surface contact with the inner peripheral surface of the housing when the hydraulic pressure is low, and the second taper surface comes into surface contact with the inner peripheral surface of the housing when the hydraulic pressure is high. That is, in the seal ring, since the surface contact is made with the inner peripheral surface of the housing regardless of the hydraulic pressure, high sealing performance can be obtained.
- the first angle may be not less than 0.1 ° and not more than 1.0 °
- the second angle may be not less than 1.0 ° and not more than 5.0 °.
- the first tapered surface and the second tapered surface come into surface contact with the inner peripheral surface of the housing more accurately, so that particularly high sealing performance can be obtained.
- the dimension of the direction of the central axis may be larger in the second tapered surface than in the first tapered surface.
- the area of the second taper surface is large, that is, the area of the contact surface between the second taper surface and the inner peripheral surface of the housing is large, so that more stable sealing performance can be obtained even when the hydraulic pressure is high. It is done.
- the seal ring may further include an R surface that connects the outer peripheral surface and the side surface. With this configuration, the seal ring can slide smoothly with respect to the shaft and the housing.
- the side surface may approach the flat surface as the distance from the outer peripheral surface increases.
- the side surface may form a third angle larger than the second angle with respect to the plane.
- FIG. 2 is a cross-sectional view of the seal ring taken along line AA ′ of FIG. It is a fragmentary sectional view which expands and shows the area
- FIG. 1 is a side view of a seal ring 1 according to an embodiment of the present invention.
- the seal ring 1 according to the present embodiment can be applied to various hydraulic devices such as a hydraulic automatic transmission for automobiles.
- the seal ring 1 is formed in an annular shape around the central axis C, and has an outer peripheral surface 10, an inner peripheral surface 20, and two side surfaces 30a and 30b.
- the seal ring 1 is provided with an abutment 40 in a part of its circumferential direction.
- the joint 40 In the free state of the seal ring 1 where no force is applied to the seal ring 1, the joint 40 is slightly open. The diameter of the seal ring 1 increases by widening the joint 40 and decreases by narrowing the joint 40.
- the shape of the abutment 40 is not particularly limited, and a known shape can be adopted.
- the joint 40 for example, a right angle (straight) joint, an oblique (angle) joint, a stepped joint, a double angle joint, a double cut joint, a triple step joint, or the like can be used.
- the joint 40 is configured to be able to engage with each other so that oil leakage at the joint 40 is suppressed.
- the joint 40 is particularly preferably a stepped joint, a double angle joint, a double cut joint, a triple step joint, or the like.
- the material for forming the seal ring 1 can be appropriately determined depending on the driving environment. In order to reduce the friction loss (friction loss) of the seal ring 1, it is preferable that the material forming the seal ring 1 is excellent in sliding characteristics. Moreover, it is preferable that the material which forms the seal ring 1 is excellent in heat resistance.
- resin materials that can be used for the seal ring 1 include polyether ether ketone (PEEK), polytetrafluoroethylene (PTFE), tetrafluoroethylene / perfluoroalkyl vinyl ether copolymer (PFA), and tetrafluoroethylene / ethylene.
- PEEK polyether ether ketone
- PTFE polytetrafluoroethylene
- PFA perfluoroalkyl vinyl ether copolymer
- tetrafluoroethylene / ethylene examples include a copolymer (ETFE), polyvinylidene difluoride (PVDF), and polyphenylene sulfide (PPS).
- FIG. 2A is a cross-sectional view of the seal ring 1 taken along line AA ′ of FIG.
- FIG. 2B is an enlarged partial cross-sectional view of a portion of the seal ring 1 surrounded by a one-dot chain line in FIG. 2A.
- the seal ring 1 has a symmetrical shape with respect to the center plane D, which is a plane perpendicular to the center axis C. For this reason, the sealing performance by the seal ring 1 does not depend on the direction of the seal ring 1. Therefore, the seal ring 1 can be attached to the groove portion G of the shaft S without considering its direction.
- the outer peripheral surface 10 and the two side surfaces 30a and 30b are connected by the first R surface 15, respectively, and the inner peripheral surface 20 and the two side surfaces 30a and 30b are connected by the second R surface 21, respectively.
- the R surfaces 15 and 21 are configured as convex curved surfaces. As described above, the seal ring 1 can be smoothly slid with respect to the shaft S and the housing H because the corners are eliminated by the four corners being the R surfaces 15 and 21.
- the outer peripheral surface 10 of the seal ring 1 is provided with a top portion 13, a first tapered surface 11, and a second tapered surface 12 along the circumferential direction.
- the top portion 13 is provided along the center surface D and has the largest diameter on the outer peripheral surface 10.
- the 1st taper surface 11 is extended from the top part 13 to each boundary part 14 in the intermediate position of the center surface D and the side surfaces 13a and 13b.
- the second tapered surface 12 extends from each boundary portion 14 to the R surface 15.
- the top portion 13 and the boundary portion 14 may be configured as corner portions where the respective planes intersect, or may include a curved surface such as an R surface.
- an axis C ′ parallel to the central axis C is indicated by a one-dot chain line.
- the first taper surface 11 forms a first angle ⁇ 1 with respect to the center axis C
- the second taper surface 12 forms a second angle ⁇ 2 with respect to the center axis C.
- the second angle ⁇ 2 related to the second tapered surface 12 is larger than the first angle ⁇ 1 related to the first tapered surface 11.
- the outer peripheral surface 10 is configured to incline downward from the top portion 13 toward the side surfaces 30 a and 30 b, and to have a steep gradient at the boundary portion 14.
- the first angle ⁇ 1 related to the first tapered surface 11 and the second angle ⁇ 2 related to the second tapered surface 12 are determined by the hydraulic pressure applied to the seal ring 1 and the like.
- the first angle ⁇ 1 is preferably 0.1 ° or more and 1.0 ° or less
- the second angle ⁇ 2 is 1.0 ° or more. It is preferably 5.0 ° or less.
- the first dimension in the central axis C direction of the first tapered surface 11 is L 1
- a second dimension in the central axis C direction of the second tapered surface 12 is L 2.
- the first dimension L 1 related to the first tapered surface 11 and the second dimension L 2 related to the second tapered surface 12 can be determined as appropriate.
- the second dimension L 2 related to the second tapered surface 12 should be larger than the first dimension L 1 related to the first tapered surface 11.
- the second dimension L 2 is preferably first is less than 1.5 times 1.2 times the dimension L 1.
- the two side surfaces 30a and 30b of the seal ring 1 are formed in a tapered shape whose width decreases from the outer peripheral surface 10 side toward the inner peripheral surface 20 side.
- the side surface 30a is configured as a seal side surface 30a that contacts the upper end of the groove portion G of the shaft S
- the side surface 30b is configured as a pressure receiving side surface 30b that mainly receives hydraulic pressure.
- a plane D ′ parallel to the center plane D is indicated by a one-dot chain line.
- Each of the side surfaces 30a and 30b is configured as a plane that forms a third angle ⁇ 3 with respect to the center plane D.
- the third angle ⁇ 3 related to each of the side surfaces 30 a and 30 b is preferably larger than the second angle ⁇ 2 related to the second tapered surface 12.
- FIG. 3 is a cross-sectional view schematically showing the seal ring 1 incorporated in a hydraulic device.
- the seal ring 1 is mounted in the groove G of the shaft S of the hydraulic device, and the shaft S is inserted through the housing H together with the seal ring 1.
- the diameter of the seal ring 1 incorporated in the hydraulic equipment is slightly smaller than the free state. That is, the seal ring 1 presses the inner peripheral surface H ⁇ b> 1 of the housing H by the outer peripheral surface 10 by an elastic force that attempts to return to the free state.
- FIG. 3 shows a non-hydraulic state in which no oil flows between the housing H and the shaft S and no hydraulic pressure is applied to the seal ring 1.
- the outer peripheral surface 10 of the seal ring 1 is in line contact with the inner peripheral surface H1 of the housing H at the top portion 13.
- FIGS. 4A and 4B show a low oil pressure state in which oil flows between the housing H and the shaft S and a low oil pressure is applied to the seal ring 1. It is assumed that the oil pressure at the time of low oil pressure is in a first range that can be set according to the use conditions of the seal ring 1 and the like.
- the seal ring 1 at the time of low hydraulic pressure is inclined until the first tapered surface 11 comes into surface contact with the inner peripheral surface H1 of the housing H, and the first stable state where the first tapered surface 11 comes into surface contact with the inner peripheral surface H1 of the housing H. It becomes. That is, when hydraulic pressure is applied to the seal ring 1, the contact mode of the seal ring 1 with respect to the inner peripheral surface H1 of the housing H changes from the line contact shown in FIG. 3 to the surface contact shown in FIGS. 4A and 4B.
- the first taper surface 11 is in surface contact with the inner peripheral surface H1 of the housing H, that is, the first taper surface 11 is pressed by the inner peripheral surface H1 of the housing H. Yes. Therefore, since the shape of the seal ring 1 in the first stable state is regulated by the inner peripheral surface H1 of the housing H, the seal ring 1 is not easily deformed.
- an elastic force is exerted on the seal ring 1 in the first stable state so that the elastically deformed seal ring 1 returns to its original shape.
- This elastic force works in the direction opposite to the pressing force by the oil. For this reason, the seal ring 1 in the first stable state is unlikely to be further elastically deformed even when subjected to hydraulic pressure.
- the first taper surface 11 is maintained in the first stable state where the first taper surface 11 is in surface contact with the inner peripheral surface H1 of the housing H, so that excellent sealing performance can be obtained.
- FIGS. 5A and 5B show a high oil pressure state in which high oil pressure is applied to the seal ring 1 as oil further flows into the housing H and the shaft S from the state shown in FIGS. 4A and 4B. Yes.
- the hydraulic pressure at high hydraulic pressure is in the second range that can be set according to the usage conditions of the seal ring 1 and the like.
- the second range of oil pressure at the time of high oil pressure is higher than the first range of oil pressure at the time of low oil pressure.
- the seal ring 1 When the hydraulic pressure applied to the seal ring 1 rises from the first range to the second range, the seal ring 1 cannot maintain the first stable state, and the seal side surface is centered on the top portion 13 over the entire circumference. It is elastically deformed so as to be further inclined toward the 30a side.
- the seal ring 1 at the time of high hydraulic pressure is inclined until the second tapered surface 12 comes into surface contact with the inner peripheral surface H1 of the housing H, and the second stable state where the second tapered surface 12 comes into surface contact with the inner peripheral surface H1 of the housing H. It becomes. That is, even if the hydraulic pressure applied to the seal ring 1 rises from the first range to the second range, the surface contact with the inner peripheral surface H1 of the housing H by the seal ring 1 is maintained.
- the seal ring 1 in a second stable state Then, the seal side surface 30a and the side surface of the groove portion G of the shaft S are separated without surface contact. Thereby, in the seal ring 1, since the sliding resistance with respect to the groove part G of the shaft S is kept small, the friction loss with the shaft S is reduced.
- the second tapered surface 12 is in surface contact with the inner peripheral surface H1 of the housing H, that is, the second tapered surface 12 is pressed by the inner peripheral surface H1 of the housing H. Yes. Therefore, since the shape of the seal ring 1 in the second stable state is regulated by the inner peripheral surface H1 of the housing H, the seal ring 1 is not easily deformed.
- the action of regulating the shape of the seal ring 1 by the inner peripheral surface H1 of the housing H is that the area of the second taper surface 12 is large, that is, the area of the contact surface between the second taper surface 12 and the inner peripheral surface H1 of the housing H. The larger the is, the more effectively it is obtained. Therefore, to be greater than the first dimension L 1 of the second dimension L 2 of the second tapered surface 12 shown in FIG. 2B in the first tapered surface 11, the sealing ring 1 is less likely to be deformed.
- the elastic force for the elastically deformed seal ring 1 to return to the original shape is larger than that in the first stable state. For this reason, the seal ring 1 in the second stable state is unlikely to undergo further elastic deformation even when subjected to high hydraulic pressure.
- the seal ring 1 is in the first stable state at low oil pressure and is in the second stable state at high oil pressure, so that it can exhibit excellent sealing performance at both low and high oil pressures. That is, in the seal ring 1, excellent sealing performance can be obtained regardless of the hydraulic pressure.
- seal ring 1 can adopt a design different from the above embodiment.
- FIG. 6 is a cross-sectional view showing an example of the design of the seal ring 1 according to this embodiment.
- the seal rings 1a, 1b, and 1c according to the design example illustrated in FIG. 6 are different from the seal ring 1 according to the present embodiment only in the configuration of the side surfaces 30a and 30b.
- the side surfaces 30a and 30b are configured as convex curved surfaces. In this configuration, it is possible to prevent the seal side surface 30a from being in surface contact with the side surface of the groove portion G of the shaft S. For this reason, in the seal ring 1a, the friction loss between the shaft S and the shaft S can be reduced.
- the angles of the side surfaces 30a and 30b with respect to the central surface D are not constant, but are larger on the inner peripheral surface 20 side.
- the pressing force applied from the oil to the seal side surface 30a increases.
- the friction loss between the seal ring 1b and the shaft S can be reduced.
- concave pockets Pa and Pb are provided on the inner peripheral surface 20 side of the side surfaces 30a and 30b.
- the pressing force applied from the oil to the seal side surface 30a increases.
- the friction loss between the seal ring 1c and the shaft S can be reduced.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Architecture (AREA)
- Fluid Mechanics (AREA)
- Sealing Devices (AREA)
Abstract
Description
上記外周面は、頂部と、第1テーパ面と、第2テーパ面と、を有する。
上記頂部は、上記平面に沿って設けられている。
上記第1テーパ面は、上記頂部から離れるにつれて小径になり、上記中心軸に対して第1の角度を成す。
上記第2テーパ面は、上記第1テーパ面よりも上記側面側に設けられ、上記第1テーパ面から離れるにつれて小径になり、上記中心軸に対して上記第1の角度よりも大きい第2の角度を成す。
この構成のシールリングでは、第1テーパ面及び第2テーパ面がより的確にハウジングの内周面に面接触するようになるため、特に高いシール性が得られる。
この構成のシールリングでは、第2テーパ面の面積が大きく、つまり第2テーパ面とハウジングの内周面との接触面の面積が大きくなるため、油圧が高い場合においてより安定したシール性が得られる。
この構成により、上記シールリングがシャフトやハウジングに対してスムーズに摺動可能となる。
上記側面は、上記平面に対して上記第2の角度よりも大きい第3の角度を成していてもよい。
この構成により、上記シールリングの側面が溝部の側面に面接触しにくくなる。このため、上記シールリングでは、シャフトの溝部に対する摺動抵抗が小さくなるため、シャフトの溝部との間におけるフリクションロスが低減される。
図1は、本発明の一実施形態に係るシールリング1の側面図である。本実施形態に係るシールリング1は、油圧式の自動車用自動変速機など、種々の油圧機器に適用可能である。シールリング1は、中心軸Cを中心とする環状に形成され、外周面10と、内周面20と、2つの側面30a,30bと、を有する。
シールリング1では上記実施形態とは異なるデザインを採用することが可能である。
10…外周面
11…第1テーパ面
12…第2テーパ面
13…頂部
14…境界部
15…R面
20…内周面
30a,30b…側面
C…中心軸
D…中央面
Claims (6)
- 中心軸に垂直な平面について対称に形成された外周面及び側面を具備し、
前記外周面は、
前記平面に沿って設けられた頂部と、
前記頂部から離れるにつれて小径になり、前記中心軸に対して第1の角度を成す第1テーパ面と、
前記第1テーパ面よりも前記側面側に設けられ、前記第1テーパ面から離れるにつれて小径になり、前記中心軸に対して前記第1の角度よりも大きい第2の角度を成す第2テーパ面と、
を有する
シールリング。 - 請求項1に記載のシールリングであって、
前記第1の角度は0.1°以上1.0°以下であり、前記第2の角度は1.0°以上5.0°以下である
シールリング。 - 請求項1又は2に記載のシールリングであって、
前記中心軸の方向の寸法が前記第1テーパ面より前記第2テーパ面の方が大きい
シールリング。 - 請求項1から3のいずれか1項に記載のシールリングであって、
前記外周面と前記側面とを接続するR面を更に具備する
シールリング。 - 請求項1から4のいずれか1項に記載のシールリングであって、
前記側面は前記外周面から離れるにつれて前記平面に近接する
シールリング。 - 請求項5に記載のシールリングであって、
前記側面は、前記平面に対して前記第2の角度よりも大きい第3の角度を成す
シールリング。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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CN201580071498.3A CN107110361B (zh) | 2015-01-08 | 2015-12-15 | 密封圈 |
US15/542,355 US10378651B2 (en) | 2015-01-08 | 2015-12-15 | Seal ring |
KR1020177019773A KR101900394B1 (ko) | 2015-01-08 | 2015-12-15 | 밀봉 링 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2015002344A JP6491885B2 (ja) | 2015-01-08 | 2015-01-08 | シールリング |
JP2015-002344 | 2015-01-08 |
Publications (1)
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WO2016111121A1 true WO2016111121A1 (ja) | 2016-07-14 |
Family
ID=56355823
Family Applications (1)
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PCT/JP2015/085056 WO2016111121A1 (ja) | 2015-01-08 | 2015-12-15 | シールリング |
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US (1) | US10378651B2 (ja) |
JP (1) | JP6491885B2 (ja) |
KR (1) | KR101900394B1 (ja) |
CN (1) | CN107110361B (ja) |
WO (1) | WO2016111121A1 (ja) |
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DE102018114701A1 (de) * | 2018-06-19 | 2019-12-19 | Konzelmann Gmbh | Hydrodynamisch wirksamer Dichtring und Drehdurchführung mit einem solchen Dichtring |
JP7153161B2 (ja) * | 2019-12-11 | 2022-10-13 | Ntn株式会社 | シールリングおよび油圧機器 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002295692A (ja) * | 2001-04-02 | 2002-10-09 | Nok Corp | シールリング |
WO2012102250A1 (ja) * | 2011-01-25 | 2012-08-02 | 日本バルカー工業株式会社 | シール材 |
JP2014202221A (ja) * | 2013-04-01 | 2014-10-27 | Nok株式会社 | シールリング及び密封構造 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1160574A (en) * | 1966-08-05 | 1969-08-06 | Dowty Seals Ltd | Seal |
US3727927A (en) * | 1968-09-06 | 1973-04-17 | Int Harvester Co | Ring manufacture, productive of line contact seal |
US3771801A (en) * | 1972-06-05 | 1973-11-13 | Greene Tweed & Co Inc | Sealing device |
US4350352A (en) * | 1981-07-24 | 1982-09-21 | Mack Trucks, Inc. | Piston ring and groove assemblies |
JP2551701Y2 (ja) | 1991-03-27 | 1997-10-27 | エヌティエヌ株式会社 | 自動変速機用オイルシールリング |
US5524905A (en) * | 1994-09-28 | 1996-06-11 | Greene, Tweed Of Delaware, Inc. | Sealing assembly with T-shaped seal ring and anti-extrusion rings |
JP3437312B2 (ja) * | 1995-02-16 | 2003-08-18 | 株式会社リケン | シールリングおよびシール装置 |
US6450502B1 (en) * | 1998-11-14 | 2002-09-17 | Ti Specialty Polymer Products, Inc. | Rotary seal with relief angle for controlled tipping |
JP2005003130A (ja) * | 2003-06-12 | 2005-01-06 | Nok Corp | ガスケットの組付け方法及びガスケット |
JP2006316947A (ja) * | 2005-05-16 | 2006-11-24 | Mitsubishi Cable Ind Ltd | 塗装機用ピストンパッキン |
JP2012255495A (ja) | 2011-06-09 | 2012-12-27 | Nok Corp | シールリング |
-
2015
- 2015-01-08 JP JP2015002344A patent/JP6491885B2/ja active Active
- 2015-12-15 KR KR1020177019773A patent/KR101900394B1/ko active IP Right Grant
- 2015-12-15 WO PCT/JP2015/085056 patent/WO2016111121A1/ja active Application Filing
- 2015-12-15 CN CN201580071498.3A patent/CN107110361B/zh active Active
- 2015-12-15 US US15/542,355 patent/US10378651B2/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002295692A (ja) * | 2001-04-02 | 2002-10-09 | Nok Corp | シールリング |
WO2012102250A1 (ja) * | 2011-01-25 | 2012-08-02 | 日本バルカー工業株式会社 | シール材 |
JP2014202221A (ja) * | 2013-04-01 | 2014-10-27 | Nok株式会社 | シールリング及び密封構造 |
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CN107110361A (zh) | 2017-08-29 |
CN107110361B (zh) | 2019-06-18 |
KR20170105516A (ko) | 2017-09-19 |
KR101900394B1 (ko) | 2018-09-20 |
US20180274679A1 (en) | 2018-09-27 |
US10378651B2 (en) | 2019-08-13 |
JP6491885B2 (ja) | 2019-03-27 |
JP2016125644A (ja) | 2016-07-11 |
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