US20070054586A1 - Rotation shaft seal - Google Patents

Rotation shaft seal Download PDF

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Publication number
US20070054586A1
US20070054586A1 US11/506,898 US50689806A US2007054586A1 US 20070054586 A1 US20070054586 A1 US 20070054586A1 US 50689806 A US50689806 A US 50689806A US 2007054586 A1 US2007054586 A1 US 2007054586A1
Authority
US
United States
Prior art keywords
axis
rotation shaft
orthogonal
pressure
concavo
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US11/506,898
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English (en)
Inventor
Takeshi Baba
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Cable Industries Ltd
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
Assigned to MITSUBISHI CABLE INDUSTRIES, LTD. reassignment MITSUBISHI CABLE INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BABA, TAKESHI
Publication of US20070054586A1 publication Critical patent/US20070054586A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F16J15/3216—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip supported in a direction parallel to the surfaces
    • 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
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring
    • 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
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports

Definitions

  • This invention relates to a rotation shaft seal, especially, a rotation shaft seal used to seal high-pressure fluid such as gas.
  • a rotation shaft seal 31 as shown in FIG. 3C having a rubber lip portion 33 , is used (refer to Japanese patent provisional publication No. 2003-097723).
  • a rubber member 37 surrounding an inner brim portion 36 of an outer case 34 , and the inner brim portion 36 are united by adhesion or baking, and the rubber lip portion 33 composed of a part of the rubber member 37 is supported on a low-pressure side E and an inner peripheral face side (back side) by a supporting metal 38 L-shaped in cross section.
  • a lip end portion 33 a is greatly extended toward a sealed fluid side (high-pressure side) C and the lip portion 33 is formed as a cylinder of which center is an axis L of a rotation shaft 32 .
  • this is a rotation shaft seal provided with a rubber sealing portion 39 having a sliding portion S 0 which contacts a surface of the rotation shaft 32 and an outer case 34 of metal to which the rubber sealing portion 39 is unitedly fixed.
  • the outer case 34 has an inner brim portion 36 on an inner end portion on the sealed fluid side (high-pressure side C), the inner brim portion 36 is covered by the rubber sealing portion 39 , and the sliding portion S 0 is disposed within a dimension M of the outer case 34 in axis direction including a thickness dimension T 4 2 of a rubber covering layer 42 covering the inner brim portion 36 on the sealed fluid side.
  • the lip portion 33 is not extended toward the high-pressure side (sealed fluid side) C as shown in FIG. 3C , and the sliding portion S 0 is disposed on or near an axis-orthogonal face 43 including the inner brim portion 36 as shown in FIG. 8 .
  • the rubber sealing portion 39 is provided with an axis-orthogonal wall portion 44 having the sliding portion S 0 on an inner peripheral edge, and the axis-orthogonal wall portion 44 is supported by an axis-orthogonal supporting metal 45 on a low-pressure side E.
  • the inner peripheral edge 45 a circular and formed as a flat washer, uniformly supports the whole periphery of the back face (low-pressure side E) of the axis-orthogonal wall portion 44 of the rubber sealing portion 39 . Therefore, the rubber lip portion 33 is disposed on the inner peripheral edge side along the axis-orthogonal face 43 and having extremely small pressure-receiving area.
  • the lip portion 33 sliding on the rotation shaft 32 in high-speed rotation, is greatly deformed by receiving the pressure of the cooling medium, heat generation is increased, abrasion rapidly progresses, and operational life of the seal is made short.
  • FIG. 1 is a cross-sectional view of a principal portion showing an embodiment of the present invention
  • FIG. 2 is a front view showing an embodiment of a principal part (back-supporting metal);
  • FIGS. 3A, 3B , and 3 C are explanatory cross-sectional views to compare configurations and working of the present invention and the conventional example, and to explain working of the present invention;
  • FIG. 4A is an explanatory perspective view to explain a principal portion and working
  • FIG. 4B is an explanatory graph to explain the principal portion and working
  • FIG. 5 is a front view of a principal part showing another embodiment
  • FIG. 6A is an enlarged longitudinal cross-sectional view showing a principal part
  • FIG. 6B is an enlarged longitudinal cross-sectional view showing a principal part
  • FIG. 7A is a cross-sectional view of a principal portion showing experimental result of the present invention.
  • FIG. 7B is a cross-sectional view of a principal portion showing experimental result of a conventional example.
  • FIG. 8 is a cross-sectional view of a principal portion showing ter conventional example.
  • FIGS. 1, 2 , 3 A, and 3 B show an embodiment of the present invention.
  • FIG. 1 is a longitudinal cross-sectional view
  • FIG. 2 is a front view of a principal part
  • FIGS. 3A and 3B are longitudinal cross-sectional views to explain working of a principal portion.
  • This rotation shaft seal is, for example, for sealing high-pressure cooling media on a sealed fluid chamber 21 side.
  • a half cross section of the rotation shaft seal is shown in FIGS. 1, 3A , and 3 B, and FIG. 1 shows free state (unattached state).
  • a rotation shaft 20 and a housing (casing) 22 are shown with two-dot broken lines.
  • solid lines in FIGS. 3A and 3B show pressure-receiving state (described later) in which the seal is placed between the rotation shaft 20 and the housing 22 .
  • a mark 1 represents an outer case having inner brim portions 2 and 3
  • rubber sealing portion 5 is unitedly fixed to a peripheral face of a cylindrical wall portion 4 of the outer case 1 and both of front and rear faces of the inner brim portion 2 on a sealed fluid side C (the sealed fluid chamber 21 side) by adhesion, welding, or heat molding.
  • a seal element 7 with a spiral groove 6 is disposed on an opposite side Z (also mentioned as low-pressure side or atmosphere side) to the sealing portion 5 .
  • the seal element 7 is preferably composed of fluororesin such as PTFE.
  • a mark 8 represents a back face supporting metal 8 which is approximately L-shaped in cross section, serving also as a so-called inner case, and composed of a cylindrical plate portion 15 fit to the inner peripheral face of the cylindrical wall portion 4 of the outer case 1 and an axis-orthogonal plate portion 16 at right angles with the axis L.
  • the back face supporting metal 8 , an inner case 9 of I-shaped cross section, the seal element 7 , and an inner member 11 of L-shaped cross section are serially layered and fixed to the inner brim portions 2 and 3 .
  • the rubber sealing portion 5 is provided with a cylindrical cover portion 5 a , having a concavo-convex wave portion (in free state) to elastically touch the inner peripheral face of the housing 22 for sealing work, and an axis-orthogonal wall portion 5 b having an inner brim cover portion of U-shaped cross section, covering the front and rear faces of the inner brim portion 2 , on a peripheral side, and a sliding portion 23 , touching the surface of the rotation shaft 20 , on an inner peripheral edge.
  • the axis-orthogonal wall portion 5 b is formed as to be at right angles with the axis L, extended from the inner brim cover portion covering the inner brim portion 2 of the outer case 1 inward in radius direction, and having the sliding portion 23 on the inner peripheral edge.
  • the axis-orthogonal plate portion 16 of the back face supporting metal 8 supports the axis-orthogonal wall portion 5 b of the rubber sealing portion 5 from the low-pressure side Z.
  • a ring concave groove 24 is formed on the low-pressure side Z (back face side) of the axis-orthogonal wall portion 5 b .
  • the ring concave groove 24 has a function to prevent compressed rubber under pressure-receiving state of the axis-orthogonal wall portion 5 b from excessively flowing inward (refer to FIG. 3A ), the concave groove 24 may be occasionally omitted in the present invention.
  • the outer case 1 has the inner brim portion 2 on the inner end portion on the sealed fluid side C, and the sliding portion 23 is disposed on an axis-orthogonal face P 0 including the inner brim portion 2 .
  • the inner brim portion 2 has a (small) thickness, and plural axis-orthogonal faces P 0 exist with an interval in the axis direction for the (small) thickness.
  • a position in the axis direction of the sliding portion 23 is disposed on one of the axis-orthogonal faces P 0 .
  • the position in the axis direction of the sliding portion 23 is defined as a center of gravity G of contact pressure P on a position sliding on the rotation shaft 20 under the maximum operational pressure (refer to FIG. 3A ).
  • the position in the axis direction of the sliding portion 23 may be preferably disposed near the axis-orthogonal face P 0 . “Near” means deviation within five times of the thickness of the inner brim portion 2 .
  • the position in the axis direction of the sliding portion 23 is disposed within an inner dimension M of the outer case 1 in the axis direction.
  • the inner dimension M in the axis direction is defined as a dimension including (together with) a thickness dimension T 17 of the rubber covering layer 17 covering the inner brim portion 2 on the sealed fluid side C.
  • the inner peripheral edge of the axis-orthogonal plate portion 16 of the back face supporting metal 8 is formed concavo-convex.
  • three protruding portions 25 are disposed on the inner peripheral edge to form concave portions 26 between the neighboring protruding portions 25 .
  • the hammer-shaped lip portion 27 having the sliding portion 23 is sufficiently supported by the protruding portion 25 on the peripheral position where the protruding portion exists, and hardly deformed toward the right side in FIG. 3A (the low-pressure side Z).
  • the sliding portion 23 draws a concavo-convex wave pattern W as shown in FIG. 4A . That is to say, the center of gravity G of the contact pressure P of the sliding portion 23 changes along the periphery as to draw waves along the peripheral face of the rotation shaft 20 .
  • FIG. 4B is a graph in which the position X in the axis direction is shown on the axis of abscissa and a position R in peripheral direction is shown on the axis of ordinate.
  • the sliding portion 23 accurately, the center of gravity G of the contact pressure P, where the sliding portion 23 is pressed to the surface of the rotation shaft 20 , changes in the axis direction as to draw the concavo-convex wave pattern W.
  • supporting force of the axis-orthogonal plate portion 16 of the supporting metal 8 supporting the axis-orthogonal wall portion 5 b from the low-pressure side is increased and decreased along the peripheral direction as the position of the sliding portion 23 draws the concavo-convex wave pattern W along the peripheral direction on the surface of the rotation shaft 20 in the pressure-receiving state.
  • FIGS. 5 and 6 A show another embodiment.
  • FIG. 5 is a front view of the back face supporting metal 8 as a part of the principal portion
  • FIG. 6A is an enlarged longitudinal cross-sectional view of FIG. 5 .
  • concave portions 28 are formed along the peripheral direction by cutting, etc. on a sealing portion supporting face 16 a where the axis-orthogonal plate portion 16 supports the axis-orthogonal wall portion 5 b of the sealing portion 5 from the low-pressure side Z, and concavo-convex portions are formed on the inner peripheral edge of the supporting face 16 a . That is to say, convex portions 29 are composed of parts where the supporting face 16 a remains, and the concave portions 28 are composed of slightly cut (shaved) parts. Other constructions are same as that of the above-described embodiment in FIGS. 1 and 2 .
  • FIG. 6B shows a modification.
  • three concave portions 28 are formed along the peripheral direction on the inner peripheral edge of the sealing portion supporting face 16 a of the axis-orthogonal plate portion 16 by press work to form concavo-convex portions. That is to say, convex portions 29 are composed of parts where the supporting face 16 a remains, and the concave portions 28 are composed by slight plastic deformation.
  • Other constructions are same as that of the above-described embodiment in FIGS. 1 and 2 .
  • the number of the concave portions 28 may be 2 or more than 4 in FIGS. 5, 6A , and 6 B.
  • the lip portion 27 deforms as to intrude to the concave portion 28 toward the low-pressure side Z.
  • the sliding portion 23 (refer to FIG. 1 ) draws a concavo-convex wave pattern W as shown in FIG. 4A
  • the center of gravity G of contact pressure P (refer to FIG. 3A ) changes according to the position in the peripheral direction as to draw a wave on the periphery along the peripheral face of the rotation shaft 20 . That is to say, the concavo-convex wave pattern W is drawn as shown in FIG. 4B .
  • the concavo-convex portions are formed along the peripheral direction on the sealing portion supporting face 16 a of the axis-orthogonal plate portion 16 of the back face supporting metal 8 as the configuration of the sliding portion 23 of the lip portion 27 becomes concavo-convex wave along the peripheral direction on the surface of the rotation shaft 20 under the pressure-receiving state.
  • the concave portion 26 may be formed by cutting the inner peripheral edge on the concave portion 28 in FIGS. 5, 6A , and 6 B for a small dimension in radius direction in comparison with FIGS. 1 and 2 .
  • Comparison experiment was conducted to compare the product of the present invention shown in FIGS. 1 and 2 with the conventional example of FIG. 8 under the condition of pressure of 4.0 MPa, fluid temperature of 100° C., and sliding speed of the sliding portion of 4.6 m/sec. Abrasions on the sliding portions 23 and S 0 are respectively shown in FIGS. 7A and 7B .
  • an abraded portion 47 after 10 hours is extremely large.
  • an abraded portion 47 after 17 hours is small as shown in FIG. 7A .
  • the sliding portion S 0 is on the axis-orthogonal face 43 , oil film is hardly generated, amount of heat generation is large, and large abrasion was resulted thereby.
  • the product of the present invention sliding on the concavo-convex wave W as shown in FIGS. 4A and 4B , oil film is easily generated, heat radiation is enhanced, abrasion amount of the sliding portion 23 of the lip portion 27 is reduced, and durability is improved thereby.
  • an inner peripheral edge 45 a may be formed on the axis-orthogonal supporting metal 45 in the conventional example shown in FIG. 8 as to be concavo-convex like the axis-orthogonal plate portion 16 in FIGS. 1 and 2 , or a concave portion 28 may be formed as in FIG. 6 (not shown in Figures).
  • two or more seal elements 7 may be disposed, the seal element 7 may be omitted, and, configuration of the supporting metal 8 , number and configuration of the inner case 9 and the inner member 11 may be freely changed.
  • lubricant oil (sealed fluid) is introduced to the portion between the sliding portion 23 and the rotation shaft 20 where the sliding portion 23 is moved to the low-pressure side Z, the lubricant oil (sealed fluid) is spread over the entire periphery of the sliding portion 23 along the rotation of the rotation shaft 20 , friction heat generation and early abrasion are prevented, and the seal is made long-life because the rotation shaft seal, provided with the rubber sealing portion 5 having the axis-orthogonal wall portion 5 b , having the sliding portion 23 which contacts the surface of the rotation shaft 20 on the inner peripheral edge, and the back face supporting metal 8 having the axis-orthogonal plate portion 16 which supports the axis-orthogonal wall portion 5 b from the low-pressure side, is constructed as that the inner peripheral edge of the axis-orthogonal plate portion 16 of the back face supporting metal 8 is formed concavo-convex, and the sliding portion 23 is made the concavo-convex wave W along the peripheral
  • lubricant oil (sealed fluid) is introduced to the portion between the sliding portion 23 and the rotation shaft 20 where the sliding portion 23 is moved to the low-pressure side Z, the lubricant oil (sealed fluid) is spread over the entire periphery of the sliding portion 23 along the rotation of the rotation shaft 20 , friction heat generation and early abrasion are prevented, and the seal is made long-life because the rotation shaft seal, provided with the rubber sealing portion 5 having the axis-orthogonal wall portion 5 b , having the sliding portion 23 which contacts the surface of the rotation shaft 20 on the inner peripheral edge, and the back face supporting metal 8 having the axis-orthogonal plate portion 16 which supports the axis-orthogonal wall portion 5 b from the low-pressure side, is constructed as that the concavo-convex portion is formed on the sealing portion supporting face 16 a of the axis-orthogonal plate portion 16 of the back face supporting metal 8 along the peripheral direction, and the sliding portion 23 is made
  • the seal having excellent durability is appropriate for sealing high-pressure gas of compressors for car air conditioners.
  • depth of the concavo-convex portion to be formed on the sealing portion supporting face 16 a can be relatively easily set (made) according to operational pressure and configurations of the lip portion 27 , and the seal can correspond to operational conditions with flexibility.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
US11/506,898 2005-09-07 2006-08-21 Rotation shaft seal Abandoned US20070054586A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-259613 2005-09-07
JP2005259613A JP4579110B2 (ja) 2005-09-07 2005-09-07 回転軸シール

Publications (1)

Publication Number Publication Date
US20070054586A1 true US20070054586A1 (en) 2007-03-08

Family

ID=37575195

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/506,898 Abandoned US20070054586A1 (en) 2005-09-07 2006-08-21 Rotation shaft seal

Country Status (5)

Country Link
US (1) US20070054586A1 (fr)
EP (1) EP1762758A1 (fr)
JP (1) JP4579110B2 (fr)
KR (1) KR20070028217A (fr)
CN (1) CN1928397A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080169613A1 (en) * 2007-01-15 2008-07-17 Mitsubishi Cable Industries, Ltd. Rotation shaft seal
CN103398176A (zh) * 2013-07-26 2013-11-20 苏州天华有色金属制品有限公司 一种轴封圈
US20150042044A1 (en) * 2013-08-05 2015-02-12 Aktiebolaget Skf Sealing assembly
US20150267817A1 (en) * 2014-03-24 2015-09-24 Mitsubishi Cable Industries, Ltd. Shaft seal

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016208697A1 (de) * 2016-05-20 2017-11-23 Trelleborg Sealing Solutions Germany Gmbh Rotationsdichtungsanordnung mit druckaktivierbarer Rotationsdichtung sowie Rotationsdichtung

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2208482A (en) * 1936-08-19 1940-07-16 Victor Mfg & Gasket Co Grease retainer with integral diaphragm and outer seal
US2209750A (en) * 1937-08-07 1940-07-30 Victor Mfg & Gasket Co Fluid seal with spongy packing
US2590696A (en) * 1945-09-13 1952-03-25 Resta S Gregoire Oil seal
US3306620A (en) * 1964-04-16 1967-02-28 Koppers Co Inc Thermally stable lip seal
US4427206A (en) * 1982-07-20 1984-01-24 Keeper Co., Ltd. Oil seal assembly with unbonded backup ring
US5183271A (en) * 1990-01-25 1993-02-02 Nok Corporation Sealing device and manufacturing method of the same
US20060249915A1 (en) * 2005-04-29 2006-11-09 Federal Mogul World Wide, Inc. Shaft seal having integrated removal feature
US7344140B2 (en) * 2003-02-27 2008-03-18 Eagle Industry Co., Ltd. Lip-type seal

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US2867462A (en) * 1953-12-28 1959-01-06 Borg Warner Housing confined lip seal
US4323287A (en) * 1979-10-03 1982-04-06 The Torrington Company Bearing seal
GB2139299A (en) * 1983-04-26 1984-11-07 Coal Ind Improvements relating to seals
DE3425431C1 (de) * 1984-07-11 1985-12-05 Heinz Konrad Prof. Dr.-Ing. 7050 Waiblingen Müller Wellendichtung
DE3502799A1 (de) * 1984-07-11 1986-07-31 Martin Merkel GmbH & Co KG, 2102 Hamburg Wellendichtung
DE3830706A1 (de) * 1988-09-09 1990-03-22 Freudenberg Carl Fa Wellendichtung
JPH0351279U (fr) * 1989-09-26 1991-05-17
JPH0642142Y2 (ja) * 1990-03-23 1994-11-02 イーグル工業株式会社 リップ型シール
DE19703355C2 (de) * 1997-01-30 2003-05-15 Zf Sachs Ag Dichtungsanordnung
JPH11159629A (ja) * 1997-11-28 1999-06-15 Nok Corp オイルシール
JP2003097723A (ja) 2001-09-25 2003-04-03 Mitsubishi Cable Ind Ltd 回転軸シール
JP2004353765A (ja) * 2003-05-29 2004-12-16 Mitsubishi Cable Ind Ltd 回転軸シール
US7134670B2 (en) * 2003-05-29 2006-11-14 Mitsubishi Cable Industries, Ltd. Rotation shaft seal

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2208482A (en) * 1936-08-19 1940-07-16 Victor Mfg & Gasket Co Grease retainer with integral diaphragm and outer seal
US2209750A (en) * 1937-08-07 1940-07-30 Victor Mfg & Gasket Co Fluid seal with spongy packing
US2590696A (en) * 1945-09-13 1952-03-25 Resta S Gregoire Oil seal
US3306620A (en) * 1964-04-16 1967-02-28 Koppers Co Inc Thermally stable lip seal
US4427206A (en) * 1982-07-20 1984-01-24 Keeper Co., Ltd. Oil seal assembly with unbonded backup ring
US5183271A (en) * 1990-01-25 1993-02-02 Nok Corporation Sealing device and manufacturing method of the same
US7344140B2 (en) * 2003-02-27 2008-03-18 Eagle Industry Co., Ltd. Lip-type seal
US20060249915A1 (en) * 2005-04-29 2006-11-09 Federal Mogul World Wide, Inc. Shaft seal having integrated removal feature

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080169613A1 (en) * 2007-01-15 2008-07-17 Mitsubishi Cable Industries, Ltd. Rotation shaft seal
US7780172B2 (en) * 2007-01-15 2010-08-24 Mitsubishi Cable Industries, Ltd. Rotation shaft seal
CN103398176A (zh) * 2013-07-26 2013-11-20 苏州天华有色金属制品有限公司 一种轴封圈
US20150042044A1 (en) * 2013-08-05 2015-02-12 Aktiebolaget Skf Sealing assembly
US9410555B2 (en) * 2013-08-05 2016-08-09 Aktiebolaget Skf Sealing assembly
US20150267817A1 (en) * 2014-03-24 2015-09-24 Mitsubishi Cable Industries, Ltd. Shaft seal
US9506567B2 (en) * 2014-03-24 2016-11-29 Mitsubishi Cable Industries, Ltd. Shaft seal

Also Published As

Publication number Publication date
KR20070028217A (ko) 2007-03-12
JP2007071309A (ja) 2007-03-22
EP1762758A1 (fr) 2007-03-14
JP4579110B2 (ja) 2010-11-10
CN1928397A (zh) 2007-03-14

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AS Assignment

Owner name: MITSUBISHI CABLE INDUSTRIES, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BABA, TAKESHI;REEL/FRAME:018216/0286

Effective date: 20060713

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION