WO2012120383A1 - Agencement d'étanchéité, système hydraulique comprenant ce dernier et bague d'appui pour l'agencement d'étanchéité - Google Patents

Agencement d'étanchéité, système hydraulique comprenant ce dernier et bague d'appui pour l'agencement d'étanchéité Download PDF

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Publication number
WO2012120383A1
WO2012120383A1 PCT/IB2012/000888 IB2012000888W WO2012120383A1 WO 2012120383 A1 WO2012120383 A1 WO 2012120383A1 IB 2012000888 W IB2012000888 W IB 2012000888W WO 2012120383 A1 WO2012120383 A1 WO 2012120383A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
sealing arrangement
groove
inner ring
valve
Prior art date
Application number
PCT/IB2012/000888
Other languages
English (en)
Other versions
WO2012120383A8 (fr
Inventor
David Green
Javedkhan Nijam TAMBOLI
Parag S. JADHAV
Original Assignee
Eaton Limited
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 Eaton Limited filed Critical Eaton Limited
Publication of WO2012120383A1 publication Critical patent/WO2012120383A1/fr
Publication of WO2012120383A8 publication Critical patent/WO2012120383A8/fr

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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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
    • 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
    • F16J15/021—Sealings between relatively-stationary surfaces with elastic packing
    • 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
    • F16J15/021—Sealings between relatively-stationary surfaces with elastic packing
    • F16J15/028—Sealings between relatively-stationary surfaces with elastic packing the packing being mechanically expanded against the sealing surface
    • 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
    • F16J15/166—Sealings between relatively-moving surfaces with means to prevent the extrusion of the packing
    • 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
    • F16J15/181—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings for plastic packings

Definitions

  • the present invention relates to a sealing arrangement for sealing an interface between two components in a hydraulic system, for example, a sealing arrangement that forms a face seal in a two way cartridge valve.
  • Two way cartridge valves are well known and are typically used as direction control valves, flow control valves or pressure control valves.
  • Known two way cartridge valves comprise an insert that is inserted into a standard bore hole in a manifold, a flat cover for covering the insert in the manifold and a face seal provided between the insert and the cover to prevent leakage of hydraulic fluid during the operation of the valve.
  • the height of the insert and the depth of the bore hole are an exact match but in practice manufacturing tolerances in the dimensions of these components often result in the height of the insert being less than the depth of the bore hole. If the height of the insert is less than the depth of the bore hole, the insert is able to oscillate up and down in the bore in response to pressure changes in the valve.
  • Embodiments of the present invention aim to provide a sealing arrangement that is durable and robust.
  • the sealing arrangement is particularly, but not exclusively, suitable for forming a seal between a cover and an insert of a two way cartridge valve and negates the need to use a shim in instances when the height of the insert is less than the depth of the bore hole.
  • Embodiments of the invention also aim to provide an improved back up ring for use in such a sealing arrangement.
  • a sealing arrangement for inserting in a groove in a hydraulic system to form a seal between two surfaces in the system, the sealing arrangement comprising: an outer ring and an inner ring arrangeable co-planarly and concentrically in the groove, wherein the inner ring comprises a resiliently deformable material and the outer ring is more rigid than the inner ring and is for supporting the inner ring in the groove, wherein the outer ring comprises an inner surface facing substantially radially inwardly of the outer ring and the inner ring comprises an outer surface facing substantially radially outwardly of the inner ring, wherein the inner surface of the outer ring describes a surface recess that accepts at least a portion of the outer surface of the inner ring.
  • the recess is preferably concave.
  • a sealing arrangement for inserting in a groove in a hydraulic system to form a seal between two surfaces in the system, the sealing arrangement comprising: an outer ring and an inner ring arrangeable co-planarly and concentrically in the groove, wherein the inner ring comprises a resiliently deformable material and the outer ring is more rigid than the inner ring and is for supporting the inner ring in the groove, wherein the outer ring comprises an inner surface facing substantially radially inwardly of the outer ring and the inner ring comprises an outer surface facing substantially radially outwardly of the inner ring, wherein the outer ring compresses the inner ring radially.
  • the outer ring may comprise an outer circumferential surface facing substantially radially outwards of the outer ring and which slants, so that in cross section the outer ring appears roughly trapezoidal.
  • a back up ring for supporting an elastomeric ring seal in a groove of a hydraulic system, the back up ring comprising an inner circumferential surface that extends around an inner circumference of the back up ring and faces generally radially inwardly of the ring, the inner circumferential surface describing a surface recess for receiving an outer circumferential surface portion of the elastomeric ring seal.
  • a hydraulic system comprising a back up ring for supporting an elastomeric seal in the system, wherein the back up ring is in a pre-compressed state in the system.
  • Figure 1 is a schematic axial sectional view of a known valve
  • Figure 2 is a schematic axial sectional view of a valve system embodying the present invention
  • Figure 3 is a schematic plan view of the valve system of Figure 2 with a valve cover removed;
  • Figure 4 is a highly schematic enlarged view of part of the valve system of Figure 2.
  • Figure 5 is a schematic axial section view showing part of the valve system embodying the invention.
  • Figure 6 is a schematic view of part of a cross section of a back up ring used in the valve system of Figure 2. Detailed Description
  • FIG. 1 illustrates a typical known two port cartridge valve 1.
  • the valve 1 comprises a generally tubular valve sleeve 4, extending along an axial axis A of the valve 1 and which is inserted into a stepped bore 2 of a manifold 3.
  • the valve 1 further comprises a poppet 5 mounted within the valve sleeve 4 for sliding reciprocal movement along the axis A, and a closure spring 6 that biases the poppet 5 into a sealing engagement with a valve seat 7 formed in valve sleeve 4.
  • the stepped bore 2 comprises a first bore step 8 and a second bore step 9 of larger diameter than the first bore step 8.
  • the second bore step 9 has its mouth in an upper surface 10 of the manifold 3.
  • a first flow channel 11 for hydraulic fluid in the manifold 3 opens coaxially into the first bore step 8 and a second flow channel 12 for the hydraulic fluid opens laterally into the second bore step 9.
  • a valve cover 13, which covers the valve sleeve 4 in the manifold 3 is connected to the upper surface 10 by suitable fixing means 14, for example bolts.
  • the valve sleeve 4 comprises an upper section 15 having a cross sectional diameter that corresponds with that of the second bore step 9 and a lower section 16 having a cross sectional diameter that corresponds with that of the first bore step 8.
  • the valve sleeve 4 further comprises a middle section 17, between the upper 15 and lower 16 sections, the middle section 17 and the manifold 3 defining, in the second bore step 9, an annular chamber 18 that surrounds the valve sleeve 4.
  • the valve sleeve 4 defines an internal axial guide bore 19 within which the poppet 5 is mounted for reciprocal movement between the valve seat 7 and the cover 13.
  • the valve sleeve 4 defines an axial fluid port 20 that communicates with the first flow channel 1 1 in the manifold 3.
  • the valve sleeve 4 defines in its middle section 17 a plurality of lateral fluid ports 21, spaced apart around the circumference of the middle section 17, which open into the annular chamber 18.
  • the poppet 5 comprises at its lower end a closure member 22 for sealingly engaging the valve seat 7 to close the axial fluid port 20.
  • the poppet 5 defines an axial spring chamber 23 containing the closure spring 6.
  • the closure spring 6 has a free end supported on the underside of the valve cover 13 and is biased so as to urge the poppet 5 towards the valve seat 7.
  • An axial pilot oil chamber 24 is defined within the guide bore 19, which is connected to a pilot oil source (not shown) via a pilot oil bore 25 in the cover 13.
  • the lower section 16 of the valve sleeve 4 comprises, part way down its length, a groove 26 formed around its circumference, containing a first sealing ring arrangement 27 forming a seal between the lower section 16 and the manifold 3.
  • the upper section 15 of the valve sleeve 4 comprises, part way down its length, a groove 28 formed around its circumference, containing a second sealing ring arrangement 29 forming a seal between the upper section 15 and the manifold 3.
  • the upper section 15 of the valve sleeve 4 comprises another groove 31 formed around its circumference, containing a third sealing ring arrangement 32, forming a seal between the upper section 15 and the cover 13.
  • seals may typically be comprised of a suitable elastomer, for example, PolyUtherene.
  • a flow of liquid generally oil
  • the poppet 5 may be lifted under the pressure of fluid in the first flow channel 11 , lifting the closure element 22 away from the valve seat 7 to enable fluid to flow from the first flow channel 11 to the second flow channel 12 via the axial fluid port 20, the lateral fluid ports 21 and the annular chamber 18.
  • the poppet 5 may be lowered against the pressure of fluid in the first flow channel 1 1 , bringing the closure element 22 into sealing engagement with the valve seat 7 and preventing fluid flow from the first flow channel 1 1 to the second flow channel 12.
  • both they and the stepped manifold bores must conform to defined standards, for example, the ISO 7368 standard in the UK and elsewhere which defines allowed characteristics including lengths and diameters.
  • the height of the valve sleeve 4 matches exactly the depth of the stepped bore 2.
  • the manufacturing tolerances associated with these dimensions often results in a valve sleeve that is shorter than the stepped bore into which it is to be inserted.
  • this gap enables the valve sleeve to move up and down in response to the prevailing fluid pressure conditions in the valve/manifold system.
  • This motion varies the cavity volume between the upper section of the valve sleeve 15 and the cover 13 which is available to the sealing arrangement 32.
  • FIG. 2 to 6 there is described a two port cartridge valve 40, embodying the present invention, which is inserted in a stepped bore of a manifold 3 ⁇
  • FIG. 2 to 6 which are identical to features illustrated in Figure 1 have the same reference numerals as in Figure 1 followed by a ⁇
  • FIG. 2 to 6 An important difference between the prior art valve design shown in Figure 1 and the valve design described with respect to Figures 2 to 6 is in the sealing arrangement 41 in the groove 3 which forms a face seal between the upper section 15 x of the valve sleeve 4 " and the cover 13 ' .
  • the sealing arrangement 41 comprises an elastomeric seal 42, in this example an O-ring, which in use forms a seal between the valve insert 4 ' and the cover 13' (not shown in Figure 3), and a back up ring 43, formed from a more rigid material than that of the elastomeric seal 42, which acts to retain the elastomeric seal 42 in position in the groove 3Tto prevent its extrusion.
  • an elastomeric seal 42 in this example an O-ring, which in use forms a seal between the valve insert 4 ' and the cover 13' (not shown in Figure 3)
  • a back up ring 43 formed from a more rigid material than that of the elastomeric seal 42, which acts to retain the elastomeric seal 42 in position in the groove 3Tto prevent its extrusion.
  • Both the elastomeric seal 42 and the back up ring 43 are ring shaped and lie co-axially and concentrically in the groove 3 , with in plan view, the inner circumference of the back up ring 43 arranged around the outer circumference of the elastomeric seal 42 so that the back up ring 43 circumscribes the elastomeric seal 42.
  • the elastomeric seal 42 may therefore be thought of as an inner ring and the back up ring 43 as an outer ring of the sealing arrangement 41.
  • the back up ring 43 comprises an inner circumferential surface 44 which faces generally radially inwardly of the back up ring 43 towards the centre of the ring 43 and defines an inner circumference of the ring 43, and an outer circumferential surface 45 which faces generally radially outwardly of the back up ring 43 and defines an outer circumference of the ring 43.
  • the back up ring 43 further comprises an upper surface 46 and a lower surface 47 which is parallel with the upper surface 46. It can be seen that in cross section, the back up ring 43 appears roughly trapezoidal. When the back up ring 43 is in situ in the groove 3 , the lower surface 47 rests against the bottom surface 31 a of the groove 31 ' and the upper surface 46 faces the underside of the cover 13 ⁇
  • the inner circumferential surface 44 describes a recess 44a for receiving at least a portion of an outer facing side 48 of the elastomeric seal 42.
  • the recess 44a is substantially concave and extends substantially across the whole width of the inner circumferential surface 44 and substantially around the whole length of the inner circumferential surface 44 (i.e. around the inner circumference of the back up ring 43).
  • the shape of the recess 44a formed in the inner circumferential surface 44 complements the shape of the outer facing side 48 of the elastomeric seal 42.
  • the two shapes are the inverse of each other, so that as in case of the described preferred example where the shape of the recess 44a is concave, the outer facing side 48 of the elastomeric seal 42 is convex.
  • the inner circumferential surface 44 is thus not shaped like the internal surface of a regular cylinder, which would not curve inwardly as does surface 44 as shown in Figures 4 and 5 but instead would appear as a straight vertical line.
  • the outer circumferential surface 45 of the back up ring 43 slants inwardly of the ring 43 from the upper surface 46 to the lower surface 47.
  • the outer circumferential surface 45 has the same shape as does the side surface of a right frusto - cone having its base in the plane of the upper surface 46.
  • the outer circumferential surface 45 faces around it length an upper surface section 49 of the second bore step 8.
  • the upper surface section 49 slants inwardly from the rim of the mouth of the second bore step 8 to a depth approximately a little more than the depth of the groove 3 ⁇ .
  • the slant angle of the upper surface section 49 is very slightly less than that of the outer circumferential surface 45 so that a small wedge shaped gap 50 exists between the two.
  • this provides a space to accommodate slight tilting movements of the back up ring 43 when in use, which helps prevent the back up ring fracturing.
  • a somewhat wider gap 51 exists between an inner facing side 50 of the elastomeric seal 42 and a side wall 31b of the groove 3 .
  • the outer circumferential surface 45 thus has a different shape than the corresponding outer circumferential surfaces of conventional back up rings which surfaces are shaped like the external surface of a regular cylinder.
  • the sealing arrangement 41 forms a particularly robust and durable seal between the valve sleeve 4' and the cover 12 ⁇ This is at least in part because the arrangement of having the outer facing side 48 of the elastomeric seal 42 received in the recess defined in the inner surface 44 of the back up ring 43 helps prevent relative movement between the back up ring 43 and the elastomeric seal 42. This enhances the ability of the back up ring 43 to retain the elastomeric seal 42 in place and prevent its extrusion.
  • the back up ring 43 is arranged to compress the elastomeric seal 42 radially (e.g. generally transverse to the longitudinal axis), which helps maintain the two in close contact.
  • This may be achieved by the back up ring having a maximum internal diameter (indicated as di in Figure 5 ) which is slightly smaller than the outer diameter of the elastomeric seal 42 (as measured when the seal 42 is not under any stress) so that the elastomeric seal 42 must be compressed radially in order to fit around the inside of the back up ring.
  • the back up ring 43 compresses the outer diameter of the elastomeric seal by about 1% to 5%.
  • the elastomeric seal 42 has an inner diameter (indicated as d 2 in Figure 5) which is greater than the inner diameter of the groove 31 ' (indicated as d 3 in Figure 5) so that there is a space between the elastomeric seal 42 and the surface 31b" of the groove which can accommodate changes in the shape of the elastomeric seal 42 induced by pressure changes when the valve is in use.
  • This arrangement contrasts with known arrangements in which the inner diameter of the elastomeric seal 42 is slightly smaller than the inner diameter of the groove 31 so that the elastomeric seal 42 has to be stretched to fit into the groove and remains in tight contact with the inner side of the groove.
  • the ratio of the volume of the elastomeric seal 42 and the volume of the space available to the elastomeric seal 42 in the groove is less than a pre-determined value.
  • a pre-determined value is advantageous because we have found that if the elastomeric seal 42 occupies too much of the volume available to it in the groove 3 , in use, the forces exerted on the sealing arrangement 41 cause crimping of the back up ring 43 and/or the O-ring 42. We find in particular that such crimping is minimised if the aforementioned ratio is less than about 0.85.
  • the valve 40 is assembled such that the sealing arrangement 41 is located in the groove 3 in a pre-compressed state (i.e. the sealing arrangement is permanently under compression even when the assembled valve 40 is inactive and there is no internal fluid pressure in the valve).
  • This may be achieved by using a back up ring 43 of a length or height along its longitudinal axial direction (indicated as d 4 in Figure 5) and an elastomeric seal 42 comprising a longitudinal axial cross sectional diameter (indicated as d 5 in Figure 5) which are both greater than the perpendicular distance (indicated as d 6 in Figure 5) between the underside of the cover 13 ⁇ when fixed in place, and the bottom surface 31 a of the groove 31 ' when the insert is fully inserted into the bore.
  • the elastomeric seal 42 is pre-compressed along the longitudinal axis by 30% or less and the back up ring 43 by 20% or less.
  • the minimum thickness of the back up ring 43 along the radial direction is about equal to half the difference between the outer diameter of the back up ring 43 (indicated as d 8 in Figure 5) and the inner diameter of the back up ring 43. This minimum thickness requirement helps prevent the back up ring 43 fracturing.
  • the inner upper edge 44b, the inner lower edge 44c, the upper outer edge 45a and the lower outer edge 45b are slightly curved so as not to form sharp edges.
  • the radii of curvature of the outer upper 45a and outer lower 45b edges are (to within manufacturing tolerances) the same and are greater than the radii of curvature of the inner upper 44b and inner lower 44c edges which are (to within manufacturing tolerances) also the same.
  • the radii of curvature of the outer edges may be for example twice that of the inner edges. It is believed that the curved edges, as opposed to sharp edges enhance the lifetime of the sealing arrangement.
  • the sealing arrangement 41 is so effective that it negates the need to use shims in valves in which manufacturing tolerances have resulted in a valve sleeve that is shorter than the stepped bore. Accordingly, as can be seen by comparing Figures 1 and 2, the valve 40, unlike the valve 1, does not make use of a shim 33 and as is illustrated in Figure 4, a small gap 53 exists between the valve sleeve 3' and the cover 13 ' allowing movement of the valve 1 back and forth along the axial direction.
  • the back up ring 43 may be made out of any suitably robust material, for example a thermoplastic material such as Teflon, optionally containing a filler for example glass fibres.
  • the elastomeric seal 42 may be made from any suitable resiliently deformable material, for example Nitrile with 90 shore hardness. Many modifications or variations may be made to the described embodiment, without departing from the scope of the claims.
  • the sealing arrangement may be used as a seal, in particular a face seal, in many types of hydraulic systems not just the cartridge valve of the described embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Gasket Seals (AREA)

Abstract

La présente invention se rapporte à un agencement d'étanchéité à introduire dans une rainure d'un système hydraulique afin de former un joint entre deux surfaces du système. L'agencement d'étanchéité comprend une bague extérieure et une intérieure pouvant être agencées de façon coplanaire et concentrique dans la rainure. La bague intérieure comprend un matériau élastiquement déformable et la bague extérieure est plus rigide que la bague intérieure et sert à soutenir la bague intérieure dans la rainure. La bague extérieure comprend une surface intérieure tournée de manière sensiblement radiale vers l'intérieur de la bague extérieure et la bague intérieure comprend une surface extérieure tournée de manière sensiblement radiale vers l'extérieur de la bague intérieure. La surface intérieure de la bague extérieure décrit un évidement de surface qui accepte au moins une partie de la surface extérieure de la bague intérieure.
PCT/IB2012/000888 2011-03-04 2012-05-04 Agencement d'étanchéité, système hydraulique comprenant ce dernier et bague d'appui pour l'agencement d'étanchéité WO2012120383A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1103664.7 2011-03-04
GB1103664.7A GB2488588B (en) 2011-03-04 2011-03-04 A sealing arrangement, hydraulic system comprising the same and a back up ring for the sealing arrangement

Publications (2)

Publication Number Publication Date
WO2012120383A1 true WO2012120383A1 (fr) 2012-09-13
WO2012120383A8 WO2012120383A8 (fr) 2013-02-21

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PCT/IB2012/000888 WO2012120383A1 (fr) 2011-03-04 2012-05-04 Agencement d'étanchéité, système hydraulique comprenant ce dernier et bague d'appui pour l'agencement d'étanchéité

Country Status (2)

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WO (1) WO2012120383A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7382150B2 (ja) * 2019-03-25 2023-11-16 エドワーズ株式会社 真空ポンプ、及び、真空ポンプに用いられるシール部材

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US2002450A (en) * 1933-03-09 1935-05-21 George Mfg Company Inc Cylinder cock
US3698728A (en) * 1971-01-07 1972-10-17 Mc Donnell Douglas Corp Fluid sealing device
DE2521118A1 (de) * 1975-05-13 1976-11-25 Rokal Armaturen Gmbh Ventil-dichtung, insbesondere aus polytetrafluoraethylen
US6173965B1 (en) * 1998-12-28 2001-01-16 Leopold J. Niessen Actuator seal bearing assembly and method
US20020017327A1 (en) * 2000-07-28 2002-02-14 Shigehiro Kawaai Single seat valve apparatus
EP1197692A1 (fr) * 2000-10-13 2002-04-17 HydraForce, Inc. Distributeur piloté proportionnel
JP2007100900A (ja) * 2005-10-06 2007-04-19 Mitsubishi Cable Ind Ltd シール材
EP1832787A1 (fr) * 2004-12-28 2007-09-12 NOK Corporation Dispositif d'etancheite
US20100101666A1 (en) * 2008-10-28 2010-04-29 Gm Global Technology Operations, Inc. Pressure regulator for hydrogen storage system
WO2010098001A1 (fr) * 2009-02-24 2010-09-02 Nok株式会社 Dispositif d'étanchéité

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US4576386A (en) * 1985-01-16 1986-03-18 W. S. Shamban & Company Anti-extrusion back-up ring assembly
US4614348A (en) * 1985-10-04 1986-09-30 Aeroquip Corporation Anti-blowout seal
DE10000084A1 (de) * 2000-01-04 2001-07-05 Mueller Friedrich Stützring zur Abstützung eines O-Rings
US20040084850A1 (en) * 2002-11-04 2004-05-06 Brian Lang Annular seal
US7793944B2 (en) * 2004-12-28 2010-09-14 Nok Corporation Sealing device
CN201627914U (zh) * 2009-12-08 2010-11-10 宁波欧易液压有限公司 液压装置中两结合面之间的密封结构

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2002450A (en) * 1933-03-09 1935-05-21 George Mfg Company Inc Cylinder cock
US3698728A (en) * 1971-01-07 1972-10-17 Mc Donnell Douglas Corp Fluid sealing device
DE2521118A1 (de) * 1975-05-13 1976-11-25 Rokal Armaturen Gmbh Ventil-dichtung, insbesondere aus polytetrafluoraethylen
US6173965B1 (en) * 1998-12-28 2001-01-16 Leopold J. Niessen Actuator seal bearing assembly and method
US20020017327A1 (en) * 2000-07-28 2002-02-14 Shigehiro Kawaai Single seat valve apparatus
EP1197692A1 (fr) * 2000-10-13 2002-04-17 HydraForce, Inc. Distributeur piloté proportionnel
EP1832787A1 (fr) * 2004-12-28 2007-09-12 NOK Corporation Dispositif d'etancheite
JP2007100900A (ja) * 2005-10-06 2007-04-19 Mitsubishi Cable Ind Ltd シール材
US20100101666A1 (en) * 2008-10-28 2010-04-29 Gm Global Technology Operations, Inc. Pressure regulator for hydrogen storage system
WO2010098001A1 (fr) * 2009-02-24 2010-09-02 Nok株式会社 Dispositif d'étanchéité

Also Published As

Publication number Publication date
GB2488588A (en) 2012-09-05
GB2488588B (en) 2017-03-15
GB2549366A (en) 2017-10-18
WO2012120383A8 (fr) 2013-02-21
GB201701820D0 (en) 2017-03-22
GB2549366B (en) 2017-11-22
GB201103664D0 (en) 2011-04-13

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