WO2013177392A1 - Joint spiralé - Google Patents

Joint spiralé Download PDF

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Publication number
WO2013177392A1
WO2013177392A1 PCT/US2013/042419 US2013042419W WO2013177392A1 WO 2013177392 A1 WO2013177392 A1 WO 2013177392A1 US 2013042419 W US2013042419 W US 2013042419W WO 2013177392 A1 WO2013177392 A1 WO 2013177392A1
Authority
WO
WIPO (PCT)
Prior art keywords
metallic strip
filler material
relatively soft
less
axial width
Prior art date
Application number
PCT/US2013/042419
Other languages
English (en)
Inventor
Jose Carlos CARVALHO VEIGA
Nelson KAVANAGH
Original Assignee
Teadit N.A., Inc.
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 Teadit N.A., Inc. filed Critical Teadit N.A., Inc.
Publication of WO2013177392A1 publication Critical patent/WO2013177392A1/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
    • 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
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/12—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering
    • F16J15/121—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement
    • F16J15/125—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement generally perpendicular 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/16—Flanged joints characterised by the sealing means
    • F16L23/18—Flanged joints characterised by the sealing means the sealing means being rings

Definitions

  • the present invention relates to a spiral wound gasket used for sealing flanged joints.
  • the present invention relates to a spiral wound gasket with improved sealability having a spiral sealing element that includes a metallic strip and a relatively soft filler material, wherein the axial width of the relatively soft filler material is greater than the axial width of the metallic strip.
  • the present invention also relates to a spiral wound gasket with improved sealability having a controlled gasket density and in which the metallic strip has a uniform and symmetrical "V" or "W" cross-sectional shape.
  • BACKGROUND Spiral wound gaskets are used within many industries, including those that process liquids, gases and gaseous hydrocarbons, to seal flange joints.
  • spiral wound gaskets are shown in Fig. 1 and include a spiral sealing element 10 made of alternating layers of a metallic strip 12 and a strip of a relatively soft filler material 14 spirally wound around a central axis.
  • the construction of the spiral sealing element 10 typically begins with a base structure that includes initial windings of the metallic strip 12 for three contiguous rotations, without the addition of any relatively soft filler material 14.
  • the initial windings are spot welded together at regular intervals, typically every 76 mm along the perimeter of the metallic strip 12, to insure the integrity of the base structure.
  • the construction of the spiral sealing element 10 then introduces layers of the relatively soft filler material 14 in between each layer of the metallic strip 12.
  • the construction of the spiral sealing element 10 proceeds to the final windings of the metallic strip 12 for three contiguous rotations, without the addition of any relatively soft filler material 14, to form the outer circumference of the spiral sealing element 10. These final windings are welded together in the same manner as the initial windings described above.
  • the thickness of the metallic strip 12 used in the construction of spiral wound gaskets must be within the range of from 0.15 mm to 0.23 mm.
  • the thickness of the relatively soft filler material 14 may vary, however, at the discretion of the gasket manufacturer. Consequently, in conventional spiral wound gaskets, the relatively soft filler material 14 has a significantly larger thickness compared to the metallic strip 12, so as to reduce manufacturing costs.
  • the density defined as the number of windings of metal and filler per millimeter of gasket thickness, of such conventional spiral wound gaskets, is concomitantly reduced.
  • typical conventional spiral wound gaskets have a density ranging from about 0.80 windings per millimeter (w/mm) to about 1.35 w/mm.
  • the relatively soft filler material 14 has the same axial width as the metallic strip 12. According to the standards set forth in ASME B 16.20, the typical axial width of the metallic strip 12 and the relatively soft filler material 14 ranges from about 4.31 mm to about 4.57 mm.
  • conventional spiral wound gaskets may include an outer ring 16 assembled around the outer circumference of the spiral sealing element 10.
  • the outer ring 16 includes a groove 18 on its inner edge and the outer surface of the spiral sealing element 10 has an apex or nose 20 which fits in the groove 18.
  • the outer ring 16 helps to restrict the maximum compression of the spiral wound gasket, increases the radial strength of the gasket, and aids in centering the gasket within the bolt ring of the flange joint.
  • conventional spiral wound gaskets may also include an inner ring 22 located within the inner perimeter of the spiral sealing element 10, which helps to prevent inward extrusion of the spiral wound gasket as well as to protect the spiral sealing element 10 from contamination or turbulence from the flow of fluid through the pipe.
  • a spiral wound gasket 24 is typically placed between the flanges 26 installed on the ends of pipes 28.
  • the flanges are held together by bolts 30 spaced around the circumference of the flanges 26.
  • the bolts 30 help to center the gasket 24 placed between the flanges 26.
  • the metallic strip 12 engages with the inner faces of the flanges 26.
  • the pressure or seating stress applied through the flanges 26 axially compresses the metallic strip 12, typically down to the axial width of the outer ring 16. Additionally, the pressure or seating stress applied through the flanges 26 axially compresses and increases the density of the relatively soft filler material 14. Together, these actions create a seal between the flanges 26.
  • conventional spiral wound gaskets have an axial width of approximately 4.31 to 4.57 mm when in an uncompressed form, and are designed to be compressed axially to a width of approximately 2.97 to 3.33 mm, which is the axial width of a typical outer ring 16.
  • the gasket may reach full compression before the seating stress applied to the gasket is sufficient to provide adequate sealing. In these cases, small leaks of fluid or gas traveling through the pipes 28, called fugitive emissions, may occur.
  • ugitive emissions values for example in oil or gas transport pipes.
  • Some environmental protection organizations mandate a fugitive emissions value, with respect to the emission of volatile organic compounds, of less than 500 parts per million in volume (ppmV).
  • Other, more rigorous standards require a fugitive emissions value of less than 100 ppmV.
  • Figs. 5 and 6 show the results of fugitive emissions tests conducted with conventional spiral wound gaskets having a density of 0.869 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the metallic strip and the relatively soft filler material have the same axial width and the metallic strip has a uniform and symmetrical "V" cross-sectional shape.
  • the fugitive emissions tests were conducted by measuring the leakage of methane gas using a Thermo Fisher Scientific Inc. model TVA- 1000 toxic vapor analyzer. Figs.
  • Fig. 7 shows the results of fugitive emissions tests conducted with conventional spiral wound gaskets having densities of 0.869 w/mm, 0.994 w/mm and 1.132 w/mm, in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the metallic strip and the relatively soft filler material have the same axial width and the metallic strip has a uniform and symmetrical "V" cross-sectional shape.
  • the fugitive emissions tests were conducted by measuring the leakage of methane gas using a Thermo Fisher Scientific Inc. model TVA-1000 toxic vapor analyzer.
  • Fig. 7 clearly demonstrates that at a particular seating stress, the lower the density, the greater the leakage.
  • the low density of conventional spiral wound gaskets allows the sealing surfaces 32 of the flanges 26 to come into contact with the outer ring 16 under pressure.
  • the sealing surfaces 32 of the flanges contact the outer ring 16, the sealing surfaces 32 of the flanges 26 rotate, which reduces the seating stress applied to the inner diameter area 34 of the spiral wound gasket, thereby reducing the sealing capability of the spiral wound gasket.
  • Figure 1 illustrates a cross-sectional view of a conventional spiral wound gasket.
  • Figure 2 illustrates a cross-sectional view of a conventional spiral wound gasket demonstrating that the width of the relatively soft filler material is the same as the width of the metallic strips.
  • Figure 3 illustrates a section of a pipe with a conventional spiral wound gasket placed between two unjoined flanges.
  • Figure 4 illustrates a pipe section in which two pipes, each with a corresponding flange are joined together by bolts.
  • Figure 5 illustrates leakage and seating stress measurements of a typical low density conventional spiral wound gasket in which the metallic strip has an axial width that is greater than the axial width of the guide ring, and the metallic strip and the relatively soft filler material have the same axial width under a range of pressures.
  • Figure 6 illustrates leakage and seating stress measurements of a conventional low density spiral wound gasket in which the metallic strip has an axial width that is greater than the axial width of the guide ring, and the metallic strip and the relatively soft filler material have the same axial width.
  • Figure 7 illustrates leakage and seating stress measurements of various conventional low density spiral wound gaskets in which the metallic strip has an axial width that is greater than the axial width of the guide ring, and the metallic strip and the relatively soft filler material have the same axial width.
  • Figure 8 illustrates a section of a conventional spiral wound gasket engaged with two flanges, wherein the sealing surfaces of the flanges are in contact with the outer ring of the gasket.
  • Figure 9 illustrates a cross-sectional view of a spiral wound gasket according to the present invention in which the axial width of the metallic strip is greater than the axial width of the guide ring and the axial width of the relatively soft filler material is greater than the axial width of the metallic strip.
  • Figure 10 illustrates a spiral wound gasket according to the present invention.
  • Figure 11 illustrates a cross-sectional view of a spiral wound gasket according to the present invention.
  • Figure 12 illustrates an exploded view of a spiral wound gasket according to the present invention.
  • Figure 13 illustrates comparative leakage and seating stress measurements of a conventional low density spiral wound gasket in which the axial width of the metallic strip is greater than the axial width of the guide ring and the relatively soft filler material has the same axial width as the metallic strip, and a spiral wound gasket according to the present invention in which the axial width of the metallic strip is greater than the axial width of the guide ring and the axial width of the relatively soft filler material is greater than the axial width of the metallic strip.
  • Figure 14 illustrates comparative leakage and seating stress measurements of a conventional low density spiral wound gasket in which the axial width of the metallic strip is greater than the axial width of the guide ring and the relatively soft filler material has the same axial width as the metallic strip, and low density spiral wound gaskets in which the axial width of the metallic strip is greater than the axial width of the guide ring and the axial width of the relatively soft filler material is greater than the axial width of the metallic strip.
  • Figure 15 illustrates comparative leakage and seating stress measurements of spiral wound gaskets of various densities according to the present invention in which the axial width of the metallic strip is greater than the axial width of the guide ring and the axial width of the relatively soft filler material is greater than the axial width of the metallic strip.
  • the apparatus of the present invention provides a spiral wound gasket with improved sealing capabilities for use in the sealing of flange joints.
  • a spiral sealing element 40 is constructed using the conventional winding procedure described above.
  • the spiral sealing element 40 includes a metallic strip 42 and a relatively soft filler material 44.
  • the metallic strip 42 has a thickness of from about 0.15 mm to about 0.23 mm.
  • the metallic strip 42 and the relatively soft filler material 44 have a "V" or "W” shape, as shown in Fig. 9, which facilitates axial compression of the spiral sealing element 40 under pressure.
  • the "V" or "W” shape of the metallic strip 42 is uniform and symmetrical.
  • the metallic strip 42 used in the construction of the spiral sealing element 40 is made of at least one of any number of suitable metals known by those of ordinary skill in the art, including carbon-rich or stainless steel, titanium, nickel, or nickel alloy.
  • the relatively soft filler material 44 used in the construction of the spiral sealing element 40 is made of any of a number of relatively soft filler materials known by those of ordinary skill in the art that are capable of deforming when the spiral wound gasket is compressed between the pipe flanges that define the flange joint, including, for example, fluorocarbon resin, such as polytetrafluoroethylene (“PTFE”), graphite, including exfoliated graphite, flexible graphite and oxidation inhibited graphite, ceramics, and aluminum.
  • fluorocarbon resin such as polytetrafluoroethylene (“PTFE”)
  • graphite including exfoliated graphite, flexible graphite and oxidation inhibited graphite, ceramics, and aluminum.
  • the choice of the particular type of metal or relatively soft filler material used depends on the environment in which the spiral wound gasket according to the present invention is to be used. According to some embodiments of the present invention, the spiral wound gasket may be used in environments having operating temperatures of up to 850° F.
  • the spiral wound gasket includes an outer ring 50 assembled around the outer circumference of the spiral sealing element 40.
  • the outer ring 50 may be in the form of a metal annulus, and may be made of at least one suitable material known by those of ordinary skill in the art, such as carbon-rich or stainless steel, titanium, nickel, or nickel alloy.
  • the outer ring 50 includes a groove 52 on its inner edge and the outer surface of the spiral sealing element 40 has an apex or nose 54 that fits within the groove 52.
  • the outer ring 50 has an axial width of from about 2.97 mm to about 3.33 mm.
  • the spiral wound gasket includes an inner ring 60 located within the inner perimeter of the spiral sealing element 40.
  • the inner ring 60 may be in the form of a metal annulus, and may be made of at least one suitable material known by those of ordinary skill in the art, such as carbon-rich or stainless steel, titanium, nickel, or nickel alloy.
  • the metallic strip protrudes axially beyond the outer ring 50 and the inner ring 60, and, the relatively soft filler material 44 protrudes axially beyond the metallic strip 42 on either or both sides of the spiral sealing element 40.
  • the axial protrusion of the relatively soft filler material 44 allows the compressible relatively soft filler material 44 to come in contact with the flanges of the pipes to be sealed before the metallic strip 42 as seating stress is applied. This allows the relatively soft filler material 44 to fill in any irregularities on the faces of the flanges, thereby improving the sealing capabilities of the spiral wound gasket.
  • the axial width of the relatively soft filler material 44 can be chosen based on the environment in which the spiral wound gasket including the relatively soft filler material 44 is to be used and any applicable environmental regulations.
  • Fig. 13 shows the results of fugitive emissions tests conducted with a conventional spiral wound gasket having a density of 0.818 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the metallic strip and the relatively soft filler material have the same axial width and the metallic strip has a uniform and symmetrical "V" cross-sectional shape, and a spiral wound gasket according to the present invention having a density of 1.615 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes for a distance of between 0.2 mm and 1.0 mm from both sides of the metallic strip, and the metallic strip has a uniform and symmetrical "V" cross-sectional shape.
  • Fig. 13 clearly demonstrates that the spiral wound gasket according to the present invention exhibits improved fugitive emission values as compared to the conventional low density spiral wound gasket in which the relatively soft filler material has the same axial width as the metallic strip.
  • the spiral wound gasket according to the present invention exhibits a fugitive emissions value of less than 10 ppmV of methane gas at a seating stress of as low as 40 MPa, whereas the conventional spiral wound gasket requires a seating stress of at least 190 MPa to achieve such a low fugitive emissions value.
  • Fig. 14 shows the results of fugitive emissions tests conducted with a conventional spiral wound gasket having a density of 0.818 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the metallic strip and the relatively soft filler material have the same axial width and the metallic strip has a uniform and symmetrical "V" cross-sectional shape, and spiral wound gaskets having a density of 0.994 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes for a distance of about 0.4 mm or about 0.8 mm from both sides of the metallic strip, and the metallic strip has a uniform and symmetrical "V" cross-sectional shape.
  • a low density spiral wound gasket in which the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes axially from both sides of the metallic strip for a distance about 0.4 mm yields fugitive emissions values of less than 100 ppmV of methane gas at a seating stress of approximately 50 MPa and less than 10 ppmV of methane gas at a seating stress of approximately 105 MPa. Also as shown in Fig.
  • a low density spiral wound gasket in which the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes axially from both sides of the metallic strip for a distance about 0.8 mm yields fugitive emissions values of less than 100 ppmV of methane gas at a seating stress of approximately 100 MPa and less than 10 ppmV of methane gas at a seating stress of approximately 145 MPa.
  • the axial width of the relatively soft filler material 44 used in certain embodiments of the present invention can be adjusted to account for the maximum seating stress allowed for the particular flanges used and the surrounding environment.
  • the relatively soft filler material 44 protrudes axially from the metallic strip 42 by a distance of at least 0.2 mm on either or both sides of the spiral sealing element 40.
  • the relatively soft filler material 44 protrudes axially from the metallic strip 42 by a distance of at least 0.3 mm on either or both sides of the spiral sealing element 40.
  • the relatively soft filler material 44 protrudes axially from the metallic strip 42 by a distance of from about 0.2 mm to less than about 1.0 mm on either or both sides of the spiral sealing element 40.
  • the relatively soft filler material 44 protrudes axially from the metallic strip 42 by a distance of from about 0.3 mm to less than about 1.0 mm on either or both sides of the spiral sealing element 40. According to another embodiment, the relatively soft filler material 44 protrudes axially from the metallic strip 42 by a distance of from about 0.4 mm to about 0.8 mm on either or both sides of the spiral sealing element 40.
  • the gasket has a density of from about 1.4 w/mm to about 1.90 w/mm. Such a gasket density renders the gasket strong enough to withstand the required seating stresses such that the surface of the flanges do not contact the outer ring 50.
  • Fig. 15 shows the results of fugitive emissions tests conducted with spiral wound gaskets according to the present invention having densities of 1.491 w/mm, 1.509 w/mm and 1.863 w/mm in which the metallic strip has an axial width that is greater than the axial width of the guide ring, the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes from the metallic strip by a distance of from more than 0.2 mm up to 1.0 mm, and the metallic strip has a uniform and symmetrical "V" cross-sectional shape.
  • the fugitive emissions tests were conducted by measuring the leakage of methane gas using a Thermo Fisher Scientific Inc. model TVA-1000 toxic vapor analyzer. Fig.
  • spiral wound gaskets manufactured in accordance with the present invention having densities of 1.491 w/mm, 1.509 w/mm and 1.863 w/mm, in which the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes from the metallic strip by a distance of from more than 0.2 mm up to 1.0 mm, yield fugitive emissions values of about 10 ppmV of methane gas at seating stresses below 100 MPa and fugitive emissions values of less than 30 ppmV of methane gas at seating stresses below 50 MPa.
  • the relatively soft filler material has an axial width that is greater than the axial width of the metallic strip and protrudes from the metallic strip by a distance of from more than 0.2 mm up to 1.0 mm
  • a spiral wound gasket according to the present invention with a density of 1.491 w/mm yields a fugitive emissions value of about 10 ppmV of methane gas or less at a seating stress of about 100 MPa or less.
  • a spiral wound gasket according to the present invention with a density of 1.509 w/mm yields a fugitive emissions value of about 10 ppmV of methane gas or less at a seating stress of about 50 MPa or less.
  • a spiral wound gasket according to the present invention with a density of 1.863 w/mm yields a fugitive emissions value of about 5 ppmV of methane gas or less at a seating stress of about 50 MPa or less.
  • the spiral wound gasket of the present invention yields a fugitive emissions value of less than 10 ppmV of methane gas at a seating stress of less than 50 MPa. In other embodiments, the spiral wound gasket of the present invention yields a fugitive emissions value of less than 100 ppmV of methane gas at a seating stress of less than 100 MPa. In yet other embodiments, the spiral wound gasket of the present invention yields a fugitive emissions value of less than 30 ppmV of methane gas at a seating stress of less than 50 MPa.
  • the spiral wound gasket has a circular shape. In other embodiments, the spiral wound gasket has an oval shape. In still other embodiments, the spiral wound gasket has any suitable shape known by those of ordinary skill in the art.
  • the elements and teachings of the various illustrative exemplary embodiments may be combined in whole or in part in some or all of the illustrative exemplary embodiments.
  • one or more of the elements and teachings of the various illustrative exemplary embodiments may be omitted, at least in part, and/or combined, at least in part, with one or more of the other elements and teachings of the various illustrative embodiments.
  • any spatial references such as, for example, “upper,” “lower,” “above,” “below,” “between,” “bottom,” “vertical,” “horizontal,” “angular,” “upwards,” “downwards,” “side-to- side,” “left-to-right,” “left,” “right,” “right-to -left,” “top-to-bottom,” “bottom-to-top,” “top,” “bottom,” “bottom-up,” “top-down,” etc., are for the purpose of illustration only and do not limit the specific orientation or location of the structure described above.
  • steps, processes, and procedures are described as appearing as distinct acts, one or more of the steps, one or more of the processes, and/or one or more of the procedures may also be performed in different orders, simultaneously and/or sequentially.
  • the steps, processes and/or procedures may be merged into one or more steps, processes and/or procedures.
  • one or more of the operational steps in each embodiment may be omitted.
  • some features of the present disclosure may be employed without a corresponding use of the other features.
  • one or more of the above-described embodiments and/or variations may be combined in whole or in part with any one or more of the other above-described embodiments and/or variations.

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

Abstract

L'invention concerne un joint spiralé pour fermer hermétiquement des joints à bride. Le joint spiralé a une capacité d'étanchéité améliorée ayant un élément d'étanchéité en spirale (40), qui comprend une bande métallique (42) et un matériau de remplissage relativement souple (44), la largeur axiale du matériau de remplissage relativement souple (44) étant supérieure à la largeur axiale de la bande métallique (42). Le joint spiralé a également une capacité d'étanchéité améliorée ayant une densité de joint commandée et dans lequel la bande métallique (42) a une forme transversale en « V » ou « W » uniforme et symétrique.
PCT/US2013/042419 2012-05-23 2013-05-23 Joint spiralé WO2013177392A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
BR2020120123113 2012-05-23
BR202012012311-3U BR202012012311Y1 (pt) 2012-05-23 2012-05-23 disposição introduzida em junta de vedação
US201261678446P 2012-08-01 2012-08-01
US61/678,446 2012-08-01

Publications (1)

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WO2013177392A1 true WO2013177392A1 (fr) 2013-11-28

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Application Number Title Priority Date Filing Date
PCT/US2013/042419 WO2013177392A1 (fr) 2012-05-23 2013-05-23 Joint spiralé

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BR (1) BR202012012311Y1 (fr)
WO (1) WO2013177392A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2516931B (en) * 2013-08-07 2019-12-25 Intelligent Energy Ltd Interface seal for a fuel cartridge
EP3839298A4 (fr) * 2018-08-16 2022-04-27 Nippon Pillar Packing Co., Ltd. Joint spiralé

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3132870A (en) * 1962-12-14 1964-05-12 Karl J Pschera Gaskets and method of making same
US5527047A (en) * 1992-07-20 1996-06-18 W. L. Gore & Associates, Inc. Fire safe spiral wound gasket with expanded PTFE and graphite windings
US20090115139A1 (en) * 2007-11-02 2009-05-07 Jenkins Willie A Spiral-wound gasket

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3132870A (en) * 1962-12-14 1964-05-12 Karl J Pschera Gaskets and method of making same
US5527047A (en) * 1992-07-20 1996-06-18 W. L. Gore & Associates, Inc. Fire safe spiral wound gasket with expanded PTFE and graphite windings
US20090115139A1 (en) * 2007-11-02 2009-05-07 Jenkins Willie A Spiral-wound gasket

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
VEIGA.: "Setting The Standards to be Leak Free.", May 2011 (2011-05-01), Retrieved from the Internet <URL:http://www.teadit.com.br/new/geral/ISA-LDAR-2012.pdf> [retrieved on 20131001] *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2516931B (en) * 2013-08-07 2019-12-25 Intelligent Energy Ltd Interface seal for a fuel cartridge
EP3839298A4 (fr) * 2018-08-16 2022-04-27 Nippon Pillar Packing Co., Ltd. Joint spiralé

Also Published As

Publication number Publication date
BR202012012311Y1 (pt) 2018-12-11
BR202012012311U2 (pt) 2014-10-21

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