US20070024007A1 - Seal ring and method - Google Patents

Seal ring and method Download PDF

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Publication number
US20070024007A1
US20070024007A1 US11/191,888 US19188805A US2007024007A1 US 20070024007 A1 US20070024007 A1 US 20070024007A1 US 19188805 A US19188805 A US 19188805A US 2007024007 A1 US2007024007 A1 US 2007024007A1
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US
United States
Prior art keywords
members
seal
seal ring
seal body
flexible flange
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
US11/191,888
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English (en)
Inventor
Samuel Putch
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to US11/191,888 priority Critical patent/US20070024007A1/en
Priority to PCT/US2006/028609 priority patent/WO2007016021A2/fr
Priority to CA2616361A priority patent/CA2616361C/fr
Priority to GB0801262A priority patent/GB2441731B/en
Publication of US20070024007A1 publication Critical patent/US20070024007A1/en
Priority to US11/789,184 priority patent/US7703773B2/en
Priority to US11/810,033 priority patent/US7624991B2/en
Priority to US12/685,065 priority patent/US20100127461A1/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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L17/00—Joints with packing adapted to sealing by fluid pressure
    • F16L17/06—Joints with packing adapted to sealing by fluid pressure with sealing rings arranged between the end surfaces of the pipes or flanges or arranged in recesses in the pipe ends or flanges
    • 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
    • F16J15/0881—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by plastic deformation 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L17/00—Joints with packing adapted to sealing by fluid pressure
    • F16L17/06—Joints with packing adapted to sealing by fluid pressure with sealing rings arranged between the end surfaces of the pipes or flanges or arranged in recesses in the pipe ends or flanges
    • F16L17/08—Metal sealing rings
    • 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
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/40—Application of doors, windows, wings or fittings thereof for gates
    • E05Y2900/402—Application of doors, windows, wings or fittings thereof for gates for cantilever gates

Definitions

  • This invention relates to seal rings of a type for sealing between first and second members each having a throughbore, such as flanges, clamps, and hub type connectors. More particularly, this invention relates to a seal ring which is pressure energized within the groove receiving the sealing ring, thereby maintaining sealing integrity even if the securing bolts between the first and second members elongate to permit flange separation.
  • Pressure vessels are conventionally composed of structural sections having flanges or other connectors at their extreme ends.
  • the flanges are secured to the assembly by securing bolts that extend through the mating flanges.
  • the opposed flanges may be drawn together about a metal sealing ring with sufficient force to cause metal-to-metal sealing between surfaces on the seal ring and tapered surfaces on the opposing seal grooves in the first and second members.
  • An API seal ring may leak under circumstances where the bolts are properly tightened to secure the flanges in sealed engagement, but thereafter excessive heat causes bolt extension such that the flanges are allowed to be moved apart a slight amount. When this occurs, there may be insufficient mechanical force between the seal ring and the mating wall surfaces of the seal groove to maintain a fluid tight seal. Also, when the flange bolts are made up very tightly, metal coining between the seal ring and the mating wall surfaces may occur, in which case only a slight movement of the flanges may cause seal leakage. Coining of the seal ring typically occurs, because the seal ring metal is less hard than the metal defining the receiving grooves in the flange. Overstressing the studs to shut off a leak may also cause coining of the seal ring groove. It is frequently recommended to employ periodic tightening of flange bolts to prevent leaking in high temperature applications.
  • U.S. Pat. No. 4,410,186 discloses a seal ring for flanged joints, and was part of a seal concept for nuclear reactor applications. Due to wide tolerances, an API seal ring groove would be coined by this type of seal ring. To eliminate coining, one would have to make several sizes of a seal ring for a specific ring groove. This type of seal ring also would not seem suitable for holding pressures at high temperatures when the studs elongate because of its limited flexibility.
  • U.S. Pat. No. 5,058,906 discloses a seal ring formed from a high strength material. For the seal ring to function, the ring flexes against the ring groove wall to burnish and form a seal. The seal ring is intended to flex within its elastic limits, and again would require numerous different seal rings to work satisfactorily within a single API ring groove.
  • U.S. Pat. No. 5,240,263 discloses a seal ring with a substantial uniform cross sectional thickness.
  • the patent teaches substantially planar contact between surfaces of the seal ring and the tapered surfaces defining the seal groove. This type of seal may leak because there is no pressure energization. Because the seal areas are large, pressure can migrate into the seal area thus equalizing pressure, resulting in leakage.
  • a seal ring for sealing between first and second members each having an outer groove surface and an inner groove surface includes a metal seal body for engagement with each of the radially outward surfaces on the first and second members when the securing members secure the first member to the second member.
  • a metal flexible flange radially inward of the seal body has a cantilevered end which provides substantially line contact sealing engagement with a respective inner groove surface, while a spacing or gap between the flexible flange and the seal body provides for fluid pressure energization of the flexible flange. The flexible flange is deformed beyond its elastic range when the securing members secure the first member to the second member.
  • the seal ring includes a metal flexible flange supported on the seal body and extending radially inward such that a cantilevered end of a flexible flange provides substantially line contact engagement with one of a groove base surface and an inner groove surface on the respective first or second member.
  • the flexible flange is deformed beyond its elastic limit when the securing members secure the first member to the second member, and a spacing or gap between the flexible flange and the seal body provides for fluid pressure energization of the flexible flange.
  • the seal ring as disclosed herein is able to maintain dynamic sealing integrity even in the event of a fire. Due to plastic yielding and/or telescoping, the shape of the seal is able to change while maintaining high sealing reliability.
  • FIG. 1 illustrates a side view of a seal ring according to the present invention for sealing between first and second members.
  • FIG. 2 illustrates in greater detail a cross section of the seal ring shown in FIG. 1 .
  • FIG. 3A discloses an alternate embodiment of a seal ring
  • FIG. 3B discloses a seal ring as shown in FIG. 3A when the securing members have secured the first member to the second member.
  • FIG. 4 discloses yet another embodiment of a seal ring wherein the flexible flanges are slidably movable relative to the seal body.
  • FIG. 5 discloses yet another embodiment of a seal ring.
  • FIG. 6 and 7 disclose additional embodiments of a seal ring.
  • FIG. 8 discloses an embodiment of a seal ring with a radially extending flexible flange.
  • FIG. 9 discloses a flexible flange slidably movable relative to a seal body.
  • FIGS. 10A and 10B illustrate yet another embodiment of a seal ring wherein a pair of flexible flanges are shown in FIG. 10A supported on a seal ring before the securing members are tightened, and FIG. 10B illustrates the same sealing ring with the securing members tightened.
  • FIG. 11A depicts yet another embodiment of a seal ring prior to the member being secured to the second member, and FIG. 11B shows the same seal ring with the first and second members secured.
  • FIG. 1 illustrates a seal ring 10 for sealing between first and second members 12 , 14 each having a respective throughbore 13 , 15 .
  • Each member 12 , 14 has an outer tapered groove surface 16 directed radially inward in a direction away from an interface between the members 12 , 14 , and an inner tapered groove surface 18 directed radially outward in a direction away from the interface between members 12 and 14 .
  • a groove base 20 is shown spaced between the surfaces 16 , 18 , and is substantially perpendicular to a common axis 22 of the throughbores.
  • a plurality of securing members 24 such as bolt and nut assemblies, are arranged circumferentially about the members 12 , 14 and secure the first member to the second member.
  • clamping devices or other types of flange connecting members may be used to rigidly secure the first member to a flange end of a second member.
  • An annular groove formed by the surfaces 16 , 18 , 20 is thus provided for receiving the sealing ring 10 therein.
  • the sealing ring 10 comprises a metal seal body 26 for engagement with the radially outer surface 16 on the first and second members when the securing members 24 secure the first member to the second member.
  • An annular flange 28 may be pressed on or otherwise secured to the seal body 26 , and is compressed between the surface 25 on the body 12 and surface 27 on the body 14 when the bolts 24 are tightened.
  • the sealing ring 10 further includes a pair of metal flexible flanges 30 , 32 each radially inward of the seal body 26 , such that a cantilevered end 31 , 33 of each flexible flange provides substantially line contact sealing engagement with the inner tapered surface 18 on a respective first and second member 12 , 14 .
  • a spacing 34 , 36 between each flexible flange and the seal body 26 provides for fluid pressure energization of the flexible flange.
  • the cantilevered or tip end 31 , 33 of each flange is thus forced radially inward into tighter sealing engagement with a respective surface 18 in response to high pressure fluid in the bore of the members 12 , 14 .
  • the seal body 26 and the flexible flanges 30 , 32 are formed from a unitary homogeneous material.
  • the annular flange 28 and the seal body 26 may be formed from a unitary homogeneous material.
  • the seal body 26 and the pair of flanges 30 , 32 as shown in FIG. 2 form a substantially C-shaped cross-sectional configuration, as shown in FIGS. 1 and 2 .
  • FIG. 2 depicts in dashed lines the “as manufactured” configuration of the seal body and flexible flanges, and illustrates in solid lines the final position of the seal body and flexible flanges after the bolts have been tightened and before high pressure is applied to the seal ring 10 .
  • the mismatched surfaces on the seal body may be pressed outward into substantially planar engagement with the groove surfaces 26 on the first and second members, since the seal body deforms slightly in response to this high fluid pressure.
  • the seal between these components is effectively provided by line contact engagement, since even under high pressure, substantially higher sealing forces are exerted at point 38 than at other points along the radially outer surface 27 of the seal body.
  • substantially line contact metal-to-metal sealing is achieved at point 38 .
  • Sealing effectiveness of the seal ring is not solely dependent upon bolt loading, since the flexible flange of the seal ring is also pressure energized. Also, the surface on the first and second member which is sealingly engaged by a metal flexible flange preferably is not coined.
  • the seal ring changes its shape to maintain seal integrity when opposing seal grooves move apart due to temperature changes or changes in the seal ring due to flexure or yielding, or by telescoping of the seal ring, as explained further below.
  • the flanges may move axially apart 0.025 inches or greater, yet seal integrity may be maintained at a high pressure.
  • the seal maintains an effectiveness during flange separation, and is interchangeable with standard API and/or ANSI seal rings.
  • the installed flexible flange tip makes sealing contact with a wall of the groove, while a corner of the OD of the seal ring and/or an annular sealing bump on the OD of the seal ring contacts the outside groove wall.
  • the flexible flange is flexed outwardly while the OD of the seal ring is flexed inward, resulting in strengthened self-energization of the seal ring.
  • an additional fluid pressure generated force is created on the flexible flange, while simultaneously an outward force is created on the seal body.
  • FIG. 3A depicts an alternate seal body 42 and a pair of metal flexible flanges 44 and 46 with a spacing 48 , 50 provided between each flexible flange and the seal body 42 .
  • the seal body as shown in FIG. 3A does not include a annular flange, and accordingly the surface 25 on the member 12 directly engages the surface 27 on the member 14 when the bolts are tightened, as shown in FIG. 3B .
  • FIG. 3B also depicts each flexible flange 44 , 46 in substantially line contact sealing engagement with the base surface 20 at point 45 on the cantilevered end of flanges 44 and 46 .
  • the configuration of the seal body and flexible flanges in its “as manufactured” condition is shown in dashed lines in FIG. 3B , and is shown in solid lines in its position when the bolts are tightened.
  • Other seal configurations discussed below also show the “as manufactured” and “final” position, although only the final position is shown in some figures. All seal configurations are, however, deflected before obtaining the final configuration.
  • the end surface 45 forming a substantially line contact seal is thus similar to the end surface 31 shown in FIG. 2 , except that sealing engagement in the FIG.
  • 3B embodiment is with the base surface 20 rather than the inner groove surface 18 .
  • a mismatch between the angle of the surface 16 and the radially outward angled surfaces 43 on the seal body 42 are depicted, with the body thus being configured for substantially line contact sealing engagement with each of the annular flanges.
  • the seal body 52 is provided with an annular flange 28 .
  • a mismatch between the outer surface 53 on body 52 and the tapered outer groove surface 16 results in line contact sealing engagement with the members 12 , 14 at sealing point 38 .
  • a pair of metal flexible flanges 54 and 56 provide a line contact seal with the surfaces 18 on the first and second members at point 31 , while spacing 55 , 57 between the metal flexible flanges 54 , 56 and the seal body 52 , and in this case between the flexible flanges 54 , 56 and the flange supporting component 58 of each flexible flange, provides fluid pressure energization of the flexible flange.
  • the flange component 58 is slidable in a generally axial direction relative to the seal body 52 , and the surfaces 59 on the flanges 54 , 56 engage the base surface 20 of the groove in response to high fluid pressure, as shown. Again, the flexible flange is deformed beyond its elastic range when the securing member secure the first member to the second member. Sealing between 58 and 52 is accomplished by tapering one of the surfaces on 58 or 52 which engage the other component, and/or by providing an annular bump or protrusion on one of these surfaces.
  • FIG. 5 depicts yet another embodiment of a seal ring, wherein the seal body 60 is unitary and homogeneous with the annular flange 28 .
  • the seal body supports flexible end flanges 62 and 64 each open to fluid pressure energization by a respective gap 66 provided between the surface 18 and the body 60 .
  • Spacings 63 , 65 provide for fluid pressure energization of the flexible flanges 62 and 64 .
  • Additional slots 67 , 68 and 69 are provided for increasing the flexibility of the end flanges 62 , 64 , with slots 67 and 69 being directed substantially radially inward, and the slot 68 being directed substantially radially outward.
  • the seal ring 60 seals at point 38 with the surface 16 as previously explained, and the cantilevered end 31 of each flange member 62 , 64 thereby obtains substantially line contact sealing engagement with the surface 18 .
  • FIG. 6 depicts another embodiment on a metal seal body 70 having a radially outward flange 28 secured thereto.
  • the seal body is intended for substantially line contact sealing engagement with the radially outward surface of each member 12 , 14 , and accordingly annular bump 72 is provided on the member 12 for substantially line contact sealing engagement with the seal body 70 , while the mismatch of the angles between the outer surface of the seal body and the radially outward groove wall 16 also may or may not provide line contact sealing at point 73 .
  • a sealing bump 74 may be provided on the seal body, as shown in FIG. 6 .
  • a pair of metal flexible flanges 76 and 78 are each configured for substantially line contact sealing engagement with the radially inward tapered surface of the members 12 , 14 at point 31 .
  • a spacing 77 , 79 is provided between each flexible flange and the seal body for fluid pressure energization of the flexible flanges.
  • Each of the flexible flanges 76 , 78 is deformed beyond its elastic limit when the securing members secure the first member to the second member.
  • FIG. 7 illustrates an alternative seal body 80 which is integral with the radially outward flange 28 .
  • Line contact sealing engagement with the member 12 is provided by the annular bump 82 on the seal body, and by the mismatch surfaces which may result in line contact sealing at point 84 .
  • FIG. 7 also depicts a bump 86 provided on the lower member 14 for line contact sealing engagement with the seal body.
  • the pair of flexible flanges 88 and 90 include respective spacings 89 and 91 for fluid pressure energization of the flexible flanges. Each flange 88 , 90 is thus pressure energized, and provides a substantially line contact seal with the groove surface 18 at point 31 .
  • one of the bumps on the seal body or on the member 12 , 14 , or one of the line contact seals 84 created by angular mismatch, may be eliminated, since both a primary and a backup seal with each member 12 , 14 is shown in FIGS. 6 and 7 .
  • FIG. 8 depicts yet another seal body 92 having a flange 28 secured thereto, with the seal body 92 supporting a pair of flexible flanges 94 and 96 each configured for substantially line contact sealing engagement at 31 with the radially inner wall 18 of each body 12 , 14 .
  • a substantially radially extending gap 95 and 97 is provided between and flexible flange and the seal body for fluid pressure energization of each flexible flange.
  • FIG. 9 depicts an alternative seal body 110 having a radially outward flange 28 secured thereto.
  • flange 114 is provided on the seal body for substantially line contact sealing engagement at 31 with the tapered surface 18 on the lower member 14 , with a groove 115 provided between the flexible flange 114 and the body 110 .
  • a flange 112 is provided on flange support 116 , which is slidable in a substantially radial direction relative to the body 110 .
  • a bump 118 on the flange support 116 provides substantially line contact sealing engagement with the body 110 , while the mismatch between the outer surface of the support 116 and the inner surface of the body 110 provides for substantially line contact sealing engagement at 120 .
  • Spacing 113 provides for fluid energization of the flexible flange 112 .
  • the body 110 also seals with the members 12 , 14 by line contact sealing of mismatched angular surfaces, as previously discussed. Increased flexibility is provided since flange 112 is axially movable relative to body 110 .
  • FIG. 10A depicts yet another embodiment of a seal ring including a metal seal body 122 having a flange 28 integral therewith.
  • An annular bump 124 on the seal body is provided for sealing engagement with the radially outward surface 126 of each member 12 , 14 .
  • a pair of metal flexible flanges 128 each include a support member 130 for slidable engagement with the inner wall 132 of the body 122 , and an annular bead or raised section 134 is provided for substantially line contact sealing engagement with the metal seal body.
  • Each flange 128 includes an annular bead 136 for substantially line contact sealing engagement with the inner wall 138 of the groove. Shown in FIG.
  • the seal ring seals with each member 12 , 14 by substantially line contact sealing engagement with radially inward groove surface 138 at point 136 between the metal flexible flange and a respective member, by the seal 134 provided between each flange support member 130 and the metal seal body 122 , and by annular bead 124 provided between the metal seal body and the radially outward groove wall 126 of the members 12 , 14 .
  • the spacing 127 between each flexible flange 128 and a respective support member 130 provides for fluid pressure energization of the flexible flange.
  • Each flexible flange is axially movable relative to the body 122 , so that axial variations between the base surfaces 20 of the ring groove do not have a significant adverse effect on sealing effectiveness.
  • FIG. 11A discloses another embodiment, wherein the seal body 140 has a flange 28 integral and homogeneous therewith.
  • a mismatch between the outer surfaces on the flange body and the outer tapered groove surfaces 16 on the members 12 , 14 provides for substantially line contact sealing engagement between the seal body and the members at point 142 , as shown in FIG. 11B .
  • Surfaces 141 on body 140 may be tapered to facilitate sliding the base piece 143 on the seal body 140 .
  • Each seal body also includes a pair of flexible flanges 144 and 146 each in contact with an insert body 148 . When assembled, line contact sealing engagement at point 31 is formed between each flange 144 , 166 and the respective body 12 , 14 .
  • Protrusion 145 on each base piece 143 forms a line contact seal with surface 141 on seal body 140 .
  • the spacing 147 between flexible flanges 144 and 146 and the sliding base piece 143 is preferably filled with a compressible material, as shown in FIG. 11A , such as an elastomer, a high temperature graphite, TeflonTM, or a plastic.
  • Base piece 145 may be formed from metal, but alternatively may be a plastic material component. When the bolts are tightened, the insert 148 is compressed, resulting in the seal body shown in FIG. 11B .
  • comparatively low preloading may be used to form an effective seal between the groove surfaces of the ANSI or API flange and the seal ring.
  • An API or ANSI flange joint may have mismatched members, and the seal ring groove surface diameters may vary by ⁇ 0.032 or more.
  • the seal ring may be pressure energized by the internal pressure within the first and second members to maintain an effective seal.
  • An API or ANSI seal ring material may have a yield strength of 30,000 pounds or less. The seal ring will thus only stretch 0.001 inches or less per inch of diameter. If the yield strength of the seal ring gasket is increased to 60,000 psi or greater, the seal ring as well as the groove walls may be permanently deformed. The seal ring is sufficiently flexible that the internal pressure will flex the seal ring and make it yield under applications of use, such as flange separation at high temperature.
  • One seal ring may be made to fit one size groove without a problem because of a flexure, yielding, and telescoping capabilities of the seal ring, without the sealing surface being coined and preferably only burnished at the point of sealing contact.
  • the seal ring is highly interchangeable since the seal ring fits into a standard API and/or ANSI seal ring groove.
  • the features of the seal ring are realized when the flange joint is assembled according to recommended practices.
  • flanges made from A 105 carbon steel, 2 inch size, Class 300 with B7 studs were torqued to 125 pounds.
  • the API classification for this flange is Class F, meaning that the flange should leak under the requirements of the test.
  • the upper flange reached a temperature of 1225° F.
  • the lower flange temperature was 1265° F.
  • the stud temperature reached 1250° F. Sealing integrity was maintained with no leakage, and the flange was subjected to a connection test of 555 psi.
  • measurements of the stud showed that they averaged 0.010 inch permanent elongation due to high stud torque applied to the studs.
  • the fluid internal pressure does not exert enough separation load on the flange to make the studs yield at this temperature.
  • line contact seal or “substantially line contact sealing” mean that sealing engagement between the metal components is provided by substantially aligned contact engagement, e.g., of a metal flexible flange with one of the first and second members. Such line contact sealing engagement is significantly more effective at sealing than substantial planar-to-planar engagement of metal surfaces. Substantially line contact engagement may nevertheless result from sealing engagement of surfaces over a short length, so that the forces resulting in sealing are concentrated along a small surface area.
  • Each of the embodiments disclosed herein provides for a relatively thin flexible flange which is responsive to high fluid pressure within the interior of the members 12 , 14 to increase sealing effectiveness. Each flexible flange is thus forced into tighter sealing engagement with the respective member when fluid pressure increases. Each flexible flange is also deformed from its original as manufactured condition to a sealing position in which at least part of the seal ring is deformed beyond its elastic limit when securing members secure the first member to the second member.
  • the seal disclosed herein may be used in API or ANSI flange ring grooves and other special ring grooves, and will maintain seal integrity with very low restraining load, such as stud load, even if the flanges separate a small amount in a fire and the studs elongate in response to a temperature of up to about 1200° F.
  • the seals are especially sensitive to leakage with flange separation. For example, for every 0.001′′ of flange separation, a prior art seal may lose 0.001′′ squeeze in each ring groove, and if the seal shifts, the seal may lose 0.002′′ squeeze and leak. Any movement on standard seals will leak.
  • seal As disclosed herein to work in these types of grooves, it forms a dynamic seal that changes its shape as the gland formed by the two ring grooves changes shape, and the seal is pressure energized.
  • the seal design is thus based on flexure, instead of rigidity and high compression loading common for standard seals.
  • the metal seal body disclosed herein is designed so that it changes shape by flexing, yielding and/or telescoping. Because the seal body can change shape these three ways, shape changes such as thermal expansion and contraction can practically be ignored.
  • the pressure energized metal seal achieves high sealing with a pressure multiplier designed into the seal. This feature creates a substantially greater force per square inch between the seal ring and the ring groove than the internal pressure on the seal body causing this force. If the internal pressure of 1000 psi acts on 10 square inches and the seal engages the groove at only 0.5 square inches, the force acting on the seal to force sealing engagement is 20,000 pounds.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Gasket Seals (AREA)
  • Flanged Joints, Insulating Joints, And Other Joints (AREA)
US11/191,888 2005-07-28 2005-07-28 Seal ring and method Abandoned US20070024007A1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US11/191,888 US20070024007A1 (en) 2005-07-28 2005-07-28 Seal ring and method
PCT/US2006/028609 WO2007016021A2 (fr) 2005-07-28 2006-07-24 Bague d'etancheite et procede associe
CA2616361A CA2616361C (fr) 2005-07-28 2006-07-24 Bague d'etancheite et procede associe
GB0801262A GB2441731B (en) 2005-07-28 2006-07-24 Seal ring and method
US11/789,184 US7703773B2 (en) 2005-07-28 2007-04-24 Seal ring and method
US11/810,033 US7624991B2 (en) 2005-07-28 2007-06-04 Seal ring and method
US12/685,065 US20100127461A1 (en) 2005-07-28 2010-01-11 Seal ring and method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/191,888 US20070024007A1 (en) 2005-07-28 2005-07-28 Seal ring and method

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US11/789,184 Division US7703773B2 (en) 2005-07-28 2007-04-24 Seal ring and method
US11/810,033 Continuation US7624991B2 (en) 2005-07-28 2007-06-04 Seal ring and method

Publications (1)

Publication Number Publication Date
US20070024007A1 true US20070024007A1 (en) 2007-02-01

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Application Number Title Priority Date Filing Date
US11/191,888 Abandoned US20070024007A1 (en) 2005-07-28 2005-07-28 Seal ring and method
US11/789,184 Expired - Fee Related US7703773B2 (en) 2005-07-28 2007-04-24 Seal ring and method
US11/810,033 Expired - Fee Related US7624991B2 (en) 2005-07-28 2007-06-04 Seal ring and method
US12/685,065 Abandoned US20100127461A1 (en) 2005-07-28 2010-01-11 Seal ring and method

Family Applications After (3)

Application Number Title Priority Date Filing Date
US11/789,184 Expired - Fee Related US7703773B2 (en) 2005-07-28 2007-04-24 Seal ring and method
US11/810,033 Expired - Fee Related US7624991B2 (en) 2005-07-28 2007-06-04 Seal ring and method
US12/685,065 Abandoned US20100127461A1 (en) 2005-07-28 2010-01-11 Seal ring and method

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US (4) US20070024007A1 (fr)
CA (1) CA2616361C (fr)
GB (1) GB2441731B (fr)
WO (1) WO2007016021A2 (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050258603A1 (en) * 2004-03-30 2005-11-24 Durr Ecoclean Gmbh Surface seal for arrangement on a component and a method of arranging a surface seal on a component
EP1965117A1 (fr) * 2007-03-02 2008-09-03 REINERT. RITZ GmbH Brides de liaison
US20090224488A1 (en) * 2008-03-04 2009-09-10 Daniel Measurement And Control, Inc. System and method of a flange seal ring
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CN112513554A (zh) * 2018-04-06 2021-03-16 热力工程国际(美国)公司 双向自激励垫圈
WO2021077046A1 (fr) * 2019-10-17 2021-04-22 Seaboard International Llc Joint non métallique utilisant une géométrie de changement de forme induite thermiquement
US11180234B2 (en) * 2018-12-20 2021-11-23 Yamaha Hatsudoki Kabushiki Kaisha Outboard motor
CN114060516A (zh) * 2022-01-18 2022-02-18 中国空气动力研究与发展中心超高速空气动力研究所 一种锥面自紧密封绝缘环
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EP1965117A1 (fr) * 2007-03-02 2008-09-03 REINERT. RITZ GmbH Brides de liaison
US20090224488A1 (en) * 2008-03-04 2009-09-10 Daniel Measurement And Control, Inc. System and method of a flange seal ring
WO2009111560A3 (fr) * 2008-03-04 2009-12-10 Daniel Measurement And Control, Inc. Système et procédé pour bague d’étanchéité de bride
US8177238B2 (en) 2008-03-04 2012-05-15 Daniel Measurement And Control, Inc. System and method of a flange seal ring
US9625068B2 (en) 2008-03-04 2017-04-18 Daniel Measurement And Control, Inc. System and method of a flange seal ring
CN103032150A (zh) * 2012-12-28 2013-04-10 淄博柴油机总公司 水封套管
US20140246192A1 (en) * 2013-03-01 2014-09-04 Cameron International Corporation Multi-stage seal for well fracturing
EP3567286A1 (fr) * 2014-11-24 2019-11-13 Thomas Schneider Joint plat
EP3023674A3 (fr) * 2014-11-24 2016-09-21 Thomas Schneider Fermeture et joint plat
US20170307116A1 (en) * 2016-04-26 2017-10-26 Pro-Flange Limited Pipe coupling
US11480274B2 (en) * 2016-04-26 2022-10-25 Janak H. Handa Pipe coupling
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US20230133675A1 (en) * 2016-10-05 2023-05-04 Garlock Pipeline Technologies, Inc. Gasket with electrical isolating coatings
US11015710B2 (en) * 2016-10-05 2021-05-25 Garlock Pipeline Technologies, Inc. Gasket with electrical isolating coatings
US20180299044A1 (en) * 2016-10-05 2018-10-18 Garlock Pipeline Technologies, Inc. Gasket with electrical isolating coatings
US11543030B2 (en) 2016-10-05 2023-01-03 Garlock Pipeline Technologies, Inc. Gasket with electrical isolating coatings
CN112513554A (zh) * 2018-04-06 2021-03-16 热力工程国际(美国)公司 双向自激励垫圈
JP2021521399A (ja) * 2018-04-06 2021-08-26 サーマル エンジニアリング インターナショナル （ユーエスエイ） インコーポレイテッド 二方向型の自己付勢ガスケット
EP3775749A4 (fr) * 2018-04-06 2022-01-12 Thermal Engineering International (USA) Inc. Joints d'étanchéité auto-activés bidirectionnels
US11180234B2 (en) * 2018-12-20 2021-11-23 Yamaha Hatsudoki Kabushiki Kaisha Outboard motor
CN110185798A (zh) * 2019-06-24 2019-08-30 江苏省特种设备安全监督检验研究院 一种自密封式合金双波纹密封复合垫片
WO2021077046A1 (fr) * 2019-10-17 2021-04-22 Seaboard International Llc Joint non métallique utilisant une géométrie de changement de forme induite thermiquement
WO2022060752A1 (fr) * 2020-09-18 2022-03-24 Nuscale Power, Llc Fermetures pour cuves sous pression et systèmes et procédés associés
CN114060516A (zh) * 2022-01-18 2022-02-18 中国空气动力研究与发展中心超高速空气动力研究所 一种锥面自紧密封绝缘环

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US7703773B2 (en) 2010-04-27
GB0801262D0 (en) 2008-02-27
WO2007016021B1 (fr) 2007-11-22
US7624991B2 (en) 2009-12-01
GB2441731B (en) 2009-12-23
CA2616361A1 (fr) 2007-02-08
GB2441731A (en) 2008-03-12
WO2007016021A3 (fr) 2007-09-20
US20080029971A1 (en) 2008-02-07
WO2007016021A2 (fr) 2007-02-08
CA2616361C (fr) 2012-11-27
US20100127461A1 (en) 2010-05-27
US20080111313A1 (en) 2008-05-15

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