US20100127461A1 - Seal ring and method - Google Patents
Seal ring and method Download PDFInfo
- Publication number
- US20100127461A1 US20100127461A1 US12/685,065 US68506510A US2010127461A1 US 20100127461 A1 US20100127461 A1 US 20100127461A1 US 68506510 A US68506510 A US 68506510A US 2010127461 A1 US2010127461 A1 US 2010127461A1
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- United States
- Prior art keywords
- members
- seal
- seal body
- flange
- seal ring
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- Abandoned
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- 238000007789 sealing Methods 0.000 claims abstract description 74
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- 238000000429 assembly Methods 0.000 description 1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0881—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
-
- 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.
- FIGS. 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.
- 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 A105 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)
Abstract
A seal ring 10 for sealing between first and second members 12, 14 each having an outer groove surface 16, 126 and inner groove surface 18, 127 includes a metal seal body 26, 42, 52, 60, 70, 80, 92, 110, 122, 140 for engagement with the outer groove surface on the first and second members, and a metal flexible flange 30, 32, 44, 46, 54, 56, 62, 64, 76, 78, 88, 90, 94, 96, 112, 114, 128, 144, 146 with a cantilevered end of a flexible flange providing substantially line contact sealing engagement with the inner groove surface on respective first and second member. The metal flexible flange is configured for being fluid pressure energized, and is deformed beyond its elastic limit when securing members secure the first member to the second member.
Description
- 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.
- The disadvantages of the prior art are overcome by the present invention, and an improved seal ring and method are hereinafter disclosed for reliable sealing between two members.
- In one embodiment, 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.
- In another embodiment, 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.
- These and further features and advantages of the present invention will become apparent from the following detailed description, wherein reference is made to the figures in the accompanying drawings.
-
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 inFIG. 1 . -
FIG. 3A discloses an alternate embodiment of a seal ring, andFIG. 3B discloses a seal ring as shown inFIG. 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. -
FIGS. 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 inFIG. 10A supported on a seal ring before the securing members are tightened, andFIG. 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, andFIG. 11B shows the same seal ring with the first and second members secured. -
FIG. 1 illustrates aseal ring 10 for sealing between first andsecond members respective throughbore member tapered groove surface 16 directed radially inward in a direction away from an interface between themembers tapered groove surface 18 directed radially outward in a direction away from the interface betweenmembers groove base 20 is shown spaced between thesurfaces common axis 22 of the throughbores. A plurality of securingmembers 24, such as bolt and nut assemblies, are arranged circumferentially about themembers surfaces ring 10 therein. - Referring to
FIG. 2 , thesealing ring 10 comprises ametal seal body 26 for engagement with the radiallyouter surface 16 on the first and second members when the securingmembers 24 secure the first member to the second member. Anannular flange 28 may be pressed on or otherwise secured to theseal body 26, and is compressed between thesurface 25 on thebody 12 andsurface 27 on thebody 14 when thebolts 24 are tightened. The sealingring 10 further includes a pair of metalflexible flanges seal body 26, such that acantilevered end surface 18 on a respective first andsecond member spacing seal body 26 provides for fluid pressure energization of the flexible flange. The cantilevered ortip end respective surface 18 in response to high pressure fluid in the bore of themembers - For the embodiment as shown in
FIG. 2 , theseal body 26 and theflexible flanges annular flange 28 and theseal body 26 may be formed from a unitary homogeneous material. Theseal body 26 and the pair offlanges FIG. 2 form a substantially C-shaped cross-sectional configuration, as shown inFIGS. 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 theseal ring 10. There is a small angular mismatch between the radially outer taperedsurface 29 on theseal body 26 and the corresponding outer taperedsurface 16 on each of themembers line contact seal 38 between the seal body and thesurfaces 16. Those skilled in the art appreciate that, in response to high fluid pressure within the bore, 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. Whether under high pressure or low pressure, the seal between these components is effectively provided by line contact engagement, since even under high pressure, substantially higher sealing forces are exerted atpoint 38 than at other points along the radiallyouter surface 27 of the seal body. Thus even if high pressure results in substantially planar contact betweensurfaces 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. During substantial separation of the first and second members, 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.
- By including a flexible flange on the seal ring ID and an interference fit on the seal ring OD, 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. When the flange bolts are tightened, 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. When internal pressure is applied to 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. These fluid pressure induced forces further strengthen the seal and establish a pressure-energized seal. The seal ring maintains sealing integrity during flange face separation since the inward flexure of the seal body and the outward flexure of the flexible flange stores energy in the seal ring, acting in the manner of a spring. This stored energy is released when being supplemented by the internal fluid pressure within the first and second members to maintain contact between the seal ring and the groove walls during separation.
-
FIG. 3A depicts analternate seal body 42 and a pair of metalflexible flanges spacing seal body 42. The seal body as shown inFIG. 3A does not include a annular flange, and accordingly thesurface 25 on themember 12 directly engages thesurface 27 on themember 14 when the bolts are tightened, as shown inFIG. 3B . -
FIG. 3B also depicts eachflexible flange base surface 20 atpoint 45 on the cantilevered end offlanges 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. Theend surface 45 forming a substantially line contact seal is thus similar to theend surface 31 shown inFIG. 2 , except that sealing engagement in theFIG. 3B embodiment is with thebase surface 20 rather than theinner groove surface 18. A mismatch between the angle of thesurface 16 and the radially outwardangled surfaces 43 on theseal body 42 are depicted, with the body thus being configured for substantially line contact sealing engagement with each of the annular flanges. Referring toFIG. 4 , theseal body 52 is provided with anannular flange 28. A mismatch between theouter surface 53 onbody 52 and the taperedouter groove surface 16 results in line contact sealing engagement with themembers point 38. A pair of metalflexible flanges surfaces 18 on the first and second members atpoint 31, while spacing 55, 57 between the metalflexible flanges seal body 52, and in this case between theflexible flanges flange supporting component 58 of each flexible flange, provides fluid pressure energization of the flexible flange. Theflange component 58 is slidable in a generally axial direction relative to theseal body 52, and thesurfaces 59 on theflanges 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 theseal body 60 is unitary and homogeneous with theannular flange 28. In this case, the seal body supportsflexible end flanges respective gap 66 provided between thesurface 18 and thebody 60.Spacings flexible flanges Additional slots end flanges slots slot 68 being directed substantially radially outward. Theseal ring 60 seals atpoint 38 with thesurface 16 as previously explained, and thecantilevered end 31 of eachflange member surface 18. -
FIG. 6 depicts another embodiment on ametal seal body 70 having a radiallyoutward flange 28 secured thereto. The seal body is intended for substantially line contact sealing engagement with the radially outward surface of eachmember annular bump 72 is provided on themember 12 for substantially line contact sealing engagement with theseal body 70, while the mismatch of the angles between the outer surface of the seal body and the radiallyoutward groove wall 16 also may or may not provide line contact sealing atpoint 73. As an alternative to providing the raisedbump 72 on the member, a sealingbump 74 may be provided on the seal body, as shown inFIG. 6 . A pair of metalflexible flanges members point 31. Aspacing flexible flanges - The embodiment in
FIG. 7 illustrates analternative seal body 80 which is integral with the radiallyoutward flange 28. Line contact sealing engagement with themember 12 is provided by theannular bump 82 on the seal body, and by the mismatch surfaces which may result in line contact sealing atpoint 84.FIG. 7 also depicts abump 86 provided on thelower member 14 for line contact sealing engagement with the seal body. The pair offlexible flanges respective spacings flange groove surface 18 atpoint 31. If desired, one of the bumps on the seal body or on themember member FIGS. 6 and 7 . -
FIG. 8 depicts yet anotherseal body 92 having aflange 28 secured thereto, with theseal body 92 supporting a pair offlexible flanges inner wall 18 of eachbody gap -
FIG. 9 depicts an alternative seal body 110 having a radiallyoutward flange 28 secured thereto. In this case,flange 114 is provided on the seal body for substantially line contact sealing engagement at 31 with the taperedsurface 18 on thelower member 14, with agroove 115 provided between theflexible flange 114 and the body 110. Aflange 112 is provided onflange support 116, which is slidable in a substantially radial direction relative to the body 110. Abump 118 on theflange support 116 provides substantially line contact sealing engagement with the body 110, while the mismatch between the outer surface of thesupport 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 theflexible flange 112. The body 110 also seals with themembers flange 112 is axially movable relative to body 110. -
FIG. 10A depicts yet another embodiment of a seal ring including ametal seal body 122 having aflange 28 integral therewith. Anannular bump 124 on the seal body is provided for sealing engagement with the radiallyoutward surface 126 of eachmember flexible flanges 128 each include asupport member 130 for slidable engagement with theinner wall 132 of thebody 122, and an annular bead or raisedsection 134 is provided for substantially line contact sealing engagement with the metal seal body. Eachflange 128 includes anannular bead 136 for substantially line contact sealing engagement with theinner wall 138 of the groove. Shown inFIG. 10B , the seal ring seals with eachmember inward groove surface 138 atpoint 136 between the metal flexible flange and a respective member, by theseal 134 provided between eachflange support member 130 and themetal seal body 122, and byannular bead 124 provided between the metal seal body and the radiallyoutward groove wall 126 of themembers flexible flange 128 and arespective support member 130 provides for fluid pressure energization of the flexible flange. Each flexible flange is axially movable relative to thebody 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 theseal body 140 has aflange 28 integral and homogeneous therewith. A mismatch between the outer surfaces on the flange body and the outer tapered groove surfaces 16 on themembers point 142, as shown inFIG. 11B .Surfaces 141 onbody 140 may be tapered to facilitate sliding thebase piece 143 on theseal body 140. Each seal body also includes a pair offlexible flanges insert body 148. When assembled, line contact sealing engagement atpoint 31 is formed between eachflange 144, 166 and therespective body base piece 143 forms a line contact seal withsurface 141 onseal body 140. The spacing 147 betweenflexible flanges base piece 143 is preferably filled with a compressible material, as shown inFIG. 11A , such as an elastomer, a high temperature graphite, Teflon™, or a plastic. Base piece 145 may be formed from metal, but alternatively may be a plastic material component. When the bolts are tightened, theinsert 148 is compressed, resulting in the seal body shown inFIG. 11B . - According to the present invention, 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.
- In a room temperature test on a 2 1/16th inch, 5,000 psi API flange connection with a seal ring according to the present invention, the flange joint was made up finger tight on the bolts, yet the connection held sealing integrity at 100 psi at 70° F. Pressure was subsequently increased to 10,000 psi, and was maintained for 24 hours without leakage.
- In a fire test, flanges made from A105 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. During the test, the upper flange reached a temperature of 1225° F., and the lower flange temperature was 1265° F., and 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. As the test equipment cooled down to 72° F., 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.
- It should be understood that the terms “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 - 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. For the 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.
- Although specific embodiments of the invention have been described herein in some detail, this has been done solely for the purposes of explaining the various aspects of the invention, and is not intended to limit the scope of the invention as defined in the claims which follow. Those skilled in the art will understand that the embodiment shown and described is exemplary, and various other substitutions, alterations and modifications, including but not limited to those design alternatives specifically discussed herein, may be made in the practice of the invention without departing from its scope.
Claims (16)
1-29. (canceled)
30. A method of sealing between first and second members each having a through bore in fluid communication with the throughbore in the other member, each member having a circumferential mating surface extending radially outward from the respective throughbore and a circumferential groove in the mating surface open to the circumferential groove in the other member and having a radially outer circumferential groove surface, a radially inner circumferential groove surface, and a circumferential base surface between a respective outer groove surface and inner groove surface, the outer groove surface being a tapered surface directed radially inward in a direction away from an interface of the first and second members, and the inner groove surface being a tapered surface directed radially outward in a direction away from the interface of the first and second members, and securing members arranged circumferentially about the first and second members to secure the first member to the second member, the method comprising:
engaging a metal seal body with each of the outer groove surface on the first and second members when the securing members secure the first member to the second member;
supporting a pair of flexible flanges on to the seal body and each extending radially inward such that a cantilevered end of a flexible flange provides substantially line contact engagement with at least one of the base surface and the inward groove surface on a respective first and second member, each of the flexible flanges formed from a metal with a yield strength of 30,000 psi or less;
deforming each flexible flange beyond its elastic limit when the securing members secure the first member to the second member; and
providing a spacing between the flexible flange and seal body for fluid pressure energization of the flexible flange, the spacing projecting in a substantially radially outward direction from a radially inward surface of the seal body.
31. A method as defined in claim 30 , further comprising:
providing an annular flange extending radially outward from the seal body for planar engagement with planar flange engaging faces on the first and second members.
32. A method as defined in claim 30 , further comprising:
dimensioning of the metal seal ring and grooves such that when the first and second members are drawn together, the seal body contacts the outer tapered surface of each groove and the line contact surface of each flexible flange contacts the inner tapered wall of a respective groove.
33. A method as defined in claim 30 , wherein movement of the members toward each other causes the seal body to slide on the outer surface of each groove creating a burnished seal contact surface, while also forcing the seal body radially inward thereby moving each flexible flange against the inner groove surface and forcing each flexible flange into a reduced diameter surface, causing each flexible flange to yield and conform to the inner groove surface.
34. A method as defined in claim 30 , wherein the seal body and the pair of flexible flanges form a substantially C-shaped cross-sectional configuration.
35. A method as defined in claim 30 , wherein the seal body and the flexible flanges are formed from a unitary homogenous material.
36. A seal ring sealing between first and second members each having a through bore, the seal ring and first and second members comprising:
each first and second member having a radially outer circumferential groove surface inclined outwardly in a direction toward the seal ring, and a radially inner circumferential groove surface inclined inwardly in a direction toward the seal ring;
securing members arranged circumferentially about the first and second members to secure the first member to the second member; and
a seal ring including a metal seal body having a yield strength of 30,000 psi or less engaging each of the outer groove surfaces on the first and second members when the securing members secure the first member to the second member, the metal seal body being flexed inward when the securing members are moved to secure the first member to the second member, and a metal flexible flange radially inward at the seal body such that a cantilevered end of the flexible flange provides substantially line contact sealing engagement with at least one of the base surface and the inner groove surface on a respective first and second member, a spacing between the flexible flange and the seal body projecting in a substantially radially outward direction from a radially inward surface of the seal body to increase flexibility of the flange and providing for fluid pressure energization of the flexible flange, and the flexible flange flexed outwardly and being deformed beyond its elastic range when the securing members secure the first member to the second member.
37. A seal ring and first and second members as defined in claim 36 , wherein the seal body and the flexible flange are formed from a unitary homogenous material.
38. A seal ring and first and second members as defined in claim 36 , wherein the seal body has substantially line contact sealing engagement with the outer groove surface on a respective first and second member.
39. A seal ring and first and second members as defined in claim 36 , further comprising:
an annular flange extending radially outward from the seal body for planar engagement with planar flange engaging faces on the first and second members.
40. A seal ring and first and second members as defined in claim 36 , wherein the seal body and another flexible flange form a substantially C-shaped cross-sectional configuration.
41. A seal ring and first and second members as defined in claim 36 , wherein the spacing between each of the pair of flexible flanges and the seal body is substantially filled with an elastomer, such that fluid pressure on the elastomer exerts increasing sealing pressure between each flexible flange and the inner groove surface on a respective first and second member.
42. A seal ring and first and second members as defined in claim 36 , wherein the outer groove surface is a tapered surface directed radially inward in a direction away from an interface of the first and second members, and the inner groove surface is a tapered surface directed radially outward in a direction away from the interface of the first and second members.
43. A seal ring and first and second members as defined in claim 36 , further comprising:
another flexible flange for substantially line contact sealing engagement with the other of the first and second members.
44. A seal ring and first and second members as defined in claim 36 , wherein a radially outer portion of the seal body is thicker than a thickness of either of the pair of metal flexible flanges.
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US5058906A (en) * | 1989-01-19 | 1991-10-22 | Vetco Gray Inc. | Integrally redundant seal |
US5240263A (en) * | 1988-06-01 | 1993-08-31 | Specialist Sealing Limited | Metallic sealing rings and their manufacture |
US5257792A (en) * | 1991-10-15 | 1993-11-02 | Fip Incorporated | Well head metal seal |
US5354072A (en) * | 1989-12-19 | 1994-10-11 | Specialist Sealing Limited | Hollow metal sealing rings |
US6722426B2 (en) * | 2001-06-29 | 2004-04-20 | Abb Vetco Gray Inc. | Gasket with multiple sealing surfaces |
US7032905B2 (en) * | 2004-09-22 | 2006-04-25 | Mullally Michael J | Leak resistant seal |
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US3275335A (en) * | 1963-03-18 | 1966-09-27 | Donaldson Co Inc | High pressure seal |
US3531133A (en) * | 1968-11-08 | 1970-09-29 | Res Eng Co | Seal |
US20010045709A1 (en) * | 1999-10-28 | 2001-11-29 | Stobbart John Edward | Seal ring and joint |
-
2005
- 2005-07-28 US US11/191,888 patent/US20070024007A1/en not_active Abandoned
-
2006
- 2006-07-24 WO PCT/US2006/028609 patent/WO2007016021A2/en active Application Filing
- 2006-07-24 GB GB0801262A patent/GB2441731B/en not_active Expired - Fee Related
- 2006-07-24 CA CA2616361A patent/CA2616361C/en not_active Expired - Fee Related
-
2007
- 2007-04-24 US US11/789,184 patent/US7703773B2/en not_active Expired - Fee Related
- 2007-06-04 US US11/810,033 patent/US7624991B2/en not_active Expired - Fee Related
-
2010
- 2010-01-11 US US12/685,065 patent/US20100127461A1/en not_active Abandoned
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Publication number | Priority date | Publication date | Assignee | Title |
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US4410186A (en) * | 1982-04-12 | 1983-10-18 | Petroleum Designers, Inc. | Sealing system for pressurized flanged joints |
US4452462A (en) * | 1983-10-06 | 1984-06-05 | Gray Tool Company | Temperature resistant joint packing with E-shaped spring seal |
US4747606A (en) * | 1985-09-23 | 1988-05-31 | Vetco Gray Inc. | Bi-directional metal-to-metal seal |
US5240263A (en) * | 1988-06-01 | 1993-08-31 | Specialist Sealing Limited | Metallic sealing rings and their manufacture |
US5058906A (en) * | 1989-01-19 | 1991-10-22 | Vetco Gray Inc. | Integrally redundant seal |
US5354072A (en) * | 1989-12-19 | 1994-10-11 | Specialist Sealing Limited | Hollow metal sealing rings |
US5257792A (en) * | 1991-10-15 | 1993-11-02 | Fip Incorporated | Well head metal seal |
US6722426B2 (en) * | 2001-06-29 | 2004-04-20 | Abb Vetco Gray Inc. | Gasket with multiple sealing surfaces |
US7032905B2 (en) * | 2004-09-22 | 2006-04-25 | Mullally Michael J | Leak resistant seal |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103377725A (en) * | 2012-04-27 | 2013-10-30 | 上海核工程研究设计院 | Reactor internal of reactor |
US20150021863A1 (en) * | 2013-07-22 | 2015-01-22 | Jui-Kung WANG | Mutiple-Leak Proof Sealiing System |
CN104179979A (en) * | 2014-07-30 | 2014-12-03 | 东方电气集团东方汽轮机有限公司 | Seal structure for flange butt joint surface |
US20160040810A1 (en) * | 2014-08-08 | 2016-02-11 | Rohr, Inc. | Bolted duct joints |
US10287990B2 (en) * | 2014-08-08 | 2019-05-14 | Rohr, Inc. | Bleed system bolted duct with recessed seals |
US11118513B2 (en) | 2014-08-08 | 2021-09-14 | Rohr, Inc. | Bolted duct joints |
US11015710B2 (en) * | 2016-10-05 | 2021-05-25 | 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 |
US20230133675A1 (en) * | 2016-10-05 | 2023-05-04 | Garlock Pipeline Technologies, Inc. | Gasket with electrical isolating coatings |
US11898637B2 (en) * | 2016-10-05 | 2024-02-13 | Gpt Industries, Llc | Gasket with electrical isolating coatings |
Also Published As
Publication number | Publication date |
---|---|
US7703773B2 (en) | 2010-04-27 |
CA2616361A1 (en) | 2007-02-08 |
US7624991B2 (en) | 2009-12-01 |
US20070024007A1 (en) | 2007-02-01 |
WO2007016021A3 (en) | 2007-09-20 |
CA2616361C (en) | 2012-11-27 |
WO2007016021B1 (en) | 2007-11-22 |
WO2007016021A2 (en) | 2007-02-08 |
US20080111313A1 (en) | 2008-05-15 |
GB0801262D0 (en) | 2008-02-27 |
GB2441731A (en) | 2008-03-12 |
GB2441731B (en) | 2009-12-23 |
US20080029971A1 (en) | 2008-02-07 |
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Legal Events
Date | Code | Title | Description |
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STCB | Information on status: application discontinuation |
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