US20140131954A1 - Shrinkage compensated seal assembly and related methods - Google Patents
Shrinkage compensated seal assembly and related methods Download PDFInfo
- Publication number
- US20140131954A1 US20140131954A1 US13/674,481 US201213674481A US2014131954A1 US 20140131954 A1 US20140131954 A1 US 20140131954A1 US 201213674481 A US201213674481 A US 201213674481A US 2014131954 A1 US2014131954 A1 US 2014131954A1
- Authority
- US
- United States
- Prior art keywords
- seal
- elongate body
- head portion
- pin
- pin members
- 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
Links
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B33/00—Sealing or packing boreholes or wells
- E21B33/10—Sealing or packing boreholes or wells in the borehole
- E21B33/12—Packers; Plugs
-
- 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
- F16J15/068—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces the packing swelling under working conditions
-
- 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
- F16J15/064—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces the packing combining the sealing function with other functions
-
- 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
- F16L21/00—Joints with sleeve or socket
- F16L21/08—Joints with sleeve or socket with additional locking means
Abstract
Shrinkage compensated seal assemblies and methods of compensating for shrinkage of a seal due to temperature variations, are provided. According to an exemplary shrinkage compensated seal assembly, the assembly includes a seal, a first compression member for engaging the upper surface of the seal, a second compression member for engaging the lower surface of the seal, and a plurality of pin members each having an elongate body and a head portion. The elongate body of each separate one of the plurality of pin members slidably extends through a different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member to provide for maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in the volume size of the seal.
Description
- 1. Field of the Invention
- This invention relates to seal assemblies, in general, and to seal assemblies having seal material that undergoes a substantial volume change resulting from varying temperatures at given pressures, in particular, and methods of compensating for seal shrinkage due to varying temperatures at given pressures.
- 2. Description of the Related Art
- Casing hanger seal assemblies, often referred to as slab packing, pack-off, etc., are provided to prevent well fluid from escaping through the casing head. The force necessary to energize the seal packing is equivalent to the pressure to be contained multiplied by the exposed surface area of packing of the seal in compression. The exposed surface is the portion facing downwards towards the casing hanger slip bowl and/or the opposite upward facing surface. As the exposed surface area is reduced, the force required to energize the seal packing to contain a certain pressure is also reduced.
- Bolting that is employed to hold the packing to the casing hanger bowl necessarily covers part of the exposed surface area, and thus, acts as a built in surface area reducer. The bolting is normally tightened sufficiently to cause a substantial level of stress in the seal. When shrinkage occurs in the seal due to cold temperature, however, some of the stress that is stored in the seal material is relieved, causing the seal to leak. This phenomenon occurs because the bolt head top junk ring and casing hanger bowl remain in a fixed location relative to the complementing nut. In an extreme case, if enough shrinkage were to occur, the amount of stress applied to the seal by bolting would be reduced to zero.
- This problem has been previously addressed by compressing the seal sufficiently to attempt to compensate for the varying compression at the varying temperatures resulting from the temperature driven volume changes. This methodology, however, requires application of a higher energizing force during the complete cycle, which can in turn drive a requirement for the seal to be made of special material that is strong enough to withstand the compression forces under both stable conditions and at the varying temperatures. Additionally, since these bolts are used to hold the assembly together, the compression of the seal can only stay constant as long as the bolts can resist elongation (bolt stretch) at the varying temperatures.
- A similar problem has been found in interference elastomer seal applications. In such applications, volume fill and squeeze can play a major role in the design of the seal. When the seal is exposed to a wide range of temperature variations, shrinkage becomes an issue to the amount of squeeze in the seal. The larger the volume of the seal material, the more that shrinkage plays a major role in the seal's design.
- This shrinkage factor problem has been previously addressed in the pump field by changing seal compounds and/or by reducing radial clearance between housing and piston. This makes the assembly process more difficult and can result in damage to the seal during assembly.
- Another attempt at solving the problem in a subsea well field application involved intensifying pressure on the seal through use of a metal ‘T-Ring’ with rubber molded on the outside and inside of the ring. Implementation, however, has been deemed to be excessively complicated and cost-prohibitive. Further, such a configuration does not provide an ability to compress the seal bi-directionally.
- Recognized by the inventors, therefore, is the need for an apparatus/assembly and methods of compensating for shrinkage that does not require an excessively high energizing source and/or requirement for specially made seals or custom seal material. Also recognized by the inventors, with respect to an interference seal application, is the need for an apparatus/assembly and methods of compensating for shrinkage that does not require the reduction in radial clearance, and thus, does not require reduced tolerances and higher costs.
- In view of the foregoing, various embodiments of the present invention provide a shrinkage compensated seal assembly and methods of compensating for shrinkage of a seal, which provide a plurality of floating pin members slidably positioned through an otherwise conventional seal assembly portion. Advantageously, when used, for example, in a high temperature pack off, the floating pin members can reduce the surface area of the exposed portion of the seal, which results in a requirement of less force to energize the packing, especially when the annular area of the packing is large. The floating pin members also advantageously improve the ability of the packing to maintain a seal with a well casing and/or casing head when the temperature cycles from hot to cold. As the volume decreases due to shrinkage, a constant force can still be applied by the pin members to compensate for the reduced compression in the seal material due to the shrinkage.
- Advantageously, when used, for example, in interference elastomer seal applications, the floating pin members can reduce the volume fill, and thus, reduce the amount of force required to energize the packing. Additionally, the floating pin members can provide a constant force, allowing the packing to maintain a seal at a reduced packing volume and/or volume-dependent compressive force caused by shrinkage of the seal material due to low temperatures. Further, when employed bidirectionally, the floating pin members can compensate for pressure located both above and below the seal assembly.
- More specifically, an example of an embodiment of a shrinkage compensated seal assembly includes a seal, a first compression member having a first surface for engaging a first surface of the seal and a second surface opposite the first surface, a second compression member having a first surface for engaging a second surface of the seal and a second surface opposite the first surface, and a plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body. The elongate body of each separate one of the plurality of pin members slidably extends through a different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member to provide for maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal. In an exemplary configuration, the head of each pin member on the lower side of the seal assembly engages the second compression member in response to in situ pressure. Also or alternatively, some of pin members are oriented opposite with other of the members to provide a bi-directional capability.
- According to another aspect, the head of each pin member is positioned within a recess of a casing hanger slip bowl. According to another aspect, each pin member also includes a fastener connected to the second end of the elongate body. The fastener includes an engagement surface positioned (oriented) to engage the second surface of the second compression member when the shrinkage compensated seal assembly is operationally employed and when a sum of force applied to a surface opposite the engagement surface of the respective fastener and the force applied to the surface of the second end of the elongate body of the respective pin member exceeds the force applied to the surface of the head portion of the respective pin member opposite the engagement surface thereof to provide the bi-directional capability. According to another aspect, the first compression member is a compression plate and the second compression member is a bottom plate landed upon the slip bowl.
- According to another aspect, the first compression member is a first split ring, the second compression member is a second split ring, and the seal assembly is positioned within a recess in the casing head. The recess forms a confined space to restrict movement of the pin members to both allow free-floating of the pin members and to prevent an inadvertent departure of the pin members from within the split rings and/or seal.
- According to another embodiment of the present invention, a method of compensating for shrinkage of a seal for a casing head member due to temperature variations at given pressures, is provided. The method includes the step of providing a seal assembly comprising an seal, a first compression member having a first surface for engaging a first surface of the seal and a second surface opposite the first surface, a second compression member having a first surface for engaging a second surface of the seal and a second surface opposite the first surface, and providing a plurality of pin members. Each pin member has an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body. The method also includes the steps of slidably extending the elongate body of each separate one of the plurality of pin members through a corresponding different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member, and maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal.
- According to another aspect, the method can also or alternatively include the step of providing a second plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body. The head portion of each pin member has a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body. Further, each head portion of each pin member of the second plurality of pin members has an engagement surface positioned to engage the second surface of the first compression member. According to this aspect, the method also includes the step of slidably extending the elongate body of each separate pin member of the second plurality of pin members through a corresponding different one of a second plurality of sets of apertures in the first compression member, the seal, and the second compression member, a direction opposite that of the first plurality of pin numbers. The method also includes the step of maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal by each of the second plurality of pin members when in situ force applied to a surface opposite the engagement surface of the head portion of the respective pin member exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
- So that the manner in which the features and advantages of the invention, as well as others which will become apparent, may be understood in more detail, a more particular description of the invention briefly summarized above may be had by reference to the embodiments thereof which are illustrated in the appended drawings, which form a part of this specification. It is to be noted, however, that the drawings illustrate only various embodiments of the invention and are therefore not to be considered limiting of the invention's scope as it may include other effective embodiments as well.
-
FIG. 1 is a part sectional and part environmental view of a high temperature pack off including a shrinkage compensated seal assembly employed as a casing hanger seal according to an embodiment of the present invention. -
FIG. 2 is a perspective view of a 49.1° section of the seal assembly shown inFIG. 1 according to an embodiment of the present invention. -
FIG. 3 is a sectional view of a floating pin shown inFIG. 2 according to an embodiment of the present invention. -
FIG. 4 is a schematic diagram of a free-end floating pin extending through an alternative seal arrangement according to an embodiment of the present invention. -
FIG. 5 is a part schematic heart perspective view of a high-pressure pack off according to an embodiment of the present invention. -
FIG. 6 is a part sectional and part environmental view of a pair of a shrinkage compensated interference elastomer seal assemblies employed as a casing head seal according to an embodiment of the present invention. -
FIG. 7 is a sectional view of a shrinkage compensated interference elastomer seal assembly according to an embodiment of the present invention. -
FIG. 8 is a sectional view of a detailed portion of a shrinkage compensated interference elastomer seal assembly according to an embodiment of the present invention. -
FIG. 9 is a sectional view of a portion of a shrinkage compensated interference elastomer seal assembly encapsulated by a threaded ring according to an embodiment of the present invention. - The present invention will now be described more fully hereinafter with reference to the accompanying drawings, which illustrate embodiments of the invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the illustrated embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout. Prime notation, if used, indicates similar elements in alternative embodiments.
- As production of oil and gas occurs at greater water and surface depths the temperature variation becomes wider and more critical to the effectiveness of elastomer seals. Accordingly, a constant effectiveness of the
seal 43, especially at higher pressures, has become more desirable. Various embodiments of the present invention provide compensation for the behavior of the seals at these varying temperatures. Specifically, various embodiments of the present invention feature seal assemblies, which employ a plurality of floating pins, bolts, or other similar structures, that can function as both a seal surface area reducer and a constant effectiveness shrinkage compensator. The various embodiments can be used in a plethora of seal applications including, but not limited to, casing hanger seal arrangements and interference seal arrangements. - Referring to
FIG. 1 a shrinkage compensated casinghanger seal assembly 30 circumscribes anouter surface 31 of acasing tube 33 and is positioned between theouter surface 31 of thecasing tube 33 and aninner surface 35 of acasing head 37. Referring also toFIG. 2 , theseal assembly 30 is bolted to the upper portion of a casinghanger slip bowl 41. Theseal assembly 30 includes aseal 43, which is typically of an elastomeric material as known to those of ordinary skill in the art, although materials also known to those of ordinary skill in the art are with the scope of the present invention. According to the illustrated embodiment, theinner diameter surface 45 of theseal 43 compressibly engages against theouter surface 31 of thecasing tube 33, and theouter diameter surface 47 compressibly engages aninner surface 35 of thecasing head 37. - Referring primarily to
FIG. 2 , theseal assembly 30 also includes acompression plate 51 positioned atop theseal 43 and abottom plate 53 positioned adjacent to or integral with theslip bowl 41. A set of clamping members 55 (only one shown) each include anelongate body 57 that extends through a set of coaxially aligned apertures (not shown) in thecompression plate 51,seal 43, andbottom plate 53. The clampingmembers 55 rigidly connect theseal assembly 30 to theslip bowl 41. The lower end of each clampingmember 55 either independently connects to the upper portion of theslip bowl 41, or in conjunction with a lower end connector (not shown), engages an upper panel of theslip bowl 41. A washer stack and/or additional connector, individually or collectivelyupper connector 59, is fixedly connected to the upper end of each clampingmember 55 to securely hold thecompression plate 51 andbottom plate 53 in compressive engagement withseal 43 to put theseal 43 in a state of compression. Theseal assembly 30 also includes a set of floatingpin members 61 each having anelongate body 63 positioned to slidably extend through a set of coaxially alignedapertures compression plate 51,seal 43, andbottom plate 53, respectively. - Referring primarily to
FIG. 3 , eachpin member 61 includes ahead 71 which has a larger diameter than theelongate body 63 and larger diameter than that of at least thecoaxial aperture 69 extending through thebottom plate 53. It also typically has a diameter that is larger than that of thecoaxial apertures head 71 is located within arecess 73 extending into the top of theslip bowl 41. The depth of therecess 73 is substantially larger than the longitudinal thickness of thehead 71 to allow thepin member 61 to slide up and down within the set ofcoaxial apertures pin member 61 includes anut 75 or other connector having a diameter that is larger than theaperture 65 extending through thecompression plate 51. The tail end portion of eachpin member 61 receiving thenut 75 can have a smaller diameter in order to accommodate the addition of threads and to create a shoulder for the nut to bottom on, hence, preventing premature energization of the seal assembly. Other configurations, however, are within the scope of the present invention. - The
body 63 of eachpin member 61 is sufficiently long so that thenut 75 can be connected spaced apart at a sufficient distance from thehead 71 of thepin members 61 to allow substantial bidirectional movement of thepin member 61. Eachpin member 61 moves upward when the annulus pressure between thecasing head 37 and theouter surface 31 of thecasing 33 provides net forces on thehead 71 of thepin member 61 which exceed those provided on the upper surfaces of thenut 75 andpin member body 63. This results in thehead 71 of thepin member 61 engaging the lower surface of thebottom plate 53, and correspondingly, theseal 43 being compressed against thecompression plate 51 and lower surface ofupper fastener 59. Similarly, thepin member 61 moves downward when the forces acting upon the upper surfaces of thenut 75 andpin member body 63 exceed those acting upon the lower facing surface of thehead 71 of thepin member 61. This results in thenut 75 engaging the upper surface of thecompression plate 51, and correspondingly, theseal 43 being compressed against thebottom plate 53 and theslip bowl 41 that is sitting on a shoulder 76 in thecasing head 37. - Whether or not the
pin members 61 engage thebottom plate 51 orcompression plate 51 is dependent upon the in situ pressure acting upon thehead 71 or tail of thepin members 61. - Note, according to an alternative configuration, the
pin members 61 may not include thenut 75. In such configuration, it is assumed that the forces applied to thehead 71 of thepin member 61 will always control. If the pressure associated with the tail of thepin member 61 instead exerts a greater force on the tail surface than that exerted on thehead 71, the associatedrecess 73 in theslip bowl 41 will prevent therespective pin member 61 from being blown out of theseal assembly 30. Non-extrusion rings 77, 79, are located in theplates seal 43 coaxial withaperture 67. - In operation, the floating
pin members 61 are extended through thecompression plate 51,seal 43, and bottom plate 53 (i.e., slab packing) prior to installing theseal assembly 30 on the casinghanger slip bowl 41. Thepin members 61 are retained from both ends of the packing and are allowed to float in either direction. As pressure is applied from either direction of the packing a net force is exerted by thepin members 61 that is equivalent to the pressure applied times the sealed area of eachpin member 61. That force will act against the connectors of the clampingmembers 55 which is retaining theseal assembly 30 to theslip bowl 41, while the casing tube weight holds theslip bowl 41 in place. This force will remain substantially constant if the pressure remains substantially constant. This constant force is proportional to the number ofpin members 61 installed and the pressure applied, irrespective of the temperature. Hence that force can provide constant stress in the seal material independent to what happens to the volume of the seal material as the temperature changes. Note, as the outer diameter ofhead 71 is not sealed to the sidewalls of therecess 73 inslip bowl 41 as in the embodiment shown inFIG. 3 , for example, the terminology “net force” has been utilized to denote that the motivating “force” would be net of the force acting upon the downward facing surface of thehead 71 minus the force acting upon the surface portion facing the lower surface ofbottom plate 53. - Referring to
FIG. 4 , according to an alternative configuration, a first pair of wire mesh or junk compression/anti-extrusion rings 101 configured to circumscribe the outer surface of thecasing tube 33 are received in a corresponding pair ofrecesses 103 extending into the inner surface of theseal 43. Additionally, a second pair ofwire mesh 105 circumscribe theseal 43′ and extend into a corresponding pair ofrecesses 107 in the outer surface of theseal 43′. The second pair ofwire mesh 105 are configured to fit along the outer surface of theseal 43′ against the inner diameter of thecasing head 37. In this configuration, the illustratedpin members 61′ are shown to have a shorterelongate body 63′. - According to the illustrated configuration, similar to the embodiment of the
pin member 61 including anut 75 or other connector, eachpin member 61′ moves upward when the pressure between thecasing head 37 and theouter surface 31 of thecasing tube 33 provides net forces on thehead 71′ of thepin member 61′, which exceed those provided on the upper surfaces of thepin body 63′. This results in theseal 43′ being compressed between theplates pin member body 63′ exceed those acting upon the lower facing surface of thehead 71′ of thepin member 61′, thepin member 61′ will move downward until hitting the bottom of therecess 73 in theslip bowl 41. - In operation, the floating
pin members 61′ are extended through thecompression plate 51, seal 43′, and bottom plate 53 (slab packing) and are assembled into thewire mesh seal assembly 30′ on the casinghanger slip bowl 41. With respect to conditions where the pressure is higher on the underside of thepin members 61′, the function remains the same as that described with respect to pin members 61 (FIG. 3 ). - Referring to
FIG. 5 , according to an alternative configuration of the seal assembly(s)/apparatus FIGS. 3 and 4 , aseal assembly 30″ includes acompression plate 51′ positioned atop aseal 43″ and abottom plate 53′ landing upon a shoulder 111 circumscribed by a coiled spring 113. A set of clamping members (not shown) each include an elongate body that extends through a set of coaxially aligned apertures (not shown) in thecompression plate 51′, seal 43″, andbottom plate 53′. Anouter recess 115 extending into outer diameter portions of thecompression plate 51′ receive the tail end portion of anmember 61 andfastener 75, or alternatively, thehead portion 71, depending upon the configuration. Anouter recess 73′ extends into lower surface portions of thebottom plate 53′ to receive a ahead 71 of thepin member 61, or alternatively, the tail end portion andfastener 75, depending upon the configuration. Theseal 43″ can include a plurality ofrecesses - According to a configuration, a first
non-extrusion ring recess 121 having a camber angle (beveled cut) extends between the inner diameter surface and lower facing surface of thecompression plate 51′ to receive a firstnon-extrusion ring 123. Similarly, asecond recess 125 having an oppositely oriented camber angle (beveled cut) extends between the inner diameter surface and upper facing surface of thebottom plate 53′ to receive a secondnon-extrusion ring 127 to prevent extrusion of theseal 43″, or seal 43, 43′, depending upon the respective application of the non-extrusion rings. Note, in an exemplary configuration, extrusion rings 123, 127, are “PEEK” or other hard ATL non-extrusion rings. Note also, one of ordinary skill in the art would recognize that various combinations ofcompression plate seal bottom plate -
FIG. 6 illustrates a pair of a shrinkage compensated interferenceelastomer seal assemblies 130 employed as a casing head seal within a casing head (spool) 137 according to an exemplary configuration. Eachseal assembly 130 circumscribes anouter surface 31 of acasing tube 33 and is positioned between theouter surface 31 of thecasing tube 33 and aninner surface 135 of thecasing spool 137. Referring also toFIG. 7 , eachseal assembly 130 is positioned within anannular recess 148. Theseal assembly 130 includes aseal 143, which is typically of an FS-type seal 143 or PE-type seal 143′ constructed of an elastomeric material as known to those of ordinary skill in the art. Other materials also known to those of ordinary skill in the art are, however, within the scope of the present invention. - Referring primarily to
FIG. 8 , according to the illustrated embodiment, the inner diameter surface of theseal 143 has aconvex portion 181 typically referred to as a bulge or bump, which compressibly engages against theouter surface 31 of thecasing tube 33. In order to provide for variation of the volume fill due to casing tolerances, the outer diameter surface typically has aconcave portion 183 between a pair ofengagement portions 185 which engage the inner surface of thecasing spool 137. Theseal assembly 130 includes a pair of segmented rings, e.g., PEEK or other hard ATL rings 187, 188, positioned above and belowseal 143 and a pair of beveled non-extrusion rings 189, 190, positioned in complementing annular recesses in each of thesegmented rings - In the embodiment shown in
FIG. 8 , the upper andlower rings beveled cut 191 and a scarf cut at each end of the segment to facilitate placement within therecess 148 in thecasing spool 137 at installation. In an exemplary configuration, when rings 187, 188, are segmented rings, each end of the respective ring segments include the scarf cut to provide an overlapping connection between the respective segments. - In the embodiment shown in
FIG. 9 , one or more threaded rings 193 (only one shown) is/are utilized to form therecess 148. In the exemplary configuration, acoiled spring 195 is molded with theseal 143 on the casing surface-side of theseal 143 to prevent extrusion of theseal 143 between theouter surface 31 of thecasing tube 33 and thesegmented rings seal assembly 130 also includes a set of floatingpin members 161 spaced apart along the circumference of theseal 143, typically in alternating directions (seeFIG. 7 ). - Each
pin member 161 has anelongate body 163 positioned to slidably extend through a set of coaxially aligned apertures/recesses 201, 202, 203, in the uppersegmented ring 187, theseal 143, and the lowersegmented ring 188, respectively. Eachpin member 161 also includes ahead 171, typically round, which has a larger diameter than theelongate body 163 and larger than at least the coaxial aperture extending through the upper or lower segmented ring, respectively, depending upon the orientation of thepin members 161. Thehead 171 is located within arecess 211 extending into the upper or lowersegmented ring pin member 161 is oriented facing upward or facing down. In the exemplary configuration, the depth of therecess 211 is substantially the same as the thickness of thehead 171. - According to the exemplary configuration, the longitudinal length L1 of the
seal assembly 130 is less than the longitudinal length L2, e.g., typically approximately 1.5″ in this application, and the combined length of thepin 161 andhead 171 is typically slightly smaller than that of L1, to allow thepin member 161 to slide up and down within the set of coaxial apertures/recesses 201, 202, 203, and to allow for a certain amount of compression of theseal 143. The difference between the lengths L1 and L2 are sufficiently small to prevent thepin members 161 from extracting through either of the apertures/recesses pin members 161 capable of floating within a confined space. Thepin members 161 function to compensate for shrinkage of theseal 143, preventing leaking of theseal 143 as a result of a temperature-induced volume reduction. Also, the volume of thepin member 161 that penetrates the, e.g., elastomer seal material, as a result of the apertures in theseal 143, will reduce the volume of material needed to construct theseal 143, and thus, will further reduce the amount of expected shrinkage. - Note, although the
pin members 161 are shown inFIG. 7 as extending through theseal 143 in opposite directions to provide shrinkage compensation in both directions, if the effect of higher pressure is expected only from a single direction, thepin members 161 need only be oriented with the top of thehead 171 of eachpin member 161 facing that direction. - In operation, when pressure is applied on the face of the
seal 143 at low temperature, the floatingpin members 161 will push theseal 143 towards the opposite wall of therecess 148 in thecasing spool 137, thereby compensating for the lost squeeze in theseal 143 due to temperature-induced shrinkage. Depending upon whether the effective pressure is greater at the upper or lower end of theseal 143, thesegmented rings seal 143 are engaged by thehead 171 of the associatedpin members 161. The segmented rings 187, 188 act as hard surfaces for thepin members 161 to act on theseal 143 and to distribute the compressive force evenly. The upper and lower segmented rings, along with the respective pair of taperedrings pin members 161, also can act as non-extrusion devices. In the embodiments having thepin members 161 alternating in opposite directions, thepin members 161 compensate for shrinkage when pressure is applied in either direction. - Various embodiments of the present invention provide several advantages. For example, in a casing hanger seal-type implementation, various embodiments reduce the surface area of the packing, and thus, reduce the amount of force necessary to energize the packing, especially when the annular area of the packing is large. Various embodiments provide improved packing ability to seal between the casing head and the casing tube when the temperature cycles from hot to cold. As the volume decreases due to shrinkage, a constant force is still being applied by the
pin members 161 to compensate for the reduced compression in the seal material (e.g., rubber) due to shrinkage. In an interference seal-type implementation, for example, various embodiments reduce the volume fill due to the floatingpin members 161, which requires less force to energize the packing. Various embodiments also provide a dependable seal function at low temperatures due to the application of a substantially constant force applied by thepin members 161 to compensate for the shrinkage factor resulting from the low temperatures. Advantageously, the various embodiments satisfy a need for elastomer seals of different configurations capable of sealing oil and gas components subject to substantial temperature variations at greater water and surface depths, by providing a more stable/constant effectiveness, a factor which can be more critical at such depths, especially at higher pressures. - In the drawings and specification, there have been disclosed at set of typical preferred embodiments of the invention, and although specific terms are employed, the terms are used in a descriptive sense only and not for purposes of limitation. The invention has been described in considerable detail with specific reference to these illustrated embodiments. It will be apparent, however, that various modifications and changes can be made within the spirit and scope of the invention as described in the foregoing specification. For example, the seal assemblies were described as circumscribing an outer surface of a casing tube. The various embodiments can work equally as well around smaller components such as, for example, shafts or other components.
Claims (24)
1. A shrinkage compensated seal assembly, comprising:
a seal;
a first compression member having a first surface for engaging a first surface of the seal and a second surface opposite the first surface;
a second compression member having a first surface for engaging a second surface of the seal and a second surface opposite the first surface; and
a plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body, the elongate body of each separate one of the plurality of pin members slidably extending through a different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member to provide for maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal.
2. A shrinkage compensated seal assembly as defined in claim 1 , wherein the head portion of each pin member has a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, wherein each head portion of each pin member of the plurality of pin members has an engagement surface positioned to engage the second surface of the first compression member when the shrinkage compensated seal assembly is operationally employed, and wherein each of the plurality of pin members maintains compressive engagement with the seal during shrinkage thereof due to a temperature change when in situ force applied to a surface of the head portion opposite the engagement surface of the head portion exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
3. A shrinkage compensated seal assembly as defined in claim 1 , wherein the plurality of pin members are oriented substantially vertically when the shrinkage compensated seal assembly is operationally employed, and wherein the first end of the elongate body and head portion connected thereto are positioned below the second end of the elongate body.
4. A shrinkage compensated seal assembly as defined in claim 3 , wherein the seal is an annular seal, wherein the first and second compression members are or form corresponding first and second annular compression plates, wherein the annular seal has a first engagement surface oriented to engage an outer surface of a casing extending through a bore of a casing head and a second engagement surface opposite the first engagement surface and oriented to engage inner surface portions of the casing head circumscribing the bore extending therethrough, and wherein the plurality of pin members are positioned to be actuated to compress the annular seal responsive to pressure in an annulus between the outer surface of the casing and an inner surface of the casing head.
5. A shrinkage compensated seal assembly as defined in claim 1 , wherein the head portion of the elongate body of each pin member has a maximum axial length, and wherein each respective head portion is positioned within a recess extending into a casing hanger slip bowl positioned in contact with the second surface of the first compression member, each recess having an axial length substantially exceeding the maximum axial length of the respective head portion positioned therein to provide for slidable movement thereof.
6. A shrinkage compensated seal assembly as defined in claim 5 , further comprising:
a plurality of clamping members each having elongate bodies extending through a corresponding different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member, said plurality of sets of apertures being different than those receiving the plurality of pin members, each of the plurality of clamping members engaging the second surface of the first compression member and fixedly connected to an upper surface of the casing hanger slip bowl to thereby maintain the seal in a constant state of compression at given pressure and given temperature.
7. A shrinkage compensated seal assembly as defined in claim 1 , further comprising:
a plurality of fasteners each separately connected to an outer surface portion of the second end of the elongate body of a different one of the plurality of pin members.
8. A shrinkage compensated seal assembly as defined in claim 7 , wherein each fastener includes an engagement surface positioned to engage the second surface of the second compression member when the shrinkage compensated seal assembly is operationally employed and when a sum of force applied to a surface opposite the engagement surface of the respective fastener and the force applied to the surface of the second end of the elongate body of the respective pin member exceeds the force applied to the surface of the head portion of the respective pin member opposite the engagement surface thereof.
9. A shrinkage compensated seal assembly as defined in claim 1 , wherein the seal is an annular seal, wherein the annular seal has a first engagement surface oriented to engage an outer surface of a casing extending through a bore of a casing head and a second engagement surface opposite the first engagement surface and oriented to engage inner surface portions of the casing head circumscribing the bore extending therethrough, wherein the annular seal is positioned within an annular recess extending into the inner surface of the casing head, wherein an axial length of each pin member is smaller than an axial length of a portion of the recess adjacent thereto when positioned therein, and wherein the plurality of pin members are positioned to be actuated to compress the annular seal responsive to pressure between the outer surface of the casing and inner diameter portions of the casing head.
10. A shrinkage compensated seal assembly as defined in claim 9 , wherein the pin members are a first plurality of pin members, wherein the plurality of sets of apertures is a first plurality of sets of apertures, the seal assembly further comprising:
a second plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body, the head portion of each pin member having a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, each head portion of each pin member of the second plurality of pin members having an engagement surface positioned to engage the second surface of the second compression member when the shrinkage compensated seal assembly is operationally employed,
the elongate body of each separate pin member of the second plurality of pin members slidably extending through a different one of a second plurality of sets of apertures in the first annular compression member, the annular seal, and the second compression member to provide for maintaining a substantially constant pressure on the annular seal at given pressure under varying temperature conditions when force applied to a surface opposite the engagement surface of the head portion of each respective pin member of the second plurality of pin members exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
11. A shrinkage compensated seal assembly for a casing head member, comprising:
an annular seal having a first engagement surface, a second engagement surface, a first compression member engagement surface, and a second compression member engagement surface, the first engagement surface oriented to engage an outer surface of a tubular member positioned within a bore of a casing head, the second engagement surface oriented to engage inner surface portions of the casing head circumscribing a bore extending therethrough, the annular seal varying in volume size as a result of changes in temperature at given pressures;
a first annular compression member having a first surface for engaging the first compression member engagement surface of the annular seal and a second surface opposite the first surface;
a second annular compression member having a first surface for engaging the second compression member engagement surface of the annular seal and a second surface opposite the first surface;
a plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body;
the elongate body of each separate one of the plurality of pin members slidably extending through a different one of a plurality of sets of apertures in the first annular compression member, the annular seal, and the second annular compression member to provide for maintaining a substantially constant pressure on the annular seal at given pressure under varying temperature conditions that result in variations in volume size of the annular seal.
12. A shrinkage compensated seal assembly as defined in claim 11 , wherein the head portion of each pin member has a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, wherein each head portion of each pin member of the plurality of pin members has an engagement surface positioned to engage the second surface of the first compression member when the shrinkage compensated seal assembly is operationally employed, and wherein each of the plurality of pin members maintains compressive engagement with the annular seal during shrinkage thereof due to a temperature change when in situ force applied to a surface of the head portion opposite the engagement surface of the head portion exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
13. A shrinkage compensated seal assembly as defined in claim 12 , wherein the plurality of pin members are oriented substantially vertically when the shrinkage compensated seal assembly is operationally employed, and wherein the first end of the elongate body and head portion connected thereto are positioned below the second end of the elongate body.
14. A shrinkage compensated seal assembly as defined in claim 13 , wherein the tubular member is a casing extending through the bore of the casing head, and wherein the plurality of pin members are positioned to be actuated to compress the annular seal responsive to pressure in an annulus between the outer surface of the casing and an inner surface of the casing head.
15. A shrinkage compensated seal assembly as defined in claim 11 , wherein the head portion of the elongate body of each pin member has a maximum axial length, and wherein each respective head portion is positioned within a recess extending into a casing hanger slip bowl positioned in contact with the second surface of the first annular compression member, each recess having an axial length substantially exceeding the maximum axial length of the respective head portion positioned therein to provide for slidable movement therein.
16. A shrinkage compensated seal assembly as defined in claim 15 , further comprising:
a plurality of clamping members each having elongate bodies extending through a corresponding different one of a plurality of sets of apertures in the first annular compression member, the annular seal, and the second compression member, said plurality of sets of apertures being different than those receiving the plurality of pin members, each of the plurality of clamping members engaging the second surface of the first annular compression member and fixedly connected to an upper surface of a casing hanger slip bowl to thereby maintain the annular seal in a constant state of compression at given pressure and given temperature.
17. A shrinkage compensated seal assembly as defined in claim 11 , further comprising:
a plurality of fasteners each separately connected to an outer surface portion of the second end of the elongate body of a different one of the plurality of pin members.
18. A shrinkage compensated seal assembly as defined in claim 17 , wherein each fastener includes an engagement surface positioned to engage the second surface of the second compression member when the shrinkage compensated seal assembly is operationally employed and when a sum of force applied to a surface opposite the engagement surface of the respective fastener and the force applied to the surface of the second end of the elongate body of the respective pin member exceeds the force applied to the surface of the head portion of the respective pin member opposite the engagement surface thereof.
19. A shrinkage compensated seal assembly as defined in claim 13 , wherein the tubular member is a casing extending through the bore of the casing head, wherein the annular seal is positioned within an annular recess extending into the inner surface of the casing head, wherein an axial length of each pin member is smaller than an axial length of a portion of the recess adjacent thereto when positioned therein, and wherein the plurality of pin members are positioned to be actuated to compress the annular seal responsive to pressure between the outer surface of the casing and inner diameter portions of the casing head.
20. A shrinkage compensated seal assembly as defined in claim 19 , wherein the plurality of pin members are a first plurality of pin members, wherein plurality of sets of apertures is a first plurality of sets of apertures, and wherein each of the plurality of pin members maintains compressive engagement with the annular seal during shrinkage thereof due to a temperature change when the in situ force applied to the surface of the head portion opposite the engagement surface of the head portion of the respective pin member exceeds force applied to the end surface of the second end of the elongate body of the respective pin member, the seal assembly further comprising:
a second plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body, the head portion of each pin member of the second plurality of pin members having a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, each head portion of each pin member of the second plurality of pin members having an engagement surface positioned to engage the second surface of the second compression member when the shrinkage compensated seal assembly is operationally employed,
the elongate body of each separate pin member of the second plurality of pin members slidably extending through a different one of a second plurality of sets of apertures in the first annular compression member, the annular seal, and the second compression member to provide for maintaining a substantially constant pressure on the annular seal at given pressure under varying temperature conditions that result in variations in volume size of the annular seal when in situ force applied to a surface of the head portion opposite the engagement surface of the head portion of each respective pin member of the second plurality of pin members exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
21. A method of compensating for shrinkage of a seal for a casing head member due to temperature variations at given pressures, the method comprising the steps of:
providing a seal assembly comprising a seal, a first compression member having a first surface for engaging a first surface of the seal and a second surface opposite the first surface, a second compression member having a first surface for engaging a second surface of the seal and a second surface opposite the first surface, and a plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body;
slidably extending the elongate body of each separate one of the plurality of pin members through a corresponding different one of a plurality of sets of apertures in the first compression member, the seal, and the second compression member; and
maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal.
22. A method as defined in claim 21 , wherein the head portion of each pin member has a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, wherein each head portion of each pin member of the plurality of pin members has an engagement surface positioned to engage the second surface of the first compression member when the seal assembly is operationally employed, and wherein the step of maintaining a substantially constant pressure on the seal includes each of the plurality of pin members maintaining compressive engagement with the seal during shrinkage thereof due to a temperature change when in situ force applied to a surface of the head portion opposite the engagement surface of the head portion of the respective pin member exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
23. A method as defined in claim 21 , wherein the plurality of pin members are oriented substantially vertically when the seal assembly is operationally employed, wherein the first end of the elongate body and head portion connected thereto of each pin member are positioned below the second end of the elongate body, wherein each of the plurality of pin members includes or carries a fastener connected to an outer surface portion of the second end of the elongate body, the method further comprising the step of:
engaging the second surface of the second compression member with an engagement surface of each fastener when a sum of force applied to a surface opposite the engagement surface of the respective fastener and the in situ force applied to the surface of the second end of the elongate body of the respective pin member exceeds the force applied to the surface of the head portion of the respective pin member opposite the engagement surface thereof, thereby maintaining a substantially constant pressure on the seal by each of the plurality of fasteners at given pressure under varying temperature conditions.
24. A method as defined in claim 21 , wherein the plurality of pin members is a first plurality of pin members, and wherein the step of maintaining a substantially constant pressure on the seal is performed when in situ force applied to a surface opposite the engagement surface of the head portion of the respective pin member exceeds force applied to an end surface of the second end of the elongate body of the respective pin member, each head portion of each pin member of the first plurality of pin members having the engagement surface positioned to engage the second surface of the second compression member, the method further comprising the steps of:
providing a second plurality of pin members each having an elongate body including a first end, a second end opposite the first end, and a head portion connected to the first end of the elongate body, the head portion of each pin member having a diameter along a radial axis thereof substantially larger than a diameter along the radial axis of the elongate body, each head portion of each pin member of the second plurality of pin members having an engagement surface positioned to engage the second surface of the first compression member;
slidably extending the elongate body of each separate pin member of the second plurality of pin members through a corresponding different one of a second plurality of sets of apertures in the first compression member, the seal, and the second compression member; and
maintaining a substantially constant pressure on the seal at given pressure under varying temperature conditions that result in variations in volume size of the seal, by each of the second plurality of pin members when in situ force applied to a surface opposite the engagement surface of the head portion of the respective pin member exceeds force applied to an end surface of the second end of the elongate body of the respective pin member.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/674,481 US20140131954A1 (en) | 2012-11-12 | 2012-11-12 | Shrinkage compensated seal assembly and related methods |
PCT/US2013/067733 WO2014074387A1 (en) | 2012-11-12 | 2013-10-31 | Shrinkage compensated seal assembly and related methods |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/674,481 US20140131954A1 (en) | 2012-11-12 | 2012-11-12 | Shrinkage compensated seal assembly and related methods |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140131954A1 true US20140131954A1 (en) | 2014-05-15 |
Family
ID=49641844
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/674,481 Abandoned US20140131954A1 (en) | 2012-11-12 | 2012-11-12 | Shrinkage compensated seal assembly and related methods |
Country Status (2)
Country | Link |
---|---|
US (1) | US20140131954A1 (en) |
WO (1) | WO2014074387A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9617820B2 (en) * | 2015-07-08 | 2017-04-11 | Ge Oil & Gas Pressure Control Lp | Flexible emergency hanger and method of installation |
CN107060654A (en) * | 2016-08-01 | 2017-08-18 | 中嵘能源科技集团有限公司 | A kind of heat-insulated gas injection tube column of anticorrosion |
US10392914B2 (en) | 2016-03-28 | 2019-08-27 | Ge Oil & Gas Pressure Control Lp | Systems and methods for fracturing a multiple well pad |
US10436368B2 (en) | 2016-03-18 | 2019-10-08 | Ge Oil & Gas Pressure Control Lp | Trunk line manifold system |
WO2024006202A1 (en) * | 2022-06-30 | 2024-01-04 | Baker Hughes Oilfield Operations Llc | Reinforced compression plate split for slip hanger |
Citations (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1725836A (en) * | 1925-06-12 | 1929-08-27 | Frederick C Langenberg | Packing for high-pressure joints |
US3215442A (en) * | 1962-04-27 | 1965-11-02 | Parker Hannifin Corp | Fluid seal |
US3302953A (en) * | 1963-02-25 | 1967-02-07 | Clarence O Glasgow | Gasket ring and conduit coupling |
US3492009A (en) * | 1967-05-17 | 1970-01-27 | Boris Ivanovich Beresnev | Device for packing gaps,mainly in high pressure apparatus |
US3573870A (en) * | 1968-11-05 | 1971-04-06 | United Aircraft Prod | Retaining ring for sealing assembly |
US3578346A (en) * | 1969-01-29 | 1971-05-11 | Parker Hannifin Corp | Sealed joint and gasket therefor |
US3656769A (en) * | 1968-09-30 | 1972-04-18 | Parker Hannifin Corp | Fluid sealing joint and gasket |
US4756561A (en) * | 1985-02-14 | 1988-07-12 | Mazda Motor Corporation | Sealing gasket |
US4836158A (en) * | 1988-03-28 | 1989-06-06 | Custom Chrome, Inc. | Motorcycle gasket and assembly |
US4848777A (en) * | 1987-09-18 | 1989-07-18 | Fmc Corporation | Pressure energized/pressure intensified casing seal |
US4884723A (en) * | 1987-04-23 | 1989-12-05 | Acf Industries, Incorporated | Hard gasket for retrofit installation on hopper outlet/hopper gasket outlet |
US5054793A (en) * | 1988-10-11 | 1991-10-08 | Brunswick Corporation | Resilient gasket with spacers |
US5333919A (en) * | 1993-09-02 | 1994-08-02 | Ron Nerenberg | Gasket for a pipe joint |
US5518280A (en) * | 1995-04-07 | 1996-05-21 | Mann; Dennis L. | Seal for an exhaust system |
US5558344A (en) * | 1993-11-23 | 1996-09-24 | Dana Corporation | Exhaust pipe flange gasket |
US5904354A (en) * | 1996-09-13 | 1999-05-18 | Halliburton Energy Services, Inc. | Mechanically energized element |
US5944322A (en) * | 1997-02-11 | 1999-08-31 | Parker-Hannifin Corporation | Combination graphite foil and metal sealing gasket |
US5947533A (en) * | 1996-08-02 | 1999-09-07 | Fisher; Ronald K. | Gasket assembly with elastomer expansion area |
US5955020A (en) * | 1996-04-26 | 1999-09-21 | Global Corrosion | Apparatus and method for injecting corrosion control compounds into pipe flanges and the like |
US6015152A (en) * | 1997-01-03 | 2000-01-18 | Eg&G Pressure Science, Inc. | Seal retainer having an indicator |
US6039319A (en) * | 1997-02-24 | 2000-03-21 | Swagelok Company | Hygienic fitting with thermal expansion area for gasket |
US6236128B1 (en) * | 1999-10-28 | 2001-05-22 | Siemens Westinghouse Power Corporation | Radial lead spanner nut assembly with integral seals for hydrogen-cooled power generators and associated methods |
US6340162B1 (en) * | 1999-08-13 | 2002-01-22 | Trw Inc. | Seal for integral power steering gear |
US6402159B1 (en) * | 1997-04-08 | 2002-06-11 | Gary A. Kohn | Dielectric gasket |
US6460859B1 (en) * | 2000-04-12 | 2002-10-08 | Parker-Hannifin Corporation | Resilient elastomer and metal retainer gasket for sealing between curved surfaces |
US6502829B2 (en) * | 2000-03-24 | 2003-01-07 | Nippon Gasket Co., Ltd. | Gasket-squeeze construction |
US6565124B2 (en) * | 1996-05-17 | 2003-05-20 | Beckswift Limited | Pipe joint and a gasket therefor |
US6869081B1 (en) * | 2002-12-20 | 2005-03-22 | Jjenco, Inc. | Constant seating stress gasket system |
US7520511B2 (en) * | 2005-07-04 | 2009-04-21 | Nichias Corporation | O-ring and clamp-type joint for vacuum apparatus |
US7722053B2 (en) * | 2005-07-04 | 2010-05-25 | Nichias Corporation | Outer ring and clamp-type joint for vacuum apparatus |
US20120187632A1 (en) * | 2009-09-14 | 2012-07-26 | Max White | Packer with non-extrusion ring |
US20140062025A1 (en) * | 2012-08-28 | 2014-03-06 | Vetco Gray Inc. | Seal Assembly For A Casing Hanger |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0435640Y2 (en) * | 1985-11-22 | 1992-08-24 | ||
TW201341B (en) * | 1992-08-07 | 1993-03-01 | Raychem Corp | Low thermal expansion seals |
US5518257A (en) * | 1993-08-23 | 1996-05-21 | Corrosion Control Corp. | Seal device for flow line applications |
US8191933B2 (en) * | 2008-07-16 | 2012-06-05 | General Electric Company | Extrusion resistant gasket face seal |
US20120139188A1 (en) * | 2010-12-02 | 2012-06-07 | Dana Automotive Systems Group, Llc | Exhaust Manifold Gasket |
CN202597709U (en) * | 2012-04-13 | 2012-12-12 | 中冶华天南京工程技术有限公司 | Expansion and contraction compensation mechanism for sealing rubber belt of cylindrical thin oil sealed chamber |
-
2012
- 2012-11-12 US US13/674,481 patent/US20140131954A1/en not_active Abandoned
-
2013
- 2013-10-31 WO PCT/US2013/067733 patent/WO2014074387A1/en active Application Filing
Patent Citations (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1725836A (en) * | 1925-06-12 | 1929-08-27 | Frederick C Langenberg | Packing for high-pressure joints |
US3215442A (en) * | 1962-04-27 | 1965-11-02 | Parker Hannifin Corp | Fluid seal |
US3302953A (en) * | 1963-02-25 | 1967-02-07 | Clarence O Glasgow | Gasket ring and conduit coupling |
US3492009A (en) * | 1967-05-17 | 1970-01-27 | Boris Ivanovich Beresnev | Device for packing gaps,mainly in high pressure apparatus |
US3656769A (en) * | 1968-09-30 | 1972-04-18 | Parker Hannifin Corp | Fluid sealing joint and gasket |
US3573870A (en) * | 1968-11-05 | 1971-04-06 | United Aircraft Prod | Retaining ring for sealing assembly |
US3578346A (en) * | 1969-01-29 | 1971-05-11 | Parker Hannifin Corp | Sealed joint and gasket therefor |
US4756561A (en) * | 1985-02-14 | 1988-07-12 | Mazda Motor Corporation | Sealing gasket |
US4884723A (en) * | 1987-04-23 | 1989-12-05 | Acf Industries, Incorporated | Hard gasket for retrofit installation on hopper outlet/hopper gasket outlet |
US4848777A (en) * | 1987-09-18 | 1989-07-18 | Fmc Corporation | Pressure energized/pressure intensified casing seal |
US4836158A (en) * | 1988-03-28 | 1989-06-06 | Custom Chrome, Inc. | Motorcycle gasket and assembly |
US5054793A (en) * | 1988-10-11 | 1991-10-08 | Brunswick Corporation | Resilient gasket with spacers |
US5333919A (en) * | 1993-09-02 | 1994-08-02 | Ron Nerenberg | Gasket for a pipe joint |
US5558344A (en) * | 1993-11-23 | 1996-09-24 | Dana Corporation | Exhaust pipe flange gasket |
US5518280A (en) * | 1995-04-07 | 1996-05-21 | Mann; Dennis L. | Seal for an exhaust system |
US5955020A (en) * | 1996-04-26 | 1999-09-21 | Global Corrosion | Apparatus and method for injecting corrosion control compounds into pipe flanges and the like |
US6565124B2 (en) * | 1996-05-17 | 2003-05-20 | Beckswift Limited | Pipe joint and a gasket therefor |
US5947533A (en) * | 1996-08-02 | 1999-09-07 | Fisher; Ronald K. | Gasket assembly with elastomer expansion area |
US5904354A (en) * | 1996-09-13 | 1999-05-18 | Halliburton Energy Services, Inc. | Mechanically energized element |
US6015152A (en) * | 1997-01-03 | 2000-01-18 | Eg&G Pressure Science, Inc. | Seal retainer having an indicator |
US5944322A (en) * | 1997-02-11 | 1999-08-31 | Parker-Hannifin Corporation | Combination graphite foil and metal sealing gasket |
US6039319A (en) * | 1997-02-24 | 2000-03-21 | Swagelok Company | Hygienic fitting with thermal expansion area for gasket |
US6402159B1 (en) * | 1997-04-08 | 2002-06-11 | Gary A. Kohn | Dielectric gasket |
US6340162B1 (en) * | 1999-08-13 | 2002-01-22 | Trw Inc. | Seal for integral power steering gear |
US6236128B1 (en) * | 1999-10-28 | 2001-05-22 | Siemens Westinghouse Power Corporation | Radial lead spanner nut assembly with integral seals for hydrogen-cooled power generators and associated methods |
US6502829B2 (en) * | 2000-03-24 | 2003-01-07 | Nippon Gasket Co., Ltd. | Gasket-squeeze construction |
US6460859B1 (en) * | 2000-04-12 | 2002-10-08 | Parker-Hannifin Corporation | Resilient elastomer and metal retainer gasket for sealing between curved surfaces |
US6869081B1 (en) * | 2002-12-20 | 2005-03-22 | Jjenco, Inc. | Constant seating stress gasket system |
US7520511B2 (en) * | 2005-07-04 | 2009-04-21 | Nichias Corporation | O-ring and clamp-type joint for vacuum apparatus |
US7722053B2 (en) * | 2005-07-04 | 2010-05-25 | Nichias Corporation | Outer ring and clamp-type joint for vacuum apparatus |
US20120187632A1 (en) * | 2009-09-14 | 2012-07-26 | Max White | Packer with non-extrusion ring |
US20140062025A1 (en) * | 2012-08-28 | 2014-03-06 | Vetco Gray Inc. | Seal Assembly For A Casing Hanger |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9617820B2 (en) * | 2015-07-08 | 2017-04-11 | Ge Oil & Gas Pressure Control Lp | Flexible emergency hanger and method of installation |
US10436368B2 (en) | 2016-03-18 | 2019-10-08 | Ge Oil & Gas Pressure Control Lp | Trunk line manifold system |
US10895340B2 (en) | 2016-03-18 | 2021-01-19 | Vault Pressure Control Llc | Trunk line manifold system |
US10392914B2 (en) | 2016-03-28 | 2019-08-27 | Ge Oil & Gas Pressure Control Lp | Systems and methods for fracturing a multiple well pad |
CN107060654A (en) * | 2016-08-01 | 2017-08-18 | 中嵘能源科技集团有限公司 | A kind of heat-insulated gas injection tube column of anticorrosion |
WO2024006202A1 (en) * | 2022-06-30 | 2024-01-04 | Baker Hughes Oilfield Operations Llc | Reinforced compression plate split for slip hanger |
Also Published As
Publication number | Publication date |
---|---|
WO2014074387A1 (en) | 2014-05-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CA2579111C (en) | Spring/seal element | |
US4455040A (en) | High-pressure wellhead seal | |
US20140131954A1 (en) | Shrinkage compensated seal assembly and related methods | |
US8622142B2 (en) | Sealing wellhead members with bi-metallic annular seal | |
US9243715B2 (en) | Seal assembly | |
AU2012232952B2 (en) | Damage tolerant casing hanger seal | |
US9249797B2 (en) | Plunger packing with wedge seal having extrusion recess | |
US5129660A (en) | Seal assembly for a well housing hanger structure | |
US10214986B2 (en) | Variable ram for a blowout preventer and an associated method thereof | |
US11492871B2 (en) | Buckle prevention ring | |
US2791278A (en) | Packing structures for well devices | |
CA1196857A (en) | Packoff and seal ring assembly | |
US9556700B2 (en) | Downhole sealing assembly | |
US11391108B2 (en) | Shear ram for a blowout preventer | |
US20080156501A1 (en) | Non-backed-up packing element system | |
US8210542B1 (en) | Plunger seal ring | |
CN104769211A (en) | Seal assembly for a casing hanger | |
US20030209857A1 (en) | Metal end cap seal with o-ring | |
RU2712865C1 (en) | Non-metallic sealing element | |
US4613159A (en) | Pressure-assisted dynamic seal apparatus | |
US3210087A (en) | Radially contained packing having radially inner and outer sealing rings | |
US4583746A (en) | Method and apparatus for sealing between two concentric members | |
CN211448607U (en) | Quick-setting expanding hydraulic packer for petroleum machinery | |
RU2698348C1 (en) | Packing unit of packer | |
RU2513937C1 (en) | Method of sealing by restricted gasket |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: VETCO GRAY INC., TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KOLEILAT, BASHIR MOHAMMAD;OLVERA, ALFRED;AL-AKKAD, AMAN;AND OTHERS;SIGNING DATES FROM 20121022 TO 20121031;REEL/FRAME:029281/0436 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |