US20140131954A1 - Shrinkage compensated seal assembly and related methods - Google Patents

Shrinkage compensated seal assembly and related methods Download PDF

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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
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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
Application number
US13/674,481
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English (en)
Inventor
Bashir Mohammad Koleilat
Alfred Olvera
Aman Al-Akkad
Jim Hwang
Saurabh KAJARIA
Gajanan Hegde
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vetco Gray LLC
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Vetco Gray LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Vetco Gray LLC filed Critical Vetco Gray LLC
Priority to US13/674,481 priority Critical patent/US20140131954A1/en
Assigned to VETCO GRAY INC. reassignment VETCO GRAY INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AL-AKKAD, Aman, HEGDE, Gajanan, KAJARIA, SAURABH, KOLEILAT, BASHIR MOHAMMAD, HWANG, JIM, OLVERA, ALFRED
Priority to PCT/US2013/067733 priority patent/WO2014074387A1/fr
Publication of US20140131954A1 publication Critical patent/US20140131954A1/en
Abandoned legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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

Definitions

  • 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.
  • Casing hanger seal assemblies 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.
  • 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.
  • volume fill and squeeze can play a major role in the design of the seal.
  • shrinkage becomes an issue to the amount of squeeze in the seal.
  • 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.
  • the floating pin members when used, for example, in a high temperature pack off, 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.
  • the floating pin members when used, for example, in interference elastomer seal applications, 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.
  • 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.
  • 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.
  • 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.
  • some of pin members are oriented opposite with other of the members to provide a bi-directional capability.
  • each pin member is positioned within a recess of a casing hanger slip bowl.
  • 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.
  • the first compression member is a compression plate and the second compression member is a bottom plate landed upon the slip bowl.
  • the first compression member is a first split ring
  • the second compression member is a second split ring
  • 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.
  • a method of compensating for shrinkage of a seal for a casing head member due to temperature variations at given pressures 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.
  • 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.
  • 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.
  • 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.
  • 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 in FIG. 1 according to an embodiment of the present invention.
  • FIG. 3 is a sectional view of a floating pin shown in FIG. 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.
  • various embodiments of the present invention provide compensation for the behavior of the seals at these varying temperatures.
  • 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.
  • a shrinkage compensated casing hanger seal assembly 30 circumscribes an outer surface 31 of a casing tube 33 and is positioned between the outer surface 31 of the casing tube 33 and an inner surface 35 of a casing head 37 .
  • the seal assembly 30 is bolted to the upper portion of a casing hanger slip bowl 41 .
  • the seal assembly 30 includes a seal 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.
  • the inner diameter surface 45 of the seal 43 compressibly engages against the outer surface 31 of the casing tube 33
  • the outer diameter surface 47 compressibly engages an inner surface 35 of the casing head 37 .
  • the seal assembly 30 also includes a compression plate 51 positioned atop the seal 43 and a bottom plate 53 positioned adjacent to or integral with the slip bowl 41 .
  • a set of clamping members 55 each include an elongate body 57 that extends through a set of coaxially aligned apertures (not shown) in the compression plate 51 , seal 43 , and bottom plate 53 .
  • the clamping members 55 rigidly connect the seal assembly 30 to the slip bowl 41 .
  • the lower end of each clamping member 55 either independently connects to the upper portion of the slip bowl 41 , or in conjunction with a lower end connector (not shown), engages an upper panel of the slip bowl 41 .
  • a washer stack and/or additional connector, individually or collectively upper connector 59 is fixedly connected to the upper end of each clamping member 55 to securely hold the compression plate 51 and bottom plate 53 in compressive engagement with seal 43 to put the seal 43 in a state of compression.
  • the seal assembly 30 also includes a set of floating pin members 61 each having an elongate body 63 positioned to slidably extend through a set of coaxially aligned apertures 65 , 67 , 69 , in the compression plate 51 , seal 43 , and bottom plate 53 , respectively.
  • each pin member 61 includes a head 71 which has a larger diameter than the elongate body 63 and larger diameter than that of at least the coaxial aperture 69 extending through the bottom plate 53 . It also typically has a diameter that is larger than that of the coaxial apertures 65 and 67 .
  • the head 71 is located within a recess 73 extending into the top of the slip bowl 41 . The depth of the recess 73 is substantially larger than the longitudinal thickness of the head 71 to allow the pin member 61 to slide up and down within the set of coaxial apertures 65 , 67 , 69 .
  • each pin member 61 includes a nut 75 or other connector having a diameter that is larger than the aperture 65 extending through the compression plate 51 .
  • the tail end portion of each pin member 61 receiving the nut 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.
  • each pin member 61 is sufficiently long so that the nut 75 can be connected spaced apart at a sufficient distance from the head 71 of the pin members 61 to allow substantial bidirectional movement of the pin member 61 .
  • Each pin member 61 moves upward when the annulus pressure between the casing head 37 and the outer surface 31 of the casing 33 provides net forces on the head 71 of the pin member 61 which exceed those provided on the upper surfaces of the nut 75 and pin member body 63 . This results in the head 71 of the pin member 61 engaging the lower surface of the bottom plate 53 , and correspondingly, the seal 43 being compressed against the compression plate 51 and lower surface of upper fastener 59 .
  • the pin member 61 moves downward when the forces acting upon the upper surfaces of the nut 75 and pin member body 63 exceed those acting upon the lower facing surface of the head 71 of the pin member 61 .
  • the pin members 61 may not include the nut 75 .
  • the forces applied to the head 71 of the pin member 61 will always control. If the pressure associated with the tail of the pin member 61 instead exerts a greater force on the tail surface than that exerted on the head 71 , the associated recess 73 in the slip bowl 41 will prevent the respective pin member 61 from being blown out of the seal assembly 30 .
  • Non-extrusion rings 77 , 79 are located in the plates 51 , 53 , or alternatively, in the upper and lower surfaces of the seal 43 coaxial with aperture 67 .
  • the floating pin members 61 are extended through the compression plate 51 , seal 43 , and bottom plate 53 (i.e., slab packing) prior to installing the seal assembly 30 on the casing hanger slip bowl 41 .
  • the pin members 61 are retained from both ends of the packing and are allowed to float in either direction.
  • a net force is exerted by the pin members 61 that is equivalent to the pressure applied times the sealed area of each pin member 61 . That force will act against the connectors of the clamping members 55 which is retaining the seal assembly 30 to the slip bowl 41 , while the casing tube weight holds the slip bowl 41 in place. This force will remain substantially constant if the pressure remains substantially constant.
  • a first pair of wire mesh or junk compression/anti-extrusion rings 101 configured to circumscribe the outer surface of the casing tube 33 are received in a corresponding pair of recesses 103 extending into the inner surface of the seal 43 .
  • a second pair of wire mesh 105 circumscribe the seal 43 ′ and extend into a corresponding pair of recesses 107 in the outer surface of the seal 43 ′.
  • the second pair of wire mesh 105 are configured to fit along the outer surface of the seal 43 ′ against the inner diameter of the casing head 37 .
  • the illustrated pin members 61 ′ are shown to have a shorter elongate body 63 ′.
  • each pin member 61 ′ moves upward when the pressure between the casing head 37 and the outer surface 31 of the casing tube 33 provides net forces on the head 71 ′ of the pin member 61 ′, which exceed those provided on the upper surfaces of the pin body 63 ′. This results in the seal 43 ′ being compressed between the plates 51 , 53 . If, however, the forces acting upon the upper surfaces of the pin member body 63 ′ exceed those acting upon the lower facing surface of the head 71 ′ of the pin member 61 ′, the pin member 61 ′ will move downward until hitting the bottom of the recess 73 in the slip bowl 41 .
  • the floating pin members 61 ′ are extended through the compression plate 51 , seal 43 ′, and bottom plate 53 (slab packing) and are assembled into the wire mesh 101 , 105 , prior to installing the seal assembly 30 ′ on the casing hanger slip bowl 41 .
  • the function With respect to conditions where the pressure is higher on the underside of the pin members 61 ′, the function remains the same as that described with respect to pin members 61 ( FIG. 3 ).
  • a seal assembly 30 ′′ includes a compression plate 51 ′ positioned atop a seal 43 ′′ and a bottom plate 53 ′ landing upon a shoulder 111 circumscribed by a coiled spring 113 .
  • a set of clamping members each include an elongate body that extends through a set of coaxially aligned apertures (not shown) in the compression plate 51 ′, seal 43 ′′, and bottom plate 53 ′.
  • An outer recess 115 extending into outer diameter portions of the compression plate 51 ′ receive the tail end portion of an member 61 and fastener 75 , or alternatively, the head portion 71 , depending upon the configuration.
  • An outer recess 73 ′ extends into lower surface portions of the bottom plate 53 ′ to receive a ahead 71 of the pin member 61 , or alternatively, the tail end portion and fastener 75 , depending upon the configuration.
  • the seal 43 ′′ can include a plurality of recesses 117 , 118 , and 119 , 120 extending into upper-facing and lower-facing surfaces, respectively.
  • a first non-extrusion ring recess 121 having a camber angle (beveled cut) extends between the inner diameter surface and lower facing surface of the compression plate 51 ′ to receive a first non-extrusion ring 123 .
  • a second recess 125 having an oppositely oriented camber angle (beveled cut) extends between the inner diameter surface and upper facing surface of the bottom plate 53 ′ to receive a second non-extrusion ring 127 to prevent extrusion of the seal 43 ′′, or seal 43 , 43 ′, depending upon the respective application of the non-extrusion rings.
  • extrusion rings 123 , 127 are “PEEK” or other hard ATL non-extrusion rings.
  • compression plate 51 , 51 ′, seal 43 , 43 ′, 43 ′′, and bottom plate 53 , 53 ′, and non-extrusion rings 123 , 127 are within the scope of the present invention.
  • recesses 118 , 119 can receive a set of oppositely oriented non-extrusion rings 128 , 129 .
  • FIG. 6 illustrates a pair of a shrinkage compensated interference elastomer seal assemblies 130 employed as a casing head seal within a casing head (spool) 137 according to an exemplary configuration.
  • Each seal assembly 130 circumscribes an outer surface 31 of a casing tube 33 and is positioned between the outer surface 31 of the casing tube 33 and an inner surface 135 of the casing spool 137 .
  • each seal assembly 130 is positioned within an annular recess 148 .
  • the seal assembly 130 includes a seal 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.
  • the inner diameter surface of the seal 143 has a convex portion 181 typically referred to as a bulge or bump, which compressibly engages against the outer surface 31 of the casing tube 33 .
  • the outer diameter surface typically has a concave portion 183 between a pair of engagement portions 185 which engage the inner surface of the casing spool 137 .
  • the seal assembly 130 includes a pair of segmented rings, e.g., PEEK or other hard ATL rings 187 , 188 , positioned above and below seal 143 and a pair of beveled non-extrusion rings 189 , 190 , positioned in complementing annular recesses in each of the segmented rings 187 , 188 .
  • segmented rings e.g., PEEK or other hard ATL rings 187 , 188
  • the upper and lower rings 187 , 188 are segmented and include a beveled cut 191 and a scarf cut at each end of the segment to facilitate placement within the recess 148 in the casing spool 137 at installation.
  • each end of the respective ring segments include the scarf cut to provide an overlapping connection between the respective segments.
  • one or more threaded rings 193 (only one shown) is/are utilized to form the recess 148 .
  • a coiled spring 195 is molded with the seal 143 on the casing surface-side of the seal 143 to prevent extrusion of the seal 143 between the outer surface 31 of the casing tube 33 and the segmented rings 187 , 188 .
  • the seal assembly 130 also includes a set of floating pin members 161 spaced apart along the circumference of the seal 143 , typically in alternating directions (see FIG. 7 ).
  • Each pin member 161 has an elongate body 163 positioned to slidably extend through a set of coaxially aligned apertures/recesses 201 , 202 , 203 , in the upper segmented ring 187 , the seal 143 , and the lower segmented ring 188 , respectively.
  • Each pin member 161 also includes a head 171 , typically round, which has a larger diameter than the elongate body 163 and larger than at least the coaxial aperture extending through the upper or lower segmented ring, respectively, depending upon the orientation of the pin members 161 .
  • the head 171 is located within a recess 211 extending into the upper or lower segmented ring 187 , 188 , depending upon whether the pin member 161 is oriented facing upward or facing down.
  • the depth of the recess 211 is substantially the same as the thickness of the head 171 .
  • the longitudinal length L 1 of the seal assembly 130 is less than the longitudinal length L 2 , e.g., typically approximately 1.5′′ in this application, and the combined length of the pin 161 and head 171 is typically slightly smaller than that of L 1 , to allow the pin 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 the seal 143 .
  • the difference between the lengths L 1 and L 2 are sufficiently small to prevent the pin members 161 from extracting through either of the apertures/recesses 201 , 203 , in the upper or lower segmented rings 87 , 88 , respectively.
  • the pin members 161 function to compensate for shrinkage of the seal 143 , preventing leaking of the seal 143 as a result of a temperature-induced volume reduction. Also, the volume of the pin member 161 that penetrates the, e.g., elastomer seal material, as a result of the apertures in the seal 143 , will reduce the volume of material needed to construct the seal 143 , and thus, will further reduce the amount of expected shrinkage.
  • pin members 161 are shown in FIG. 7 as extending through the seal 143 in opposite directions to provide shrinkage compensation in both directions, if the effect of higher pressure is expected only from a single direction, the pin members 161 need only be oriented with the top of the head 171 of each pin member 161 facing that direction.
  • the floating pin members 161 In operation, when pressure is applied on the face of the seal 143 at low temperature, the floating pin members 161 will push the seal 143 towards the opposite wall of the recess 148 in the casing spool 137 , thereby compensating for the lost squeeze in the seal 143 due to temperature-induced shrinkage.
  • the segmented rings 187 , 188 located at the respective upper and lower ends of the seal 143 are engaged by the head 171 of the associated pin members 161 .
  • the segmented rings 187 , 188 act as hard surfaces for the pin members 161 to act on the seal 143 and to distribute the compressive force evenly.
  • 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 floating pin members 161 , which requires less force to energize the packing.
  • the seal material e.g., rubber
  • Various embodiments also provide a dependable seal function at low temperatures due to the application of a substantially constant force applied by the pin members 161 to compensate for the shrinkage factor resulting from the low temperatures.
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Gasket Seals (AREA)
US13/674,481 2012-11-12 2012-11-12 Shrinkage compensated seal assembly and related methods Abandoned US20140131954A1 (en)

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US13/674,481 US20140131954A1 (en) 2012-11-12 2012-11-12 Shrinkage compensated seal assembly and related methods
PCT/US2013/067733 WO2014074387A1 (fr) 2012-11-12 2013-10-31 Ensemble joint offrant une compensation contre le rétrécissement et procédés associés

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Cited By (6)

* Cited by examiner, † Cited by third party
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 (zh) * 2016-08-01 2017-08-18 中嵘能源科技集团有限公司 一种防腐蚀隔热注气管柱
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 (fr) * 2022-06-30 2024-01-04 Baker Hughes Oilfield Operations Llc Division d'une plaque de compression renforcée pour suspension avec coins
WO2024191899A1 (fr) * 2023-03-16 2024-09-19 Baker Hughes Oilfield Operations Llc Plaque de compression flexible pour dispositif de suspension coulissant ou garniture d'étanchéité

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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
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WO2024006202A1 (fr) * 2022-06-30 2024-01-04 Baker Hughes Oilfield Operations Llc Division d'une plaque de compression renforcée pour suspension avec coins
WO2024191899A1 (fr) * 2023-03-16 2024-09-19 Baker Hughes Oilfield Operations Llc Plaque de compression flexible pour dispositif de suspension coulissant ou garniture d'étanchéité
US20240309716A1 (en) * 2023-03-16 2024-09-19 Baker Hughes Oilfield Operations Llc Compliant compression plate for a slip hanger or packoff

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