US20080023917A1

US20080023917A1 - Seal for blowout preventer with selective debonding

Info

Publication number: US20080023917A1
Application number: US11/829,697
Authority: US
Inventors: Shafiq Khandoker
Original assignee: Hydril Co LP
Current assignee: Hydril USA Distribution LLC
Priority date: 2006-07-28
Filing date: 2007-07-27
Publication date: 2008-01-31
Also published as: CA2658994A1; CN101517284B; CA2658994C; EP2049764A4; EP2049763A4; CA2658997A1; EP2049763A1; WO2008039589A1; WO2008014515A1; CA2658708A1; WO2008014517A1; MX2009001112A; EP2049763B1; JP5011476B2; EP2049765A4; CA2659000A1; BRPI0713825A2; EP2049764A1; JP2009544875A; MX2009001065A

Abstract

A seal and a method of manufacturing a seal for a blowout preventer. The seal includes a rigid material insert disposed within an elastomeric body, with at least a portion of the rigid material insert selectively de-bonded from the elastomeric body.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This Application claims the benefit of the following provisional applications under 35 U.S.C. 119(e): U.S. Patent Application Ser. No. 60/820,723 filed on Jul. 28, 2006; U.S. Patent Application Ser. No. 60/847,760 filed on Sep. 28, 2006; U.S. Patent Application Ser. No. 60/862,392 filed on Oct. 20, 2006; and U.S. Patent Application Ser. No. 60/912,809 filed on Apr. 19, 2007, all incorporated by reference in their entirety herein.

BACKGROUND OF INVENTION

1Field of the Invention
Embodiments disclosed herein generally relate to blowout preventers used in the oil and gas industry. Specifically, embodiments selected relate to an improved seal including elastomer and a rigid material for use in blowout preventers, in which the clastomer is selectively de-bonded from the rigid material.
2. Background Art
Well control is an important aspect of oil and gas exploration. When drilling a well, for example, safety devices must be put in place to prevent injury to personnel and damage to equipment resulting from unexpected events associated with the drilling activities.
Drilling wells involves penetrating a variety of subsurface geologic structures, or “layers.” Occasionally, a wellbore will penetrate a layer having a formation pressure substantially higher than the pressure maintained in the wellbore. When this occurs, the well is said to have “taken a kick.” The pressure increase associated with a kick is generally produced by an influx of formation fluids (which may be a liquid, a gas, or a combination thereof) into the wellbore. The relatively high-pressure kick tends to propagate from a point of entry in the wellbore uphole (from a high-pressure region to a low-pressure region). If the kick is allowed to reach the surface, drilling fluid, well tools, and other drilling structures may be blown out of the wellbore. Such “blowouts” may result in catastrophic destruction of the drilling equipment (including, for example, the drilling rig) and substantial injury or death of rig personnel.
Because of the risk of blowouts, devices known as blowout preventers are installed above the wellhead at the surface or on the sea floor in deep water drilling arrangements to effectively seal a wellbore until active measures can be taken to control the kick. Blowout preventers may be activated so that kicks are adequately controlled and “circulated out” of the system. There are several types of blowout preventers, the most common of which are annular blowout preventers (including spherical blowout preventers) and ram blowout preventers. Each of these types of blowout preventers will be discussed in more detail.
Annular blowout preventers typically use large annular, rubber or elastomeric seals having metal inserts, which are referred to as “packing units.” The packing units may be activated within a blowout preventer to encapsulate drillpipe and well tools to completely seal an “annulus” between the pipe or tool and a wellbore. In situations where no drillpipe or well tools are present within the bore of the packing unit, the packing unit may be compressed such that its bore is entirely closed. As such, a completely closed packing unit of an annular blowout preventer acts like a shutoff valve. Typically, packing units seal about a drillpipe, in which the packing unit may be quickly compressed, either manually or by machine, to affect a seal thereabout to prevent well pressure from causing a blowout.
An example of an annular blowout preventer having a packing unit is disclosed in U.S. Pat. No. 2,609,836, issued to Knox, assigned to the assignee of the present invention, and incorporated herein by reference in its entirety. The packing unit of Knox includes a plurality of metal inserts embedded in an elastomeric body, in which the metal inserts are completely bonded with the elastomeric body. The metal inserts are spaced apart in radial planes in a generally circular fashion extending from a central axis of the packing unit and the wellbore. The inserts provide structural support for the elastomeric body when the packing unit is radially compressed to seal against the well pressure. Upon compression of the packing unit about a drillpipe or upon itself, the elastomeric body is squeezed radially inward, causing the metal inserts to move radially inward as well.
Referring now to FIG. 1, an annular blowout preventer 101 including a housing 102 is shown. Annular blowout preventer 101 has a bore 120 extending therethrough corresponding with a wellbore 103. A packing unit 105 is then disposed within annular blowout preventer 101 about bore 120 and wellbore 103. Packing unit 105 includes an elastomeric annular body 107 and a plurality of metal inserts 109. Metal inserts 109 are disposed within elastomeric annular body 107 of packing unit 105, which are distributed in a generally circular fashion and spaced apart in radial planes extending from wellbore 103. Further, packing unit 105 includes a bore 111 concentric with bore 120 of blowout preventer 101.
Annular blowout preventer 101 is actuated by fluid pumped into opening 113 of a piston chamber 112. The fluid applies pressure to a piston 117, which moves piston 117 upward. As piston 117 moves upward, piston 117 translates force to packing unit 105 through a wedge face 118. The force translated to packing unit 105 from wedge face 118 is directed upward toward a removable head 119 of annular blowout preventer 101, and inward toward a central axis of wellbore 103 of annular blowout preventer 101. Because packing unit 105 is retained against removable head 119 of annular blowout preventer 101, packing unit 105 does not displace upward from the force translated to packing unit 105 from piston 117. However, packing unit 105 does displace inward from the translated force, which compresses packing unit 105 toward central axis of wellbore 103 of the annular blowout preventer 101. In the event drillpipe is located within bore 120, with sufficient radial compression, packing unit 105 will seal about the drillpipe into a “closed position.” The closed position is shown in FIG. 5.
In the event a drillpipe is not present, packing unit 105, with sufficient radial compression, will completely seal bore 111.
Annular blowout preventer 101 goes through an analogous reverse movement when fluid is pumped into opening 115 of piston chamber 112, instead of opening 113. The fluid translates downward force to piston 117, such that wedge face 118 of piston 117 allows the packing unit 105 to radially expand to an “open position.” The open position is shown in FIG. 4. Further, removable head 119 of annular blowout preventer 101 enables access to packing unit 105, such that packing unit 105 may be serviced or changed if necessary.
Referring now to FIGS. 2, 3A, and 3B together, packing unit 105 and metal inserts 109 used in annular blowout preventer 101 are shown in more detail. In FIG. 2, packing unit 105 includes an elastomeric annular body 107 and a plurality of metal inserts 109. Metal inserts 109 are distributed in a generally circular fashion and spaced apart in radial planes within elastomeric annular body 107 of packing unit 105. FIGS. 3A and 3B show examples of metal inserts 109 that may be disposed and embedded within elastomeric annular body 107 of packing unit 105. Typically, metal inserts 109 are embedded and completely bonded to elastomeric annular body 107 to provide a structural support for packing unit 105. The bond between annular body 107 and metal inserts 109 restricts relative movement between annular body 107 and inserts 109, movement which is seen to cause failure of the elastomer within the elastomeric annular body 107. More discussion of the bonds between elastomeric bodies and metal inserts within a packing unit may be found in U.S. Pat. No. 5,8519,013, issued to Simons, assigned to the assignee of the present invention, and incorporated herein by reference in its entirety.
Referring now to FIGS. 4 and 5, an example of packing unit 105 in the open position (FIG. 4) and closed position (FIG. 5) is shown. When in the open position, packing unit 105 is relaxed and not compressed to seal about drillpipe 151 such that a gap is formed therebetween, allowing fluids to pass through the annulus. As shown in FIG. 5, when in the closed position, packing unit 105 is compressed to seal about drillpipe 151, such that fluids are not allowed to pass through the annulus. Therefore, the blowout preventer may close the packing unit 105 to seal against wellbore pressure from the blowout originating below.
Similarly, spherical blowout preventers use large, semi-spherical, elastomeric seals having metal inserts as packing units. Referring to FIG. 6, an example of a spherical blowout preventer 301 disposed about a wellbore axis 103 is shown. FIG. 6 is taken from U.S. Pat. No. 3,667,721 (issued to Vujasinovic and incorporated by reference in its entirety). As such, spherical blowout preventer 301 includes a lower housing 303 and an upper housing 304 releasably fastened together with a plurality of bolts 311, wherein housing members 303, 304 may have a curved, spherical inner surface. A packing unit 305 is disposed within spherical blowout preventer 301 and typically includes a curved, elastomeric annular body 307 and a plurality of curved metal inserts 309 corresponding to the curved, spherical inner surface of housing members 303, 304. Metal inserts 309 are thus disposed within annular body 307 in a generally circular fashion and spaced apart in radial planes extending from a central axis of wellbore 103.
Additionally, ram blowout preventers may also include elastomeric seals having metal inserts. The large seals are typically disposed on top of ram blocks or on a leading edge of ram blocks to provide a seal therebetween. Referring now to FIG. 7, a ram blowout preventer 701 including a housing 703, a ram block 705, and a top seal 711 is shown. With respect to FIG. 7, only one ram block 705 is shown; typically, though, two corresponding ram blocks 705 are located on opposite sides of a wellbore 103 from each other (shown in FIG. 8). Ram blowout preventer 701 includes a bore 720 extending therethrough, bonnets 707 secured to housing 703 and piston actuated rods 709, and is disposed about central axis of a wellbore 103. Rods 709 are connected to ram blocks 705 and may be actuated to displace inwards towards wellbore 103. Rams blocks 705 may either be pipe rams or variable bore rams, shear rams, or blind rams. Pipe and variable bore rams, when activated, move to engage and surround drillpipe and/or well tools to seal the wellbore. In contrast, shear rams engage and physically shear any wireline, drillpipe, and/or well tools in wellbore 103, whereas blind rams close wellbore 103 when no obstructions are present. More discussion of ram blowout preventers may be found in U.S. Pat. No. 6,554,247, issued to Berckenhoff, assigned to the assignee of the present invention, and incorporated herein by reference in its entirety.
Referring now to FIG. 8, ram blocks 705A, 705B and top seals 711A, 711B used in ram blowout preventer 701 are shown in more detail. As shown, top seals 711A, 711B are disposed within grooves 713 of ram blocks 705A, 705B, respectively, and seal between the top of ram blocks 705 and housing 703 (shown in FIG. 7). As depicted, ram block 705A is an upper shear ram block having top seal 705A, and ram block 705B is a lower shear ram block having top seal 705B. When activated, ram blocks 705A, 705B move to engage, in which shears 715A engage above shears 715B to physically shear drillpipe 151. As ram blocks 705A, 705B move, top seals 705A, 705B seal against housing 703 to prevent any pressure or flow leaking between housing 703 and ram blocks 705A, 705B.
Referring now to FIGS. 9A and 9B, top seals 711A, 711B are shown in more detail. As shown particularly in FIG. 9A, top seals 711A, 711B comprise an elastomeric band 751, elastomeric segments 753 attached at each end of elastomeric band 751, and a metal insert 755 disposed within each elastomeric segment 753. Top seal 705A for ram block 705A (i.e., the upper shear ram block) may also include a support structure 757 connected between elastomeric segments 753. As shown in a cross-sectional view in FIG. 9B, metal insert 755 disposed within elastomeric segment 753 has an H-shaped cross-section. The H-shaped cross-section of metal insert 755 provides support and optimal stiffness to elastomeric segment 753. Furthermore, it should be understood that top seals 711A, 711B may be used with either pipe rams, blind rams, or shear rams (shown in FIG. 8).
Referring now to FIG. 10, a ram block 705A with a top seal and a ram packer 717A used in ram blowout preventer (e.g., 701 of FIG. 7) are shown. FIG. 10 is taken from U.S. Publication No. US 2004/0066003 A1 (issued to Griffen et al. and incorporated herein by reference in its entirety). Instead of a shear rams (shown in FIGS. 7 and 8), FIG. 10 depicts a pipe ram assembly having a variable bore ram packer 717A comprised of elastomer and metal. As shown, variable bore ram packer 717A comprises an elastomeric body 761 of a semi-elliptical shape having metal packer inserts 763 molded in elastomeric body 761. Metal packer inserts 763 are arranged around a bore 765 of elastomeric body 761. As mentioned above with respect to pipe rams or variable bore rams, when activated, ram packer 717A (along with a corresponding ram packer oppositely located from ram packer 717A) moves to engage and surround drillpipe and/or well tools located in bore 765 to seal the wellbore.
For any seal mechanism comprising elastomers and metal in blowout preventers (e.g., packing units in the annular and spherical blowout preventers and top seals and ram packers in the ram blowout preventer), loads may be applied to contain pressures between various elements of the blowout preventers. For example, with respect to the annular blowout preventer shown in FIG. 1, as the fluid force is translated from piston 117 and wedge face 118 to packing unit 105 to close packing unit 105 towards central axis of wellbore 103, the fluid force generates stress and strain within packing unit 105 at areas and volumes thereof contacting sealing surfaces (e.g., wedge face 117 and drillpipe 151) to seal against wellbore pressure from below. The stress occurring in packing unit 105 is approximately proportional to the fluid force translated to packing unit 105.
As stress is incurred by blowout preventer seals, the material of the seals will strain to accommodate the stress and provide sealing engagement. The amount of strain occurring in the material of the seal is dependent on a modulus of elasticity of the material. The modulus of elasticity is a measure of the ratio between stress and strain and may be described as a material's tendency to deform when force or pressure is applied thereto. For example, a material with a high modulus of elasticity will undergo less strain than a material with a low modulus of elasticity for any given stress. Of the materials used in blowout preventer seals, the metal inserts have substantially larger moduli of elasticity than the elastomeric portions. For example, the modulus of elasticity for steel (typically about 30,000,000 psi; 200 GPa) is approximately 20,000-30,000 times larger than the moduli of elasticity for most elastomers (typically about 1,500 psi; 0.01 GPa).
Historically, when examining, designing, and manufacturing seals for blowout preventers, such as packing units for blowout preventers, the locations and amounts of stress and/or strain (i.e., stress concentrations, strain concentrations) occurring within the seal have been the largest concern and received the most attention and analysis. As the seal is subject to loads (e.g., repetitive and cyclic closures of a packing unit of an annular blowout preventer about a drillpipe or about itself), the magnitude and directions of the stresses and strains occurring across the seal are evaluated to determine the performance of the seal. A common technique used for this evaluation is finite element analysis (“FEA”). Specifically, the FEA may be used to simulate and evaluate the stress and/or strain concentrations which occur across the seal under given displacement conditions.
Traditionally with FEA, seals for blowout preventers are modeled with finite elements to determine the performance of the seal under various displacement conditions. For example, using FEA modeling, the packing unit of an annular blowout preventer may be simulated with a displacement condition to move into the closed position around a drillpipe, in which the packing unit would be compressed between the piston and the removable head from the annular blowout preventer and the drillpipe. The FEA model may be used to produce a strain plot of the seal (packing unit in this example) to display the strain concentrations within the seal under that specific displacement condition.
However, this evaluation of the strain concentrations may not result in the most accurate prediction and representation of the performance of the seals used in blowout preventers. Typically, the seals used in blowout preventers experience extremely high amounts of strain from the stresses that may be incurred. For example, when a packing unit is compressed into the closed position to seal about a section of drillpipe, an elastomeric body of the packing unit may experience strains in excess of 300% in the areas of the strain concentrations. Further, in a case where no drillpipe is present, the packing unit may begin experiencing strains of about 400-450% in sealing about itself. These elevated strains, especially when repetitively and cyclically performed upon the packing seal, usually lead to the ultimate failure of the seal.
Furthermore, as described above, the metal and elastomers used for seals in blowout preventers typically have large differences in their moduli of elasticity. Because of this difference between the moduli of elasticity, when bonded together, the metal will tend to control the “flow” and deformation of the elastomers in the seals when compressed in the blowout preventers. With the large amounts of strain, especially the strain resulting from repetitive and cyclic displacements, coupled with the significant difference between the moduli of elasticity of the seal's materials, FEA evaluating strain concentrations may not accurately represent the capabilities of the seals.
In FEA applications, the seal comprising a rigid material and elastomer may be represented by a geometrically similar representation consisting of many finite elements (i.e. discrete regions), commonly referred to as a mesh. The finite elements interact with one another to model the seal and provide simulated data and results for various displacement conditions. However, the finite elements within areas of high stress and/or strain (i.e., stress and/or concentrations) with substantial differences between materials' moduli of elasticity may improperly deform. Common improper deformations of the finite elements that may occur include the elements collapsing upon themselves, distorting without bound, or sustaining losses in stress, strain, and/or energy. These, in addition to other improper deformations of the finite elements may produce inaccurate results for the stress and strain occurring across the model.
Historically, when the FEA is producing erroneous results, the number of finite elements of the mesh is increased for better resolution in at least some selected locations (e.g., areas of high stress or strain concentration). Thus, it is common for areas with stress and/or strain concentrations to receive more localized “attention” when modeling in FEA than other areas. However, this process may allow the analysis to become inherently localized on the areas of the seal models with the stress and/or strain concentrations, leading to solutions that may be narrowly constructed and/or inaccurate. For example, it is common FEA practice to increase the number of elements of (and thus further complicate) the seal model in the areas of these concentrations to increase the accuracy of the simulated stress and strain within the concentration regions. The same may also be done for a seal model in the areas of strain concentrations. However, it should be understood that by increasing the number of elements, or decreasing the mesh size, the solution time and the amount of computing power required may be increased. This may lead to solution stalling (due to computational error) and/or the generation of inaccurate results.
Referring now to FIG. 11, a graph displaying strain (y-axis) versus number of iterations (x-axis) within FEA is shown. Specifically, the simulated strain displayed on the y-axis may be a magnitude of a principal strain occurring in a specific direction simulated across a finite element of a seal model for a given displacement condition. For example, those having ordinary skill in the art will recognize that the y-axis of the graph may display the magnitude of a principal strain (e.g., strain occurring in the direction of the z-axis; shear strain occurring in the plane of the y-axis and the z-axis) occurring within a finite element when the seal model is simulated with a displacement condition (e.g., closing of a packing unit about a drillpipe). Further, the number of iterations displayed on the x-axis refers to the amount of simulations of FEA used when modeling the seal. As such, each “iteration” refers to a single execution of the FEA process to simulate a displacement of the seal for the blowout preventer, thus determining the magnitude of strain of the finite element of the seal model.
In this approach, the resolution of the finite elements in the mesh (seal model) is increased with each iteration. Specifically, as mentioned above, it is ordinary practice to increase the resolution of the finite elements of the mesh in regions that experience large amounts of stress and/or strain. However, because of the characteristics of metal reinforced elastomer seals, such localized analysis may result in an FEA stress and/or strain output that fails to correlate to an experimentally observed solution. Furthermore, because of the complexity, the FEA stress and/or strain output may not even be capable of converging to a solution at all.
As shown, theoretical strain of the finite element occurring in the direction of the simulated principal strain from the y-axis in FIG. 11 is determined and shown for a seal of a blowout preventer under the displacement condition. As the number of iterations increases for the FEA model, the simulated strain solution produced (i.e., a trend line of strain points found from each iteration produced using FEA) thereby may not correspond and converge with the theoretical strain under a comparable displacement condition. A tolerance band of ±about 1% of the theoretical strain is shown to indicate a range that may be acceptable for the simulated strain solution to converge within. This concept of convergence of FEA stress and/or strain output may be understood as when the simulated stress/strain solution reaches a solution within the tolerance band, the simulated stress/strain solution continues to stay within the tolerance band as further iterations of the solution are continued.
Therefore, as shown, when designing and manufacturing high strain elastomeric seals containing rigid inserts, there may be a significant discrepancy between the theoretical stress and strain predicted by FEA and actual stress and strain. Thus, current modeling and analysis techniques for blowout preventer seals may not provide adequate information to improve their design and manufacture.

SUMMARY OF INVENTION

In one aspect, embodiments disclosed herein relate to a seal of a blowout preventer. The seal includes at least one rigid material insert disposed within an elastomeric body. Further, at least one portion of the at least one rigid material insert is selectively de-bonded from the elastomeric body.
In another aspect, embodiments disclosed herein relate to a method of manufacturing a seal of a blowout preventer. The method includes generating a finite element analysis seal model, analyzing a strain plot of the finite element analysis seal model based on a displacement condition, and identifying in the finite element analysis seal model at least one portion of at least one rigid material insert to selectively de-bond from an elastomeric body. The method further includes manufacturing the seal with the identified at least one portion of the at least one rigid material insert selectively de-bonded from the elastomeric body.
Further, in another aspect, embodiments disclosed herein relate to an annular blowout preventer. The annular blowout preventer includes a housing, a piston chamber formed in the housing, a piston disposed within the piston chamber, and a packing unit disposed adjacent to the piston. The packing unit includes an elastomeric body and at least one portion of the at least one rigid material insert disposed within the elastomeric body. At least one portion of the at least one rigid material insert is selectively de-bonded from the elastomeric body.
Other aspects and advantages of the embodiments disclosed herein will be apparent from the following description and the appended claims.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a cross-sectional view of an annular blowout preventer.
FIG. 2 is a cross-sectional view of a packing unit for an annular blowout preventer.
FIG. 3A is a perspective view of a metal insert for a packing unit for an annular blowout preventer.
FIG. 3B is a side view of an alternative metal insert for a packing unit for an annular blowout preventer.
FIG. 4 is a cross-sectional view of a prior art packing unit for an annular blowout preventer shown in a relaxed position.
FIG. 5 is a cross-sectional view of a packing unit for an annular blowout preventer in a closed position.
FIG. 6 is a cross-sectional view of a spherical blowout preventer.
FIG. 7 is a cross-sectional view of a ram blowout preventer.
FIG. 8 is a perspective view of ram shears for a ram blowout preventer.
FIG. 9A is a perspective view of a top seal for ram blocks of a ram blowout preventer.
FIG. 9B is a cross-sectional view of a top seal for ram blocks of a ram blowout preventer.
FIG. 10 is a perspective view of a variable bore ram packer for a ram block of a ram blowout preventer.
FIG. 11 is a graphical representation of strain versus the number of FEA iterations.
FIG. 12 is a flow chart depicting a method of manufacturing a seal for a blowout preventer in accordance with embodiments disclosed herein.
FIG. 13 is a cross-sectional, axial profile of an annular packing unit in a two-dimensional plot (using x and z axes) in accordance with embodiments disclosed herein.
FIG. 14 is a cross-sectional, radial profile of an annular packing unit in a two-dimensional plot (using x and y axes) in accordance with embodiments disclosed herein.
FIG. 15 is a portion of a seal model of an annular packing unit in a three-dimensional plot (using x, y, and z axes) in accordance with embodiments disclosed herein.
FIG. 16 is a portion of a seat mesh of an annular packing unit in a three-dimensional plot (using x, y, and z axes) in accordance with embodiments disclosed herein.
FIG. 17A is an end view of a metal insert for a packing unit for an annular blowout preventer.
FIG. 17B is an end view of a metal insert for a packing unit for an annular blowout preventer in accordance with embodiments disclosed herein.
FIG. 18A is a top view of a metal insert for a packing unit for an annular blowout preventer.
FIG. 18B is a top view of a metal insert for a packing unit for an annular blowout preventer.
FIG. 19A is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 19B is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 20A is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 20B is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 21A is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 21B is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 22 is a graphical representation of strain versus number of FEA iterations in accordance with embodiments disclosed herein.
FIG. 23A is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 23B is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 24A is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 24B is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 25A is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 25B is a strain plot of a seal model of an annular packing unit with selective de-bonding in accordance with embodiments disclosed herein.
FIG. 26 depicts a computer system used to design seals for blowout preventers in accordance with embodiments disclosed herein.
FIG. 27A is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 27B is a strain plot of a seal model of an annular packing unit in accordance with embodiments disclosed herein.
FIG. 28 is a seal model of an annular packing unit in accordance with embodiment disclosed herein.

DETAILED DESCRIPTION

In one aspect, embodiments disclosed herein relate to a method of manufacturing a seal for a blowout preventer. In another aspect, embodiments disclosed herein relate to a method of optimizing a seal for a blowout preventer that incorporates using a strain plot in the method. In another aspect, embodiments disclosed herein relate to a method of certifying a seal model for a blowout preventer using FEA to produce a strain plot after the model has been smoothed and bulk analyzed in response to a displacement condition.
As used herein, a “rigid material” refers to any material that may provide structure to a seal of a blowout preventer, both metal and non-metal. Examples for a rigid material may include, but are not limited to, steel, bronze, and high strength composites (e.g., carbon composites, epoxy composites, thermoplastics). Further, as used herein, a “seal” refers to a device that is capable of separating zones of high pressure from zones of low pressure. Examples of blowout preventer seals include, but are not limited to, annular packing units, top seals, and variable bore rams.
As mentioned above, techniques and models historically used to design and manufacture seals having elastomer and rigid materials for blowout preventers may not provide accurate information to improve the performance of the seal's design. Therefore, in designing, manufacturing, and certifying a seal for a blowout preventer in accordance with embodiments disclosed herein, a method including FEA of bulk strain and generating a strain plot may be used to yield more accurate convergent results under a given displacement condition. This FEA method, in addition to certain techniques for generating and modifying the seal models, may more accurately calculate the strain in the seal because it is tailored to accommodate the large amounts of stress and strain experienced by blowout preventer seals. Suitable software to perform such FEA includes, but is not limited to, ABAQUS (available from ABAQUS, Inc.), MARC (available from MSC Software Corporation), and ANSYS (available from ANSYS, Inc.).
Specifically, embodiments and methods disclosed herein may advantageously provide techniques for generating and analyzing seal models within FEA to determine the seal's response under displacement conditions characterized by large amounts of strain. Methods disclosed herein may use a simplified seal design and/or model of a seal to assist in the analysis of the seal. For example, methods disclosed herein may avoid analyzing stress and strain concentrations of a complex seal design by “smoothing” that design.
As used herein, the term “smoothing” refers to various techniques to simplify a complex geometry of a seal design for use with FEA. These techniques may allow the analysis of a smoothed model (i.e., a FEA model constructed from a smoothed design) to correlate with experimentally observed conditions and to converge to a definitive result when analysis of a non-smoothed model may not. As such, a model constructed from a smoothed design may be analyzed within FEA to determine an overall, or “bulk”, strain condition. By analyzing this bulk (i. e., non-localized) strain, the performance, and/or possibly failure, of a seal under various displacement conditions may be predicted with more accuracy. Following the analysis of the smoothed model for the bulk strain condition, knowledge obtained therefrom may be incorporated into a (non-smoothed) seal design that is to be manufactured.
Referring now to FIG. 12, a flow chart depicting a method of manufacturing a seal including an elastomer and a rigid material is shown. As a first step 1210, properties of the seal's materials (e.g., the elastomers and the rigid materials) are determined. The material properties may either be determined through empirical testing or, in the alternative, may be provided from commercially available material properties data. Next, a three-dimensional seal model (i.e., a mesh) for the seal is generated 1220. As such, generating a seal model 1220 may also comprise importing a seal design 1221 and subsequently smoothing the imported seal design 1222 to simplify FEA analysis.
Next, displacement conditions are simulated in FEA using the smoothed seal model 1230. Preferably, these simulated displacement conditions reflect the forces, load states, or strains that the seal may expect to experience in operation. Further, after simulating displacement conditions, a strain plot showing the strain and deformation occurring in the seal model is generated and analyzed 1240. Ideally, the strain plot shows the location and amount of strain occurring in the seal model in response to the simulated displacement conditions. The strain plot may be analyzed and reviewed 1240 to determine the performance characteristics of the seal model. If the seal model requires improvement, the method may loop back to 1210 to determine material properties of another material for the seal, or alternatively may loop back to 1220 for generation and analysis of another seal model. This loop allows the seal model to be further simulated in FEA to determine its performance after further modifications or models. Otherwise, if the seal model is considered acceptable and meets a specified criteria, the seal model may be used to manufacture a seal for a blowout preventer 1250.
In initial step 1210, the properties of the seal's materials are determined. Of the materials, the elastomeric materials will have lower moduli of elasticity than the rigid materials. Thus, when the seal is subjected to large amounts of stress, the elastomeric portion of the seal will strain more than the rigid material portions. For example, when the packing unit in an annular blowout preventer is stressed in the closed position, the elastomeric body of the packing unit will strain significantly more than the metal inserts. Because elastomers strain significantly more than the rigid materials for any given stress input, it may be especially important to determine the material properties of an elastomer used in the seal, specifically the relationship between stress and strain across the elastomer.
In viscoelastic materials under constant stress, the strain may increase with time (i.e., creep). Conversely, under a constant strain rate, the stress within viscoelastic materials decreases over time (i.e., relaxation). Furthermore, higher strain rates and lower temperatures may lead to an increase in the moduli of elasticity for viscoelastic materials. Elongation of a material refers to the percentage change in length of a material. The maximum amount of tensile strain to which a material may be subjected, or elongated to, before failure is referred to as the elongation at break. A material may have a high or low modulus of elasticity, but may exhibit a low elongation at break such that the material will fail without experiencing much strain. Further, the tensile strength of a material is the maximum amount of stress (in tension) a material may be subjected to before failure. As stress is exerted upon the material, the material strains to accommodate the stress. Once the stress is too much for the material, it will no longer be able to strain, and the material fails. The failure point of the material is known as the ultimate tensile strength.
Furthermore, if cyclic displacements are applied to an elastomeric material, hysteresis (phase lag) may occur, leading to a dissipation of mechanical energy within the elastomeric material. Hysteresis may occur when there is softening induced by stress and strain. This may be described as an instantaneous and irreversible softening for a material that occurs when an applied displacement increases beyond any prior maximum value, resulting in a shift of the stress-strain curve of the material. This induced softening, which may also be referred to as the Mullin's effect, is thought to be at least partially attributed to the microscopic breakage of links in a elastomeric material. This weakens the elastomeric material during an initial deformation so that the material is, in turn, weaker in subsequent deformations of the material.
Thus, in one embodiment of the present disclosure, to determine at least one of the material properties of the elastomer for the seal of the blowout preventer, as described above, empirical testing of the elastomer may be used. Specifically, tests may be performed to determine the properties of the elastomeric material. Examples of tests that may be performed include, but are not limited to, a uniaxial tension test, a uniaxial compression test, a lap shear test, and a biaxial tension test. A uniaxial tension test applies tensile stress in one direction to a material and measures the corresponding strain induced in the material. A uniaxial compression test applies compressive stress in one direction to a material and measures the corresponding strain induced in the material. A lap shear test applies shear stress to a material and measures the corresponding shear strain of the material. Further, a biaxial tension test applies tensile stress in two directions to a material and measures the corresponding strain of the material. The use of these tests, in addition to other tests commonly known in the art, may assist in analyzing and determining the material properties of the elastomer. Furthermore, it should be understood by one of ordinary skill in the art, that as material properties of most materials vary by temperature, the performance of multiple tests at differing temperatures may be prudent to establish certain material properties.
In step 1220, a model (i.e., a mesh) for the seal is generated. When generating the model of the seal, design features of the seal are chosen and applied to the model. For example, for a packing unit for an annular blowout preventer, the number of inserts used, the width of the rigid material inserts, and the specific material used for the rigid material inserts may be chosen when generating the seal model. The seal models may be created in a computer aided design (“CAD”) software package (e.g., AutoCAD available from Autodesk, Inc., and Pro/Engineer available from Parametric Technology Corporation) and imported into the FEA software package or, in the alternative, may be generated within the FEA packages (e.g., ABAQUS and PATRAN) themselves.
Referring now to FIGS. 13-16, a method of generating a seal model in accordance with embodiments disclosed herein is shown. Specifically, as shown, a model of packing unit 105 of an annular blowout preventer may be generated from a seal design created using CAD software. As shown in FIG. 13, cross-sectional, axial profiles 1301 of a seal design may be generated of annular packing unit 105 in a two-dimensional plot (using x and z axes). Packing unit 105 includes elastomeric body 107 and rigid (e.g., metal) material insert 109 with bore 111. Multiple radial and axial cross-sectional profiles may be generated to represent different sections of the seal. For example, profiles may be generated of the sections of a packing unit 105 that do or do not have metal inserts 109.
From here, as shown in FIG. 14, in addition to generating cross-sectional, axial profiles 1301, cross-sectional, radial profiles 1401 of the seal design may be generated to represent different radial sections of the seal in a two-dimensional plot (using x and y axes). Because of the symmetry of packing unit 105, only a radial portion of cross-sectional, radial profiles 1401, as shown, may need to be generated. Then, as shown in FIG. 15, by combining axial and radial profiles 1301, 1401, a three-dimensional seal design 1501 may be generated to represent at least a portion of packing unit 105 in a three-dimensional plot (using corresponding x, y, and z axes from FIGS. 13 and 14). In three-dimensional seal design 1501, metal inserts 109 and elastomeric body 107 are generated as separate bodies which may interact with one another. Depending on the complexity of the design of the seal (L e., packing unit in this case), more profiles 1301, 1401 of the seal may be generated for more detail in seal design 1501.
Further, as shown, seal design 1501 and model or mesh 1601 (discussed below) may only represent a radial portion of packing unit 105. However, the remainder of packing unit 105 may be easily generated by taking advantage of the symmetrical geometry of packing unit 105. Those having ordinary skill in the art will appreciate that in the case of radially symmetric models, symmetric portions and profiles may be used and replicated to simplify the generation of the model.
Referring now to FIG. 16, seal design 1501 created using CAD software may be imported into FEA software to generate a model or mesh 1601 of numerous finite elements 1603. Finite elements 1603 of mesh 1601 work together to simulate a seal and a packing unit when stresses and forces are applied. Finite elements 1603 of elastomeric body 107 of packing unit 105 will simulate and respond to stress and forces (L e., they will exhibit strain) corresponding to the material properties of the elastomeric material.
Similarly, finite elements 1603 of metal inserts 109 of packing unit 105 will simulate and respond to stress and forces corresponding to the material properties of the metal inserts. Thus, finite elements 1603 deform and strain to simulate the response of the different materials (e.g., elastomers and rigid materials) of the seal in accordance with their material properties. While finite elements 1603 are shown as eight-noded elements (i.e., brick elements), finite elements of any shape known in the art may be used.
Further, while generating a seal model 1220, a number of smoothing techniques may be used on the seal design 1222. In many circumstances, as mentioned above, analyzing the actual manufactured geometry of the seal using FEA may lead to complications when large amounts of stress and strain are simulated. Particularly, as manufactured, the geometry of metal seal components include radiused corners and other stress-concentration reducing features to more evenly distribute stress across the component as it is loaded. However, it has been discovered that these techniques may adversely affect FEA models in FEA in that they increase the complexity of the model and may prevent the FEA from producing accurate results. Therefore, a seal model generated from a smoothed design may include removing as-manufactured stress concentration features in an effort to improve the results of FEA.
In one embodiment, the seal design's rigid material may be modified (i.e., smoothed) to reduce their complexity. Referring now to FIG. 17A, an end view of a metal insert 1701 including flanges 1703 connected by a web 1705 is shown. Metal insert 1701 typically includes radiused internal corners 1707 and squared external corners 1709. However, in one embodiment of smoothing a design, the corners of the metal insert may be modified. For example, referring now to FIG. 17B, an end view of a metal insert 1711 design including flanges 1713 connected by a web 1715 in accordance with embodiment disclosed herein is shown. In smoothing the design, internal corners 1717 may be modified to reduce or eliminate their radii (as shown) in an attempt to simplify a subsequently constructed model. Further, in smoothing the seal design, external corners 1719 may be modified to add or increase their radii (also shown) in an attempt to simplify a subsequently constructed model A seal model constructed in this manner may be analyzed for bulk strains such that the FEA may produce more accurate and definitive results than would be possible using the former, more “localized” approach.
Furthermore, in another embodiment, instead of smoothing the design by modifying internal and external corners of the rigid material insert, the smoothing may include modifying the shape of the rigid material insert and its position within the elastomeric body. Referring now to FIG. 18A, a top view of a metal insert 1801 disposed within a portion of an elastomeric body 1802 of an annular packing unit is shown. Flange 1803 and web 1805 (outline shown) of metal insert 1801 shown has a rectangular outline, in which flange ends 1804A, 1804B of flange 1803 and web ends 1806A, 1806B of web 1805 are defined by straight edges. Ends 1804A, 1806A are radially closer to central axis 103 than ends 1804B, 1806B.
However, referring to FIG. 18B, the shape and orientation of the metal insert may be smoothed for bulk strain analysis. In FIG. 18B, a top view of a metal insert 1811 disposed within a portion of an elastomeric body 1802 of an annular packing unit in accordance with embodiments disclosed herein is shown. As shown, flange 1813 and web 1815 (outline shown) of metal insert 1811 have arcuate ends to define a radial outline centered about central axis 103+Specifically, sides 1814C, 1814D of flange 1813 may follow along radial lines 1817 extending radially out from central axis 103. Sides 1816C, 1816D of web 1815 may similarly follow along radial lines (not shown). With this, flange ends 1814A, 1814B disposed between flange sides 1814C, 1814D and web ends 1816A, 1816B disposed between web sides 1816C, 1816D may then follow an arcuate path to have an arc, bow, or bend, as shown. Preferably, arcuate ends 1814A, 1814B, 1816A, 1816B follow radial paths 1818 defined about central axis 103. Thus, as shown, a width of flange 1813 and web 1815 increases when following along their sides 1814C, 1814D, 1816C, 1816D from ends 1814A, 1816A to ends 1814B, 1816B. As such, a seal model constructed in this manner may be able to more accurately simulate strain during FEA to produce more accurate and definitive results.
Further still the elastomeric body of the seal design may be smoothed as well.
Referring again to FIG. 15, elastomeric body 107 includes a compression face 108 corresponding to wedge face 118 of piston (117 of FIG. 1). When piston 117 is activated, wedge face 118 contacts and compresses packing unit 105 to seal the well. In one technique, the seal design may be smoothed by modifying the compression face to have approximately the same angle as the wedge face of the piston. Alternatively, the wedge and compression faces may be modified to increase a contact region therebetween. By modifying the compression face, the wedge face, or both, a seal model constructed therefrom may be able to more accurately simulate strain for the strain plots during FEA. As the compressive face of the elastomeric body would otherwise have a different angle than the wedge face of the piston, the output of the FEA may be simplified to produce more accurate or definitive results when displaced.
Those having ordinary skill in the art will appreciate that, in addition to these described smoothing techniques and modifications, other techniques may be used as well in addition. For example, in another embodiment, the web of the rigid material insert may be modified, such as hollowing the web of the insert, as long as the rigid material insert provides sufficient structural support for the seal to sustain the forces applied thereto when under any and all displacement conditions.
Preferably, when generating the seal models in step 1220, especially when smoothing the seal design 1222 of the seal model, the volume of the elastomeric body and the rigid material inserts of the seal model remains substantially constant. If the volume does not remain constant, the results and simulated strain from the strain plots created by the FEA may not be accurate or consistent. For example, when applying a force to an element, the force upon the element will stress the element, causing the element to strain to accommodate the stress. The stress applied to the element, though, is directly proportional to the force applied to the element and inversely proportional to the area or volume of the element. Thus, if the force applied to the element increases and/or the volume of the element decreases, the stress will correspondingly increase in the element.
Using this concept, the respective volumes of the elastomeric body and the rigid material inserts preferably remain substantially constant to provide accurate results. For example, if the volume of the overall seal model has substantially changed from the actual seal, the strain plots of the seal model may show an increase in strain in the elastomeric body with corresponding displacement conditions. Further, if the volume of the seal model changes from the smoothing techniques applied to the seal design of the seal model, such as increasing the volume of the elastomeric body of the seal model during the smoothing process, the strain plots of the smoothed model may show a decrease in simulated strain with corresponding displacement conditions. Thus, if the volume of the elastomeric body and the rigid material insert of the model of the seal increases or decreases, the simulated strain in the model would inherently change, independent if the seal model was modified for any improvements. Furthermore, if the overall volume of the seal remains consistent between non-smoothed and smoothed models but the relative volumes of the elastomeric body and the rigid inserts change, the strain plots may be similarly compromised.
Continuing now with step 1230, displacement conditions are simulated upon a seal for a blowout preventer in FEA using the generated seal model. Preferably, the simulated displacement conditions are loads and strains the seal may expect to experience in service. For example, a model of a packing unit of an annular blowout preventer may require a simulated displacement condition correlating to compressing into a closed position to seal about a section of drillpipe. Further, if no drillpipe is present, the model may experience a simulated displacement condition correlating to compressing to close about itself to seal the bore.
In step 1240, a strain plot, showing strain and deformation occurring in the seal model in response to displacement conditions may be analyzed and reviewed to determine the performance of the modeled seal. Referring now to FIGS. 19-21, cross-sectional strain plots of a seal model in accordance with embodiments disclosed herein are shown. Specifically, the seal model is of a packing unit for an annular blowout preventer, in which packing unit model is initially simulated with a displacement condition as closed about a drillpipe 151. Then, the packing unit is shown in an original condition before the packing unit is simulated with the displacement condition, but the strain from the simulated displacement condition is superimposed across the non-displaced packing unit. This technique may be performed by calculating the strain from each element of the seal model with the displacement condition and showing the strain upon each corresponding element of the seal model in the original condition. This may allow the strain occurring in the packing unit under the simulated displacement condition to be “mapped” back to its original location in the packing unit.
Referring now to FIG. 19A, a strain plot of the packing unit model shows the maximum principal log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 19B, a strain plot of the seal model shows the packing unit originally before the displacement condition is simulated across the seal model in FIG. 19A, but the maximum principal log strain plot from FIG. 19A is superimposed across the undistorted seal model. Specifically, the strain of each element in the seal model in the displacement condition in FIG. 19A is added to each element in the undistorted seal model in FIG. 19B. This allows the strain plot to show where the strain concentrations will be located when in an undisplaced condition.
Similarly, referring to FIG. 20A, a strain plot of the packing unit model shows the axial log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 20B, a strain plot of the seal model shows the packing unit originally before the displacement condition is simulated across the seal model in FIG. 20A, but the axial log strain plot from FIG. 20A is superimposed across the undistorted seal model.
Similarly still, referring to FIG. 21A, a strain plot of the packing unit model shows the shear log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 21B, a strain plot of the seal model shows the packing unit originally before the displacement condition is simulated across the seal model in FIG. 21A, but the shear log strain plot from FIG. 21 A is superimposed across the undistorted seal model.
As shown in FIGS. 19-21, the packing unit experiences large amounts of strain to accommodate the closed position simulated displacement condition simulated with the seal model. Because of these large strains, the finite elements of the model or mesh may not deform properly to converge to an accurate or definitive result. However, by analyzing a bulk strain plot of a smoothed model in step 1240, a definitive result may be found. FEA focusing on the evaluation of bulk strain may be used to produce more accurate results.
Referring now to FIG. 22, a graph displaying strain (y-axis) versus number of iterations (x-axis) within FEA in is shown. The simulated strain on the y-axis is a magnitude of the principal strain in a specific direction simulated across a finite element of the seal model for a given displacement condition. Further, the number of iterations on the x-axis refers to the amount of simulations of FEA used when modeling the seal. However, in contrast to the FEA iterations of FIG. 11 whereby the model is iteratively made more localized (i.e., complex), each iteration of FIG. 22 may incrementally smooth the analyzed model (while maintaining consistent volume) to make such analysis less complex in nature. As such, as the analysis progresses from a more localized strain analysis (i.e., the left side of the x-axis) to a bulk strain analysis (i.e., the right portion of the x-axis), the solution converges and is contained within a tolerance band of about ±1%. Specifically, the FEA solution may be seen to converge in FIG. 11 because when the simulated strain solution reaches a solution within the tolerance band, the solution continues to stay within the tolerance band even as more iterations are continued. Desirably, the simulated strain of the seal model may converge within a tolerance of at least about 0.5% of the theoretical strain.
As such, in contrast to what one of ordinary skill in the art would intuitively believe, a simplified, smoothed model may produce a more convergent and accurate FEA solution than more complex, detailed models. As shown in this embodiment, the simulated strain produced using FEA correlates with experimentally observed solutions and converges to a definitive and correct result about the theoretical strain and within the tolerance band limitations. As the number of iterations increases (and as the model is further smoothed), the simulated strain solution produced by the FEA corresponds to the strain found in the seal through empirical testing. With these results, bulk strain FEA may provide useful results for simulation of seals for blowout preventers to further improve their designs.
For example, referring now to FIGS. 27A, 27B, and 28, strain that a seal model will sustain when simulated with a displacement condition may be shown on a strain plot when still in an undisplaced condition. This technique allows strains to be determined within areas and elements of the seal model while still in the undisplaced condition. In FIG. 27A, an enlarged view of a strain plot of a packing unit model shows the maximum principal log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. Three finite elements 2711, 2713, 2715 experiencing strain when simulated with the closed displacement condition have been marked and identified. In FIG. 27B, an enlarged view of a strain plot of the seal model shows the packing unit originally before the displacement condition is simulated across the seal model in FIG. 27A, but the maximum principal log strain occurring in the seal model from the displacement condition in FIG. 27A is superimposed across the seal model. As elements 2711, 2713, 2715 were marked when in the displacement condition in FIG. 27A, elements 2711, 2713, 2715 may be followed back in FIG. 27B to determine their original location within the seal model to graphically represent the magnitude and direction of the strains they experience. FIG. 28 also shows the packing unit seal model and mesh from FIGS. 27A, 27B with elements 2711, 2713, 2715. Using this and similar techniques, the areas of the seal model with the strain concentrations may be more easily determined to further improve the design of the seal model as necessary.
Further, when analyzing the strain plot in step 1240, the strain plots may be used to certify the seal model for use in a blowout preventer. Specifically, the strain plots may be compared against one or more specified criteria to determine if the performance of the seal model meets necessary requirements. Specified criteria, for example, may include performance requirements, customer's requirements, or even industry requirements for seals. Furthermore, such criteria may be compared against the strain plots of an analyzed seal model to determine if a seal manufactured in accordance with the model would be in compliance with such requirements. For example, a customer may require packing units of annular blowout preventers to be capable of experiencing strains in excess of 300%. A strain plot of the seal model packing unit in a closed position displacement conditions may then be compared against the specified criteria to determine if the seal model is capable of satisfying such requirements.
In another example, industry requirements, such as API 16A/ISO 13533:2001, may be used as specified criteria to compare and certify a seal model. In particular, API 16A, Section 5.7.2 references a “closure test” for ram-type blowout preventers while API 16A. Section 5.7.3 references a closure test for annular-type blowout preventers. Under API 16A/ISO 13533:2001, a packing unit may be required to undergo six closures about the drill pipe and, on a seventh closure, be capable of effectively sealing against pressure of about 200-300 psi (1.4-2.1 MPa). Thus, displacement conditions from industry requirements may be used in conjunction with a simulation to determine if a seal is capable of satisfying such requirements. Using methods and embodiments disclosed herein, the seal model may then be certified by comparing the strain plots of the seal model against these specified criteria.
If the seal model generated in step 1220 and analyzed in step 1240 may be improved further (e.g., if the model does not meet the specified criteria), the method may loop back to step 1210 to determine material properties for another material of the seal, or the method may loop back to step 1220 to have the seal model regenerated or modified as necessary. This loop of generating the seal model 1220 and analyzing the seal model 1240 may be repeated several times until an “optimized” seal model is reached.
In one embodiment, selected portions of an elastomeric body of a packing unit may be selectively de-bonded from the rigid material inserts when looping back and re-generating the seal model 1220 to reduce to reduce the amount and location of strain. Typically, the elastomeric body is completely bonded to metallic inserts for the packing unit to maintain maximum rigidity, as discussed above with respect to the prior art. However, specific portions of the elastomeric body may be identified to be selectively de-bonded from the rigid material inserts to reduce strain in the elastomer of the packing unit when the packing unit is modeled in FEA to show the strain plots.
As used herein, “selectively de-bonded” refers not only to de-bonding a specific or selected portion of the rigid material insert from the elastomeric body, but also to the degree the rigid material insert is de-bonded from the elastomeric body (partially de-bonded). For example, in one embodiment, it may be desirable to completely de-bond portions of the rigid material insert from the elastomeric body to reduce strain within the seal. However, in another embodiment, it may be desirable to vary the degree of the bond between the rigid material insert and the elastomeric body to create a partial de-bond to reduce strain within the seal. With a partial de-bond, a portion of the bond between the rigid material insert and the elastomeric body may be selectively weakened to have a bond strength between a full strength bond and a complete de-bond. Those having ordinary skill in the art will appreciate that these selectively de-bonded embodiments may also be used in combination, in which some portions of the rigid material insert are completely de-bonded from the elastomeric body of the seal and other portions of the rigid material insert are partially de-bonded. Further, in certain embodiments, selectively de-bonded may refer to a portion of the rigid material insert that is never bonded to the elastomeric body to begin with. In this embodiment selected portions of the rigid body may be bonded to the elastomeric body of the seal, with the remaining portions of the rigid insert not bonded to the elastomeric body of the seal.
Referring now to FIGS. 23-25, strain plots of a smoothed seal model having such selective de-bonding are shown. Specifically, the seal model is of a packing unit for an annular blowout preventer, in which packing unit model is initially simulated with a displacement condition as closed about a drillpipe 15 1. Then, the packing unit is shown in an original condition before the packing unit is simulated with the displacement condition, but the strain from the simulated displacement condition is superimposed across packing unit. This technique is similar to FIGS. 19-21 from above. However, the elastomeric body of the seal model in FIGS. 23-25 is additionally selectively de-bonded from a back surface 109B behind a head 109A of metal insert 109.
Referring now to FIG. 23A, a strain plot of the packing unit model with a selectively de-bonded elastomeric body shows the maximum principal log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 23B, a strain plot of the seal model shows the selectively de-bonded packing unit model originally before the displacement condition is simulated across the seal model in FIG. 23A, but the maximum principal log strain plot from FIG. 23A is superimposed across the undistorted seal model. This allows the strain plot to show where the strain concentrations will be located when in an undisplaced condition.
Similarly, referring to FIG. 24A, a strain plot of the packing unit model with a selectively de-bonded elastomeric body shows the axial log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 24B, a strain plot of the seal model shows the selectively de-bonded packing unit model originally before the displacement condition is simulated across the seal model in FIG. 24A, but the axial log strain plot from FIG. 24A is superimposed across the undistorted seal model.
Similarly still, referring to FIG. 25A, a strain plot of the packing unit model with a selectively de-bonded elastomeric body shows the shear log strain occurring in the seal model with a simulated displacement condition of closing the packing unit about drillpipe 151. In FIG. 25B, a strain plot of the seal model shows the selectively de-bonded packing unit model originally before the displacement condition is simulated across the seal model in FIG. 25A, but the shear log strain plot from FIG. 25A is superimposed across the undistorted seal model
Each of the strain plots of the packing unit model with a selectively de-bonded elastomeric body (i.e., FIGS. 23-25) indicates less strain than the strain plots of the packing unit model without selective de-bonding of the elastomeric body (i.e., FIGS. 19-21). Specifically, the volume of the elastomeric body adjacent to the back surface of the head of the rigid material insert indicates less strain in the strain plots of the seal model when the elastomeric body is selectively de-bonded from the rigid material insert, Thus, as shown with the selectively de-bonded packing unit, the seal model may be modified and re-generated to produce an optimized seal model that reduces the location and amount of strain occurring in the seal model.
Further, those having ordinary skill in the art will appreciate that the selectively de-bonded embodiments disclosed herein are not limited to the specific portions, locations, or amounts of de-bonding shown between the rigid material inserts and the elastomeric body of the seal. For example, in one embodiment, a portion of the web of the metal insert in a packing unit may be selectively de-bonded from the elastomeric body. Further, in another example, a portion of the metal insert of a variable bore ram packer may be selectively de-bonded from the elastomeric body.
Similar to above with respect to generating a seal model in step 1220, when simulating displacement conditions across the seal models 1230, it is preferable for the volumes of the seal model and its components to remain substantially constant. If the volumes do not remain constant, the results of the strain plots and simulated strain in FEA may not correlate with experimentally observed results or with one another, thereby providing inaccurate results. For example, if the volume of the seal models of the packing units shown in the strain plots of FIGS. 19-21 changes from the volume of the seal models of the packing units shown in the strain plots of FIGS. 23-25, it would be difficult to compare the strain plots because of the added factor of the changing volume. As the volume of the seal model of the packing unit increases or decreases, the simulated strain in the packing unit inherently changes, independent if the seal model was modified for any improvements.
In step 1250, after being generated, analyzed, and possibly re-generated (if necessary), the seal model may be used to manufacture a seal for a blowout preventer 1250. Specifically, using techniques known in the art, a seal based upon the three-dimensional seal model may be manufactured for use in a blowout preventer, such as a packing unit for an annular blowout preventer or a top seal or variable bore ram packer a ram blowout preventer. For example, the seal model of the packing unit for the annular blowout preventer having the rigid material inserts selectively de-bonded from the elastomeric body, as discussed above and shown in FIGS. 23-25, may be manufactured for use in the industry. The selectively de-bonded packing unit generated in FEA reduced the strain concentrations in the packing unit when in the closed position, as compared to the packing unit shown in FIGS. 19-21. This selectively de-bonded seal model may then be manufactured for use or testing within a blowout preventer because of its improved performance over the other packing unit shown from the FEA.
Those having ordinary skill in the art will appreciate that multiple techniques may be used when manufacturing the selectively de-bonded seal. For example, in one embodiment, a primer may be applied to all of the portions of the rigid material insert which shall be bonded to the elastomeric body, with no or minimal primer applied to the portions of the rigid material insert to be selectively de-bonded from the elastomeric body. Thus, by simply not applying primer to portions of the rigid material insert, a selectively de-bonded seal may be manufactured. Further, in another embodiment, a release agent may be applied to the portions of the rigid material insert that shall be selectively de-bonded from the elastomeric body of the seal. The release agent may assist in preventing the rigid material of the insert from at least partially, if not completely, bonding to the elastomeric body. Typical release agents known in the art are silicon based release agents. Those having ordinary skill in the art will appreciate that these techniques, in addition to others, may be used in combination to vary the degree and location of the selectively de-bonded portions of the seal during manufacturing of the seal.
Aspects of embodiments disclosed herein, such as generating and analyzing a seal model of a seal for a blowout preventer using FEA, may be implemented on any type of computer regardless of the platform being used. For example, as shown in FIG. 26, a networked computer system 3060 that may be used in accordance with an embodiment disclosed herein includes a processor 3062, associated memory 3064, a storage device 3066, and numerous other elements and functionalities typical of today's computers (not shown). Networked computer 3060 may also include input means, such as a keyboard 3068 and a mouse 3070, and output means, such as a monitor 3072. Networked computer system 3060 is connected to a local area network (LAN) or a wide area network (e.g., the Internet) (not shown) via a network interface connection (not shown). Those skilled in the art will appreciate that these input and output means may take many other forms. Additionally, the computer system may not be connected to a network. Further, those skilled in the art will appreciate that one or more elements of aforementioned computer 3060 may be located at a remote location and connected to the other elements over a network.
Advantageously, methods and embodiments disclosed herein may provide improved and more accurate results when using FEA. Methods and embodiments disclosed herein use strain within FEA to determine the performance characteristics of seals for blowout preventers under simulated displacement conditions. This allows the finite elements within the seal model to displace when accommodating large amounts of strain.
Further, methods and embodiments disclosed herein may provide techniques for analyzing, smoothing, simplifying, and modifying seal models for use in FEA. Using these techniques, the accuracy of the results of the strain plots created using FEA may be improved. Additionally, using these techniques, the seal model may be modified to reduce the amount and location of strain (e.g., strain concentrations) occurring in the seal model from the simulated strain plots.
Furthermore, methods and embodiments disclosed herein may provide for a seal for a blowout preventer with an increased working lifespan. For example, the packing unit may be modeled with simulated displacement conditions of repeated closures (i.e., repeatably closing the seal about a drillpipe or itself) to determine design features that may extend the working lifespan (i.e., number of closures) of the packing unit.
While the invention has been described with respect to a limited number of embodiments, those skilled in the art, having benefit of this disclosure, will appreciate that other embodiments may be devised which do not depart from the scope of the invention as disclosed herein. Accordingly, the scope of the invention should be limited only by the attached claims.

Claims

1. A seal of a blowout preventer, comprising:

at least one rigid material insert disposed within an elastomeric body;

wherein at least one portion of the at least one rigid material insert is selectively de-bonded from the elastomeric body.

2. The seal of claim 1, further comprising a release agent applied to the at least one portion of the at least one rigid material insert.

3. The seal of claim 1, wherein the release agent comprises silicon.

4. The seal of claim 1, further comprising a primer applied to a bonded portion of the at least one rigid material insert.

5. The seal of claim 1, wherein the seal comprises a packing unit of an annular blowout preventer.

6. The seal of claim 5, wherein the at least one portion comprises a back surface behind a head of the at least one rigid material insert.

7. The seal of claim 1, wherein the seal comprises a top seal of a ram blowout preventer.

8. The seal of claim 1, wherein the seal comprises a variable bore ram packer of a ram blowout preventer.

9. A method of manufacturing a seal of a blowout preventer, the method comprising:

generating a finite element analysis seal model;

analyzing a strain plot of the finite element analysis seal model based on a displacement condition;

identifying in the finite element analysis seal model at least one portion of at least one rigid material insert to selectively de-bond from an elastomeric body; and

manufacturing the seal with the identified at least one portion of the at least one rigid material insert selectively de-bonded from the elastomeric body.

10. The method of claim 9, wherein the manufacturing comprises:

applying a release agent to selectively de-bond the at least one portion of the at least one rigid material insert from the elastomeric body of the manufactured seal.

11. The method of claim 9, wherein the manufacturing comprises:

applying a primer to the seal to a bonded portion of the at least one rigid material insert of the manufactured seal.

12. An annular blowout preventer, comprising:

a housing;

a piston chamber formed in the housing;

a piston disposed within the piston chamber; and

a packing unit disposed adjacent to the piston, the packing unit comprising;

an elastomeric body; and

at least one rigid material insert disposed within the elastomeric body;

13. The seal of claim 12, wherein the at least one portion of the at least one rigid material insert further comprises a back surface behind a head of the at least one rigid material insert.

14. The seal of claim 12, further comprising a release agent applied to the at least one portion of the at least one rigid material insert.

15. The seal of claim 14, wherein the release agent comprises silicon.

16. The seal of claim 12, further comprising a primer applied to a bonded portion of the at least one rigid material insert.