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    • 专利摘要:
    TENSIONER TO MAINTAIN A TRACTION FORCE IN A RISER AND METHOD FOR TENSIONING A RISER. The present invention relates in general to marine riser tensioners and, in particular, to a RAM style lifting tensioner that accommodates the riser slope. The tensioner (11) to maintain a tensile force in a riser (13), which has a geometric axis (39) and which extends from an underwater wellhead assembly through an opening (15) in a deck floating platform (17), comprises a tensioning ring (21) coupled to the riser (13); a plurality of hydropneumatic cylinders (35), each of which has flexible joints (33) at opposite ends for coupling the cylinders (35) between the deck (17) and the tensioning ring (21); the plurality of hydropneumatic cylinders (35) movable in at least one plane between an operating position and a remote activation tensioning position; and cylinders (35) adapted to automatically engage the tensioning ring (21) after moving from the operating position to the tensioning position.
    公开号:BR102012003065B1
    申请号:R102012003065-9
    申请日:2012-02-10
    公开日:2020-10-20
    发明作者:Bulent Aksel；Steven Matthew Wong；Tsorng-Jong Maa；Joseph William Pallini, Jr
    申请人:Vetco Gray Inc；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION
    [001] The present invention relates in general to risermarine tensioners and, in particular, to a RAM style lifting tensioner that accommodates the riser inclination. BACKGROUND OF THE INVENTION
    [002] Offshore production platforms must support production rise columns from oil or gas wells that extend to the platform from underwater wells. For platforms that are fixed to the ocean floor, this is readily accomplished and is well known in the prior art. However, for underwater conclusions in deep waters that require the use of floating platforms, such as tension leg platforms (TLPs) or semi-submersible platforms, support risers present significant problems. These platforms move under the influence of waves, wind, and current and are subjected to various forces. Therefore, the riser tensioning mechanism should allow the platform to move in relation to the riser.
    [003] The riser tensioning mechanism must also maintain the riser under tension so that the entire weight of the riser is transferred to the wellhead and so that the riser collapses under its own weight. The tensioning mechanism must then exert a continuous tensioning force on the riser. Also, this force must be kept within a narrow tolerance.
    [004] The lifting tensioners have several advantages in subsea applications, one of them in which the tensioner accommodates larger loads in a smaller space in relation to other types of tensioners. This is partly because lifting tensioners use a more efficient piston end and do not require a tension pull device on the end connection. In addition, the pressure in lifting tensioners does not act on the rod side of the cylinder. Where the seas are rough, and the floating platform is subjected to a wide range of vertical movement, the lifting tensioners are better able to accommodate such vertical movement. In addition, the use of a lifting tensioner can minimize the corrosive effects of the saltwater environment in which they must operate because the tensioner's high pressure seals are not located adjacent to the atmosphere and are isolated from fluids and caustic debris.
    [005] TLPs provide stable drilling platforms in deeper waters. In TLPs, the tension legs extend from the platform below to an anchor located on the seabed. The tension legs are relatively inflexible, meaning that much of the vertical movement of the platform is eliminated. TLPs allow location of the wellhead assembly on the surface rather than on the seabed. A riservai typically extends from the wellhead assembly below to the bottom of the sea. This configuration allows simpler well completion and better production control. However, in TLPs, the riser can tilt vertically in relation to TLP. The amount of inclination of riserverticalmente is not static and varies with the time during the operation.
    [006] Although the use of both TLPs and RAM type hoisting tensioners is desired, due to the variant riser slope, RAM-style hoisting tensioners built so far are not currently suitable for use with TLPs. In all previous RAM systems, the cylinders remain in line with the riser, which allows for small spacing of the riser columns. Although the small size of the RAM-style lifting tensioner is desirable, the small size also causes a problem in that it limits the size of the passage in which the riser can be aligned. Therefore, there is a need for a riser tensioner that can tilt with the riser to allow adequate space for aligning a riser for use in a TLP. DESCRIPTION OF THE INVENTION
    [007] These and other problems are generally solved or circumvented, and technical advantages are generally achieved, by the preferred embodiments of the present invention which provides a risermarine tensioner, and a method for using the same.
    [008] In accordance with an embodiment of the present invention, a tensioner for maintaining a tensile force in a riser has a geometric axis is disclosed. The riserse extends from an underwater wellhead assembly through an opening in a floating platform deck. The tensioner comprises a tensioning ring coupled to the riser, and a plurality of hydropneumatic cylinders. Each hydropneumatic cylinder has flexible joints at opposite ends to couple the cylinder between the deck and the tensioning ring. The plurality of hydropneumatic cylinders is movable by remote actuation in at least one plane between an aligned position and a tensioning position. The cylinders are adapted to automatically attach to the tensioning ring after moving from the aligned position to the tensioning position.
    [009] According to another embodiment of the present invention, a tensioner for maintaining a tension force in a riser has a geometric axis is disclosed. The riserse extends from an underwater wellhead assembly through an opening in a floating platform deck. The tensioner comprises a tensioning ring for coupling to the riser, and a plurality of hydropneumatic cylinders. The hydropneumatic cylinders extend between the deck and the tensioning ring. The tensioner also includes a guide bearing assembly that is adapted to mount on the deck and roll along the riser. A conductive sleeve extends from the tensioning ring parallel to the riser and is adapted to interface with the bearings in the guide bearing assembly. When the riser rises in relation to the deck, the conductive sleeve will resist the rotation of the tensioner through reaction forces exerted by the guide bearing assembly while allowing the rotation of the riser in relation to the tensioning ring.
    [010] In accordance with yet another embodiment of the present invention, a method for intending a riserque passes through an opening in a platform deck is disclosed. The method comprises placing a plurality of hydropneumatic cylinders around the opening in the deck. The cylinders are then flexibly connected to a first end on the deck. The method then moves the cylinders from an aligned position perpendicular to the deck to a tensioning position at an angle to the deck. After moving the cylinders to the tensioning position, the method automatically engages a second end of each cylinder to a tensioning ring attached to the riser. As the riser tilts relative to the platform, the method allows the cylinders to move in more than a plan to accommodate the riser slope.
    [011] An advantage of a preferred embodiment is that a lifting tensioner can accommodate the variant slope of a riser that extends from an underwater environment to a tension leg platform (TLP). The disclosed achievements allow the maximum space to be used to guide the riser, although still inserting into a smaller footprint compared to other conventional tensioners. Also, the achievements disclosed accommodate a greater range of vertical movement between risere and TLP. The disclosed achievements also allow for higher tensioner loads and reduced corrosion events while allowing lifting tensioners to be used with TLPs. BRIEF DESCRIPTION OF THE DRAWINGS
    [012] Just as the resources, advantages and objectives of the invention, as well as others will be apparent, are achieved, and can be understood in more detail, a more particular description of the invention briefly summarized above can be given as a reference to the achievements of the same which are illustrated in the accompanying drawings that form a part of this specification. It should be noted, however, that the drawings illustrate only one preferred embodiment of the invention and therefore should not be considered as limiting its scope since the invention can admit other equally effective realizations.
    [013] Figure 1 is a perspective view of a riser tensioner assembly according to an embodiment of the present invention.
    [014] Figure 2 is a cross-sectional view of the riser tensioner assembly of Figure 1 taken along line 2—2.
    [015] Figure 3 is a top view of the Figure 1 riser tensioner assembly that illustrates the cylinder alignment of the Figure 1 riser tensioner assembly.
    [016] Figure 4 is a top view of an alternative embodiment of the Figure 1 riser assembly that illustrates an alternate cylinder alignment of the Figure 1 riser assembly.
    [017] Figure 5 is a partial view of a cylinder assembly of Figure 1 in a first position.
    [018] Figure 6 is a partial view of the cylinder assembly of Figure 5 in a second position.
    [019] Figures 7, 8A, and 9 schematically illustrate the movement of the cylinders in Figure 1 from an aligned position to a tensioning position.
    [020] Figures 8B to 8E schematically illustrate alternative embodiments of an automatic coupling apparatus for coupling the cylinders of Figure 1 to a tensioning ring of Figure 1.
    [021] Figure 10 illustrates the Figure 1 riser tensioner assembly that accommodates the riser slope according to an embodiment of the present invention.
    [022] Figure 11 is a cross-sectional view of the Figure 10 riser tensioner assembly taken along line 11 —11.
    [023] Figures 12A and 12B are side and top views, respectively, of an alternative embodiment of the riser tensioner assembly of Figure 1.
    [024] Figures 13A and 13B are side and top views, respectively, of an alternative embodiment of the riser tensioner assembly of Figure 1.
    [025] Figures 14A and 14B are side and top cross-sectional views, respectively, of an alternative embodiment of the riser tensioner assembly of Figure 1. DESCRIPTION OF REALIZATIONS OF THE INVENTION
    [026] The present invention will now be described more fully hereinafter with reference to the accompanying drawings illustrating embodiments of the invention. This invention can, however, be incorporated in many different forms and should not be recognized as limited to the illustrated achievements set forth here. Instead, these achievements are provided so that this disclosure is complete and complete, and will fully communicate the scope of the invention to a person skilled in the art. Related numbers refer to related elements, and the main notation, if used, indicates similar elements in alternative embodiments.
    [027] In the following discussion, several specific details are established to provide a comprehensive understanding of the present invention. However, it will be obvious to one skilled in the art that the present invention can be practiced without such specific details. In addition, for the most part, details regarding well drilling, descent operations, and the like have been omitted in many of these details as they are not considered necessary to obtain a complete understanding of the present invention, and are considered part of the skills of a technician on the subject.
    [028] With reference to Figure 1 and Figure 2, a riser tensioner assembly11 supplies tension to a riser13 that has its lower end attached to the subsea equipment like an subsea wellhead assembly (not shown). The riser tensioner assembly11 has a tensioning position, shown in Figures 1 to 4, 8A, and 9 to 14, and an aligned position, shown in Figures 5, and 7. In the aligned position, cylinder assemblies 19 are decoupled from the tensioning ring 21 and placed in a vertical position perpendicular to a deck 17 as shown in Figure 5 and Figure 7 and described in more detail below. In this way, the riser tensioner assembly 11 is released from an opening 15 on deck 17, allowing the maximum amount of space to align the riser13 and the equipment attached to the riser.
    [029] The riser13 extends upward through opening 15 on deck 17 of a vessel (not shown). Although anchored, deck 17, that is, the vessel, will typically move relative to the riser13 in response to current and wave movement. A plurality of cylinder assemblies 19 are provided with fluid and hydraulic gas under pressure to provide an upward force to the riser13 to maintain uniform tension in the riser13 as deck 17 moves relative to the riser13. Six sets of cylinder 19 are shown in this invention for clarity of explanation. One skilled in the art will understand that more or less cylinder assemblies 19 may be used.
    [030] A lower end of each cylinder assembly 19 attaches to deck 17 and an upper end removably attaches to a tension ring 21. The tension ring 21 is an object similar to an annular disk that can attach to the riser13 so that the tensioning ring 21 is coaxial with a geometric axis 39 that passes through the riser13. The tensioning ring 21 can also be threaded to the riser13 or a riser tensioner joint as described in more detail below. One skilled in the art will understand that riser 13 can refer to the riser that extends between the wellhead and the drilling rig or a riser tensioner joint coupled to the riser13 next to the riser tensioner assembly11.
    [031] The lower ends of each cylinder assembly 19 are placed circumferentially around the opening 15. In the illustrated embodiment, the lower ends of each cylinder are coupled to an edge of the opening 15, such that the diameter of a circle having a the edge that passes through each lower end coupling location of each cylinder assembly 19 will be larger than the diameter of the tensioning ring 21. In this way, the riser tensioner assembly11 will not tip over at the maximum expected inclination of the riser13. One skilled in the art will understand that the lower end of each cylinder assembly 19 may engage deck 17 a greater distance from opening 15 as necessary such that the lower ends of cylinder assemblies 19 will not engage deck 17 directly below the deck. tension ring 21 when riser13 is in a non-tilted state. In addition, the riser tensioner assembly 11 may include an anti-displacement assembly or guide assembly 23 employed to guide or center the riser13 in the opening 15. The guide assembly 23 is mounted around the riser13 while in the tensioning position for engagement with the riser13, or to a riser-mounted component13.
    [032] Each cylinder assembly 19 includes a coupler 33 at each end of a cylinder 35. Each cylinder 35 has a barrel and a rod, allowing each cylinder 35 to move between a contracted position shown in Figure 8A, and an extended position shown in Figure 9. In the extended position, the top end of each cylinder 35 moves away from the respective bottom end of each cylinder 35, and in the contracted position, the top end of each cylinder 35 moves close to the bottom end of each cylinder 35. The lower end of each cylinder 35 is pivotally coupled to deck 17 with coupler 33, as shown in the ball and socket joint. In the exemplary embodiment, the cylinder 35 can rotate on the lower coupler 33. Similarly, each cylinder 35 is coupled to the tensioning ring 21 with the coupler 33, as the ball and socket joint illustrated. As with the lower coupler 33, the upper coupler 33 allows the cylinder 35 to rotate over the upper coupler 33. The cylinder 35 can rotate over each coupler 33 in one or more planes. For example, cylinder 35 can rotate in three dimensions defined by three perpendicular geometric axes that have an origin in each coupler 33. In this way, cylinder 35 can rotate in one or more planes, and preferably in unlimited planes, as the deck 17 moves in relation to the riser13.
    [033] Turning on the couplers 33 will occur as deck 17 and riser13 move relative to each other. Therefore, as riser 13 tilts away from the vertical in relation to deck 17, tensioner ring 21 will move from the position shown in Figure 1. In an exemplary embodiment, riser13 and tensioner ring 21 can occupy variably the position shown in Figures 10 and 11. As shown in Figures 10 and 11, cylinders 35 will rotate on the upper and lower couplers 33 to maintain connection with both deck 17 and tension ring 21. Each cylinder will extend, contract, and it will rotate as necessary to remain coupled with tensioning ring 21 and deck 17. Similarly, as the riser13 tilts, each cylinder will contract, expand and rotate as needed to exert a tensioning force on the riser13.
    [034] As shown in Figure 1, each cylinder assembly 19 also includes a mechanical bulkhead 31 that mounts to deck 17 adjacent to each cylinder 35. Each mechanical bulkhead 31 extends vertically from deck 17 and defines a partial cylindrical receptacle 37 facing opening 15 on deck 17. Receptacle 37 extends the length of mechanical bulkhead 31 and is of a size and shape to receive cylinder 35 when cylinder 35 rotates to a position that is perpendicular to deck 17 as shown in Figures 5 and 7. When the cylinder 35 is in the perpendicular position, a surface of the cylinder 35 will confine the receptacle 37. In the event that the riser inclination13 tries to push the cylinder 35 beyond the perpendicular position away from the opening 15 and towards at a surface of deck 17, the mechanical bulkhead 31 will exert a reaction force against cylinder 35, keeping cylinder 35 in a perpendicular position.
    [035] The exemplary embodiment of the riser tensioner assembly 11 illustrated in Figure 3 shows the alignment of the cylinders 35 of the cylinder assemblies 19 around the opening 15. As shown in Figure 3, the six cylinders 35 of the exemplary embodiment are arranged around of the opening 15 such that a vertical plane will pass through both ends of each cylinder on the upper and lower couplers 33, and geometry axis 39. For example, a vertical plane that passes through the upper and lower ends of the cylinder 35A on couplers 33 will include the axis 39. Similarly, separate vertical planes that pass through the upper and lower ends of each cylinder 35B, 35C, 35D, 35E, 35F on the couplers 33, respectively, will include the axis 39.
    [036] In an alternative embodiment, illustrated in Figure 4, cylinders 35 comprise three pairs of cylinder 35G and 35G ', 35H and 35H', and 35I and 35I '. In this embodiment, a vertical plane that passes through the ends of each individual cylinder in the couplers 33 will not include the axis 39. Instead, the upper couplers 33 of each cylinder will be displaced from the position described in Figure 3, with the coupler 33 of each cylinder stop displaced by an equivalent amount in opposite directions. For example, the lower couplers 33 are mounted around the opening 15 as described above with respect to Figure 3. However, in Figure 4, the upper couplers 33 of each cylinder 35 are not mounted around the tensioning ring 21 in a vertical plane. that passes through the geometry axis 39 and the lower couplers 33. As shown in Figure 4, a vertical plane 42 passes through the lower coupler 33 of the cylinder 35G and the geometric axis 39. Another vertical plane 40 passes through the lower coupler 33 of the cylinder 35G and the upper coupler 33 of the 35G cylinder. The plane 42 and the plane 40 form angle α in the lower coupler 33 of the cylinder 35G. The matched cylinder 35G 'will be moved in a similar way in the opposite direction. For example, a vertical plane 44 passes through the lower coupler 33 of the cylinder 35G 'and the geometric axis 39. Another vertical plane 46 passes through the lower coupler 33 of the cylinder 35G' and the upper coupler of the cylinder 35G '. Plane 44 and plane 46 will form angle - α in the lower coupler 33 of cylinder 35G '. In a similar manner, the upper coupler 33 of the cylinder 35H will be displaced at an angle y, θ the upper coupler 33 of the cylinder 35H 'will be displaced at an angle -y. The upper coupler 33 of cylinder 35I will be displaced at an angle β, and the upper coupler of cylinder 35I 'will be displaced at an angle -β.
    [037] By moving each cylinder in the pair in opposite directions, as illustrated in the figure 4, additional torsional stability is achieved. Therefore, if the vessel turns on the riser13, while a cylinder in the pair can intensify the rotation, the opposite cylinder in the pair will react to reduce rotation. For example, if deck 17 rotates clockwise with respect to riser 13 from the position shown in Figure 4, the force exerted on tensioner ring 21 and riser13 by cylinder 35H 'will accelerate rotation; however, as cylinder 35H is moved an equal amount in the opposite direction from cylinder 35H ', the force exerted on the tensioning ring 21 and riser13 by cylinder 35H will neutralize the accelerated rotation by cylinder 35H'. The same is true for 35G and 35G ', and 35I and 35I' cylinder pairs.
    [038] As shown in Figure 5 and Figure 6, cylinder assembly 19 includes a placement assembly 51. In the illustrated embodiment, placement assembly 51 includes a placement cylinder 53, a coupling cylinder 55, and a rigid coupler 57 The rigid coupler 57 mates with an upper end of the mechanical bulkhead 31 and provides a mounting point for a first end of the roll cylinder 53. The rigid coupler 57 can comprise a pin assembly, a screwed support assembly or any other suitable coupling device. The rigid coupler 57 is located at a sufficient distance from receptacle 37 such that when cylinder 35 is perpendicular to deck 17, a surface of cylinder 35 can come into contact with a surface of receptacle 37 and allows the placement cylinder 53 remain attached to cylinder 35 while in the aligned position. A second end of the delivery cylinder 53 is coupled to the coupling cylinder 55. The coupling cylinder 55 is coupled to the cylinder 35 such that the placing cylinder 53 will exert a force on cylinder 35. The placing cylinder 53 acts to move the cylinder 35 to from the aligned position perpendicular to deck 17, shown in Figure 5, to the angled tensioning position on board towards opening 15, shown in Figure 6. Once the placement cylinders 35 are in the tensioning position, the placement cylinders 53 no longer operate. In an exemplary embodiment, after placing the cylinders 35 in the tensioning position of Figure 6 and coupling the tensioning ring 21 to the cylinders 35, as shown in Figure 8A and described below, the placing cylinders 35 can be uncoupled from the cylinders 35 .
    [039] Once the alignment of the riser13 is complete, the cylinder assemblies 19 are tilted in the tensioning position shown in Figures 1 to 4, 6, and 8 to 11, by the placement cylinders 53. In the exemplary embodiment, the cylinders of Placement 53 are hydraulic cylinders that can be actuated by an operator to move cylinders 35 from the aligned position to the tensioning position. Preferably, the actuation process is remotely operated by any suitable control mechanism, such as a hydraulic pressure system, electronic control system, or the like. One skilled in the art will understand that the illustrated set 51 is nothing more than an example of a mechanism for moving cylinders 35 from the aligned position of Figure 5 to the tensioning position of Figure 6. Alternative assemblies may include H mold assemblies , screw assemblies, or the like adapted to operate as described above with respect to the hydraulic cylinder placement assembly 51. These additional achievements are contemplated and included by the disclosed achievements.
    [040] Tension ring 21 can attach to riser13 next to riser11 tensioner assembly and be aligned on riser13 next to riser11 tensioner assembly. The cylinders 35 of the cylinder assemblies 19 then rotate towards the riser13, as shown in Figure 6, and attach to the tensioning ring 21, as shown in Figure 8A. The coupling of the cylinders 35 of the cylinder assemblies 19 to the tensioning ring 21 will occur in an automatic manner such that as the tensioning ring 21 descends in the riser13 following the placement of the cylinders 35 in the tensioning position of Figure 6 by the placing assemblies 51 , the couplers 33 at the upper ends of the cylinders 35 will automatically engage the coupler receptacles on a lower side of the tension ring 21.
    [041] One way in which the cylinders 35 can be coupled to the tensioning ring 21 is illustrated in Figure 8B. The tensioning ring 21 can include a plurality of orientation receptacles 22, an orientation receptacle 22 corresponding to each cylinder 35. The orientation receptacles 22 have a tapered lower end 24 that transitions from an end of larger diameter to a diameter a cylindrical tube 26 where the guide receptacles 22 join the lower portion of the tensioning ring 21. The cylindrical tube 26 defines an annular lock channel 28 on an inner diameter surface of the cylindrical tube 26. The coupler 33 includes a seat ball 30 which defines an upper semi-spherical cavity 32. Coupler 33 also includes a ball retainer 54 which defines a lower semi-spherical cavity 56. Ball retainer 54 has a conical opening 34 at a lower end of ball retainer 54. The cavity 32 and the cavity 56 define a spherical cavity of a diameter substantially equal to the diameter of a ball of the coupler 33, as illustrated, that t in an opening in a lower portion of the cavity 56 such that the opening has a narrower diameter than the cavities 32, 56. The conical opening 34 transitions from a diameter on a lower surface of the ball retainer 54 to the diameter narrower of the cavity opening 56. After the ball end of the coupler 33 is inserted into the cavity 32, the ball retainer 54 will be attached to the ball seat 30 through the matching threads 58. The coupler 33 can rotate on the ball through the strip of movement allowed by the conical opening 34 in the ball retainer 54. In the illustrated embodiment, the coupler ball 33 will be inserted into the ball seat 30 before placing the cylinder 35 in the tensioning position of Figure 6, and preferably during the assembly of the tensioner from riser11. A locking ring 36 is coupled around an outer diameter portion of the ball seat 30 and is adapted to insert into the lock channel 28 when the ball seat 30 is moved into the cylindrical tube 26, thereby coupling the cylinder 35 to the tension ring 21.
    [042] A person skilled in the art will understand that this can be achieved without manual insertion by an operator as the tensioning ring 21 descends on the riser13 next to the cylinders 35. After movement of the cylinders 35 by the placing assemblies 51 to the tensioning position Figure 6, the ball seat 30 will be close to the tapered lower end 24 of the guide receptacle 22. As the tension ring 21 moves axially downwards towards the cylinders 35, the ball seat 30 will be in contact and will slide along the inner surface of the conical lower end 24 until it reaches the cylindrical tube 26. There, the ball seat 30 will land and substantially fill the cylindrical tube 26, causing the lock ring 36 to insert into the lock channel 28, securing the cylinder 35 to tensioner ring 21 while allowing cylinder 35 to rotate over coupler 33. One skilled in the art will understand that each cylinder may extend or contact var as necessary to insert into the orientation receptacle 22.
    [043] In an alternative embodiment, shown in Figure 8C, coupler 33 'comprises a cylindrical upper end of cylinder 35. Orientation receptacle 22' is similar and includes components of orientation coupler 22 of Figure 8B. As shown in Figure 8C, the orientation coupler 22 'includes a fork hook 38 mounted on an upper portion of the cylindrical tube 26'. Tension ring 21 defines a recess 50 that extends from the bottom surface of tension ring 21 inward enough to accommodate fork hook 38 and a pin 48. Pin 48 passes through fork hook 38 and is secured at any end within the recess 50 to the tensioning ring 21 such that a load can be transferred between the orientation receptacle 22 'and tensioning ring 21 through the fork 38 and the pin 48.
    [044] Similar to that described above with respect to Figure 8B, after movement of the cylinders 35 by the placement assemblies 51 to the tensioning position of Figure 6, the coupler 33 'will be close to the conical lower end 24' of the orientation receptacle 22 ' . As the tension ring 21 moves axially downward towards the cylinders 35, the coupler 33 'will contact and slide along the inner surface of the conical lower end 24' until it reaches the cylindrical tube 26 '. There, the coupler 33 'will land and substantially fill the cylindrical tube 26', causing the lock ring 36 'to insert into the lock channel 28', attaching cylinder 35 to tensioner ring 21 while allowing cylinder 35 to turn over the coupler 33 'on the fork 38 and the pin 48.
    [045] One skilled in the art will understand that the apparatus described above with respect to Figures 8B and 8C are just examples of a mechanism for attaching cylinders 35 to the tension ring 21 without direct manual manipulation by an operator. One skilled in the art will understand that any suitable means for attaching cylinders 35 to the tensioning ring 21 after placing the cylinders 35 in the tensioning position is contemplated and included in the disclosed embodiments. Preferably, the lift mechanism will be free of direct manual manipulation by an operator although the lift mechanism may include remote operator manipulation.
    [046] As shown in Figure 8D, lock ring 36 and lock channel 28 can operate as described below. A retraction ring 52 can circumscribe the ball seat 30. The retraction ring 52 will attach to the ball seat 30 such that the retraction ring 52 can move axially along the outer surface of the ball seat 30. The retraction 52 can move axially by rotating through threads on an inner diameter of retraction ring 52 that matches the corresponding threads on an outer diameter of ball seat 30. Alternatively, the retraction ring can slide axially through the tooth ratchet, or can move axially in any other suitable way. The retraction ring 52 can optionally be guided to a lower position shown in Figure 8D. Locking ring 36 mounts on ball seat 30 within an annular channel axially above retraction ring 52. A mounting ring can attach to an outer portion of ball seat 30 and extend into the ball seat channel 30 to prevent locking ring 36 from moving radially completely out of the channel on ball seat 30. Preferably, locking ring 36 is guided to an engaged position shown in Figure 8D. In the illustrated embodiment, the locking ring 36 is a broken ring adapted to be guided to the engaged position. One skilled in the art will understand that other suitable guidance methods are contemplated and included in the disclosed achievements.
    [047] As shown in Figure 8D, the outer diameter of the lock ring 52 has a profile adapted to engage a matching profile of the lock channel 28. The matching profiles are adapted to allow the lock ring 36 to move axially upward from an area below the lock channel 28 to an area above the lock channel 28 when the lock ring 36 is in the engaged position of Figure 8D, while engaging to prevent the lock ring 36 from moving from the area above the lock channel 28 to the area below the lock channel 28 when the lock ring 36 is in the engaged position illustrated in Figure 8D. When the ball seat 30 inserts into the guide receptacle 22, the lock ring 36 will slide past the matching profile of the lock channel 28 and then engage the matching profile of the lock channel 28 to secure the cylinder 35 to the tension ring 21. One skilled in the art will understand that the illustrated example is just a mechanism for attaching cylinder 35 to tension ring 21. Any suitable method that secures cylinder 35 to tension ring 21 without direct manual manipulation is contemplated and included in the disclosed embodiments.
    [048] As shown in Figure 8E, cylinder 35 can be released by moving retraction ring 52 up axially relative to ball seat 30. This can be accomplished by rotating retraction ring 52 around ball seat 30 through the illustrated threads. This will cause one end of the retraction ring 52 to engage a tapered edge of the lock ring 36. Continued upward movement of the retraction ring 52 will cause the engaged surfaces to slide apart from one another and move the lock ring 36 radially. into the ball seat channel 30. In this way, the tensioning ring 21 can be released from the cylinder 35 for later operations. One skilled in the art will understand that the illustrated embodiment is just one example of a mechanism for releasing cylinder 35 from coupling with tension ring 21. Any suitable method that releases cylinder 35 from tension ring 21 is contemplated and included in the disclosed embodiments. Preferably, the mechanism will include direct manual manipulation of the release mechanism through direct operator contact or manipulation by the operator of a hand tool.
    [049] Referring again to Figures 1 and 2, the guide assembly 23 includes a cylindrical sleeve 25 mounted around the riser13. The sleeve 25 is rigidly fixed to and involves an external surface of the riser13 so that the sleeve 25 does not move axially or rotationally in relation to the riser13 and can therefore be considered as part of the riser13. The sleeve 25 is longer than the maximum stroke of the cylinder assemblies 19 from the contracted to extended positions of each cylinder 35 such that the bearings 47, described in more detail below, remain engaged with the sleeve 25.
    [050] The sleeve 25 may have a flange 27 at its upper and lower ends that extend radially outwardly. An axially extending key or spline 29 is mounted on the outside of sleeve 25 and extends from the lower flange 27 (Figure 2) to the upper flange 27. The spline 29 can be fixed by welding or clamps. The groove 29 can have a rectangular configuration or other cross-sectional configuration.
    [051] As shown in Figure 1 and Figure 2, the guide assembly 23 also includes rigid horizontal members 41, each has a first end that pivotally engages deck 17. In an exemplary embodiment, the rigid horizontal members 41 meet dock directly to deck 17 in any suitable manner. In an alternative embodiment, the rigid horizontal members 41 can be coupled to a plate 43 (Figure 1) coupled to the mechanical bulkhead 31. The plate 43 can include a separate object from the mechanical bulkhead 31 that is later welded or even coupled to the bulkhead mechanical 31. Plate 43 can also be an integral component of mechanical bulkhead 31 formed as a part of mechanical bulkhead 31. In the illustrated embodiment, plate 43 extends from a vertical portion of mechanical bulkhead 31 adjacent to opening 37. A Plate 43 does not inhibit the movement of cylinder 35 in reinforcement with receptacle 37. One skilled in the art will understand that any mechanism suitable for mounting rigid horizontal members 41 to deck 17 such that they can operate as described in this invention is contemplated and included in the embodiments. disclosed.
    [052] A second end of the rigid horizontal members 41 includes a bearing assembly 45 aligned with sleeve 25. As shown in Figure 2, bearing assembly 45 includes bearing 47. Bearing 47, can optionally comprise two bearings as illustrated in Figures 12 to 14. As shown in Figure 2, bearing 47 engages with sleeve surface 25 and allows sleeve 25 to move axially along geometry axis 39; however, any attempt at lateral displacement in a radial direction from the geometry axis 39 is limited by the rigid horizontal members 41. Optionally, the bearing set 45 includes a rigid alignment set 49 (Figure 1) that extends along of the circumference of the sleeve 25 and engages the spline 29, thereby preventing rotation of the sleeve 25 relative to the guide assembly 23. While limiting rotation and radial or lateral displacement, the guide assembly 23 allows the riser13 to rotate over the ends of the horizontal members rigid 41, then allows the riser13 to tilt relative to deck 17.
    [053] In an alternative embodiment, shown in Figures 12A and 12B, a conductive sleeve 61 extends axially downward parallel to the geometric axis 39 from a lower portion of the tensioning ring 21. In the illustrated embodiment, the conductive sleeve 61 does not enter in contact with the outer surface of the riser13. The conductive sleeve 61 defines an annular space between the outer surface of the riser13 and the inner surface of the conductive sleeve 61. The grooves 63 are formed on the outer surface of the conductive sleeve 61 and extend the length of the conductive sleeve 61 parallel to the geometric axis 39. As shown in Figure 12B, the bearings 47 of the guide assembly 23 interface with the conductive sleeve surface 61 between each groove 63. The conductive sleeve 61 has sufficient material strength to withstand permanent deformation or failure when subjected to a reaction force radial exerted by the guide assembly 23 as the riser13 tilts. An optional support ring 64 can be attached to the riser13 within the ring between the conductive sleeve 61 and the riser13 next to the bearings 47 to provide additional lateral support to the conductive sleeve 61. As described above, when the riser13 tries to move radially in the opening 15 relative to deck 17, the bearings 47 of the guide assembly 23 will exert a reaction force against the conductive sleeve 61 to limit lateral displacement in the radial direction. In this way, the inclination of the riser13 can be accommodated without allowing the displacement of the riser13 in the opening 15 which can cause the riser13 to come into contact with deck 17, damaging both deck 17 and riser13.
    [054] Rigid alignment assemblies 49 can be mounted on the end of each rigid horizontal guide member 41 so that one end of each optional rigid alignment assembly 49 is next to an adjacent groove 63. In this way, the Conductive sleeve 61 rotation is prevented by rigid alignment sets 49. As conductive sleeve 61 attempts to rotate in relation to deck 17 and riser tensioner assembly11, splines 63 will press against rigid alignment sets 49. Rigid alignment sets 49 will be of sufficient strength to withstand rotation without significant deformation or failure. Similarly, the coupling of the rigid horizontal members 41 to deck 17 on plate 43 will be of sufficient strength to provide a repetitive reaction force to the rotating force of the conductive sleeve 61 without significant deformation or failure. Rigid alignment assemblies 49 may include rollers at the ends of adjacent grooves 63 to allow grooves 63 to move axially above rigid alignment assemblies 49. The reaction rotation force exerted against 63 will prevent the riser tensioner assembly11 rotate with the riser13. Thus, the torque generated in the riser tensioner set11 will not be transmitted to the riser13, and similarly, the torque generated in the riser13 will not be transmitted to the riser tensioner set11.
    [055] Referring again to Figure 12A, the tensioning ring 21 can be attached to the riser13 as described above with respect to Figures 1 to 11; or alternatively, the riser13 may include a riser tensioner joint 65. The riser tensioner joint 65 will engage in alignment with the riser13 in any suitable manner so that the tensioner joint 65 is brought close to the riser tensioner assembly11. The riser tensioner joint13 includes a thread 67 on an outer surface of the riser tensioner joint65. In the illustrated embodiment of Figure 12A, tension ring 21 will have a corresponding thread 69 formed on a surface of inner diameter of tension ring 21 so that tension ring 21 can be threaded on the riser tensioner joint 65 to the position shown in Figure 12A. If an external force causes the riser13 to rotate relative to deck 17, the rotational force will be reflected by the rigid alignment sets 49, the grooves 63 of the conductive sleeve 61, and the frictional forces at the thread interface 67, 69. Similarly , if the cylinders 35 transmit a rotation to the riser13, the rotational force will be reflected by the rigid alignment assemblies 49, the grooves 63 of the conductive sleeve 61, and the frictional forces at the thread interface 67, 69. The inclination of the riser13 will still be accommodated according to the riser13 it can articulate or tilt over the ends of the rollers 47 of the rigid horizontal members 41 that are in contact with the sleeve 61.
    [056] In another embodiment, illustrated in Figure 13A and 13B, u-shaped channels 71 are formed on the surface of the conductive sleeve 61. The U-shaped channels 71 extend along the axial length of the conductive sleeve 61 parallel to the geometric axis 39. A bearing 47 of each guide assembly 23 will substantially fill a width between the legs of each corresponding U-shaped channel 71. Similar to the grooves 63 of Figures 12A and 12B, the rollers 47 will exert a reaction force on the conductive sleeve 61 through the U-shaped channels 71 to prevent the rotation of the conductive sleeve 61. When combined with the threaded tensioning ring 21, the U-shaped channels 71 will prevent the transfer of rotational movement of the riser13 in relation to deck 17, and the movement rotationally transferred by the cylinders 35 to the riser13 in the same way as the grooves 63 of Figure 12A and 12B.
    [057] In another alternative embodiment, illustrated in Figure 14A and 14B, the conductive sleeve 61 defines slits 73 that extend from the outer surface of the conductive sleeve 61 to the inner diameter surface of the conductive sleeve 61. The slits 73 extend in axial length of the conductive sleeve 61 parallel to the geometric axis 39. A bearing 47 of each guide assembly 23 will substantially fill a width of each slot 73. Similar to the grooves 63 of Figures 12A and 12B and U-shaped channels 71 of Figures 13A and 13B, the rollers 47 will exert a reaction force on the conductive sleeve 61 through the slots 73 to prevent the rotation of the conductive sleeve 61. When combined with the threaded tensioning ring 21, the slots 73 will prevent the transfer of rotational movement of the riser13 in relation to deck 17 and rotational movement transferred by the cylinders 35 to the riser13 in the same way as the grooves 63 of Figures 12A and 12B, and the U-shaped channels 71 of Figures 13A and 13B.
    [058] As shown in Figure 9, once the cylinders 35 are rotated and coupled to the tensioner ring 21, the riser tensioner assembly11 maintains an upward axial force on the riser13 by expanding and contracting the cylinders 35 of the cylinder assemblies 19, so that deck 17 moves, the riser13 will substantially maintain its position in relation to the wellhead assembly (not shown) and the submarine soil. The riser13 will not catch or detach in response to the movement of deck 17. Additionally, the riser11 tensioner assembly can accommodate varying inclination of the riser13. As shown in Figure 10 and Figure 11, as the riser13 tilts in relation to deck 17, so that the geometry axis 39 does not meet a horizontal plane of deck 17 at a substantially perpendicular angle, the cylinders 35 of the cylinder assembly 19 are they will articulate in the upper and lower couplers 33, allowing the cylinders 35 to maintain the engagement with the tensioning ring 21.
    [059] As shown in Figures 10 and 11, each cylinder 35 of cylinder assemblies 19 will expand or contract a variable amount while pivoting on couplers 33. For example, as shown in Figure 10, the riser13 is tilted to the left in relation to deck 17. The cylinders 35 on the right side of Figure 10 are expanded and hinged on board a degree greater than that shown in Figure 8 and Figure 9 to accommodate the relative movement between the riser13 and the deck 17. conversely, cylinders 35 on the left side of Figure 10 contracted and pivoted outboard to a greater degree than shown in Figures 8 and 9 to accommodate the relative movement between the riser13 and deck 17. In this way, the cylinders 35 will continue to exert an axial force on the riser13 that maintains the tension of the riser13. The guide assembly 23 will allow the riser13 to tilt over the ends of the rigid horizontal members, but not to move radially, thus preventing the riser13 from contracting or engaging an opening edge 15 on deck 17 and becoming damaged.
    [060] In this way, the revealed achievements provide numerous advantages over state of the art riser tensioners. For example, the revealed achievements provide an impulse riser tensioner that can accommodate larger loads in a smaller space compared to conventional lever riser tensioners. Additionally, the revealed achievements are less prone to corrosion problems due to being placed on the tension leg deck deck rather than below. This also reduces the need for additional deck structure to support the riser tensioner. The revealed achievements also eliminate the build-up of high pressure while using fewer cylinders. In addition, the revealed achievements provide an impulse tensioner that accommodates the inclination of the risere and can be used in a TLP. The disclosed achievements also provide a riser tensioner that can be articulated outside the drilling opening on the platform deck so that equipment larger than the nominal diameter of the riser tensioner can operate on the riser in an underwater location.
    [061] It is understood that the present invention can take many forms and embodiments. In this way, several variations can be made in the previous one without departing from the spirit and scope of the invention. Having thus described the present invention by reference to its preferred realizations, it is noted that the realizations disclosed are illustrative rather than limiting in nature and that a wide range of variations, modifications, changes and substitutions are contemplated in the previous disclosure and, in some occurrences, some attributes of the present invention can be employed without corresponding use of the other attributes. Many such variations and modifications may be considered obvious and desirable by a person skilled in the art based on a review of the previous description of the preferred embodiments. Accordingly, it is appropriate for the appended claims to be interpreted widely and in a manner consistent with the scope of the invention.
    权利要求:
    Claims (15)
    [0001]
    1. TENSIONER (11) TO MAINTAIN A TRACTION STRENGTH IN A RISER (13), which has a geometric axis (39) and which extends from an underwater wellhead assembly through an opening (15) in a floating platform deck (17), the tensioner (11) being characterized by comprising: a tensioning ring (21) coupled to the riser (13); a plurality of hydropneumatic cylinders (35), each of which has flexible joints (33) at opposite ends for coupling the cylinders (35) between the deck (17) and the tensioning ring (21); the plurality of hydropneumatic cylinders (35) movable in at least one plane between an operating position and a remote activation tensioning position; and cylinders (35) adapted to automatically engage the tensioning ring (21) after moving from the operating position to the tensioning position.
    [0002]
    TENSIONER (11), according to claim 1, characterized in that: the plurality of cylinders (35) comprise pairs of cylinders (35G, 35G '), each pair of cylinders (35G, 35G') having a first cylinder (35G) and a second cylinder (35G1), the first being the second cylinders (35G, 35G ') have lower ends arranged circumferentially around the opening (15) so that the lower end of the first cylinder (35G ) of each pair of cylinders (35G, 35G ') is close to the lower end of the second cylinder (35G1); the upper end of the first cylinder (35G) is coupled to the tensioning ring (21) deviated from a plane (42) that passes through the lower end of the first cylinder (35G) and the geometric axis (39); and the upper end of the second cylinder (35G ') is coupled to the tensioning ring (21) deviated from a plane (44) that passes through the lower end of the second cylinder (35G') and the geometric axis (39), the offset of the second cylinder (35G ') is equivalent to offset of the first cylinder (35G) in the opposite direction, thus causing the first and second cylinders (35G, 35G') to exert rotational forces in opposite directions.
    [0003]
    TENSIONER (11), according to any one of claims 1 to 2, characterized in that it also comprises a plurality of mechanical screens (31) to limit the articulation of the cylinders (35) in relation to the geometric axis of the riser (39 ), each mechanical bulkhead (31) being adapted to be coupled to the deck (17) outside a corresponding cylinder (35) to limit the outboard inclination of a corresponding cylinder (35).
    [0004]
    TENSIONER (11) according to any one of claims 1 to 3, characterized in that it also comprises a plurality of extensible fluid delivery cylinders (53), each of which is coupled to one of the hydropneumatic cylinders (35) to tilt each hydropneumatic cylinder (35) from the operating position when the riser (13) is being installed to the tensioning position.
    [0005]
    TENSIONER (11), according to any one of claims 1 to 4, characterized in that it further comprises: a guide bearing assembly (23) that is adapted to be mounted on the deck (17) and to roll along the riser ( 13); and a conductive sleeve (61) extending from the tensioning ring (21) parallel to the riser (13) and adapted to interface with the bearings (47) of the guide bearing assembly (23) so that when the riser ( 13) rotate in relation to the deck (17), the conductive sleeve (61) resists the rotation of the tensioner (11) through reaction forces exerted by the guide bearing assembly (23).
    [0006]
    6. TENSIONER (11) according to claim 5, characterized in that the conductive sleeve (61) defines axial grooves to receive the bearings (47) and allow the bearings (47) to approach a surface of the riser (13).
    [0007]
    TENSIONER (11) according to any one of claims 1 to 6, characterized in that it further comprises: a plurality of orientation receptacles (22) mounted on a lower part of the tensioning ring (21), each receptacle of orientation (22) corresponds to a respective hydropneumatic cylinder (35); each of the orientation receptacles (22) defining an inner cavity adapted to receive an upper end of a respective cylinder (35); and a plurality of coupling assemblies mounted on the guide receptacles (22) and the upper ends of the cylinders (35) so that the cylinders (35) automatically engage the tensioning ring (21) when the upper end of each cylinder (35 ) is inserted into the respective inner cavity of a guide receptacle (22).
    [0008]
    TENSIONER (11) according to claim 6, characterized in that the coupling assemblies comprise: an annular channel defined by an outer surface of an upper end (33) of the cylinder (35); a locking ring (36) mounted within the annular channel and tending to a radially outward position; a locking channel (28) defined on an inside diameter surface of the orientation receptacle (22); the locking ring (36) and the locking channel (28) having corresponding correlated profiles adapted to allow upward axial movement relative to each other and to prevent downward axial movement relative to each other when the locking (36) is inserted into the locking channel (28); a retraction ring (52) that circumscribes the upper end of the cylinder (35) axially below the locking ring (36); and the retraction ring (52) adapted to move axially upwards and release the locking ring (36) from the engagement with the locking channel (28).
    [0009]
    TENSIONER (11) according to any one of claims 1 to 8, characterized in that each cylinder (35) within the plurality of cylinders (35) is able to assume a different amount of extension when the riser (13) is tilted in relation to the deck (17).
    [0010]
    10. METHOD FOR TENSIONING A RISER (13) that passes through an opening (15) in a deck (17) of a platform, characterized by comprising the steps of: (a) placing a plurality of hydropneumatic cylinders (35) around the opening (15); (b) flexibly connect a first end of each cylinder (35) to the deck (17); (c) moving the cylinders (35) from an operating position perpendicular to the deck (17) to a tensioning position at an angle to the deck (17); (d) automatically coupling a second end of each cylinder (35) to a tensioning ring (21) coupled to the riser (13); and (e) as the riser (13) tilts in relation to the platform, allow the cylinders (35) to move in more than one plane.
    [0011]
    11. METHOD, according to claim 10, characterized by step (c) comprising the substeps of: flexibly attaching the lower ends of the cylinder (35) to the deck (17); tilting the upper ends of the cylinder (35) out of edge in relation to a geometry axis (39) of the opening (15); lower the riser (13) through the opening (15); then tilt the upper ends of the cylinders (35) on board.
    [0012]
    A method according to any one of claims 10 to 11, characterized in that the upper ends on board comprise steps of coupling delivery cylinders (53) to hydropneumatic cylinders (35) and activating the delivery cylinders (53) to tilt the cylinders hydropneumatic (35).
    [0013]
    13. METHOD, according to claim 10, characterized in that step (d) comprises the steps of: inserting an upper end of each cylinder (35) in a corresponding orientation receptacle (22) mounted on a lower part of the tensioning ring (21); and inserting a fastener (36) attached to the upper end of each cylinder (35) in a corresponding channel (28) of each orientation receptacle and, thus, coupling each cylinder (35) to the tensioning ring (21).
    [0014]
    Method according to any one of claims 10 to 13, characterized in that step (e) comprises allowing at least one of the cylinders (35) to contract more than at least one other of the cylinders (35).
    [0015]
    15. METHOD, according to any one of claims 10 to 14, characterized in that step (e) further comprises a substep of preventing any of the cylinders (35) from tilting off-board more than ninety degrees in relation to a geometric axis (39) of the riser (13)
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    同族专利:
    公开号 | 公开日
    SG183612A1|2012-09-27|
    NO20120103A1|2012-08-13|
    AU2012200634B2|2016-10-20|
    GB2488036B|2017-07-05|
    US20120207550A1|2012-08-16|
    MY155985A|2015-12-31|
    BR102012003065A2|2018-05-02|
    US8496409B2|2013-07-30|
    BR102012003065A8|2018-06-12|
    CN102673747A|2012-09-19|
    AU2012200634A1|2012-08-30|
    GB201202207D0|2012-03-21|
    GB2488036A|2012-08-15|
    NO344735B1|2020-03-30|
    CN102673747B|2016-09-14|
    NO20200073A1|2012-08-13|
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    法律状态:
    2018-05-02| B03A| Publication of an application: publication of a patent application or of a certificate of addition of invention|
    2018-06-12| B03H| Publication of an application: rectification|
    2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-09-10| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-02-27| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application according art. 36 industrial patent law|
    2020-06-02| B09A| Decision: intention to grant|
    2020-10-20| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 10/02/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US201161442073P| true| 2011-02-11|2011-02-11|
    US61/442,073|2011-02-11|
    US13/072,233|US8496409B2|2011-02-11|2011-03-25|Marine riser tensioner|
    US13/072,233|2011-03-25|
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