[go: up one dir, main page]

US20090078425A1 - Flexible hang-off arrangement for a catenary riser - Google Patents

Flexible hang-off arrangement for a catenary riser Download PDF

Info

Publication number
US20090078425A1
US20090078425A1 US11/861,080 US86108007A US2009078425A1 US 20090078425 A1 US20090078425 A1 US 20090078425A1 US 86108007 A US86108007 A US 86108007A US 2009078425 A1 US2009078425 A1 US 2009078425A1
Authority
US
United States
Prior art keywords
riser
spool
spiral
platform
spools
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/861,080
Other languages
English (en)
Inventor
Krzysztof J. Wajnikonis
Steven John Leverette
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Seahorse Equipment Corp
Original Assignee
Seahorse Equipment Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Seahorse Equipment Corp filed Critical Seahorse Equipment Corp
Priority to US11/861,080 priority Critical patent/US20090078425A1/en
Assigned to SEAHORSE EUIPMENT CORP. reassignment SEAHORSE EUIPMENT CORP. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LEVERETTE, STEVEN JOHN, WAJNIKONIS, KRZYSZTOF J.
Assigned to SEAHORSE EQUIPMENT CORP. reassignment SEAHORSE EQUIPMENT CORP. CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE NAME WHICH WAS MISSPELLED. PREVIOUSLY RECORDED ON REEL 019875 FRAME 0979. ASSIGNOR(S) HEREBY CONFIRMS THE ASSIGNMENT OF PATENT RIGHTS. Assignors: LEVERETTE, STEVEN JOHN, WAJNIKONIS, KRZYSZTOF J.
Priority to AU2008211995A priority patent/AU2008211995B2/en
Priority to MYPI20083486A priority patent/MY165417A/en
Priority to EP08016739.8A priority patent/EP2042682B1/en
Priority to BRPI0803418-4A priority patent/BRPI0803418A2/pt
Publication of US20090078425A1 publication Critical patent/US20090078425A1/en
Priority to US12/564,622 priority patent/US8689882B2/en
Priority to US12/850,759 priority patent/US8550171B2/en
Priority to AU2010238542A priority patent/AU2010238542B2/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/01—Risers
    • E21B17/015—Non-vertical risers, e.g. articulated or catenary-type
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/01—Risers
    • E21B17/017—Bend restrictors for limiting stress on risers
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/002—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling
    • E21B19/004—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling supporting a riser from a drilling or production platform

Definitions

  • This invention relates to offshore structures and the risers used to connect such structures to undersea wells, pipelines and the like. More particularly, it relates to catenary risers, including steel catenary risers (SCR's) and catenary risers constructed from other materials like titanium, and the apparatus used to attach a catenary riser to and support a catenary riser from a floating (or fixed) offshore structure.
  • catenary risers including steel catenary risers (SCR's) and catenary risers constructed from other materials like titanium
  • a riser including a catenary riser and including a Steel Catenary Riser (SCR)
  • SCR Steel Catenary Riser
  • a platform floater, vessel, platform, including a Tension Leg Platform—TLP, spar, buoy, etc
  • a platform supported on the seabed floatet platform, compliant tower etc.
  • All types of floating structures are referred to herein as floaters.
  • FIG. 1 depicts an SCR suspended from a truss spar floater.
  • FIG. 1 b illustrates an example of the combined surge and pitch or sway and roll motions of a floater have on the geometry of a catenary riser, which in particular can be an SCR.
  • the floater motions outlined above are the result of static, dynamic, aerodynamic and hydrodynamic interactions between the floater on its mooring, currents, wind and waves. What is of particular interest here are those interactions that result in large translational and angular offsets of the floater from its mean design positions, like those the example of which is shown in FIG. 1 . Those large offsets have typically static and dynamic components. Static offsets are caused by mean currents and winds, while large time variable offsets are caused by dynamic interactions of the floater on its mooring with low frequency wave drift forces and with wind gusts. The low frequency floater motions occur typically with periods of the order of hundreds of seconds.
  • the largest amplitudes of those motions occur where resonance takes place between the fluid dynamic forcing, like wave drift forces or/and wind gust forces, and the vessel mooring.
  • the vessel moored can typically be approximated in each of the 6 degrees of freedom as a damped mass-spring system, whereas the motions for individual degrees of freedom can be fairly independent, or static and/or dynamic couplings can exist between degrees of freedom.
  • static and dynamic couplings are represented by the existence of non-zero off-diagonal terms in the stiffness and mass matrices of the dynamic system, respectively.
  • floaters are also subject to so called first order dynamic motions caused by the floater responses to waves. These motions occur at the wave frequencies, i.e. with periods from a few to a few dozens seconds. For large offshore floaters the motion amplitudes of the said first order motions tend to be smaller than the static and dynamic offsets caused by the mean forces and the low frequency forces.
  • the floaters are approximated herein as rigid bodies, while the geometries of slender structures such as the risers adjust to the translational and angular offsets of the floater.
  • Riser changes the angles both statically and dynamically due to movements of the hang-off point and due to direct forcing and response of riser to wave and current forces.
  • the variation in the relative angle between any orientation on the floater and that of the axis of the riser at the hang-off is of interest herein.
  • the said relative angular floater/riser offsets can result in high bending loads (and stresses), while the translational and combined translational and angular offsets can result in high variations in the effective tensions at the riser hang-offs.
  • the riser stress variations due to the changes in the said angular offsets and effective hang-off tensions can sometimes be mitigated by adding stress and/or tapered transition joints at the SCR hang-off.
  • These can utilize steel materials, or for larger offsets and stresses titanium alloys can be used. Titanium alloys tend to have higher allowable strains than most typical steel materials used offshore and their Young's Moduli tend to be lower than those of steels. Both the above characteristics of titanium alloys are beneficial for tolerating high angular and translational floater offsets in comparison with the corresponding characteristics of steels.
  • FRP Fiber Reinforced Plastics
  • a flexjoint comprises flexible (rubbery) elastomeric components that ‘absorb’ the angular deflections.
  • By the said ‘absorbing’ it is meant that most of the bending required occurs by deforming the flexible elastomeric components of the flexjoint thus reducing the amount of bending and the said bending stresses in the metal components of the SCR system.
  • elastomeric components of a flexjoint are subjected to pressure and surface action of internal components. Both said pressure action and physical and/or chemical surface action may limit the use of flexjoints in particular due to high pressures, due to thermal, erosive, corrosive, etc. action(s) of internal fluids.
  • Flexjoints require the elastomeric material to be exposed to riser contents and pressure.
  • Piping swivels are subject to leaks, have limited pressure ratings and also may require complicated guiding systems to reduce spool bending on the piping swivels.
  • Catenary riser pipes routinely see limited torque loading that is incidental to any combination of 3-D bending, shear and tension load. Torsional stresses in the catenary risers due to the said torques are usually small in comparison with other loads.
  • torsion rods have been used as wheel springs in the suspension of many successful automobiles throughout the twentieth century until now. These do not need to have large dimensions in order to accommodate significant vertical movement of a wheel required that is translated to the torsion of the ‘wheel end’ of the rod.
  • the suspension of the said top of the riser, including a catenary riser, including a Steel Catenary Riser is by means of a pivoting arrangement.
  • the riser can be suspended from a riser porch, a riser bank, a turret of a Floating Production Storage and Offloading (FPSO) vessel, Floating Production Storage (FPS) vessel, buoy, I-tube, J-tube, hawse pipe, fairlead, chute, etc.
  • FPSO Floating Production Storage and Offloading
  • FPS Floating Production Storage
  • the said pivoting arrangement may utilize a ball joint, a universal joint, a flexjoint, any plurality of or any combination of shackles, chain links, etc, including a single shackle and a single chain link, a bellmouth, a chute, an entry or exit to/from an I-tube or/and a J-tube or/and a hawse pipe that might or might not incorporate a bellmouth, a fairlead, a pulley, any arbitrary line re-directing device, etc.
  • a flexjoint its design could be simpler than that shown by Langner.
  • the elastomeric components of the flexjoint would typically be arranged external to the pressure containing part of the piping, thus considerably simplifying the design.
  • the said pivoting arrangement resists the tension in the SCR and it also resists any transverse forces on the top of the SCR that is suspended from the pivot.
  • the pivoting arrangement allows the top part of the SCR to undergo angular deflections relative to the said platform, the said floater, the said jacket, the said compliant tower, etc.
  • SCRs are often referred to herein for brevity, because the SCRs are the most widely used rigid catenary risers.
  • any type of rigid catenary riser is meant. This is because, any other metallic, non-metallic, composite, etc. riser that has higher bending stiffness than a flexible riser, can be substituted for an SCR in any implementation of this invention.
  • the said angular deflections include deflections in plane and out of plane of the SCR. Torsional angular deflections of the SCR at the pivot may or may not be partly or totally resisted by the pivot (in other words torsional deflections of the SCR at its hang-off are immaterial to the designs of interest herein).
  • this design comprises pipe components that are typically all fixed to each other by means of welding, using bolted flanges, connectors, swaging, etc., which can tolerate higher pressures and are often more cost efficient than the said prior art designs.
  • the spools are arranged in geometrical figures, whereas the axes of the spools (straight, bent or curved) are offset from and have tangents that form large angles with the tangent to the top joint of the SCR at the hang-off.
  • large angles in particular right angles and angles close to right angles are meant.
  • the said tangent lines of the spools that are close to being orthogonal to the SCR axis at the hang-off would in general not lie in the same planes, but in some cases may lie in the same planes.
  • the said spools can form continuous segmented lines, can be arranged in loops and/or coils and/or spirals and/or helices, so that the bending of the top part of the SCR is transformed mostly to torsion in the spools. However, some residual bending and other than torsional shear load can still be present in the spool system.
  • Example implementations of this invention featuring example spiral spool arrangements are depicted in FIGS. 2 through 10 .
  • the said novel designs utilize relatively low torsional stiffness of a pipe that allows high angles of twist without generating high torsional stresses.
  • the arbitrary level of the in-plane and out-of-plane rotational flexibilities of the spool system required are achieved by adjusting the lengths of the spool segments and/or by adjusting the diameters or side lengths of the said loops or/and spirals.
  • the said in-plane and out-of-plane rotational flexibilities of the spool system required are also adjusted by selecting required number of spool segments, loops or turns in the spirals as well as by using spool geometries that are featured by spool axes being close to perpendicular to the riser axis at the hang-off. In agreement with the generalized Hooke's Law, the longer the said dimensions and the higher the said numbers of coil turns, loop turns and/or spiral turns the more flexible is the system.
  • any straight or segmented lines may be merged by bends that would have specified their minimum radii of curvature.
  • Typical radii of curvature of bends used in pipeline engineering include three times (3D bends) and five times (5D bends) the nominal diameter of the pipe. However, in some designs different bent radii are used.
  • the 5D bends are standard bends for pigable risers and pipelines, accordingly bends of 5D or greater radii would be most likely utilized in riser spool systems.
  • riser systems need to be pigable and any standard or not standard bent radius, could be used, including OD [zero-D], for sharp joints between straight or curved pipe segments.
  • Finite Element Analysis demonstrates that, even with very high pressures in the piping and large maximum deflection angles, the said novel system can be designed with a limited number of turns in the coil or even an incomplete 360° loop, in the coil, spiral, helix, etc. This also includes different shapes of the spool system that could have similar effective lengths subjected to increased torsion. In such designs the risers could be provided with an optional tapered or stepped stress joints on the riser and/or spool sides of the pivot. These would see only relatively limited bending and acceptable bending stresses.
  • Increasing the diameter(s) and/or the side length(s) of the segmented spool line(s) of the loop(s) and/or spiral(s) and/or increasing the number of segments and/or loops and/or turns in a spiral makes the spool system more flexible.
  • a greater flexibility of the spool system decreases both bending stresses in the top segment of the SCR and it also decreases torsional stresses in the spools.
  • an increased flexibility in the spool system allows a greater variation in the maximum SCR hang-off deflection angle.
  • the said greater flexibility of the spool system can be utilized both to reduce quasi static and dynamic bending stresses in the catenary riser.
  • greater rotational flexibility helps to reduce that part of bending stresses (and to increase the corresponding fatigue life), that would otherwise be transferred to the riser from the moving platform or vessel.
  • FIGS. 2 through 7 Examples of designs featuring the effective pivot locations close to the optimum locations are shown in FIGS. 2 through 7 .
  • piping swivel(s) in the spools can also be included in the novel designs.
  • FIG. 1 a presents a typical catenary riser suspended from a truss spar floater.
  • An example of effects of the spar offsets on the riser geometry is illustrated in FIG. 1 b.
  • FIG. 2 depicts pivot-spool arrangements featuring ball joints located close to the centers of progressive spirals.
  • FIG. 2 a features a circular spiral spool and
  • FIG. 2 b features a quadrangular spiral spool.
  • FIG. 3 depicts pivot-spool arrangements featuring flexjoints located close to the centers of progressive spirals.
  • FIG. 3 a features a circular spiral spool and
  • FIG. 3 b features a quadrangular spiral spool.
  • FIG. 4 depicts pivot-spool arrangements utilizing hawse pipes as pivots that are located close to the centers of progressive spirals.
  • FIG. 4 a features a circular spiral spool and
  • FIG. 4 b features a quadrangular spiral spool.
  • FIG. 5 depicts pivot-spool arrangements utilizing I-tube entries or J-tube entries as pivots located close to the centers of progressive spirals.
  • FIG. 5 a features a circular spiral spool and
  • FIG. 5 b features a quadrangular spiral spool.
  • FIG. 6 depicts pivot-spool arrangements utilizing bellmouths as pivots located close to the centers of planar (flat) spirals.
  • FIG. 6 a features a circular spiral spool and
  • FIG. 6 b features a quadrangular spiral spool.
  • FIG. 7 depicts pivot-spool arrangements utilizing universal joints as pivots located close to the centers of spirals.
  • FIG. 7 a features a triangular spiral spool and
  • FIG. 7 b features a pyramidal spiral spool with the pyramid shape narrowing upwards.
  • FIG. 7 c features a pyramidal spiral spool with the pyramid shape narrowing downwards.
  • FIG. 8 depicts a pivot-spool arrangement utilizing a flexjoint as a pivot located above the center of a planar (flat) spiral.
  • the circular spiral spool is supported with a 4 leg beam frame.
  • FIG. 9 depicts a pivot-spool arrangement featuring progressive spirals offset to locations above the pivot.
  • FIG. 9 a features a ball joint and a circular spiral spool and
  • FIG. 9 b features a flexjoint and a quadrangular spiral spool.
  • FIG. 10 depicts pivot-spool arrangements featuring ball joints as pivots and progressive spirals offset approximately horizontally with regard to the locations of the pivots, suspended from turrets of an FPSO or an FSO.
  • FIG. 10 a features a circular spiral spool and
  • FIG. 10 b features a triangular spiral spool.
  • FIG. 11 depicts example details of an SCR hang-off clamp assembly design similar to those utilized in the designs depicted in FIGS. 2 through 10 and other example details.
  • FIG. 11 a depicts an example SCR stress joint-gooseneck arrangement.
  • FIG. 11 a also depicts an exemplary hang-off clamp design utilizing a ball joint assembly as a pivoting arrangement.
  • FIG. 11 b depicts an example of a pivot design utilizing a ball joint.
  • FIG. 11 c depicts an example of a pivot design utilizing a flexjoint.
  • FIG. 11 d depicts an example of a clamp hang-off design utilizing an universal joint.
  • FIG. 11 e depicts an example of a clamp hang-off design utilizing a shackle and pad-eye assembly.
  • FIG. 11 f depicts an example of a assembly incorporating a hang-off clamp, shackles, padeye and chain.
  • FIG. 11 g depicts an example of a buoyancy clamp used on a pipe spool.
  • FIG. 11 h depicts an example of a helicoidal strake clamp used on a pipe spool to suppress Vortex Induced Vibrations (VIVs).
  • VIVs Vortex Induced Vibrations
  • FIG. 11 i depicts examples of bumper-support clamps which may be used on a pipe spool to suppress VIVs and to support the submerged weight of parts of the spools.
  • All the pipe elbow bends depicted for sake of examples in FIGS. 2 through 11 are planar 5D bends, including all goosenecks as well as all spiral entry and spiral exit bends. It is, however, noted that those are examples only and that any bend radii can be used in these designs.
  • the radii of curvatures of the curvilinear 3-D spirals depicted herein are all greater than 5D, either slightly greater or considerably greater. It might be also beneficial to use three dimensional bends in some designs.
  • 3-D bends might for example make the spool system more compact, which might result in lowering stresses, make it easier to connect to other spool components by extending the lengths of straight pup-joints between those components, allow easier fitting of flanges or connectors into the system, etc.
  • FIG. 1 a An example of a catenary riser 10 l suspended from a truss spar floater platform 103 is shown in FIG. 1 a .
  • IP in-plane
  • the angular offsets ⁇ 1 and ⁇ 2 are measured from the tangent to the riser axis at the hang-off of the design catenary of the said riser pertaining to the mean, design location of the platform.
  • the in-plane design hang-off offset angle is angle ⁇ o, see FIG. 1 b.
  • FIG. 1 b is a detail view from FIG. 1 a.
  • Floater surging and pitching can attain large amplitudes, like those shown for example in FIG. 1 .
  • surge and pitch motions (named relative to the ‘in-plane’ design plane of the catenary) occur with different periods and accordingly, from time to time the maximum angular offsets due to the surge and the maximum angular offsets due to pitch coincide, as it is shown on the example depicted in FIGS. 1 a and 1 b.
  • the range of offset angles ⁇ 1 and ⁇ 2 typically increases additionally due to additional deflections of the risers that are caused by quasistatic drag forces on the risers and dynamic forces on risers. These quasistatic and dynamic forces result from current and wave (relative current flow) interactions with the system components. The said drag forces can be increased if VIVs are present.
  • the hang-off location on the spar moves both horizontally and vertically in-plane (and also out-of-plane) of the catenary.
  • the riser touch-down point (TDP) moves accordingly from the mean design location 107 towards locations 109 and 111 , which are additionally modified by currents.
  • the submerged weight of the suspended part of the riser 101 that is supported at the hang-off varies considerably, it is the lowest at the TDP at the near location 109 and it is the greatest with the TDP at location 111 .
  • the quasi-static vertical load of the catenary riser at the hang-off 105 is approximately equal to the said submerged weight of the riser.
  • the quasi-static horizontal tension in the riser varies little along the catenary. This horizontal tension is the greatest when the TDP is located at 111 , and it is the smallest for the TPD at 109 .
  • the total effective tension at the hang-off is equal to the vector sum of the said vertical and the said horizontal load components at the hang-off.
  • the said total effective tension at the hang-off provides a stress stiffening effect to the SCR structure at the hang-off location 105 , which affects the angular deflections of the riser below the hang-off, together with the bending stiffness of the riser and the riser stress joint at the hang-off, if present.
  • the rotational stiffness at the hang-off is the bending stiffness of the riser (or the SCR stress joint) at the hang-off.
  • the pipe cannot rotate at the hang-off and the relative in-plane angle is constant at ⁇ o, independent of the in-plane or out-of-plane offsets of the platform.
  • the deflection angle ⁇ depends on the bending moment and on the effective in-plane rotational stiffness at the pivot.
  • the said effective in-plane stiffness at the pivot is the sum of the in-plane rotational stiffness of the pivot arrangement (non-zero and typically non-linear whenever a flexjoint is used) and the in-plane rotational stiffness of the spool system, reduced to the location of the pivot 105 .
  • the said effective in-plane rotational stiffness of the spool system combines the torsional stiffness of the spool system together with the bending and shear stiffnesses of the spool system, all reduced to the pivot location 105 .
  • the said rotational in-plane spring stiffness is non-linear, but it can be easily determined for any load condition using FEA. Approximate values can be calculated ‘by hand’ using basic structural engineering approach. Performing the FEA and/or the said approximate hand calculations is known to those skilled in the field.
  • any spools of types represented in FIGS. 2 through 10 are regarded herein as coils, spirals or helices.
  • any spools of types represented in FIGS. 2 through 10 or any of their parts are regarded herein as coils, spirals or helices.
  • straight or curvilinear segments resembling letters ‘L’, ‘C’, ‘Z’, ‘O’, etc that include line segments that are approximately orthogonal to the axis of the riser pipe near the hang-off are also regarded herein as spirals and claimed as novel according to this invention.
  • pipe spool shapes resembling the said letter ‘L’ are regarded herein as partial, approximately half-loop spiral shapes
  • pipe spool shapes resembling letter ‘C’ are regarded herein as partial, approximately three-quarter spiral shapes, etc. whether or not the sides of the said partial spiral shapes are curvilinear or straight, whether or not the corners of the said spiral shapes are sharp, or smoothened utilizing constant or variable radius bends.
  • the spool systems 205 and 207 are relatively flexible in rotation reduced to the pivot location when compared to the bending stiffness of the SCR/stress joint/transition joint at the riser hang-off 105 .
  • the said combined rotational flexibility of the spool system reduced to the pivot location can be increased by means of:
  • FIGS. 2 through 10 depict examples of structurally effective spool designs according to this invention.
  • the design configurations depicted in the figures are examples only that illustrate the principle of this invention. Many other configurations according to this principle are feasible and there are understood to be included in the subject matter of this invention. In addition to that, it is also understood that most design details and variations depicted in FIGS. 1 through 11 , those features and design alternatives described herein as well as all other design variations and solutions, whether general or specific to any applications are also covered by the subject matter of this invention.
  • the said segmented lines can feature any combinations of curvilinear and/or straight segments and the statements about spool effectiveness listed a few paragraphs above apply to all spiral spool arrangements, in the broadest possible sense highlighted herein.
  • these can be either regular or arbitrary irregular polygons, including regular and irregular polygonal spiral shapes.
  • piping adjacent to the spiral spools also participates in making the combined spool system more flexible, while introducing some level of axial asymmetry in the structural flexibility of the combined system.
  • the said level of axial asymmetry can be controlled by orienting the spiral entry and the spiral exit spool joints at different azimuth angles (i.e. angles measured in the planes orthogonal to the riser axis at the pivot point) and at different meridional angles (i.e. angles between the riser axis at the pivot and the axis of the spool).
  • the said level of axial symmetry can be also controlled by using higher or lower numbers of turns or loops in the spirals and by using spirals featuring the said azimuth angle variations along the entire spiral length that are closer or farther from integer multiples of 360°.
  • the combined detailed effects of the said spool geometry on the 3-D flexibilities of the system can be assessed using FEA or by performing approximate structural calculations that are well-known by those skilled in the field.
  • non-polygonal and non-broken line shapes of spirals are also covered by this invention, even though they might have not been explicitly mentioned or shown on any of the figures. These include for example approximately spherical, approximately parabolic, approximately elliptic, and conical spirals, etc. and other more complex two and three dimensional shapes.
  • conical spirals can be regarded as a not shown generalizations of circular spirals in a similar way pyramidal spirals shown in FIGS. 7 b and 7 c are generalizations of polygonal spirals depicted on many figures.
  • FIG. 2 depicts pivot spool arrangements featuring ball joint assemblies 201 and 203 located close to the centers of progressive spirals.
  • FIG. 2 a features a circular spiral spool 205 and
  • FIG. 2 b features a quadrangular spiral spool 207 .
  • riser porches 213 and 21 5 that are attached to sides of pontoons 217 and 219 .
  • Porches 213 and 215 can be attached to any kind of platform known, however, those featured in FIGS. 2 a and 2 b might be used for example on semi submersible vessels, or on TLPs, or on FPSOs. It is clear to those skilled in the field that instead of porches 213 and 215 , continuous or non-continuous riser banks that support more than one riser each could be used, other support structures like for example turret structures of an FPSO, etc., can be used instead of porches shown in FIGS. 2 a and 2 b without any loss of generality of this invention.
  • FIGS. 2 a and 2 b depict optional bolt connections between hang-off clamp assemblies 221 , 223 and ball joints 201 , 203 , respectively.
  • This type of connection depicted is an optional solution that is structurally feasible, however, in the particular designs depicted in FIGS. 2 a and 2 b , as well as on many other figures herein use of full penetration butt, etc. welds between parts like hang-off clamp assemblies 221 , 223 and ball joints 201 , 203 are preferred for structural reasons.
  • FIG. 10 b that demonstrates a use of an implementation of this invention utilizing receptacle basket 1019 .
  • the preferred implementations of this invention involve the use of the said receptacle basket 1019 with example designs like those shown for example in FIGS. 2 a through 3 b , FIGS. 7 a through 8 and FIG. 10 .
  • the said receptacle baskets can be preferably incorporated structurally inside riser porches, riser banks, etc. which is a commonly used design solution known to those skilled in the field.
  • the preferred use of the said receptacles would involve fitting the receptacle in a bellmouth, in an exit of a hawse pipe, in an exit of an I-tube, in an exit of J-tube, etc., which again is a common practice known to those skilled in the field. In these cases it is a common practice to permanently clamp the said receptacle baskets to the said exits of the I-tube, J-tube, hawse pipe, bellmouth, etc. utilizing bolts or other means like latching, etc.
  • a meridionally-split external parts of the ball joint similar to those shown in FIGS. 2 , 10 b and 11 a and 11 b could have their external shape modified to fit the receptacle basket; the operations of such ball joints would thus be reversed in that the joint would be effectively flipped 180° and the said joint ball would be welded, or otherwise connected structurally, to the said riser hang-off clamps utilizing a tapered stress joint, etc.;
  • the pivots should be located near to the centers of the spirals and in many cases there might not be enough room inside a spiral for the pivoting arrangement assembly, for the receptacle basket and for the structural support of the receptacle basket.
  • the receptacles may be located above the pivoting arrangements as it is shown for example in FIG. 10 b.
  • connectors can be used as principal subsea joints made during the offshore installation of the system between the pivoting arrangement 201 , 203 and riser hang-off clamp 221 , 223 , see for example FIGS. 7 a through 7 c and FIG. 10 a .
  • the use of the said optional subsea connectors includes in particular utilization of collet connectors.
  • the use of subsea connectors in the said applications is routine for those skilled in the field and with such a use all the parts between the connector and the platform would preferably be welded, etc. together before the offshore installation of the platform used, including vessels and semi submersibles.
  • any of the said off-the-shelf connectors are designed to contain pressure as well as to carry high structural loads.
  • a connector utilized to contain pressure see for example FIG. 2 a and 2 b , FIG. 3 a and 3 b , FIG. 7 , etc.
  • the design of such a connector could be customized for the application according to this invention, which might in particular cases involve design simplifications.
  • Many design variations are feasible for the application of connectors according to this invention, which will be readily deduced by those skilled in the field.
  • Bolted connections like those shown for example in FIG. 2 a through FIG. 3 b can also be utilized as optional design solutions.
  • top segments of risers 209 and 211 would be usually (but optionally) strengthened with optional stress joints 225 and/or 227 and/or with optional transition joints 229 and/or 231 .
  • transition joints like 229 and/or 231 shown incorporate several steps (stepped transition joints, example 209 ) with gradually increasing wall stiffnesses, between those of the SCR pipes used 233 and 235 and those of optional stress joints 225 and/or 227 .
  • transition joints can feature continuously increasing wall thickness, like those called tapered transition joints, see 211 , whereas the wall pipe wall thickness used features continuously increasing wall thicknesses between those of the SCR pipes 233 and 235 used and those of the said optional stress joints 225 and/or 227 .
  • Design details of the said optional stress joint and of the said optional transition joints can be selected in ways that are known to those skilled in the field.
  • the said selections of the design parameters of the optional stress and transition joints need, however, to be selected in ways that are compatible with the design of the novel spirals 237 and 239 according to this invention.
  • the stiffer (smaller and/or less effective) the spirals 237 and 239 the more need there is to use the optional stress joints 225 and/or 227 and/or the more reasons there is to use transition joints 229 and/or 231 .
  • the stiffer (smaller and/or less effective) are the spirals 237 and 239 , the greater wall thicknesses of the said stress joints and the greater the lengths of the said SCR transition joints need to be, and vice versa.
  • Fluids (including homogenous or/and non-homogenous gases and liquids that may carry other phases with their flow) transported inside the SCRs are transferred between the risers and spiral spools 237 and 239 using goosenecks 241 and 243 .
  • the goosenecks can feature the same pipe wall thickness as that used to construct spiral spools 237 and 239 , or it can be greater in order to decrease bending stresses in the goosenecks. The specific design choices will depend on detailed stress and fatigue analyses of the entire riser-spool systems that are performed in usual ways well-known to those skilled in the field.
  • Spiral entry spool segments 245 and 247 connect the goosenecks with the spirals.
  • Spiral entry spool segments 245 and 247 typically incorporate spiral entry bends 249 and 251 and straight or curvilinear pup joints 253 and 255 . They can also incorporate optionally flanges or connectors 257 and 259 .
  • Spiral exit spool segments 265 and 267 connect the spirals with the platform piping using optional flanges or optional connectors 281 and 283 .
  • Spiral exit spool segments 261 and 263 typically incorporate spiral exit bends 265 and 267 , straight or curvilinear pup joints 269 and 271 and they can also incorporate additional, optional bends and segments like for example 273 and 275 . They can also incorporate optionally flanges or connectors 277 and 279 .
  • Spiral exit spool systems are connected to the platform piping 285 and 287 .
  • some optional bending flexibility may be required in the design of the spiral exit spool systems depending on the requirements of any particular structural system. This optional bending flexibility has been achieved in the designs shown in FIG.
  • FIGS. 2 through 11 many aspects and details of design implementations depicted in FIGS. 2 through 11 are shown considerably simplified for the sake of illustration.
  • most connections shown as bolted could be optionally bolted, bolted and welded, bolted and welded and additionally reinforced by means of component shape interaction, in particular for those connections that transfer axial forces in the riser hang-off system.
  • the preference would be for bolted connections not to carry axial loads in the system, unless the highest loads are transferred by a combination of shape and full penetration welded connections.
  • the design connections featured herein would be made up for the life of the equipment in question, which means that most connections would typically be designed for a single assembly before or during the installation. Disassembly of any system components at the end of their design life or in cases of unexpected failures could be carried out using other means, including flame or mechanical cutting, cutting using explosive charges, etc. Those components that might have failed structurally, etc. or might require preventive repairs, etc. might be replaced with new components of the same or modified design or repaired, whatever is preferred.
  • Shackles, bolts, connectors etc. could be diver-less [for example utilizing Remote Operated Vehicle (ROV) and/or other actuations from the surface] or/and made up with a help of divers, as required.
  • Typical subsea equipment like for example hydraulically and/or mechanically and/or electromagnetically assisted bolt tensioning systems, etc. could be used, if preferred so. It is understood that the only some example design implementations of connections are shown, and/or highlighted herein, and many other implementations that may differ from those featured are also covered by the substance matter of this invention.
  • VIV suppression devices like strakes, etc. and/or wave and current shielding devices and/or buoyancy devices, etc. are also omitted from most drawings for simplicity, it is understood that they will be used by the designer whenever and wherever so preferred, with any of the design implementations of to this invention.
  • the wall stiffnesses of spiral spools 237 and 239 , spiral entry spools 245 and 247 as well as those of the said spiral exit spool systems are selected using usual design approach and preferably confirmed by utilizing FEA.
  • non-linear FEAs are required that adequately account for the elbow flexibilities of all the curved elements, including any 2-D elbows (bends) and 3-D curvatures of spirals like 237 , in addition to accounting for stress-stiffening in the riser.
  • one-dimensional pipe and elbow elements in the FEAs.
  • typically in-plane and out-of-plane elbow flexibilities used would require calibrations using shell and/or solid elements, as required by the details of the specific system modeled. These include any possible effects of bent torsion on the said flexibilities. Additional calibration—validation of the modeling techniques needs to account for any 3-D curvatures of the piping used, like that of spiral spool 237 . For spool 237 accounting only for in plane and out of plane elbow flexibility might be insufficient.
  • Passive and active corrosion protection including the use off corrosion resistant alloys and other materials, in particular nearly homogenous materials like for example, ferritic and/or austenitic alloys, including Duplex alloys, including Super-Duplex alloys, including Inconel alloys, etc.
  • Lubrication requirements for interacting components like those of the ball joints 201 and 203 —these might require a use of for example bronze, teflon, nylon, etc. materials on the ball joint or universal joint contact surfaces,
  • buoyancy of the pipe per unit length required in order to limit spool system deformations (if necessary) due to the submerged weight; this is in particular important when very heavy wall pipe is used (high internal pressures),
  • pipe material is important. Depending on the maximum structural and fatigue loads and sizing of the spiral spools high yield strength offshore pipe materials or higher strength steels, like for example AISI 4130 can be used. Generally, the use of higher strength materials allows the engineer to achieve more compact designs. Where higher loads occur, higher strength alloys, like titanium alloys can be used. Alternatively, more flexible materials including other metallic materials and non-metallic materials, including FRPs can be used.
  • the materials used can feature very wide ranges of mechanical properties. The most important properties are the bulk shear modulus (and the elastic modulus) together with the bulk yield, ultimate and fatigue strength of homogenic, approximately homogenic (steels, alloys, etc. are regarded as homogenic or approximately homogenic for the purpose of this specification) or composite material used.
  • the following combinations of beneficial properties can be used:
  • High strength materials examples include most steels, whereas the shear and elastic moduli are typically high in addition to high strength properties
  • Low shear moduli and high strength materials examples include titanium alloys, some FRPs, like some FRPs utilizing for example carbon fibers, nanotubes, KEVLAR® aramid fibers, etc.).
  • the latter group of the said materials featuring low shear moduli combined with high strength properties provides the most beneficial structurally set of mechanical properties for construction of the said spiral spools.
  • beneficial low effective (bulk) shear moduli can be achieved by suitable spatial arrangements of reinforcing fibers in the material.
  • the shear moduli of the fiber material itself may or may not be high.
  • Using suitably engineered FRPs or other pipe cross-section of complex design can allow achieving low bulk torsional stiffness, combined with high hoop stiffness and high axial stiffness in tension, which the combination is particularly beneficial.
  • spiral spool pipe designs may include using multilayer bonded or/and unbonded pipes, whereas different layers may have differing construction and differing purpose including, strength, torsional flexibility, pressure containment, corrosion protection, etc.
  • FIG. 3 depicts a pivot-spool arrangement featuring flexjoints 301 and 303 located close to the centers of progressive spirals.
  • FIG. 3 a features a circular spiral spool 305 and
  • FIG. 3 b features a quadrangular spiral spool 307 .
  • Flexjoints 301 and 303 used as pivots in designs according to this invention do not contain internal fluid pressure like it is shown for example in U.S. Pat. No. 5,269,629. Accordingly, unlike the designs shown for example by Langner, flexjoints can be successfully utilized in the designs according to this invention with no internal pressure limitations. It is noted that wide variety of flexjoint designs can be used successfully in designs according to this invention and that they can differ in many details from those illustrated for example only in FIGS. 3 a and 3 b.
  • the said flexjoints used in designs according to this invention can be more compact, can be designed to be more flexible in bending than conventional SCR flexjoints are and they can allow greater maximum bending angles.
  • FIGS. 3 a and 3 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 3 a and 3 b and those of wide ranges of similar designs will be readily deduced by those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 4 depicts pivot-spool arrangements utilizing hawse pipe entries 401 and 403 as pivots that are located close to the centers of progressive spirals 405 and 407 .
  • FIG. 4 a features a circular spiral spool 405 and
  • FIG. 4 b features a quadrangular spiral spool 407 .
  • the said spirals depicted in FIGS. 4 a and 4 b feature examples of placing the spiral assembly in locations that are sheltered from hydrodynamic loads, like for example those due to the actions of waves, currents and/or relative motions of the supporting structure through the water.
  • Any of the coiled pipes arrangements according to this invention and/or adjacent components featured herein can be shielded from hydrodynamic loads due to VIV, drag and/or inertia forces, etc. by placing them in a convenient sheltered, shielded or partly shielded location relative the supporting structure or/and by providing specially designed shields.
  • the detailed arrangements of the said shields would depend on the degree of sheltering or shielding required, on the position of the riser hang-off and the type of the supporting structure.
  • the sheltering of shielding from hydrodynamic action can be applied to any extent preferred together with any implementation of this invention.
  • FIGS. 4 a and 4 b depict keel ends of a floater 409 and 411 .
  • the said coils 405 and 407 are sheltered in floater moonpools or specially arranged shafts 413 and 415 .
  • Optional shielding surfaces 417 and 419 are depicted in FIGS. 4 a and 4 b.
  • Shielding structures 417 and 419 can extend in any direction, if required and can provide sheltering or shielding from any side.
  • shielding structures can surround completely any coiled assembly according to this invention.
  • the said shielding structures can be arranged totally inside the outlines of any supporting structure, totally outside the said outlines or/and partly inside and partly outside the said outlines.
  • Part of the shielding structure 419 shown in FIG. 4 b is optionally hinged for ease of installation.
  • Supporting structures like 409 and 411 featured in FIGS. 4 a and 4 b could for example represent keel fragments of keel regions of a spar, a TLP, a semi submersible or any other floater.
  • Said coiled riser hang-off assembly can be located near to the sides of said moonpools or shafts, or they can be located away from those sides (internally or externally with regard to the outline(s) of the said structures), if necessary, as governed by of any design requirements, functional requirements, available space requirements or/and any kind or requirements or preferences whatsoever.
  • FIGS. 4 a and 4 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 4 a and 4 b and those of wide ranges of similar designs will be routine for those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 5 depicts a pivot-spool arrangement utilizing J-tube entries or I-tube entries as pivots located close to the centers of progressive spirals.
  • the said J-tube is annotated as 501 and the said I-tube is annotated 503 .
  • FIG. 5 a features a circular spiral spool 505 and
  • FIG. 5 b features a quadrangular spiral spool 507 .
  • the J-tubes or I-tubes can be utilized for example on a spar platform or on any other type of a platform, vessel or buoy. It is noted that, similar to FIGS. 4 a and 4 b , the examplary implementation of this invention depicted in FIG. 5 b features an optional structure shielding spool 507 from waves and currents.
  • hang-off clamps 509 and 511 feature components that are welded together utilizing full penetration welds.
  • both the half-shells of 509 and 511 as well as the hang-off pad-eye plate attachments featured in the said examples are welded, rather than bolted together.
  • Bolting and welding, as well as bolting only would also be acceptable in these and any similar implementations of this invention.
  • FIGS. 5 a and 5 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 5 a and 5 b and those of wide ranges of similar designs will be routine for those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 6 depicts a pivot-spool arrangement utilizing bellmouths 601 and 603 as a pivots located close to the centers of planar (flat) spirals.
  • FIG. 6 a features a circular spiral spool 605 and
  • FIG. 6 b features a quadrangular spiral spool 607 .
  • planar spiral spools tend to be more structurally efficient than designs utilizing progressive spiral geometries. Accordingly, in addition to spirals featuring more than 360° loops, like those shown in FIGS. 6 a and 6 b , loops featuring smaller loop angles, in particular angles smaller than 360° can be used in designs according to this invention, depending on the range of limiting design ranges of in-plane and out-of-plane angles ⁇ (including ⁇ 1 and ⁇ 2), spool materials used (including FRP and other complex designs) and according to the spool geometry, lateral dimensions included.
  • the said spool shapes featuring loop angles smaller than 360° include in particular ‘C’-shaped, ‘L’-shaped spools, etc. These do not need to be arranged exactly in the planes orthogonal to the SCR axes at or close to the hang-offs like those represented for example by the bellmouths 601 and 603 .
  • FIGS. 6 a and 6 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 6 a and 6 b and those of wide ranges of similar designs will be routine for those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • pivot arrangements that utilize chain, connection links and shackles like those featured for example in FIGS. 4 through 6 and FIGS. 11 e and 11 f need to be designed very carefully and high design factors or component load resistance (including bending, impact abrasion, corrosion, fatigue, etc. resistance) need to be applied in the design of those components that are continuously and/or repeatedly subjected to high structural, fatigue, etc. loads.
  • component load resistance including bending, impact abrasion, corrosion, fatigue, etc. resistance
  • in-plane bending is a common type of bending of chain link or connection link material, but a combination of in-plane and out-of plane bending also combined with associated shear, including torsional shear is somewhat unusual in engineering and it needs to be accounted for in the design of such systems.
  • design implementations of this invention like those featured for example in FIGS. 4 through 6 and in FIGS. 11 e and 11 f do present some simplicity and cost effectiveness advantages, both on the construction engineering and on the installation engineering sides. It is noted, that in addition to the said careful design consideration of the said high loads it is recommended to utilize said simple and cost effective design solutions for those SCR systems that tend to be less highly loaded (smaller diameter SCRs, SCR systems utilizing higher buoyancies and/or high degrees of thermal insulation, etc.) Detailed design and installation implications and considerations related to those and similar designs to these highlighted in this paragraph will be routine for those skilled in the field.
  • any kinds of pivots including ball joints, flexjoints, universal joints, etc. can be utilized instead of highly loaded links like those depicted on the said figures.
  • the ‘fixed’ parts of the said ball joints, flexjoints, universal joints, etc. can be fitted, latched, clamped, etc. at the exits of the hawse pipes, I-tubes, J-tubes, bellmouths, and/or other arrangements having similar functional purpose, etc.
  • Receptacle baskets or/and subsea connectors can be utilized for that purpose as well, in particular collet connectors.
  • the SCR hang-off assemblies can be pulled to their design locations using chain, wire, coiled tubing, etc. and fixed, clamped or/and latched in place.
  • the chain, wire, coiled tubing, etc. that was required for installation can be detached and removed or either the whole of it or a lower part of it can be retained in place as optional secondary (back-up) attachment means.
  • the upper parts of the said I-tubes, J-tubes etc. can be optionally utilized to contain platform piping pertaining to the riser in question, other risers, umbilicals, etc. Platform piping can also be lead outside said I-tubes, J-tubes, hawse pipes, etc. Design solutions like those described above are common in subsea engineering and further details are within the routine expertise of those skilled in the field.
  • FIG. 7 depicts a pivot-spool arrangement utilizing universal joints 701 , 703 and 705 as pivots located close to the centers of spirals.
  • FIG. 7 a features a triangular spiral spool 707 and
  • FIG. 7 b features a pyramidal spiral spool 709 with the pyramid shape narrowing upwards.
  • FIG. 7 c features a pyramidal spiral spool 711 with the pyramid shape narrowing downwards.
  • a spool similar to 707 can be designed to feature a smaller minimum lateral distance 713 between the center axis of the spring 715 and the center of a spool pipe cross section 717 than those that are possible for circular spools or other than triangular polygonal spool geometries.
  • triangular spools can feature greater tube lengths per spiral turn than those spool designs that are based on higher side number polygons, like for example quadrangles (including squares, rectangles and trapezoids), pentagons, etc.
  • quadrangles including squares, rectangles and trapezoids
  • pentagons etc.
  • this practical advantage is lost, because the tube lengths of all regular polygon-based spirals tend to the similar length of a circular spiral as the maximum spiral radius 719 approaches XD (say 5D), the lengths of the straight tubular segments tend to zero and the spiral geometry progressively better approximates a regular helix (i.e. a circular progressive spiral).
  • pyramidal spiral designs like those for example illustrated as 709 and/or 711 can be advantageous for example depending on installation considerations and/or requirements for improved access to the SCR hang-off assembly or/and to the pivot units like for example 701 , 703 or 705 .
  • Other advantages of the said pyramidal, conical and similar spool geometries can include:
  • FIGS. 7 a through 7 c feature optional examples of use of optional collet connectors 721 , 723 and 725 used for the principal structural subsea joints made offshore during the installations of the example systems featured.
  • Connectors can be also optionally used on one or both ends of spiral spools, as well as in any other optional locations, as it has already been mentioned herein.
  • FIGS. 7 a through 7 c Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 7 a through 7 c and those of wide ranges of similar designs will be routine to those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 8 depicts a pivot-spool arrangement utilizing a flexjoint 801 located above the center of planar (flat) spiral.
  • FIG. 8 features a circular spiral spool 803 supported with a 4 leg beam support frame 805 .
  • beam support frame 805 is pivoted on the riser hang-off assembly utilizing universal joint 807 .
  • the optional support (spider) beam structures shown in FIGS. 8 can have multiple purposes, for example:
  • the sliding support frame can be pivoted at location 807 , like is the spider frame shown in FIGS. 8 .
  • the said frame can be also rigidly or flexibly supported from the stress joint or transition joint of the SCR, it can be rigidly or flexibly supported from the floater (using springs, using elastic bungies, catenary lines, etc.).
  • Beam spider supports featuring any arbitrary numbers of support legs can be used.
  • a pivoted or flexible support it is beneficial to utilize 3-leg spider support frames, because of the advantages of three-point supports in 3-D.
  • Three-point supports tend to be effective in relieving self-weight stresses and providing reliable (also self-adjustable, if pivoted) span supports.
  • FIG. 8 shows for example purposes only a spider frame support 805 that supports the spiral spool at selected optional locations, whereas every other spool turn is supported by spider beams at optional locations. In the design shown there is no spool-support beam contact at locations between the optional sliding support locations.
  • a wide range of solutions for the design of optional fixed or movable spool support structures can be implemented. These can provide structural support to any kind of spiral spools that can feature planar or progressive spirals. Greater than one numbers of spool support structures that may be pivoted or fixed can be used to support a single spiral spool, whenever it is necessary or beneficial.
  • FIG. 9 depicts pivot 901 and 903 —spool 905 and 907 arrangements featuring progressive spirals 905 and 907 offset to locations above the said pivots.
  • FIG. 9 a features a ball joint 901 and a circular spiral spool 905 and
  • FIG. 9 b features a flexjoint 903 and a quadrangular spiral spool 907 .
  • platform piping in FIG. 9 is attached to semi submersible or TLP columns 909 and 911 .
  • a qualification related to design examples depicted in FIGS. 9 a and 9 b is that vertical offsetting of the spool center locations with regard to the locations of the pivots is that often higher stressing of the spools results, or larger spiral dimensions and/or greater number of spiral loops and/or higher strength materials might be required in designs like those presented in FIGS. 9 a and 9 b than on better stress-optimized designs.
  • the said qualification might be less relevant, or it might not apply or they not apply in cases where high torsional flexibility materials or high torsional flexibility section constructions are used.
  • the lateral and/or longitudinal offsets of the spiral spools allow the engineer more flexibility in the equipment design. Selections of offset spool locations can be made for reasons of ease of installation, ease of equipment access, ease of spatial arrangement, including staggering of equipment with regard to other equipment, etc.
  • FIGS. 9 a and 9 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 9 a and 9 b and those of wide ranges of similar designs will be routine for those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 10 depicts a pivot-spool arrangement featuring ball joints 1001 and 1003 and progressive spirals 1005 and 1007 offset approximately horizontally with regard to the location of the pivots 1009 and 1011 .
  • FIG. 10 a features a circular spiral spool and
  • FIG. 10 b features a triangular spiral spool.
  • FIG. 10 a depicts the riser hang-off assembly optionally sheltered from the action of waves and currents inside turret 1013 of an FPSO or FSO vessel.
  • Riser hang-off clamp 1021 is attached to ball joint 1001 utilizing optional collet connector 1017 .
  • FIG. 10 b depicts the riser hang-off assembly including the spiral located outside turret 1015 of an FPSO or FSO vessel.
  • the said riser hang-off assembly utilizes a tapered receptacle basket 1019 , which in the design implementation featured, is used during the system installation as the ‘principal’ structural offshore subsea connection.
  • said basket 1019 has, for the example design shown in FIG. 10 b , a similar role from the system installation point of view, to that of connector 1017 depicted in FIG. 10 a .
  • spirals 1005 , 1007 needed sheltering from waves and currents, optional shielding structures (not shown) would be arranged around the said spirals and they would typically be suspended from the said turrets.
  • FIGS. 10 a and 10 b Construction and design considerations related to those implementations of this invention that are depicted in FIGS. 10 a and 10 b and those of wide ranges of similar designs will be routine for those skilled in the field on the basis of the detailed descriptions of designs depicted in FIGS. 2 a and 2 b and considerations highlighted herein.
  • FIG. 11 depicts example details of a design of an SCR hang-off clamp assembly 1101 that is similar to those utilized in the designs depicted in FIGS. 2 through 10 . Additional design details are also shown in FIG. 11 .
  • FIG. 11 a depicts an example SCR stress joint 1103 —gooseneck 1105 arrangement.
  • FIG. 11 a also depicts an example hang-off clamp design 1107 utilizing a ball joint assembly 1109 as a pivoting arrangement.
  • FIG. 11 b depicts an example pivoting arrangement utilizing a ball joint assembly 1109 .
  • the said ball joint example shown is an example only and details of any ball joint design are immaterial to the matter of this invention.
  • the exploded assembly design shown features for example a meridionally split body 1111 , 1113 that is assembled utilizing optional locating pins 1115 and 1117 .
  • Optional fixed spherical bushing surfaces 1119 and optional adjustable spherical bushing surfaces 1121 are shown.
  • the assemblies can be welded or optionally bolted together using cover flanges 1123 and 1125 and optional stud bolts 1127 and 1129 .
  • the ball joint body and the cover flanges can be provided with optional strengthening ribs 1131 , 1133 and/or 1135 .
  • the external parts of the said ball joint assembly 1109 can be optionally shaped to fit a receptacle basket similar to that shown for example as 1019 in FIG. 10 b .
  • the optional bolted connection such as that depicted in FIG. 11 a between hang-off clamp 1101 and ball joint assembly 1111 , 1113 might preferably be replaced with a bolted and welded connection or it might optionally be replaced with an optional subsea connector.
  • the ball assembly 1137 can be attached to riser porch 1139 utilizing optional centering pins 1141 and 1143 , optional bolt or optional studs 1145 or it can be preferably landed inside the said receptacle basket that is structurally incorporated into or attached to the said porch.
  • ball assembly 1137 can be welded, or otherwise attached permanently, to any riser support structure utilized.
  • FIG. 11 c depicts an examplary flexjoint assembly 1147 connected to a hang-off clamp.
  • Optional high load bolted flange 1148 is depicted in FIG. 11 c, but for most applications use of full penetration butt welds instead of bolts, etc. would be preferable.
  • An optional connector could be optionally used instead of direct welding.
  • FIG. 11 d depicts an example hang-off clamp 1151 design utilizing a universal joint 1153 .
  • FIG. 11 e depicts an example hang-off clamp 1155 design utilizing shackles 1157 and padeyes 1159 assembly.
  • FIG. 11 f depicts an example assembly incorporating a hang-off clamp 1161 , shackle 1163 , padeye 1165 and chain 1167 .
  • FIG. 11 g depicts an example of a buoyancy clamp 1171 used on a pipe spool 1173 .
  • FIG. 11 h depicts an example of a helicoidal strake clamp 1175 used on a pipe spool 1173 to suppress VIVs.
  • Buoyancy clamps of a variety of designs can be used on the equipment described herein for several reasons, in particular:
  • FIG. 11 i depicts an example of bumper-support clamps 1177 used on a pipe spool 1173 to suppress VIVs and to support the submerged weight of parts of the spools.
  • the details of the shapes of the said bumper-support clamps 1177 as well as the gaps between clamps 1177 , their shapes, their buoyancies and sizes of the said bumper-support clamps 1177 used need to be optimized in the design process of any particular system.
  • Bumper support clamps 1177 that are used in different locations on spools 1173 could be of different sizes, as featured as an example only in FIG. 11 i, or they may be of the same size.
  • bumper-support clamps 1177 may be provided with contact shoes (not shown), which may be used in order to adjust any gaps between components to values required.
  • FIG. 11 i The example of a bumper-support clamp depicted in FIG. 11 i can have any combination of functional purposes in addition to those listed above. These may include in particular:
  • the nearly continuous or continuous supports can be achieved by using large numbers of said bumper support clamps installed densely on the piping.
  • the said bumper clamps can be provided with loose or tight optional shape protrusions 1179 made of the same or of different materials, loose optional sling connections 1181 and/or 1183 etc. in order to mechanically tie spiral loops together ( 1179 ) and/or in order to more effectively anchor the system ( 1181 , 1183 ) and thus effectively protect the system from the actions of currents and waves.
  • the shapes of the bumper clamps as well as the said optional protrusions and/or optional sling interconnections need to be designed so that the piping had sufficient capability to undergo torsional deformations as per the objectives of this invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Types And Forms Of Lifts (AREA)
US11/861,080 2007-09-25 2007-09-25 Flexible hang-off arrangement for a catenary riser Abandoned US20090078425A1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US11/861,080 US20090078425A1 (en) 2007-09-25 2007-09-25 Flexible hang-off arrangement for a catenary riser
AU2008211995A AU2008211995B2 (en) 2007-09-25 2008-09-04 Flexible hang-off arrangement for a catenary riser
MYPI20083486A MY165417A (en) 2007-09-25 2008-09-09 Flexible hang-off arrangement for a catenary riser
EP08016739.8A EP2042682B1 (en) 2007-09-25 2008-09-24 Flexible hang-off arrangement for a catenary riser
BRPI0803418-4A BRPI0803418A2 (pt) 2007-09-25 2008-09-25 arranjo suspenso flexìvel para um duto elevatório em catenária
US12/564,622 US8689882B2 (en) 2007-09-25 2009-09-22 Flexible hang-off arrangement for a catenary riser
US12/850,759 US8550171B2 (en) 2007-09-25 2010-08-05 Flexible hang-off arrangement for a catenary riser
AU2010238542A AU2010238542B2 (en) 2007-09-25 2010-10-29 Flexible hang-off arrangement for a catenary riser

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/861,080 US20090078425A1 (en) 2007-09-25 2007-09-25 Flexible hang-off arrangement for a catenary riser

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/564,622 Division US8689882B2 (en) 2007-09-25 2009-09-22 Flexible hang-off arrangement for a catenary riser

Publications (1)

Publication Number Publication Date
US20090078425A1 true US20090078425A1 (en) 2009-03-26

Family

ID=40196857

Family Applications (3)

Application Number Title Priority Date Filing Date
US11/861,080 Abandoned US20090078425A1 (en) 2007-09-25 2007-09-25 Flexible hang-off arrangement for a catenary riser
US12/564,622 Expired - Fee Related US8689882B2 (en) 2007-09-25 2009-09-22 Flexible hang-off arrangement for a catenary riser
US12/850,759 Expired - Fee Related US8550171B2 (en) 2007-09-25 2010-08-05 Flexible hang-off arrangement for a catenary riser

Family Applications After (2)

Application Number Title Priority Date Filing Date
US12/564,622 Expired - Fee Related US8689882B2 (en) 2007-09-25 2009-09-22 Flexible hang-off arrangement for a catenary riser
US12/850,759 Expired - Fee Related US8550171B2 (en) 2007-09-25 2010-08-05 Flexible hang-off arrangement for a catenary riser

Country Status (5)

Country Link
US (3) US20090078425A1 (pt)
EP (1) EP2042682B1 (pt)
AU (2) AU2008211995B2 (pt)
BR (1) BRPI0803418A2 (pt)
MY (1) MY165417A (pt)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011070376A1 (en) * 2009-12-11 2011-06-16 Subsea 7 Limited Pipeline hold back clamp
US20130209175A1 (en) * 2010-08-04 2013-08-15 Craig Scott Keyworth Corrosion protection of pipes suspended in seawater
US20150142396A1 (en) * 2012-04-27 2015-05-21 Acergy Frnace SA Method and Apparatus for Design of Pipeline Components
US20190136687A1 (en) * 2016-12-20 2019-05-09 Halliburton Energy Services, Inc. Methods and Systems for Downhole Inductive Coupling
CN109795634A (zh) * 2019-02-19 2019-05-24 长沙学院 连杆调节式柔性托架
US10597952B2 (en) 2017-03-09 2020-03-24 Single Buoy Moorings, Inc. Steel catenary riser top interface
CN111539544A (zh) * 2020-06-22 2020-08-14 中铁工程设计咨询集团有限公司 一种接触网设备管理方法及系统
US10967949B2 (en) 2016-11-10 2021-04-06 Single Buoy Moorings, Inc. Seawater intake riser interface with vessel hull
WO2022036426A1 (pt) * 2020-08-19 2022-02-24 Petróleo Brasileiro S.A. - Petrobras Sistema para flexibilizaçãoda suportação de riser em unidades estacionárias de produçãoe método de instalação
CN117895727A (zh) * 2024-03-12 2024-04-16 德阳市建安机械制造有限公司 变转速抽水蓄能机组转子中空曲面零部件及其加工方法
EP4488487A1 (en) * 2023-07-04 2025-01-08 Nexans Cable system connectable to an offshore structure

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090078425A1 (en) * 2007-09-25 2009-03-26 Seahorse Equipment Corp Flexible hang-off arrangement for a catenary riser
EP2372206A1 (en) * 2010-03-24 2011-10-05 BP Exploration Operating Company Limited Spool piece
US9352808B2 (en) 2012-01-16 2016-05-31 Seahorse Equipment Corp Offshore platform having SCR porches mounted on riser keel guide
US9701369B2 (en) 2012-06-21 2017-07-11 National Oilwell Varco Denmark I/S Offshore top site system
ES2454044B1 (es) 2012-10-08 2015-03-10 Iberdrola Ingenieria Y Construccion S A U Plataforma flotante en tensión de especial aplicación para aprovechamiento eólico
KR102066630B1 (ko) * 2013-11-19 2020-01-15 대우조선해양 주식회사 스틸 커티너리 라이저 지지장치 및 이를 구비한 부유식 해양 구조물
KR102065935B1 (ko) * 2013-11-20 2020-01-14 대우조선해양 주식회사 라이저 거치대 및 이를 포함하는 부유식 구조물 또는 선박
GB201321416D0 (en) * 2013-12-04 2014-01-15 Balltec Ltd Apparatus and method for disconnecting male and female connectors
US9587446B2 (en) * 2015-03-26 2017-03-07 Chevron U.S.A. Inc. Subsea removable flex joint laydown tool
US11156313B2 (en) 2015-04-16 2021-10-26 Krzysztof Jan Wajnikonis Mechanical connectors
WO2016168797A1 (en) 2015-04-16 2016-10-20 Krzysztof J Wajnikonis Mechanical connector of long torsional and bending fatigue life
US11906079B2 (en) 2015-04-16 2024-02-20 Krzysztof Jan Wajnikonis Telescopically assembled mechanical connector
US11781682B2 (en) 2015-04-16 2023-10-10 Krzysztof Jan Wajnikonis Enhancements of mechanical connector technology
GB2556700B (en) * 2015-05-27 2021-03-24 Jan Wajnikonis Krzysztof Flexible hang-off for a rigid riser
WO2017008988A1 (en) * 2015-07-15 2017-01-19 Seaproof Solutions As Variable length offshore cable and method of installation
US9988860B2 (en) 2015-12-03 2018-06-05 Single Buoy Moorings, Inc. Method and apparatus for elevating the tapered stress joint or flex joint of an SCR above the water
WO2017204649A1 (en) * 2016-05-26 2017-11-30 Statoil Petroleum As A riser hanger and method
BR102016024269B1 (pt) * 2016-10-18 2023-05-16 Petróleo Brasileiro S.A. - Petrobras Sistema de auto-alinhamento e enrijecimento de dutos flexíveis em uma unidade estacionária de produção, e, método de instalação de dutos flexíveis através do mesmo
GB2566055B (en) * 2017-08-31 2021-12-01 Subsea 7 Norway As Subsea pig launchers
GB2566502B (en) * 2017-09-15 2021-06-09 Equinor Energy As Offshore wellhead platform
EP3781778B1 (en) * 2018-04-20 2024-06-26 Oceaneering International, Inc. Underwater scr lifting frame
US10544630B1 (en) * 2018-12-12 2020-01-28 Chevron U.S.A. Inc. Systems and methods for slug mitigation
CN111188597B (zh) * 2019-12-31 2022-03-15 中国海洋石油集团有限公司 一种软悬挂状态下的隔水管安全监测系统及方法
GB2593494B (en) 2020-03-24 2022-09-07 Subsea 7 Do Brasil Servicos Ltda Subsea Risers
US11572745B2 (en) * 2020-04-08 2023-02-07 Oil States Industries, Inc. Rigid riser adapter for offshore retrofitting of vessel with flexible riser balconies
US11274504B2 (en) 2020-05-07 2022-03-15 Subsea 7 Do Brasil Servicos Ltda Top connections of subsea risers
DK4273431T3 (da) * 2022-05-05 2025-03-24 Technipfmc Subsea France Ophængningssystem til måling af en topspænding i et fleksibelt rør, tilhørende anordning og monteringsmetode

Citations (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3189098A (en) * 1961-12-29 1965-06-15 Shell Oil Co Marine conductor pipe assembly
US3461916A (en) * 1966-12-13 1969-08-19 Exxon Production Research Co Flexible flowline
US3701551A (en) * 1970-11-23 1972-10-31 Subsea Equipment Ass Ltd Multi-conduit riser with a flexible joint
US3718183A (en) * 1971-07-12 1973-02-27 Byron Jackson Inc Subsea bumper sub hydraulic bypass system
US3913668A (en) * 1973-08-22 1975-10-21 Exxon Production Research Co Marine riser assembly
US4067202A (en) * 1976-04-30 1978-01-10 Phillips Petroleum Company Single point mooring buoy and transfer facility
US4127145A (en) * 1975-12-20 1978-11-28 Metallschlauch-Fabrik Pforzheim (Vorm. Hch. Witzenmann) Gesellschaft Mit Beschrankter Haftung Movable pipeline element
US4137948A (en) * 1977-07-26 1979-02-06 Single Buoy Moorings Inc. Intermediate conduit between two pivotally connected conduits
US4165108A (en) * 1977-01-14 1979-08-21 Societe Nationale Elf Aquitaine (Production) Device for connecting tubes having a small cross-section perpendicularly to a universal coupling element
US4279544A (en) * 1977-01-11 1981-07-21 Compagnie Francaise Des Petroles Helical apparatus for coupling submerged pipes
US4311327A (en) * 1979-12-20 1982-01-19 Exxon Production Research Company Universal joint for multiple flowline system
US4348137A (en) * 1977-08-12 1982-09-07 Entreprise D'equipements Mecaniques Et Hydrauliques Emh Pivotal connection for articulated column of sea-bed working structure
US4362215A (en) * 1979-11-30 1982-12-07 Institut Francais Du Petrole Marine riser provided with a hinged foot for offshore hydrocarbon production
US4398331A (en) * 1980-04-24 1983-08-16 Agency Of Industrial Science & Technology Method of connecting pipe pieces via universal joint
US4456073A (en) * 1982-08-24 1984-06-26 Exxon Production Research Co. Flexible connection apparatus
US4529334A (en) * 1984-01-30 1985-07-16 Exxon Production Research Co. Production riser assembly
US4630681A (en) * 1985-02-25 1986-12-23 Decision-Tree Associates, Inc. Multi-well hydrocarbon development system
US4915416A (en) * 1986-11-27 1990-04-10 The British Petroleum Company P.L.C. Underwater oil production
US5269629A (en) * 1991-07-29 1993-12-14 Shell Oil Company Elastomeric swivel support assembly for catenary riser
US5447392A (en) * 1993-05-03 1995-09-05 Shell Oil Company Backspan stress joint
US5553976A (en) * 1994-02-18 1996-09-10 Korsgaard; Jens Fluid riser between seabed and floating vessel
US5702205A (en) * 1995-12-04 1997-12-30 Mobil Oil Corporation Steel catenary riser system for marine platform
US6062769A (en) * 1998-08-06 2000-05-16 Fmc Corporation Enhanced steel catenary riser system
US6213215B1 (en) * 1996-11-27 2001-04-10 Den Norske Stats Oljeselskap A. S System, vessel, seabed installation and method for producing oil or gas
US20040031614A1 (en) * 2002-04-26 2004-02-19 Kleinhans John W. Marine bottom tensioned riser and method
US6739804B1 (en) * 1999-04-21 2004-05-25 Ope, Inc. SCR top connector
US20080214072A1 (en) * 2004-10-11 2008-09-04 Stolt Offshore Sa Apparatus And Method For Connection And Disconnection Of A Marine Riser

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4195416A (en) * 1977-05-30 1980-04-01 Hall Marshall J Combination hair/hand/body dryer and vapor dispenser
GB2203508A (en) * 1987-04-16 1988-10-19 Shell Int Research System and method for securing a marine riser to a floating structure
FR2689603B1 (fr) * 1992-04-07 1994-05-20 Coflexip Dispositif de montage d'une ligne flexible comportant un limiteur de courbure.
DE9312997U1 (de) * 1993-08-30 1995-01-05 Pies, Gerrit, 42699 Solingen Nutenstein
US5615977A (en) * 1993-09-07 1997-04-01 Continental Emsco Company Flexible/rigid riser system
GB9915998D0 (en) * 1999-07-09 1999-09-08 Dixon Roche Keith Riser system
FR2807814B1 (fr) * 2000-04-17 2002-07-12 Techlam Dispositif de connexion d'une ligne immergee de transport de fluide
US6536527B2 (en) * 2000-05-16 2003-03-25 Abb Vetco Gray Inc. Connection system for catenary riser
NO318188B1 (no) 2003-06-02 2005-02-14 Aker Riser Systems As Anordning ved stigeror
NO325132B1 (no) * 2004-03-31 2008-02-04 Aker Subsea As Konnektor
US7472755B2 (en) * 2004-06-28 2009-01-06 Riggs David C Method for inspection and repair of a flexible joint
WO2006041904A1 (en) * 2004-10-06 2006-04-20 Single Buoy Moorings, Inc. Riser connector
FR2890098B1 (fr) * 2005-08-26 2008-01-04 Saipem S A Sa Installation comprenant au moins deux liaisons fond-surface d'au moins deux conduites sous-marines reposant au fond de la mer
US20090078425A1 (en) * 2007-09-25 2009-03-26 Seahorse Equipment Corp Flexible hang-off arrangement for a catenary riser

Patent Citations (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3189098A (en) * 1961-12-29 1965-06-15 Shell Oil Co Marine conductor pipe assembly
US3461916A (en) * 1966-12-13 1969-08-19 Exxon Production Research Co Flexible flowline
US3701551A (en) * 1970-11-23 1972-10-31 Subsea Equipment Ass Ltd Multi-conduit riser with a flexible joint
US3718183A (en) * 1971-07-12 1973-02-27 Byron Jackson Inc Subsea bumper sub hydraulic bypass system
US3913668A (en) * 1973-08-22 1975-10-21 Exxon Production Research Co Marine riser assembly
US4127145A (en) * 1975-12-20 1978-11-28 Metallschlauch-Fabrik Pforzheim (Vorm. Hch. Witzenmann) Gesellschaft Mit Beschrankter Haftung Movable pipeline element
US4067202A (en) * 1976-04-30 1978-01-10 Phillips Petroleum Company Single point mooring buoy and transfer facility
US4279544A (en) * 1977-01-11 1981-07-21 Compagnie Francaise Des Petroles Helical apparatus for coupling submerged pipes
US4165108A (en) * 1977-01-14 1979-08-21 Societe Nationale Elf Aquitaine (Production) Device for connecting tubes having a small cross-section perpendicularly to a universal coupling element
US4137948A (en) * 1977-07-26 1979-02-06 Single Buoy Moorings Inc. Intermediate conduit between two pivotally connected conduits
US4348137A (en) * 1977-08-12 1982-09-07 Entreprise D'equipements Mecaniques Et Hydrauliques Emh Pivotal connection for articulated column of sea-bed working structure
US4362215A (en) * 1979-11-30 1982-12-07 Institut Francais Du Petrole Marine riser provided with a hinged foot for offshore hydrocarbon production
US4311327A (en) * 1979-12-20 1982-01-19 Exxon Production Research Company Universal joint for multiple flowline system
US4398331A (en) * 1980-04-24 1983-08-16 Agency Of Industrial Science & Technology Method of connecting pipe pieces via universal joint
US4456073A (en) * 1982-08-24 1984-06-26 Exxon Production Research Co. Flexible connection apparatus
US4529334A (en) * 1984-01-30 1985-07-16 Exxon Production Research Co. Production riser assembly
US4630681A (en) * 1985-02-25 1986-12-23 Decision-Tree Associates, Inc. Multi-well hydrocarbon development system
US4915416A (en) * 1986-11-27 1990-04-10 The British Petroleum Company P.L.C. Underwater oil production
US5269629A (en) * 1991-07-29 1993-12-14 Shell Oil Company Elastomeric swivel support assembly for catenary riser
US5447392A (en) * 1993-05-03 1995-09-05 Shell Oil Company Backspan stress joint
US5553976A (en) * 1994-02-18 1996-09-10 Korsgaard; Jens Fluid riser between seabed and floating vessel
US5702205A (en) * 1995-12-04 1997-12-30 Mobil Oil Corporation Steel catenary riser system for marine platform
US6213215B1 (en) * 1996-11-27 2001-04-10 Den Norske Stats Oljeselskap A. S System, vessel, seabed installation and method for producing oil or gas
US6062769A (en) * 1998-08-06 2000-05-16 Fmc Corporation Enhanced steel catenary riser system
US6739804B1 (en) * 1999-04-21 2004-05-25 Ope, Inc. SCR top connector
US20040031614A1 (en) * 2002-04-26 2004-02-19 Kleinhans John W. Marine bottom tensioned riser and method
US7104329B2 (en) * 2002-04-26 2006-09-12 Bp Corporation North America Inc. Marine bottomed tensioned riser and method
US20080214072A1 (en) * 2004-10-11 2008-09-04 Stolt Offshore Sa Apparatus And Method For Connection And Disconnection Of A Marine Riser

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011070376A1 (en) * 2009-12-11 2011-06-16 Subsea 7 Limited Pipeline hold back clamp
US20130209175A1 (en) * 2010-08-04 2013-08-15 Craig Scott Keyworth Corrosion protection of pipes suspended in seawater
US20150142396A1 (en) * 2012-04-27 2015-05-21 Acergy Frnace SA Method and Apparatus for Design of Pipeline Components
US10216873B2 (en) * 2012-04-27 2019-02-26 Acergy France SAS Method and apparatus for design of pipeline components
US10967949B2 (en) 2016-11-10 2021-04-06 Single Buoy Moorings, Inc. Seawater intake riser interface with vessel hull
US10801320B2 (en) * 2016-12-20 2020-10-13 Halliburton Energy Services, Inc. Methods and systems for downhole inductive coupling
US20190136687A1 (en) * 2016-12-20 2019-05-09 Halliburton Energy Services, Inc. Methods and Systems for Downhole Inductive Coupling
US10597952B2 (en) 2017-03-09 2020-03-24 Single Buoy Moorings, Inc. Steel catenary riser top interface
CN109795634A (zh) * 2019-02-19 2019-05-24 长沙学院 连杆调节式柔性托架
CN111539544A (zh) * 2020-06-22 2020-08-14 中铁工程设计咨询集团有限公司 一种接触网设备管理方法及系统
WO2022036426A1 (pt) * 2020-08-19 2022-02-24 Petróleo Brasileiro S.A. - Petrobras Sistema para flexibilizaçãoda suportação de riser em unidades estacionárias de produçãoe método de instalação
GB2613315A (en) * 2020-08-19 2023-05-31 Petroleo Brasileiro Sa Petrobras System for improving flexibility of riser supports in stationary production units and installation method
GB2613315B (en) * 2020-08-19 2024-11-27 Petroleo Brasileiro Sa Petrobras System for improving flexibility of riser supports in stationary production units and installation method
EP4488487A1 (en) * 2023-07-04 2025-01-08 Nexans Cable system connectable to an offshore structure
CN117895727A (zh) * 2024-03-12 2024-04-16 德阳市建安机械制造有限公司 变转速抽水蓄能机组转子中空曲面零部件及其加工方法

Also Published As

Publication number Publication date
AU2008211995A1 (en) 2009-04-09
AU2008211995B2 (en) 2010-11-25
US8689882B2 (en) 2014-04-08
US20100006300A1 (en) 2010-01-14
EP2042682B1 (en) 2015-01-21
US8550171B2 (en) 2013-10-08
BRPI0803418A2 (pt) 2009-06-02
US20100294504A1 (en) 2010-11-25
AU2010238542B2 (en) 2012-02-16
MY165417A (en) 2018-03-21
EP2042682A2 (en) 2009-04-01
AU2010238542A1 (en) 2010-11-18
EP2042682A3 (en) 2013-12-25

Similar Documents

Publication Publication Date Title
US8689882B2 (en) Flexible hang-off arrangement for a catenary riser
US10024121B2 (en) Flexible hang-off for a rigid riser
EP1468164B1 (en) Riser for connection between a vessel and a point at the seabed
US8888411B2 (en) Catenary line dynamic motion suppression
US20090133612A1 (en) Dynamic motion suppression of riser, umbilical and jumper lines
EP2699754B1 (en) Subsea conduit system
EP3004519B1 (en) Pipe components and methods of manufacture
CN1118618A (zh) 挠性/刚性上升管系统
AU2002335590A1 (en) Riser for connection between a vessel and a point at the seabed
US7677837B2 (en) Device for transferring fluid between two floating supports
EP4127379B1 (en) Subsea risers
US20250361776A1 (en) Improving fatigue resistance of steel catenary risers
EP4544146A1 (en) Improving fatigue resistance of steel catenary risers

Legal Events

Date Code Title Description
AS Assignment

Owner name: SEAHORSE EUIPMENT CORP., TEXAS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:WAJNIKONIS, KRZYSZTOF J.;LEVERETTE, STEVEN JOHN;REEL/FRAME:019875/0979;SIGNING DATES FROM 20070924 TO 20070925

AS Assignment

Owner name: SEAHORSE EQUIPMENT CORP., TEXAS

Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE NAME WHICH WAS MISSPELLED. PREVIOUSLY RECORDED ON REEL 019875 FRAME 0979;ASSIGNORS:WAJNIKONIS, KRZYSZTOF J.;LEVERETTE, STEVEN JOHN;REEL/FRAME:021456/0017;SIGNING DATES FROM 20070924 TO 20070925

STCB Information on status: application discontinuation

Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION