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US3248886A - Anti-flutter device for riser pipe - Google Patents

Anti-flutter device for riser pipe Download PDF

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Publication number
US3248886A
US3248886A US304038A US30403863A US3248886A US 3248886 A US3248886 A US 3248886A US 304038 A US304038 A US 304038A US 30403863 A US30403863 A US 30403863A US 3248886 A US3248886 A US 3248886A
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riser pipe
sheet
cylinder
assembly
drilling
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US304038A
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Kenneth A Blenkarn
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Pan American Petroleum Corp
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Pan American Petroleum Corp
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    • 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

Definitions

  • riser pipe This is customarily taken care of by using what is called a riser pipe.
  • This riser pipe is attached to the marine drilling equipment cemented in the ocean floor.
  • a flexible joint which permits the upper end of the riser pipe to change in angular position relative to the bottom through an angle of some three to ten degrees.
  • the riser pipe assembly includes a slip joint which permits the upper portion of this assembly to move longitudinally with respect to the lower position through a distance of feet or more.
  • This telescoping joint is suitably packed off to insure no appreciable leakage of drilling fluid into the surrounding water or vice versa. Drilling operations are conducted inside this riser pipe.
  • This assembly permits the riser pipe type of drilling operation to be carried out in the presence of currents which would otherwise cause mechanical failure of this part ofthe system.
  • FIGURE 1 shows in diagrammatic view a cross section of the ocean at the location of a floating drilling vessel, showing the riser pipe'assernbly.
  • FIGURE 2 shows One form of an assembly (called a spoiler assembly) which illustrates an embodiment of my invention.
  • FIGURE 3 shows a cross sectional view of the equipment shown in FIGURE 2.
  • FIGURE 1 there is shown a cross section through the ocean at the location of a floating drilling vessel 11 located at the surface 12 of the ocean. At some point which may be of the order of 100 feet or more below the drilling vessel is the ocean floor 13. Mounted on this ocean floor and normally cemented to it is an assemblage of drilling apparatus, which is shown in diagrammatic form as a block 14, since it merely illustrates the background in which my invention is situated. It may, and customarily will, include a suitable base and one or more blowout preventers, etc.
  • riser pipe assembly 15 At the lower part of this riser pipe assembly is the flexible joint 16 which permits angular deviation of the upper part of the riser pipe as mentioned above.
  • the slip joint 17 At the upper part of the riser pipe assembly and customarily immediately below the base of the drilling vessel 11 is located the slip joint 17. The upper end of this is flexibly attached to the drilling vessel 11.
  • a drill rig 18 is mounted on the drilling vessel 11, immediately above the top of the riser pipe assembly 15.
  • the drill string is threaded through the riser pipe assembly 15.
  • drilling fluid is circulated through the drill string and back through the annulus between the string and the riser pipe assembly 15..
  • the drilling vessel is anchored by anchor lines (such as those shown at 19) from anchors (not shown).
  • This spoiler consists of a cylindrical perforated metal sheet or the like which is approximately 8 inches in diameter greater than the outer diameter of the riser pipe and which contains clamps holding the sheet to the riser pipe at intervals of the order of 4 to 6 feet.
  • FIGURE 2 is shown one unit of the'flow control spoiler. This has a length L of the order of 10 feet and a diameter D approximately 8 inches greater than the diameter D of the riser pipe.
  • the outer surface 20 of this spoiler is made of perforated sheet metal in which preferably the ratio of area of the holes to that of the remaining solid material is about one to one. This provides as much hole area as possible without too greatly weakening the structure. However, depending upon conditions, some benefit is gained if this ratio, instead of being approximately 1 to 1, is as much as 5 to 1 or as little as 1 to 5.
  • FIGURES 2 and 3 Any simple but strong clamping system may be employed to hold the perforated sheet about but radially separated from the pipe 15.
  • the spoiler assembly is made in the form of two half-cylinders each containing a matching clamping half-ring 21, the inner diameter of which is that of the riser pipe 15 and the outer diameter of which is that of the perforated sheet 20.
  • Three of 3 these rings 21 are shown in FIGURES 2 and 3, one at each end and one at about the middle. These are, of course, axially separated as they must be. They are firmly attached to the sheet, for example by welding, and are lined up so that three hinges 22 can be attached to the halves of the total assemblage.
  • each of these spoiler units may be made up with some space in between, but since it is desirable to minimize as far as possible the formation of the eddies, I prefer to butt each of these spoiler units against the adjacent ones so that there is a continuous outer cylindrical sheet of perforated metal extending substantially from the flex joint 16 to the lower end of the maximum extension of the slip joint 17, as shown in FIGURE 1. In any case, the perforate sheets of such spoiler units should cover a major part of the pipe exposed to the current.
  • the thickness of the perforated plate is not particularly critical. In one such assembly which has been tested, the plate was approximately /4 inch thick With /2 inch holes punched through it. It is desirable to have the edges of the perforations as sharp as possible.
  • each of the spoiler units making up the assembly without varying from the major design which has been shown.
  • material such as chain link fencing for the perforated plate.
  • Transverse metal grating could be employed satisfactorily.
  • the spacing between the riser pipe and the spoiler sheet is not particularly critical. While a spacing of approximately 4 inches has been found desirable, this spacing may be as little as 2 inches or as great as 6 inches or more.
  • the particular clamping assemblage shown is merely one of many that can be made up, the principal design consideration being to hold the perforated spoiler sheet substantially fixed in place relative to the outer surface of the riser pipe.
  • An assemblage for minimizing current induced transverse vibration in a cylinder extending upward from and attached to the floor of a body of water which comprises at least one cylindrical perforated sheet surrounding said cylinder, the total area of perforated sheet covering at least a major part of said cylinder, and
  • said plurality of said spoilers covering at least a major part of said pipe, but without substantial obstruction to water waves in both axial and circumferential directions.
  • An assemblage for minimizing current-induced vibration in a cylinder surrounded by a liquid which comprises a cylindrical perforated sheet surrounding said cylinder,
  • said sheet and said rings being axially split along a plane passing through the cylindrical axis of said sheet

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  • 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)

Description

May 3, 1966 K. A. BLENKARN ANTI-FLUTTER DEVICE FOR RISER PIPE 2 Sheets-Sheet 1 Filed Aug. 23 1963 INVENTOR. KENNETH A. BLENKARN BY/DQQM ATTORNEY.
y 1966 K. A. BLENKARN 3,248,886
Filed Aug. 25, 1965 2 Sheets-Sheet 2 INVENTOR. KENNETH A. BLENKARN :1 M4 w FIG-2 ATTORNEY United States Patent 3,248,836 ANTI-FLUTTER DEVICE FDR RISER PIPE Kenneth A. Blenkarn, Tulsa, 01th., assignor to Pan American Petroleum Corporation, Tulsa, Okla., a corporation of Delaware Filed Aug. 23, 1963, Ser. No. 304,038 9 Claims. (CI. 61-46) This invention pertains to marine drilling operations carried out from a floating vessel or the like. In such marine operations, it is necessary to provide a tubular conduit and guide from the anchored drilling vessel to the top of the well at the sea floor. This is customarily taken care of by using what is called a riser pipe. This riser pipe is attached to the marine drilling equipment cemented in the ocean floor. Immediately above, there is a flexible joint which permits the upper end of the riser pipe to change in angular position relative to the bottom through an angle of some three to ten degrees. low the floating drilling vessel the riser pipe assembly includes a slip joint which permits the upper portion of this assembly to move longitudinally with respect to the lower position through a distance of feet or more. This telescoping joint is suitably packed off to insure no appreciable leakage of drilling fluid into the surrounding water or vice versa. Drilling operations are conducted inside this riser pipe.
It is apparent that it is desirable to maintain the riser pipe in a fixed position during the course of drilling. However, it has been found that in marine drilling operations conducted in the presence of strong ocean currents, for example when drilling a marine inlet, near a river mouth, or the like, the riser pipe develops a strong transverse vibration. Stated another way, the middle portion of the riser pipe tends to oscillate transversely with respect to the base and top, thus causing continual flexure of this pipe and of the drill pipe inside it. Such vibration can give rise to mechanical failure, considerably impeding the successful course of drilling.
It is an object of this invention to provide simple equipment which can be assembled on or around the riser pipe and thus prevent the occurrence of vibration due to currents in the water. This assembly permits the riser pipe type of drilling operation to be carried out in the presence of currents which would otherwise cause mechanical failure of this part ofthe system.
This invention is illustrated with the following drawmgs:
FIGURE 1 shows in diagrammatic view a cross section of the ocean at the location of a floating drilling vessel, showing the riser pipe'assernbly.
FIGURE 2 shows One form of an assembly (called a spoiler assembly) which illustrates an embodiment of my invention.
FIGURE 3 shows a cross sectional view of the equipment shown in FIGURE 2.
Many explanations have been advanced for the occurrence of vibration transverse to the longitudinal axis of the riser pipe during the course of marine drilling from a floating vessel. Experience early indicated that this vibration was associated with ocean currents impinging on the riser pipe. In FIGURE 1, there is shown a cross section through the ocean at the location of a floating drilling vessel 11 located at the surface 12 of the ocean. At some point which may be of the order of 100 feet or more below the drilling vessel is the ocean floor 13. Mounted on this ocean floor and normally cemented to it is an assemblage of drilling apparatus, which is shown in diagrammatic form as a block 14, since it merely illustrates the background in which my invention is situated. It may, and customarily will, include a suitable base and one or more blowout preventers, etc. Mounted on this is the Immediately be- 3,248,886 Fatented May 3, 1966 riser pipe assembly 15. At the lower part of this riser pipe assembly is the flexible joint 16 which permits angular deviation of the upper part of the riser pipe as mentioned above. At the upper part of the riser pipe assembly and customarily immediately below the base of the drilling vessel 11 is located the slip joint 17. The upper end of this is flexibly attached to the drilling vessel 11. A drill rig 18 is mounted on the drilling vessel 11, immediately above the top of the riser pipe assembly 15. The drill string is threaded through the riser pipe assembly 15. As drilling proceeds, drilling fluid is circulated through the drill string and back through the annulus between the string and the riser pipe assembly 15.. The drilling vessel is anchored by anchor lines (such as those shown at 19) from anchors (not shown).
It is apparent from an inspection of this figure that the riser pipe assembly below the slip joint 17 is a column in compression and that such column may be subject to considerable buckling stresses under the circumstances. The presence of transverse mechanical vibrations in this riser pipe assembly accordingly accentuates any tendency of the riser pipe assembly to bend or buckle. .At the same time such vibration, by application of an alternating stress, has a considerable tendency to cause the riser pipe assembly to fail under fatigue.
It has been found that the tendency of the riser pipe assembly to vibrate transversely increases as the current of water flowing by the assembly increases. Severe mechanical oscillation in a foot riser pipe has been observed in a current of about 7 mph. with, for example, an amplitude 25 feet down of approximately four inches at a frequency of about one-third to one-half cycle per second. Apparently, the riser pipe oscillates with a maximum amplitude more or less at the middle and substantially Zero amplitude at both ends.
One might assume that the principal problem would be that of dam-ping vibration and that, in the presence of the water, such vibration could be easily damped. However, this is not the main problem, which is that of preventing the formation of streams of eddies behind the riser pipe; that is, downstream from it. The presence of these eddies gives rise to an oscillating force transverse to the riser pipe. Accordingly, it is necessary to utilize a system minimizing the formation of these eddy currents.
I have found that it is possible substantially to prevent this transverse vibration due to currents by clamping to the riser pipe an apparatus which I call a flow control spoiler. This spoiler consists of a cylindrical perforated metal sheet or the like which is approximately 8 inches in diameter greater than the outer diameter of the riser pipe and which contains clamps holding the sheet to the riser pipe at intervals of the order of 4 to 6 feet. Thus, for example, in FIGURE 2 is shown one unit of the'flow control spoiler. This has a length L of the order of 10 feet and a diameter D approximately 8 inches greater than the diameter D of the riser pipe. The outer surface 20 of this spoiler is made of perforated sheet metal in which preferably the ratio of area of the holes to that of the remaining solid material is about one to one. This provides as much hole area as possible without too greatly weakening the structure. However, depending upon conditions, some benefit is gained if this ratio, instead of being approximately 1 to 1, is as much as 5 to 1 or as little as 1 to 5.
Any simple but strong clamping system may be employed to hold the perforated sheet about but radially separated from the pipe 15. In FIGURES 2 and 3, one form of such clamp is shown. The spoiler assembly is made in the form of two half-cylinders each containing a matching clamping half-ring 21, the inner diameter of which is that of the riser pipe 15 and the outer diameter of which is that of the perforated sheet 20. Three of 3 these rings 21 are shown in FIGURES 2 and 3, one at each end and one at about the middle. These are, of course, axially separated as they must be. They are firmly attached to the sheet, for example by welding, and are lined up so that three hinges 22 can be attached to the halves of the total assemblage. Completely opposite from the hinges 22 are three simple clamps 23 Welded to the half-rings 21. Accordingly, as the riser pipe assembly is made up, the spoiler unit is simply placed about the pipe and the halves clamped together, for example, by bolts 24. This firmly attaches one unit of the spoiler assembly about the riser pipe.
These assemblies may be made up with some space in between, but since it is desirable to minimize as far as possible the formation of the eddies, I prefer to butt each of these spoiler units against the adjacent ones so that there is a continuous outer cylindrical sheet of perforated metal extending substantially from the flex joint 16 to the lower end of the maximum extension of the slip joint 17, as shown in FIGURE 1. In any case, the perforate sheets of such spoiler units should cover a major part of the pipe exposed to the current.
The thickness of the perforated plate is not particularly critical. In one such assembly which has been tested, the plate was approximately /4 inch thick With /2 inch holes punched through it. It is desirable to have the edges of the perforations as sharp as possible.
It is apparent that numerous modifications and changes may be made in the design of each of the spoiler units making up the assembly without varying from the major design which has been shown. Thus, for example, it is possible to substitute material such as chain link fencing for the perforated plate. Transverse metal grating could be employed satisfactorily. However, it is still desirable to maintain a ratio of hole area to remaining sheet area of approximately 1 to 1 if possible. Again, the spacing between the riser pipe and the spoiler sheet is not particularly critical. While a spacing of approximately 4 inches has been found desirable, this spacing may be as little as 2 inches or as great as 6 inches or more. The particular clamping assemblage shown is merely one of many that can be made up, the principal design consideration being to hold the perforated spoiler sheet substantially fixed in place relative to the outer surface of the riser pipe.
I claim:
1. An assemblage for minimizing current induced transverse vibration in a cylinder extending upward from and attached to the floor of a body of water which comprises at least one cylindrical perforated sheet surrounding said cylinder, the total area of perforated sheet covering at least a major part of said cylinder, and
a plurality of axially substantially separated supports radially attaching said perforated sheet firmly to but' separated from said cylinder, said supports forming the ratio of area of perforations to the area of remaining sheet lying between approximately 1:5 I
and 5:1, and at least two substantially axially separated radial supports, one near each end of each spoiler mounting said perforatedsheet firmly upon but I radially separated from said pipe,
said plurality of said spoilers covering at least a major part of said pipe, but without substantial obstruction to water waves in both axial and circumferential directions.
3.- Apparatus in accordance with claim 2 in which the radial spacing from said sheet to the outer surface of said pipe is about 2 to 6 inches.
4. Apparatus in accordance with claim 2 in which the radial spacing from said sheet to the outer surface of-said pipe is about 2 to 6 inches and said ratio is approximately 1:1.
5. An assemblage for minimizing current-induced vibration in a cylinder surrounded by a liquid which comprises a cylindrical perforated sheet surrounding said cylinder,
and
a plurality of axially separated supporting rings the inher diameter of which is substantially the outer diameter of said cylinder, said rings being firmly attached to-said sheet with at least one of said rings near each end of said sheet, said rings being axially separated by a distance substantially greater than the difference in outer diameter of said sheet and said cylinder and furnishing the only obstruction to axial flow of liquid between said sheet and said cylinder,
said sheet and said rings being axially split along a plane passing through the cylindrical axis of said sheet,
a plurality of hinges connecting one set of adjacent ends of said rings, and
a plurality of clamps mounted on the opposite set of ends of said rings from said hinges, whereby said assemblage may be mounted around and clamped to said cylinder.
6. Apparatus in accordance with claim 5 in which the radial spacing of each of said rings is about 2 to 6 inches.
7. Apparatus in accordance with claim 5 in which the radial spacing of each of said rings is about 4 inches.
8. Apparatus in accordance with claim 5 in which the radial spacing of each of said rings is about 2 to 6 inches and the ratio of area of perforations of said sheet to the remaining area of said sheet lies between about 1:5 and 5:1.
9. Apparatus in accordance with claim 5 in which the radial spacing of each of said rings is about 2 to 6 inches and the ratio of area of perforations of said sheet to the remaining area of said sheet is approximately 1:1.
References Cited by the Examiner UNITED STATES PATENTS 1,157,328 '10/1915 Scowden 61-54 2,475,888 7/1949 Hackett 6146 CHARLES E. OCONNELL, Primary Examiner. I. SHAPIRO, Assistant Examiner.-

Claims (1)

1. AN ASSEMBLAGE FOR MINIMIZING CURRENT-INDUCED TRANSVERSE VIBRATION IN A CYLINDER EXTENDING UPWARD FROM AND ATTACHED TO THE FLOOR OF A BODY OF WATER WHIHC COMPRISES AT LEAST ONE CYLINDRICAL PERFORATED SHEET SURROUNDING SAID CYLINDER, THE TOTAL AREA OF PERFORATED SHEET COVERING AT LEAST A MAJOR PART OF SAID CYLINDER, AND A PLURALITY OF AXIALLY SUBSTANTIALLY SEPARATED SUPPORTS RADIALLY ATTACHING SAID PERFORATED SHEET FIRMLY TO BUT SEPARATED FORM SAID CYLINDER, SAID SHEET AND SAID CYLTHE SLOE CONNECTION BETWEEN SAID SHEET AND SAID CYLINDER.
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Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3369511A (en) * 1964-05-04 1968-02-20 German John Gordon Marine floating structure
US3383869A (en) * 1965-01-18 1968-05-21 Canadian Patents Dev Marine piers
US3411321A (en) * 1966-03-01 1968-11-19 Chevron Res Large-diameter fluid bypass drill collar
US4470468A (en) * 1981-04-30 1984-09-11 Raymond International Builders, Inc. Offshore drilling of large diameter holes in rock formations
US4480944A (en) * 1981-04-30 1984-11-06 Raymond International Builders, Inc. Offshore drilling of large diameter holes in rock formations
US4505617A (en) * 1979-10-12 1985-03-19 National Research Development Corporation Stabilizing bluff structures against oscillation
US4632600A (en) * 1985-09-25 1986-12-30 Nippon Kokan Kabushiki Kaisha Movable fixed-type semi-submerged construction
US4909327A (en) * 1989-01-25 1990-03-20 Hydril Company Marine riser
US5410979A (en) * 1994-02-28 1995-05-02 Shell Oil Company Small fixed teardrop fairings for vortex induced vibration suppression
US5421413A (en) * 1993-11-02 1995-06-06 Shell Oil Company Flexible fairings to reduce vortex-induced vibrations
WO1995026294A1 (en) * 1994-03-28 1995-10-05 Shell Internationale Research Maatschappij B.V. Spar platform
US5549417A (en) * 1993-11-19 1996-08-27 Shell Oil Company Subsea pipeline shroud
US6039118A (en) * 1997-05-01 2000-03-21 Weatherford/Lamb, Inc. Wellbore tool movement control and method of controlling a wellbore tool
US6070670A (en) * 1997-05-01 2000-06-06 Weatherford/Lamb, Inc. Movement control system for wellbore apparatus and method of controlling a wellbore tool
US6685394B1 (en) * 2000-08-24 2004-02-03 Shell Oil Company Partial shroud with perforating for VIV suppression, and method of using
US6712559B2 (en) * 2000-01-24 2004-03-30 Saipem Sa Seafloor-surface linking device comprising a stabilizing element
FR2870287A1 (en) * 2004-05-13 2005-11-18 Inst Francais Du Petrole SYSTEM AND METHOD FOR LIMITING VORTEX INDUCED VIBRATIONS USING PERMEABLE COATING
US20080302537A1 (en) * 2007-06-07 2008-12-11 Mcmiles Barry James Dimpled riser floatation module
CN101949404A (en) * 2010-08-27 2011-01-19 中国计量学院 Subduction method for cylindrical wave current load
US20120067449A1 (en) * 2010-09-17 2012-03-22 Sulzer Pumpen Ag Apparatus and method for the vibration control of a rising pipe of a vertical pump
US8770894B1 (en) * 2011-12-27 2014-07-08 VIV Solutions LLC Helical strakes with molded in stand-offs
US20160097175A1 (en) * 2013-03-26 2016-04-07 Alton F. Parker Aggregate replacement
US10337649B1 (en) 2016-03-02 2019-07-02 VIV Solutions LLC Strake system
US10473131B1 (en) 2016-07-10 2019-11-12 VIV Solutions LLC Helical strakes and collar
US10545037B2 (en) 2016-08-01 2020-01-28 Saudi Arabian Oil Company Flow line insert with indentations
US10544635B2 (en) 2012-11-24 2020-01-28 VIV Solutions LLC Installation systems and methodology for helical strake fins
WO2020177825A1 (en) * 2019-03-01 2020-09-10 Vestas Wind Systems A/S A longitudinal structure for an offshore wind turbine
US10865910B1 (en) 2015-04-17 2020-12-15 VIV Solutions LLC Coupled fairing systems
US11261675B2 (en) 2018-01-16 2022-03-01 VIV Solutions LLC Methods for constructing a helical strake segment using one or more shell sections and fins

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1157328A (en) * 1912-05-04 1915-10-19 Edward W Scowden Method and apparatus for concreting piles.
US2475888A (en) * 1947-09-19 1949-07-12 Allen S Hackett Pier for offshore drilling rigs

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1157328A (en) * 1912-05-04 1915-10-19 Edward W Scowden Method and apparatus for concreting piles.
US2475888A (en) * 1947-09-19 1949-07-12 Allen S Hackett Pier for offshore drilling rigs

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3369511A (en) * 1964-05-04 1968-02-20 German John Gordon Marine floating structure
US3383869A (en) * 1965-01-18 1968-05-21 Canadian Patents Dev Marine piers
US3411321A (en) * 1966-03-01 1968-11-19 Chevron Res Large-diameter fluid bypass drill collar
US4505617A (en) * 1979-10-12 1985-03-19 National Research Development Corporation Stabilizing bluff structures against oscillation
US4470468A (en) * 1981-04-30 1984-09-11 Raymond International Builders, Inc. Offshore drilling of large diameter holes in rock formations
US4480944A (en) * 1981-04-30 1984-11-06 Raymond International Builders, Inc. Offshore drilling of large diameter holes in rock formations
US4632600A (en) * 1985-09-25 1986-12-30 Nippon Kokan Kabushiki Kaisha Movable fixed-type semi-submerged construction
US4909327A (en) * 1989-01-25 1990-03-20 Hydril Company Marine riser
US5421413A (en) * 1993-11-02 1995-06-06 Shell Oil Company Flexible fairings to reduce vortex-induced vibrations
US5549417A (en) * 1993-11-19 1996-08-27 Shell Oil Company Subsea pipeline shroud
US5410979A (en) * 1994-02-28 1995-05-02 Shell Oil Company Small fixed teardrop fairings for vortex induced vibration suppression
WO1995026294A1 (en) * 1994-03-28 1995-10-05 Shell Internationale Research Maatschappij B.V. Spar platform
GB2301648A (en) * 1994-03-28 1996-12-11 Shell Int Research Spar platform
GB2301648B (en) * 1994-03-28 1998-07-15 Shell Int Research Spar platform
US6039118A (en) * 1997-05-01 2000-03-21 Weatherford/Lamb, Inc. Wellbore tool movement control and method of controlling a wellbore tool
US6070670A (en) * 1997-05-01 2000-06-06 Weatherford/Lamb, Inc. Movement control system for wellbore apparatus and method of controlling a wellbore tool
US6712559B2 (en) * 2000-01-24 2004-03-30 Saipem Sa Seafloor-surface linking device comprising a stabilizing element
US6685394B1 (en) * 2000-08-24 2004-02-03 Shell Oil Company Partial shroud with perforating for VIV suppression, and method of using
FR2870287A1 (en) * 2004-05-13 2005-11-18 Inst Francais Du Petrole SYSTEM AND METHOD FOR LIMITING VORTEX INDUCED VIBRATIONS USING PERMEABLE COATING
US20080302537A1 (en) * 2007-06-07 2008-12-11 Mcmiles Barry James Dimpled riser floatation module
CN101949404A (en) * 2010-08-27 2011-01-19 中国计量学院 Subduction method for cylindrical wave current load
CN101949404B (en) * 2010-08-27 2012-11-21 中国计量学院 Subduction method for cylindrical wave current load
US20120067449A1 (en) * 2010-09-17 2012-03-22 Sulzer Pumpen Ag Apparatus and method for the vibration control of a rising pipe of a vertical pump
US9182001B2 (en) * 2010-09-17 2015-11-10 Sulzer Management Ag Apparatus and method for the vibration control of a rising pipe of a vertical pump
US8770894B1 (en) * 2011-12-27 2014-07-08 VIV Solutions LLC Helical strakes with molded in stand-offs
US10544635B2 (en) 2012-11-24 2020-01-28 VIV Solutions LLC Installation systems and methodology for helical strake fins
US11168525B2 (en) 2012-11-24 2021-11-09 VIV Solutions LLC Installation systems and methodology for helical strake fins
US20160097175A1 (en) * 2013-03-26 2016-04-07 Alton F. Parker Aggregate replacement
US10865910B1 (en) 2015-04-17 2020-12-15 VIV Solutions LLC Coupled fairing systems
US10337649B1 (en) 2016-03-02 2019-07-02 VIV Solutions LLC Strake system
US10473131B1 (en) 2016-07-10 2019-11-12 VIV Solutions LLC Helical strakes and collar
US10545037B2 (en) 2016-08-01 2020-01-28 Saudi Arabian Oil Company Flow line insert with indentations
US11261675B2 (en) 2018-01-16 2022-03-01 VIV Solutions LLC Methods for constructing a helical strake segment using one or more shell sections and fins
WO2020177825A1 (en) * 2019-03-01 2020-09-10 Vestas Wind Systems A/S A longitudinal structure for an offshore wind turbine

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