EP0088608A2 - Spannvorrichtung für Unterwasser-Steigrohr - Google Patents

Spannvorrichtung für Unterwasser-Steigrohr Download PDF

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Publication number
EP0088608A2
EP0088608A2 EP83301178A EP83301178A EP0088608A2 EP 0088608 A2 EP0088608 A2 EP 0088608A2 EP 83301178 A EP83301178 A EP 83301178A EP 83301178 A EP83301178 A EP 83301178A EP 0088608 A2 EP0088608 A2 EP 0088608A2
Authority
EP
European Patent Office
Prior art keywords
fluid
housing
piston
platform
hydraulic
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.)
Withdrawn
Application number
EP83301178A
Other languages
English (en)
French (fr)
Other versions
EP0088608A3 (de
Inventor
Thomas L. Elliston
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.)
Hydra Rig Inc
Original Assignee
Hydra Rig Inc
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 Hydra Rig Inc filed Critical Hydra Rig Inc
Publication of EP0088608A2 publication Critical patent/EP0088608A2/de
Publication of EP0088608A3 publication Critical patent/EP0088608A3/de
Withdrawn legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/12—Underwater drilling
    • E21B7/128—Underwater drilling from floating support with independent underwater anchored guide base
    • 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
    • E21B19/006—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 including heave compensators
    • 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
    • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
    • E21B19/09—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods specially adapted for drilling underwater formations from a floating support using heave compensators supporting the drill string

Definitions

  • the present invention relates generally to offshore production equipment and in particular to motion compensating apparatus for use on a floating platform for supporting a marine riser extending to the platform from the ocean floor.
  • the surface facility may be a tanker, a drill ship, a barge, a floating platform or a platform which is fixed to the ocean floor.
  • the riser must be supported at or near the water surface to prevent collapse. This is easily accomplished when the surface facility is a platform which is fixed to the ocean floor, but a more difficult problem is presented when the water depth is 30 great that the surface facility must be floating and hence is not stationary.
  • the invention may be practiced in combination with a floating platform or vessel of the type including a deck and having a well opening extending through the deck to provide access to the ocean beneath the platform.
  • the invention is embodied in motion compensating apparatus which includes displaceable means engageable between the deck of the vessel and the pipe string and operable for varying the distance between the vessel and the pipe string. Passive means are coupled to the displaceable means for operating the displaceable means to maintain a positive lifting force on the pipe string as the vessel is displaced vertically relative to the pipe string.
  • a resilient bearing member is disposed intermediate the vessel and the displaceable means with the resilient - bearing member being coupled in supporting engagement with the displaceable means for permitting angular displacement of the vessel relative to the pipe string in response to roll and pitch movements imparted to the vessel by wave action, while reacting both radial and axial loads.
  • the displaceable means comprises a linear hydraulic actuator which includes a cylindrical housing and a cylindrical piston having a first end or rod portion for attachment to the pipe string and a second end or head portion movably disposed in the housing and defining a fluid pressure chamber that changes in volume as the piston is displaced relative to the housing.
  • Accumulator means are connected in fluid communication with the pressure chamber for supplying hydraulic fluid to and for receiving hydraulic fluid from the pressure chamber in response to changes in its volume.
  • a source of compressed gas is connected in .fluid communication with the accumulator means for maintaining the hydraulic working fluid under pressure in the chamber as the platform rises and falls in response to tidal or wave movements of the ocean. Hydraulic fluid leakage past the primary piston and rod portion seals or packings is conducted through separate fluid lines to a low pressure fluid reservoir. Seal leakage is monitored by pressure switches and associated indicators connected to the leakage flow return lines.
  • the aforementioned resilient bearing member comprises an annular section of a substantially spherical laminated body of superposed layers-of an elastic material and of a relatively inelastic material for reacting radial and axial loads.
  • the resilient bearing member cooperates with the displaceable means to relieve axial stresses as well as decoupling bending moments.
  • the hydraulic actuator comprises a cylinder member or housing projecting through a central opening of the resilient bearing member and having an annular piston slidably disposed within the housing.
  • the annular volume intermediate the piston and housing defines a fluid pressure chamber which changes in volume with of the piston relative to the housing so that the piston and the riser. which is attached to the piston- is supported on an annular column of hydraulic fluid.
  • a further advantage of the abeventioned piston and cylinder arrangement is that drill tybing other production equipment may pass directly through the piston of the actuator and through the central opening of the resilient bearing member for direct connection to a diverter assembly or to the other production equipment without the interference associated with the complex cables and sheave arrangements of prior art tensioner systems.
  • the motion compensating apparatus of the present invention is indicated generally at 10 and is mounted on the deck 12 of a surface facility such as a floating oil well production platform indicated generally at 14.
  • the surface facility 14 has an opening 16, extending through the deck 12, to provide access to a production riser 18 extending thereto from the ocean floor 20.
  • the surface facility 14 is not limited to a floating platform but may be any such floating structure such as a drill ship, a tanker, or a barge.
  • the motion compensating apparatus will be described in connection with a floating platform.
  • the motion compensating apparatus 10 has utility for use in connection with drilling, servicing or production operations in which a marine riser is employed.
  • the deck 12 is supported above the surface 22 of the ocean by means of a plurality of downwardly extending controllably buoyant members or legs 24 which maintain the deck 12 at a desired elevation above the ocean surface 22.
  • the buoyant members 24 have sufficient tank capacity that the deck 12 can be raised or lowered as desired by use of a suitable control system for transporting the structure at minimum draft while in transit or for positioning it at a working draft over a production site.
  • the respective buoyant members 24 are further provided with an interconnecting truss structure 26 and other necessary understructure for stabilizing the platform.
  • a plurality of mooring lines and anchors may be provided for holding the platform over a production site 23. An example of such an arrangement is illustrated in U.S. Patent 3,983,706,
  • Basic wellhead equipment 30 is shown imbedded in the ocean floor 20 beneath the platform 14.
  • the production riser 18 expends from the wellhead equipment 30 to a conventional marine riser which is provided with flex joints and integral choke and kill usual christmas tree arrangement and control member. although not shown, may also be included in the wellhead equivalent 30 to control the production operation insofar as production fluid flow is
  • the lower and of the riser 18 is preferably pivotally allow for a limited amount of relative movement at the platform 14 is subjected to some lateral displacement from is desired location above the production site 28.
  • the production riser is typically comprises a numbe of elongated tubular members connected end to end and having sufficient diameter to enclose drill tubing and to conduct drilling mud.
  • a typical cross-section dimension of the riser is sixteen inches O.D. with one-half inch wall thickness.
  • prior art marine riser structures are subject to buckling forces induced by the heaving action of the floating platform 14 and are also subject to bending moments induced by the roll and pitch movements of the platform.
  • the harmful effects of the binding moment and buckling forces are intensified when the platfcrm 14 is laterally displaced excessively, and subjected to extreme vertical movement due to severe weather conditions on the water surface, for example.
  • the production riser 18 is supported of a column of pressurised hydraulic fluid whose volume varies in proportion to the displacement of the floating platform 14 relative to of the production riser 18.
  • the linear hydraulic actuator assembly 40 includes a cylinder member comprising a housing 44 having a first open end portion 46 suitably connected to an annular collar 48.
  • the collar 48 includes a cylindrical mounting flange portion which is bolted to a mounting weldment or ring 50 of the resilient bearing member 38.
  • the actuator assembly 40 includes a cylindrical annular piston member 52 which is concentrically disposed for extension and retraction within the housing 44.
  • the piston member 52 has a tubular piston rod portion 53 of relatively smaller diameter than the bore 54 of housing 44, thereby defining an annular pressure chamber 55 which changes in volume as the piston is displaced along the longitudinal axis of the housing.
  • the piston 52 includes a head 58 formed as a separate part which is threadedly connected to the upper end of the rod 53.
  • the piston head 58 includes primary seals or packings 56 and secondary packings 60 which are disposed in annular grooves formed in the head for sliding engagement with the cylinder bore 54.
  • a circumferential fluid leakage flow groove 57 is formed in the head 58 between the packings 56 and 60 and is in communication with an elongated passages 61 formed in the rod portion 53.
  • the passage 61 may be formed as a groove in the rod portion 53 which is closed by a sleeve 63 disposed over the outer diameter of the rod portion as shown.
  • the passage 61 is in communication with a flexible leakage flow return line 65 by way of a suitable fitting, as shown.
  • the piston rod portion 53 extends through an end cap 62 threadedly secured to the lower end 64 of the housing 44 and is in fluid sealing engagement with primary seals or packings 67 and secondary packings 66.
  • An annular groove 69 is formed in the inner bore wall of the cap 62 for conducting primary packing leakage fluid to a flexible return line 84.
  • the cylinder end cap 62 is threadedly connected to the lower end 64 of the housing 44 in sealing engagement therewith.
  • the piston 52 is displaceable along the longitudinal axis of the housing 44 and is slidable with respect to an elongated tubular sleeve 68 which is concentrically disposed within the piston and suitably secured to the annular collar 48. Also secured to the collar a corresponding connector diverter assembly (not shown). Connection to the opposite and of the motion compensating apparatus is provided by a connector portion 72 threadedy secured to the lower end of the piston red 53, The connector 72 is adapted to be connected to the user connector 32. The piston 52 and sleeve 68 cooperate to form an central passage extending through the apparatus 10 from the connector 70 to the connector 72.
  • the linear hydraulic actuator assembly 40 is supported from the deck 12 cf the floating platform 14 by the resilient bearing member 38 which is disposed in load supporting relation intermediate the deck 12 and the annular cellar assembly 48.
  • the bearing member 38 is an annular section of a substantially spherical laminated body of superposed layers of an elastic material 74 and of a relatively inelastic material 76 as can best be seen in Figure 3 of the drawing.
  • the laminated body is interposed between the mounting ring 50 and a supporting base member 51 disposed on the deck 12.
  • a central, somewhat conical shaped passage 15 is formed axially through the bearing member 38 for receiving the cellar 48 whereby the actuator 40 extends downwardly through the bearing member and the deck 12.
  • the purpose of the resilient bearing member 38 is to permit angular displacement of the floating platform 14 with respect to the hydraulic aactuator assembly 40 and the riser 18 and, in particular, to decouple the bending moment forces which would otherwise be imparted to the riser 18 as the platform 14 rolls and pitches in response tc wave movements of the sea.
  • the elastic layer 74 is preferably formed of an elastomer material such as rubber and the relatively inelastic layer 76 is preferably formed of a metal such as steel which in combination are capable of supporting a working compressive load in excess of the production riser weight.
  • the resilient bearing member 33 can react axial as well as radial loads, thereby cooperating' with the linear actuator assembly 40 to relieve stresses induced by heaving and lateral displacement of the platform 11.
  • the resilient bearing member 38 is designed, to support an axially applied, load of 350,000 pounds and is able tc withstand a full plus or minus seven degree rotation about a radial cycles.
  • the spring constant of the resilient bearing member 38 can be varied somewhat by increasing or decreasing the amount of resilient material in the layer 74.
  • the linear hydraulic actuator assembly 40 it is designed to exert a force of 350,000 pounds at a hydraulic fluid pressure of 2,200 psi.
  • the maximum recommended operating pressure is 2,650 psi.
  • the cylindrical housing member 44 and piston 52 are preferably constructed from a low carbon steel which is suitable for low temperature service.
  • the piston 52 preferably has a maximum stroke of 18 feet and is adapted to be driven at a rate of 0.6 feet per second.
  • the force, stroke and displacement rate may, of course, vary according to the requirements of a particular application.
  • the annular fluid pressure chamber 55 is supplied with hydraulic fluid by a pump 92 and an accumulator assembly 42 through a flexible supply line or hose 80.
  • High pressure working fluid is preferably conveyed through multiple runs of hydraulic hoses 80 to provide redundancy, although only one hose is shown in the drawing figures.
  • the hoses 80 are preferably provided with back to back flow rate limiting or velocity fuse type check valves 78 and 79 as shown schematically in Figure 2.
  • the valves 78 and 79 are operable to close in response to a break in the line 80 to prevent fluid from escaping from the chamber 55 or from being totally discharged from the supply circuit including the pump 92 and accumulator assembly 42.
  • a manually operable valve 81 is connected across check valve 78 for repressurizing a repaired or replaced hose so that the valve 78 may be reopened without depressurizing the fluid supply circuit.
  • High pressure hydraulic fluid is conducted through the line 80 into an inlet passage 82 in end cap 62 which leads to the annular fluid pressure chamber 55 by way of an annular chamber 83 and fluid passages 85.
  • the pneumo-hydraulic accumulator assembly 42 is suitably charged to place the riser 18 under a predetermined level of tension.
  • the pneumo-hydraulic accumulator assembly 42 includes a plurality of hydraulic pressure tanks 88 which are adapted to receive a variable volume of hydraulic working fluid and to be charged with air or an inert gas from a The air or gas pressure is regulate to a substantially constant valve and may also be provided by of compressed air or gas bottles (not shown).
  • the lined hydraulic actuator assembly 40 is charged with hydraulic fluid to place a predetermined level of tensi for example 250 kips, on the riser 18.
  • tensi for example 250 kips
  • the housing 18 in displaced downwardly with respect to the piston 52.
  • the volume of the pressure chamber 55 increases proportionately and the pressure of the working fluid contained therein tends to diminish but the check valves 78 and 79, which are suitably blased to be normally open, admit high pressure hydraulic wherein fluid from the accumulator assembly 42 into the inlet passage of by way of line 80.
  • the pressure chamber 55 is maintained filled with high pressure hydraulic working fluid at a substantially constant pressure whereby the piston 52 and production riser 18 are supported by a column of hydraulic fluid which increases and decreases in its longitudinal extent as the housing member 44 is displaced by the heaving action of the fleating platform.
  • the working fluid contained within the pressure chamber 55 is discharged back through the line 80 by way of the normally open valves 78 and 79 into the accumulator tanks 88.
  • the hydraulic fluid supply circuit further includes a reservoir 86 connected to the inlet port of the pump 92 for supplying makeup fluid through a check valve 94 to the system including the accumulator tanks 88.
  • the reservoir 83 includes a float switch assembly 96 connected to a source of pressure air for operating the pump 92 When a float 99 senses a predetermined level in the reservoir.
  • the leakage flow return lines 65 and 84 are connected to the reservoir by way of the inlet line for pump 92, as shown.
  • the leakage flow return lines 65 and 84 are also connected to repsective pressure switches 95 and 97 which, in turn, are operable to energize respective indicators 103 and 101 if the fluid flow through the lines 65 and/or to above exceed a predetermined rate. Accordingly, imminent failure of the primary packings 56 and 67 may be detected and corrective action taken before the actuator assembly 40 suffers a total loss of fluid from the chamber 55.
  • Dynamic operation of the hydraulic actuator assembly 40 is illustrated in Figure 4 of the drawing, where the force variation exerted by the actuator is shown graphically as a function of the ship position with respect to an arbitrary reference level which corresponds to a predetermined tension level.
  • the force variation exerted by the actuator 40 for a 92 cubic foot accumulator is shown by the graph 100 and the corresponding force variation for a 183 cubic feet accumulator is shown by the graph 102.
  • These graphs indicate that as the capacity of the accumulator system increases, proportionately less cylinder force variation is experienced for a given change in platform position.
  • the present invention provides a versatile and robust motion compensating apparatus for maintaining a substantially constant tension load on a production riser while substantially reducing the bending stresses induced in the riser by the roll and pitch of the platform to which it is attached.

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  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)
  • Agricultural Chemicals And Associated Chemicals (AREA)
EP83301178A 1982-03-05 1983-03-04 Spannvorrichtung für Unterwasser-Steigrohr Withdrawn EP0088608A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US35492382A 1982-03-05 1982-03-05
US354923 1982-03-05

Publications (2)

Publication Number Publication Date
EP0088608A2 true EP0088608A2 (de) 1983-09-14
EP0088608A3 EP0088608A3 (de) 1984-07-11

Family

ID=23395470

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83301178A Withdrawn EP0088608A3 (de) 1982-03-05 1983-03-04 Spannvorrichtung für Unterwasser-Steigrohr

Country Status (6)

Country Link
EP (1) EP0088608A3 (de)
JP (1) JPS58173289A (de)
CA (1) CA1205740A (de)
DK (1) DK109383A (de)
FI (1) FI830746L (de)
NO (1) NO830764L (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2584449A1 (fr) * 1985-01-31 1987-01-09 Vetco Offshore Ind Inc Ensemble superieur pour tube prolongateur marin, joint coulissant auto-tensionneur, joint de palier de rotation, conduit tubulaire, navire et procede les utilisant
WO2010090531A1 (en) * 2009-02-09 2010-08-12 Fmc Kongsberg Subsea As Trigger joint
US7988385B2 (en) 2007-01-08 2011-08-02 Vetro Gray Inc. Ram style tensioner with fixed conductor and floating frame
US8496409B2 (en) 2011-02-11 2013-07-30 Vetco Gray Inc. Marine riser tensioner
GB2533783A (en) * 2014-12-29 2016-07-06 Cameron Int Corp Subsea support
US10174566B2 (en) 2016-03-02 2019-01-08 Vetco Gray, LLC Inverted pull-up riser tensioner
CN113833418A (zh) * 2021-10-28 2021-12-24 上海外高桥造船海洋工程项目管理有限公司 浮式钻井平台井下工具绞车波浪补偿装置
US11598161B2 (en) * 2018-01-17 2023-03-07 Noble Drilling A/S Offshore drilling rig assembly and method

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3643751A (en) * 1969-12-15 1972-02-22 Charles D Crickmer Hydrostatic riser pipe tensioner
US3739844A (en) * 1971-04-28 1973-06-19 Shell Oil Co Apparatus for carrying out underwater wellhead operations
US4004532A (en) * 1975-05-05 1977-01-25 Western Gear Corporation Riser tension system for floating platform
US4200054A (en) * 1976-12-10 1980-04-29 Elliston Thomas L Stabilized hoist rig for deep ocean mining vessel
US4359095A (en) * 1980-08-04 1982-11-16 Conoco Inc. Well support system
US4367981A (en) * 1981-06-29 1983-01-11 Combustion Engineering, Inc. Fluid pressure-tensioned slip joint for drilling riser

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4712620A (en) * 1985-01-31 1987-12-15 Vetco Gray Inc. Upper marine riser package
FR2584449A1 (fr) * 1985-01-31 1987-01-09 Vetco Offshore Ind Inc Ensemble superieur pour tube prolongateur marin, joint coulissant auto-tensionneur, joint de palier de rotation, conduit tubulaire, navire et procede les utilisant
US8215872B2 (en) 2007-01-08 2012-07-10 Vetco Gray Inc. Ram style tensioner with fixed conductor and floating frame
US7988385B2 (en) 2007-01-08 2011-08-02 Vetro Gray Inc. Ram style tensioner with fixed conductor and floating frame
US8011858B2 (en) 2007-01-08 2011-09-06 Vetco Gray Inc. Ram style tensioner with fixed conductor and floating frame
US8123438B2 (en) 2007-01-08 2012-02-28 Vetco Gray Inc. Ram style tensioner
US8875794B2 (en) 2009-02-09 2014-11-04 Fmc Kongsberg Subsea As Trigger joint
WO2010090531A1 (en) * 2009-02-09 2010-08-12 Fmc Kongsberg Subsea As Trigger joint
EP2863005A1 (de) * 2009-02-09 2015-04-22 FMC Kongsberg Subsea AS Auslöserverbindung
US8496409B2 (en) 2011-02-11 2013-07-30 Vetco Gray Inc. Marine riser tensioner
GB2533783A (en) * 2014-12-29 2016-07-06 Cameron Int Corp Subsea support
US9845654B2 (en) 2014-12-29 2017-12-19 Cameron International Corporation Subsea support
GB2533783B (en) * 2014-12-29 2019-06-05 Cameron Tech Ltd Subsea support
US10174566B2 (en) 2016-03-02 2019-01-08 Vetco Gray, LLC Inverted pull-up riser tensioner
US11598161B2 (en) * 2018-01-17 2023-03-07 Noble Drilling A/S Offshore drilling rig assembly and method
CN113833418A (zh) * 2021-10-28 2021-12-24 上海外高桥造船海洋工程项目管理有限公司 浮式钻井平台井下工具绞车波浪补偿装置

Also Published As

Publication number Publication date
FI830746A7 (fi) 1983-09-06
FI830746L (fi) 1983-09-06
DK109383D0 (da) 1983-03-04
NO830764L (no) 1983-09-06
DK109383A (da) 1983-09-06
EP0088608A3 (de) 1984-07-11
CA1205740A (en) 1986-06-10
FI830746A0 (fi) 1983-03-04
JPS58173289A (ja) 1983-10-12

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Inventor name: ELLISTON, THOMAS L.