WO2006048669A1 - Améliorations des béliers hydrauliques ou les concernant - Google Patents

Améliorations des béliers hydrauliques ou les concernant

Info

Publication number
WO2006048669A1
WO2006048669A1 PCT/GB2005/004272 GB2005004272W WO2006048669A1 WO 2006048669 A1 WO2006048669 A1 WO 2006048669A1 GB 2005004272 W GB2005004272 W GB 2005004272W WO 2006048669 A1 WO2006048669 A1 WO 2006048669A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
piston
hydraulic
supplementary force
ram
Prior art date
Application number
PCT/GB2005/004272
Other languages
English (en)
Inventor
Anthony Stephen Bamford
Original Assignee
Hydril Company Lp
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
Priority claimed from GB0424401A external-priority patent/GB0424401D0/en
Priority claimed from GB0512995A external-priority patent/GB0512995D0/en
Application filed by Hydril Company Lp filed Critical Hydril Company Lp
Priority to CN2005800442256A priority Critical patent/CN101128645B/zh
Priority to AT05804239T priority patent/ATE469287T1/de
Priority to US11/718,705 priority patent/US20090127482A1/en
Priority to EP05804239A priority patent/EP1809858B1/fr
Priority to BRPI0517055-9A priority patent/BRPI0517055A2/pt
Priority to DE602005021532T priority patent/DE602005021532D1/de
Publication of WO2006048669A1 publication Critical patent/WO2006048669A1/fr
Priority to NO20072782A priority patent/NO20072782L/no

Links

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
    • E21B33/00—Sealing or packing boreholes or wells
    • E21B33/02—Surface sealing or packing
    • E21B33/03—Well heads; Setting-up thereof
    • E21B33/06—Blow-out preventers, i.e. apparatus closing around a drill pipe, e.g. annular blow-out preventers
    • E21B33/061—Ram-type blow-out preventers, e.g. with pivoting rams
    • E21B33/062—Ram-type blow-out preventers, e.g. with pivoting rams with sliding rams
    • E21B33/063—Ram-type blow-out preventers, e.g. with pivoting rams with sliding rams for shearing drill pipes

Definitions

  • the present invention relates to hydraulic rams and in particular, though not exclusively, to an actuator for delivering a supplementary force to the piston of a shear ram in a blowout preventer.
  • Each ram typically includes a piston which is driven forward by a hydraulic force.
  • hydraulic rams are located in blowout preventers.
  • shear rams In an emergency procedure when a well is required to be shut in to prevent a blow-out whilst drilling, two opposing rams are brought together to seal the well bore.
  • shear rams In an emergency procedure when a well is required to be shut in to prevent a blow-out whilst drilling, two opposing rams are brought together to seal the well bore.
  • shear rams typically referred to as shear rams as they include a shear blade on the front face of the piston used to sever drill pipe or casing in the wellbore.
  • the opposing shear blades When the shear rams are actuated by a hydraulic force, the opposing shear blades are brought together to interact, with the blades being driven by the hydraulic pistons.
  • the shear blades first crush and then shear the drill string, casing or other tubular in the well.
  • the tubulars As wells are drilled to greater depths the tubulars are of increasing diameter, wall thickness and increased steel grades. Consequently shearing the tubular in the well requires more hydraulic force. This calls for a larger actuator piston, hence larger operating fluid volumes and higher closure pressures.
  • a supplementary force actuator for use on a hydraulic ram, the actuator comprising: an actuator body including fixation means to connect the body to a hydraulic ram; first and second chambers located in the body, the chambers isolated from each other by an actuator piston; a rod adapted to be connected to an operating piston of the hydraulic ram, pass through the first chamber and the actuator piston, and extend into at least a portion of the second chamber; the actuator piston being releasably engageable to the rod by gripping means; and wherein the hydraulic ram is operated by a force from movement of the operating piston and by a supplementary force from movement of the actuator piston.
  • the actuator piston can be released to provide a supplementary force on the ram.
  • the actuator includes a release mechanism to operate the actuator piston.
  • the actuator piston can be released at or near the end of the stroke of the operating piston and thereby provide the supplementary force where it is most required.
  • a separation element is located between the hydraulic ram and the body. More preferably one or more seals are arranged on the separation element to act upon the rod and prevent the release of hydraulic fluid from the body into a hydraulic fluid chamber of the hydraulic ram.
  • the actuator includes energy storage means arranged to provide a force to act upon the actuator piston.
  • the energy storage means is a mechanical means.
  • the mechanical means is one or more springs held in compression.
  • the mechanical means is a plurality of Bellville springs as are known in the art.
  • the energy storage means is a hydraulic means.
  • the hydraulic means is hydraulic fluid held under pressure.
  • the actuator includes resetting means to move the actuator piston back to its original operating position.
  • the actuator includes ram setting means to move the operating piston back to its original position. In this way the hydraulic ram may be reset.
  • the gripping means comprises a ball-gripping device and may comprise a device of the type disclosed in US Patent No. 2,062,628 (Yannetta) or US Patent No. 2,182,797, the disclosures of which are incorporated herein by way of reference.
  • the ball gripping device may comprise a plurality of balls mounted in a ball mounting element, which may be a ball cage or sleeve, having a plurality of apertures, each aperture associated with a corresponding ball.
  • the actuator in particular, the actuator piston may be adapted to urge the balls into engagement with the rod, to grip the rod. This may facilitate application of the supplementary force.
  • the actuator piston may define one or more cam surface or ramp for urging one or more of the balls radially into engagement with the rod.
  • the ball gripping device may be adapted to grip the rod during movement of the actuator piston in a first direction and to release the rod during movement in a second, opposite direction.
  • the device may comprise a ball release mechanism for permitting relative movement between the ball mounting element and the actuator piston.
  • the ball release mechanism may comprise a shoulder or the like which, during return movement of the actuator piston, may be adapted to abut the ball mounting element, to exert a force on the ball element to disengage the balls from the rod.
  • the ball mounting element may comprise a flange or spring plate, and at least one spring may be provided between the flange and the actuator piston. The spring may facilitate operation of the actuator and may prevent the actuator piston from impacting other components of the actuator following disengagement of the balls from the rod. Following release, the rod may move independently of the actuator piston back to a start position.
  • a method of operating a hydraulic ram comprising the steps; (a) releasing a first piston to act on a ram; (b) using the movement of the first piston to trigger a release mechanism; (c) releasing a second piston on operation of the release mechanism, to act upon the ram.
  • the method includes the step of compressing/pressurising hydraulic fluid behind the first piston which is then used to operate the first piston.
  • the method includes the step of releasably engaging the second piston to the first piston, so that the second piston is stationary when the first piston operates and the second piston also moves the first piston upon operation of the second piston.
  • the release mechanism is triggered at or near the end of the stroke of the first piston.
  • the method includes the step of resetting the hydraulic ram by moving the first and second pistons back to their original operating positions.
  • a blow out preventer for use in oil well drilling, the blow out preventer comprising: a pair of opposing hydraulic rams, each ram having a shear blade on a leading face; at least one supplementary force actuator according to the first aspect located on at least one of the hydraulic rams. 5 004272
  • a supplementary, force actuator is arranged on each of the hydraulic rams.
  • the rams will initially crush the tubular by action of the operating piston and then the tubular is sheared by operation of the actuator piston.
  • the energy storage means is a hydraulic energy store.
  • the blow out preventer can be kept within the dimensions of 5.7m x 5.7m for deployment through a moon pool .
  • Figure 1 is a schematic cross-sectional view of a hydraulic ram including a supplementary force actuator according to a first embodiment of the present invention, shown in a first operating position;
  • Figure 2 is an illustration of the release mechanism of the supplementary force actuator of Figure 1;
  • Figure 3 is a schematic cross-sectional view of the hydraulic ram including a supplementary force actuator of Figure 1, shown in a second operating position;
  • Figure 4 is a schematic cross-sectional view of the hydraulic ram including a supplementary force actuator of Figure 1, shown in a third operating position;
  • Figure 5 is a schematic cross-sectional view of a hydraulic ram including a supplementary force actuator according to a second embodiment of the present invention
  • Figure 6 is a schematic cross-sectional view of a hydraulic ram including a supplementary force actuator according to a third embodiment of the present invention.
  • Figures 7 and 8 are schematic cross-sectional views of part of a supplementary force actuator according to a further embodiment of the present invention, shown in second and third operating positions, respectively.
  • FIG. 1 shows a hydraulic ram, generally indicated by reference numeral 10, upon which is mounted a supplementary force actuator 12, according to a first embodiment of the present invention.
  • the hydraulic ram 10 is part of a blow out preventer 14.
  • Blow out preventer 14 comprises a body 16 having an axial bore 18 therethrough and at least one transverse port 20 accessing the bore 18.
  • Mounted at the transverse port 20 is the hydraulic ram 10.
  • the ram 10 comprises cylindrical shaft 22 having a piston 24 at a first end and a shear blade 26 mounted on an opposing end. The piston is operated by the pressurisation of hydraulic fluid behind the piston 24, in a ram chamber 36.
  • a drill pipe or tubular 28 is located through the bore 18.
  • the piston 24 is actuated to force the shaft 22 towards the bore 18.
  • two opposing hydraulic rams 10 are mounted across the bore so that the shear blades 26 interact. The shear blades first crush and then shear the tubular 28. The shear blades are arranged such that when they meet, the bore 18 is sealed and blow out is prevented.
  • the supplementary force actuator 12 is connected to an existing hydraulic ram 10. In this way the actuator 12 may be retrofitted to existing ram systems. An end cap can be removed from the existing ram and the body 30 is then located at this position 32. Body 30 is fixed to the ram, being secured by bolts 34 or other accepted fixation means. A separation plate 40 isolates the ram chamber 36 from the inside of the body 30.
  • Body 30 comprises first and second chambers, 38,37 respectively.
  • these chambers 37,38 have a greater diameter than chamber 36.
  • the chambers are divided by a piston 46.
  • the piston 24 of the conventional ram 10 is fitted with an additional connecting rod 42 that extend through seals 44 on the separation plate 40. Said seals 44 contain the full hydraulic pressure that is applied to close the ram 10.
  • the connecting rod 42 travels through the first chamber 38 and through the centre of the piston 46.
  • a gripping device 48 mounted within the piston 46.
  • the gripping device 48 is a ball gripping device of the type described in US 2,062,628, incorporated herein by reference.
  • the ball-gripping device 48 is described hereinafter with reference to Figures 5 and 6. Essentially the device 48 selectively grips the rod 42 such that the piston 46 and rod 42 move together. It will be understood that gripping devices of various different types may be utilised.
  • a stack of Bellville springs 50 Mounted behind the piston 46 in the second chamber 37 are a stack of Bellville springs 50. These springs 50 can store enormous amounts of energy but the applied force drops off rapidly over a few centimetres of travel. Chamber 38 is arranged to provide only a small distance of possible travel for the piston 46. The purpose of the piston 46 is to compress and retain the Bellville springs 50 arranged in radial fashion around the connecting rod 42. Pressure applied to chamber 38 acting on piston 46 compresses the Bellville springs 50.
  • FIG. 1 is a schematic diagram of a release mechanism, generally indicated by reference numeral 56.
  • the choice of linkage depends on the provision made for safety of personnel in the release of the stored energy.
  • a circular plate 54 as illustrated in figure 2 has obvious safety advantages.
  • a spring loaded linkage arm 58 rotates the "half pin” 52 once the piston 46 has compressed Bellville springs 50.
  • the load is supported on the flattened section of the rotating "half pin” 52 as indicated by the arrow in figure 2.
  • the linkage arm 58 is attached to an adjustable collar 60 fixed to the connecting rod 42 so that when it has moved by a pre-adjusted length, the spring operates the rotation of the circular plate 54 and hence the rotating "half pin” .
  • the Bellville Springs 50 By changing the position of the adjustable collar 60, the operator can set at what point in the shear ram closure, the Bellville Springs 50 will discharge their load. This feature would be useful where the properties of steel and other materials to be sheared are changed. Also affecting the optimum discharge point would be the geometry of the pipe or pipes to be sheared. For example pipe in pipe shearing may require an earlier discharge point than single pipe configurations.
  • the chambers 36,38 are filled with hydraulic fluid so as to move the pistons 24,46 away from the bore 18.
  • piston 24 moves it retracts the shear blade 26 of the ram 10.
  • the linkage arm 58 also moves rotating the plate 54 as described above.
  • the piston 46 moves independently of the rod 42 to compress the Bellville springs 50 under the force of the hydraulic fluid supplied to the chambers 36,38.
  • This operating position is as illustrated in Figure 1 and the ram 10 and actuator 12 can remain fixed in this position until movement of the ram is required.
  • the operation of the shear ram is illustrated in figure 3.
  • the operator functions the controls of the hydraulic piston 24 and shaft 22 as would occur on a conventional ram 10.
  • the piston 24 is urged forward to advance the shaft 22, so that the shear blades 26 start to crush the pipe 28 to be sheared.
  • the linkage arm 58 causes the circular plate 54 and "half pin” 42 to rotate and release the stored energy in the Bellville springs 50. This is because the "half pin" cutaway section is flush with the circular section of the actuator wall.
  • the piston 46 moves towards the bore 18.
  • FIG. 4 shows the configuration when the force of the Bellville Springs 50 has been expended.
  • a second ram, referenced 10a, is illustrated to show that the blades 26,26a interact to seal the bore 18.
  • a control system directs hydraulic fluid to chamber 36 on the front face of piston 24. This immediately starts to compress the Bellville springs 50.
  • the piston 46 with the attached female ball-gripping device 48 makes contact with actuator sleeve 62, the compression of the Bellville springs 50 is complete.
  • Bellville springs 50 could be replaced by an ordinary coil spring to provide an alternative embodiment.
  • Other types of ball gripping devices may be employed, such as those of the type disclosed in US Patent No 2,182,797 to Dillon, the disclosure of which is incorporated herein by way of reference.
  • Further embodiments could use alternative mechanical gripping devices instead of the ball-gripper system 48, for example, based on tapered slips.
  • Other spring retaining mechanisms could be used based for example on the ball-gripper mechanisms.
  • the automated mechanical linkage of the release mechanism 56 could be changed in subsequent embodiments, for example instead of a conventional spring a small closed hydraulic piston could be used.
  • Another embodiment would be to use a proximity switch or some electronic method of pre-determining the point at which the stored mechanical energy in the Bellville spring 58 is discharged.
  • the release mechanism 56 would be operated by solenoid.
  • Yet another embodiment would provide for a release mechanism based on a pre-set value of hydraulic pressure. Once this hydraulic pressure threshold is reached communication to the release mechanism 56 could be via a pilot hydraulic line, a solenoid or even a pneumatic line in the event the mechanism is deployed at atmospheric pressure.
  • FIG. 5 of the drawings illustrates a hydraulic ram, generally indicated by reference numeral 110, including a supplementary force actuator 112 according to a second embodiment of the present invention.
  • reference numeral 110 a hydraulic ram
  • supplementary force actuator 112 according to a second embodiment of the present invention.
  • Like parts to those of Figures 1 to 4 have been given the same reference numeral with the addition of 100.
  • the actuator 12 in the first embodiment had a design length of 1.761 metres.
  • the overall design length was 7.61 metres.
  • the BOP stack must be lowered through a moon pool for sub sea deployment, this size is unacceptable as many moon-pools have dimensions of 6.5 metres by 6.5 metres.
  • the length of the actuator can be reduced by re-designing the Bellville springs 50. So instead of a single stack, there are multiple stacks, typically four in number arranged radially around the rod 42. However for some BOP's the diameter of the resulting actuator 12 impinged on the space of the next ram which was located in series down the well bore.
  • the overall length of the actuator 12 is 1.18 metres which results in a BOP stack with an overall design length of 5.966 metres, just outside the limit set by certain oil companies of 5.7 metres.
  • the second embodiment seeks to achieve the same objectives i.e. to reduce the volume of accumulator bottles required for shearing pipe, especially in deepwater, whilst maintaining or enhancing the available stored shearing force, but with a reduced overall length.
  • the ram 110 of Figure 5 has the same arrangement as the ram 10 of Figures 1 to 4.
  • the actuator 112 is similar except that the first chamber 138 is narrower than the second chamber 137 so that the body 130 increases in diameter at one end, typically into an 18" cylinder.
  • the actuator piston 146 is located in the second chamber 137.
  • the piston 146 is connected directly to the ball-gripping device 148, which is of the type described US 2,062,628.
  • the ball gripping device 148 comprises a surface of tapered sections forming cam surfaces or ramps 139 in each of which a ball 141 can travel on the tapered edge.
  • a ball mounting element in the form of a ball cage 143 is biased, via springs for example, to constrain the balls 141 within the tapered sections 139.
  • the balls 141 thus travel in the tapers 139, constrained by the ball cage 143.
  • the ball cage 143 is moved so that the balls can retract into pockets within the tapered sections 141.
  • it is contact between the cage 143 and the actuator sleeve 62 which causes movement of the cage 143 to retract the balls 141.
  • the purpose of the actuator piston 146 is to apply a second stage force, once the primary piston 124 has had fluid pressure applied to it and has moved sufficiently to deform and crush the pipe in the well-bore 18.
  • the release of the actuator piston 146 is controlled and actuated by means of a pressure signal from the hydraulic fluid applied to the primary piston 124 or from a position indicator/sensor measuring the desired length of stroke.
  • the inlet valve 164 is opened to a separate accumulator bank containing operating fluid, whose pressure is normally stored at 200 bar. Movement of the piston 146 causes the ball-gripping device 148 to engage the rod 142 and apply the full force of the pressure applied over the cross sectional area of the actuator piston 146. At the same time full operating pressure is applied to the piston 124 in the first chamber 136. The shear blades 126 will thus engage and shear the tubular 128, sealing the bore 118 and shutting in the well.
  • the small volume of fluid required to operate the actuator piston 146 in chamber 137 means that accumulator pressure will not fall as rapidly as would be the case with a larger volume piston.
  • an electric pump operating from a subsea reservoir may be used to ensure maximum applied pressure to the inlet 164 at all times.
  • the well may be opened by applying a small pressure at port 170 in the second chamber 138.
  • the seal 172 causes the ball-gripper device 148 to move to the right and allows the balls to be retracted and hence the well may be opened by applying pressure to the front face of piston 124.
  • the length of stroke of the actuator piston 146 is small, generally about 50mm, which is enough to apply maximum force at the point it is needed to sever the pipe 128 in the well-bore 118. It is expected that the actuator piston 146 and the chamber 141 it occupies will be typically about 270 mm in length and the ball-gripping device 148 about 250mm in length. The total length of the actuator 112 should be about 520 mm in length.
  • an accumulator 174 of a given volume is filled with nitrogen and kept as close as possible to atmospheric pressure.
  • the accumulator 174 is connected to the inlet 166 by a valve 176.
  • the accumulator lines and valve 176 will be rated for a collapse pressure of at least 300 bar.
  • the valve 176 is opened. This allows the fluid on the return side of the actuator piston 146 to vent to the accumulator 174.
  • seawater pressure alone may be sufficient to drive the actuator piston 146 to the left and shear the pipe 128.
  • accumulator pressure may be required at inlet 166 to shear the pipe 128.
  • FIG 7 there is shown a schematic cross-sectional view of part of a supplementary force actuator according to a further embodiment of the present invention, the actuator indicated generally by reference numeral 212.
  • the actuator 212 Like components of the actuator 212 with the actuator 12 of Figures 1 to 4, and with the actuator 112 of Figures 5 and 6 share the same reference numerals incremented by 200 and 100, respectively.
  • the actuator 212 is essentially of similar structure to the actuator 112, and is for use with a ram such as the ram 110. Accordingly, only the substantial differences between the actuator 212 and the actuator 112 of Figure 5 will be described herein in detail.
  • the actuator 212 is shown in a second operating position similar to that of the actuator 12 shown in Figure 3. In this position, an actuator piston 246 is retracted.
  • the actuator 212 includes a ball gripping device 248 of similar structure and operation to the device 148 of Figure 5, except that the device 248 additionally includes a release mechanism 78 which facilitates release of balls 141 from engagement with a rod 242.
  • the release mechanism 78 comprises a flange or spring plate 80 provided on a ball cage 243 and a number of springs 82 provided between the flange 80 and a shoulder 84 on the actuating piston 246.
  • the release mechanism 78 additionally includes a shoulder 86 formed on or in a body housing the actuator piston 246.
  • the actuator 212 is operated in a similar fashion to the actuator 112, and is shown in Figure 8 following movement of the actuator piston 246 towards a bore of a blow out preventer such as the BOP 14 shown in Figure 1. As with the actuator 112, this movement causes the balls 141 to be urged radially inwardly to grip the rod 242.
  • the actuator piston 246, carrying the rod 242 is moved back towards the position of Figure 7. During this movement, the ball cage flange 80 comes into contact with the shoulder 86 before the actuator piston 246 has fully returned to its start position.
  • the principal advantage of the present invention is that it provides a supplementary force actuator for use with a hydraulic ram to augment the force supplied by the hydraulic ram without requiring large volumes of hydraulic fluids.
  • a further advantage of the present invention is that it provides a supplementary force actuator for use with a hydraulic ram in a two stage application of force to shear an object such as a pipe.
  • An initial force is delivered by the standard hydraulic ram and a secondary force is discharged at a preset point on the stroke to more or less double the applied force.
  • a yet further advantage of the present invention is that it provides a supplementary force actuator for use with a hydraulic ram wherein the preset point where the supplementary force is discharged is adjustable to optimise the pipe severance load at the point of hydraulic stroke where the discharged mechanical force is most effective.

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Actuator (AREA)
  • Formation And Processing Of Food Products (AREA)

Abstract

La présente invention décrit un actionneur pour fournir une force supplémentaire au piston d'un bélier à cisailler dans un obturateur (BOP) et un BOP correspondant. Dans un mode de réalisation, on décrit un actionneur de force supplémentaire (12) à utiliser sur un bélier hydraulique (10), l'actionneur comprenant: un corps d'actionneur (30) raccordé au bélier hydraulique; une première et une seconde chambres (38, 36) situées dans le corps, les chambres étant séparées l'une de l'autre par un piston d'actionneur (46); une tige (42) reliée à un piston (24) de mise en œuvre du bélier hydraulique, qui traverse la première chambre et le piston d'actionneur et pénètre au moins dans une partie de la seconde chambre; le piston d'actionneur pouvant s'engager de façon réversible sur la tige par des moyens d'accrochage (48); et le bélier hydraulique étant mis en œuvre par une force provenant du mouvement du piston de mise en œuvre et par une force supplémentaire provenant du mouvement du piston d'actionneur.
PCT/GB2005/004272 2004-11-04 2005-11-04 Améliorations des béliers hydrauliques ou les concernant WO2006048669A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
CN2005800442256A CN101128645B (zh) 2004-11-04 2005-11-04 关于液压防喷器闸板的改进
AT05804239T ATE469287T1 (de) 2004-11-04 2005-11-04 Verbesserungen in bezug auf hydraulisch betätigte kolben-strangpressen
US11/718,705 US20090127482A1 (en) 2004-11-04 2005-11-04 Hydraulic rams
EP05804239A EP1809858B1 (fr) 2004-11-04 2005-11-04 Améliorations des béliers hydrauliques ou les concernant
BRPI0517055-9A BRPI0517055A2 (pt) 2004-11-04 2005-11-04 aperfeiçoamentos em ou relacionados a arìete
DE602005021532T DE602005021532D1 (de) 2004-11-04 2005-11-04 Kolben-strangpressen
NO20072782A NO20072782L (no) 2004-11-04 2007-05-31 Forbedringer ved og knyttet til hydrauliske avstengere

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB0424401.8 2004-11-04
GB0424401A GB0424401D0 (en) 2004-11-04 2004-11-04 HM blowout preventers
GB0512995.2 2005-06-25
GB0512995A GB0512995D0 (en) 2005-06-25 2005-06-25 Improvements in or relating to hydraulic rams

Publications (1)

Publication Number Publication Date
WO2006048669A1 true WO2006048669A1 (fr) 2006-05-11

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2005/004272 WO2006048669A1 (fr) 2004-11-04 2005-11-04 Améliorations des béliers hydrauliques ou les concernant

Country Status (8)

Country Link
US (1) US20090127482A1 (fr)
EP (1) EP1809858B1 (fr)
AT (1) ATE469287T1 (fr)
BR (1) BRPI0517055A2 (fr)
DE (1) DE602005021532D1 (fr)
NO (1) NO20072782L (fr)
RU (1) RU2370627C2 (fr)
WO (1) WO2006048669A1 (fr)

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EP2199535A1 (fr) * 2008-12-18 2010-06-23 Hydril USA Manufacturing LLC Dispositif et procédé de génération de force sous-marine
GB2484741A (en) * 2010-10-22 2012-04-25 Weatherford Lamb Restricting fluid flow in a bore with an actuator isolated from bore pressure
US8220773B2 (en) 2008-12-18 2012-07-17 Hydril Usa Manufacturing Llc Rechargeable subsea force generating device and method
WO2016064582A1 (fr) * 2014-10-20 2016-04-28 Worldwide Oilfield Machine, Inc. Système de coupage compact et procédé correspondant
US10655421B2 (en) 2014-10-20 2020-05-19 Worldwide Oilfield Machine, Inc. Compact cutting system and method
US10954738B2 (en) 2014-10-20 2021-03-23 Worldwide Oilfield Machine, Inc. Dual compact cutting device intervention system
US11156055B2 (en) 2014-10-20 2021-10-26 Worldwide Oilfield Machine, Inc. Locking mechanism for subsea compact cutting device (CCD)

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BRPI0916907A2 (pt) * 2008-08-04 2019-09-24 Cameron Int Corp acumulador submarino de área diferencial
GB2488812A (en) * 2011-03-09 2012-09-12 Subsea 7 Ltd Subsea dual pump system with automatic selective control
US20140061522A1 (en) * 2012-09-05 2014-03-06 Vetco Gray Inc. Valve Actuator with Degressive Characteristic Spring
WO2014074747A1 (fr) 2012-11-07 2014-05-15 Transocean Sedco Forex Ventures Limited Stockage d'énergie sous-marin pour blocs obturateurs de puits (bop)
US9410392B2 (en) * 2012-11-08 2016-08-09 Cameron International Corporation Wireless measurement of the position of a piston in an accumulator of a blowout preventer system
BR112016002183A2 (pt) 2013-08-01 2017-08-01 Bop Tech Llc dispositivo para conter pressão associada a um poço
US10018009B2 (en) * 2015-02-26 2018-07-10 Cameron International Corporation Locking apparatus
CN105298428B (zh) * 2015-09-16 2018-04-06 盐城市大冈石油工具厂有限责任公司 单杠自剪切式高温封井器
US10190382B2 (en) * 2015-10-20 2019-01-29 Worldwide Oilfield Machine, Inc. BOP booster piston assembly and method
WO2017120101A1 (fr) 2016-01-05 2017-07-13 Noble Drilling Services Inc. Actionneur de vérin motorisé assisté par pression pour dispositif de commande de pression de puits
CN106194096A (zh) * 2016-08-04 2016-12-07 中国石油大学(华东) 一种海上平台有杆采油复合井口装置
CN112983331B (zh) * 2021-03-24 2021-12-07 大庆市天德忠石油科技有限公司 一种液压双闸板封井器

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ATE469287T1 (de) 2010-06-15
RU2370627C2 (ru) 2009-10-20
EP1809858B1 (fr) 2010-05-26
EP1809858A1 (fr) 2007-07-25
RU2007120581A (ru) 2008-12-10
NO20072782L (no) 2007-08-01
BRPI0517055A2 (pt) 2011-08-02
DE602005021532D1 (de) 2010-07-08
US20090127482A1 (en) 2009-05-21

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