EP0581838A1 - Machine motrice pour operations sous-marines et dispositifs entraines par une telle machine - Google Patents

Machine motrice pour operations sous-marines et dispositifs entraines par une telle machine

Info

Publication number
EP0581838A1
EP0581838A1 EP92909601A EP92909601A EP0581838A1 EP 0581838 A1 EP0581838 A1 EP 0581838A1 EP 92909601 A EP92909601 A EP 92909601A EP 92909601 A EP92909601 A EP 92909601A EP 0581838 A1 EP0581838 A1 EP 0581838A1
Authority
EP
European Patent Office
Prior art keywords
sampler
piston
valve
hydrostatic
low pressure
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.)
Granted
Application number
EP92909601A
Other languages
German (de)
English (en)
Other versions
EP0581838B1 (fr
Inventor
Kare Aardal
Philip Howard Dixon
Yngve Kristoffersen
Anders Lien
Eldar Lien
Kaare Nordbo
Sigurd Ree
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.)
Selantic Industrier AS
Original Assignee
Selantic Industrier AS
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 NO911669A external-priority patent/NO911669D0/no
Priority claimed from NO911668A external-priority patent/NO911668D0/no
Application filed by Selantic Industrier AS filed Critical Selantic Industrier AS
Publication of EP0581838A1 publication Critical patent/EP0581838A1/fr
Application granted granted Critical
Publication of EP0581838B1 publication Critical patent/EP0581838B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63C—LAUNCHING, HAULING-OUT, OR DRY-DOCKING OF VESSELS; LIFE-SAVING IN WATER; EQUIPMENT FOR DWELLING OR WORKING UNDER WATER; MEANS FOR SALVAGING OR SEARCHING FOR UNDERWATER OBJECTS
    • B63C11/00—Equipment for dwelling or working underwater; Means for searching for underwater objects
    • B63C11/52—Tools specially adapted for working underwater, not otherwise provided for
    • 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
    • E21B25/00—Apparatus for obtaining or removing undisturbed cores, e.g. core barrels or core extractors
    • E21B25/18—Apparatus for obtaining or removing undisturbed cores, e.g. core barrels or core extractors the core receiver being specially adapted for operation under water
    • 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
    • E21B41/00—Equipment or details not covered by groups E21B15/00 - E21B40/00
    • E21B41/0007—Equipment or details not covered by groups E21B15/00 - E21B40/00 for underwater installations
    • 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
    • E21B7/124—Underwater drilling with underwater tool drive prime mover, e.g. portable drilling rigs for use on underwater floors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature

Definitions

  • the invention concerns an engine which is intended to operate at great depths by utilizing the energy which is released when surrounding water masses under great hydrostatic pressure are admitted into a low pressure reservoir via a hydraulic motor.
  • the invention also concerns a hydrostatic sampler, especially for core samples of marine sediments, wherein the sampler comprises a substantially cylindrical head and a substantially cylindrical sampler section whose longitudinal axis passes approximately through the head's centre of gravity and wherein the sampler section comprises a sampler tube consisting of at least one sampler tube section.
  • the reason behind the invention is that the supply of, e.g., hydraulic or electrical power from, e.g., a ship to a working tool on the seabed, entails increasing difficulties as the depth increases, since transmission lines or pipes become extremely expensive, heavy, difficult to handle and vulnerable.
  • the machine according to the invention uses an integral low pressure reservoir as a "hydrostatic accumulator", the energy which is released when the surrounding liquid is admitted into the low pressure reservoir under controlled conditions being determined by the product of the pressure difference and the internal volume of the low pressure reservoir.
  • a low pressure reservoir with an internal volume of l m 3 and approximately empty of gas, when lowered to a depth of 2000 metres (corresponding to a pressure of approximately 20 MPa) will be capable of releasing a pressure energy from, surrounding water masses of 20 x 10 7 Nm, or approximately 5.5 kWh.
  • the energy thus available will increase in proportion to the water depth and in proportion to the volume of the low pressure reservoir.
  • the invention concerns with various different arrangements for the utilization of this energy, together with various relevant applications.
  • Hydrostatic samplers are used to take core samples of the sediments in deep sea reservoirs. Such core samples are of great interest with regard to paleooceanography and paleoclimatology, since deep sea sediments consist mainly of deposits resulting from the biogenic activity in the water masses. Small calcareous and siliceous organisms accumulate on the seabed at a rate of approximately 1 cm in the course of 1,000 years. The fauna and flora populations in the water masses are adapted to the special temperatures and salinities which exist at any given time, and their fossil deposits therefore bear testimony to the physical properties of the water over the ages.
  • hydrostatic sampler By taking core samples of the upper sedimentary layer in.deep sea reservoirs, and up to the upper part of the continental shelf, by using a core length of approximately 10-12 m, a record can be obtained of the geological and paleontological history over a period of approximately 1,000,000 years. Since the core samples 'do not require to be of greater length than this and moreover the sedimentary layers are not especially hard, a hydrostatic sampler is well-suited to this purpose.
  • the use of hydrostatic samplers entails driving a sampler tube down into the sedimentary layer under the influence of the hydro ⁇ static pressure, i.e. the water pressure at the depth at which the sample is taken.
  • hydrostatic samplers particularly light and simple in design compared with samplers which require an external power supply, via, e.g., mechanical or hydraulic motors or with a built-in motor of some kind.
  • hydrostatic samplers since the surveys often take place in distant waters and extremely demanding environments, where it is a considerable advantage to have equipment which is easy to transport and operate.
  • the pressure reservoir as a housing for the complete system, including the valve control, all sensitive components can be safely housed in the pressure reservoir's container. Together with its contents, this constitutes the mass which is used as a pile-driver.
  • the piston in the hydrostatic motor is used directly to run the lifting and dropping operations, thus minimising the losses during the energy conversion.
  • the pressure reservoir which forms the sampler's head is lifted, a downward directed recoil effect is obtained, and this again causes a double-acting effect which further contributes to the improvement of the present sampler over the prior art.
  • the hydrostatic sampler according to the present invention thus offers a number of advantages in comparison with the known sampler.
  • the sampler according to the present invention provides a greater ratio between drop weight and hammer mass, a higher pump pressure, thus avoiding the need for power transfer and a greater lifting acceleration, which gives a substantial recoil effect, since the lifting acceleration is of the same order as the drop acceleration, which provides a doubling of the force of impact per blow. At great depths, moreover, the lifting forces become even more predominant.
  • the sampler according to the present invention is directly activated by the surrounding sea water, while Selvin and McCoy's sampler uses a membrane and hydraulic oil as a moder ⁇ ator. The sampler according to the invention can therefore be expected to give substantially lower internal losses.
  • the hydrostatic machine according to the invention is characterized by those features described in the claims 1-20, the reference numbers in these claims corresponding to the reference numbers in figs. 1-9, while a sampler according to the present invention is characterized by those features which are described in the claims 21-44, the reference numbers in these claims corresponding to the reference numbers in figs. 10-18.
  • Fig. 2 is an arrangement wherein an axial piston motor 2a driven by the hydro-static pressure is provided within a low pressure chamber 11.
  • Fig. 3 is a more refined arrangement in which, in addition to the hydrostatic water-driven axial piston motor 2a there is provided an axial piston pump 20 which supplies fluid to a separate hydraulic rotary engine 2b.
  • a separate hydraulic rotary engine 2b Two separate low pressure reservoirs are also provided, viz. the "integrated" reservoir 11 as in fig. 1 together with the external reservoir 3b.
  • Fig. 4 is an arrangement wherein the piston pump 20 and the rotary engine 31 together with the accumulators 32 and pressure control valves comprise a closed system operated by a suitable hydraulic oil, while only the piston motor 2a uses water as its operating medium.
  • Fig. 5 illustrates an embodiment of the invention as an impact device or percussion drill.
  • Fig. 6 illustrates an embodiment of the invention as a sampler for taking core samples of marine sediments on the seabed.
  • Fig. 7 illustrates an embodiment of the invention for driving an anchor 70 down into sediments on the seabed, the anchor according to the invention being in compressed form and in accordance with the invention being driven down into the sediments.
  • the anchor has hinged arms which will form flukes when the anchor chain 72 is under tension.
  • the machine forms an integral whole in which the machine's specific weight also makes a positive contribution to the effect of the anchor.
  • Fig. 8 illustrates another embodiment of a "hydrostatic anchor", in which the machine is equipped with a screw 17 with relatively large threads 170 driven down into the sediments with a combined hammering and screwing movement caused by a hydrostatic axial piston engine and a hydraulic rotary engine respectively.
  • Fig. 9 illustrates schematically an application of the hydrostatic pressure and arrangements for utilizing this in accordance with the invention in order to provide propulsion for a subsea vehicle.
  • Fig. 10 is a basic view of a sampler according to the present invention.
  • Fig. 11a illustrates a preferred embodiment of a deep water version of the sampler according to the present invention.
  • Fig. lib illustrates a preferred embodiment of a version of the sampler according to the present invention for shallow water.
  • Figs. 12a and 12b illustrate a preferred embodiment of the hydrostatic operating mechanism.
  • Figs. 13a and 13b illustrate another preferred embodiment of the hydrostatic operating mechanism.
  • Figs. 14a and 14b illustrate details of the embodiment in figs. 13a and 13b.
  • Fig. 15 illustrates schematically the lowering of the hydrostatic sampler according to the present invention.
  • Fig. 16 illustrates the sampler in fig. 15 ready for operation.
  • Fig. 17 illustrates the sampler in fig. 16 during operation.
  • Fig. 18 illustrates schematically the sampler in operation with full penetration of the sampler tube in the sedimentary layer.
  • Fig. 10 illustrates schematically the sampler according to the present invention.
  • the hydrostatic sampler comprises a pressure reservoir 1 which forms the head of the sampler and which is composed of sections, thus enabling the volume of the pressure reservoir to be regulated according to the number of sections used in the embodiment.
  • a high pressure cylinder 13 attached to the walls of the pressure reservoir.
  • the high pressure cylinder has a high pressure chamber which via openings 133 and 134 is connected with a low pressure chamber 14 which is formed by the upper volume of the pressure reservoir 1, and via an inlet valve 11 in connection with the outside of the pressure reservoir.
  • the high pressure chamber 130 constitutes the cylinder of a pump device which in reality is the sampler's motor, there being provided in the high pressure chamber 130 a first piston 131.
  • This piston 131 is rigidly connected via the piston rod with a second piston 21 in a secondary pump system 2 which is fitted to an extension of the pressure reservoir 1.
  • the object of the second piston 21 is first of all to cause the transfer of impact, or the lifting movement between the pressure reservoir 1 and a sampler section 3 which comprises the sampler tube 30, and secondly to provide a secondary pump system 2, in which the pump cylinder 2 can be emptied into the environment or used to inject water into the conduit 35 in order to provide lubrication of the sampler tube 30 via a three-way valve 22.
  • a pressure relief valve 10 to the environment, while an equalization of pressure is obtained in the non-active cylinder volume in the secondary pump system 2, via opening 203 and three-way valve 22 respectively.
  • the top plate of the pressure reservoir 1 is provided with an eye-bolt for the attachment of lines, while the pressure reservoir's top and bottom plates are attached by means of assembly bolts 7. The fitting of further sections to the pressure reservoir 1 can then be performed very easily by loosening the top or bottom plate of the pressure reservoir 1 and fitting the required number of extra sections, the length of the assembly bolts used naturally corresponding to the required length of the pressure reservoir 1.
  • FIGS 11a and lib illustrate in more detail a preferred embodiment of the hydrostatic sampler according to the invention.
  • Fig. 11a illustrates a deep water version of the sampler, wherein the internal volume of the high pressure chamber 130 in the high pressure cylinder is reduced by the insertion of a lining 135, as is more clearly illustrated in fig. 12a.
  • the ratio between the volume of the low pressure chamber 14 and the high pressure chamber 130 is thereby increased, thus enabling a correspondingly larger number of strokes to be achieved at great depth under a greater hydrostatic pressure, the number of impacts obviously being determined by the ratio between the chamber volumes.
  • Fig. lib illustrates a shallow water version of the hydrostatic sampler and, apart from the lining in the high pressure chamber 130, is exactly the same as the version in fig.
  • the high pressure cylinder 13 is illustrated in more detail in figures 12a, 12b, 13a and 13b.
  • a sleeve-shaped slide valve 15 which can be moved axially around the upper section of the high pressure cylinder.
  • the valve housing 15 is provided with an inlet opening 150 which communicates with a corresponding inlet opening 133 in the high pressure cylinder 13 when the slide valve is located in an upper position on the high pressure cylinder, at the same time as the piston 131 in the high pressure cylinder is located in a starting position.
  • the inlet opening 150 on the slide valve 15 is further connected with the inlet valve 11 via a flexible hose 12.
  • the manoeuvering device 110 is triggered, the inlet valve 11 opened and water under the surrounding pressure streams through the flexible hose 12 and into the high pressure chamber 130, the piston 131 in the high pressure cylinder as shown in, e.g., fig.
  • a first embodiment of the compression spring mechanism 16 is illustrated in fig. 12a, where the piston 131 is located in the starting position and in fig. 12b, where the piston is located in the final position.
  • the compression spring mechanism here comprises a helical spring which is placed in a spring housing 162 and fitted around a spring bolt 161.
  • the spring bolt 161 is passed through a fixed circumferential disc 151 on the slide valve 15 and a fixed locating disc 132 arranged on the piston rod at the bottom of the piston 131.
  • the spring bolts are provided parallel to the piston and the spring housing 162 is installed in the high pressure cylinder 13 beside this, as illustrated in fig. 12a or fig. 12b.
  • On the end of the spring bolts are fitted stop nuts 163 and 164.
  • the slide valve In the starting position of the piston 131, the slide valve is kept pressed into its upper position by the compression spring 160 by means of the capture disc 132 which causes the spring housing to abut against the stop nut 164, thus causing the tension in the compression spring 160 to be completely relaxed and the upper stop nut 163 on the spring bolt 161 to abut against the circumferential disc 151 on the slide valve 15 and to draw this with it into a lower position, thus interrupting the communication between the inlet openings 133 and 150 and stopping the flow of water to the high pressure chamber 130.
  • the piston 131 Under the weight of the pressure reservoir 1 or the sampler's head and if the pressure in the high pressure chamber 130 is equalized, the piston 131 now returns from the starting position to the final position, while at the same time the capture disc 132 once more abuts against the valve housing 160 and stretches the compression spring 160 which via the circum ⁇ ferential disc 151 again presses the slide valve into the upper position and creates a connection from the inlet valve 111 and through the openings 150 and 133 to the high pressure chamber which is filled once again, whereafter the piston stroke is repeated.
  • the tension spring 170 which is considerably weaker than the compression spring 160 is again stretched during this operation, but naturally cannot counteract the return movement of the slide valve 15.
  • the slide valve 15, together with the openings 133, 134 and 150 constitute a valve mechanism for the high pressure cylinder 130 which, together with the piston 131 in reality constitute a hydrostatic motor for the operation of the sampler.
  • Figures 13a and 13b illustrate a second embodiment of the spring mechanism for manoeuvering the slide valve 15, fig. 13a illustrating the piston 131 in the starting position and fig. 13b the piston in the final position.
  • figs. 13a and 13b correspond to figures 11a and lib respectively and describe the same embodiment as illustrated there.
  • a spring bolt 161 which is passed through an opening on the side of the high pressure cylinder, and through the circumferential disc 151 with which it is permanently connected.
  • the capture disc 132 also abuts against a stop nut 194 on the end of a camshaft 190, which similarly is arranged parallel to the first piston 131 on the outside of the high pressure cylinder 13 and passed through an opening on the side of this.
  • the blocking mechanism 18 is located in the starting position of the slide valve 15 in blocking abutment against the circumferential disc 151, but the blocking is cancelled when the camshaft 190 is pulled with the capture disc 132, thus cancelling the engagement between the camshaft 191 and the cam groove 182 in the ratchet mechanism.
  • the slide valve 15 thereby moves without hindrance under the influence of the compression spring 160a to the lower position, while a helical spring mechanism 17 which is attached to the upper section of the high pressure cylinder 13 and the camshaft, now that the cam disc is disengaged from the ratchet mechanism, pulls the camshaft 191 upwards, thus engaging the cam disc once again with the cam groove 182 in the ratchet mechanism 18, and the slide valve 15 via the circumferential disc engages in a locking manner with a locking groove 181 on the ratchet' mechanism 18.
  • the slide valve is thereby moved by the compression spring 160a and ends in its lower position, securely locked in this position by the ratchet mechanism 18, whereby free passage is created between the high pressure chamber 130 and the low pressure chamber 14 via the opening 134, thus equalizing the hydrostatic pressure, and the piston 131 begins the return stroke back to the starting position under the weight of the pressure reservoir or head 1 and the falling pressure in the high pressure chamber 130.
  • the capture disc 132 pulls the sleeve 195 which is permanently fitted on to the camshaft 190 and also the sleeve 165 on to the spring bolt 161, during which the cam disc 191 is disengaged from the ratchet mechanism 18 and at the same time the compression spring 160b is stretched.
  • the compression springs 160a and 160b are preferably designed as Belleville springs. As already described, the springs in the helical spring mechanism 17 are a tension spring 171.
  • the first piston 131 as illustrated schematically in fig. 10 and in more detail in, e.g., fig. 12a, is rigidly connected via the piston rod with the second piston 21 in the secondary pump system 2 , as is most clearly illustrated in figures 11a and lib. In fig. 11a both the pistons 131 and 21 are shown in their starting positions.
  • the second piston 21 in the secondary pump cylinder 20 is moved to act upon the sampler tube which is connected to the lower end of the secondary pump piston 21 via the sampler tube adaptor 33. This can slide on the control bolt 24 which is attached in the locking ring 201 on the lower part of the secondary pump cylinder 20, and prevents the sampler tube 30 or the sampler tube adaptor 33 from rotating on the secondary pump piston 21.
  • a three-way valve 22 which is opened during the lowering of the sampler and causes water to enter in under hydrostatic pressure into an annular space 202 which in the secondary pump piston's 21 starting position is created between the sliding bearing 200 on the secondary pump piston and the sliding bearing 211 on the inside of the wall of the secondary pump cylinder 20 when the sampler is positioned on the seabed, while at the same time it is opened for the working stroke of the piston 132.
  • the secondary pump piston 21 is forced downwards, while at the same time the inlet opening in the three-way valve 22 is closed. In its place a connection is obtained between the annular space 202 and an outlet opening in the three-way valve which is connected with a flexible hose 23.
  • the secondary pump piston 21 returns to the starting position and the water is forced out via the opening 203 in the upper volume of the secondary pump cylinder 20, while the annular space 202 which is again formed during the return movement via the three-way valve 22 is connected with the environment and once again filled with water under hydrostatic pressure, after which the cycle is repeated.
  • fig. 15 the sampler 1 is illustrated during lowering from, e.g., a research vessel.
  • the head or pressure reservoir 1 is attached .to the lowering line and on the sampler section 3 there is provided an attachment point for a support leg 6, which is shown closed around the sampler tube 30.
  • Release lines 60 for the support legs are shown hanging in a slack arc around the sampler.
  • the sampler according to the invention will be equipped with completely different instruments, including an inclination sensor for detecting the sampler's true inclination on the seabed, a sonar device for measuring the distance to the bottom, depths of penetration and also for the transfer of information on inclination.
  • the sonar device which is not illustrated in more detail, but which may be, e.g., a known per se modulated pinger, indicates the distance to the bottom, thereby enabling the support legs 6 to be released and brought into position by the release line 60 before the sampler reaches the bottom, the support legs sliding along the sampler tube to abut against the sampler head 31 as illustrated in fig. 16.
  • any inclination indicated can now be compensated by means of the lines 60, thus allowing the sampler tube to be positioned in a substantially vertical manner.
  • the driving operation continues in an alternating stroke cycle until the desired depth of penetration is achieved or the hydrostatic energy potential approaches zero. This usually involves approximately 200 strokes, depending, as mentioned above, on the ratio between the volume of the low pressure chamber and the volume of the high pressure chamber.
  • the sampler and the sampler tube with the core sample are pulled up to the surface by means of a lifting line, the pressure in the high pressure chamber 130 and the low pressure chamber 14 now being the same and identical with the surrounding hydrostatic pressure.
  • lifting the borehole is refilled with water to prevent the creation of a vacuum when the core sample and the sampler tube are pulled out.
  • the pressure reservoir is decompressed via the pressure relief valve 10.
  • the hydrostatic sampler weighs approximately 550 kg without the sampler tube. It is arranged to work at water depths between 200 and 6,000 m and consequently must be designed to resist the pressure forces which prevail at such depths. Depending on the water depth the number of strokes can be approximately 200 with an stroke length of approximately 350 mm. The possible penetration, depending on the nature of the sediments, can amount to up to 30 m, which means that the core sample's length is 30 m and this again means that special precautions must be taken on the mother vessel when the core sample is taken aboard.
  • the stroke frequency used can vary from, e.g. 0.6 - 3 Hz, i.e. the actual sampling operation can be performed in the course of a few minutes or less.
  • the stroke frequency can be adjusted via the inlet valve 111, and this is usually necessary as too high an stroke frequency results in severe dynamic loads on the piston rod. It will be obvious to those skilled in the art that there are a number of structural requirements which have to be satisfied in a hydrostatic sampler of this kind, with the purpose of operating at depths as low as 6,000 m. It is, e.g., important to dimension conduits and valves in order to avoid flow friction loss and there are naturally special requirements regarding resistance to corrosion, which can be met by the choice of the correct corrosion- and pressure-resistant materials.
  • the operation of the sampler can be monitored by means of a hydrophone connected to an amplifier aboard the mother vessel in order to record the sound of the impacts.
  • the sampler head 31 can be designed as a rotary drill chisel to which a rotating motion is provided by, e.g., converting a part of the impact energy to rotary motion by means of a suitable device, and in a known per se manner.
  • the rotary movement could possibly also be provided directly by an additional hydrostatic motor.
  • sampler tube itself, it is designed in a known per se manner and composed of sections which may, e.g., be 3 m in length.
  • the individual sampler tube sections are connected by means of a tube section adaptor 36 which also provides fluid connection between the water injection conduits 35 inside the individual sections.
  • a core retaining device 32 which grips the core and is pushed upwards in the tube sections during penetratio .

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Geology (AREA)
  • Physics & Mathematics (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Control Of Velocity Or Acceleration (AREA)
  • Soil Working Implements (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Confectionery (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Earth Drilling (AREA)

Abstract

Machine pour l'exécution de travaux à de grandes profondeurs, utilisant l'énergie libérée lorsque des masses d'eau environnantes, sous une pression hydrostatique élevée, sont admises dans un réservoir basse pression en passant par un moteur hydraulique (2). Cette machine met en oeuvre un réservoir basse pression (3) intégré faisant office d'accumulateur hydrostatique, l'énergie libérée lorsque le fluide environnant est admis dans ce réservoir basse pression est fonction du produit de la différence de pression par le volume intérieur dudit réservoir. Selon un mode de réalisation particulier (fig. 10), la machine est conçue comme engin hydrostatique de prélévement, particulièrement adaptée au prélévement par carottage d'échantillons de sédiments marins au fond de la mer.
EP92909601A 1991-04-26 1992-04-24 Machine motrice pour operations sous-marines et son utilisation dans un dispositifs carottier Expired - Lifetime EP0581838B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
NO911668 1991-04-26
NO911669 1991-04-26
NO911669A NO911669D0 (no) 1991-04-26 1991-04-26 Maskin for utfoerelse av arbeid paa store havdyp under utnyttelse av det hydrostatiske trykk.
NO911668A NO911668D0 (no) 1991-04-26 1991-04-26 Hydrostatisk proevetaker.
PCT/NO1992/000078 WO1992019836A1 (fr) 1991-04-26 1992-04-24 Machine motrice pour operations sous-marines et dispositifs entraines par une telle machine

Publications (2)

Publication Number Publication Date
EP0581838A1 true EP0581838A1 (fr) 1994-02-09
EP0581838B1 EP0581838B1 (fr) 1998-11-04

Family

ID=26648283

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92909601A Expired - Lifetime EP0581838B1 (fr) 1991-04-26 1992-04-24 Machine motrice pour operations sous-marines et son utilisation dans un dispositifs carottier

Country Status (8)

Country Link
EP (1) EP0581838B1 (fr)
JP (1) JPH06506996A (fr)
AT (1) ATE173050T1 (fr)
AU (1) AU656186B2 (fr)
CA (1) CA2109107A1 (fr)
DE (1) DE69227511T2 (fr)
NO (1) NO933843L (fr)
WO (1) WO1992019836A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11248433B2 (en) 2018-04-24 2022-02-15 Subsea 7 Norway As Injecting fluid into a hydrocarbon production line or processing system

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO964259D0 (no) 1996-10-07 1996-10-07 Kaare Aardal Hydrostatisk arbeidsinnretning og verktöy for samme
NO964723L (no) * 1996-11-07 1998-05-08 Selantic As Invertert akkumulator
CN102678682B (zh) * 2012-05-22 2015-06-10 淮海工学院 一种水下恒压差气源
CN110422306B (zh) * 2019-09-18 2024-05-03 江苏科技大学 一种海水驱动深海履带车底盘

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118417A (en) * 1962-07-30 1964-01-21 Stanwick Tad Method and apparatus for anchor embedment
US3418818A (en) * 1966-04-22 1968-12-31 Pan American Petroleum Corp Underwater power source
US3436914A (en) * 1967-05-29 1969-04-08 Us Navy Hydrostatic energy accumulator
US3412814A (en) * 1967-06-28 1968-11-26 Usa Hydrostatic corer
US3504648A (en) * 1968-04-29 1970-04-07 Frederick A Kriedt Deepwater hydraulic power unit
US3595012A (en) * 1970-02-06 1971-07-27 Us Navy Sea pressure operated power device
US3670680A (en) * 1970-09-25 1972-06-20 Frederick A Kriedt Water expulsion system
US4215544A (en) * 1978-05-17 1980-08-05 Tad Stanwick Method of generating rotary power in a deepsea environment
US4619593A (en) * 1979-09-11 1986-10-28 Steven Molnar Apparatus comprising a turbine and associated water extractor and method of translating the potential energy of deep sea water into useful work
NL8800632A (nl) * 1988-03-15 1989-10-02 Ihc Holland Nv Werkwijze voor het aandrijven van een hydraulisch onderwater werktuig.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9219836A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11248433B2 (en) 2018-04-24 2022-02-15 Subsea 7 Norway As Injecting fluid into a hydrocarbon production line or processing system

Also Published As

Publication number Publication date
ATE173050T1 (de) 1998-11-15
DE69227511D1 (de) 1998-12-10
WO1992019836A1 (fr) 1992-11-12
DE69227511T2 (de) 1999-07-15
AU1686992A (en) 1992-12-21
EP0581838B1 (fr) 1998-11-04
JPH06506996A (ja) 1994-08-04
NO933843L (no) 1993-12-27
NO933843D0 (no) 1993-10-25
AU656186B2 (en) 1995-01-27
CA2109107A1 (fr) 1992-10-27

Similar Documents

Publication Publication Date Title
US4575282A (en) System for driving open end pipe piles on the ocean floor using pneumatic evacuation and existing hydrostatic pressure
US8668472B2 (en) Wave actuated pump and means of connecting same to the seabed
CN101551303B (zh) 利用静水压力驱动的沉积物取样器
US2176477A (en) Method of and apparatus for taking earth cores
US3793835A (en) Variable rate hydraulic-pneumatic weight control and compensating apparatus
NO155984B (no) Anordning for generering av elektrisitet under boring av et borehull.
CN101650270A (zh) 机械手持式深海静水压力驱动保真取样器
US5382760A (en) Seismic well source
EP0581838B1 (fr) Machine motrice pour operations sous-marines et son utilisation dans un dispositifs carottier
US20220010661A1 (en) Rodless Pump and Multi-Sealing Hydraulic Sub Artificial Lift System
US5495902A (en) Coil tubing hydraulic jar device
US20140069723A1 (en) Method and apparatus for penetrating particulate substrates
US5456325A (en) Method and apparatus for driving a probe into the earth
Wang et al. Energy performance evaluation of an innovative hydrostatic motor
Robin et al. " TWO GAS-DIRTVE SAMPLING DEVICES
Selwyn et al. The hydrostatic motor: Utilization of hydrostatic pressure differentials in the deep sea
RU2488683C2 (ru) Способ депрессивного гидродинамического воздействия на пласт и устройство для его реализации
RU51681U1 (ru) Водяной двигатель
Wang et al. Implementation of a seafloor sediment corer with a novel hydrostatic motor
SU1465489A1 (ru) Глубоководна морска бурова платформа
Chen et al. Development and Sea Trials of a Deep-sea Energy Storage Buoyancy Regulating System
RU2447462C2 (ru) Скважинный имплозивный источник сейсмических колебаний
McCoy et al. The hydrostatic corer
SU1492017A1 (ru) Пробоотборник
Selwyn et al. The Use of Ocean Energy--A Hydrostatic Motor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19931124

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU MC NL SE

17Q First examination report despatched

Effective date: 19950308

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU MC NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19981104

Ref country code: LI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: GR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19981104

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19981104

Ref country code: CH

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

REF Corresponds to:

Ref document number: 173050

Country of ref document: AT

Date of ref document: 19981115

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69227511

Country of ref document: DE

Date of ref document: 19981210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19990204

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990424

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990424

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19990622

Year of fee payment: 8

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19991031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19991101

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19990424

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19991101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010201