US3902319A - Method and apparatus for instantaneously isolating a fluid operated load applying cylinder from its source - Google Patents

Method and apparatus for instantaneously isolating a fluid operated load applying cylinder from its source Download PDF

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Publication number
US3902319A
US3902319A US394720A US39472073A US3902319A US 3902319 A US3902319 A US 3902319A US 394720 A US394720 A US 394720A US 39472073 A US39472073 A US 39472073A US 3902319 A US3902319 A US 3902319A
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valve
pressure
isolator
sensing
fluid
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Peter B Olmsted
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Olmsted Products Co
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Olmsted Products Co
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Priority to NO743202A priority patent/NO743202L/no
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004—Fluid pressure supply failure

Definitions

  • ABSTRACT The continuous comparison of a retained fluid pressure memory sensed or monitored from a pulsating flow of fluid under pressure to and from a load supporting hydraulic pressure compensating working cylinder through an isolating valve, with said pulsating fluid under pressure to irrevocably close the isolating valve and thereby isolate the working cylinder upon a calculated threshold loss of load or of fluid pressure to immediately render the pressure differences harmless.
  • This invention deals in the art of closing an isolating valve to instantaneously trap the fluid in a load supporting hydraulic pressure compensating working cylinder rendering the same harmless.
  • a hydraulic fluid pressure memory control is not new in hydraulic controls as such, as evi denced in the US. Pat. No. 3,108,759 issued Oct. 29, I963.
  • the problems solved in the prior art by the use of memory systems of fluid under pressure do not teach the system, method and structure of the present invention, nor do they have any suggestion as to how such an invention could or should be made.
  • the drill string When drilling at the bottom of the sea where the water may be anywhere from three to five miles deep, the drill string becomes very heavy and must be supported on an anchored ship that is subjected to constant wave movement as well as to storms of all magnitude and directions which tend to increase the threshold of pressures of operation in the isolator valve and produces a very heavy load on the hydraulic motion compensating cylinder. It is, of course, desirable to produce a hull on the ship that will decrease the wave action as much as possible and also hold the ship regardless of the direction of the waves and wind.
  • the pressures involved may possibly convert the compensator load piston into a missile head which, if not retained upon the breakage of a long drill string, will, if allowed to escape, tear out the traveling and crown blocks as well as the top of the rigs. Such accidents not only delay the operation, but are expensive and the loss of time for shutdown for repairs is, of course, added to the cost of the project.
  • the present invention provides a very fast isolator to confine high working hydraulic pressures to compensate for quick load release or pressure loss and prevent damage to the equipment where heavy loads are supported under constant or changing load levels due to changing in load movement or in hydraulic pressures within predetermined limits of the threshold pressure involved.
  • This problem arises in many hydraulic applications, but the most colorful and challenging is that of drilling many miles in the floor of the seas or oceans, which is being performed at such depths that is impossible to have caissons as where employed in the prior art.
  • the principal object of this invention is the provision of an improved method and structure together with a novel system to isolate a hydraulic load compensating device that provides hydraulic intelligence to confine the fluid under pressure in such a compensating cylinder within a few milliseconds, thereby avoiding disaster.
  • the load applying hydraulic compensator of the present invention comprises a supported liquid operated compensating cylinder with a piston having an extending stem to which a load is applied.
  • An isolater valve is operable in a chamber connected between the load applying end of the compensating cylinder and one end of an interface liquid-gas separator cylinder or interface bottle which transfers pressure between the liquid and gas, and the other end of the liquid-gas separator cylinder is connected to a supply of gas under pressure.
  • a pressure memory means is provided to control the closing of the isolator valve.
  • a correlation of the pressure of the fluid supplied to the operating cylinder is continuously monitored and retained as a reference.
  • the pressure of the fluid in the operating cylinder is continuously compared with the monitored reference pressure, and the isolator valve is irrevocably closed when the pressure in the operating cylinder falls below a predetermined threshold relative to the monitored reference pressure which gradually varies with the operating cylinder pressure when the latter gradually changes during periods of time.
  • the monitoring of the fluid supplied to the operating cylinder to retain a reference which is a correlation of that pressure provides the basis of a pressure memory means to control the closing of the isolator valves should the fluid supplied under pressure to the cylinder retain a predetermined threshold minimum.
  • FIG. I is a perspective view of a derrick rig mounted aboard ship.
  • FIG. 2 is a schematic view of the hydraulic system illustrated in FIG. 1.
  • FIG. 3 is a monoplanic layout view of the physical valve structure showing the isolator valve, the sensing valve and its accumulator with the pilot valve and its filter system.
  • FIG. 4 is a time graph of the changes in pressure due to the sea waves in the hydraulic system of the isolator valve.
  • FIG. is a time graph of the movement of the sensing valve spool and the main isolator spool upon closing the former.
  • FIG. 6 is a time graph of the movement of the sensing valve spool and the main isolator spool when the sensing valve is actuated by exterior means such as a solenoid pilot valve to open the isolator valve.
  • FIG. 7 is a hydraulic circuit diagram of the isolator valve hydraulic system.
  • the ship 1 supports the derrick rig 2 from the platform 3 and is provided with the usual crown block 4 woven by the hoisting cable 5 to the traveling block 6.
  • Hanger means 7 suspend the compensating cylinder 8 by usual clamping collar indicated at 9.
  • the cylinder has a stem 10 extending from the bottom thereof which, in turn, is connected to the yoke 11 having a swivel hanger upon which is suspended the kelly bar 12.
  • the device may suspend the drill string itself from the usual hangers suspended in a similar manner; or when adding or removing lengths of drill pipe to the string, the same may be held by wedge slip blocks supported in the drill table itself which is ordinarily placed below the platform 3 and is provided with the proper rotary mechanism.
  • a section or so of the drill string may be supported within the rig ready for use, however, it has to be anchored against movement owing to the wave action, otherwise they are locked in racks on the deck of the ship from which they are withdrawn for use.
  • the isolator valve 13 has its large opening indicated as region A in FIG. 3 connected to the side of the compensating cylinder 8 adjacent the end from which the piston stem 10 extends.
  • the lower side of the isolator valve housing 14 contains region B or the connection for the hose 15 (FIGS. 1 and 2) which is sufficiently long to allow for at least to 30 foot heave in the ship as well as for the length of drill pipe or casing that is added to the string for the purpose of drilling or for the purpose of extracting oil from the well, or other prod ucts sought.
  • the other end of the hose 15 is supported from the hydraulic pipe coupling 16 which is connected through a section of the pipe 17 to the gas-oil separator cylinder 18 which may be provided with a rigid piston or diaphragm member that separates the gas from the oil such as indicated at 20.
  • the bottom of the gas-oil separator 18 is connected to the end of the pipe 17 and the upper end of this separator is connected by the pipe 21 which is provided with a series of valve connections for connecting independent bottles of gas that function as reservoirs, and each of the reservoirs as indicated at 22 represent a reservoir bank which may be independently or individually connected into the compressor or gas pump 23, each having their separate control valve for this purpose which may or may not be automatic for switchboard operation.
  • FIG. 3 is a monoplanic layout view of the physical valve structure showing the isolator valve in its open position; it is in its normal position for allowing the hydraulic fluid to surge in and out of the compensating chamber to maintain a substantial uniform elevation of the drill string or drill pipe, the reproducing lines, or whatever may be suspended from the traveling block.
  • the piston in the compensating cylinder is allowed to have a 20 or more foot stroke if such is the average movement created by the ordinary sea expected.
  • the hose connection must be sufficiently long to reach the upper and lower extremities of the movement of the traveling block.
  • the isolator valve body 13 is provided with a substantially horizontal cylinder port that connects to the lower end of the compensator cylinder as illustrated in FIG. 2, and this port is designated as region A; the hose port, which is designated as region B is the same size.
  • the isolator valve 24 is a sleeve type valve having two seating surfaces, one a cylindrical surface, the perimeter of the valve being seatable on the seat 25. The other seat is on the end of the isolator valve, and it is represented by the poppet seating surface 26 which seats against the poppet seat 27, which in this instance is illustrated as part of the valve body, but of course, it is a separate seating member which is of prepared steel capable of functioning to produce the results expected of this valve.
  • the sleeve valve is mounted on a guide plug which seals and snugly fits the inner bore of the valve.
  • the recess 28 is sufficiently large to receive the spring 30 which preloads the isolator valve to close.
  • the recess 28 is connected by radial ports to the region C which is termed the closing region, and accepts the fluid under pressure and passes it to the back or rear loaded base of the valve 24 to force it forward to its seating position.
  • region C merely connects to a circular port about a sensing spool 31 which has the same designated letter C.
  • the cylinder port has a passageway 37 which leads to filter A representing the region A or pressure chamber of the compensator cylinder.
  • Port 37 passes through the filter A and thence flows past the check valve 38 which is spring loaded and thence to passage 40, which is the E passage or region E wherein fluid pressure therein is applied to the aforesaid opposite side of the valve spool 31, representing a smaller total area in the operating section of the sensing spool as indicated at M then the total area opposing it.
  • Check valve 44 is also spring loaded, and the pressure within the accumulator 47 which, by the way is represented as region H, will flow outwardly directly to and past the check valve, if the pressure is sufficient to overcome the spring load plus the pressure in region E, from the sensing accumulator to the area or region E.
  • the pilot valve 50 is attached to and forms a part of the valve body 13 and as shown is provided with a connection to the tank as indicated by the letter T which not only collects from both ends of the pilot valve, but also connects to the latching passage G from the sensing valve poppet face 32. In the position of that shown in FIG. 3, the latching passage is directly open to the tank through the pilot valve 50. As shown, this pilot valve has three positions; one indicated as the central position shown in the view of FIG. 3 wherein the spool is in the central position and F is connected to E through a restriction such as the restriction illustrated within the pilot valve spool at 51. Thus, so far two restrictive orifices to which fluid must flow have been shown.
  • the restriction 51 permits the passage of fluid from the pressure area E to the pressure area F, passage 52 of which is connected to the spring loaded area 53 of sensing spool 31 which is opposed to the opposite side or region E of the valve spool as indicated at 4].
  • These areas together with the split area of the face 32 represent additional constants which may be changed to suit the purposes desired for calculating the operation of the sensing valve in controlling the closure of the isolator valve 24.
  • the sizes of the opposing faces of the sensing valve may be chosen so that the area of the operating face 584 in region E is selected in a manner to determine the threshold pressure on the area of the preloaded face 53, which latter face will initiate the motion of the sensing spool expressed by the following equation:
  • P is the pressure on the operating face E or 41.
  • F is the friction or stiction force which inevitably accompanies a valve member not continuously actuated and which has been stationary for a period of time which normally increases with that period of time.
  • K may represent the ratio of the closing and opening areas represented in regions E and F or against the faces 41 and 53.
  • K is the proportion between one of the pressure operating areas and the spring pressure exerted by the spring 35.
  • the sensing valve spool 31 is provided with a spool type area that connects the tank passage 55 to the region C that is connected directly to the chamber within the guide plug for the isolator valve 24 and is provided with radial ports to connect the region C directly to the annular recess 28 which exposes the whole rear of the face of isolator closure valve 24 to the pressure therein.
  • this chamber is now connected to tank by the cylindrical valve surface 36 and the pres sure within the cylinder port, which is required to be greater than a pressure such as 64 psi.
  • FIG. 4 which illustrates the heave cycle of the typical variation wherein the reference pressure P is indicated by a substantially horizontal line and for all practical purposes is equal to that of the pressure P as indicated.
  • This is the reference pressure which must at all times be materially higher than the troughs of the wave cycles which are represented by the changing pressures in the regions of the cylinder port A as represented by P, and of the hose port B represented by P
  • the volume of the hydraulic fluid within the cylinder which constantly changes owing to the waves that produce heave cycles, is immediately reflected in the curve P
  • the pressures in the chamber P of course, lag slightly as demonstrated by the dashed curve P
  • the tripping pressure which causes sensing valve spool 31 to function for the purpose of closing the isolator valve 24 is demonstrated by a pressure curve which is substantially similar in shape to the pressure curve P but appears materially below the troughs of the wave cycle indicated at b and b, etc.
  • any loss of load in any position along the wave cycle as shown in FIG. 4 which would cause both of the pressures of P or P to fall below the heave cycles to a value equivalent that of the tripping pressure P represents the threshold pressure. Since valve 58 allows free flow from region F to region B, the pressure in region F will follow, the pressure in region B when the latter falls. When the pressure P,, falls below P the valve 58 opens, starting movement of the sensing spool. This would shift the sensing valve spool 31 from the position shown in FIG.
  • the next function in the downward movement of the sensing spool is the closing by the spool area 36 of the closing region C of the isolator valve 24 from the tank connection 55.
  • the closing of the isolator valve is performed in a relatively short period of time, and due to the cylindrical valve seat 25 and the poppet valve seat 27, a small hydraulic cushion is formed just before the valve finishes its seating process.
  • the latching passage G continues to deplete fluid from the region F of the sensing valve flowing past the poppet seat 33 to this latching passage 56 and provides a lack of pressure in the region F.
  • the poppet valve 58 rcscats itself because of the continued drainage of fluid pressure from the region F.
  • the poppet valve 58 is closed before the isolator valve starts to move, or at best slightly after the isolator valve begins to move.
  • FIG. 7 is a hydraulic circuit diagram of the structure illustrated in FIG. 3.
  • the same reference numerals are applied to the same lines and indicated symbol structure as that shown in FIG. 3.
  • the valve housing body 13 encompasses the pilot valve, the hose port region B having the passage 42 connected thereto, and the cylindrical port region A which is directly attached to the bottom of the compensating cylinder below the travel of the compensating piston that supports the load suspended from the stem 10.
  • bypass valve which circumvents the entire isolator valve 24 in order to permit one to manually bypass the same if desired.
  • the isolator valve comprising this invention controls the flow of hydraulic fluid to and from compensating working cylinder 8 which heaves up and down with the ship but allows the working piston therein to travel as much as feet in the cylinder under controlled pressure conditions of flow of the hydraulic fluid so as to compensate for the heave of the waves in lifting and lowering the motion of the ship from the crest to the trough thereof as illustrated in FIG. 4.
  • This isolator valve is for the purpose of preventing any relative motion of the drill string relative to the ship when drill string sections are added or taken from the drill string or for the purpose of adding sections of drill pipe or casing pipe as the case may be when connecting the pipe to the drill string or for the production of oil from the drilled well, which may lie several miles below the surface of the sea where it penetrates the mantle of the earth for the production of gas, oil or other substances to be obtained from the bowels of the earth.
  • the isolator valve therefore must be actuated to close upon the addition of any section of drill string for further penetrating the drilling operation.
  • This isolator valve Another function of this isolator valve is the production of a check operation of the isolator valve itself and the equipment in conjunction therewith which function merely proves to the operator that the equipment is always in readiness to perform its proper function when a drill string breaks or the pressure supplied from the hose is lost. This or any other type of failure may be employed to actuate the isolator valve for the purpose of saving the equipment from reduction of very high pressure that would charge the compensating cylinder and convert the piston carrying the load to function as a missile.
  • the heave cycle of the movement of the water is seasonal, and allowances for variations of these seasonal conditions are necessary to the continued operation of the system.
  • Such variations require not only a change of the number of gallons per minute in the compensating cylinder but also the stroke of the piston in the compensating cylinder.
  • the load carried by the piston within the cylinder varies considerably but in all cases it supports the majority of the weight of the drill string.
  • the piston of compensator cylinder strokes in and out, and the total volume for gas varies in the compensators. This, in turn, causes a variation in the gas pressure that reflects back to the cylinder causing the load variations. Even though the load variation is undesirable, there is usually enough gas volume in the bank to keep the pressure from varying more than 10% percent per heave cycle.
  • the heave cycle period is approximately 15 seconds, during which time the piston of the compensator cylinder may stroke as much as 20 feet in each direction.
  • One of the principal advantages of this invention lies in the structure of the isolator spool valve per se. It is provided in the form of the cylindrical spool operating between the plug and a recess with small operating areas relative to its length and preloaded by a spring force in its closed position which requires a predetermined pressure in the cylinder for opening the valve.
  • the sensing spool like the isolator spool, is preloaded to keep the same closed in a normal operating position that permits the operating pressure within the cylinder port to hold the isolator valve in its open position against its preloaded spring pressure.
  • One of the important features of this invention is the provision of the latching passage such as described in the specification as G passage 56.
  • This passage has the unique func tion of controlling the operation of the sensing spool, which when actuated under predetermined pressure conditions operates to produce an irreversible closing operation of the isolator valve. It is impossible to stop or otherwise interfere with the operation of closing of the isolator spool to seal the fluid within the compensating cylinder once the sensing spool has been started in its performance to actually close the isolator valve.
  • pressures are interconnected in region E through passage 40 and the restriction 51 in the pilot valve 50, and passage 52 to region F.
  • fluid so supplied is continuously bled off past the check valve 58 to region B causing the pressure in region F to follow any variations occurring in region B.
  • the sensing spool 31 will begin to move as previously described and will cause flow from the accumulator to open the valve 44 to bring in the memory pressure for the purpose of operating the isolator spool 24 because the pressure did go below that thereshold where the system will function to irrevocably shift the sensing spool because the threshold pressure signifies a catastrophy has occurred.
  • the sensing spool is activated in the manner as illustrated by the curve in FIG. 5, the memory pressure from the pilot accumulator opens region E to region C after the latter has been closed to tank.
  • the isolator valve 24 quickly and irrevocably is closed as indicated in FIG. 5.
  • this invention contemplates the closing of the poppet valve 58 to shut off flow from region B, the hose port, to region F upon the opening of region E to C when closing the isolator valve.
  • Region F under standby conditions as shown in FIG. 3 will follow closely the pressures of the region B representing the hose connection to the compensator cylinder 8 and at the same time there is a steady flow of oil from region E to region F through the orifice in the spool of the pilot valve tending to keep region F pressure high. However, as shown in FIG. 5, that pressure is quickly drained off upon the opening of the poppet .valve 58 draining the region F to B.
  • pilot valve 50 in combination with the sensing valve to unbalance the sensing spool 31 in the same manneras the unbalance which would occur if there is a loss of pressure in region B.
  • the region E is fully open to the region C for maintaining the isolator valve 24 in its closed position and further since the pilot valve is in its center position as originally shown in FIG. 3, F continues to drain through passageway 34 of the sensing valve to and past the poppet face 33 to the latching passage G, 56, thence through the poppet valve to tank.
  • the latching passage really functions not only to latch the isolator valve in its closed position but also to latch the sensing valve in its operated position to maintain the isolator valve in its closed position regardless of the surge pressure received from the region B.
  • the solenoid valve of the pilot valve In order to reopen the isolator valve 24, the solenoid valve of the pilot valve must be momentarily energized as shown in FlG. 6 to block the latching passage G, 56, and prevent the drainage of region F of pressure to tank.
  • the sequence of operation is illustrated by the curves of FIG. 6 as previously stated from the shifting of the sensing valve to the opening of the isolator valve 24.
  • the precharged pressure is that pressure showing on the gauge 64 of FIGS. 2 and 3 which should be that pressure shown on the pilot gauge after the oil pressure in the system has been drained off and the gas tempera ture has had a chance to stabilize at ambient temperatures.
  • a load applying hydraulic compensator comprising a supported liquid operated compensating cylinder with a piston having an extending stem to which a load is applied, an isolator valve operable in a chamber connected between the load applying end of said compensating cylinder and one end of an interface liquid gas separator cylinder transferring pressure, the other end of which is connected to a supply of gas under pressure, and pressure memory means to store and directly apply a memory pressure sensed from said isolator valve chamber to control the closing of said isolator valve.
  • the structure of claim 4 characterized by a fluid pressure controlled preloaded sensing valve displaceable to control the flow of liquid under pressure to said operating area of said isolator valve, a sensing accumulator to retain a pressure memory within predetermined limits to move said sensing valve for admitting liquid under pressure from said sensing accumulator to operate said isolator valve to its closed position upon a predetermined reduction of pressure in said compensating cylinder.
  • the structure of claim 6 which also includes a preloaded face on said sensing valve which is greater in area than an opposing face on said sensing valve supplied with fluid pressure from said sensing accumulator which overcomes the pressure against said preloaded face upon the loss of pressure on either side of said isolator valve chamber, and a balancing area on opposite ends of said sensing valve equal to the difference between the area of said sensing valve preloaded face and the area of its said opposing face.
  • the structure of claim 7 which also includes a three-state externally controlled pilot valve means connected when operated to one state to connect said preloaded area of said sensing valve to a tank and cause said isolator valve to close, and when operated to its second state to cause said isolator valve to open by applying fluid pressure from said sensing accumulator to said preloaded area of said sensing valve and block said latching passage to keep from bleeding off said fluid pressure and open said isolator valve and connected in its third state to open said latching passage to tank and to supply fluid pressure to said preloaded area of said sensing valve from said sensing accumulator through a restriction orifice, said sensing valve blocking said isolator valve latching passage.
  • the method of claim 15 which also includes the step of providing an independent source of fluid under pressure as a basic reference pressure. limiting the rate of flow of the monitored reference pressure to the basic reference pressure.
  • the method of claim 16 which also includes the step of providing an unrestricted flow of the basic reference pressure directly to the isolator valve when the predetermined threshold pressure is reached to close the isolator valve.
  • the method of claim 17 which also includes the step of replenishing the correlated pressure from the fluid in the operating cylinder or from the fluid supplied to the operating cylinder from both sides of the isolator valve with an independent source of fluid under pressure as a basic reference pressure to control the monitored correlation of reference pressures.
  • the method of claim 15 which also includes the step of providing a pressure sensing valve with predetermined opposed pressure areas one to maintain the sensing valve closed and another to open the sensing valve upon a predetermined pressure thresold that causes the irrevocable closing of the isolator valve.
  • the method of claim 20 which also includes the step of externally actuating a pilot valve system to produce the same operable procedure as created when the operation of the isolator valve is automatic upon the creation of a predetermined threshold pressure to irrevocably close the isolator valve.
  • the method of claim 20 which also includes the step of providing a fast pressure unloading flow from the sensing valve preloading face to provide instant closing of the isolator valve upon sudden loss of pressure from the fluid supplied to the operating cylinder.

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US394720A US3902319A (en) 1973-09-06 1973-09-06 Method and apparatus for instantaneously isolating a fluid operated load applying cylinder from its source
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NL7411866A NL7411866A (nl) 1973-09-06 1974-09-06 Hydraulische compensator.

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US4098082A (en) * 1977-03-18 1978-07-04 Packer Martin R Wave-motion compensating apparatus for use in conjunction with an off-shore crane, or the like
US4362438A (en) * 1980-10-03 1982-12-07 A/S Akers Mek. Verksted Supporting device
US5365737A (en) * 1992-08-19 1994-11-22 Komatsu Ltd. Hydraulically-operated equipment for construction machinery
WO2001018350A1 (en) * 1999-10-19 2001-03-15 Huisman Special Lifting Equipment B.V. Hoisting device, with compensator built into hoisting cable system
US20070158076A1 (en) * 2006-01-11 2007-07-12 Hollingsworth Jimmy L Jr Stand compensator
US20100050917A1 (en) * 2006-06-01 2010-03-04 Von Der Ohe Christian System for Active Heave Compensation and Use Thereof
US20140331908A1 (en) * 2013-05-09 2014-11-13 Icon Engineering Pty Ltd Heave compensation and tensioning apparatus, and method of use thereof
US9359837B2 (en) 2012-12-10 2016-06-07 Mhwirth As Multi capacity riser tensioners
US9476264B2 (en) 2014-09-02 2016-10-25 Icon Engineering Pty Ltd Coiled tubing lift frame assembly and method of use thereof
USD835678S1 (en) * 2017-07-08 2018-12-11 Daqing Dannuo Petroleum Technology Development Co., Ltd. Pumping unit
US10385630B2 (en) 2015-07-13 2019-08-20 Mhwirth As Riser tensioning system

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US3108759A (en) * 1962-01-19 1963-10-29 Weinman Pump & Supply Co Coil positioning control
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US3721293A (en) * 1971-02-16 1973-03-20 Vetco Offshore Ind Inc Compensating and sensing apparatus for well bore drilling vessels

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US2865401A (en) * 1954-07-06 1958-12-23 Ludwig A Majneri Shut-off valve assembly for fluid pressure systems
US3108759A (en) * 1962-01-19 1963-10-29 Weinman Pump & Supply Co Coil positioning control
US3163005A (en) * 1962-11-19 1964-12-29 Jersey Prod Res Co Apparatus for use on floating drilling platforms
US3687205A (en) * 1970-10-28 1972-08-29 Gulf Research Development Co Floating rig motion compensator
US3721293A (en) * 1971-02-16 1973-03-20 Vetco Offshore Ind Inc Compensating and sensing apparatus for well bore drilling vessels

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4098082A (en) * 1977-03-18 1978-07-04 Packer Martin R Wave-motion compensating apparatus for use in conjunction with an off-shore crane, or the like
US4362438A (en) * 1980-10-03 1982-12-07 A/S Akers Mek. Verksted Supporting device
US5365737A (en) * 1992-08-19 1994-11-22 Komatsu Ltd. Hydraulically-operated equipment for construction machinery
WO2001018350A1 (en) * 1999-10-19 2001-03-15 Huisman Special Lifting Equipment B.V. Hoisting device, with compensator built into hoisting cable system
WO2001029366A1 (en) * 1999-10-19 2001-04-26 Roodenburg, Joop Hoisting mechanism, with compensator installed in a hoisting cable system
NO340227B1 (no) * 2006-01-11 2017-03-20 Weatherford Lamb Inc Fremgangsmåte for å beskytte en eller flere kompenseringssylindere til bruk under rørhåndteringsoperasjoner
US20070158076A1 (en) * 2006-01-11 2007-07-12 Hollingsworth Jimmy L Jr Stand compensator
EP1808568A3 (en) * 2006-01-11 2007-09-26 Weatherford/Lamb, Inc. Stand compensator
US7546882B2 (en) 2006-01-11 2009-06-16 Weatherford/Lamb, Inc. Stand compensator
EP2085568A1 (en) * 2006-01-11 2009-08-05 Weatherford/Lamb, Inc. Stand compensator
US20090245996A1 (en) * 2006-01-11 2009-10-01 Hollingsworth Jr Jimmy L Stand compensator
US8162045B2 (en) 2006-01-11 2012-04-24 Weatherford/Lamb, Inc. Stand compensator
US20100050917A1 (en) * 2006-06-01 2010-03-04 Von Der Ohe Christian System for Active Heave Compensation and Use Thereof
US8251148B2 (en) * 2006-06-01 2012-08-28 National Oilwell Norway As System for active heave compensation and use thereof
US9359837B2 (en) 2012-12-10 2016-06-07 Mhwirth As Multi capacity riser tensioners
US20140331908A1 (en) * 2013-05-09 2014-11-13 Icon Engineering Pty Ltd Heave compensation and tensioning apparatus, and method of use thereof
US9422791B2 (en) * 2013-05-09 2016-08-23 Icon Engineering Pty Ltd Heave compensation and tensioning apparatus, and method of use thereof
US9476264B2 (en) 2014-09-02 2016-10-25 Icon Engineering Pty Ltd Coiled tubing lift frame assembly and method of use thereof
US10385630B2 (en) 2015-07-13 2019-08-20 Mhwirth As Riser tensioning system
USD835678S1 (en) * 2017-07-08 2018-12-11 Daqing Dannuo Petroleum Technology Development Co., Ltd. Pumping unit

Also Published As

Publication number Publication date
NL7411866A (nl) 1975-03-10
NO743202L (en:Method) 1975-04-01

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