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
  • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
  • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
  • E21B19/09—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods specially adapted for drilling underwater formations from a floating support using heave compensators supporting the drill string

Definitions

• the invention relates to a hydraulic sea state compensation device according to the preamble of claim 1.
• Such sea state compensation devices are used, for example, in naval technology, when a load is to be deposited by a ship on an object supported on the seabed, for example a platform, wherein, for example, a crane is arranged on the ship.
• the crane can also be arranged on a platform supported on the seabed, so that the load can be placed on a ship or a corresponding floating object.
• a similar task is also present when, for example, a drill string is lowered from a floating platform and it is raised and lowered by the sea.
• heavy measuring devices or supply stations for robots or the like are lowered from a ship via a winch to great depths, the sea cable causing the holding cable to be subjected to considerable tensile loads.
• US Pat. No. 3,946,559 discloses a sea compensation system in which the load, in the present case a drill string, is fastened to an actuator embodied as a cylinder, which in turn is mounted on a ship or a platform.
• a pressure chamber of the actuator is subjected to the pressure of a passive hydropneumatic storage which has a piston, via which a gas space is separated from a pressure medium space.
• the piston can be moved by means of an active cylinder.
• a problem with the known solutions is that the systems are comparatively complex and have a large footprint.
• the invention has for its object to provide a sea state compensation device, which allows a simple compensation of a reliable compensation caused by sea conditions movements.
• the sea state compensation device has a compensation system, which consists in principle of a hydropneumatic storage (passive cylinder) and an active cylinder device.
• the active cylinder device is integrated in the hydropneumatic accumulator, wherein a common piston arrangement is arranged within a common cylinder housing.
• a pressure chamber is limited, one of which is preferably a gas space of the hydropneumatic accumulator.
• the active cylinder device is attached to the hydropneumatic accumulator, so that such a solution requires considerably more space and device complexity.
• the unit of hydropneumatic accumulator with integrated therein active cylinder device can be operated in operative connection with a linear actuator (hydraulic cylinder) or a winch, of which the load is held.
• the load is thus supported by the actuator designed as a hydraulic cylinder, whose pressure chamber, which is effective in the supporting direction of the load, is connected via a pressure line to the second pressure chamber of the common cylinder housing.
• This working space forming a pressure chamber and the above-mentioned gas space then form the two end portions of the common cylinder housing.
• the guided in this common cylinder housing piston assembly has two piston bottom surfaces forming piston collars, which are connected by a piston land. This passes sealingly through a partition wall of the cylinder housing, so that the two control chambers of the active cylinder device are formed by the annular end faces of the piston collars on the one hand and the housing partition on the other hand.
• the load is supported on a winch.
• This is preferably driven by a hydraulic motor whose pressure side is connected to a working space of the cylinder housing, so that there is a pressure medium connection between the hydraulic motor and the active cylinder device.
• the unit of hydrodynamic storage and active cylinder device in this embodiment preferably has a piston assembly with two end piston collars and a central annular collar, which are connected to each other via two piston webs.
• Each of these piston webs passes through a housing partition wall of the cylinder housing, so that in addition to the two outer cylinder chambers (one of which is the gas space) in the cylinder housing by two adjacent annular end faces of the above piston collars and the housing partition between them, the two control chambers of the active cylinder device and by the other two annular end faces the piston collars and the intermediate housing partition of the working space and another working space are formed.
• a gas space and a further pressure chamber are delimited on the front side in the cylinder housing, the latter can be acted upon in a preferred embodiment, with ambient pressure.
• the provided for driving the winch hydraulic motor can be performed in a closed or open pressure fluid circuit.
• the hydraulic motor is supplied with pressure medium via a variable displacement pump driven by a motor, wherein a suction port of the pump via a suction line with a low pressure port of the hydraulic motor and a pressure port of the pump via a high pressure line with a pressure port connected to the hydraulic motor.
• the high-pressure line via a pressure line with the first-mentioned working space and the suction line via a Nieder- pressure line connected to the other working space, so that the hydraulic motor can be supplied with pressure medium either over or over the pump or work spaces.
• Both the collars of the common piston and the piston webs can be designed with different diameters.
• a fast-switching shut-off valve isolation valve
• the actuator hydropaulic cylinder
• the working space of the cylinder housing or between the working space and the pressure line of the hydraulic winch drive, so that the connection between the actuator or the Winch drive and the compensation system (hydropneumatic storage / active cylinder device) can be interrupted in no time.
• the piston assembly may be formed integrally or from a plurality of pistons.
• Figure 1 shows a hydraulic sea state compensation device for a load held on a linear actuator
• Figure 2 is a sea state compensation device for a load held on a winch and Figure 3 shows a concrete application of the sea state compensation device according to Figure 1 in a drilling device.
• FIG. 1 shows a functional diagram of a sea state compensation device (Heave Compensation System) 1, in which a load L is movable by means of a designed as a hydraulic cylinder 2 linear drive. It is assumed that this hydraulic cylinder 2 is stationarily mounted on a ship or a floating platform and the load L is to be held in a predetermined relative position with respect to a fixed target, for example a platform supported on the seabed.
• the compensation of the static load and the sea state via a dot-dash line indicated compensation system 4 with hydropneumatic memory, via which the hydraulic cylinder 2 is controlled such that the load L retains the predetermined relative position to the target object.
• the designed as a differential cylinder hydraulic cylinder 2 has a differential piston 35, which divides the hydraulic cylinder 2 in a penetrated by the piston rod annular space 36 and a bottom-side cylinder chamber. At least the annular space 36 is connected via a pressure medium supply, not shown, for extending and retracting the piston rod 39 with a pump or a tank to raise or lower the load L.
• a linear drive is designed only for relatively small strokes.
• the compensation system 4 consists essentially of a hydropneumatic accumulator 6 and an active cylinder 8 designed as a synchronous cylinder, which is integrated in the hydropneumatic accumulators.
• the unit of hydropneumatic accumulator 6 and active cylinder 8 is referred to as an active storage.
• the Hydropneumatic accumulator 6 is designed to be able to support load L statically, ie without supporting the dynamic cycling due to sea state, while the active cylinder is intended to balance the dynamic alternating loads such as friction and other parasitic factors and to provide position control to enable the load at high speed.
• the existing from the memory 6 and the active cylinder 8 active storage has a common cylinder housing 10 in which a piston 12 is guided axially displaceable.
• This has two outer piston collars 14, 16, which are interconnected by a piston web 18.
• This passes through a housing partition 20 of the cylinder housing, so that it is divided by the bottom of the piston collar 16 in a gas space 22 and the bottom of the piston collar 14 in a working space 24.
• a first control chamber 26 and the second annular space 28 is limited by the annular end face of the piston collar 14 and the housing partition 20.
• seals are arranged in the illustration of Figure 1, via which the aforementioned spaces of the cylinder housing are separated from each other.
• the gas space 22 is connected via a gas line 30 to a gas reservoir 32, so that acts on the bottom surface of the piston collar 16 of the gas pressure.
• the two control chambers 26, 28 can be connected via connections A, B to a control valve device described in more detail below and to a pressure medium source or a tank, so that the annular end face of the piston collar 16 or the annular end face of the piston collar 14 can be actively pressurized. around the piston 12 in response to the movement of the load L. slide.
• the terminals A, B can also be short-circuited to put the active cylinder in "clearance"; then the system works as a passive memory.
• the working space 24 is connected via a pressure line 34 to an annular space 36 of the hydraulic cylinder 2 in order to prevent shock loads when lifting loads from a movable location (eg deck of a ship in sea state), in the pressure line 34 a dashed line indicated fast switching Shut-off valve 38 may be provided, via which the oil side of the active storage of the hydraulic cylinder 2 is separable. About this shut-off valve 38 and the memory function can be disabled.
• the passive hydropneumatic accumulator is thus formed by the gas accumulator 32, the gas space 22 and the working space 24, while the active cylinder is formed by the two annular control spaces 26, 28 which are separated from one another by the housing dividing wall 20 which can be acted upon via the connections A, B with pressure medium.
• the load L is moved by means of a winch 40, which is driven via one or more hydraulic motors 42.
• the hydraulic motor 42 is arranged in a closed circuit and is supplied via a driven by a motor M variable 44 with pressure medium.
• a pressure port P of the variable displacement pump 44 is connected via a high pressure line 47 to a pressure port P 'of the hydraulic motor and a suction port S of the variable displacement pump 44 via a suction line 49 to a low pressure port T of the hydraulic motor 42.
• variable pressure sucks pressure medium from a tank T and the pressure medium via the low pressure port T of the hydraulic motor 42 is returned to the tank T.
• the compensation system 4 essentially consists in turn of a hydropneumatic accumulator 6 and a synchronous cylinder 8 formed as a synchronous cylinder, which in turn are designed as a unit (active accumulator).
• a piston 12 is guided, which in the illustrated embodiment has two outer piston collars 14, 16 and a central annular collar 46.
• the annular collar 46 and the piston collar 14 are of a first piston ridge 48 and the annular collar 46 and the piston collar 16 connected to each other via a second piston ridge 50, which, for example, has a smaller diameter than the first piston ridge 48.
• the piston web 48 passes through a first housing partition wall 52 and the second piston web 50 passes through a further housing partition 54.
• the cylinder housing 10 is thus subdivided into six pressure chambers by the piston 12, which is designed with three collars, the pressure chamber being the gas chamber 22 in FIG.
• the two control chambers 26, 28 are limited by the housing partition wall 52 and the annular collar 46 and the piston collar 14.
• Another working space 56 is limited by the further housing wall 54 and the middle annular collar 46 and the working space 24 through the housing partition wall 54 and the right piston collar 16.
• the gas space 22 is connected to the gas reservoir 32 via a gas line 30, as in the previously described embodiment, so that the gas pressure acts on the bottom surface of the piston collar 16.
• a space 58 is limited, the z. B. connected to the environment or the low-pressure room or can be completed.
• the working space 24 is connected via the pressure line 34 to the high-pressure line 47 and the further working space 56 is connected via a low-pressure line 60 to the suction line 49.
• fast closing check valves 38 may be provided in the low-pressure line 60 and / or the pressure line 34 in turn fast closing check valves 38 may be provided.
• shock loads shock loads
• the two control chambers 26, 28 can in turn, as in the above embodiment via the terminals A, B and a control valve assembly, not shown, connect to a pressure medium source or a tank to perform an active position control of the accumulator piston, and thus the load.
• variable displacement pump 44 does not promote pressure means to the hydraulic motor 42.
• the piston 12 is the control of the active cylinder 8 is shifted as a function of the vertical movement of the ship, so that correspondingly from the working spaces 24 or 56 pressure medium to the motor 42 is guided so that it drives the winch 40 accordingly to allow the compensation movement.
• the load L is supported by the pressure in the hydropneumatic accumulator 6.
• the active cylinder must apply pressure differences due to gas characteristics, friction and dynamic influences.
• the gas pressure should be designed so that it can support the load.
• the gas pressure in the gas storage 32 is variable in dependence on this load.
• a compressor with the associated control devices for adjusting the gas pressure should be provided.
• the adjustment of the compensation force to the load to be handled can also take place in that the hydraulic motor 42 of the winch 40 is designed with a variable displacement volume or in that a plurality of hydraulic motors 42 with variable displacement volume are connected in parallel.
• the displacement volume is then adjusted as a function of the load, the pressure at the gas side of the active reservoir, i. the pressure in the gas space 22 and in the gas storage 32 can be kept constant, so that no separate compressor and no gas pressure regulating device are required.
• the hydraulic circuit containing the pump 44 and the hydraulic motor 42 is still performed with all conventional devices, such as pressure relief valves, rinse cycle, coolers, filters, as used in conventional closed circuits. Leakage can be compensated in the same way as conventional systems.
• control chamber 28 are interchanged with the working space 24.
• the piston 12 is made in one piece, in principle, this piston could also be designed in several parts.
• FIG. 3 shows a concrete application of the sea state compensation device shown in FIG. 1 for a drill string forming the load L, wherein a drill head is to be lowered from a ship 62 to the ocean floor in order, for example, to remove a seabed sample or to drill for oil.
• a hydraulic cylinder arrangement 2 is formed by two or more hydraulic cylinders connected in parallel, wherein the piston rods 39 are mounted on a drilling stand 64 supported on the ship 62 and the load L (drill string) is fastened to the vertically displaceable cylinders.
• a laser measuring device 66 is arranged in the illustrated embodiment, via which the position of the ship can be detected. The position of the cylinder 2 is detected by displacement transducer 68.
• Figure 3 shows the essential components of the control unit for controlling the active cylinder 8, over which the movements, or the pressure fluctuations on the hydraulic cylinders 2 are actively compensated due to the sea state.
• the load L ie the weight of the cylinder and the drill string is statically supported by the hydropneumatic storage 6 by the gas pressure in the gas chamber 22 and thus in the gas storage 32 is set accordingly.
• the gas storage 32 can also be charged directly via the compressor unit 74 and the gas pressure control unit 70, wherein the gas pressure is variable depending on the weight of the drill string and possibly the sea state.
• the pressure medium supply of the active cylinder 8, the hydraulic cylinder 2 and the working chamber 24 via a variable displacement pump 76, can be sucked via the pressure medium from a tank T and conveyed into the pressure line 34.
• This pressure line 34 is connectable via a lifting valve 78 with a pump line 80 connected to the pump 76 and via a drain valve 82 with a tank line 84 connected to the tank T. Both valves 78, 80 are biased leak-free in a blocking position.
• the lifting valve 78 is a switching valve, while the lowering valve 82 is a continuously variable directional control valve, in which a drain aperture is proportionally adjustable.
• a feed line 86 branches off from the pump line 80 and a drain line 88 branches off from the tank line 84, leading to two input connections P, T of a proportionally adjustable active storage control valve 90.
• Two working ports A, B of the active storage control valve 90 are connected via a supply line 92 and a drain line 94 to the working ports A and B of the active cylinder 8.
• the supply line 92 and the drain line 94 can be switched via a bypass valve 97, so that the active cylinder 8 is then ineffective and the memory 4 only works as a passive memory.
• the two control chambers 26, 28 of the active cylinder 8 in response to the ship movement with pressure medium be charged or connected to the tank T.
• the Aktiv istventil 90 is executed in its spring-biased home position with a floating position and can be adjusted via proportionally adjustable electromagnets so that either the control chamber 26 or the control chamber 28 is connected to the variable displacement 76, while the pressure medium from the other pressure chamber to the tank T displaces becomes.
• the filling of the working space 24 of the hydropneumatic accumulator 6 and the annular spaces 36 of the hydraulic cylinder arrangement 2 takes place via a filling control valve 96 whose single working port A is connected via a filling line 98 to a connecting line 100 between the working space 24 and the pressure line 34.
• this connection line 100 the above-described check valve 38 is arranged, via which the connection between the working space 24 and the hydraulic cylinder assembly 2 can be shut off or opened.
• a pressure port P of the Artregelventils 96 is connected via a pump branch line 102 to the pump line 80 and a tank port T of the Greregelventils 96 via a tank branch line 104 with the tank line 84, in which further means for cooling, filtering, etc. of the pressure medium are provided.
• the hydropneumatic accumulator 6 is first moved to a starting position and the gas pressure in the gas space 22 is set as a function of the weight of the drill string, this setting being set proportionally to the expected weight to be lowered minus the desired feed force acting on the drill head.
• These Setting of the active accumulator 8 via the filling control valve 96, via which the working space 24 is supplied with pressure medium, while the check valve 38, the lifting valve 78, the drain valve 82 are closed and the bypass valve 97 is opened, so that the two control chambers 26 and 28 of the Active cylinder 8 are connected.
• the drill head is lowered to the seabed.
• the shut-off valve 38 remains closed and the valves 78 and 82 are used to allow by retracting and extending the hydraulic cylinder assembly 2, the assembly of the drill string and lower the drill head.
• the hydraulic cylinder arrangement 2 should be adjusted in such a way that there is still sufficient travel path for the sea state compensation.
• the pressures in the gas space 22 and in the working space 24 can still be adjusted correspondingly via the filling valve 96 or the gas pressure regulating unit 70 in order to compensate for the weight of the drill string.
• a passive sea state compensation is first switched on, whereby the load pressure of the hydraulic cylinder arrangement 2 is detected.
• the valves 78, 82 are moved to their locked position, the active storage control valve 90 is still in its home position and the check valve 38 is open.
• the active storage 8 is still ineffective, since the bypass valve 97 still remains in its passage position.
• This controlled extraction of the drill head from the ground is effected in that via the fill control valve 96 when the bypass valve 97 is open, pressure medium is conveyed into the annular spaces 36 of the hydraulic cylinder arrangement 2, so that the drill head is pulled out of the ground at a constant speed.
• an active sea state compensation takes place by means of the setting of the active storage control valve 90, via which the pressure required for sea state compensation in the control chambers 26, 28 is adjusted in order to pull the drill head out of the ground at a constant speed.
• a Seegangskompensations Nureau in which the compensation of a generated by the sea relative movement of a load with respect to a desired position via a passive hydropneumatic storage and an actively controlled active cylinder takes place.
• the active cylinder is integrated in the hydropneumatic accumulator, so that the compensation device is constructed extremely compact and simple. LIST OF REFERENCE NUMBERS

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• 2005
  • 2005-12-09 DE DE102005058952A patent/DE102005058952A1/de not_active Withdrawn
• 2006
  • 2006-03-30 WO PCT/DE2006/000567 patent/WO2006105764A1/fr not_active Application Discontinuation
  • 2006-03-30 EP EP06722719A patent/EP1869282B1/fr not_active Not-in-force
  • 2006-03-30 AT AT06722719T patent/ATE445081T1/de active
  • 2006-03-30 DE DE502006005035T patent/DE502006005035D1/de active Active
• 2007
  • 2007-11-02 NO NO20075563A patent/NO332099B1/no not_active IP Right Cessation

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