US3871622A - Method and apparatus for the control of a weight suspended from a floating vessel - Google Patents
Method and apparatus for the control of a weight suspended from a floating vessel Download PDFInfo
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- US3871622A US3871622A US378963A US37896373A US3871622A US 3871622 A US3871622 A US 3871622A US 378963 A US378963 A US 378963A US 37896373 A US37896373 A US 37896373A US 3871622 A US3871622 A US 3871622A
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- 238000000034 method Methods 0.000 title claims description 19
- 238000007667 floating Methods 0.000 title description 8
- 238000005553 drilling Methods 0.000 claims abstract description 42
- 230000009471 action Effects 0.000 claims abstract description 22
- 230000006872 improvement Effects 0.000 claims abstract description 7
- 239000007788 liquid Substances 0.000 claims description 47
- 238000004891 communication Methods 0.000 claims description 33
- 230000008859 change Effects 0.000 claims description 29
- 238000006073 displacement reaction Methods 0.000 claims description 25
- 230000007423 decrease Effects 0.000 claims description 22
- 239000012530 fluid Substances 0.000 claims description 14
- 230000003247 decreasing effect Effects 0.000 claims description 9
- 230000008569 process Effects 0.000 claims description 6
- 230000033001 locomotion Effects 0.000 description 20
- 125000004122 cyclic group Chemical group 0.000 description 8
- 238000012546 transfer Methods 0.000 description 8
- 230000001276 controlling effect Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 241001640034 Heteropterys Species 0.000 description 1
- 230000003213 activating effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000009966 trimming Methods 0.000 description 1
- 238000004260 weight control Methods 0.000 description 1
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Classifications
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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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S60/00—Power plants
- Y10S60/907—Working member positioned against counterforce by constantly applied motive fluid
Definitions
- ABSTRACT The invention concerns the control of the suspended weight supported from a piston of a pneumatichydraulic system on a vessel subject to wave and tidal action and particularly a vessel employed in connection with submarine drilling operation.
- the particular improvement concerns the modulation of the pressure in a portion only of the system to compensate for changes in pressure in another portion of the system so as to maintain the total force on the piston substantially constant during each portion of the cycle action of the heave. This may be accomplished by supporting the load from a piston system supported by two cylindrical elements and independently modulating the pressure in one of them to compensate for variations in pressure in another of the cylinder elements.
- This invention relates to improvements in methods and apparatus for the control of a suspended weight from a floating vessel and is particularly directed to the control of forces imposed on the drill string of a floating vessel employed in drilling, coring, running casing, reaming, cementing, testing, or other services in bore holes drilled in subaqueous environments where the vessel is subjected to wave or tidal action.
- the particular and preferred object of this invention is to improve the operation of such systems in which the element constituting the load is suspended from a pneumatically controlled hydraulic system.
- the drill string due to the great length above the drill collar, is a very flexible member subjected to considerable stretch due to its length and due to its own weight.
- the weight on the bit is less than the total static weight of the drill string because of the tension in the drill string imposed by the drilling lines as is well understood by those skilled in this art.
- the practice during drilling is to keep the drill pipe above the drill collar in tension.
- the drill collar acts as a weight-producing element which exerts the load on the drill bit.
- Wave action imposes a vertical oscillatory motion on the vessel which is imposed on an hydraulic cylinder resulting in variations in the tension in the drill pipe and therefore in variation in the load imposed upon the drill bit, when this is employed or any other load connected to the piston rod.
- the pressure on the liquid underneath the piston rod is maintained by gas pressure in an accumulator; such systems are shown in the Hanes et al., U.S. Pat. No. 3,714,995 and in the Larralde et al., U.S. Pat. No. 3,718,316.
- Floating vessels operating as drilling vessels in the open sea may experience vertical motions, i.e., heave due to wave action ranging, for example, from as low as 2 inches to feet or more trough to crest as, for example, has been experienced in drilling of the North Sea.
- wave action imposes a vertical displacement of the drilling vessel at a sinusoidal frequency. The period of such cycles has been reported in the range of 8 to 16 seconds but may be either greater or less.
- the drill is to be advanced at a controlled rate while maintaining a controlled weight on the bit. It is desirable to maintain a desired upper load limit on the bit in order that excessive stresses and torque are not developed which will be so large as to injure or even cause rupture of the drill pipe. On the other hand, it-is desirable that the load on the bit be not reduced excessively so that the rate of advance is unreasonably reduced. Since the cost of operation of the drilling operation is materially effected by the drilling rate, it is desirable that the drilling rate be maintained at as high a rate as is consistent with safety. This is established by the driller based on his experience and the performance of the drilling operation under consideration. The driller sets the load required for the drilling advance to make the advance be at a satisfactory rate consistent with safety.
- the hydraulic cylinder be mounted on the derrick to support the crown block or between the traveling block and the hook and that a force be applied to the piston sufficient to maintain the desired fraction of the total-load of the drill string during drilling operation so as to hold the desired load upon the drill bit.
- the weight which in our presently preferred application of our invention may be a drill string, is connected .as above to the piston of a hydraulic cylinder with the liquid under the piston in communication with a pneumatic accumulator under gas pressure. It is the purpose of our invention to maintain a desired force on the piston in the cylinder to be maintained during the complete wave cycle so that a predetermined load or a predetermined load variation on the drill can be maintained notwithstanding the amplitude or frequency or changes in the frequency or amplitude of the wave action. Where it is desired that the drill be advanced, ourinvention will provide a control for the advance of the bit under a controlled load during the advance of the drill.
- FIG. 1 is a somewhat schematic showing of the arrangement of the relations of parts of the system of our invention.
- FIG. 2 is a section of a conventional valve employed in our system.
- FIG. 3 is a schematic diagram of a control system of our invention.
- FIG. 1 shows the application of a control of our invention to an operation from a floating vessel 1 acting as the drilling platform.
- the conventional derrick 2 mounted on the vessel carries the split crown block 3 from which the sheaves 5 are suspended by the drilling lines.
- the sheaves 5 carry a cylinder 4, vented at 7, in which is positioned a piston 8 connected to a tubular rod 9 from which is suspended the conventional hook 10 which carries a swivel 11 and the kelly 12.
- the drill pipe 14 is connected to the kelly and to the drill collar which is connected to the bit 15.
- the casing 16 is composed of the conventional marine riser and the bore hole casing assembly together with the usual drilling equipment.
- the hollow piston rod carries a piston head 13 connected to the cylinder head by a closed-end tube 17 which passes through a seal in the piston 8.
- the tubular member 17 is bored at 6 to provide a communication between the inlet 19 to member 17 and to annulus 18 between the tubular rod 9 and the tubular member 17.
- This cylinder and rod construction and its use as a weight control have been described in the aforesaid application, Ser. No. 274,880, which is herewith incorporated in this specification by this reference.
- the tubular member 17 is connected by a pipe 19 via the solenoid valve 20, to be more fully described below, and to the reservoir 21 through valves 22, pump 24, and valve 23. Valves 22 and 23 are solenoid controlled as will be described below.
- the reservoir 21 is also in communication with the accumulator 34 through the valve 27.
- the pump may circulate via valve 29 and also through lines 31 and 32 via valve 20.
- FIG. 2 illustrates a proportional metering valve 20 by which flow proportional to the magnitude and sign of the electric signal which activates coils 49 and is obtained as will be described below.
- a torquing armature 47 is supported by a flexure tube 48 in such a manner that energizing coil 49 or coil 50 will cause torquing armature 47 to move in a direction determined by the relative forces exerted by the solenoid coils 49 and 50, moving element 51 and deflecting spring 52 with reference to pin 53.
- the resultant movement of the valve spool 56 will determine the area of the ports 61 and 61' which are uncovered and determine the relative flow of fluid from port 57 to ports and 62 via interconnected ports 58, 61, and 61.
- Feedback shaft 53 engages feedback spring 52 which, in turn, bears on element 51 attenuating the movement of element 51 so that movement of element 51 represents the summation of forces resulting from the relative elasticity of flexure tube 48, feedback spring 52, and the magnetic flux forces in coil 49 or 50, thus assuring a displacement of valve spool 56 in such a manner to allow flow proportional to the difference in the electric signal to coils 49 and 50.
- valve 20 described herein is a well-known valve, and no invention is claimed for the valve apart from its use in the combination and for the purpose of our invention.
- Other valves to regulate the direction and magnitude of flow which will function similarly in our invention may be used.
- the pneumatic accumulator 30 is in communication with the cylinder 4 through the valve 26.
- the tubular member 17 is connected to the reservoir 21 through valves 20 and 22 or via valve 20, line 32, and valve 23.
- the tubular member 17 may also be connected to the accumulator 30 via the by-pass line 40 and valve 41 and to the accumulator 30a which may be pressurized by the gas inlet through valve 30b.
- the line 19 is connected to the port 62.
- the line 31 is connected to the port 57 and to the accumulator 34 via valve 27 and to the reservoir 21 through the valve 22, pump 24 or through the regulator valve 29 to the reservoir 21.
- the pump during the operation of the system continuously circulates fluid through the by-pass valve 29.
- the reservoir may be at any pressure desired, e.g., it may be at ambient pressure and the pressure of the pump 24 may be set by the regulator 29.
- Line 32 is connected to the port 60 and to the reservoir through valve 23 and to the accumulator 34 through valve 27.
- the by-pass 40 with valve 41 connects the line 31 to the accumulator 30 via the by-pass 40 with the manual valve 41.
- the by-pass with the manual valve 45 connects the accumulator 34 and line 32.
- the valve 23 is by-passed by a manual valve 43 and the valve 22 is bypassed by a manual valve 42.
- the pressure in the accumulator 34 is sensed by a pressure sensor 36 to give a voltage of e responsive to the pressure in 34.
- a strain gauge of 35 is mounted on the piston rod above the hook to give an output e proportional to the stress in the piston rod.
- the stress and pressure sensors are provided with readouts which produce a voltageproportional to the parameters to which they respond.
- FIG. 3 illustrates the servo control of the volume of the liquid in the accumulator. All electrical elements used in the system are conventional, and their selection will be understood by those skilled in the art to which they pertain. Their assembly in combination with the system here described illustrates the preferred embodiment of the control assembly of our invention.
- the output voltage e of the strain gauge 35 sensor is compared with the output voltage e, of the pressure sensor 36 in comparator 46 to give an output proportional to the difference between e, and e
- the comparator may be any conventional device to give a signal responsive to the difference of two volt ages, such as a summation resistance network or a differential amplifier or a bridge. With switches 65, 66 and 71 open (see FIG. 2), valves 22 and 23 are closed; manual valves 42, 41, 19b, 45, 27 open. Liquid under pressure is available for and 300 from the pump or the pressure source 24 if used. 7 I I We prefer to employ a differential amplifier-rectifier 46a.
- the inputs to the differential amplifier are the outputs e and e and the outputs of the differential amplifier-rectifier are applied, one to the coil 49 and the other to the coil 50.
- the differential tractive effort of 49 and 50 is, therefore, proportional to the respective signals and magnitudes of e, and e
- the resultant displacement of the spool 56 is, therefore proportional to this difference.
- the orifices at ports 65 and 61 will depend on the aforesaid difference. The rate of addition or removal of fluid from the annulus is thus made proportional to the demand in order to establish the desired level of forces.
- the pump 24 circulates fluid through the pressure regulator valve 29 and via the manual valve 42, line 31, by-pass valve 41, valve 45, manual valve 27 to the accumulator 34 and to the accumulator 30 and via the manual valves 45 and 43 back to the reservoir.
- the pressure regulator 29 is set so that the pressure at 22 is above the highest pressure attained in the annulus during operation. If the pressure source is used during operation to supply pressure to the annulus as described herein, it is established at this higher pressure.
- Fluid also passes from line 31 via the by-pass line 40, valve 41 to the cylinder 4 and via the by-pass line 19a and manual valve 191; to the annulus 18 via line 19.
- Pressure in the accumulators 30, 30a and 34 is adjusted by adjusting the valve 29 and gas pressure in the accumulators and the circulation continued until the strain sensor 35 gives an output 2 measured at the readout 35a (see FIG. 3) which establishes the stress required to support the fraction of the weight of the drill string as described above.
- the output 2, of the pressure gauge 36 at that stress is read at the readout 360 (see FIG. 3). This pressure which corresponds to that stress is exerted in this annulus l8 and in the cylinder 4 and in the accumulators.
- the gas pressure in 34, 30, and 30a is adjusted to hold the required pressure.
- valve 27 may be, but need not be, used.
- a fixed orifice 27a shown in dotted lines, may be positioned in the line connecting the accumulator 34 and line 31.
- the accumulator 34 is connected to the accumulator 30 via valve 34.
- the orifice is of such character and of such time constant that for the period of the heave and the pressure differences which are effective across the orifice the pressure in the accumulator remain substantially constant.
- the pressure in 34 and the output e is thus a reference for the forces on the piston which establishes the stress required to support the desired load as measured by the output e; of the sensor 35.
- the stress sensor output and the voltage e become greater than e the output voltage of the fixed reference sensor 36.
- the tractive effort of solenoid 50 exceeds that of the solenoid 49, and the spool shifts so as to place the port 57 in communication with both ports 60 and 62.
- the annulus discharges through port 60.
- solenoid 70 closes switch 68, activating the solenoid 73 to open valve 23.
- Switch 67 remains open, and valve 22 is closed.
- the pressure in the annulus 18 is vented through 19, valve 20, line 32, and valve 23 to the reservoir 21, to compensate for the increase in pressure in the cylinder 4, until the sum of the forces in the annulus 18 and the cylinder 4 as reported by the sensor output e equals the output e,.
- the switch 67 opens and valve 22 closes, 23 remaining closed.
- the tractive effort of 50 equals that of 49.
- switch 67 closes, energizing the solenoid 71 opening valve 22. Pressure is exerted via valve 22, through 31, port 62 to the annulus 18.
- valve 22 closes as does valve 20 as described above.
- the system thus withdraws fluid from the annulus and accumulator 30a during the period of the heave from the trough to the crest and adds fluid to the system during the period of the heave from the crest to the trough in an amount and under a pressure to maintain the total force on the piston substantially constant.
- the withdrawal or the addition is interrupted when the force in the piston sensed as a stress in the piston rod has reached a predetermined force at which the piston is to be supported. This operation will occur even though the descent of the piston from the drilling operation occurs.
- the criterion for the additional withdrawal of liquid is the deviation of the force from a predetermined norm, which is the force desired to be maintained under the piston under the conditions which it is sought to maintain the piston.
- the gas pressure is adjusted to either increase or decrease the pressure in 30 and 30a as desired; and the system will automatically adjust itself to that pressure as will be evident from what has been described above.
- the motion of the piston with respect to space is a combined motion of the piston due to the heave of thevessel and the advance of the drill during drilling.
- the vessel and the cylinder are subjected to substantially sinusoidal motions which may be out of phase with the piston which is at lesser or greater amplitude, depending on the structure and operation conditions of the system. This will appear from the following:
- the effective area of the piston i.e., the sum of the effective area a of the piston 8 and b the effective area of the piston 13.
- V Volume of the gas in the accumulator when the system is at rest i.e., when 0 0.
- V The volume of the gas in the accumulator at any angle 6 of the cycle.
- the piston motion is influenced by damping considerations and moves out of phase with the motion of the cylinder.
- the phase angle (b depends on the dynamics of the system.
- the cylinder motion with respect to the space is sinusoidal. Being sinusoidal, the spacial displacement of the cylinder at any angle 0 of the cyclic motion may be expressed as y A sin 6 and the displacement of the piston per degree of the cycle at the angle 0 of the cylinder cycle due only to the cyclic action is x A f (6) wheref( 0) is a function of the damping and other conditions of the system which may vary from cycle to cycle and even during any cycle and on wave condition, i.e., frequency and amplitude.
- n is the polytropic gas constant which in the systems under consideration may be taken to be 1 to 1.1 for practical purposes.
- V is the volume of the gas at any angle 0.
- AV is the change in volume in the accumulator at any angle 0 of any quarter of a cylce.
- the consequent pressure on the gas and liquid is where p, is the pressure in the accumulator and the cylinder at V i AV.
- the total change in volume of the gas in the accumulator as a result of one complete cycle is the relative displacement of the piston and cylinder resulting from the advance of the drill into the earth during the cycle.
- the pressure p in the annulus is modulated upon any change in pressure in so that the force remains con stant.
- the pressure in the annulus is increased 50 compensate for the decrease in pressure in the cylinder so as to maintain a substantially constant force on the piston.
- the pressure in the annulus is reduced to compensate for the increase in pressure in the cylinder. The result of this operation is to maintain a substantially constant force on the piston. This is accomplished both when the piston is held at substantially constant position in space or is advanced with respect to space at a constant or modified rate into the earth as in drilling.
- V 100 cu. ft. and y at 6 i.e., A be taken as 5 ft.
- the heave is thus 10 feet.
- z .02 feet per second i.e., a drilling rate of 72 feet per hour.
- This volume is transferred to the accumulator 30, decreasing the volume of the gas.
- the volume of liquid in the cylinder 4 again decreases and the liquid on transfer to the accumulator decreases the volume of the gas by 2.2725 cu. ft. from 102.1825, resulting in a volume of 99.91 cu. ft. and a pressure of 2502.3 psig.
- the pressure in the annulus must be reduced from 2981 psig to 2502.3 psig.
- the compensating pressure p at any angle 6 of any cycle is given by the general formula where 1,0 p b F and m-l is the number of complete cycles traversed and 0 is the angle in degrees traversed in the last incomplete cycle.
- the value of p is at a maximum at the trough when 0 270, i.e. 31r/2.
- the pressure p in the accumulator 30a is at the maximum at the trough in the first cycle since as m-l increases, p, becomes greater and thus p diminishes. 1t drops to 0 when p becomes 2777.8 lbs. so as to by itself establish a force of 180,000 lbs.
- the volume of the gas in the accumulator 30 is 2777.8 2500 (VJ/V1 AND cl V 2500 X 100/2777.8 90 cu. ft.
- the total volume of fluid replaced to the annulus under pressure is during the half cycle from thecrest to the trough in each cycle 2 X .05 (5 .05) .495 cu. ft.
- the drilling lines are again adjusted to adjust the piston in the cylinder.
- the pressures are again establishehd as described above to begin again the new 100-cycle phase.
- weight is added to the drill string,
- the pressures reflect this added weight in order to maintain the desired weight on the bit.
- a stress transducer as the signal to report the integrated forces on the piston system which generates the force on the piston rod. Since this I force is proportional to the sum of the forces in the cylinder 4 and annulus 18, we may use any means for reporting the magnitude of this sum.
- the butput signal may be a voltage which may be added, each multiplied by a factor proportional in one case to a and in the other, proportional to b.
- the multiplied voltages may then be added in a summation network to give the signal e which is employed as above.
- a pneumatic system for maintaining a constant force on the piston by employing a hydraulic-pneumatic system
- the force on each of the cylinders may thus be a pneumatic force exerted from a source of gas pressure.
- the pressures in the annulus 18 and the cylinder 4 may then be modulated by increasing and decreasing them as described above to maintain a constant force on the piston and constant stress on the piston rod.
- an apparatus adapted to be mounted on a vessel subject to heave due to wave action, which apparatus includes a hydraulic cylinder, a first piston and a first piston rod in said cylinder, means to connect a load to said first piston rod, a second hydraulic cylinder and a second piston in said second hydraulic cylinder; said second piston operatively connected to said first piston, separate pneumatic accumulator systems, one each connected to each one of said cylinders for control of the forces exerted on said piston rod, the improvement which comprises means separately to vary the pressure in a first of said accumulator systems, to modulate the pressure in said first accumulator system to compensate for change in pressure in a second accumulator system on imposition of a load on said first piston, whereby the forces on said piston rod are maintained substantially constant.
- said means to modulate said pressure including a source of liquid under pressure and a reservoir at a pressure lower than in one of said accumulator systems, control means for selectively opening a first communication between the said one of said accumulator systems and said source and selectively closing a second communication between said one of said accumulator systems and said reservoir when said first communication is opened and control means for opening said second communication and closing said first communication.
- said control means comprising a signal means responsive to the forces imposed on the first piston rod by said load when said apparatus is mounted on said vessel, during all portions of the heave, means to generate a signal responsive to the forces predetermined to be maintained on the first piston rod by said load, means to generate an error signal responsive to the differences between said first and second-mentioned signals and means selectively to open and selective to close the aforesaid communications responsive to said error signal,
- said communications including pipe connections between each of the cylinders and each accumulator system, a gas connection between each of the accumulator systems and a source of gas under pressure, a pipe connected between one of said cylinders and the accumulator system connected thereto and connected to said source, and another pipe connected between said last-named accumulator system and said reservoir, said means to open and close said communications through said pipes including valves in each of said pipes, means to open a first valve in one of said first-mentioned pipes and means to close a second valve in the other of said pipes when the first valve is opened and means to open said second valve when said first valve is closed.
- control means to open the first valve in said pipe connected to said first accumulator system and said source and to close a second valve in the pipe connecting said first accumulator system to said reservoir system, when The force imposed on said piston rod by said lead when said apparatus is mounted on a vessel, is substantially below a predetermined value and control means to open the second valve and close the first valve when the force exerted on said piston rod is substantially above said predetermined value.
- said control means comprising means to generate a signal responsive to the forces imposed on the first piston rod in said first cylinder, during all portions of the heave, means to generate a signal responsive to the forces predetermined to be maintained on the first piston rod, means to generate an error signal responsive to the differences between said first and second-mentioned signals and means to selectively open and selectively close the aforesaid valves responsive to said error signal.
- said control means comprising a means to generate a signal responsive to the forces imposed on the piston rod during all portions of the heave, means to generate a signal responsive to a predetermined stress to be maintained in the piston rod, means to generate an error signal responsive to the differences between said first and second-mentioned signals, and means to selectively open and selectively close the aforesaid communications responsive to said error signal.
- control means including means selectively to open a first valve in said first pipe means and to close a second valve in said second pipe means when the said force is substantially below a predetermined value and means to close said first valveand open the second valve when the force exerted on said piston is substantially above said predetermined value.
- an apparatus adapted to be mounted on a vessel subject to heave due to wave action, which apparatus includes a first cylinder, a first piston, and a first piston rod in said first cylinder, a second cylinder and a second piston in said second cylinder, said second pis ton in said second cylinder operatively connected to said first piston rod, a fluid pressure source connected to one of said cylinders for control of the forces exerted on said piston rod, which comprises means separately to vary the pressure in one of said cylinders, to modulate the pressure in one of the cylinders to compensate for change in pressure in another of said cylinders, whereby the forces on said piston rod are maintained substantially constant.
- a control means comprising a signal means responsive to the forces imposed on the first piston rod, during all portions of the heave, means to generate a signal responsive to the forces predetermined to be maintained on the first piston rod, means to generate an error signal responsive to the differences between said first and secondmentioned signals and means to adjust the pressure in one of said cylinders responsive to said error signal.
- a plurality of pistons connected to the same piston rod, means to establish separate pressures on said pistons, said means including a cylinder element for each piston, a source of pressure connected to each cylinder, means to increase the pressure in one of said cylinders during that portion only of the heave when the volume under the piston on the other of said cylinders tends to decrease and means to decrease the pressure in said one cylinder during that portion only of the heave when the volume under the piston in the other cylinder tends to increase.
- said means comprising a means to generate a signal responsive to the forces imposed on the piston rod during all portions of the heave, means to generate a signal responsive to a predetermined stress to be maintained in the piston rod, means to generate an error signal responsive to the differences between said first and second-mentioned signals, and means to selectively increase and decrease said pressure responsive to said error signal.
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Abstract
Description
Claims (20)
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US378963A US3871622A (en) | 1972-07-25 | 1973-07-13 | Method and apparatus for the control of a weight suspended from a floating vessel |
NL7405988A NL7405988A (en) | 1973-07-13 | 1974-05-03 | EQUIPMENT FOR INSTALLATION ON A SHIP SUBJECT TO AN INCREASING DEIGN DUE TO WAVE EFFECTS. |
JP5777274A JPS5418643B2 (en) | 1973-07-13 | 1974-05-22 | |
FR7424113A FR2237050B1 (en) | 1973-07-13 | 1974-07-11 | |
GB3129374A GB1482441A (en) | 1973-07-13 | 1974-07-15 | Method and apparatus for the control of a weight suspended from a floating vessel |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00274880A US3841607A (en) | 1972-07-25 | 1972-07-25 | Hydraulic motion compensating apparatus |
US373968A US3866696A (en) | 1972-07-25 | 1973-06-27 | Method and apparatus for the control of a weight suspended from a floating vessel |
US378963A US3871622A (en) | 1972-07-25 | 1973-07-13 | Method and apparatus for the control of a weight suspended from a floating vessel |
Publications (1)
Publication Number | Publication Date |
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US3871622A true US3871622A (en) | 1975-03-18 |
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Application Number | Title | Priority Date | Filing Date |
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US378963A Expired - Lifetime US3871622A (en) | 1972-07-25 | 1973-07-13 | Method and apparatus for the control of a weight suspended from a floating vessel |
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US (1) | US3871622A (en) |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3946559A (en) * | 1973-10-09 | 1976-03-30 | Brown Brothers & Company Limited | Heave compensating devices for marine use |
US4121806A (en) * | 1976-03-18 | 1978-10-24 | Societe Nationale Elf Aquitaine (Production) | Apparatus for compensating variations of distance |
US4215851A (en) * | 1977-01-28 | 1980-08-05 | A/S Strommen Staal | System for active compensation of unwanted relative movements, preferably during loading of cargo |
US4449854A (en) * | 1981-02-12 | 1984-05-22 | Nl Industries, Inc. | Motion compensator system |
US4535972A (en) * | 1983-11-09 | 1985-08-20 | Standard Oil Co. (Indiana) | System to control the vertical movement of a drillstring |
US4759256A (en) * | 1984-04-16 | 1988-07-26 | Nl Industries, Inc. | Tensioner recoil control apparatus |
US4858694A (en) * | 1988-02-16 | 1989-08-22 | Exxon Production Research Company | Heave compensated stabbing and landing tool |
US5894895A (en) * | 1996-11-25 | 1999-04-20 | Welsh; Walter Thomas | Heave compensator for drill ships |
US6691784B1 (en) * | 1999-08-31 | 2004-02-17 | Kvaerner Oil & Gas A.S. | Riser tensioning system |
US20070089882A1 (en) * | 2005-10-21 | 2007-04-26 | Bart Patton | Compensation system for a jacking frame |
US8496409B2 (en) | 2011-02-11 | 2013-07-30 | Vetco Gray Inc. | Marine riser tensioner |
US20140331908A1 (en) * | 2013-05-09 | 2014-11-13 | 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 |
US20180335356A1 (en) * | 2017-05-22 | 2018-11-22 | Schlumberger Technology Corporation | Top drive load measurement weight on bit |
CN110077538A (en) * | 2014-10-24 | 2019-08-02 | 伊特里克公司 | offshore drilling system, vessel and method |
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US3653636A (en) * | 1970-02-09 | 1972-04-04 | Exxon Production Research Co | Wave motion compensation system for suspending well equipment from a floating vessel |
US3718316A (en) * | 1970-09-04 | 1973-02-27 | Vetco Offshore Ind Inc | Hydraulic-pneumatic weight control and compensating apparatus |
US3746329A (en) * | 1971-11-05 | 1973-07-17 | Hughes Tool Co | Piston type shock absorbing and static load supporting drill string apparatus |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3946559A (en) * | 1973-10-09 | 1976-03-30 | Brown Brothers & Company Limited | Heave compensating devices for marine use |
US4121806A (en) * | 1976-03-18 | 1978-10-24 | Societe Nationale Elf Aquitaine (Production) | Apparatus for compensating variations of distance |
US4215851A (en) * | 1977-01-28 | 1980-08-05 | A/S Strommen Staal | System for active compensation of unwanted relative movements, preferably during loading of cargo |
US4449854A (en) * | 1981-02-12 | 1984-05-22 | Nl Industries, Inc. | Motion compensator system |
US4535972A (en) * | 1983-11-09 | 1985-08-20 | Standard Oil Co. (Indiana) | System to control the vertical movement of a drillstring |
US4759256A (en) * | 1984-04-16 | 1988-07-26 | Nl Industries, Inc. | Tensioner recoil control apparatus |
US4858694A (en) * | 1988-02-16 | 1989-08-22 | Exxon Production Research Company | Heave compensated stabbing and landing tool |
US5894895A (en) * | 1996-11-25 | 1999-04-20 | Welsh; Walter Thomas | Heave compensator for drill ships |
US6691784B1 (en) * | 1999-08-31 | 2004-02-17 | Kvaerner Oil & Gas A.S. | Riser tensioning system |
US20070089882A1 (en) * | 2005-10-21 | 2007-04-26 | Bart Patton | Compensation system for a jacking frame |
US7404443B2 (en) * | 2005-10-21 | 2008-07-29 | Schlumberger Technology Corporation | Compensation system for a jacking frame |
US8496409B2 (en) | 2011-02-11 | 2013-07-30 | Vetco Gray Inc. | Marine riser tensioner |
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 |
CN110077538A (en) * | 2014-10-24 | 2019-08-02 | 伊特里克公司 | offshore drilling system, vessel and method |
CN110077538B (en) * | 2014-10-24 | 2021-01-15 | 伊特里克公司 | Offshore drilling system, vessel and method |
US20180335356A1 (en) * | 2017-05-22 | 2018-11-22 | Schlumberger Technology Corporation | Top drive load measurement weight on bit |
US10619418B2 (en) * | 2017-05-22 | 2020-04-14 | Schlumberger Technology Corporation | Top drive load measurement weight on bit |
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Owner name: VETCO GRAY INC., Free format text: MERGER;ASSIGNORS:GRAY TOOL COMPANY, A TX. CORP. (INTO);VETCO OFFSHORE INDUSTRIES, INC., A CORP. (CHANGED TO);REEL/FRAME:004748/0332 Effective date: 19861217 |