US3788074A - Device supplying a working fluid under a determined pressure - Google Patents

Device supplying a working fluid under a determined pressure Download PDF

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US3788074A
US3788074A US00248728A US3788074DA US3788074A US 3788074 A US3788074 A US 3788074A US 00248728 A US00248728 A US 00248728A US 3788074D A US3788074D A US 3788074DA US 3788074 A US3788074 A US 3788074A
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jack
pressure
group
source
path
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A Castela
P Joubert
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IFP Energies Nouvelles IFPEN
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IFP Energies Nouvelles IFPEN
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    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7121—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in series
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • 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
    • Y10S254/00—Implements or apparatus for applying pushing or pulling force
    • Y10S254/90—Cable pulling drum having wave motion responsive actuator for operating drive or rotation retarding means

Definitions

  • ABSTRACT Device for supplying a working fluid under a determined pressure with the use, as pressure source, of an accumulator delivering to a jack an auxiliary fluid under a pressure varying with the displacement of one element (piston or cylinder) of said jack, comprising at least two jacks, one of which has one element articulated to a fixed point and the other element articulated to one element of another jack through a movable articulation member compelled to be displaced along a predetermined path when one of the elements of a jack is displaced with respect to the other.
  • the present invention relates to a device for supplying a working fluid under a determined pressure.
  • gas accumulator such as an oleopneumatic (oil-and-gas) accumulator
  • operations such as off-shore drilling, preformed from a floating installation from which is suspended, for example, an elongated member, such as a drill-string.
  • the drill string has to be kept under a substantially constant tension, so as to be unaffected by the vertical movements of the floating installation.
  • the upper end of the drill string is generally connected to a hook carried by a travelling block which is suspended, by a cable used for handling the drill string, from a stationary crown block, located at the top of a derrick carried by the floating installation.
  • An automatic compensation for the movements of the floating installation is obtained by supplying the jack with fluid under pressure delivered by an oleopneumatic accumulator.
  • volume variations A V, and pressure variations A P of the mass of gas contained in the accumulator, resulting from the vertical movements of the floating installation are defined by the relationship
  • P is the initial gas pressure in the accumulator which is the same as that of the fluid contained in the jack, whereby a tension force can be exerted on the drill string, V, is the volume of gas at the pressure of the accumulator and K a coefficient which V K AV,
  • An object of the present invention is accordingly to suppress or at least, to reduce the drawbacks of the prior devices, by providing a device for keeping a working fluid under a determined pressure, this device being, in particular, suitable for use in apparatuses for keeping an elongated member under a substantially constant tension.
  • the device according to the invention supplying a working fluid under a determined pressure, comprises in combination a source of at least one pressurized fluid, said source containing a gas whose pressure varies with the volume occupied by the gas, and at least one group of jacks, an element of at least one jack of said group being connected through a moveable articulation to an element of at least another jack of said group, the element of at least one jack of said group which is not connected to said moveable articulation being rotatably mounted on a fixed point of the installation, said moveable articulation being compelled to move along a predetermined path, fixed with respect to the installation, said fixed point being so located that the axis of said rotatable jack remains inclined on said path during the rotation of said rotatable jack, at least one jack of said group being fed with pressurized fluid from said source, and at least one jack of said group supplying the working fluid.
  • One of the main advantages of the device according to the invention is to make possible the use of an accumulator of very small volume and of reduced weight and bulk, this accumulator delivering an auxiliary fluid under a variable pressure.
  • FIG. ll diagrammatically shows an apparatus for keeping substantially constant the tension exerted on a drill string suspended from a floating installation, used in offshore drilling operations, this apparatus being equipped with the device according to the invention
  • FIG. 2 illustrates a preferred embodiment of the 'device according to the invention.
  • FIG. 3 diagrammatically illustrates an alternative embodiment of the device of FIG. 2.
  • FIG. 4 diagrammatically shows another embodiment of the apparatus using the device illustrated in FIG. 2, and
  • FIG. diagrammatically illustrates another type of hydraulic accumulator which can be used in the device of the invention and FIGS. 6 and 7 respectively show the variation in the pressure supplied to the main jack and in the tension exerted on the drill column, as a function of the displacements of the piston of this jack, under the action of the vertical movements of the floating-installation.
  • FIG. 1 diagrammatically shows an apparatus for keeping substantially constant the tension applied to an elongated element, such as a drill string suspended from a floating installation, for off-shore drilling operations, this apparatus being equipped with a device according to the invention.
  • an elongated element such as a drill string suspended from a floating installation, for off-shore drilling operations
  • Reference numeral 1 indicates the floating installation topped by a derrick 2.
  • a drill string (not shown) is suspended from the floating installation through handling means constituted, in this particular embodiment, by a hook 3 integral with a travelling block 4 suspended by a cable 5 from a crown block 6.
  • the cable 5, used for handling the drill string passes over a device, which forms no part of the invention, constituted by articulated arms 7 and 8, and pulleys 9 and 10, for preventing the wear of the cable which might result from friction on the crown block 6.
  • the crown block 6 is suspended from the end of the rod of a main jack or supporting jack 11 fixed to the derrick 2 and constituting the means for supporting the drill string.
  • This jack is placed substantially in line with the direction of the vertical movements of the floating installation, i.e. along a substantially vertical direction.
  • the jack 1 1 is connected through a pipe 12 to the device of the invention, indicated as a whole by reference numeral 13.
  • the device 13 keeps under a determined pressure, in the manner indicated hereinafter, the working fluid supplied to the jack 11.
  • the device 13 is connected through a pipe 203 to a pressure accumulator 20 which delivers an auxiliary fluid under a variable pressure, such as an accumulator housing an invariable or constant mass of gas.
  • a pressure accumulator 20 which delivers an auxiliary fluid under a variable pressure, such as an accumulator housing an invariable or constant mass of gas.
  • This accumulator is, for example, as diagrammatically illustrated in FIG. 1, an oleopneumatic accumulator of small capacity.
  • This apparatus exhibits, among others, the advantage of requiring only one supporting jack 11 at the top of the derrick for supporting the means for handling the drill string, so that it is possible, in contrast to the previously used apparatuses, to reduce the top heaviness of the floating installation which reduce the stability of 5 the floating installation, due to the important weight of the jacks which must support very heavy loads.
  • Such an embodiment of apparatus for maintaining constant with sufficient, accuracy the tension exerted on an elongated member requires the use of the device 0 13 maintaining under a determined pressure, the working fluid supplied to the supporting jack 11.
  • the device 13 comprises a first jack 14 having one of its constituting elements, for example its cylinder, articulated at one of its ends about a fixed point 15 on the floating installation, a second jack 16 having one of its constituting elements, for example its cylinder, articulated at one of its ends about a fixed point 17 on the floating installation, the two points 15 and 17 being remote from each other.
  • a first jack 14 having one of its constituting elements, for example its cylinder, articulated at one of its ends about a fixed point 15 on the floating installation
  • a second jack 16 having one of its constituting elements, for example its cylinder, articulated at one of its ends about a fixed point 17 on the floating installation, the two points 15 and 17 being remote from each other.
  • the other elements constituting the jacks 14 and 16, i.e. the rods of their pistons are interconnected and articulated through a movable member 18 which constitutes a common articulating member displaceable along a guiding way 19 determining the path of the movable member 18.
  • the path of the movable member 18 defined by the guiding way 19 has been so determined, with consideration of the locations of the fixed articulation points 15 and 17 of the jacks 14 and 16, that the jacks 14 and 16 are inclined on the guiding way 19, so that at any moment the smaller or acute angles formed by the direction of the guiding way 19 and the directions of each of the jacks 14 and 16 (these angles being respectively indicated as a and B vary in opposite directions relative to each other, when the movable member 18 is displaced along the guiding way 19.
  • the jack 16 is connected through pipe 12 to the supporting jack 11, the cylinders of the jacks 11 and 16 and the pipe 12 being filled by a fluid which may be for example incompressible, such as oil or water, kept under a determined pressure by the device 13.
  • a fluid which may be for example incompressible, such as oil or water, kept under a determined pressure by the device 13.
  • the jack 14 is connected to an accumulator of hydraulic energy 20, which, in this embodiment is an oleopneumatic accumulator having an initial pressure I with a volume V the pressure in this accumulator varying as a function of the relative movements of the elements constituing the jack 14.
  • the device works as follows
  • the jacks l4 and 16 being in a determined position, for example that illustrated in FIG. 1, the pressure P applied by the piston of the jack 16 to the hydraulic working fluid is P P(s/S) (cosa/cosB) member 18 is located at point B on the guide way 19 and a minimum value P for which the movable member is located at point H.
  • the weight of the devices located at the top of the derrick is simultaneously reduced by 30 to 60 percent, so that it does not affect the stability of the floating installation, this being an important factor when this installation is for example a ship, and does not induce dynamic stresses in the derrick.
  • the characteristics of the device 13, i.e. the limit-values of the angles a and B the volume of the accumulator etc., have to be determined in accordance with the conditions of use.
  • an accumulator having a pressure P of 300 bars with a gas volume of 2m", the angle a varying between 20 and 45, the angle ,8 varying between 45 and 20, the variation in the pressure of the auxiliary fluid being 70 bars for an amplitude of the vertical displacements of the floating installation of 4.5 m, the tension in the drill string being kept substantially constant with small variations not exceeding 1.5 percent with respect to a preselected value.
  • FIG. 2 diagrammatically shows a preferred embodiment of the device according to the invention.
  • the forces applied by the jacks l4 and 16 to the movable member, in a direction at right angles to the path T are substantially compensated by two additional jacks 14a and 16a.
  • Each of these jacks has one of its ends articulated about a point on the floating installation (points 1511 and 17a) said jacks being respectively placed in a position symmetrical to that of the jacks l4 and 16 with respect to the path T.
  • the other ends of these jacks are interconnected and articulated to a movable point 18.
  • the jacks 14 and 14a are connected to the accumulator 20, while the jacks 16 and 16a are connected to the pipe 12.
  • FIG. 3 illustrates an alternative embodiment of the device of FIG. 2, wherein the jacks 14, 14a, 16 and 16a are located in two substantially parallel planes, so as to minimize the bulkiness of the device 13.
  • FIG. 4 diagrammatically illustrates an arrangement in series of a number n of devices according to the invention, whereby the volume V, required for the accumulator 20 can be considerably decreased, n devices such as the device 13 illustrated by FIG. 2 have been connected in series, each device being identified by an index (devices 13,, 13 13 13 13 The jacks 14 and 14a of the device 13 are connected to the accumulator 20 while the jacks 16 and 16a are connected to the jacks l4 and 14a of the device 13 ,,etc.
  • the pressure P, at the outlet of the device 13, will be COS d COS 012 COS Di COS 06 cos B cos B cos B,, cos B" and in the case where the devices are identical P P (s/S)" X (cos a/cos B)" so that it is possible to obtain a determined pressure P, which is substantially constant by using an accumulator 20 adaptable to very large pressure variations and hence a very small volume.
  • the device according to the invention may be used with an accumulator of hydraulic energy whose pressure varies in inverse proportion to its volume.
  • an accumulator of hydraulic energy whose pressure varies in inverse proportion to its volume.
  • This description contemplates the utilization of oleopneumatic accumulators, but it will be possible to make use of an accumulator of the type illustrated in FIG. 5.
  • This accumulator consists of a cylinder 21, having a piston 22 slidably mounted therein which delimits two spaces 23 and 24.
  • the first of these spaces 23 is filled with an incompressible auxiliary fluid, such as oil, whereas in the second space is housed a resilient element, for example helical spring 25 which transmits to the fluid, through the intermediary of the piston 22 a pressure which is proportional to its compression rate.
  • an incompressible auxiliary fluid such as oil
  • a resilient element for example helical spring 25 which transmits to the fluid, through the intermediary of the piston 22 a pressure which is proportional to its compression rate.
  • Such an accumulator has the advantage of being less expensive than oleopneumatic accumulators.
  • the guide way of the travel path of the movable point may have any configuration, provided that the ratio of the cosines of the angles a and B varies in inverse proportion to the pressure of the auxiliary fluid when the movable point moves along its path.
  • One of the jacks 14 or 16 might be not articulated about its point of fixation, this jack being then placed in line with the axis of the path of the movable point, provided that the other jack be inclined with respect to the path of this movable point, so that the abovedefined ratio cos a/cos B varies in inverse proportion to the pressure of the auxiliary fluid, when the movable point is displaced along its path.
  • the pressure Pu supplied by the jack 16 and the pressure P in the accumulator are interrelated through the relationship Pu P (s/ s) (Cos oi/cos 3
  • the values of this pressure which correspond to the limit positions (B and H) of the moveable articulation 18 in the guideway 19 (FIG. 1) are respectively Pu P (s/ S)(Cos a /Cos B and Pu P (s/S)(Cos a /Cos B wherein the indexes B and H indicate the particular values of the different parameters Pu, P, a and B of the relation (1), corresponding to the respective positions B and H of the moveable articulation 18.
  • the values Pu and Pa will be selected as a function of the particular conditions of each considered case of utilization.
  • the values of Pu and Pu will for example be determined with consideration of the influence of a system of pulleys interposed between the drill column and the supporting jack 1].
  • Test values are selected for the construction parameters of the regulating system, these parameters being (FIG. 1) the values of d and d (respective distances of the articulation points 15 and 17 from the axis of the guideway 19), the limit values a a and B 8,, of the angles a and B and the values of the respective crosssections s and S of the jacks l4 and 16 respectively.
  • the pressure P in this accumulator varies substantially according to a physical law having the form PV" constant, wherein K is a coefficient whose value depends, in particular, on the nature of the pressurized gas and V is the volume of gas at the pressure P in the accumulator 20, applied to the piston of the jack 14.
  • V and V are the values of the volume of pressurized gas when the position of the moveable articulation 18 is respectively at point B and point H of the guideway 19.
  • V V Letting V V, be defined as AV there results from the relation (5)
  • the value of AV is known, since it is equal to the product of the cross-section s of the jack 14 by the stroke of its piston when the moveable articulation 18 is displaced between points B and H, V being the minimum value of the volume of pressurized gas.
  • the nominal volume of the accumulator 20 can thus be determined since the values of P and P have already been determined (the calibrating pressure of this accumulator is substantially equal to P,,).
  • each value of h corresponds a well defined position of the moveable articulation 16 along the guideway 19, i.e. well defined values for the angles a and B, when the values B B d and S have been fixed.
  • the displacement of the piston of jack 11 from its lowermost position corresponds to a determined variation of the volume of hydraulic fluid in the cylinder of jack 16 through the pipe 12 (at any moment the displacements of the pistons of the jacks 11 and 16 from their initial position (lowest position), represent the same percentage of their maximal stroke).
  • the graphs of FIGS. 6 and 7 show respectively the variations of Pu (expressed in kglcm and T (expressed in tons), as a function of the stroke h (expressed in meters) of the piston of jack 11, obtained in accordance with the following data horizontal distance between the axes of pulleys 9 and 10 and the axis of pulley 6 when the latter is in its lowermost position 3.3 meters,
  • the cable 5 forms 12 turns between the pulley 6 and the moveable block or pulley system 4.
  • a device for supplying a working fluid under a determined pressure to a chamber means of variable volume comprising in combination a source of at least one pressurized fluid, said source containing a gas whose pressure varies with the volume occupied by the gas, and at least one group of jacks, an element of at least one jack of said group being connected through a moveable articulation to an element of at least another jack of said group, an element of at least one jack of said group which is not connected to said moveable articulation being rotatably mounted on a fixed point of an installation, said moveable articulation being compelled to move along a predetermined path, fixed with respect to the installation, said fixed point being so located that the axis of said jack having the rotatably mounted element remains inclined on said path during the rotation of the rotatably mounted element of said jack, at least one jack of said group being fed with pressurized fluid from said source, and at least one jack of said group supplying the working fluid to the chamber means of variable volume under
  • a device for supply supplying working fluid under a determined pressure to a chamber means of variable volume comprising in combination a source of at least one pressurized fluid, said source containing a gas whose pressure varies with the volume occupied by the gas, and at least one group of jacks, an element of at least one jack of said group being connected through a moveable articulation to an element of at least another jack of said group, an element of at least one jack of said group which is not connected to said moveable articulation being rotatably mounted on a fixed point of an installation, said moveable articulation being compelled to move along a predetermined path, fixed with respect to the installation, said fixed point being so located that the axis of said jack having the rotatably mounted element remains inclined on said path during the rotation of the rotatably mounted element of said jack, at least one jack of said group being fed with pressurized fluid from said source, and at least one jack of said group supplying the working fluid to the chamber means of variable volume under a pressure different
  • a device wherein said path is rectilinear.
  • a device comprising at least one jack having one element connected at one end to said moveable articulation and another element connected at one end to a fixed point of the installation.
  • a device wherein said moveable articulation is slidable along a fixed guide way defining said path.
  • a device wherein said source is constituted by a gas accumulator.
  • a device wherein said source consists of an oleopneumatic accumulator housing a constant mass of gas.
  • a device for compressing an hydraulic working fluid under a determined pressure in a chamber means having a variable volume comprising at least one accumulator containing a gas under pressure and connected to a regulating system including at least one regulating jack mounted for pivotal movement about a fixed point and connected to an articulated member moveable along a predetermined path, said pivotable regulating jack remaining inclined with respect to said path during its pivotal movement in which the regulating system supplies the chamber means through an auxiliary system, said auxiliary system having at least one jack connected to the chamber means through a duct containing the compressed working fluid, said jack of said auxiliary system being connected to said pivotable regulating jack via said articulated member and providing a relative positional arrangement of said pivotable regulating jack and said jack of said auxiliary system with respect to said predetermined path such that the ratio cos a/cos [3 of the values of the cosines of the acute angles a and B of said pivotable regulating jack and said jack of said auxiliary system, respectively, with respect to said predetermined pre

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  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
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  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
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US00248728A 1971-05-03 1972-04-28 Device supplying a working fluid under a determined pressure Expired - Lifetime US3788074A (en)

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FR7115911A FR2147771B1 (enrdf_load_stackoverflow) 1971-05-03 1971-05-03

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US00248727A Expired - Lifetime US3788073A (en) 1971-05-03 1972-04-28 Apparatus for applying a substantially constant tension to an elongated member connected to an installation subject to alternating movements

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US (2) US3788074A (enrdf_load_stackoverflow)
JP (2) JPS5429961B1 (enrdf_load_stackoverflow)
CA (2) CA956922A (enrdf_load_stackoverflow)
DE (2) DE2221654B2 (enrdf_load_stackoverflow)
DK (2) DK135865B (enrdf_load_stackoverflow)
ES (1) ES402339A1 (enrdf_load_stackoverflow)
FR (1) FR2147771B1 (enrdf_load_stackoverflow)
GB (2) GB1394202A (enrdf_load_stackoverflow)
IT (1) IT954956B (enrdf_load_stackoverflow)
NL (2) NL149253B (enrdf_load_stackoverflow)
NO (2) NO131617C (enrdf_load_stackoverflow)
SE (2) SE393429B (enrdf_load_stackoverflow)
SU (1) SU633496A3 (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3948486A (en) * 1973-09-07 1976-04-06 Institut Francaise Du Petrole, Des Carburants Et Lubrifiants New device for applying a determined force to an element connected to an installation subjected to alternating movements
DE3735236A1 (de) * 1987-10-17 1989-04-27 Teves Gmbh Alfred Einrichtung zur anpassung der kennlinie eines hydrospeichers an die kennlinie eines verbrauchers
US5160219A (en) * 1991-01-15 1992-11-03 Ltv Energy Products Company Variable spring rate riser tensioner system
US5454408A (en) * 1993-08-11 1995-10-03 Thermo Power Corporation Variable-volume storage and dispensing apparatus for compressed natural gas
US5482406A (en) * 1993-04-15 1996-01-09 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US5520369A (en) * 1984-12-28 1996-05-28 Institut Francais Du Petrole Method and device for withdrawing an element fastened to a mobile installation from the influence of the movements of this installation
US5628586A (en) * 1995-06-23 1997-05-13 Continental Emsco Company Elastomeric riser tensioner system
US5641248A (en) * 1993-04-15 1997-06-24 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US6585455B1 (en) 1992-08-18 2003-07-01 Shell Oil Company Rocker arm marine tensioning system
US20150008382A1 (en) * 2013-07-03 2015-01-08 Cameron International Corporation Motion Compensation System
USD835678S1 (en) * 2017-07-08 2018-12-11 Daqing Dannuo Petroleum Technology Development Co., Ltd. Pumping unit
US10253579B2 (en) * 2016-12-19 2019-04-09 IFP Energies Nouvelles Motion compensation system for a load hanging from a mobile unit with a main cylinder and a secondary cylinder
US10359093B2 (en) * 2014-09-16 2019-07-23 IFP Energies Nouvelles System for controlling the movement of a load

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US3791628A (en) * 1972-07-26 1974-02-12 Ocean Science & Eng Motion compensated crown block system
US3943868A (en) * 1974-06-13 1976-03-16 Global Marine Inc. Heave compensation apparatus for a marine mining vessel
GB2005751B (en) * 1977-09-05 1982-04-21 Vickers Ltd Tensioning of members
US4688764A (en) * 1984-10-31 1987-08-25 Nl Industries, Inc. Crown block compensator
FR2575452B1 (fr) * 1984-12-28 1987-11-13 Inst Francais Du Petrole Methode et dispositif pour soustraire un element accroche a une installation mobile aux mouvements de cette installation
US4867418A (en) * 1986-03-03 1989-09-19 N.L. Industries, Inc. Apparatus for increasing the load handling capability of support and manipulating equipment
US4739584A (en) * 1986-10-23 1988-04-26 Peter Zellman Garage door locking mechanism
US20110011320A1 (en) * 2009-07-15 2011-01-20 My Technologies, L.L.C. Riser technology

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US3163005A (en) * 1962-11-19 1964-12-29 Jersey Prod Res Co Apparatus for use on floating drilling platforms
US3208728A (en) * 1962-11-19 1965-09-28 Exxon Production Research Co Apparatus for use on floating drilling platforms
US3687205A (en) * 1970-10-28 1972-08-29 Gulf Research Development Co Floating rig motion compensator

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US3163005A (en) * 1962-11-19 1964-12-29 Jersey Prod Res Co Apparatus for use on floating drilling platforms
US3208728A (en) * 1962-11-19 1965-09-28 Exxon Production Research Co Apparatus for use on floating drilling platforms
US3687205A (en) * 1970-10-28 1972-08-29 Gulf Research Development Co Floating rig motion compensator

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3948486A (en) * 1973-09-07 1976-04-06 Institut Francaise Du Petrole, Des Carburants Et Lubrifiants New device for applying a determined force to an element connected to an installation subjected to alternating movements
US5520369A (en) * 1984-12-28 1996-05-28 Institut Francais Du Petrole Method and device for withdrawing an element fastened to a mobile installation from the influence of the movements of this installation
DE3735236A1 (de) * 1987-10-17 1989-04-27 Teves Gmbh Alfred Einrichtung zur anpassung der kennlinie eines hydrospeichers an die kennlinie eines verbrauchers
US5160219A (en) * 1991-01-15 1992-11-03 Ltv Energy Products Company Variable spring rate riser tensioner system
US6585455B1 (en) 1992-08-18 2003-07-01 Shell Oil Company Rocker arm marine tensioning system
US5482406A (en) * 1993-04-15 1996-01-09 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US5641248A (en) * 1993-04-15 1997-06-24 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US5454408A (en) * 1993-08-11 1995-10-03 Thermo Power Corporation Variable-volume storage and dispensing apparatus for compressed natural gas
US5628586A (en) * 1995-06-23 1997-05-13 Continental Emsco Company Elastomeric riser tensioner system
US20150008382A1 (en) * 2013-07-03 2015-01-08 Cameron International Corporation Motion Compensation System
US9784051B2 (en) * 2013-07-03 2017-10-10 Cameron International Corporation Motion compensation system
US10359093B2 (en) * 2014-09-16 2019-07-23 IFP Energies Nouvelles System for controlling the movement of a load
US10253579B2 (en) * 2016-12-19 2019-04-09 IFP Energies Nouvelles Motion compensation system for a load hanging from a mobile unit with a main cylinder and a secondary cylinder
USD835678S1 (en) * 2017-07-08 2018-12-11 Daqing Dannuo Petroleum Technology Development Co., Ltd. Pumping unit

Also Published As

Publication number Publication date
GB1394202A (en) 1975-05-14
DE2221700B2 (de) 1973-09-27
ES402339A1 (es) 1975-11-01
NO131616C (enrdf_load_stackoverflow) 1975-06-25
US3788073A (en) 1974-01-29
DE2221654C3 (enrdf_load_stackoverflow) 1974-04-18
NO131617C (enrdf_load_stackoverflow) 1975-06-25
JPS5429961B1 (enrdf_load_stackoverflow) 1979-09-27
FR2147771A1 (enrdf_load_stackoverflow) 1973-03-16
SU633496A3 (ru) 1978-11-15
NO131617B (enrdf_load_stackoverflow) 1975-03-17
IT954956B (it) 1973-09-15
CA956922A (en) 1974-10-29
DE2221654B2 (de) 1973-09-06
FR2147771B1 (enrdf_load_stackoverflow) 1974-05-31
DK135866B (da) 1977-07-04
NL149253B (nl) 1976-04-15
DE2221700A1 (de) 1972-11-16
JPS554913B1 (enrdf_load_stackoverflow) 1980-02-01
NL7205929A (enrdf_load_stackoverflow) 1972-11-07
DK135866C (enrdf_load_stackoverflow) 1977-12-05
NL7205930A (enrdf_load_stackoverflow) 1972-11-07
GB1394201A (en) 1975-05-14
DK135865B (da) 1977-07-04
SE393430B (sv) 1977-05-09
NO131616B (enrdf_load_stackoverflow) 1975-03-17
DE2221700C3 (de) 1974-04-25
CA957360A (en) 1974-11-05
NL149259B (nl) 1976-04-15
DK135865C (enrdf_load_stackoverflow) 1977-11-28
SE393429B (sv) 1977-05-09
DE2221654A1 (de) 1972-11-30

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