EP0323772B1 - Stabilisator für einen Bohrstrang, der zur Rotation einkuppelbar ist - Google Patents

Stabilisator für einen Bohrstrang, der zur Rotation einkuppelbar ist Download PDF

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Publication number
EP0323772B1
EP0323772B1 EP88403113A EP88403113A EP0323772B1 EP 0323772 B1 EP0323772 B1 EP 0323772B1 EP 88403113 A EP88403113 A EP 88403113A EP 88403113 A EP88403113 A EP 88403113A EP 0323772 B1 EP0323772 B1 EP 0323772B1
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EP
European Patent Office
Prior art keywords
clutch
accordance
rotation
discs
jacket
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88403113A
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English (en)
French (fr)
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EP0323772A1 (de
Inventor
Benoît Amaudric du Chaffaut
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IFP Energies Nouvelles IFPEN
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IFP Energies Nouvelles IFPEN
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Publication of EP0323772A1 publication Critical patent/EP0323772A1/de
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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
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/10—Wear protectors; Centralising devices, e.g. stabilisers
    • E21B17/1057—Centralising devices with rollers or with a relatively rotating sleeve
    • E21B17/1064—Pipes or rods with a relatively rotating sleeve

Definitions

  • the present invention relates to a centering device which can be used in particular for centering in a well a drill string consisting of a drill bit and drill collars which surmount it.
  • the transverse force applied to the rods is in principle zero, if one neglects that due to the buckling of the drill collars, as well as the dynamic effects due to the eccentricities, even weak. In general there is no preferred direction for these possible lateral forces and it can be considered that they cancel out overall, at least for their effect on the deflection.
  • the body of the rod bores its own housing in which the larger diameter equipment located below (stabilizers, tool, etc.) cannot pass during the ascent operation.
  • the keyhole designated by the term “key-seat” which also occurs in the upper part of the lining where these are the connector connectors, or in term “tool” -joints ", which jam.
  • the blades are generally constituted by rubber pads secured to a jacket of the same material in which the lining can rotate freely. Lubrication is ensured by mud (and spoil ).
  • the longitudinal translation of the liner on the body is possible between two annular stops, the lower stop being provided with teeth intended to block the rotation if necessary (over-drilling or jamming during the ascent).
  • it seems that the use of these tools is not very widespread, probably because of their short lifespan.
  • Such a device supposes the complete stop of rotation before engaging the teeth, failing which, it is subjected to strong mechanical stresses which are always harmful.
  • the present invention provides a centering device which does not generally rotate with the rods, therefore capable of ensuring effective centering, and which nevertheless spares the possibility of reaming, by driving the blades in rotation, but limiting it to the only circumstances where this is really necessary, that is to say the jamming of the drill string in the longitudinal direction.
  • the device according to the invention avoids the drawbacks mentioned above.
  • the present invention relates to a device comprising at least one centering member relative to which said lining can rotate around its axis.
  • This device is characterized in particular in that it comprises means for driving said member in rotation, consisting of a friction clutch.
  • This clutch could in particular be a disc, cone or drum clutch.
  • This clutch may include several discs or cones, some of which will be integral in rotation with said centering member and others with said lining, these discs or cones being nested one inside the other.
  • the device according to the invention may include elastic means for positioning the different discs relative to one another.
  • the device according to the invention may include dog clutch means.
  • the device according to the invention may include means for controlling the progressive drive means in rotation, these control means being actuated from a certain value, threshold of the difference between the axial force to which said subject is subjected. lining and the one to which said member is subjected.
  • control means may include return means such as springs.
  • the control means of said drive means may be assisted by a pressurized fluid.
  • control means can be mixed hydraulic and mechanical.
  • FIG. 4 illustrates an embodiment of a device according to the invention.
  • the centering device 1 comprises a certain number of straight blades 2, that is to say parallel to the axis 3 of the rods, or helical blades 4 (cf. fig. 2), similar to those which equip conventional stabilizers and which are inscribed in a volume of revolution whose maximum diameter is equal to or slightly less than that of the borehole.
  • Their ends 5 are profiled in the form of pads, or bevelled, so as to facilitate their longitudinal sliding on the walls of the well.
  • These blades 2 are mounted on a cylindrical jacket 6 inside which the tubular body 7 of the device can rotate freely, at least as long as the longitudinal friction of the blades against the walls 8 (cf. fig. 2) of the hole remains limited.
  • the rotation of the tubular body 7 in the jacket 6 carrying the blades, or centralizing members, is facilitated by the presence of bearings 9, 10 and stops 11, 12 with rollers, rollers, needles or balls, lubricated by a suitable fluid (oil or grease) contained in a sealed manner in the space 13 between the jacket 6 and the body 7.
  • bearings and stops are designed to allow the translation of the jacket on the body without preventing rotation.
  • a device for balancing the pressures between the lubricant and the drilling fluid present outside the jacket 6 completes the seal by limiting the pressure differences at the joints and by allowing variations in the volume of the lubricant with the temperature. .
  • Such a device can be a membrane or piston, as shown in FIG. 10 under the reference 14.
  • This device 14 comprises a piston 15 which slides in a cylinder 16. The stroke of the piston is limited by two stops 17 and 18.
  • One face 19 of the piston 15 is in contact with the drilling fluid, the other face 20 is in contact with the lubrication fluid.
  • This pressure balancing device can be modified by inserting between the piston 15 and the stopper 18 a helical spring in compression which will maintain a slight overpressure between the lubricant and the mud outside, so as to protect the seals from sealing against any invasion of mud.
  • the rotary drive of the blades occurs as soon as their longitudinal friction against the walls of the hole, in one direction or the other, causes by relative axial displacement of the tubular body 7 in the jacket 6 a sufficient compression of one of the two return springs 21 or 22 ( Figure 4). Due to the approximation of the clutch stop 25 secured to the tubular body 7 and the clutch stop 26 or 27 respectively secured to the jacket 6, the associated series of brake discs 23 and 24 respectively is then tightened, gradually causing the rotation of the blades 2. This rotation of the blades will be done initially with sliding of the clutch discs. If during this phase the blades have cleared the obstruction which is at the origin of the longitudinal friction, then this ceases and the system returns to its position of equilibrium due to the action of the return springs 21 and 22 .
  • the references 28 and 29 in FIG. 4 respectively designate support stops or more simply the supports of the springs 21 and 22, these supports being integral with the tubular body 7.
  • the other supports are integral with the cylindrical jacket 6.
  • the supports are made on rotating support stops referenced 11 and 12 respectively in FIG. 4.
  • the progressiveness of the transmission of the torque by the discs can be favored by the presence of a lubricating fluid.
  • FIG. 5 represents a centering device equipped with dogs.
  • references 30 and 31 designate two series of doggies which cooperate with one another to form a first pair of doggies.
  • References 32 and 33 denote two other series of dog dogs which cooperate with each other to form a second pair of dog dogs.
  • Each of the other series 31 and 33 respectively of each of the pairs of dogs is secured to a support stop (stops 34 and 35 respectively) which is itself secured in rotation to the jacket 6.
  • the stops carrying dogs and which are integral in rotation with the shirt 6 can move in the direction of the axis of the shirt.
  • Return springs 36 and 37 control the pressure exerted on the clutch discs and do not allow clutching unless a predetermined value of this pressure is exceeded.
  • the different discs can be isolated from each other by leaf springs, such as those shown in FIG. 6 and which carry the references 38 and 39.
  • the leaf springs 38 separate the discs 40 integral in rotation with the tubular body 41 and the leaf springs 39 separate the discs 42 integral in rotation with the jacket 43.
  • the discs 40 and 42 are respectively integral in rotation with the tubular body 41 and the jacket 43 by grooves 44 and 45 respectively.
  • the sealed space 13 may be limited by seals 49 fixed relative to the tubular body and which cooperate with cylindrical seats 50 integral with the jacket. Of course the size of the seats is sufficient to allow the shirt to perform extreme strokes without interrupting the sealing function.
  • the purpose of the braking discs is to synchronize the respective rotational speeds of the body, which can rotate for example at 150 revolutions / minute, and of the blades 2, which are in principle stationary, before the dogs 30, 31 or 32 engage. , 33. They are movable in axial translation and secured in rotation with the body or the jacket, by means of lugs 51 which are positioned in grooves 45 hollowed out for this purpose (cf. FIG. 6).
  • This function can be performed by any other suitable device, friction cones for example, provided however that the transmission of the torque to the blades is sufficiently progressive and that it does not produce excessive wear or overheating.
  • the aim is to drive the blades if necessary with a sufficiently slow rotation to be able to free the centering device with the minimum erosion of the wall of the hole.
  • FIG. 7 represents a device according to the invention which comprises a set of clutch discs 53 and a clutch system or pair of clutch dogs 54.
  • the clutch of the rotation is produced, for example, when the lining 52 rises, in the event of jamming in traction by landslide 56 of the walls above the centralizer (case of FIG. 9), or else when descending, if the hole 57 has narrowed, for example due to significant filtration deposits 58, or even in drilling if the blades 2 penetrate deeply into excessively soft walls (case of FIG. 8).
  • the centering device then temporarily turns into a reamer and is quickly released by rotation to resume its primary function (see fig. 4, 5, 7 or 10).
  • the jacket 6 carrying the blades 2 is held in the middle position by the two return springs 21 and 22 with sufficient clearance in each of the two directions to avoid inadvertent engagement of the rotation by possible vibrations. packing.
  • the stiffness of the springs will be adapted to the composition of the drill string. In particular, it will be important to avoid that all the centralizers employed can support too much of the weight on the tool without starting to rotate, which would happen with springs that are too stiff. Conversely, too soft springs would imply a permanent bore and the centering would quickly be ineffective.
  • the entire device is sized to withstand the forces and to axial and lateral shocks normally applied to the drill string where it is inserted.
  • the tool body may have the same mechanical characteristics as the rods or drill collars between which it is placed. Its internal diameter, if it must be different from that of neighboring rods, will not create excessive pressure drop in the flow of drilling fluid.
  • the connection with the neighboring rods can be ensured by suitable threads and sealing surfaces.
  • FIG. 10 represents a particularly interesting embodiment, according to which there are two pairs of dogs 59 and 60 intended respectively for the two directions of axial friction of the centering device in the well.
  • the sealing of the space 62 delimited by the outer wall of the tubular body 63 and the jacket 6 is done by seals 65 which cooperate directly with a seat 66 constituted by the outer surface of a cylinder secured to the tubular body, while in the embodiment of FIG. 5 the seal 49 cooperates with the outer surface of a cylinder secured to the jacket 6.
  • the springs 67 control the compression pressure on the discs, while the springs 68 position the jacket relative to the tubular body in the absence of axial friction force.
  • the hooks 69 limit the travel of the stops 70 integral in rotation with the jacket.
  • the plug 71 makes it possible to empty or fill the space 62 with a fluid lubricating the bearings 72 and 73 and the discs 61.
  • the engagement centralizer achieves a progressive rotation of the blades and triggered only by a longitudinal friction of the device on the wall of the hole. This friction being ill-defined, it is conceivable that under particular operating conditions, the machine remains for significant periods in an intermediate position where the clutch of the rotation is not yet achieved, but where the friction surfaces undergo already friction generating heat and wear, which can be harmful in the long run.
  • the rotation of the body 74 in the jacket 75 carrying the blades 76 is used to actuate, by means of a gear speed multiplier 77, an oil micro-pump 78 integral with the tubular body 74.
  • This micro-pump fills a chamber 79 at high pressure and with variable volume of oil.
  • the pressure in this chamber is maintained at a predetermined value by a non-return device 80 and by a calibrated valve 81 which bypasses the flow rate of the pump once the selected pressure is reached.
  • the longitudinal displacement of the jacket 75 relative to the body 74 is always controlled by return springs 82 and 83 which cooperate with axial stops 84, 85 and 86 some of which may be rotating, this is the case of the stops 85 and 86 .
  • a threshold value of the abovementioned longitudinal displacement is fixed by the geometrical characteristics of a hydraulic open-close system with free tilting, or slide valve 87, which, once reached the displacement threshold, abruptly puts the chamber 79 at high pressure into communication with a set of jacks 88 pressing the clutch surfaces 89 and 90.
  • a drum clutch In the case of FIG. 11, a drum clutch.
  • the clutch surface 90 is integral in rotation with the jacket 75, but movable in axial translation. This is obtained by the use of a sleeve 96 comprising grooves 97 which cooperate with grooves 98 arranged in the jacket 75. Springs 99 and 100 make it possible to maintain the sleeve 96 in an intermediate position in the absence of clutch .
  • the slide valve 87 is controlled by an arm 91 comprising a roller wheel 92 which cooperates with a groove 93.
  • a displacement axial of the jacket 75 relative to the body 74 from the equilibrium position shown in FIG. 11 causes the arm 91 to retract into the slide valve 87 and causes the actuators 88 to be activated.
  • the duration of the clutch slip period 89, 90 is thus reduced to a minimum which only depends on the filling time of the cylinders 88.
  • the contact pressure of the clutch surfaces 89 and 90 is fixed and depends only on of the valve 80 calibration.
  • the slide valve 87 opens the clutch cylinders 88 on the annular space 94, thus allowing disengagement, and closes the high pressure chamber 79 which can therefore be recharged by the rotation of the body in the jacket for a next sequence.
  • the fluid supply to the pump 78 takes place from the annular space 94.
  • FIG. 12 schematically shows a device comprising a cone clutch 95.
  • the centering device proposed in the present invention can be considered as a "self-supporting" rotation bearing by the lining 52, its role is to cancel the tangential component of the contact reactions of the rods and the wall of the hole, whatever the speed of rotation of the gasket, which makes it possible to considerably reduce the losses in torque and the violent transverse oscillations.
  • the longitudinal friction remains limited, it is likely that the arrangement of a few of these centralizers, just above the drill bit and in the last lengths of the lining, will provide a smooth drilling, therefore more efficient, a better calibrated hole and a more regular trajectory than with conventional stabilizers.
  • the rotating clutch of the centering device will gradually bring the lining and the centering device back to the conventional bore configuration.
  • the blades are spiraled to the right, so, on the one hand, that the support on the wall is distributed over a greater part of the circumference, and, on the other hand, that all beginning of rotation of the blades during drilling makes them advance by slow screwing before starting to erode the wall.
  • the profile of the blades will preferably be as they are written in a sphere or an ovoid, so that the angular difference between the axis of the well and the axis rods, introduced for example by an elbow, is produced without parasitic bending moment. This is the case of the blades 55 shown in FIG. 3.
  • the blades will be inscribed in a relatively long cylinder, producing an embedding which will limit the bending, as is the case of the blades 4 of FIG. 2.
  • the centering device therefore naturally finds its place in the bottom assembly used for inclined drilling, where one needs to create punctual supports of the drill-rods on the wall to maintain or modify the trajectory, without these supports causing excessive losses in torque or repeated shocks which translate with conventional stabilizers by uncontrollable parasitic enlargements and deviations, poor advancement and abnormal wear of the equipment. In vertical drilling, it will limit losses of rotational power and undesirable deviations, by achieving a real stabilization of the bottom assembly.
  • the drill mounts would then be lighter but more numerous, and ultimately would disappear completely in favor of simple stems.
  • the advantage of this arrangement is to limit the weight of the drill string, therefore to achieve a saving in lifting power, and to reduce the diameters at the bottom of the hole, which among other advantages would allow greater speed of maneuver vis- opposite pistoning.
  • the centralizers can also be used in the upper parts (stressed in tension) of a drilling rig for limit the friction of the rods on the walls, which is particularly important in the curved parts of the well (build-up), to avoid the formation of "key-seats", and in the tubed parts, sensitive to abrasion of the joints of rods (tool-joints).

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Claims (12)

1. Zentriervorrichtung, insbesondere verwendbar für die Zentrierung einer Bohrgarnitur bzw. -ausrüstung, mit wenigstens einem Zentrierorgan, relativ zu welchem diese Garnitur sich drehen kann, dadurch gekennzeichnet, daß sie Drehantriebsmittel (23, 24, 53, 61) dieses Organs (6) umfaßt, die aus einer Reibkupplung (23, 24, 53, 61) bestehen.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß diese Kupplung eine Scheibenkupplung (23, 24, 53, 61), Kegelkupplung oder Trommelkupplung ist.
3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß diese Kupplung mehrere Scheiben (23, 24, 53, 61) oder Kegel umfaßt, von denen gewisse drehfest bezüglich dieses Zentrierorgans (6) und andere drehfest mit dieser Garnitur sind, wobei diese Scheiben oder Kegel dachziegelartig ineinander vorgesehen sind.
4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß sie elastische Mittel (38, 39) zum Positionieren der verschiedenen Scheiben bezüglich einander umfaßt.
5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß sie Klauenkupplungsmittel (30, 31, 32, 33, 54, 59, 60) umfaßt.
6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie Mittel (21, 22, 68) zum Steuern dieser Drehantriebsmittel umfaßt, wobei diese Steuermittel ausgehend von einem gewissen Schwellenwert der Differenz zwischen der Axialkraft, der diese Garnitur (52) ausgesetzt ist und der, der dieses Organ (6) ausgesetzt ist, betätigt werden.
7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß diese Steuermittel elastische Rückstellmittel (21, 22, 68) umfassen.
8. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß sie Lager und Drucklager mit Rollen, Walzen, Nadeln oder Kugeln umfaßt.
9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, daß diese Lager und Drucklager geschmiert sind durch ein Fluid, welches dicht zwischen diesem Zentrierorgan und dieser Garnitur enthalten ist.
10. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß diese Scheiben in einem Schmierfluid baden, welches die Progressivität dieser Kupplung erleichtert.
11. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie Mittel zum Steuern dieser Drehantriebsmittel umfaßt, wobei diese Steuermittel gemischt, nämlich von hydraulischer und mechanischer Bauart, sind.
12. Vorrichtung nach Anspruch 11, dadurch gekennzeichnet, daß diese gemischten Steuermittel eine hydraulische Pumpe (78), ein Übersetzergetriebe (77), eine Hochdruckkammer (79), einen Absperrschieber, (87) und Stellzylinder (88) umfassen.
EP88403113A 1987-12-23 1988-12-08 Stabilisator für einen Bohrstrang, der zur Rotation einkuppelbar ist Expired - Lifetime EP0323772B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8718088A FR2625253A1 (fr) 1987-12-23 1987-12-23 Centreur embrayable en rotation notamment pour garniture de forage
FR8718088 1987-12-23

Publications (2)

Publication Number Publication Date
EP0323772A1 EP0323772A1 (de) 1989-07-12
EP0323772B1 true EP0323772B1 (de) 1992-03-18

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ID=9358258

Family Applications (1)

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EP88403113A Expired - Lifetime EP0323772B1 (de) 1987-12-23 1988-12-08 Stabilisator für einen Bohrstrang, der zur Rotation einkuppelbar ist

Country Status (5)

Country Link
US (1) US4989679A (de)
EP (1) EP0323772B1 (de)
DE (1) DE3869373D1 (de)
FR (1) FR2625253A1 (de)
NO (1) NO885690L (de)

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GB8914882D0 (en) * 1989-06-29 1989-08-23 Red Baron Oil Tools Rental Drill string component
US5226493A (en) * 1992-06-05 1993-07-13 Dril-Quip, Inc. Well apparatus
GB0006218D0 (en) * 2000-03-16 2000-05-03 Rastegar Gholam H Torque reducing drillstring component
WO2001071149A2 (en) * 2000-03-22 2001-09-27 Rotary Drilling Technology, Llc. Drill bit stabilizer and method of use
US6622803B2 (en) 2000-03-22 2003-09-23 Rotary Drilling Technology, Llc Stabilizer for use in a drill string
CA2413539C (en) * 2000-06-21 2009-01-13 Derek Frederick Herrera Centraliser
FR2812338B1 (fr) * 2000-07-25 2002-11-08 Total Fina Elf S A Procede et dispositif de forage rotary d'un puits
CA2351978C (en) * 2001-06-28 2006-03-14 Halliburton Energy Services, Inc. Drilling direction control device
FR2843418B1 (fr) * 2002-08-08 2005-12-16 Smf Internat Dispositif stabilisateur d'un train de tiges de forage rotatif a frottement reduit
GB0227630D0 (en) * 2002-11-27 2003-01-08 Smart Stabilizer Systems Ltd Steerable drill bit arrangement
NO346112B1 (en) 2008-08-29 2022-02-28 Statoil Petroleum As Drill pipe protector assembly
US8774697B2 (en) 2011-07-29 2014-07-08 Eastman Kodak Company Electrophotographic printer and transitional cleaning system
US20130319769A1 (en) * 2012-06-04 2013-12-05 Edward D. Scott Wellbore reaming tool having locking clutch for drill out after running wellbore tubulars
US9399894B2 (en) * 2013-03-14 2016-07-26 Premier Advanced Solution Technologies, Llc Friction reducing downhole assemblies
US10669788B2 (en) * 2015-01-12 2020-06-02 Schlumberger Technology Corporation Active stabilization
EP3279426A1 (de) * 2016-08-05 2018-02-07 Shell Internationale Research Maatschappij B.V. Verfahren und system zur hemmung von torsionsschwingungen in einer bohranordnung
US11512540B2 (en) * 2019-10-31 2022-11-29 Schlumberger Technology Corporation Methods for mitigating whirl

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Also Published As

Publication number Publication date
US4989679A (en) 1991-02-05
NO885690D0 (no) 1988-12-21
EP0323772A1 (de) 1989-07-12
NO885690L (no) 1989-06-26
FR2625253A1 (fr) 1989-06-30
DE3869373D1 (de) 1992-04-23

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