Source: http://www.google.fr/patents/US5070950?hl=fr
Timestamp: 2013-05-24 15:52:12
Document Index: 175103765

Matched Legal Cases: ['arts 94', 'arts 95', 'arts 94', 'arts 95', 'art 94', 'art 95', 'art 95', 'art 95', 'art 94', 'art 95', 'art 30', 'art 84']

Brevet US5070950 - Remote controlled actuation device - Google�BrevetsRecherche Images Maps Play YouTube Actualit�s Gmail Drive Plus » Recherche avanc�e dans les brevets | Historique Web | Connexion Recherche avanc�e dans les brevets BrevetsAn actuator for an appliance associated with a ducted body, through the duct of which flows an incompressible fluid, includes a differential piston axially moveable within the duct and operatively connected to the appliance. The piston has a tubular shape and a central bore which includes a first profiled...http://www.google.fr/patents/US5070950?utm_source=gb-gplus-shareBrevet US5070950 - Remote controlled actuation device Num�ro de publicationUS5070950 AType de publicationOctroi Num�ro de demande07/563,448 Date de publication10 d�c. 1991 Date de d�p�t3 ao�t 1990 Date de priorit�7 janv. 1985Autre r�f�rence de publicationCA1248936A1EP0190529A1EP0190529B1US4821817US4951760 InventeursJean BouletAndre Cendre Cessionnaire d'origineSfm International Classification aux �tats-Unis175/74175/232175/317175/324 Classification internationaleE21B17/10E21B34/10E21B21/10F16K17/30E21B43/112E21B7/08E21B7/06E21B33/127 Classification coop�rativeE21B43/112E21B7/06E21B33/127E21B17/1014E21B34/10E21B21/10F16K17/30 Classification europ�enneE21B 17/10CE21B 33/127E21B 21/10F16K 17/30E21B 7/06E21B 34/10E21B 43/112R�f�rencesCitations de brevets (27) R�f�renc� par (18)Liens externesUSPTO Cession USPTO EspacenetRemote controlled actuation deviceUS 5070950 A R�sum� An actuator for an appliance associated with a ducted body, through the duct of which flows an incompressible fluid, includes a differential piston axially moveable within the duct and operatively connected to the appliance. The piston has a tubular shape and a central bore which includes a first profiled throttling portion the minimum internal diameter of which is smaller than the internal diameter of the duct. A protruding profiled element secured in the duct body is disposed coaxially with the piston and cooperates therewith for selectively increasing the loss of head of the incompressible fluid as it flows in the direction of circulation. A spring is arranged between the piston and part of the drill-string for biasing the piston in a direction of movement opposite the direction of circulation of the incompressible fluid. A measurement device is provided for measuring the pressure of the incompressible fluid at the first end of the drill-string. The device can serve for actuation of an orientation device for orienting a drilling tool connected to a drill-string. The device can also serve for actuating a stabilizer of a set of drill rods.
We claim: 1. A remote controlled actuation device for the actuating of an appliance operatively connected to a drill-string having a bore of a substantially constant internal diameter that has an incompressible fluid circulating therein in an axial direction, the drill-string comprising a first end through which the incompressible fluid is introduced by a pumping means at an adjustable flow rate and a second end which is distant from the first end, the device being secured to the drill-string in a zone distant from the first end thereof, the device comprising: a body connected to the drill-string, said body having a central bore; a differential piston mounted so as to be movable in terms of translation along a defined stroke in the axial direction within said body central bore, said piston having a tubular shape and having a central bore which comprises a profiled throttling portion the minimum internal diameter of which is smaller than the internal diameter of the central bore of the piston; a protruding profiled element fixedly connected to the body and disposed substantially coaxially with the central bore of the differential piston, wherein said piston is movable along said defined stroke from a first end position to a second, lowermost, end position, at which said piston encloses at least a portion of said profiled element and a gap exists therebetween, said element having a profiled tapered external surface generally widening in the direction of circulation of the fluid along said defined stroke of said piston; a spring arranged between the piston and a part of the body for biasing the piston toward the first end position thereof; a means for measuring the pressure of the incompressible fluid upstream from said protruding profiled element, the actuation device allowing for the circulation of the fluid in the drill-string at a first flow rate without any movement of the piston away from its first end position, wherein a movement of the piston toward its second end position occurs when the fluid circulates at a second flow rate greater than said first flow rate and wherein an increasing loss of head is caused when the piston moves toward its second end position by a cooperation of the profiled throttling portion of the piston bore and the tapered external surface of the protruding profiled element so that there is a one-to-one relationship between a pressure of the working fluid and a position of the piston during the piston stroke, the movement being stopped after the actuation has been carried out such that the piston is at its second end position at which point a loss of head and a pressure of the working fluid at the first end of the drill-string have reached a maximum but the fluid still flows at the second flow rate through said gap between said profiled throttling portion of said piston and said protruding profiled element, and wherein the pressure of the fluid is measured thereby allowing a remote monitoring of the position of the piston; and, wherein said differential piston further comprises an actuating part intended to cooperate with a receiving part of the appliance when the fluid circulates at the second flow rate.
6. A remote controlled actuation device for the actuating of an appliance operatively connected to a drill-string having a bore of a substantially constant internal diameter that has an incompressible fluid circulating therein in an axial direction, the drill-string comprising a first end through which the incompressible fluid is introduced by a pumping means at an adjustable flow rate and a second end which is distant from the first end, the device being secured to the drill-string in a zone distant from the first end thereof, the device comprising: a body connected to the drill-string, said body having a central bore; a differential piston mounted so as to be movable in terms of translation along a defined stroke in the axial direction within said body central bore, said piston having a tubular shape and having a central bore which comprises a profiled throttling portion the minimum internal diameter of which is smaller than the internal diameter of the central bore of the piston; a protruding profiled element fixedly connected to the body and disposed substantially coaxially with the central bore of the differential piston, wherein said piston is movable along said defined stroke from a first end position to a second, lowermost, end position, at which said piston encloses at least a portion of said profiled element and a gap exists therebetween, said element having a profiled tapered external surface generally widening along said defined stroke of said piston; a spring arranged between the piston and a part of the body for biasing the piston toward the first end position thereof; a means for measuring the pressure of the incompressible fluid upstream from said protruding profiled element, the actuation device allowing for the circualtion of the fluid in the drill-string at a first flow rate without any movement of the piston away from its first end position, wherein a movement of the piston toward its second end position occurs when the fluid circulates at a second flow rate greater than said first flow rate and wherein an increasing loss of head is caused when the piston moves toward its second end position by a cooperation of the profiled throttling portion of the piston bore and the tapered external surface of the protruding profiled element so that there is a one-to-one relationship between a pressure of the working fluid and a position of the piston during the piston stroke, wherein when said piston is at its second end position a loss of head and a pressure of the working fluid at the first end of the drill-string have reached a maximum but the fluid still flows at the second flow rate through said gap between said profiled throttling portion of said piston and said protruding profiled element, and wherein the pressure of the fluid is measured thereby allowing a remote monitoring of the position of the piston; and, wherein a receiving part on the appliance is actuated as a result of the working fluid pressure difference between a pair of ends of the piston.
7. A remote controlled actuation device for the actuating of an appliance operatively connected to a drill-string having a bore of a substantially constant internal diameter that has an incompressible fluid circulating therein in an axial direction, the drill-string comprising a first end through which the incompressible fluid is introduced by a pumping means at an adjustable flow rate and a second end which is distant from the first end, the device being secured to the drill-string in a zone distant from the first end thereof, the device comprising: a body connected to the drill-string, said body having a central bore; a differential piston mounted so as to be movable in terms of translation along a defined stroke in the axial direction within said body central bore, said piston having a tubular shape and having a central bore which comprises a profiled throttling portion the minimum internal diameter of which is smaller than the internal diameter of the central bore of the piston; a protruding profiled element fixedly connected to the body and disposed substantially coaxially with the said central bore of the differential piston, wherein said piston is movable along said defined stroke from a first end position to a second, lowermost, end position, at which said piston encloses at least a portion of said profiled element and a gap exists therebetween, said element having a profiled tapered external surface generally widening in the direction of circulation of the fluid along said defined stroke of said piston; a spring arranged between the piston and a part of the body for biasing the piston toward the first end position thereof; and, a means for measuring the pressure of the incompressible fluid upstream from said protruding profiled element, the actuation device allowing for the circulation of the fluid in the drill-string at a first flow rate during which said piston remains in the first end position thereof, wherein a movement of the piston toward its second end position occurs when the fluid circulates at a second flow rate greater than said first flow rate and wherein an increasing loss of head is caused when the piston moves toward its second end position by a cooperation of the profiled throttling portion of the piston bore and the tapered external surface of the protruding profiled element so that there is a one-to-one relationship between a pressure of the working fluid and a position of the piston during the piston stroke, wherein when said piston is at its second end position a loss of head and a pressure of the working fluid at the first end of the drill-string have reached a maximum but the fluid still flows at the second flow rate through said gap between said profiled throttling portion of said piston and said protruding profiled element and wherein the pressure of the fluid is measured thereby allowing a remote monitoring of the position of the piston.
As can be seen in FIGS. 5 and 6, the body 60 has, on its peripheral surface, indentations 65 to allow the drilling mud to pass outside the stabilizer when it returns to the surface within the hole 53. The body 60 also has slots 66 serving for accommodating the bearing blades 68. The stabilizer illustrated in FIGS. 5 and 6 has three bearing blades 68 arranged in slot 66 placed at 120 stabilizer. Leaf springs 71, one end of which is fastened to the body 70 by means of screws, bear by means of their other end on the end parts of the blades 68, so as to keep them in the position retracted in the radial direction, as shown in FIGS. 5 and 6. Closing pieces 72 mounted in the end parts of the slot 66 outside the leaf springs 71 make it possible to guide the blades 68 in their radial direction of movement. A play is reserved for assembly between the leaf spring 71 and the closing piece 72, to allow a certain movement of the bearing blade in the radial direction between its position of complete retraction, shown in FIGS. 5 and 6, and a position of extraction or extension of the bearing blade 68 under the effect of a pair of actuating fingers 69 mounted so as to be movable in the radial direction within the body 60. Each of the fingers 69 is mounted movably and in a sealed manner in the body 60 by means of O-ring gaskets 70.
By reference to FIG. 7, it will be seen that successive inclined slopes 90a, 90b, 90c are arranged one after the other on the piston 75 over its periphery. A complete cycle of movement of a blade 68 is obtained by means of the three successive inclined slopes 90a, 90b and 90c, of which the machining depths at their ends and from the outside diameter of the piston 75 are indicated (in 10.sup.-3 m) in FIG. 7. Each of the fingers 69 is maintained, via the springs 71 of the corresponding blade 68, in contact with the bottom of a slope 90 by means of an end part machined in the form of a spherical bearing surface.
Thus, each of the three fingers 69 of an assembly executes a complete cycle of movement with three slopes 90a, 90b and 90c. The total number of slopes constituting the assembly 90 is therefore 3
It can be seen from FIG. 7 that the slopes 90a, 90b and 90c are connected to one another by means of curved parts 94 and by means of straight parts 95 of constant level, to form a continuous actuating surface 96 arranged on the periphery of the piston 75. The curved parts 94 joining the end of the slopes 90 to the end of the straight parts 95 make it possible to rotate the piston 75 step by step in the direction of the arrow 98 as a result of the interaction of the end of the finger 69 with the curved part 94, at the end of the movement of the piston 75 in one direction or the other. Each of the steps corresponds to the angular distance between the slope 90 and the adjacent plane part 95, that is to say 360
With blades in their retracted position, as shown in FIGS. 5 and 6, a flow at least equal to the actuation rate of the device is conveyed into the set of rods, thus causing a movement of the piston and an automatic and progressive increase in the loss of head, until the piston reaches its end position, the loss of head then being at the maximum. Recording the pressure from the surface makes it possible to determine the end of a step of movement of the piston. If the blades are extracted a sufficient amount, the device is automatically maintained in position as long as the feed flow of drilling fluid is not cancelled. If an additional step is to be executed to extract the blades an additional amount, the feed flow of drilling fluid is cancelled and the piston returns into its initial position as a result of the action of the spring 81. Meanwhile, a rotation of the piston through 20 positioned on a plane part 95 of the actuating surface 96. At the end of the plane part 95, the curved part 94 of the actuating surface 96 allows the piston to rotate 20 the free-wheel 100, so that the finger 69 is in alignment with the following slope 90b. As a result of an increase in the flowrate of the drilling fluid up to the value of the actuation rate, the piston 75 is moved in the direction of the arrow 93, the fingers 69 and the blades 68 being moved an additional step outwards and in the radial direction. It is obvious that the system can be returned to the initial state as a result of successive passes of the fingers 69 over the plane part 95 at the level -4.5 and over the slope 90c.
To use the actuation device, the flowrate of the drilling mud is increased progressively during the first period T.sup.A of the actuating cycle, to bring this flow rate from the value O or QS to a value Q.sub.ACT or actuating rate. At the end of this part of the cycle, the loss of head in the profiled part 30 of the piston 16 (or in the profiled part 84 of the piston 75) reaches a value Pa which is such that the excess pressure on the front face of the piston generates a force which begins to exceed the return force of the spring. The piston then moves downwards to execute a stroke C1, the flowrate being maintained at the value Q.sub.ACT. The loss of head increases slowly from the value Pa to the value Pb as a result of a slow reduction in the outlet cross-section of the piston 16 or 75 during the second phase B of the operating cycle. The stroke C1 of the piston 16 or 75 has then brought its profile 30 (or 84) opposite the profile of the needle 31 (or 85). The loss of head P increases very quickly and the piston moves downwards at an increased speed during the phase C of the operating cycle. The flowrate is maintained at the value Q.sub.ACT by means of the pumping installation 5 (or 55), the movement of the piston is self-maintained as a result of the increase in the loss of the head, and the piston 10 (or 75) moves until the fingers 34 (or 69) come up against the end part of the grooves 33 (or 90-91) by executing the stroke C2. The loss of head then changes from the value Pb to its maximum value Pm. This increase in the loss of head is considerably greater than that which could be obtained by means of an increase in the flowrate in a diaphragm with a constant aperture.
If, during the manoeuvre of the appliance 7, at the constant rate Q.sub.ACT the force exerted by the piston 16 or 75 becomes insufficient to continue carrying out the manoeuvre, the loss of head no longer increases. A plateau at a value of Pi&lt;Pm is recorded. It is then sufficient to bring the flowrate to a value Q'.sub.ACT to end the manoeuvre of the appliance 7. The maximum loss of head occurs at a value 'Pm&lt;Pm. The flowrate can subsequently be returned to and maintained at the value Q.sub.ACT which is sufficient to keep the piston 10 in the lower position.
As long as the flowrate is maintained at the value Q.sub.ACT, the differential piston 16 or 75 remains in its lower position and the loss of head P remains at its maximum value.
The piston is returned to its upper position shown in FIGS. 2 and 5 by progressively reducing the flowrate to bring it down to the value O (phase E). The tool 2 can subsequently be operated by increasing the flow rate to the value of the operating rate Q.sub.S, and with the appliance associated with the actuation device being in the new position.
During the entire operating cycle, the flowrate is increased to and maintained at Q.sub.ACT by means of the pumping installation 5, and the variations in pumping pressure P are detected and recorded by the measuring instrument 6. Both the control and the monitoring of the operating cycle are therefore carried out without difficulty from the surface, without using a remote-control device. In particular, it is easy to detect and record a stop of the piston before the end of the manoeuvre, this producing a pressure plateau. In this case, the manoeuvre is continued by increasing the flow rate to a sufficient value to release the appliance. The pumping means 5 must therefore make it possible to increase the flow rate to values higher than Q.sub.ACT, where required. In general, during the entire operating cycle of the device, recording the excess pressure corresponding to the loss of head P as a function of time makes it possible to ascertain the position of the piston 16 or 75 and therefore monitor the actuation of the device. A recorder recording the pressure as a function of time is therefore associated with the measuring device 6 (or 56).
To obtain a return of the piston to its initial position after the appliance has been actuated, it may only be necessary to reduce the pumping rate to a non-zero value below Q.sub.S. The tool 2 can subsequently be operated by increasing this rate again to the value Q.sub.S.
Citations de brevets Brevet cit� Date de d�p�t Date de publication D�posant TitreUS281904013 juil. 19567 janv. 1958Eastman Oil Well Survey CompanyDeflecting toolUS32204788 sept. 196030 nov. 1965Kinzbach Robert BCasing cutter and milling toolUS33013375 mai 196431 janv. 1967Alpha Trace, Inc.Apparatus for completing a wellUS37992693 avr. 197226 mars 1974Macco Oil Tool Co Inc,UsSafety means for well flow controlUS379927831 ao�t 197226 mars 1974Cities Service Oil Co,UsWell circulation toolUS39676801 ao�t 19746 juil. 1976Texas Dynamatics, Inc.Method and apparatus for actuating a downhole device carried by a pipe stringUS397488627 f�vr. 197517 ao�t 1976Blake, Jr.; Jack L.Directional drilling toolUS42168302 nov. 197812 ao�t 1980Otis Engineering CorporationFlapper valveUS428667624 juil. 19791 sept. 1981Institut Francais Du PetroleCrank connector for directional drillingUS43745475 mai 198122 f�vr. 1983Institut Francais Du PetroleCrank connector for directional drillingUS447184323 avr. 198218 sept. 1984Conoco Inc.Method and apparatus for rotary drill guidanceUS449118729 juin 19831 janv. 1985Russell; Larry R.Surface controlled auxiliary blade stabilizerUS481179830 oct. 198614 mars 1989Team Construction And Fabrication, Inc.Drilling motor deviation toolUS481773919 mai 19874 avr. 1989Jeter; John D.Drilling enhancement toolUS48218173 janv. 198618 avr. 1989Smf InternationalActuator for an appliance associated with a ducted body, especially a drill rodUS484417825 mars 19884 juil. 1989Smf InternationalDrilling device having a controlled pathUS484848825 mars 198818 juil. 1989Smf InternationalMethod and device for adjusting the path of a drilling tool fixed to the end of a set of rodsCA646129A7 ao�t 1962Joseph B. DufresneWell drilling toolDE317663A Titre non disponibleEP0056506A116 janv. 198128 juil. 1982Base, JimStabilizing tool for earth boring drill strings and method of using sameFR267501A Titre non disponibleGB1108723A Titre non disponibleGB2029873A Titre non disponibleGB2077811A Titre non disponibleGB2085055A Titre non disponibleGB2121455A Titre non disponibleSU523168A1 Titre non disponible R�f�renc� par Brevet citant Date de d�p�t Date de publication D�posant TitreUS531403217 mai 199324 mai 1994Camco International Inc.Movable joint bent subUS531813723 oct. 19927 juin 1994Halliburton CompanyMethod and apparatus for adjusting the position of stabilizer bladesUS531813823 oct. 19927 juin 1994Halliburton CompanyAdjustable stabilizerUS533204823 oct. 199226 juil. 1994Halliburton CompanyMethod and apparatus for automatic closed loop drilling systemUS544312814 d�c. 199322 ao�t 1995Institut Francais Du PetroleDevice for remote actuating equipment comprising delay meansUS55470329 janv. 199520 ao�t 1996Wenzel Downhole Tools Ltd.Apparatus for drilling curved sections of well holesUS583640626 juin 199717 nov. 1998Telejet Technologies, Inc.Adjustable stabilizer for directional drillingUS593123912 nov. 19973 ao�t 1999Telejet Technologies, Inc.Adjustable stabilizer for directional drillingUS628999930 oct. 199818 sept. 2001Smith International, Inc.Fluid flow control devices and methods for selective actuation of valves and hydraulic drilling toolsUS676123211 nov. 200213 juil. 2004Pathfinder Energy Services, Inc.Sprung member and actuator for downhole toolsUS720432518 f�vr. 200517 avr. 2007Pathfinder Energy Services, Inc.Spring mechanism for downhole steering tool bladesUS73773337 mars 200727 mai 2008Pathfinder Energy Services, Inc.Linear position sensor for downhole tools and method of useUS738389717 juin 200510 juin 2008Pathfinder Energy Services, Inc.Downhole steering tool having a non-rotating bendable sectionUS74647709 nov. 200616 d�c. 2008Pathfinder Energy Services, Inc.Closed-loop control of hydraulic pressure in a downhole steering toolUS772526322 mai 200725 mai 2010Smith International, Inc.Gravity azimuth measurement at a non-rotating housingUS795047324 nov. 200831 mai 2011Smith International, Inc.Non-azimuthal and azimuthal formation evaluation measurement in a slowly rotating housingUS796708111 d�c. 200828 juin 2011Smith International, Inc.Closed-loop physical caliper measurements and directional drilling methodUS81181143 mars 200921 f�vr. 2012Smith International Inc.Closed-loop control of rotary steerable bladesFaire pivoterImage d'origineAccueil Google - Plan du site - T�l�chargements par lot sur l'USPTO - R�gles de confidentialit� - Conditions d'utilisation - � propos de Google�Brevets - Envoyer des commentairesDonn�es fournies par IFI CLAIMS Patent Services©2012 Google