EP0136146B1 - Appareil de fond de puits commandé par pression de l'annulaire - Google Patents

Appareil de fond de puits commandé par pression de l'annulaire Download PDF

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Publication number
EP0136146B1
EP0136146B1 EP84306365A EP84306365A EP0136146B1 EP 0136146 B1 EP0136146 B1 EP 0136146B1 EP 84306365 A EP84306365 A EP 84306365A EP 84306365 A EP84306365 A EP 84306365A EP 0136146 B1 EP0136146 B1 EP 0136146B1
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EP
European Patent Office
Prior art keywords
power piston
pressure
fluid
valve
conducting passage
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
EP84306365A
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German (de)
English (en)
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EP0136146A3 (en
EP0136146A2 (fr
Inventor
Harold Kent Beck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Halliburton Co
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Halliburton Co
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Filing date
Publication date
Priority claimed from US06/533,701 external-priority patent/US4489786A/en
Priority claimed from US06/533,834 external-priority patent/US4557333A/en
Priority claimed from US06/533,835 external-priority patent/US4537258A/en
Priority claimed from US06/533,901 external-priority patent/US4515219A/en
Application filed by Halliburton Co filed Critical Halliburton Co
Publication of EP0136146A2 publication Critical patent/EP0136146A2/fr
Priority to MYPI87001775A priority Critical patent/MY101432A/en
Publication of EP0136146A3 publication Critical patent/EP0136146A3/en
Application granted granted Critical
Publication of EP0136146B1 publication Critical patent/EP0136146B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B23/00—Apparatus for displacing, setting, locking, releasing or removing tools, packers or the like in boreholes or wells
    • E21B23/004—Indexing systems for guiding relative movement between telescoping parts of downhole tools
    • E21B23/006—"J-slot" systems, i.e. lug and slot indexing mechanisms
    • 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
    • E21B34/00—Valve arrangements for boreholes or wells
    • E21B34/06—Valve arrangements for boreholes or wells in wells
    • E21B34/10—Valve arrangements for boreholes or wells in wells operated by control fluid supplied from outside the borehole
    • E21B34/108—Valve arrangements for boreholes or wells in wells operated by control fluid supplied from outside the borehole with time delay systems, e.g. hydraulic impedance mechanisms
    • 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
    • E21B49/00—Testing the nature of borehole walls; Formation testing; Methods or apparatus for obtaining samples of soil or well fluids, specially adapted to earth drilling or wells
    • E21B49/001—Testing the nature of borehole walls; Formation testing; Methods or apparatus for obtaining samples of soil or well fluids, specially adapted to earth drilling or wells specially adapted for underwater installations
    • 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
    • E21B2200/00—Special features related to earth drilling for obtaining oil, gas or water
    • E21B2200/04—Ball valves

Definitions

  • the tool When utilizing a tool which provides a sufficient volume of compressible silicone oil to accommodate the volume change required on the low pressure side of the power piston, the tool generally becomes very large because of the large volume of silicone oil required in view of its relatively low compressibility.
  • the present invention provides a tool which always actuates at the same differential operating pressure.
  • Tools which rely upon compressible liquids or compressible gas do not have constant differential operating pressures because the compressibility of the silicone oil and the nitrogen is non-linear.
  • the downhole tool of the present invention is shown in a testing string for use in an offshore oil or gas well.
  • a floating work station 11 is centered over a submerged oil or gas well located in the sea floor 10 having a bore hole 12 which extends from the sea floor 10 to a submerged formation 14 which is to be tested.
  • the bore hole 12 is typically lined by a steel liner or casing 16 which is cemented into place.
  • Annulus pressure in the well annulus 42 is isolated from the formation 14 to be tested by a packer 44 set in the well casing 16 just above the formation 14.
  • the pressure relief cartridge 264 has a second cartridge passageway 310, which may be referred to as a by-pass portion 310, of second pressure conducting passage means 166 disposed therethrough.
  • the by-pass portion 310 includes longitudinal bore 312 and a lower counterbore 314 disposed through the length of pressure relief cartridge 264.
  • the operation of the embodiment illustrated in FIGS. 2A-2E and FIG. 3 is as follows:
  • the tester valve 32A is initially in the position as illustrated in FIGS. 2A-2E with the power piston 140 in its upwardmost position relative to the power housing section 62 as illustrated in FIG. 2C, which first position corresponds to the closed position of the ball valve means 90 illustrated in FIG. 2A.
  • the speed of run-in must be such that the increase in fluid pressure can be transmitted through the fluid resistor 262 of metering cartridge 246 quickly enough to prevent the downward pressure differential across power piston 140 from becoming great enough to overcome spring 210.
  • the pressure relief piston means 280 Once the pressure relief piston means 280 is moved to its open position, the fluid located thereabove is relieved from the second pressure conducting passage means 166, as the power piston 140 moves from its first position to its second position. A volume of fluid sufficient to permit the power piston 140 to travel to its second position flows from the second pressure conducting passage means 166 above pressure relief piston means 280 through the pressure relief port 276, through groove 277 and through dump passage 278 into the dump zone or central bore 92 of tester valve 32A.
  • tester valve 32B of FIGS. 4A-4E from the upper adaptor 56 down to approximately the level of power piston 140 are substantially identical to the analogous portions of the tester valve 32A of FIGS. 2A-2E.
  • Identical or substantially similar parts of the tester valves 32A and 328 are designated with identical numerals, and the detailed description of those upper portions of tester valve 32A are applicable to the tester valve 32B and wiii not be repeated.
  • housing 54 of tester valve 32B includes upper adaptor 56, valve housing section 58, and first middle adaptor 60.
  • Valve housing 54 of valve tester 32B also includes a power housing section 400, a second middle adaptor 402, a metering cartridge housing section 404, and a lower adaptor 406.
  • power housing section 400 is threadedly connected to first middle adaptor 60 at threaded connection 408.
  • Metering cartridge housing section 404 is threadedly connected to second middle adaptor 402 at threaded connection 414 and an O-ring seal is provided therebetween by O-ring 416.
  • Lower adaptor 406 is threadedly connected to metering cartridge housing section 404 at threaded connection 418.
  • the first pressure conducting passage means 160 shown in FIG. 4C is substantially the same as first pressure conducting passage means 160 of tester valve 32A shown in FIG. 2C.
  • a second pressure conducting passage means 420 communicates a balancing port 422 (see FIG. 4E) with second side 144 of power piston 140.
  • a resilient biasing means 430 is operatively associated with power piston 140, for biasing the power piston 140 upward towards its first position illustrated in FIG. 4C.
  • the resilient biasing means 430 in the embodiment illustrated is a coil compression spring 430 having an upper end 432 engaging the second side 144 of power piston 140 and having its lower end 434 engaging an upward facing radially inward extending shoulder 436 of power housing section 400.
  • a metering cartridge retarding means 444 is located in an annular cavity 446 defined between a lower inner mandrel 448 and metering cartridge housing section 404.
  • Metering cartridge 444 is held longitudinally in place between a radially outward extending ledge 450 of lower inner mandrel 448 and a lower end 452 of second middle adaptor 402.
  • a flow restrictor 454 is located therein and includes a reduced diameter flow passage 456 shown in cross section therein.
  • Inner and outer 0-ring seals 458 and 460 seal between metering cartridge 444 and lower inner mandrel 448 and metering cartridge housing section 404, respectively.
  • the second pressure conducting passage means 420 of the tester valve 32B of FIGS. 4A-4E includes, beginning at the lower end, balancing port 422, annular cavity 446, longitudinal bore 462 and counterbore 464 of metering cartridge 444, longitudinal bore 466 of second middle adaptor 402, a short annular cavity 468 defined between guide mandrel means 424 and power housing section 400, first, second and third cartridge passages 470, 472 and 474 disposed through the length of pressure relief cartridge 438, and annular cavity 476 defined between guide mandrel means 424 and power housing section 400.
  • tester valve 32B of FIGS. 4A-4E and tester valve 32A of FIGS. 2A-2E, lies in the fact that the pressure relief cartridge has been very greatly modified, and the J-slot and lug type of releasable holding means 190 of FIG. 2C has been eliminated and replaced by a very different type of releasable holding means which operates based upon a hydraulic pressure differential across the power piston 140.
  • This silicone oil is sufficiently incompressible such that the volume thereof located between the power piston 140 and the pressure relief means 484 would hydraulically block the power piston 140 from travelling to its second position unless a volume of this fluid substantially equal to the displacement of power piston 140 were relieved from the first portion of the second pressure conducting passage means 420 by the pressure relief means 484.
  • the pressure relief cartridge 438 may also be referred to as a relief housing 438.
  • a relief port 486 is disposed through the relief housing 438 and communicates the first portion of the second pressure conducting passage means 420 with the fluid dump zone 92 which is also the central bore of the tester valve 32B.
  • pressure relief piston means 488 When pressure relief piston means 488 is in its closed position as illustrated in FIG. 4C, an O-ring seal 490 disposed in the outer surface of an upper end portion of pressure relief piston means 488 seals within the first cartridge passageway 470 below relief port 486.
  • a threaded insert 492 Disposed within first cartridge passageway 470 above pressure relief piston means 488 is a threaded insert 492 having a longitudinal bore 494 extending therethrough. The lowermost end portion of insert 492 is reduced in diameter and has an 0-ring seal 496 disposed thereabout.
  • An uppermost extremity of pressure relief piston 488 has a knife edge defined thereon which engages 0-ring seal 496 to provide a seal above the relief port 486.
  • a resilient relief piston biasing means 498 comprised of a stack of Belleville springs, is disposed about a lower cylindrical portion of pressure relief piston means 488 and serves to bias pressure relief piston means 488 towards its closed position.
  • a lower threaded insert 500 engages the lower end of the stack of Belleville springs 498 and may be threadedly adjusted to adjust the compression of the stack of springs 498.
  • a longitudinal bore 502 is disposed through lower threaded insert 500.
  • the relief port 486 communicates with a longitudinal groove 504 disposed in an inner cylindrical surface 506 of pressure relief cartridge 438.
  • the guide mandrel means 424 has a dump passage 508 disposed therethrough and communicated with the fluid dump zone 92.
  • Dump passage 508 includes a plurality of radial ports 509 and an outer annular groove 510 disposed in guide mandrel means 424 and communicated with the ports 509.
  • the longitudinal groove 504 of pressure relief cartridge 438 is communicated with annular groove 510 of dump passage 508 throughout the travel of power piston 140 and its attached guide mandrel means 424.
  • a back pressure check valve means 516 is disposed in second cartridge passage 472 for preventing communication of a sufficient portion of an increase in well annulus pressure to the second side 144 of power piston 140 so that so long as said increase in well annulus pressure is maintained on said first side 142 of power piston 140, a sufficient pressure differential is maintained from said first side 142 to the second side 144 of power piston 140 to prevent fhe resilient biasing means 430 from returning the power piston 140 to its first position.
  • This back pressure check valve means 516 which is only schematically illustrated in FIG. 4C, includes a ball 518 which is resiliently biased by a coil compression spring 520 downward against a valve seat 522.
  • the back pressure check valve means 516 would be designed to open at a 600 psi pressure differential so that the fluid pressure in annular cavity 476 is always at least 600 psi less than the annulus fluid pressure so long as an increase in annulus fluid pressure of greater than 600 psi which was applied to the annulus is maintained on the annulus fluid.
  • the back pressure check valve means may be said to be a releasable holding means 516 releasably preventing the power piston 140 from returning to its first position.
  • a run-in balance means 524 is disposed in third cartridge passage 474 for allowing well annulus pressure to sufficiently balance across power piston 140 as the tester valve 32B is run into the well so that a pressure differential from the first side 142 to the second side 144 of power piston 140 is neversufficientto overcomethe resilient biasing means 430 and prematurely move the power piston 140 to its second position as the tester valve 32B is run into the well.
  • the run-in balance means 524 includes a balance valve means 526 movable relative to pressure relief cartridge 438 between an open position illustrated in FIG. 4C, wherein fluid may flow through third cartridge passage 474, and a closed position, displaced downwardly slightly relative to pressure relief cartridge 438 from the position illustrated in FIG. 4C, wherein fluid flow through the third cartridge passage 474 is prevented.
  • a second end 532 of balance valve means 526 is closely received within a reduced inner diameter portion 534 of third cartridge passage 474.
  • balance valve means 526 Disposed about balance valve means 526 below the ledge 528 thereof is a coil compression balance valve biasing spring 542 which biases balance valve means 526 upward toward its open position.
  • a fluid restrictor 546 is held in place by a lower threaded insert 548. Fluid restrictor 546 protects balance valve means 526 from excessive pressure differentials which might damage it.
  • the balance valve means 526 may also be referred to as a seal valve means 526, disposed in the second pressure conducting passage means 420, for preventing communication of any further portion of the increase in well annulus pressure to the second side 144 of power piston 140 after the back pressure check valve means 516 has finally closed subsequent to the power piston 140 reaching its second position.
  • the actuating lug 544 may also be referred to as an actuating means 544, operatively associated with the power piston 1,40, for mechanically closing the seal valve means 526 when the power piston 140 moves to its second position.
  • the retarding means 444 may also be further characterized as being a means for allowing a first additional portion of the increase in well annulus pressure to be communicated to the second side 144 of the power piston 140 after the power piston 140 is moved to its second position. Operation of the Embodiment of FIGS. 4A-4E The operation of the tester valve 32B of FIGS. 4A-4E is generally as follows.
  • the tester valve 32B is then run down into the well defined by well casing 16 with the ball valve means 90 in its closed position closing the central bore flow passage 92 of the tester valve 32B, and with the power piston 140 in its first position as illustrated in FIG. 4C.
  • the downward pressure differential across pressure relief piston means 488 quickly causes pressure relief piston 488 to move downward breaking the seal with O-ring 496 so as to open the pressure relief means 484 and allow fluid trapped below the power piston 140 to be relieved through the relief port 486 and the dump passage 508 into the dump zone 92.
  • This fluid is continuously relieved to the dump zone 92 as the power piston 140 moves from its first position to its second position.
  • the volume of fluid relieved through the pressure relief means 484 is equal to a volume of fluid displaced by the power piston 140 as it travels from its first position to its second position.
  • This closing of the balance valve and seal valve means 526 prevents communication of any further portion of the increase in well annulus pressure to the second side 144 of power piston 140 after the back pressure check valve means 516 has finally closed subsequent to the power piston 140 reaching its second position.
  • FIGS. 5A-5G an elevation half section view is thereshown of a third embodiment of the tester valve of the present invention which is generally designated by the numeral 32C.
  • the indentation 602 and holding pin 604 are so arranged and constructed that when the power piston 140 is moved downward to its second position, the indentation 602 is radially aligned with the holding pin 604sothatthe holding pin 604 is moved into the indentation 602 by the pin biasing means 610 so that the power piston 140 is then releasably held in its second position.
  • Intermediate housing section 616 has its lower end threadedly connected to third middle adaptor 618 at threaded connection 632 with a seal being provided therebetween by 0-ring 634.
  • Third middle adaptor 618 has its lower end threadedly connected to retarding shoe housing section 620 at threaded connection 636 with a seal being provided therebetween by 0-ring 638.
  • Retarding shoe housing section 620 has its lower end threadedly connected to lower adaptor 54 at threaded connection 640.
  • a second pressure conducting passage means 642 communicates the well annulus 42 with the second side 144 of power piston 140, and includes a balancing port 644 (see FIG. 5G) and a plurality of passages and cavities further described below.
  • An annular cavity 654 is defined between guide mandrel means 646 and power housing section 612, and forms a part of the second pressure conducting passage means 642.
  • annular relief cartridge 668 Disposed in a lower portion of annular cavity 654 is an annular relief cartridge 668.
  • a pressure relief means 674 is disposed in the first cartridge passage 670 for relieving from a first portion of the second pressure conducting passage means 642 a volume of fluid sufficient to permit the power piston 140 to travel to its second position.
  • This first portion of the second pressure conducting passage means 642 is defined as the portion of the second pressure conducting passage means 642 between the second side 144 of power piston 140 and an annular sliding shoe- type retarding means 676 which is further described below.
  • Longitudinal groove 680 communicates with a dump passage 686 disposed through the guide mandrel means 646.
  • the dump passage 686 communicates with the dump zone 92 which is also the central bore of the tester valve 32C.
  • a dump mandrel 860 is concentrically disposed between ratchet mandrel 858 and power and relief housing section 800.
  • the lower end 862 of dump mandrel 860 abuts an upper end 864 of second middle adaptor 802.
  • Fluid dump passage means 882 also includes a first flow space 886 defined between dump mandrel 860 and ratchet mandrel 858 and communicated with first port 884.
  • Ratchet mandrel 858 has an intermediate flow passage 908 disposed therein communicating the first and second parts 902 and 904 of the first flow space 886.
  • the operating means 916 includes a spherical operating ball 918 which is closely and slidably received in the first port 884 and which engages a radially inner surface 920 of flapper-type fluid dump valve 910.
  • Operating means 916 further includes a cam means 922, operatively associated with the lower piston 140 for movement therewith, for camming the operating ball 918 radially outward toward the flapper-type fluid dump valve 910 and thereby opening the flapper-type fluid dump valve 910 as the power piston 140 starts to move from its said first position toward its said second position.
  • cam means 922 operatively associated with the lower piston 140 for movement therewith, for camming the operating ball 918 radially outward toward the flapper-type fluid dump valve 910 and thereby opening the flapper-type fluid dump valve 910 as the power piston 140 starts to move from its said first position toward its said second position.
  • the cam means 922 includes a longitudinally oriented cam surface 924 having ramp portions 926 and 928 at the lower and upper ends thereof, respectively.
  • a ratchet means 936 which is operatively associated with the power piston 140 and the cam means 922, for disengaging the cam means 922 from the operating ball 918 and thereby allowing the flapper valve 910 to close after the power piston 140 reaches its second position.
  • Ratchet means 936 includes a radially inward extending ball lug 938 which is held in place in a radial bore 940 of dump mandrel 860 by a threaded retainer 942.
  • the ball lug 938 is received within a ratchet groove 944 of ratchet means 936.
  • the ratchet groove 944 is disposed in the radially outer surface of ratchet mandrel 858, and is best seen in FIG. 7 which is a laid out view of ratchet groove 944 as viewed by a viewer looking radially inward toward the radially outer surface of ratchet mandrel 858.
  • the ball lug 938 of ratchet means 936 is in a position illustrated by the numeral 938A in FIG. 7 at the lower end of first longitudinal groove portion 946 of ratchet groove 944.
  • a releasable holding means 954 is operatively associated with power piston 140, for releasably preventing the power piston 140 from returning to its first position.
  • the manner of operation of the tester valve 32D shown in FIGS. 6A-6E, 7 and 8 is generally as follows.
  • the coil compression spring 866 resiliently biases the power piston 140 towards its first position.
  • the tester valve 32D uses a positive mechanical means of opening the flapper dump valve 910, rather than a hydraulically actuated pressure relief means such as the first three embodiments have shown, there is nothing like the pressure balance valve of the other embodiments blocking communication of pressure through the second pressure conducting passage means.
  • the cam means 922 cams the operating ball 918 radially outward to open the flapper dump valve 910.
  • the cartridge type retarding means 830 allows an additional portion of the increase in the well annulus pressure to be communicated to the second side 144 of the power piston 140 after the power piston 140 is moved to its second position, thus ultimately allowing the increase in well annulus pressure to substantially entirely balance across the power piston 140.
  • the number of times which the tester valve 32D can be cycled between the closed and open positions of ball valve means 90 is determined by the volume of fluid in the annular cavity 840 above the annular floating shoe 844. When the annular floating shoe 844 engages the threaded collar 832, the tester valve 32D can no longer be operated. It must then be removed from the well and refilled with fluid.

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

Claims (27)

1. Appareil (32A) de fond de sondage commandé par la pression annulaire, comprenant un boîtier d'outil (54), un piston moteur (140) placé afin qu'il puisse coulisser dans le boîtier, un premier circuit de passages (160) de conduction de pression destiné à faire communiquer un espace annulaire (42) du puits avec une première face (142) du piston moteur (140), un second circuit à passages (166, 420, 642, 818) de conduction de pression destiné à faire communiquer l'espace annulaire (42) du puits avec une seconde face du piston moteur (140), un dispositif retardateur (244, 444, 676, 830) placé dans le second circuit à passages (166, 420, 642, 818) afin qu'il retarde la communication d'une partie suffisante de l'augmentation de la pression annulaire à la seconde face (144) du piston moteur (140) pendant un temps suffisant pour que la différence de pression entre la première face (142) et la seconde face (144) du piston moteur (140) permette le déplacement du piston moteur (140) d'une première position à une seconde position par rapport au boîtier (54), et un dispositif de décharge de pression (272, 484, 674, 880), caractérisé en ce que le dispositif de décharge de pression communique avec une première partie du second circuit à passages (166, 420, 642, 818), entre la seconde face (144) du piston moteur (140) et le dispositif retardateur (244, 444, 676, 830) afin qu'un volume de fluide, suffisant pour que le piston moteur (140) se déplace vers sa seconde position, soit déchargé de la première partie du second circuit à passages (166, 420, 642, 818).
2. Appareil selon la revendication 1, dans lequel le dispositif retardateur (244, 444, 676, 830) se caractérise aussi en outre en ce qu'il est un dispositif permettant la communication d'une partie supplémentaire de l'augmentation de la pression annulaire à la seconde face (144) du piston moteur (140) après que le piston moteur (140) a été déplacé à sa seconde position.
3. Appareil selon la revendication 1 ou 2, dans lequel le dispositif retardateur (244, 444, 830) comporte un orifice de réduction de débit (262, 454, 840) placé dans le second circuit à passages (166, 420, 818).
4. Appareil selon la revendication 1, 2 ou 3, dans lequel, pendant l'utilisation, ladite première partie du second circuit à passages (166,420,642, 818) est remplie d'un premier fluide qui est suffisamment incompressible pour que le piston moteur (140) soit bloqué hydrauliquement et ne puisse pas se déplacer vers sa seconde position à moins qu'un volume du premier fluide soit évacué de la première partie du second circuit à passages (166, 420, 642, 818) par le dispositif de décharge de pression (272, 484, 674, 880).
5. Appareil selon la revendication 1, 2, 3 ou 4, comprenant en outre un dispositif élastique de rappel (210, 430, 656, 866) associé au piston moteur (140) et destiné à rappeler celui-ci vers la première position.
6. Appareil selon l'une quelconque des revendications 1 à 5, comprenant en outre un dispositif d'équilibrage lors de la descente (308, 524, 702, 818) destiné à permettre à la pression annulaire de s'équilibrer suffisamment de part et d'autre du piston moteur (140) lorsque l'appareil est descendu dans le puits, pour que la pression différentielle, dépendant de la profondeur, entre la première face (142) et la seconde face (144) du piston moteur (140), ne suffise jamais pour le déplacement prématuré de ce piston vers sa seconde position.
7. Appareil selon la revendication 6, dans lequel le second circuit à passages (166, 420, 642) comporte une partie de dérivation (310, 472, 672) montée en dérivation par rapport au dispositif de décharge de pression (272,484,674), et le dispositif d'équilibrage à la descente (308, 524, 702) comporte un clapet de retenue (316, 526, 704) placé dans la partie de dérivation (310, 472, 672) et destiné à permettre l'écoulement du fluide et ainsi la transmission de la pression dans un premier sens à partir de l'espace annulaire (42) du puits par l'intermédiaire de la partie de dérivation (310,472,672) du second circuit à passages (166, 420, 642) vers la seconde face (144) du piston moteur (140), et à empêcher l'écoulement du fluide dans la partie de dérivation (310, 472, 672) en sens inverse, opposé au premier sens.
8. Appareil selon l'une quelconque des revendications 1 à 7, comprenant en outre un dispositif de retenue temporaire (190, 516, 600, 954) associé au piston moteur (140) et destiné à l'empêcher temporairement de revenir à sa première position.
9. Appareil selon la revendication 8, dans lequel le dispositif de retenue temporaire (190) comporte une patte (196) raccordée au boîtier (54), une fente en J (192) associée au piston moteur (140), la patte (196) étant logée dans la fente en J (192), la fente en J (192) et la patte (196) formant un dispositif nécessitant que, pour que le piston moteur (140) soit déplacé vers sa première position (196A), il soit déplacé de la seconde position (196B) à une position de retenue intermédiaire (196C) correspondant à un retour partiel, puis à la seconde position (196D) et ensuite à la première position (196A).
10. Appareil selon l'une quelconque des revendications 1 à 9, dans lequel le dispositif de décharge de pression (272,484,674) comporte un boîtier de décharge (264, 438, 668), un orifice de décharge (276, 486, 678) disposé à travers le boîtier de décharge (264, 438, 668) et faisant communiquer la première partie du second circuit à passages (166, 420, 642, 818) avec une zone (92) d'évacuation de fluide, un piston de décharge de pression (280, 488, 688) disposé afin qu'il puisse coulisser dans le boîtier de décharge (264, 438, 668) et mobile entre une première position dans laquelle l'orifice de décharge (276, 486, 678) est fermé et une seconde position dans laquelle il est ouvert, et un dispositif élastique (282, 498, 698) de rappel du piston de décharge (280, 488, 688) vers sa première position.
11. Appareil selon la revendication 8, dans lequel le dispositif de retenue temporaire (516) comporte un clapet de retenue de contre-pression (516) placé entre le piston moteur (140) et le dispositif retardateur (444) et destiné à empêcher la communication d'une partie suffisante de l'augmentation de pression annulaire à la seconde face (144) du piston moteur (140) pour que, tant que l'augmentation de la pression annulaire est maintenue sur la première face (142) du piston moteur (140), une pression différentielle suffisante soit maintenue entre la première face (142) et la seconde face (144) pour que le piston moteur (140) ne puisse pas revenir à la première position.
12. Appareil selon les revendications 5 et 11, dans lequel le clapet de retenue de contre-pression (516) est un dispositif destiné à empêcher le dispositif élastique (430) de rappel de ramener le piston moteur (140) vers sa première position tant que l'augmentation de la pression annulaire est maintenue sur la première face du piston moteur (140).
13. Appareil selon la revendication 12, dans lequel le dispositif élastique de rappel (430) comporte un ressort hélicoïdal de compression (430).
14. Appareil selon la revendication 12 ou 13, comprenant en outre une soupape d'étanchéité (526) placée dans le second dispositif à passages (420) et destiné à empêcher la communication d'une partie supplémentaire de l'augmentation de la pression annulaire à la seconde face (144) du piston moteur (140) après que le clapet de retenue de contre-pression (516) s'est fermé finalement à la suite de l'arrivée du piston moteur (140) à sa seconde position.
15. Appareil selon la revendication 14, comprenant en outre un dispositif de manoeuvre (544) associé au piston moteur (140) et destiné à fermer mécaniquement la soupape d'étanchéité (526) lorsque le piston moteur (140) se déplace à sa seconde position.
16. Appareil selon la revendication 11, dans lequel le second dispositif à passages (420) comporte une partie de dérivation (474) placé en dérivation par rapport au dispositif de décharge de pression (484), et le dispositif d'équilibrage à la descente (524) comporte une soupape d'équilibrage (526) placée dans la partie de dérivation (474), la soupape d'équilibrage (526) étant mobile entre une position d'ouverture, dans laquelle le fluide peut s'écouler dans les deux sens par la partie de dérivation (474), et une position de fermeture dans laquelle l'écoulement d'un fluide dans la partie de dérivation est empêché, un dispositif élastique (542) de rappel de la soupape d'équilibrage (526) vers sa position d'ouverture, et un dispositif de manoeuvre (544) associé au piston moteur (140) et destiné à déplacer mécaniquement la soupape d'équilibrage (526) vers sa position de fermeture lorsque le piston moteur (140) se déplace vers sa seconde position.
17. Appareil selon la revendication 1, 4, 5, 6, 7, 8 ou 10, dans lequel le boîtier d'outil (54) comporte des organes tubulaires concentriques interne (750) et externe (620) délimitant une cavité annulaire (770) entre eux, le second circuit à passages (642) étant au moins partiellement délimité par la cavité annulaire (770), et le dispositif retardateur (676) comporte un patin flottant annulaire (676) logé intimement dans la cavité annulaire (770), le patin flottant (676) comprenant un dispositif élastique de friction (772, 776) coopérant intimement avec les organes tubulaires interne (750) et externe (620) du boîtier d'outil (54) à la fois.
18. Appareil selon la revendication 17, dans lequel le patin flottant (676) du dispositif retardateur (676) se caractérise en ce qu'il constitue aussi un dispositif permettant à une partie supplémentaire de l'augmentation de la pression annulaire d'être communiquée à la seconde face du piston moteur (140) après que le piston moteur (140) s'est déplacé dans sa seconde position.
19. Appareil selon les revendications 8 et 17, dans lequel le dispositif de retenue temporaire (600) comporte un évidement (602) formé dans un mandrin de manoeuvre (124) fixé au piston- moteur (140), un axe de retenue (604) disposé afin qu'il puisse coulisser radialement dans un trou radial (606) du boîtier (54) d'outil, un dispositif élastique (610) de rappel de l'axe de retenue (604) radialement vers l'intérieur par rapport au boîtier (54), et dans lequel l'évidement (602) et l'axe (604) sont disposés et construits de manière que, lorsque le piston moteur (140) est dans se seconde position, l'évidement (602) soit aligné sur l'axe (604) si bien que l'axe (604) pénètre dans l'évidement (602) sous la commande du dispositif de rappel (610) et maintient temporairement le piston moteur (140) dans sa seconde position.
20. Appareil selon la revendication 17,18 ou 19, dans lequel la première partie du circuit à passages (642) contient un volume suffisant de fluide pour que l'appareil puisse être utilisé de façon répétée pour le déplacement répété du piston moteur (140) de sa première position à sa seconde position sans que la première partie du second dispositif à passages (642) soit remplie à nouveau de fluide.
21. Appareil selon l'une quelconque des revendications 1 à 20, dans lequel le dispositif de décharge de pression (880) comporte une zone (92) d'évacuation de fluide, un passage (882) d'évacuation de fluide destiné à faire communiquer la première partie du second dispositif à passages (818) avec la zone d'évacuation de fluide (92), une soupape d'évacuation de fluide (910) placée entre la première partie du second dispositif à passages (818) et le passage d'évacuation de fluide (882), la soupape d'évacuation (910) étant mobile entre une position de fermeture dans laquelle elle isole la première partie du second circuit à passages (818) du passage d'évacuation de fluide (882) et une position d'ouverture dans laquelle le fluide peut s'écouler de la première partie du second circuit à passages (818) vers le passage d'évacuation de fluide (882), et un dispositif de manoeuvre (916) associé au piston moteur (140) et à la soupape d'évacuation de fluide (910) et destiné à déplacer la soupape d'évacuation de fluide (910) vers sa position d'ouverture lorsque le piston moteur (140) commence à se déplacer de sa première position vers sa seconde position, afin que la soupape d'évacuation de fluide (910) soit maintenue dans sa position d'ouverture jusqu'à ce que le piston moteur (140) atteigne sa seconde position et afin que la soupape d'évacuation de fluide (910) soit ramenée dans sa position de fermeture après que le piston moteur (140) a atteint sa seconde position.
22. Appareil selon la revendication 21, dans lequel la soupape d'évacuation de fluide (910) est un clapet anti-retour.
23. Appareil selon la revendication 21 ou 22, dans lequel le dispositif de manoeuvre (916) comporte une bille de manoeuvre (918) qui coopère avec le clapet anti-retour (910), et un dispositif à came (922) associé au piston moteur (140) est destiné à se déplacer avec lui afin qu'il déplace la bille de manoeuvre (918) par effet de came vers le clapet anti-retour (910) et ouvre ainsi ce clapet anti-retour lorsque le piston moteur (140) commence à se déplacer de sa première position vers sa seconde position.
24. Appareil selon la revendication 23, comprenant en outre un dispositif d'encliquetage (936) associé au piston moteur (140) et au dispositif à came (922) et destiné à séparer le dispositif à came (922) de la bille de manoeuvre (918) et ainsi à permettre au clapet anti-retour (910) de se fermer après que le piston moteur (140) a atteint sa seconde position.
25. Appareil selon l'une quelconque des revendications 21 à 24, comprenant en outre un clapet de retenue (909) disposé dans le passage d'évacuation de fluide (882) et destiné à permettre l'écoulement du fluide de la première partie du second circuit à passages (818) vers la zone d'évacuation (92), et à empêcher l'écoulement du fluide de la zone d'évacuation (92) à la première partie du second circuit à passages (818).
26. Appareil selon la revendication 25, dans lequel le clapet de retenue (909) est un clapet anti-retour.
27. Appareil selon l'une quelconque des revendications 21 à 26, dans lequel le second circuit à passages (818) est toujours ouvert afin qu'il permette la transmission de la pression sur toute sa longueur à partir de la seconde face (144) du piston moteur (140) vers l'espace annulaire (42) du puits lorsque l'appareil est descendu dans le puits, si bien que la pression annulaire peut s'équilibrer suffisamment de part et d'autre du piston moteur (140) et que la pression différentielle reliée à la profondeur et existant entre la première face (142) et la seconde face (144) du piston moteur (140) n'est jamais suffisante pour provoquer un déplacement prématuré de ce piston vers sa seconde position.
EP84306365A 1983-09-19 1984-09-18 Appareil de fond de puits commandé par pression de l'annulaire Expired - Lifetime EP0136146B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
MYPI87001775A MY101432A (en) 1983-09-19 1987-09-19 Annulus pressure responsive downhole tool.

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
US533901 1983-09-19
US06/533,701 US4489786A (en) 1983-09-19 1983-09-19 Low pressure responsive downhole tool with differential pressure holding means
US533835 1983-09-19
US533701 1983-09-19
US533834 1983-09-19
US06/533,834 US4557333A (en) 1983-09-19 1983-09-19 Low pressure responsive downhole tool with cam actuated relief valve
US06/533,835 US4537258A (en) 1983-09-19 1983-09-19 Low pressure responsive downhole tool
US06/533,901 US4515219A (en) 1983-09-19 1983-09-19 Low pressure responsive downhole tool with floating shoe retarding means

Publications (3)

Publication Number Publication Date
EP0136146A2 EP0136146A2 (fr) 1985-04-03
EP0136146A3 EP0136146A3 (en) 1988-01-20
EP0136146B1 true EP0136146B1 (fr) 1990-04-04

Family

ID=27504643

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84306365A Expired - Lifetime EP0136146B1 (fr) 1983-09-19 1984-09-18 Appareil de fond de puits commandé par pression de l'annulaire

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Country Link
EP (1) EP0136146B1 (fr)
DE (1) DE3481855D1 (fr)
SG (1) SG55790G (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69226903T2 (de) * 1991-06-14 1999-04-15 Baker-Hughes Inc., Houston, Tex. Druckmittelbetätigtes Bohrlochwerkzeugsystem
GB2377234B (en) * 2001-07-05 2005-09-28 Smith International Multi-cycle downhole apparatus
US7766086B2 (en) * 2007-06-08 2010-08-03 Bj Services Company Llc Fluid actuated circulating sub
CN110863796B (zh) * 2019-12-11 2023-11-07 贵州航天凯山石油仪器有限公司 一种密封段电动泄压方法及装置
CN114961643B (zh) * 2022-06-01 2023-05-23 西南石油大学 一种释放套管环空圈闭压力的可恢复式泄压装置及方法

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3858649A (en) * 1973-02-26 1975-01-07 Halliburton Co Apparatus for testing oil wells using annulus pressure
US4113012A (en) * 1977-10-27 1978-09-12 Halliburton Company Reclosable circulation valve for use in oil well testing
US4109725A (en) * 1977-10-27 1978-08-29 Halliburton Company Self adjusting liquid spring operating apparatus and method for use in an oil well valve

Also Published As

Publication number Publication date
DE3481855D1 (de) 1990-05-10
SG55790G (en) 1990-09-07
EP0136146A3 (en) 1988-01-20
EP0136146A2 (fr) 1985-04-03

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