WO2016164784A1 - Centreur à force constante - Google Patents

Centreur à force constante Download PDF

Info

Publication number
WO2016164784A1
WO2016164784A1 PCT/US2016/026733 US2016026733W WO2016164784A1 WO 2016164784 A1 WO2016164784 A1 WO 2016164784A1 US 2016026733 W US2016026733 W US 2016026733W WO 2016164784 A1 WO2016164784 A1 WO 2016164784A1
Authority
WO
WIPO (PCT)
Prior art keywords
force
arm
constant
pivoting
tool
Prior art date
Application number
PCT/US2016/026733
Other languages
English (en)
Inventor
Nathan Church
Original Assignee
Probe Technology Services, Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Probe Technology Services, Inc. filed Critical Probe Technology Services, Inc.
Priority to EP16777399.3A priority Critical patent/EP3280870A4/fr
Priority to CA2982165A priority patent/CA2982165A1/fr
Publication of WO2016164784A1 publication Critical patent/WO2016164784A1/fr

Links

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
    • 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
    • E21B17/1078—Stabilisers or centralisers for casing, tubing or drill pipes
    • 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
    • E21B17/1014—Flexible or expansible centering means, e.g. with pistons pressing against the wall of the well
    • E21B17/1021—Flexible or expansible centering means, e.g. with pistons pressing against the wall of the well with articulated arms or arcuate springs

Definitions

  • the present invention relates to a device that may apply a vectored force radially outward from a central axis.
  • S ch vectored force may be applied in multiple directions at once where the application of the vectored force is to maintain the central axis of the device relatively aligned with the central axis of the tubular through which the device passes.
  • a hydrocarbon bearing well Once a hydrocarbon bearing well has been drilled it is usually necessary to perform several tests upon the well, for instance to determine the integrity of the casing after it has been installed, to determine for instance the quality of the cementing job. or to determine the presence and locations of any hydrocarbons adjacent to the well. Such testing is usually done with a set of instruments referred to as a logging tool. In most instances the logging tool is lowered into the well on a cable, where the cable may include a power and or data line. Logging tools may be transported through any tubular structure including pipelines and refineries.
  • a centrali/er In order to centrally position the logging tool within the tubular, a centrali/er may be used. Centrali/ers typically use a set of springs, such as bow springs, to apply force radially outward from a central axis. Provided that the force is applied equally in all directions and that there is sufficient force to overcome any bias due to the weight of the logging tool, the logging tool will remain more or less centralized within the ⁇ ell bore, whether open hole or cased hole. Unfortunately the diameter of the wellbore varies as the tool progresses through the wellbore.
  • Variations in diameter may be due to other tools or equipment located in the wellbore or to different sizes of casing installed as the well progresses from the surface to the well's final depth. Other variations in the well diameter may be due to changes in the well's direction causing the casing to become ovali/ed as the tubular bends through turns.
  • the force applied to different sizes of tubulars by a standard centralizer varies such that a central i/er may have sufficient force to keep a logging tool centralized in one size of tubular, but when the logging tool is in a smaller diameter tubular such force is excessive, causing damage to the centralizer or even preventing the centralizer from progressing through the well.
  • the force applied may be sufficient to keep a logging tool centralized in one si/e of tubular, in a larger diameter tubular such force is inadequate allowing the logging tool to substantially deviate from the center of the tubular.
  • a constant force central i/er is envisioned where a first non-constant axial force drives the first set of arm assemblies and at least a second non-constant axial force drives the second set arm assemblies where the two sets of arm assemblies are offset from one another by 90°.
  • the non-constant axial forces are provided by some t pe of biasing device usually a spring or compressed gas but other t pes of biasing devices may be used.
  • a force guide may be permanently affixed, rotatably attached, or otherwise mounted on the central mandrel of the constant force centralizer. Each of the non-constant axial forces is converted to a radially extending force by an interaction of a force guide and actuator.
  • T he force guide is shaped to produce an essentially constant radially extending force through the enti e range of motion of the arm assemblies.
  • the radially extending force is maintained throughout each arm assembly ' s travel within about ten percent of the maximum radially extending force.
  • each arm assembly is comprised of a pivoting arm and telescopic section.
  • a wheel is positioned at the joint of the pivoting arm and the telescopic section to reduce friction as the constant force centralizer moves through the tubular.
  • the telescopin arm In the collapsed condition where the pivoting arm and wheel are relatively close to the mandrel of the constant force centrali/er the telescopin arm is in its substantially shortest state whereas in the extended condition where the pivoting arm and wheel are at their maximum distance from the mandrel the telescopin arm is in its longest state.
  • the telescoping arm is generally necessary in order to allow the constant force centralizer to reverse direction when moving from a larger diameter tubular to a smaller diameter tubular. A portion of the telescoping arm will interact with the tubular to force the pivoting arm and wheel to retract to at least a semi-collapsed condition.
  • pairs of arm assemblies will usually be used in a constant force centrali/er.
  • the pairs of arm assemblies are typically arranged such that a first end of the first pair and a first end of the second pair of arm assemblies extend toward each other from a first end of a mandrel and from an opposing second end of the mandrel.
  • the first pair of arm assemblies is allowed to collapse into a nested position with the second pai r of arm assemblies.
  • opposin pairs of pivoting arms overlap by some distance.
  • the overlap and telescoping arms generally allows the tool to be shorter than a standard tool not havin overlapping arms.
  • Figure 1 depicts a calculated and measured force curve of an embodiment of the invention.
  • Figure 2 depicts a calculated force curve of an alternate embodiment of the invention.
  • Figure 3 depicts a side view of an embodiment of the invention in its extended condition.
  • Figure 4 depicts an end view of an embodiment of the invention.
  • Figure 5 depicts a side view of an embodiment of the invention in its retracted condition.
  • Figure 6 depicts an end view of an embodiment of the invention in a partially extended condition in an oval tubular.
  • Figure 7 depicts an extended joint of an embodiment of the invention.
  • Figure 8 depicts a side view of an alternate embodiment of the invention in its extended condition.
  • Figure 9 depicts a side view of an alternate embodiment of the invention having a rotatable force guide in an extended condition of a constant force centralizer.
  • Figure 10 depicts an orthogonal view of a rotatable force guide.
  • Figure 11 depicts a side view of an alternate embodiment of the invention having an extension limiter in a limited extension condition.
  • Figure 12 depicts a side view of an alternate embodiment of the invention having an extension lock in a retracted and locked condition.
  • Figure 13 depicts a close-up of the area A from Figure 12.
  • Figure 1 depicts a graph of the measured force curve 10 versus the predicted force curve 14 of an embodiment of the present invention.
  • the measured force curve 10 is a poly fit of the measured points 12 while the predicted force curve is a based upon a computer simulation.
  • a perfectly flat, linear response was the original design goal, but in order to keep the mechanisms relatively simple, a slight "cun e", as depicted by the predicted force cun e 14 and the measured force curve 10 was thought to be acceptable.
  • Figure 2 depicts a graph of the predicted force curve 20 of an alternate embodiment of the present invention. While other force ranges may be used, the predicted force curve 20 utilizes a force range of from about 40 pounds of force at the minimum diameter of just over three inches increasing to about 43 pounds of force at the mid-range diameter of 8 inches then decreasing again to about 40 pounds of force at the maximum diameter of about thirteen inches. Such a force range has less than a 10% variation across the range of applied force from the minimum diameter to the maximum diameter.
  • FIG 3 is a side depiction of an embodiment of a constant force centrali/er 50 providing a substantially constant radially outward force throughout a predetermined range of tubular diameters.
  • the constant force centra! i/er 50 has an inner mandrel 52. beginning with the right side of the constant force centrali/er 50, and at least one axial biasing device such as axial biasing device 54.
  • a collar 58 is fitted to the mandrel 52 in such a manner that its position is fixed relative to the mandrel 52.
  • the collar 58 may be threaded, pinned, welded, or formed as an integral part of inner mandrel 52, or connected by any other means know n to the inner mandrel 52.
  • the axial biasing device 54 typically surrounds inner mandrel 52 and abuts collar 58.
  • the axial biasing device 54 also abuts a movable sleeve 62.
  • the movable sleeve 2 is circumferential about an exterior surface of inner mandrel 52.
  • the movable sleeve 62 is generally only axially movable.
  • a first end 70 and 72 of pivotal force arms 64 and 68 is attached to movable sleeve 62.
  • Each pivotal force arm 64 and 68 has a recess 74 and 76. Within each recess 74 and 76 is an actuator 80 and 82, such as a roller.
  • Each recess 74 and 76 is sized such that when pivotal force arms 64 and 68 are in the retracted position, lying fiat against inner mandrel 52, most of the force guides 84 and 88 that extend beyond the exterior surface of inner mandrel 52 are contained within each recess 74 and 76.
  • the force guides 84 and 88 are fixed to the inner mandrel 52 and maybe threaded on, pinned on. or formed as an integral part of the inner mandrel 52. It is generally the interaction between the force guides 88 and 84 with the corresponding actuators 80 and 82 that describes the constancy of the force curves such as the curves in figures 1 and 2.
  • Each force guide 88 and 84 will have a surface such as surfaces 90 and 92. Generally the surfaces 90 and 92 are linear surfaces at some angle a relative to the axis of mandrel 52 where the angle a provides a reasonably fiat force curve. The angle a in Figure 3 is 47°.
  • the constant force centrali/er 50 has at least one axial biasing device such as axial biasing device 56.
  • a collar 100 is fixed onto a second end 102 of inner mandrel 52.
  • the collar 100 is typically threaded onto inner mandrel 52 but may be pinned, welded, or formed as an integral part of inner mandrel 52.
  • the axial biasing device 56 typically surrounds inner mandrel 52 and abuts collar 100.
  • the axial biasing device 56 also abuts a movable sleeve 104.
  • the movable sleeve 104 is circumferential about an exterior surface of inner mandrel 52.
  • the movable sleev e 104 is generally only axially movable.
  • a second end 106 and 108 of telescopic arms 1 10 and 112 is attached to movable sleeve 104.
  • a first end 1 14 and 116 of telescopic arms 110 and I 12 is pivotally connected to a second end 120 and 122 of pivotal force arms 64 and 68.
  • a wheel such as wheel 124 and 126, a roller, a skid, or other friction reducer is attached.
  • the constant force is applied to the casing or other tubular in a direction perpendicular to the long axis of the constant force centralizer 50.
  • each of the pivotal force arms 64, 68, and telescopic arms 110, and 112 will be in a collapsed position such that wheels 124 and 126 are at a minimal radial distance from inner mandrel 52.
  • axial biasing device 54 is at maximum compression thereby applyin the maximum normal force against movable sleeve 62.
  • the force applied by axial biasing device 54 is transferred to the movable sleeve 62.
  • the force applied by axial biasing device 54 is not necessarily constant.
  • Movable sleeve 62 in turn transfers the force to pivotal force arms 64 and 68. Subsequent movement of pivotal force arm 64 is guided by actuator 80 acting on surface 90 causing end 122 to move in a direction substantially perpendicular to the axis of the mandrel 52.
  • the dimensions of pivotal force arm 64, actuator 80, force guide 88, movable sleeve 62, collar 58 and biasing device 54 are chosen so that the force from the biasing device 54 is transferred to the wheel 124 in such manner that that force of wheel 124 against the tubular remains reasonably constant as the diameter of the tubular changes.
  • pivotal force arm 68 Movement of pivotal force arm 68 is guided by actuator 82 acting on surface 92 causing end 120 to move in a direction substantially perpendicular to the axis of the mandrel 52.
  • the dimensions of pivotal force arm 68, actuator 82, force guide 84, movable sleeve 62, collar 58 and biasing device 54 are chosen so that the force from the biasing device 54 is transferred to the wheel 126 in such manner that that force of wheel 126 against the tubular remains reasonably constant as the diameter of the tubular changes.
  • a current embodiment of the tool produces 40 lbs of radial force at the wheels 124 and 126 at the joint between pivoting force arms 64 and 68 and telescoping arms 110 and 112.
  • the force response is adjustable with the nominal radial force either increased or decreased. Such increases or decreases may be adjusted where biasing devices 54 and 56 may be replaced with springs, gas chambers, etc. having proportionally higher or lower force rates. If needed, shims can add compression to the biasing devices 54 and 56 and thereby increase the axial force.
  • a flatter force response curve, see Figures 1 and 2 is achievable if a more complex shape is machined into the force guides 84 and 88.
  • the force guides 84 and 88 are generally fixed to the inner mandrel 52 of the constant force centralizer 50.
  • the force guides 84 and 88 have an angle a where the angle a is about 47° relative to the axis of the inner mandrel 52 achieving a substantially constant force response as indicated in figure 2.
  • the force guide angle and/or shape controls the shape of the force response curves such as the force response curves in Figures 1 and 2.
  • Figure 4 is an end view of the fully collapsed constant force centralizer 50.
  • the constant force centralizer depicted an outside diameter of 3.5 inches was chosen as the nominal diameter of the centralizer. A smaller outer diameter can be achieved in the centralizer design by scaling dow n the size of the components.
  • shorter tools are preferred. As tools become shorter, their overall weight is reduced. In one embodiment of the 3.5 inch diameter constant force centralizer 100, the total tool weight is less than 40 pounds.
  • the constan t force central izer 100 has a length of 26.8 inches.
  • the relatively short tool length of the design is a result of offsetting the pivoting force arms 102, 104, and 106.
  • the pivoting force arm 102 is attached to movable sleeve 108 while pivotin force arm 104 is attached to movable sleeve 1 10 by pin 1 12 and pivoting force arm 106 and is attached to movable sleeve 110 by pin 1 14.
  • the pivotin force arm 102 is connected to telescopin arm 122 at the joint 132. Also at joint 132 are wheels 116 and 1 1 7.
  • Telescoping arm 122 has a first portion 124, connected to pivoting force arm 102 at joint 132, and a second portion 126. Second portion 126 is attached to movable sleeve 1 10 via pin 134.
  • pivotin force arm 104 is attached to movable sleeve 110 by pin 1 12.
  • the pivoting force arm 104 is connected to telescopin arm 128 at the joint (not shown) where wheel 1 18 is attached to the constant force centrali er 100.
  • each of the wheels 116 and 118 are offset by some axial distance D.
  • the distance D may vary dependin upon whether the arms are fully extended or fully collapsed or at some point in between.
  • the wheels 116, 118, 1 1 7 and 120, at each of the joints between the pivoting force arms 102, 104, and 106 and the telescoping arms 122, 128, and 130 are free to rotate even when the tool is completely closed to its minimum outside diameter.
  • the constant force centralizer is designed to open from about 3.5 inches to about 12.7" which is the inner diameter of typical casing that has an outer diameter of 13-3/8 inches. As shown in Figure 2, about 40 pounds of centralizing force is active across that entire range.
  • the pivoting force arm 102 is paired with the pivoting force arm 107 on the opposite side of the constant force centralizer 100.
  • the opposing pivoting force arms 102 and 107 move symmetrically with one another.
  • the telescoping arm 128 is paired with the telescoping arm 130 on the opposite side of the constant force centralizer 100.
  • the opposing telescoping arms 128 and 130 move symmetrical! ⁇ ' with one another.
  • the telescoping arms 128 and 130 arms are generally orthogonal to the pivoting force arms 102 and 107.
  • the pivotin force arms 102 and 107 are typically coupled to each other such that the axial biasin device 140 drives both of the pivotin force arms 102 and 107.
  • the telescoping force arms 128 and 130 may be linked to the same movable sleeve 108 as the pivotin force arms 102 and 107 the telescoping mechanism does not allow force to be applied by movable sleeve 108 to the telescoping force arms 128 and 130.
  • the wheels 150 and 152 in an embodiment of the constant force centralizer are preferably as large in diameter as possible, here 1 .3 inches in diameter as shown by reference numeral 1 54, without exceeding the desired 3.5 inch constant force central i/er outside diameter. Maximizing the wheel diameter allows each wheel 150 and 152 to last longer and roll more smoothly across i regularities in the tubular.
  • each joint between the telescoping arm 158 and the pivoting arm 1 56 arm has two wheels 150 and 152 at the joint. Each wheel rolls independently on ball bearings 160.
  • the pivoting force arms 202 and 204 are at an angle ⁇ relative to the axis of the constant force centrali/er 200.
  • angle ⁇ is 30°.
  • the telescoping arms 206 an d 208 are at an angle ⁇ relative to the axis of th e constan t force centralizer 200.
  • angle ⁇ is 35°.
  • Figure 9 is a depiction an alternative embodiment of the constant force centrali/er 300.
  • the components of the centralizer assembly including the rotatable force guide 304, pivoting force arms 306, telescoping arms 308, first axial biasing device 312, first movable sleeve 316, second axial biasing device 314, second movable sleeve 318, and other associated portions of the central i/er assembly to rotate around the inner mandrel 302.
  • the wireline (not shown) avoids becoming twisted thereby avoiding any torque build up on account of constant force centrali/er 300.
  • Figure 10 is a depiction of the rotatable force guide 304 from Figure 9.
  • the rotatable force guide 304 typically consists of a first-half 356 and a second half 358. Each half 356 and 358 has a semicircular section such as 366 and semicircular section 364 each hal f 356 and 358 also has at least a portion of the force guide 304 attached to the semicircular sections 366 and 364.
  • the upper force guide includes a relatively linear surface 370 set at an angle a to the central axis of the inner mandrel 302 of the constant force centrali/er 300.
  • the upper force guide also includes a means to pivotally attach a limiting arm (not shown) such as providin a slot 372 for a wrist pin (not shown).
  • the lower force guide includes a relatively linear surface 368 set at an angle a to the central axis of the inner mandrel 302 of the constant force centralizer 300.
  • the lower force guide also includes a means to pivotally attach a limiting arm (not shown) such as providing a slot 374 for a wrist pin (not shown).
  • the rotatable force guide 304 is applied to the inner mandrel 302 by placing each half 356 and 358 such that the semicircular portions 364 and 366 surround the inner mandrel 302. Then using bolts such as bolts 362 and 360 to fix each half 356 and 358 in place around inner mandrel 302. It is envisioned that any known means of manufacturing a rotatable force guide could be used for instance in some instances the force guide 304 could be machined out of a solid piece of material and then slid onto the mandrel 302 from one end.
  • Figure 1 1 is a depiction an alternative embodiment of the constant force centralizer 400.
  • Such a limitation may be useful in. for instance, circumstances where the constant force centralizer 400 may pass through very large openings such as when it passes through a blow out preventer which might cause damage to the constant force centralizer 400.
  • One such extension li miter may use a link 410 attached to the inner mandrel
  • a first end of link 410 is attached to the rotatable force guide 414 by wrist pin 416 within slot 472.
  • a second end of link 410 is attached to pivoting force arm 402 by wrist pin 418 within slot 420.
  • Wrist pin 418 is configured such that it may slide within slot 420 depending upon the extension position of wheel 406 as wheel 406 moves towards inner mandrel 412 wrist pin 418 will move towards wheel 406 within slot 420. However as wheel 406 moves away from inner mandrel 412 wrist pin 418 moves within slot 420 towards movable sleeve 422. Eventually wrist pin 418 reaches the end of slot 420 closest to movable sleeve 422 whereupon wheel 406 is prevented from moving an ⁇ ' further radially outward from inner mandrel 412.
  • Figure 12 is a depiction of an alternative embodiment of a portion of a constant force central i/er 500.
  • a lock will maintain the pivoting force arms and telescoping arms in the retracted position until some predetermined parameter is reached.
  • a pressure actuated retainin pin 520 may be used where the pressure actuated retaining pin 520 is designed to protrude from the force guide 522 when the constant force centrali/er 500 is below some preset pressures such as atmospheric pressure.
  • the external pressure may be increased such that at some predictable point the pressure will be sufficient to force the pressure actuated retaining pin 520 inward into its recess within the force guide 522.
  • the pivoting force arm 502 is released so that the wheel 524 may move radially outward to engage the tubular at the predetermined force level.
  • Figure 13 is section A from Figure 12.
  • Figure 13 depicts force guide 522 having the pressure actuated retaining pin 520 w ithin recess 524.
  • a pressure actuated retaining pin is utilized.
  • the retainin pin could be actuated by temperature, elapsed time, a sacri ficial wear pin. by a chemical reaction, or by an electrical signal.
  • a portion 526 of the pressure actuated retaining pin 520 extends from force guide 522 into a port 528 w ithin pivoting force arm 502.
  • the pressure actuated retainin pin 520 and recess 524 form a chamber 530 sufficient to allow the pressure actuated retaining pin 522 to move into the recess 524 within force guide 522 upon the application of sufficient force to port 528 and acting upon the portion of the pressure actuated retaining pin 522 that extends into port 528.
  • the pressure actuated retaining pin 522 may be held outwardly extended by the force exerted upon the pressure actuated retaining pin 522 by the pivoting force arm 502 and/or may have any other means known in the industry for securing the pressure actuated retaining pin 522.

Landscapes

  • 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)

Abstract

L'invention concerne un dispositif à force constante ayant au moins une première force axiale non constante entraînant le premier ensemble de bras et une deuxième force axiale non constante entraînant le deuxième ensemble de bras, les deux ensembles de bras étant décalés l'un par rapport à l'autre par 900. Chacune des forces axiales non constantes est convertie en une force s'étendant dans le sens radial par l'interaction d'un actionneur et d'un dispositif de guidage de force. Le dispositif de guidage de force est attaché sur le mandrin intérieur du dispositif à force constante et est formé pour produire une force sensiblement constante s'étendant dans le sens radial à travers la totalité de la plage de mouvement des bras. Typiquement, chaque bras de la paire de bras possède un bras de pivotement et un bras télescopique où l'articulation entre le bras de pivotement et le bras télescopique présente une ou plusieurs roues servant à réduire le frottement quand le dispositif à force constante se déplace à travers l'élément tubulaire.
PCT/US2016/026733 2015-04-08 2016-04-08 Centreur à force constante WO2016164784A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP16777399.3A EP3280870A4 (fr) 2015-04-08 2016-04-08 Centreur à force constante
CA2982165A CA2982165A1 (fr) 2015-04-08 2016-04-08 Centreur a force constante

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201562144657P 2015-04-08 2015-04-08
US62/144,657 2015-04-08
US14/803,023 2015-07-17
US14/803,023 US20160298396A1 (en) 2015-04-08 2015-07-17 Constant force centralizer

Publications (1)

Publication Number Publication Date
WO2016164784A1 true WO2016164784A1 (fr) 2016-10-13

Family

ID=57073004

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2016/026733 WO2016164784A1 (fr) 2015-04-08 2016-04-08 Centreur à force constante

Country Status (4)

Country Link
US (1) US20160298396A1 (fr)
EP (1) EP3280870A4 (fr)
CA (1) CA2982165A1 (fr)
WO (1) WO2016164784A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111395989A (zh) * 2020-04-30 2020-07-10 大庆昊运橡胶制品有限公司 不拔芯大通道高温高压压裂扩张式胶筒封隔工具

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180298699A1 (en) * 2015-12-16 2018-10-18 Halliburton Energy Services, Inc. Energized Downhole Standoff
CN108999582B (zh) * 2018-07-23 2019-11-22 游精学 石油水平井越障牵引器及其使用方法
US11442193B2 (en) * 2019-05-17 2022-09-13 Halliburton Energy Services, Inc. Passive arm for bi-directional well logging instrument
WO2021022091A1 (fr) * 2019-08-01 2021-02-04 Chevron U.S.A. Inc. Centreur de dynamique de rotor à grande vitesse
US10947791B1 (en) 2020-08-06 2021-03-16 Petromac Ip Limited Device for centering a sensor assembly in a bore
US10947792B1 (en) 2020-08-19 2021-03-16 Petromac Ip Limited Device for centering a sensor assembly in a bore
US10988991B1 (en) 2020-09-30 2021-04-27 Petromac Ip Limited Sensor transportation device
CN112025755B (zh) * 2020-10-14 2024-06-18 哈工大机器人（合肥）国际创新研究院 一种恒力执行装置
US11136880B1 (en) 2021-01-15 2021-10-05 Petromac Ip Limited Device for centering a sensor assembly in a bore
USD1009088S1 (en) * 2022-05-10 2023-12-26 Kaldera, LLC Wellbore tool with extendable arms
CN115263263B (zh) * 2022-07-27 2024-05-14 西安航天化学动力有限公司 一种可控冲击波压裂装置及方法
US11713627B1 (en) * 2022-08-18 2023-08-01 Petromac Ip Limited Device for centering a sensor assembly in a bore

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5358040A (en) * 1992-07-17 1994-10-25 The Kinley Corporation Method and apparatus for running a mechanical roller arm centralizer through restricted well pipe
US6216779B1 (en) * 1997-12-17 2001-04-17 Baker Hughes Incorporated Downhole tool actuator
US20020162240A1 (en) * 2000-11-01 2002-11-07 Baker Hughes Incorporated Use of magneto-resistive sensors for borehole logging
US20030173076A1 (en) * 2002-03-13 2003-09-18 Sheiretov Todor K. Constant force actuator
US20090008152A1 (en) * 2004-03-17 2009-01-08 Mock Philip W Roller link toggle gripper and downhole tractor
US20120205093A1 (en) * 2011-02-14 2012-08-16 Nathan Paszek Instrument for Centering Tools Within a Wellbore

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5926024A (en) * 1995-01-04 1999-07-20 Atlantic Richfield Company System and method for measuring fluid properties by forming a coaxial transmission line in a cased well
US20020016224A1 (en) * 1997-05-27 2002-02-07 Pasqua Samuel A. Filler-impregnated golf ball core blend
US6629568B2 (en) * 2001-08-03 2003-10-07 Schlumberger Technology Corporation Bi-directional grip mechanism for a wide range of bore sizes
US7334642B2 (en) * 2004-07-15 2008-02-26 Schlumberger Technology Corporation Constant force actuator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5358040A (en) * 1992-07-17 1994-10-25 The Kinley Corporation Method and apparatus for running a mechanical roller arm centralizer through restricted well pipe
US6216779B1 (en) * 1997-12-17 2001-04-17 Baker Hughes Incorporated Downhole tool actuator
US20020162240A1 (en) * 2000-11-01 2002-11-07 Baker Hughes Incorporated Use of magneto-resistive sensors for borehole logging
US20030173076A1 (en) * 2002-03-13 2003-09-18 Sheiretov Todor K. Constant force actuator
US20090008152A1 (en) * 2004-03-17 2009-01-08 Mock Philip W Roller link toggle gripper and downhole tractor
US20120205093A1 (en) * 2011-02-14 2012-08-16 Nathan Paszek Instrument for Centering Tools Within a Wellbore

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3280870A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111395989A (zh) * 2020-04-30 2020-07-10 大庆昊运橡胶制品有限公司 不拔芯大通道高温高压压裂扩张式胶筒封隔工具

Also Published As

Publication number Publication date
US20160298396A1 (en) 2016-10-13
EP3280870A4 (fr) 2018-12-12
CA2982165A1 (fr) 2016-10-13
EP3280870A1 (fr) 2018-02-14

Similar Documents

Publication Publication Date Title
WO2016164784A1 (fr) Centreur à force constante
US8082988B2 (en) Apparatus and method for stabilization of downhole tools
US9399894B2 (en) Friction reducing downhole assemblies
US7140432B2 (en) Dual diameter and rotating centralizer/sub and method
US4830105A (en) Centralizer for wellbore apparatus
CA2758417C (fr) Outil mecanique a etages multiplesl
US5355950A (en) Centraliser
US11136880B1 (en) Device for centering a sensor assembly in a bore
US10724308B2 (en) Drill pipe torque reducer and method
EP1910641B1 (fr) Outil de centrage ajustable a ailettes destine a une utilisation dans des tuyaux de diametre variable
US8281880B2 (en) Expandable tool for an earth boring system
CN106639913A (zh) 用于在钻孔时抵抗旋转力的装置
CN116034206A (zh) 用于在筒中使传感器组件对中的装置
US11215015B1 (en) System and method for controlling a downhole operation using a clutch tool
US11015401B2 (en) Downhole friction reduction tools
WO2022039603A1 (fr) Dispositif de centrage d'un ensemble capteur dans un sondage
US11021914B2 (en) Connector for connecting to a downhole longitudinal member
US20240141735A1 (en) Device for centering a sensor assembly in a bore
CA2618311C (fr) Appareillage et methode de stabilisation des outils de fond de trou
CA2072552A1 (fr) Dispositif de cintrage reglable
NO344871B1 (en) Anchor device

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16777399

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2982165

Country of ref document: CA

NENP Non-entry into the national phase

Ref country code: DE