WO2018143819A1 - Accouplement - Google Patents

Accouplement Download PDF

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Publication number
WO2018143819A1
WO2018143819A1 PCT/NO2018/050025 NO2018050025W WO2018143819A1 WO 2018143819 A1 WO2018143819 A1 WO 2018143819A1 NO 2018050025 W NO2018050025 W NO 2018050025W WO 2018143819 A1 WO2018143819 A1 WO 2018143819A1
Authority
WO
WIPO (PCT)
Prior art keywords
pin
box
coupling assembly
portions
mating
Prior art date
Application number
PCT/NO2018/050025
Other languages
English (en)
Inventor
Olav Olsen
Original Assignee
Torsion Tool Company As
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
Priority claimed from NO20180062A external-priority patent/NO344834B1/en
Application filed by Torsion Tool Company As filed Critical Torsion Tool Company As
Priority to EP18706322.7A priority Critical patent/EP3577303B1/fr
Priority to EP20205320.3A priority patent/EP3822449B1/fr
Priority to US16/482,485 priority patent/US11015399B2/en
Publication of WO2018143819A1 publication Critical patent/WO2018143819A1/fr
Priority to US17/238,650 priority patent/US11624245B2/en

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
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • 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
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/046—Couplings; joints between rod or the like and bit or between rod and rod or the like with ribs, pins, or jaws, and complementary grooves or the like, e.g. bayonet catches

Definitions

  • the invention relates to the field of couplings for connecting elongated elements, such as pipes, tubes, shafts and axles. More specifically, the invention concerns a coupling assembly as specified in the preamble of claim 1, and a method of assembly as specified in the preamble of claim 17.
  • Pipe sections or tubular sections used for drilling deep wells in e.g. oil or gas reservoirs or geothermal formations utilize long sections of drill pipe, well casing or tubing that usually have a tapered, exteriorly-threaded male end called a pin member.
  • the pin members are threaded into corresponding couplings, collars or integral female pipe sections; their threaded ends are called a box member.
  • box members have an interiorly-threaded tapered thread corresponding to their respective pin members.
  • API American Petroleum Institute
  • casing tongs are used to make up casing and production pipe (or liner).
  • the externally-threaded member i.e. the "pin”
  • the externally-threaded member includes tapered threads, seal portions (i.e. metal to metal seal portions) and shoulders (e.g. torque shoulders) or these two combined.
  • the internally-threaded member i.e. the "box” also includes tapered threads, and seal portions and shoulders similarly to the pin.
  • the tapered threads are important for quickly and firmly fixing the pipe joint, the seal portions play a role of ensuring fluid and gas tight by bringing the box and the pins into metal contact at such portions, and the shoulders form a shoulder faces which play a role of abutments during make-up of the coupling.
  • Connecting ("making") and disconnecting ("breaking") a premium coupling requires higher torque than for an API coupling.
  • a premium coupling normally has thinner wall thicknesses than the API coupling, among other reasons to reduce hydrodynamic drag around the outside portion of the coupling. These thinner wall thicknesses place an increased demand on the tongs in order to avoid coupling deformation. Due to the higher make-up torque, a premium connection must withstand higher radial clamp force from the iron roughneck during make and break.
  • ETD extended-reach drilling
  • Circulating drill fluids in such long wells is also more complicated and demanding, as each connection represents a restriction in the annulus between the drill pipe and casing.
  • the prior art includes GB 2 064 041 A, which discloses a pipe connector for
  • the pipe connector comprises a tubular box member for connection to the end of a pipe and a tubular pin member for connection to the end of a pipe and which is telescopically receivable within the box member.
  • the members have corresponding generally frusto-conical peripheral surfaces which overlie one another when the members are fully telescoped together.
  • the surfaces comprise interengageable helical projection and groove means which extend therealong between end portions which are arranged to be a shrink fit one on the other.
  • the members of the connector are engageable and releasable by the use of fluid under pressure which is injected between the frusto-conical surfaces when the members are partially
  • a radial clearance is provided between the crest and root surfaces of the projection and groove means along which the pressurized fluid can flow.
  • US 4 648 627 discloses a connector assembly including a pin connector for receipt by a box connector.
  • the pin connector features a neck portion having external threads
  • the box connector features a collar portion having internal threads, generally complementary for meshing with the external threads.
  • the connectors may be threadedly joined together by longitudinally inserting the pin connector into the box connector, whereupon the two connectors are mutually sealed at two locations on opposite sides of the internal and external threads to define, with the threads, an annular region. Application of fluid pressure to the annular region may radially expand the region to permit further insertion of the pin connector into the box connector to mutually align the internal and external threads.
  • the connector assembly may be released by like application of fluid pressure to radially expand the annular region, or by mutual rotation between the pin and box connectors, to disengage the meshing between the internal and external threads.
  • US 2012/049513 Al shows a thread-less connection for coupling segments of a pipe (e.g. drill pipe used in the drilling of wellbores) longitudinally end to end.
  • the coupling includes a pin end having a groove for receiving a locking ring.
  • a box end has a groove for receiving the locking ring therein when the pin end is inserted into the box end.
  • the locking ring has an uncompressed diameter selected to exert lateral force on the groove in the box end when assembled to the pin end.
  • WO 2005/061852 Al shows a method of connecting tubular elements, particularly pipe for strings to be used in oil and gas wells.
  • the pin and box have complementary stepped profiles.
  • the pin and box are compressed and/or expanded, respectively, by means of a swaging die head.
  • a key issue in this publication is that - prior to assembly - one or both of the pin/box external surfaces are at least partially coated by plasma spraying with hard angular material.
  • US 2004/065446 Al shows an expander tool for connecting two tubulars by expanding a first tubular into a second surrounding tubular within a wellbore.
  • the lower casing string has been expanded using the expander tool into frictional contact with the inner wall of the upper casing string.
  • a sealing member is optionally disposed on the outer surface of the lower string of casing. The sealing member serves to provide a fluid seal between the outer surface of the lower string of casing and the inner surface of the upper string of casing after the lower casing string has been expanded.
  • US 2011/147009 Al shows a drill pipe connector assembly capable of connecting drill pipe segments without rotation.
  • the assembly includes the pin end of a first drill pipe stabbed within the connector end of a second drill pipe.
  • a connector nut is thread- connected or snap-locked to the connector end of the second drill pipe.
  • the connector nut includes a retaining shoulder cooperating with a beveled shoulder on the pin end of the first drill pipe to retain the first drill pipe.
  • the assembly includes seals to provide pressure integrity and prevent leaking. Cooperating rotational torque transfer profiles in the first and second drill pipes enable operational rotation of the drill string.
  • US 3 923 324 A describes a drill collar for a rotary drill string, including a threadless drill collar body having pins being frictionally mounted by means of a shrink-fit on opposite ends of the body, to corresponding boxes of opposite subs.
  • the frictional connection between the matching conical surfaces between conical pins of the drill collar body, and the corresponding subs, respectively, is accomplished as by the application of pressure fluid between the adjacent contacting surfaces, while
  • a port is provided in the box shaped portions of each sub for introduction of gaseous or hydraulic fluid pressure into the space between the box and pin, for laterally expanding the sub box during shrink-fitting thereof onto the corresponding pin.
  • GB 2 113 335 A describes a pipe connector comprising a tubular box member which is telescopically engageable with a tubular pin member, the members having
  • the surfaces are provided with interengageable projections and grooves which have varying axial extents and spacings so that, as the members are telescoped together, in all intermediate positions of the members, there is sufficient contact between crests of the grooves and surfaces between the projections to prevent inadvertent engagement of a projection with a groove.
  • the members may be fully engaged by the application of pressurized hydraulic fluid to the overlapped portions of the surfaces following initial contact, and may be disengaged in the same way, the pressurized fluid both expanding the box and/or contracting the pin to permit engagement and lubricating the crest surfaces of the projections and surfaces between the grooves to facilitate sliding of these surfaces over one another.
  • the box member may be provided with a radial duct for connection to a source of pressurized hydraulic fluid. The duct opens inwardly of the box into the region of the frusto-conical surface of the box which is provided with the projections or grooves.
  • axially extending grooves are provided in both the box member and the pin member, duct opening into groove in the box member.
  • the pressurized fluid is only required to assist engagement of the members after initial contact has been made.
  • the prior art also includes GB 2 180 312 A, GB 2 113 334 A, and US 4 561 683 A, describing configurations similar to those described above.
  • a coupling assembly for elongate elements comprising:
  • pin member having an outward-facing pin surface
  • box member having an inward-facing box surface, said pin surface and box surface configured for mating engagement
  • At least one bore having as a first opening a port configured for connection to an injection fluid reservoir and a second opening penetrating the pin surface or the box surface;
  • the pin surface comprises a plurality of pin protruding portions separated by pin recessed portions
  • the box surface comprises a plurality of box protruding portions separated by box recessed portions;
  • a pin protruding portion is shaped and dimensioned to fit into a designated box recessed portion
  • a box protruding portion is shaped and dimensioned to fit into a designated pin recessed portion.
  • Key-Loc This key-and-lock feature ensures that all ring- and-recess pairs must be aligned before the initial mating is complete.
  • the pin and box members comprise complementary and respective frusto-conical pin and box mating surfaces.
  • one or more portions of the surfaces are plain surfaces without helical threads or other pronounced protrusions configured for mating engagement. In one embodiment, one or more portions of the surfaces comprise a textured finish in order to augment static friction between the surfaces when the surfaces are connected.
  • the pin protruding portions, pin recessed portions, box protruding portions and box recessed portions are preferably circular portions, extending around the respective surface.
  • the mating surfaces may comprise single frusto-conical sections, but may also comprise several frusto-conical sections with different taper angles in order to obtain an optimally distributed contact pressure between the mating surfaces.
  • the “Key-Loc” concept contributes to the axial/tensile strength and/or torque performance, as well as positioning of the connected coupling, of the connected coupling.
  • the “Key-Loc” concept contributes to avoiding progressive failure mechanisms, such as micro-slip, from occurring under repetitive loading cycles, especially in a so-called "dog leg” situation during directional drilling.
  • the axial widths of the pin portions decrease in the direction towards a pin member free end, and the axial widths of the box portions increase in the direction towards a box member free end.
  • the larger widths are associated with the larger diameter of the frusto-conical shape of the pin and box surfaces, and the smaller widths are associated with the smaller diameter of the frusto-conical shape of the pin and box surfaces.
  • the coupling assembly comprises a friction-enhancing device, configured for being arranged on the pin surface.
  • the pin surface may comprise a plurality of stepped surfaces of diminishing surface radius towards the pin free end
  • the box surface may comprises a plurality of stepped surfaces of increasing surface radius towards the box free end.
  • a region of the box surface comprises a wall thickness which is less than the thicknesses of the adjacent box walls.
  • a region of the pin surface may comprise a wall thickness which is less than the thicknesses of the adjacent pin walls.
  • a region of the box surface comprises a material of a lower modulus of elasticity than the material of a corresponding region of the pin surface, or vice versa.
  • At least a portion of the pin and box mating surfaces comprise grooves.
  • the grooves may extend in a double-helical formation.
  • the fluid pressure and axial force in step b) are balanced and controlled to ensure a predetermined elastic deformation and prevent plastic
  • Step a) may be performed until the pin and box gaskets or seals engage and facilitates the injection of a fluid between the pin and the box.
  • the pin and box may comprise more than one seal, in order to maintain the sealing function when crossing a protrusion or recess.
  • one or more injection channels may be located on the pin shoulder, to facilitate easy access and port protection during operation.
  • the invented coupling assembly may be connected and disconnected without rotational motion (as is necessary with a threaded connection), only axial motion and application of hydraulic pressure are required.
  • the pin and box surfaces may be smooth or comprise complementary stepped profiles (protruding and recessed portions). Adhesion between the surfaces may be augmented by friction coating (e.g. electrode-less nickel coating with diamonds or similar), a serrated surface, particles in the injected fluid, "double- helix engravement" (fluid pressure distribution and friction particles distribution), separate friction sleeves, or/and by increasing surface roughness (by e.g. sandblasting or similar).
  • the hydraulic fluid may be water or glue with or without a corrosion inhibitor, with or without particles , together with a surface structure or/and a separate friction shim, or/and an applied friction increasing coating, seeking the highest possible friction factor.
  • the invented coupling exhibits improved performance over the prior art, in that it can handle combined torque, tension and compression.
  • the invented coupling assembly may be useful for connecting any elongated elements that may rotate and transfer torque; such as pipes, propeller shafts, axles, as well as various tubulars such as drill pipe (drill string) and casing for casing-drilling.
  • the invented coupling assembly transfers torque equally well in both rotational directions (as opposed a prior art threaded coupling).
  • This "bidirectional" torque capability is particularly useful is a drill pipe is jammed and it is necessary to counter-rotate to release the drill bit or other dowhhole tools.
  • the coupling assembly may also be useful for non-rotating elongated elements, such as rods, different process pipe lines, borehole casings and liners.
  • connections between pipe joint having electrical (power, signals) cables are accomplished by elaborate rotatable connections or by inductive couplings.
  • the cables may be connected by a metal-to-metal connection, for example by embedded and electrically insulated metal portions in the pin free end and the box inward shoulder.
  • Such "plug- and-socket" connection is possible with the invention, as the pipe joints need not rotate during the connection process, but merely move axially towards each other.
  • the electrical connectors may also be used to verify that the connection has been completed.
  • the invention may also replace the prior art top drive saver sub connection, which is time consuming to replace.
  • the invention may replace all threaded connections.
  • the axial movement of the invented coupling assembly will make design of connections and internal components much easier, as rotation is not required to make the connection.
  • the invention may replace complex and time- consuming welding operations associated with the connection and laying of trunk lines and pipes, both on the seabed and on land.
  • the invention is suitable with any materials commonly used in pipes, propulsion shafts, axles, drill pipe (drill string), drilling risers, rods, borehole casings, liners, etc., such as stainless steel.
  • the invented coupling also lends itself to the use of various steel grades (e.g. lOOksi box and 130ksi pin), light-weight materials, such as fibre- reinforced composites, titanium, aluminum and similar alloys. That is, both the coupling and the associated elongated elements may be made of such materials (or in
  • Figure 1 is a perspective view of a first embodiment of the coupling assembly according to the invention, in a disconnected state;
  • Figure 2 is a sectional view of the coupling assembly shown in figure 1, in a plane along the longitudinal central axis x-x, in a disconnected state;
  • Figure 3 corresponds to figure 2, but shows the coupling assembly in a partly connected state
  • Figure 4 corresponds to figure 3, but shown the coupling assembly in a connected state
  • Figure 5 is a perspective and transparent view of the coupling assembly shown in figure 1, in a connected state, i.e. corresponding to the state shown in figure 4;
  • Figure 6 is a schematic sectional view of an embodiment of the coupling assembly according to the invention, in a plane along a longitudinal central axis, in a disconnected state;
  • Figure 7 corresponds to figure 6, and illustrates a method of connecting the pin member and box member
  • Figure 8 is a perspective view of a second embodiment of the coupling assembly according to the invention, in a disconnected state;
  • Figure 9 is a sectional view of the coupling assembly shown in figure 8, in a plane along the longitudinal central axis x-x, in a disconnected state;
  • Figure 10 corresponds to figure 9, but shows the coupling assembly in a partly connected state
  • Figure 11 is an enlarged view of the section marked "B" in figure 10;
  • Figure 12 corresponds to figure 11, but shows a state in which the coupling assembly has been further connected
  • Figure 13 corresponds to figure 11 but shows a state in which the coupling assembly has been fully connected
  • Figure 14 corresponds to figure 9, but shows a state in which the coupling assembly has been fully connected, i.e. corresponding to the state shown in figure 13;
  • Figure 15 shows an embodiment of a pin surface
  • Figure 16 an enlarged view of the section marked "A" in figure 4.
  • Figure 17 is a transparent side view of an alternative embodiment of a box and pin, in which portions of the pin and the box have a reduced wall thickness;
  • Figure 18a is an enlarged view of the section marked "C" in figure 17;
  • Figure 18b is an enlarged view of the section marked "D" in figure 17;
  • Figure 19a is a perspective view of an embodiment of the invented pin, in association with a friction sleeve
  • Figure 19b corresponds to figure 19a, and illustrates the friction sleeve fitted onto the end of the pin
  • Figure 20 is a perspective view of an alternative embodiment of the invented pin, having a stepped pin profile
  • Figure 21 is a sectional perspective view of an embodiment of a pin-and-box coupling having dual seals, in a partially interconnected state
  • Figure 22 is an enlarged view of the section marked "G" in figure 21;
  • Figure 23 is a side view of the section marked "H" in figure 22;
  • Figure 24 is a transparent perspective view of an embodiment of the invented pin, illustrating wires or cables extending inside the pin body and an electrical contact surface;
  • Figure 25 is a perspective view corresponding to that of figure 24, illustrating an electrical contact surface
  • Figure 26 is a variant of the embodiment illustrated in figures 24 and 25, in which more than one wire may be connected to a contact surface.
  • the invented coupling assembly comprises a first mating member 5 and a second mating member 6.
  • the first mating member is a pin member 5 which forms an end portion of a first pipe 1 having an internal bore 3.
  • the second mating member is a box member 6 which forms an end portion of a second pipe 2 having an internal bore 4.
  • the pipes 1,2 may for example be drill pipes, liners, casing joints or other tubular elements configured for rotational movement and for conveying a fluid.
  • the pipes may be replaced by other elongated elements such as shafts and axles.
  • the invention shall therefore not be limited to a coupling assembly for tubular elements, but be applicable to a coupling assembly for any elongated elements.
  • the elongated elements 1,2 will be referred to a tubulars 1,2.
  • the pin member 5 comprises a first mating surface 12, hereinafter also referred to as a pin surface 12, here in the shape of a frusto-conical surface facing outwards with respect to the central axis x-x.
  • the pin surface ends at a pin shoulder 14.
  • the box member 6 comprises a second mating surface 13, hereinafter also referred to as a box surface 13, here in the shape of a frusto-conical surface facing inwards with respect to the central axis x-x.
  • the box surface ends at an internal box shoulder 16.
  • Seals may be arranged at the pin shoulder 14 and the pin free end 15, or (more common) at the pin free end 15 and the box inner shoulder 16.
  • the seals may be integrated (as profiles in the pin and/or box) or may be removable, and may comprise materials such as elastomers and/or metals. It should be understood, however, that the pin-and-box coupling may also be used without seals.
  • the pin surface 12 and box surface 13 are plain surfaces, without helical threads or other pronounced protrusions configured for mating engagement.
  • the pin and box surfaces are thus generally smooth, but may comprise a textured finish (roughness) of a certain topography in order to augment static friction (and hence adherence) between the pin and box when connected.
  • Such topography may be obtained by friction coating (by for example nickel coating with diamonds) or by increasing surface roughness through sandblasting or similar.
  • the pin and/or box surfaces, or portions of these surfaces may be furnished with serrations in order to increase the torque capacity of the connected coupling.
  • the frusto- conical pin surface 12 is provided with grooves 23, extending in a double-helical formation 22.
  • the grooves preferably are quite shallow in relation to the dimensions of the pin and box.
  • the groove 23 depth may be on the order of one tenth of a millimeter for a pin having an outer diameter (OD) of 120mm.
  • OD outer diameter
  • a double-helix may also be formed in the box surface, either in lieu of the double -helical formation 22 or as supplement to it.
  • the helical grooves serve two functions, by providing a) fluid distribution channels during mating and b) distribute friction- enhancing fluid with particles.
  • an opening (a port) 9a which is the outward opening of a bore 9 extending through the box member wall and into the box member interior, penetrating the box surface 13 in an inward opening 9b (another illustration of the bore 9 is provided in i.a. figure 6 and figure 16).
  • the bore 9 therefore provides a fluid access channel into the box. It should be understood that although only one bore 9 is shown in the figures, a practical embodiment of the invention may comprise several bores.
  • Figure 3 illustrates an initial step in a mating process of the pin-and-box coupling shown in figure 1 and figure 2, in which the pin member 5 has been inserted a distance into the box member 6.
  • Figure 4 and figure 5 illustrate the state in which the mating process has been completed and the connection between the pin member and box member has been made.
  • Figure 6 illustrates an embodiment of the invention that in principle is similar to the embodiment described above with reference to figures 1-5.
  • figure 6 shows how seals 7, 8 are arranged in the region of the pin shoulder and pin free end, respectively.
  • the seals may be arranged on the box instead, and that a combination of the two arrangement is conceivable.
  • the seals serve to form a frusto-conical annular cavity during the initial mating, to contain injected fluid.
  • Figure 6 also shows how a pressurized fluid reservoir 10 is connected to the bore 9 via a conduit 10a.
  • the reservoir 10 preferably contains a liquid, such as (but not necessarily limited to) water, which may be injected under pressure into the box member 6, controlled via the control valve 11.
  • Figure 6 also illustrates an alternative configuration in which the reservoir 10 is connected to a bore 9' which extends through the pin member 5 body, and where the bore 9' penetrates the pin surface 12 with the opening 9b.
  • the effect of this configuration is equivalent to the configuration in which the bore 9 extends through the box member 5 wall inasmuch as both bore configuration deposit the injected fluid at more or less the same location during a mating operation.
  • connecting the reservoir 10 to the bore 9' extending through the pin member 5 body may have certain operational advantages.
  • the wall thicknesses of the pin and box correspond inversely in the illustrated embodiment. That is, the wall thickness of the pin free end 15 corresponds (i.a. is more or less equal) to the wall thickness of the box outer end 17, and the wall thickness of the pin rear end (in the region immediately before the pin shoulder 14) corresponds to the wall thickness of the box rear end (in the region immediately before the box shoulder 16).
  • the fluid pressure inside the cavity V causes elastic deformation in the pin member and box member, such that the box member wall expands radially (see arrows "E” in figure 7) and the pin member is compressed radially (see arrows "C” in figure 7).
  • This deformation allows the pin member to be inserted an additional distance d into the box member.
  • the fluid pressure is released, causing the pin and box members to resume their original shape and thus forming a tight and high-tension connection.
  • Figures 8-14 illustrate a second embodiment of the invented coupling assembly.
  • This embodiment has several similarities to the embodiments described above with respect to figures 1-7 (and may thus be combined with that embodiment), but exhibits an additional feature that the pin surface 12 and box surface 13 each comprise radially protruded portions and radially recessed portions. More specifically, referring initially to figure 9, the pin surface 12 comprises successive (in the axial direction) circular and radially protruding portions I8 1 -3 (hereinafter referred to as "pin rings”) and circular and radially recessed portions 19i_ 4 (hereinafter referred to as "pin recesses").
  • Reference number 8' denotes a seal groove, in which a seal (not shown) may be arranged as described above with reference to figure 6. It should be understood that metal seals (embedded or inserted) may also be used, a purpose being to form a frusto-conical annular cavity into which fluids may be injected.
  • the box surface 13 comprises successive (in the axial direction) circular and radially protruding portions 20i_ 3 (hereinafter referred to as “box rings”) and circular and radially recessed portions 21 1-4 (hereinafter referred to as “box recesses”).
  • box rings circular and radially protruding portions 20i_ 3
  • box recesses circular and radially recessed portions 21 1-4
  • the axial widths of the pin rings 18i_ 3 and pin recesses 19i_ 4 decrease in the direction towards the pin free end 15; that is, the widths are greater in the region of the pin shoulder 14 than in the region of the pin free end 15.
  • the axial widths of the box rings 20 1-3 and box recesses 21 1-4 increase in the direction towards the box free end 17; that is, the widths are smaller in the region of the box inner shoulder 16 than in the region of the box free end 17 (opening).
  • wi represents the largest width
  • w 2 represents a width smaller than w 2
  • w n represents the smallest width.
  • the rings and recesses serve as individual abutment surfaces.
  • Any pin ring 18 n is shaped and dimensioned to fit with a designated box recess 21 n
  • any box ring 20 n is shaped and dimensioned to fit with a designated pin recess 19 n .
  • This is illustrated in figure 13.
  • Such key-and-lock concept (hereinafter referred to as "Key-Loc”) ensures that all ring- and-recess pairs must be aligned before the initial mating is complete.
  • the regions on the pin and box furnished with the above-mentioned rings and recesses will thus be referred to as "Key-Loc" regions K (see e.g. figure 14).
  • the “Key-Loc” concept contributes to the axial/tensile strength and/or torque performance of the connected coupling.
  • the “Key-Loc” concept contributes to avoiding progressive failure mechanisms, such as micro-slip, from occurring under repetitive loading cycles, especially in a so-called "dog leg” situation during directional drilling.
  • portions of the pin 5 and box 6 are (in the region of the respective surfaces 12, 13) formed with wall thicknesses that are thinner than the wall thicknesses of adjacent portions.
  • the region R b of the box 6 has a wall thickness t a which is less than the thicknesses t c of the adjacent box walls.
  • the region R p of the pin 5 has a wall thickness t d which is less than the thicknesses t e , t f of the adjacent pin walls. It should be noted that t a and t d do not have to be constant.
  • the regions R b , R p of reduced wall thickness generally correspond with the respective pin and box contact surfaces (e.g.
  • the regions R b , R p correspond to the above-mentioned pin and box "Key-Loc" regions. It will be understood that the walls of reduced thickness (t a , t d ) will deform elastically relatively more than the adjacent walls when fluid is applied between the pin and box to make or break a connections as described above with reference to figures 6 and 7. This "ballooning" effect is particularly advantageous as the enhanced elastic deformation in these regions allows the "Key-Loc" rings and recesses to be more pronounced (i.e. taller and deeper) that what is possible if the wall thicknesses are uniform.
  • Figures 19a and 19b illustrate another friction-enhancing device, in the form of a friction sleeve 24 which may be arranged on the free end of the pin surface 12, outside of the "Key-Loc" region K.
  • the friction sleeve may comprise a coating of a friction- enhancing materials (e.g. diamond coating) which per se is known in the art. The coating may be applied on both sides of the sleeve 24.
  • a friction- enhancing materials e.g. diamond coating
  • the coating may be applied on both sides of the sleeve 24.
  • Figure 20 illustrates an alternative embodiment of the invented pin, having a stepped pin surface, such that the pin surface radius is diminishing, in steps, towards the pin free end 15.
  • three pin surfaces 12a, 12, 12c are shown, but it should be understood that more or fewer stepped surfaces are possible.
  • the pin free end 15 and the transition between each step comprise a chamfered portion 25.
  • the box surface will have a corresponding stepped surface.
  • the pin surfaces 12a-c may be cylindrical, or frusto- conical. In the latter case, the pin taper angles increase towards the pin free end, and the box taper angles decrease correspondingly.
  • One or more of the pin surfaces may also comprise a "Key-Loc" region.
  • Figures 21, 22, 23 illustrate an embodiment of a pin-and-box coupling having dual seals.
  • the figures illustrate two seal grooves 8a, 8b in the box surface (but it should be understood that a corresponding seal configuration may be incorporated in near the pin free end. It should also be understood that the figures illustrate the seal grooves only, but the skilled person will understand that appropriate seals may be installed in the grooves 8a,b. Seals may also be integrated in the pin and box, as described above. It should also be understood that more than two seals may be included.
  • a purpose of the dual seals, which is particularly visible in figure 23, is to preserve the sealing function the pin (or box) slides across a protrusion ("ring") or recess.
  • Figures 24 and 25 illustrate an embodiment in which electrical wires 26 extending along the tubular (or shaft) 1 and terminating at a ring contact 27a on the pin 5 (a
  • wires may be connected by a metal-to-metal or plug-and-socket connection when the pin and box are mated.
  • the contact rings may be arranged at one or more selected pin/bo rings or recesses, whereby the electrical contacts may serve as a tool for verifying proper connection between the pin and box.
  • Figure 26 illustrates a similar configuration, illustrating how several wires (indicated as 28a,b) may be connected to a contact surface. It should be understood that a plurality of wires and contacts may be incorporated in the pin and box. It should also be understood that the wires may be embedded in the tubular wall or be arranged inside the tubular (or shaft).
  • break-out is accomplished by applying a suitable liquid pressure through one (or more) of the conduits (9; 9') similarly to the procedure explained above, whereupon the pin may be released (and withdrawn) from the box.
  • the invented coupling assembly is without conventional threads and therefore requires no rotation during connection or disconnection.
  • the time required to connect and disconnect the coupling is therefore reduced significantly.
  • the assembly data will be a part of the coupling operation verification.
  • the pin and box surfaces meet and furtlier advancement is not possible, due to contact between the pin member shoulder 14 and box free end 17, the hydraulic pressure between the pin and box surfaces is released, whereby the coupling is locked by means of circular preload and friction.
  • Using the enveloping contact surface will remove restrictions associated with traditional API/DSC threaded connections.
  • the invented coupling assembly will also allow the pipe joint cross-section to be reduced, a there is no need for traditional iron-roughneck, manual rig tongs or bucking units. On- site handling challenges are therefore mitigated.
  • the hydraulic friction coupling as described above will also allow drilling of significantly longer and deviated wellbores, as friction loss by circulating drilling fluid is reduced, and the torque capacity of the pipe joint is increased.
  • the invented coupling assembly will also lower the sequence time (make / break) significantly and hence the cost of drilling.

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

Abstract

L'invention concerne un ensemble d'accouplement pour des éléments allongés (1, 2), ledit ensemble comprenant un élément de broche (5) et un élément de boîte (6), lesdits éléments de broche et de boîte ayant des surfaces de contact de broche et de boîte tronconiques complémentaires et respectives (12, 13). Un alésage (9, 9') a pour première ouverture (9a) un orifice conçu pour être raccordé à un réservoir de fluide d'injection (10), et une seconde ouverture (9b) pénétrant dans la surface de contact de broche (12) ou dans la surface de contact de boîte (13). Les surfaces (12, 13) peuvent être des surfaces lisses sans filets hélicoïdaux ou autres saillies prononcées, conçues pour une mise en prise homologue, mais elles comprennent une finition texturée afin d'augmenter le frottement statique entre les surfaces (12, 13) lorsque les surfaces sont raccordées. La surface de broche peut comprendre une pluralité de parties de broche en saillie (181-n) séparées par des parties de broche montées en retrait (191-n), et la surface de boîte (13) comprend une pluralité de parties de boîte en saillie (201-n) séparées par des parties de boîte montées en retrait (211-n). Les parties de broche en saillie (18n) sont formées et dimensionnées de manière à s'ajuster dans une partie de boîte montée en retrait désignée (2n), et les parties de boîte en saillie (20n) sont formées et dimensionnées de manière à s'ajuster dans une partie de broche montée en retrait désignée (19n).
PCT/NO2018/050025 2017-01-31 2018-01-30 Accouplement WO2018143819A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18706322.7A EP3577303B1 (fr) 2017-01-31 2018-01-30 Accouplement
EP20205320.3A EP3822449B1 (fr) 2017-01-31 2018-01-30 Accouplement
US16/482,485 US11015399B2 (en) 2017-01-31 2018-01-30 Coupling assembly for elongate elements
US17/238,650 US11624245B2 (en) 2017-01-31 2021-04-23 Coupling assembly for elongate elements

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
NO20170150 2017-01-31
NO20170150 2017-01-31
NO20180062A NO344834B1 (en) 2017-01-31 2018-01-15 A coupling
NO20180062 2018-01-15

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US16/482,485 A-371-Of-International US11015399B2 (en) 2017-01-31 2018-01-30 Coupling assembly for elongate elements
US17/238,650 Continuation US11624245B2 (en) 2017-01-31 2021-04-23 Coupling assembly for elongate elements

Publications (1)

Publication Number Publication Date
WO2018143819A1 true WO2018143819A1 (fr) 2018-08-09

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ID=61249681

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PCT/NO2018/050025 WO2018143819A1 (fr) 2017-01-31 2018-01-30 Accouplement

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Country Link
WO (1) WO2018143819A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111379527A (zh) * 2018-12-28 2020-07-07 中国石油天然气股份有限公司 石油钻杆
NO20220086A1 (en) * 2022-01-21 2023-07-24 Torsion Tool Company As A clamp device
NO20221334A1 (en) * 2022-12-13 2024-06-14 Torsion Tool Company As A coupling assembly

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2296198A (en) * 1938-09-22 1942-09-15 Boynton Alexander Threadless drill stem
US3923324A (en) 1973-03-20 1975-12-02 Christensen Diamond Prod Co Drill collar with thread connections
GB2064041A (en) 1979-11-19 1981-06-10 Hunting Oilfield Services Ltd Improvements in and relating to pipe connectors
GB2113335A (en) 1982-01-18 1983-08-03 Hunting Oilfield Services Improvements in and relating to pipe connectors
GB2113334A (en) 1982-01-18 1983-08-03 Hunting Oilfield Services Improvements in and relating to pipe connectors
US4561683A (en) 1982-01-18 1985-12-31 Hunting Oilfield Services (Uk) Limited Pipe connector with interengageable tubular pin and tubular box members
US4648627A (en) 1984-01-18 1987-03-10 Dril-Quip, Inc. Stabbing connector
GB2180312A (en) 1985-07-31 1987-03-25 Pond Ltd R J Pipe connection joints
US4830408A (en) * 1981-06-05 1989-05-16 Dril-Quip, Inc. Connector assembly
US20040065446A1 (en) 2002-10-08 2004-04-08 Khai Tran Expander tool for downhole use
WO2005061852A1 (fr) 2003-12-23 2005-07-07 Bp Exploration Operating Company Limited Systeme de raccordement de conduite extensible non filete
US7011344B1 (en) * 1999-07-12 2006-03-14 Bakke Technology As Connector and method of use of the connector
US20110147009A1 (en) 2009-12-23 2011-06-23 Expert E&P Consultants, LLC Drill Pipe Connector and Method
US20120049513A1 (en) 2010-09-01 2012-03-01 Herrera Derek F Non Threaded Drill Pipe Connection

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2296198A (en) * 1938-09-22 1942-09-15 Boynton Alexander Threadless drill stem
US3923324A (en) 1973-03-20 1975-12-02 Christensen Diamond Prod Co Drill collar with thread connections
GB2064041A (en) 1979-11-19 1981-06-10 Hunting Oilfield Services Ltd Improvements in and relating to pipe connectors
US4830408A (en) * 1981-06-05 1989-05-16 Dril-Quip, Inc. Connector assembly
GB2113335A (en) 1982-01-18 1983-08-03 Hunting Oilfield Services Improvements in and relating to pipe connectors
GB2113334A (en) 1982-01-18 1983-08-03 Hunting Oilfield Services Improvements in and relating to pipe connectors
US4561683A (en) 1982-01-18 1985-12-31 Hunting Oilfield Services (Uk) Limited Pipe connector with interengageable tubular pin and tubular box members
US4648627A (en) 1984-01-18 1987-03-10 Dril-Quip, Inc. Stabbing connector
GB2180312A (en) 1985-07-31 1987-03-25 Pond Ltd R J Pipe connection joints
US7011344B1 (en) * 1999-07-12 2006-03-14 Bakke Technology As Connector and method of use of the connector
US20040065446A1 (en) 2002-10-08 2004-04-08 Khai Tran Expander tool for downhole use
WO2005061852A1 (fr) 2003-12-23 2005-07-07 Bp Exploration Operating Company Limited Systeme de raccordement de conduite extensible non filete
US20110147009A1 (en) 2009-12-23 2011-06-23 Expert E&P Consultants, LLC Drill Pipe Connector and Method
US20120049513A1 (en) 2010-09-01 2012-03-01 Herrera Derek F Non Threaded Drill Pipe Connection

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111379527A (zh) * 2018-12-28 2020-07-07 中国石油天然气股份有限公司 石油钻杆
NO20220086A1 (en) * 2022-01-21 2023-07-24 Torsion Tool Company As A clamp device
NO347916B1 (en) * 2022-01-21 2024-05-13 Torsion Tool Company As A clamp device
NO20221334A1 (en) * 2022-12-13 2024-06-14 Torsion Tool Company As A coupling assembly

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