EP2260172B1 - Accélérateur de forage de puits et connexion tubulaire - Google Patents

Accélérateur de forage de puits et connexion tubulaire Download PDF

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Publication number
EP2260172B1
EP2260172B1 EP09720006.7A EP09720006A EP2260172B1 EP 2260172 B1 EP2260172 B1 EP 2260172B1 EP 09720006 A EP09720006 A EP 09720006A EP 2260172 B1 EP2260172 B1 EP 2260172B1
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EP
European Patent Office
Prior art keywords
housing
drive
drill bit
connection
drive shaft
Prior art date
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EP09720006.7A
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German (de)
English (en)
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EP2260172A1 (fr
EP2260172A4 (fr
Inventor
Bradley R. Cote
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BBJ Tools Inc
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Priority to PL09720006T priority Critical patent/PL2260172T3/pl
Publication of EP2260172A1 publication Critical patent/EP2260172A1/fr
Publication of EP2260172A4 publication Critical patent/EP2260172A4/fr
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/006—Mechanical motion converting means, e.g. reduction gearings
    • 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
    • E21B17/0426—Threaded with a threaded cylindrical portion, e.g. for percussion rods
    • 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
    • E21B17/043—Threaded with locking means
    • 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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/10—Down-hole impacting means, e.g. hammers continuous unidirectional rotary motion of shaft or drilling pipe effecting consecutive impacts

Definitions

  • the present invention relates to down hole tools and, in particular, a wellbore drilling accelerator for applying an axially directed percussive effect to a drill bit and a tubular connection.
  • a "percussionized" drill bit should be an efficient drilling tool.
  • a common problem experienced in down hole operations relates to the effect of torque on tubular connections. This problem may be exaggerated when torque is generated in the operation of a tool down hole.
  • WO 00/55468 A1 discloses an assembly having a bend housing and a reciprocating hammer for driving a bit for forming a borehole in rock.
  • WO 00/55468 teaches a downhole hammer that may be driven by either a liquid or gas medium.
  • a further assembly is disclosed in WO 98/48141 ; it teaches a rotatable hollow shaft including fluid transfer ports extending through a stationary lobed sleeve; rotation of the hollow shaft within the lobed sleeve periodically covers and uncovers the transfer ports resulting in a periodic fluctuation in fluid pressure within the BHA used to reciprocate the drill bit.
  • WO 00/55468 nor WO 98/48141 disclose an assembly for mechanically converting rotational drive into percussive motion.
  • a method for accelerating the drilling penetration of a rotary driven drill bit comprising: providing a positive displacement motor including a motor housing, a fluid discharge and a rotor powered by fluid pressure; providing a drill bit; providing a drilling accelerator including a housing and a drive connection to mechanically convert rotational drive to axially directed percussive motion; connecting the drilling accelerator below the motor including connecting the housing to move with the motor housing, connecting the drive connection to be driven rotationally by the rotor and bringing the fluid passage into communication with the fluid discharge; connecting the drill bit below the drilling accelerator with the drive connection in drive communication with the drill bit; pumping fluid through the motor to drive the rotor and the drive connection to rotate and to generate axial percussive motion which is communicated from the drive connection to the drill bit and; discharging fluid from the fluid discharge to pass through the drilling accelerator and the drill bit.
  • drilling accelerator comprising: a housing including an upper end and a lower end; a drive connection including an upper axially rotatable drive shaft for receiving an input of rotational motion, a rotational to axial mechanical drive converter in communication with the upper axially rotatable drive shaft for converting the input of rotational motion to an axial sliding motion; a lower longitudinally moveable drive shaft in communication with the rotational to axial mechanical drive converter to receive the axial sliding motion from the rotational to axial mechanical drive converter and a lower drill bit installation site connected to the lower longitudinally moveable drive shaft for receiving the axial sliding motion and capable of conveying axial percussive motion there through, the lower drill bit installation site telescopically mounted adjacent the lower end of the housing and slidably moveable relative thereto.
  • a drilling accelerator can be installed in a drill string to facilitate wellbore drilling operations. Drilling accelerators are sometimes alternately called percussive adapters, drilling hammers, and fluid hammers. A drilling accelerator creates a percussive effect applied to the drilling bit that alone or with rotary drive of the bit causes the drill bit to drill into a formation.
  • a drilling accelerator 10 can include a drive converter connection that accepts rotational drive about axis x from a torque generating device 12 above and converts that rotational drive to an axially directed percussive force that is output to a bit box sub 14 positioned below the drilling accelerator.
  • a drill string is in use with a drill bit 16 installed in the bit box and the drill bit being rotationally driven, arrow R, the axially directed percussive force, arrow P, applied to the bit box sub is conveyed to the drill bit and can facilitate drilling at the drill bit.
  • Drilling accelerator 10 may include an outer housing 18 including an upper end 18a and a lower end 18b. Outer housing 18 is rugged, being exposed on its external surface 18c to the wellbore annulus and houses therewithin the drive components for generating a percussive force.
  • the housing can be formed in sections and connected together by various means such as by welding, interlocks or threaded engagement, as shown at connections 21.
  • Upper end 18a of the housing is formed for connection into a drill string, such as by forming as a threaded connection.
  • Lower end 18b of the housing is formed for connection, shown herein directly but may be indirect, to a bit box sub 14.
  • Bit box sub 14 has formed therein a site, such as, for example, threaded bit box 20, for accepting connection of a drill bit.
  • Bit box sub 14 is connected for rotational movement with housing 18 through a splined connection 22.
  • connection 22 permits axial sliding motion of the bit box sub within housing 18, such axial sliding motion being generated by a connection to the drive connection of drilling accelerator 10, the drive connection is intended to drive the bit box sub axially to apply a percussive force at any drill bit connected into the bit box during drilling.
  • Seals may be provided, such as O-rings and wiper seals 24 to resist fluid passage between the housing and the bit box sub, etc.
  • the drive connection includes an axial shaft 30 supported in bearings 32 to convey rotational drive from an input end 30a to an output end 30b which carries a bevel gear 34.
  • This bevel gear 34 meshes with a second bevel gear 36 mounted on transverse shaft 38 which is rotatably supported in the housing.
  • Transverse shaft 38 includes an eccentric 40 thereon which drives a drive shaft 42.
  • Drive shaft 42 includes a strap 44 with a bearing 46 therein in which eccentric 40 rotates.
  • Drive shaft 42 at its opposite end includes an eye 48 through which the drive shaft is pinned via pin 50 to a percussion adapter 52 secured to bit box sub 14 for a drill bit.
  • Rotation in shaft 30 through reduction gears 34, 36 will impart on the percussive adapter 52 an axially directed reciprocation determined by the throw of eccentric 40. This axially directed reciprocation is then conveyed directly to any bit secured in the bit box 20 of the bit box sub.
  • the input torque may be generated by a mud motor.
  • axial shaft 30 may be connected to a rotor of a mud motor such that any rotation of the rotor, by flow of drilling fluid through the motor, may be conveyed to the drive connection.
  • the mud motor may include a positive displacement-type motor (PDM), which uses pressure and flow of the drilling fluid to turn a rotor within a stator.
  • PDM positive displacement-type motor
  • Shaft 30 can be connected directly or indirectly to the rotor, as through threaded connection 60. Where a bent sub is positioned between the motor and the drilling accelerator, a universal connector may be positioned therebetween to convey rotation from the rotor to the axial shaft.
  • the accelerator may include drilling fluid passages 54 that can be connected in communication with the motor discharge and that extends from end 18a, about the drive connection components, to passages 62 through adapter 52 into a bore 56 of bit box sub 14.
  • Passages 54 may be formed, as by milling, etc. through outer housing 18 and can be directed by ports, seals, etc. from the discharge of the pump to passages 62 into the inner bore of the bit box.
  • outer housing 18 may require thickening or laminate/telescopic construction to accommodate the passages.
  • Gears 34, 36 and other moving parts may be grease packed for lubrication thereof.
  • a compensator may be provided, for example, in end 30a to accommodate or alleviate pressure differentials which may occur during down hole operations.
  • the embodiment of Figure 2 operates to drill a borehole by applying a percussive force through the drill bit to the formation, with or without rotating the drill string from surface.
  • the drilling accelerator may include a drive system for conveying rotational drive from the motor to the drill bit in addition to the percussive forces generated thereby.
  • a drilling accelerator including an outer housing 118 including a lower end 118b, an axial shaft 130 (shown in part) to convey rotational drive from an input to a gear transmission, a shaft 138 including an eccentric 140 for driving a drive shaft 142 and a percussion adapter 152 formed integral with a bit box sub 114 for a drill bit.
  • the gear transmission includes gears to convey both rotational and axially reciprocal motion to the bit box sub.
  • gear transmission includes a first gear 135 that accepts input from bevel gear 134 and meshes with a gear 136 that drives shaft 138.
  • Gear 136 also meshes with a second bevel gear 139 that drives the rotation of an inner housing 166.
  • Inner housing 166 extends and rotates within outer housing 118.
  • Inner housing 166 is connected at its lower end for rotational transmission to bit box sub 114.
  • bit box sub 114 is connected for rotational movement with housing 166 through a splined connection 122 such that any bit installed in the bit box can be driven to rotate by rotation conveyed from shaft 130.
  • Connection 122 also permits axial sliding motion of the bit box sub within housing 166, such axial sliding motion being generated by a connection to shaft 138 of the drilling accelerator, the shaft intended to drive the bit box sub axially to apply a percussive force at any drill bit connected into the bit box during drilling, while gear 139 and housing 166 drive rotation of the bit box sub.
  • Seals may be provided, such as O-rings and wiper seals 124 to resist fluid passage between the housing and the bit box sub, etc.
  • Outer housing 118 can extend down to protect the inner housing.
  • Bearings 168 and seals 124a may be provided to facilitate rotation and seal against fluid and debris migration between the parts.
  • drive shaft 142 experiences differential rotation therealong: where upper portion 142a is not rotatably driven, but lower portion 142b is pinned to percussion adapter and is rotatably driven.
  • a bearing 170 can be provided along its length. Bearing 170 allows rotational motion therein of part 142b about its long axis relative to part 142a, but resists axial sliding motion such that axial percussive movement generated by the throw of eccentric 140 is conveyed along the shaft rather than being absorbed.
  • the input torque may be generated by a mud motor.
  • axial shaft 130 may be connected to a rotor of a mud motor such that any rotation of the rotor, by flow of drilling fluid through the motor, may be conveyed to the drive connection.
  • cam and cam follower can be used to replace an eccentric and connected drive shaft (i.e. items 40, 42 of Figure 2 ).
  • cams it may be useful to use weight on bit to maintain the contact between the cam parts.
  • another drilling accelerator 210 may include an outer housing 218 including an upper end 218a and a lower end 218b.
  • Outer housing 218 is rugged, being exposed on its external surface 218c to the wellbore annulus and houses therewithin the drive components for generating a percussive force to be applied to a bit connected therebelow.
  • the housing can be formed in sections and connected together by various means such as by welding, interlocks or threaded connections 280.
  • Upper end 218a of the housing is formed for connection at the distal end of a drill string.
  • Lower end 218b of the housing accommodates a bit box sub 214, which telescopically extends from lower end 218b.
  • Bit box sub 214 has formed therein a site, such as, for example, threaded bit box 220, for accepting connection of a drill bit (not shown).
  • a bushing and safety catch 224 acts between housing 218 and sub 214 to allow rotation of the sub within the housing and may secure the sub against fully passing out of the housing lower end 218b.
  • Safety catch 224 allows some axial sliding motion of sub 214 within the housing, such axial motion, for example, resulting from moving the sub between a lower position (as shown) and an upper, weight on bit position and being that as a result of the percussive force.
  • safety catch 224 may be eliminated with the safety provisions thereof instead taken up entirely by interacting shoulders 225a, 225b on the parts. This allows housing end 218b to be thicker along its length.
  • Bit box sub 214 is connected to an axial shaft 230, the combination of sub 214 and shaft 230 acting to transmit drive energy from an input end 230a of the shaft to a drill bit installed in box 220.
  • Bit box sub 214 and axial shaft 230 may be connected by a telescoping splined connection 222 that ensures continuous rotational drive conveyance while permitting axial sliding motion of the bit box sub relative to shaft 230.
  • the input torque applied to end 230 may be generated by a mud motor.
  • axial shaft 230 may be connected to a rotor of a mud motor such that any rotation of the rotor, as by flow of drilling fluid through the motor, may be conveyed to the bit box sub.
  • the mud motor may include a positive displacement-type motor (PDM), which uses pressure and flow of the drilling fluid to turn a rotor within a stator.
  • PDM positive displacement-type motor
  • Shaft 230 can be connected directly or indirectly to the rotor, as through threaded connection 260. Where a bent sub is positioned between the motor and the drilling accelerator, a universal connector may be positioned therebetween to convey rotation from the rotor to the axial shaft.
  • the fluid that drives the motor can continue down through the axial shaft and sub 214 and to the bit.
  • these parts may include drilling fluid passages such as axial bores 254 passing therethrough that can be connected in communication with the motor discharge.
  • Bearings 268a, 268a and bushings may be positioned between the axial shaft and the housing to accommodate radial and on bottom and off bottom thrust loads.
  • a safety catch may also be provided between these parts.
  • Drilling accelerator 210 further includes a drive converter intended to convert the rotational drive from the motor to an axial, reciprocating motion to drive the bit box sub axially to apply a percussive force at any drill bit connected into the bit box during drilling.
  • the drive converter includes a pair of cam surfaces 270a, 270b.
  • the first cam surface 270a is installed in the housing and the second cam surface 270b is installed to move with bit box sub 214.
  • Cam surfaces 270a, 270b are positioned to be separated by a gap 272 when the bit box is in its lower position, as shown, but can come together when weight is placed on bit. In other words, gap 272 closes when bit box sub is moved into its upper, weight on bit position. Because the housing and shaft/bit box sub 230/214 rotate at different speeds, the cam surfaces act to ride over each other.
  • Cam surfaces 270a, 270b include one or more cam protrusions 274a, 274b that are oriented and configured to act with consideration of the direction of relative rotation therebetween such that the cam surfaces ride up over each other and drop down thereby generating an axial percussive force to be applied to the bit box sub 214.
  • Cam protrusions 274a, 274b have a ramped approach side, a peak and an exit side. The ramped approach side inclines upwardly to allow the cam protrusions to ride easily up over each other toward the peak.
  • the exit side of the protrusions can be ramped down away from the peak, but a more significant percussive effect may be provided by forming the exit side as shown with an abrupt height change forming a drop off such that the forces (i.e. weight on bit) that drive the cam surfaces together force the parts to abruptly close any gap between them, the gap formed when the protrusions exit off each other.
  • the gap closing develops an abrupt, hammering vibration as the surfaces again come together.
  • cam protrusions While one or more cam protrusions can be provided, it may be useful to position the cam protrusions in a balanced fashion about surfaces 270a, 270b, for example, by positioning the protrusions each equally spaced about the circumference of the cam surface such that all protrusions are on the approach side at the same time.
  • protrusions 274a, 274b can be in pairs on each surface with a first protrusion of the pair diametrically opposed from the second protrusion of the pair on their cam surface. This may reduce adverse lateral forces in the accelerator.
  • Cam surfaces 270a, 270b may be formed from materials that accommodate considerable wear without rapid break down.
  • one or both of the cam surfaces may be include bearings to facilitate movement of the surfaces over one another and reduce detrimental wear to increase tool longevity.
  • the cam protrusions on one of the cam surfaces for example, surface 270a of Figure 4 may be replaced by a cam insert 275a carrying rollers 279 on the cam surface 270c.
  • Rollers 279 are installed to ride up over the cam protrusions 274b of the opposite surface (i.e. surface 270b) and drop down the exit side of the protrusions to create a vibratory effect.
  • the rollers may be ball bearing type rollers carried in the selected cam surface.
  • the rollers may be cylindrical rollers, as shown, or conical type rollers held to rotate along an axis extending radially from the tool long axis X.
  • Rotation in shaft 230 and bit box sub 214 relative to housing 218 will impart on sub 214 axially directed reciprocation determined by the throw of cam protrusions 274a, 274b of surfaces 270a, 270b.
  • This axially directed reciprocation is then conveyed as a vibratory effect to any bit secured in, directly or indirectly, the bit box 220 of the bit box sub.
  • the vibratory effect may be created by axially reciprocating movement created at the interacting cam surfaces which causes a hammering effect when the two parts impact against one another.
  • the tool may be selected to create the vibratory effect by first generating axially reciprocating movement at the interacting cam surfaces that in turn cause a hammering effect at surfaces apart from the cam surfaces.
  • the form of the cam surfaces may be preserved by reducing the detrimental wear caused by the parts striking against one another.
  • the impact creating the hammering effect is generated elsewhere.
  • Such an embodiment may be provided, for example, by provision of a two part mandrel, as provided by axial shaft 230 and bit box sub 230, selected to take up and generate the hammering effect caused by the throw of the cam surfaces.
  • a two part mandrel as provided by axial shaft 230 and bit box sub 230, selected to take up and generate the hammering effect caused by the throw of the cam surfaces.
  • the cam surfaces 270a, 270b create an axially reciprocating motion
  • the hammering effect generated by that motion occurs at the telescoping splined connection 222.
  • the axially sliding motion that is created by the cam surfaces riding over one another causes the upper cam surface 270a, housing 218 and axial shaft 230 to be raised relative to bit box sub 214, as by axial movement between axial shaft 230 and bit box sub 214 at the telescoping splined connection 222.
  • cam protrusions 274a, 274b (which may or may not include rollers) will drop off each other on their exit sides and this, in turn, causes upper cam surface 270a, housing 218 and axial shaft 230 to drop down.
  • end 230a of shaft 230 will strike against upper end 214a of bit box sub 214 (inside connection 222) creating a hammering effect that is conveyed to the bit in bit box 220.
  • any operational gap between parts 214a, 230a which is the maximum gap distance achieved when there is weight on bit driving sub 214 up into the housing and the cams have driven parts 214a, 230a apart, should be at least slightly less than the maximum, unrestricted throw of cam surfaces, which is the maximum unrestricted distance that could be traveled by upper cam surface 270a as its cam protrusions 274 or rollers drop off the cam protrusions or rollers on lower cam surface 270b. If the gap between parts 214a and 230a is more than the throw of the cam surfaces, the cam surfaces will strike each other before the axial shaft and bit box sub can come together.
  • the contact surfaces between parts, where the hammering effect is generated may be supplemented with percussion plates that have a greater wear resistance than the other materials of these parts.
  • seals or structures may be provided to facilitate fluid flow through bore 254 past the impact area between parts 214a, 230a.
  • a sleeve/nipple may be provided on one part 214a or 230a that inserts into an enlarged region of the bore formed on the other of the two parts and seals, such as o-rings may be provided therebetween to prevent fluid from passing from bore 254 into the impact region between the parts.
  • first cam surface 270a is provided by a ring 275 installed in housing 218. Ring 275 forms surface 270a annularly with protrusions 274a downwardly facing. A bore 276 in the ring provides an opening through which a portion of shaft 230 (as illustrated) or bit box sub 214 extends. Second cam surface 270b, in the illustrated embodiment, is provided by a ring 277 that includes threads 278 for securing on an end of sub 214 such that surface 270b is facing upwardly to position its cam protrusions 274b for engagement against those on surface 270a.
  • Ring 275 and housing 218, at shoulder 218c bear against each other such that movement, such as upward movement caused by interaction of the cam surfaces, is transferred to the housing.
  • ring 275 and housing, at shoulder 230c also may bear against each other such that upward movement caused by interaction of the cam surfaces is as well transferred to the shaft 230.
  • the embodiment of Figure 4 operates to drill a borehole by applying a percussive force through the drill bit to the formation when weight is applied on bit.
  • the bit box sub 214 is able to drop into its lower position which separates the cam surfaces and discontinues the percussive force.
  • cam surfaces 270a, 270b When weight on bit is resumed and axial shaft 230 is driven to rotate, cam surfaces 270a, 270b will be rotated at different speeds such that their cam surfaces will ride up over one another and drop off the exit side causing housing 218 and axial shaft to be lifted away from bit box sub 214, as that sub and the bit it carries remains on bottom, and, thereafter, as the cam protrusions exit off one another, the housing and the axial shaft drop down.
  • a hammering effect is applied to bit box sub, as by surface 230a striking surface 214a.
  • a percussive adapter to apply a percussive, axially directed reciprocation to a drill bit may generate left hand torque in the drill string. Such torque may adversely effect standard threaded connections along the string, such as connections 280, causing them to become loosened or to unthread completely.
  • a threaded connection can be used at connection 280 or in connections in other string components that can accommodate left hand torque substantially without weakening the connection.
  • such a connection includes a collar 380 including a pair of threaded box ends 382, 384. Box end 382 includes a thread form extending in a direction opposite from the thread form of box end 384.
  • box end 382 includes a left hand thread
  • box end 384 includes a right hand thread.
  • a collar is the term used to describe a substantially cylindrical connector that is formed to accept threaded engagement of a pair of tubulars, each with a threaded pin end.
  • the box ends each have thread forms that start adjacent the collar end face 382a, 384a, respectively, and extend fully or partially toward a crest 385.
  • Crest 385 may be threaded or smooth, depending on the type of collar.
  • the illustrated connection further includes a first wellbore tubular 386 and a second wellbore tubular 388, each formed with a pin end 386a, 388a, respectively.
  • Tubulars 386, 388 can by housing sections of a drilling accelerator, mud motor, or other tubular portions of a down hole assembly or drill string.
  • Each pin end has a pin end face 386b, 388b, respectively.
  • the pin ends each include a thread form selected to thread into their respective box end 382 or 384.
  • Pin ends 386a, 388a further have corresponding stepped regions formed by axial extensions from their pin end faces such that the pin ends can engage each other to restrict or possibly eliminate relative rotational movement therebetween about their long axis ⁇ t, when they are held end face adjacent to end face in collar 380.
  • the stepped regions are formed by varying the pin end's length from its pin base to its end face, creating an axially extending stepped area along the pin end face.
  • one pin end face 386b includes a stepped extension where the face has a length change creating a shoulder 389a while the other pin end face 388b includes a stepped recess along its circumference also creating a shoulder 389b, the stepped recess is formed to correspond to and, for example, follow in the reverse, the stepped extension of the first pin end such that the two shoulders can be seated against each other, preventing the two pin ends from rotating relative to each other.
  • the stepped regions may be formed of abrupt length changes creating sharper corners, rather than being curved undulations that could ride over each other.
  • the stepped regions may form the shoulders along a line substantially aligned with the tubular's long axis..
  • shoulders formed by stepped regions and recesses form at least one tooth 390a, 390b extending from each pin end face 386b, 388b, each formed so that the pin end faces can mesh and be prevented from rotating relative to each other.
  • each pin end face may include at least one left hand facing shoulder and at least one right hand facing shoulder such that the tubulars are substantially prevented from rotating in either direction relative to each other.
  • the tubulars each include a plurality of left and right hand facing shoulders forming, in effect, a plurality of teeth with gaps g therebetween.
  • the teeth on the first wellbore tubular are formed to mesh closely between the teeth on the second wellbore tubular.
  • the teeth 390a of the first tubular are formed to fit tightly between the teeth 390b on the second tubular such that, if the pins are brought together, end to end, the teeth 390a fit into the gaps between teeth 390b with the sides 390a' of teeth 390a positioned closely alongside the sides 390b' of teeth 390b. In this position, engagement between the shoulders 389a, 389b formed by the sides of the teeth prevents rotation of one pin end relative to the other, when they are held pin end to pin end in the collar.
  • corresponding shoulders may have sides 390a', 390b' that are cut substantially radially, in other words substantially along a radial line extending out from the center axis of the tubular.
  • Pin end faces and shoulders may have close tolerances. If some flex is desired at the connection, such that the lateral rigidity at the connection is reduced, tolerances may be relaxed between pin end faces, such that the length of the shoulder extension on one tubular does not quite equal the depth of the shoulder on the opposite tubular. In other words, the length L of the teeth, measured from tip 392 to base 393 ( Figure 5C ) on one tubular is more than the length of the teeth on the other tubular. The gap formed between the tips of one tubulars teeth and the bases of the other tubulars teeth allows some lateral flex at the connection. Another option to provide for more lateral deflection at the connection, in addition or alternately to the foregoing, may be to indent the outer surface of the teeth.
  • the surface indentation can be initiated at a tapering surface 391 adjacent the base 393 of the teeth to provide more landing space for lateral deflection.
  • thread form including for example, taper and pitch
  • connection is not particularly important.
  • a modified Acme thread may be used to enhance seating and to deter fluid migration through the threaded interfaces at the connection, but other thread forms may be used, as desired.
  • Seals may be provided in the connection, such as for example o-rings 392 in the collar at the crest and/or at interfacing surfaces, for example surfaces 394a, 394b with close tolerances, to enhance the fluid sealing properties of the collar.
  • the first and second wellbore tubulars are aligned to be threaded into their respective box ends of the collar and also, the tubulars are aligned with their teeth offset so that the teeth of each tubular are aligned to mesh into the openings between the teeth of the other tubular.
  • the stepped regions formed by the teeth on one tubular may be set against the shoulders formed by the teeth on the other tubular.
  • the first and second wellbore tubulars are then brought into a position such that their threads can be engaged by the threads of the collar and the collar is rotated about its long axis to engage the tubular pin ends and draw the pin ends into the collar. As the tubulars are drawn in by the collar, the teeth become meshed at the thread crest.
  • the interlock provided by the intermeshed teeth act against, and may prevent completely, back off in the connection even where there is considerable left hand torque.
  • torque tends not to be transferred through the threads of the connection.
  • the connection can allow for lateral flexing, such that the connection may not become too stiff.
  • connection When using the connection, it may be useful to position the right hand threaded pin end on the uphole end of the connection.
  • torque input from surface is most often to the right.
  • placing the right hand threaded pin end on the upper end of the connection ensures that even if the connection itself binds down hole, the string will in its normal rotation continue to drive the pin end into the connection, rather than backing off. That being said, it is believed that such a condition would be rare. It is believed that with the pin to pin locking provided by the teeth, the only way the torque won't transition through the connection is if the collar completely binds down hole such that it cannot rotate, while the tubulars both have opposite torque applied thereto sufficient to overcome the interlock of the teeth.
  • Left hand torque is common and often problematic in mud motor applications such as the current motor driven drilling hammer. However, the connection may also be useful for other applications where left hand torque tends to act adversely on tubular connections such as in subs adjacent any rotationally driven drill bit.
  • the collar is reverse rotated about the connection's axis ⁇ t, again while the tubulars are held stationary.

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  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Claims (14)

  1. Procédé pour accélérer la pénétration de forage d'un trépan de forage (16) entraîné en rotation, le procédé comprenant les étapes consistant à :
    fournir un moteur à déplacement positif (12) comportant un boîtier de moteur, une décharge de fluide et un rotor alimenté par la pression de fluide ; fournir un trépan de forage (16) ;
    fournir un accélérateur de forage (10) comprenant un boîtier (18), un passage de fluide (54) et une liaison d'entraînement pour convertir mécaniquement l'entraînement en rotation en un mouvement de percussion orienté axialement ;
    connecter l'accélérateur de forage (10) en dessous du moteur (12) incluant le fait de connecter le boîtier (18) de manière à ce qu'il se déplace avec le boîtier de moteur, de connecter la liaison d'entraînement de manière à ce qu'elle soit entraînée en rotation par le rotor et d' amener le passage de fluide (54) en communication avec la décharge de fluide ; connecter le trépan de forage (16) sous l'accélérateur de forage (10) avec la liaison d'entraînement en communication d'entraînement avec le trépan de forage (16) ;
    pomper du fluide à travers le moteur (12) pour faire tourner le rotor et la liaison d'entraînement et pour générer un mouvement de percussion axial qui est communiqué de la liaison d'entraînement au trépan de forage (16) ; et
    décharger du fluide de la décharge de fluide de manière à ce qu'il passe à travers l'accélérateur de forage (10) et le trépan de forage (16).
  2. Procédé selon la revendication 1, dans lequel la liaison d'entraînement convertit mécaniquement l'entraînement en rotation en utilisant un ensemble d'engrenages.
  3. Procédé selon la revendication 1, dans lequel la liaison d'entraînement convertit mécaniquement l'entraînement en rotation en utilisant un ensemble de cames (270a, 270b) et le mouvement de percussion axial est généré par un effet de martelage d'une partie (230) d'un arbre d'entraînement de la liaison d'entraînement descendant sur une autre partie (214) d'un arbre d'entraînement de la liaison d'entraînement.
  4. Procédé selon la revendication 1, comprenant en outre l'arrêt de la génération du mouvement de percussion axial en supprimant le poids appliqué sur le trépan.
  5. Procédé selon la revendication 1, comprenant en outre le fait de fournir une connexion filetée (280) pour recevoir un couple à gauche dans le boîtier (18), la connexion filetée (280) comprenant un collier (380) comportant une boîte orientée vers le haut (384) formée de manière à accepter une forme de filetage à droite et une boîte orientée vers le bas (382) formée de manière à accepter une forme de filetage à gauche.
  6. Accélérateur de forage (10) comprenant : un boîtier (!8) comportant une extrémité supérieure (18a) et une extrémité inférieure (18b) ; une liaison d'entraînement comprenant un arbre d'entraînement supérieur à rotation axiale (30) destiné à recevoir une entrée d'un mouvement de rotation, un convertisseur d'entraînement mécanique rotatif à axial en communication avec l'arbre d'entraînement supérieur à rotation axiale (30) pour convertir l'entrée du mouvement de rotation en un mouvement de coulissement axial ; un arbre d'entraînement inférieur déplaçable longitudinalement (42) en communication avec le convertisseur d'entraînement mécanique rotatif à axial pour recevoir le mouvement de coulissement axial du convertisseur d'entraînement mécanique rotatif à axial et un site d'installation de trépan de forage inférieur (20) connecté à l'arbre d'entraînement inférieur déplaçable longitudinalement (42) pour recevoir le mouvement de coulissement axial et capable de transférer par le biais de celui-ci le mouvement de percussion axial, le site d'installation de trépan de forage inférieur (20) étant monté de manière télescopique à côté de l'extrémité inférieure (18b) du boîtier (18) et pouvant être déplacé par coulissement par rapport à celle-ci.
  7. Accélérateur de forage (10) selon la revendication 6, dans lequel l'arbre d'entraînement inférieur déplaçable longitudinalement (42) comporte un raccord de boîte de trépan de forage (14) et en option, dans lequel le site d'installation de trépan de forage inférieur (20) est connecté de manière à se déplacer en rotation avec (a) le boîtier (18) ou (b) l'arbre d'entraînement supérieur à rotation axiale (30).
  8. Accélérateur de forage (10) selon la revendication 6, dans lequel le site d'installation de trépan de forage inférieur (20) est une boîte de trépan de forage (14) et en option, dans lequel le site d'installation de trépan de forage inférieur (20) est connecté de manière à se déplacer en rotation avec (a) le boîtier (18) ou (b) l'arbre d'entraînement supérieur à rotation axiale (30).
  9. Accélérateur de forage (10) selon la revendication 6, dans lequel le convertisseur d'entraînement mécanique rotatif à axial comporte un ensemble d'engrenages (34, 36) entraînant un organe excentrique (40) ; et en option dans lequel l'ensemble d'engrenages (34, 36) comporte des engrenages pour transférer le mouvement de rotation au site d'installation de trépan de forage inférieur (20).
  10. Accélérateur de forage (10) selon la revendication 6, dans lequel le convertisseur d'entraînement mécanique rotatif à axial comporte un ensemble de cames (270a, 270b), l'ensemble de cames (270a, 270b) comportant des surfaces de cames qui se désengagent d'un contact fonctionnel lorsque l'accélérateur de forage (10) est positionné sans poids appliqué au trépan.
  11. Accélérateur de forage (10) selon la revendication 6, dans lequel le convertisseur d'entraînement mécanique rotatif à axial comporte un ensemble de cames (270a, 270b), l'arbre d'entraînement supérieur à rotation axiale (230) étant fixé de manière à se déplacer axialement avec le boîtier (18), et l'ensemble de cames (270a, 270b) comportant une surface de came supérieure (270a) sur le boîtier (18) et une surface de came inférieure (270b) sur l'arbre d'entraînement inférieur déplaçable longitudinalement (214) et la surface de came supérieure (270a) du boîtier (18) étant entraînée par la surface de came inférieure (270b) de manière à soulever le boîtier (18) et l'arbre d'entraînement supérieur à rotation axiale (230) et à abaisser l'arbre d'entraînement supérieur à rotation axiale (230) sur l'arbre d'entraînement inférieur déplaçable longitudinalement (214) pour créer le mouvement de percussion axial.
  12. Accélérateur de forage (10) selon la revendication 6, dans lequel l'arbre d'entraînement supérieur à rotation axiale (230) et l'arbre d'entraînement inférieur déplaçable longitudinalement (214) sont connectés par une liaison télescopique (222) de telle sorte que l'arbre d'entraînement inférieur déplaçable longitudinalement (214) puisse coulisser axialement par rapport à l'arbre d'entraînement supérieur à rotation axiale (230) ; et en option, dans lequel la liaison télescopique (222) est configurée pour transférer l'entraînement rotatif à travers elle.
  13. Accélérateur de forage (10) selon la revendication 6, dans lequel le boîtier (18) comporte une connexion filetée (280) reliant une première section tubulaire du boîtier (18) et une deuxième section tubulaire du boîtier (18), la première section tubulaire (388) comportant une première extrémité de broche filetée (388a) avec une forme de filetage à droite et une saillie s'étendant depuis sa face d'extrémité de broche pour créer une zone étagée sur celle-ci, la deuxième section tubulaire (386) du boîtier (18) comportant une deuxième extrémité de broche filetée (386a) avec une forme de filetage à gauche et un renfoncement sur sa face d'extrémité de broche formant un épaulement dimensionné pour recevoir la zone étagée de la première extrémité de broche (388a) reçue contre celui-ci, et la connexion filetée (280) comportant un collier (380) ayant une première boîte filetée (384) avec une première forme de filetage choisie, choisie pour s'engager par filetage avec la forme de filetage à droite sur la première extrémité de broche filetée (388) et une deuxième boîte filetée (382) avec une deuxième forme de filetage choisie pour s'engager par filetage avec la forme de filetage à gauche de la deuxième extrémité de broche filetée (386).
  14. Accélérateur de forage (10) selon la revendication 6, comprenant en outre un moteur à déplacement positif (12) comprenant un boîtier de stator et un rotor à l'intérieur du boîtier de stator, le boîtier (18) étant connecté à son extrémité supérieure (18) par-dessous, et de manière déplaçable avec, le boîtier de stator du moteur à déplacement positif (12) et le rotor fournissant l'entrée du mouvement de rotation à la liaison d'entraînement et un trépan de forage (16) connecté par-dessous le site d'installation de trépan de forage inférieur (20).
EP09720006.7A 2008-03-13 2009-03-13 Accélérateur de forage de puits et connexion tubulaire Active EP2260172B1 (fr)

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PL09720006T PL2260172T3 (pl) 2008-03-13 2009-03-13 Akcelerator wiercenia odwiertu i złącze rurowe

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US3632808P 2008-03-13 2008-03-13
US7605008P 2008-06-26 2008-06-26
US13801708P 2008-12-16 2008-12-16
PCT/CA2009/000313 WO2009111887A1 (fr) 2008-03-13 2009-03-13 Accélérateur de forage de puits et connexion tubulaire

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EP2260172A1 EP2260172A1 (fr) 2010-12-15
EP2260172A4 EP2260172A4 (fr) 2016-05-04
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Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8739901B2 (en) 2008-03-13 2014-06-03 Nov Worldwide C.V. Wellbore percussion adapter and tubular connection
WO2012027271A2 (fr) * 2010-08-26 2012-03-01 Wells David A H Système de forage contrarotatif
US9103189B2 (en) 2012-03-08 2015-08-11 Halliburton Energy Services, Inc. Segmented seat for wellbore servicing system
MX357991B (es) * 2012-10-01 2018-08-01 Halliburton Energy Services Inc Asiento segmentado de enclavamiento para herramientas en el interior de pozos.
US9593547B2 (en) 2013-07-30 2017-03-14 National Oilwell DHT, L.P. Downhole shock assembly and method of using same
US10017994B2 (en) 2014-10-17 2018-07-10 Ashmin Holding Llc Boring apparatus and method
WO2021007556A1 (fr) * 2019-07-11 2021-01-14 Baker Hughes Oilfield Operations Llc Accouplement anti-rotation à utiliser dans un ensemble de fond de trou

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191310139A (en) * 1913-04-30 1914-03-26 William Ginns Bambridge Improvements in or relating to Drilling and Boring Apparatus.
GB181194A (en) * 1921-04-21 1922-06-15 Vincent Leonard Williams Improvements in rock-boring machines
US3807512A (en) * 1972-12-29 1974-04-30 Texaco Inc Percussion-rotary drilling mechanism with mud drive turbine
DE3207183C1 (de) * 1982-02-27 1983-06-09 Mannesmann AG, 4000 Düsseldorf Rohrverbindung für Metallrohre
US4564225A (en) * 1983-10-27 1986-01-14 Taylor Vernon W Multiple lead threading
JPS6347495A (ja) * 1986-08-18 1988-02-29 株式会社リツト 空気衝撃工具
US5474334A (en) * 1994-08-02 1995-12-12 Halliburton Company Coupling assembly
DE69625472T2 (de) * 1995-03-23 2003-09-25 Hydril Co., Houston Schraubrohrverbindung
GB9708294D0 (en) * 1997-04-24 1997-06-18 Anderson Charles A Downhole apparatus
RU2148144C1 (ru) * 1997-10-20 2000-04-27 Всероссийский научно-исследовательский институт методики и техники разведки (ВИТР) Импульсный вращатель
AU3134700A (en) * 1999-03-15 2000-10-04 Ian Gray Directional drilling system for hard rock
GB9926019D0 (en) * 1999-11-04 2000-01-12 British Gas Plc Pipe joint
CA2500155A1 (fr) * 2005-03-14 2006-09-14 Dale G. Crooks Adaptateur a percussion pour moteurs volumetriques

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2260172A1 (fr) 2010-12-15
EP2260172A4 (fr) 2016-05-04
CA2717484C (fr) 2017-09-19
PL2260172T3 (pl) 2018-12-31
WO2009111887A1 (fr) 2009-09-17
CA2717484A1 (fr) 2009-09-17

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