EP3141689B1 - Raccordement filete et tige de forage avec raccordement filete - Google Patents

Raccordement filete et tige de forage avec raccordement filete Download PDF

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Publication number
EP3141689B1
EP3141689B1 EP16187999.4A EP16187999A EP3141689B1 EP 3141689 B1 EP3141689 B1 EP 3141689B1 EP 16187999 A EP16187999 A EP 16187999A EP 3141689 B1 EP3141689 B1 EP 3141689B1
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EP
European Patent Office
Prior art keywords
thread
flank
threaded connection
angle
flanks
Prior art date
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Active
Application number
EP16187999.4A
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German (de)
English (en)
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EP3141689A1 (fr
Inventor
Günter Fennel
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Sysbohr Bohrtechnik fur Den Spezialtiefbau GmbH
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Sysbohr Bohrtechnik fur Den Spezialtiefbau GmbH
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • 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
    • E21B17/042—Threaded
    • E21B17/0426—Threaded with a threaded cylindrical portion, e.g. for percussion rods

Definitions

  • the invention relates to a threaded connection and a threaded drill pipe according to the preambles of the independent claims.
  • From the CA 1 069 881 A is a threaded connection for a shaft of a lifting trough known which has a thread profile with a likewise steep load flank.
  • the US 2003/038476 A1 relates to a coupling system for a production riser in offshore oil and gas production with a thread having a profile with a steep load flank, wherein further the thread root is formed elliptical.
  • the post-published WO 2016/118324 concerns, inter alia, a thread with a likewise elliptical thread root.
  • the object of the invention is to provide a threaded connection for a drill pipe, which can take high torque and high impact energy and is easy to assemble and improves the state of the art.
  • Another object is to provide a corresponding drill pipe with a threaded connection.
  • a threaded connection of an internal thread and an external thread for a drill pipe for rotary impact drilling or vibration drilling, in particular for overburden drilling the individual boring bars having an end with the internal thread and an end with the external thread, both threads each having a first flank and a second flank have, the profile of the external thread, ie seen in longitudinal section, a flattened thread crest and a rounded thread root and the profile of the internal thread has a flattened thread crest and a rounded thread root. If the thread root of the external thread and the thread root of the internal thread are rounded in profile, the notch sensitivity of the threaded connection is reduced by the rounded thread root.
  • the rounded thread base is particularly advantageous for impact drilling and vibration drilling to prevent cracking germs.
  • the first edge in the profile according to the invention is designed to be larger than the second edge and is corresponding relatively flat.
  • the contact surfaces are made as large as possible during the screwing and reduces the surface pressure.
  • the longer flank is also intended as an inlet flank. As a result, the wear during the screwing can be reduced.
  • the shorter edge serves as a support flank when the thread is screwed and the threaded connection is thus made. Particularly favorable, a noticeable surface contact can be guaranteed and so the surface pressure and the hole pressure on the sleeve can be reduced. This reduces wear, and it can also meet the requirements of today increasingly powerful drilling rigs, especially the recent lately increasingly on the market urging vibratory drives.
  • the drill pipes are usually lifted by means of lifting devices (excavator or crane attachment, etc.) on the feed carriages of the drills and placed on the drill string, which is to be extended. It is not necessarily done sensitively.
  • the drive unit of the drill is then approached to the other end of the drill pipe and threaded with the thread thereon and screwed.
  • the drive unit can consist of one or two drives, which are mounted together on a carriage and often reach a weight of 2500 kg.
  • feed forces of 5-10 t which act hydraulically via chain drive on the drive units, must be manually controlled.
  • these edges are therefore designed so that the largest possible area is created in order to minimize the surface pressure.
  • the support flank is steeper than the entry edge designed so that the loosening torque of the threaded connection is not too large and the drill pipe can be easily dismantled.
  • flanks in the profile of thread root to thread crest can each be flattened, in particular straight, be formed.
  • the rounding at the root of the thread has a radius of at most 3 mm, wherein the radius may preferably be at most 2 mm, particularly preferably 1.6 mm.
  • the large radius of e.g. 1.6 mm in the thread root can advantageously counteract fatigue fractures.
  • the thread root of the external thread and the thread root of the internal thread may have the same radius. As a result, the surface contact is increased and a locally limited surface pressure is avoided.
  • the thread profile is conical, with each thread root and / or each thread crest along of the profile lie on an imaginary line which is inclined at an inclination angle to the thread axis.
  • the angle of inclination may be between 0.5 ° and at most 5 °, particularly preferably 4.5 °. This allows easier insertion of the internal thread in the external thread.
  • the angle of inclination describes the tapering of the conical thread, while the flank angle indicates the angle of the flanks (measured to the central axis), independently of this.
  • the first and the second flank can each enclose an angle of more than 70 °.
  • the angle in the conical thread profile at least 75 °, preferably 80 °.
  • flank angle of the external thread and the internal thread relative to the first, in particular larger flanks relative to the thread center axis can be at least 20 °.
  • the flank angle in the conical thread profile with respect to the first, in particular larger flanks relative to the thread center axis at least 35 °, preferably at least 40 °, particularly preferably 43 °.
  • flank angle of the external thread and of the internal thread relative to the second, in particular smaller, flanks relative to the thread center axis amounts to at least 45 °.
  • the flank angle in the conical thread profile at least 50 °, preferably at least 55 °, particularly preferably 57 °.
  • the number of threads increases with increasing outer diameter of the external thread or the internal thread.
  • a thread with diameters between 75 mm and 115 mm, preferably between 76.1 mm and 114.3 mm, two threads with pitch 20 and with diameters between 120 mm and 155 mm, preferably between 121 mm and 152.4 mm, three threads with pitch 30 may be provided.
  • the pitch angle is chosen so that a sufficient torque can be transmitted and still sufficient self-locking is present, so that the threaded connections do not solve unintentionally.
  • the pitch angle is suitably adapted to the diameter. With larger diameter more threads are provided and thus larger pitch angle.
  • a drill pipe for rotary impact drilling in particular for overburden drilling
  • the individual drill rods of which have one end with an internal thread and one end with an external thread, with a threaded connection as described above.
  • both threads each have a first flank and a second flank, wherein the first flanks are larger than the second flanks and the first flanks are in each case the outer flanks of the thread facing the drill rod ends.
  • the larger flank may have a shallow angle against the thread center axis of, for example, 43 °. This minimizes wear during bolting of the drill rods.
  • the smaller flank can form the support flank when the thread is screwed, and is tilted according to the invention with a larger angle of, for example, 57 ° to the thread axis.
  • the flank angles can vary depending on the purpose.
  • area information always includes all - not mentioned - intermediate values and all imaginable subintervals.
  • FIGS. 1 to 3 show a first embodiment of the invention of a conical threaded connection, in particular for a drill pipe for rotary impact drilling, in particular for overlay drilling, the individual drill rods having an end with an internal thread 20 and an end with an external thread 40.
  • FIG. 1 shows a section of a profile of the conical internal thread 20 of a sleeve 10 of one end of a drill rod ⁇ 102.
  • the internal thread 20 of the sleeve 10 surrounds a threaded central axis 22.
  • FIG. 2 shows a section of a profile of the corresponding external thread 40 of a pin 30 with conical thread.
  • the external thread 40 of the pin 30 surrounds a threaded central axis 42.
  • the inclination angle ⁇ against the respective thread center axis 22, 42 is half the cone angle and is preferably less than 5 °, preferably 4.5 °.
  • the internal thread 20 has a first flank 12 and a second flank 14.
  • the first edge 12 is formed in profile larger than the second edge 14.
  • the first flank 12 is provided as an inlet flank during the screwing, which advantageously reduces the wear.
  • the smaller flank 14, however, serves as a support flank when the internal thread 20 is screwed to the external thread 40 and the threaded connection is made.
  • the two flanks 12, 14 close an angle ⁇ 10 of more than 70 °, in particular the angle ⁇ 10 in the conical thread is at least 75 °, preferably 80 °.
  • the profile of the internal thread 20 has a flattened thread crest 18, in particular a straight thread crest 18, and a rounded thread root 16.
  • the radius R10 of the thread base is favorably between 1.5mm and 3.0mm, preferably 1.6mm.
  • the external thread 40 in FIG. 2 has a first flank 32 and a second flank 34.
  • the first edge 32 is formed in profile larger than the second edge 34.
  • the first flank 32 is provided as an inlet flank during the screwing, which advantageously reduces the wear.
  • the smaller edge 34 serves as a support flank when the internal thread 20 is screwed to the external thread 40 and the threaded connection is made.
  • the external thread 40 has a flattened thread crest 38 and a rounded thread root 36 in profile.
  • the radius R30 of the thread base is favorably between 1.5mm and 3.0mm, preferably 1.6mm.
  • the two flanks 32, 34 enclose an angle ⁇ 30 of more than 70 °, in particular the angle ⁇ 30 in the conical thread is at least 75 °, preferably 80 °.
  • FIG. 3 shows a section of the threaded connection of the conical internal thread 20 and external thread 40 of the Figures 1 and 2 , Due to the flattenings 50 of the thread crests 18, 38 and the rounded groove bases 16, 36, relatively large cavities 50 form there, which offer space for receiving contaminants such as dust and the like.
  • the first, larger flanks 12, 32 form a flank angle ⁇ with respect to the thread center axis 22, 42, which is at least 20 °, preferably at least 35 °, preferably at least 40 °, particularly preferably 43 °.
  • the second, smaller flanks 14, 34 form a flank angle ⁇ relative to the thread center axis 22, 42, which is at least 45 °, preferably at least 50 °, preferably at least 55 °, particularly preferably 57 °.
  • the larger flanks 12, 32 are in each case the outer flanks of the threads 20, 40 facing the boring bar ends of the boring bars 102, 104.

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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)

Claims (12)

  1. Raccordement fileté constitué d'un filetage interne (20) et d'un filetage externe (40) pour un tube de forage pour le forage par roto-percussion ou le forage par vibration, dont les tiges de forage individuelles (102, 104) présentent une extrémité avec le filetage interne (20) et une extrémité avec le filetage externe (40), les deux filetages (20, 40) présentant chacun un premier flanc (12, 32) et un deuxième flanc (14, 34), le profil du filetage interne (20) présentant une pointe de filetage aplatie (18) et une base de filetage arrondie (16) et le profil du filetage externe (40) présentant une pointe de filetage aplatie (38) et une base de filetage arrondie (36), le premier flanc (12, 32) étant réalisé sous forme de flanc d'entrée et étant plus long que le deuxième flanc (14, 34) réalisé sous forme de flanc de charge, le raccordement fileté étant réalisé sous forme conique et la base de filetage (16, 36) et/ou la pointe de filetage (18, 38) étant situées le long d'une coupe longitudinale sur une ligne imaginaire qui est inclinée avec un angle d'inclinaison (β) par rapport à l'axe médian du filetage (22, 42),
    caractérisé en ce que
    l'angle d'inclinaison (β) est compris entre 0,5° et 5° au maximum ; et
    l'arrondi au niveau de la base de filetage (16, 36) présente un rayon (R10, R30) de 3 mm au maximum ; et
    un angle de flanc (δ) du filetage externe (40) et du filetage interne (20) par rapport aux deuxièmes flancs (14, 34) par rapport à l'axe médian du filetage (22, 42) vaut au moins 45° à 57° ; et
    le nombre des pas de filetage augmente avec l'augmentation du diamètre du filetage (40).
  2. Raccordement fileté selon la revendication 1, caractérisé en ce que l'angle d'inclinaison (β) vaut 4,5° au maximum.
  3. Raccordement fileté selon la revendication 1 ou 2, caractérisé en ce que les flancs (12, 32 ; 14, 34), vus en coupe longitudinale depuis la base de filetage (16, 36) jusqu'à la pointe de filetage (18, 38) sont réalisés à chaque fois sous forme aplatie.
  4. Raccordement fileté selon l'une quelconque des revendications précédentes, caractérisé en ce que l'arrondi au niveau de la base de filetage (16, 36) présente un rayon (R10, R30) de 2 mm au maximum, particulièrement préférablement de 1,6 mm.
  5. Raccordement fileté selon l'une quelconque des revendications précédentes, caractérisé en ce que la base de filetage (16) du filetage externe (40) et la base de filetage (36) du filetage interne (20) présentent le même rayon (R10, R30).
  6. Raccordement fileté selon l'une quelconque des revendications précédentes, caractérisé en ce que les premiers et les deuxièmes flancs (12, 14 ; 32, 34) présentent à chaque fois un angle (α10, α30) supérieur à 70°.
  7. Raccordement fileté selon la revendication 6, caractérisé en ce que l'angle (α10, α30) vaut au moins 75°, de préférence 80°.
  8. Raccordement fileté selon l'une quelconque des revendications précédentes, caractérisé en ce que l'angle de flanc (γ) du filetage externe (20) et du filetage interne (40) par rapport aux premiers flancs (12, 32) par rapport à l'axe médian du filetage (22, 42) vaut au moins 20°.
  9. Raccordement fileté selon la revendication 8, caractérisé en ce que l'angle de flanc (γ) par rapport aux premiers flancs (12, 32) par rapport à l'axe médian du filetage (22, 42) vaut au moins 35°, de préférence au moins 40°, particulièrement préférablement 43°.
  10. Raccordement fileté selon l'une quelconque des revendications précédentes, caractérisé en ce que l'angle de flanc (δ) vaut au moins 50°, de préférence au moins 55°, particulièrement préférablement 57°.
  11. Tube de forage pour le forage par roto-percussion, dont les tiges de forage individuelles (102, 104) présentent une extrémité avec un filetage interne (20) et une extrémité avec un filetage externe (40), avec un raccordement fileté, les deux filetages (20, 40) présentant chacun un premier flanc (12, 32) et un deuxième flanc (14, 34), caractérisé en ce que le raccordement fileté est réalisé selon l'une quelconque des revendications précédentes.
  12. Tube de forage pour le forage par roto-percussion selon la revendication 11, caractérisé en ce que les premiers flancs (12, 32) sont à chaque fois les flancs extérieurs des filetages (20, 40) tournés vers les extrémités des tiges de forage.
EP16187999.4A 2015-09-11 2016-09-09 Raccordement filete et tige de forage avec raccordement filete Active EP3141689B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202015104842.4U DE202015104842U1 (de) 2015-09-11 2015-09-11 Gewindeverbindung und Bohrgestänge mit Gewindeverbindung

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EP3141689A1 EP3141689A1 (fr) 2017-03-15
EP3141689B1 true EP3141689B1 (fr) 2019-12-04

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11125361B2 (en) 2018-03-01 2021-09-21 Mitchell Z. Dziekonski Thread form and threaded article
CN114320175B (zh) * 2020-09-29 2024-05-14 宝山钢铁股份有限公司 一种抗粘扣的快速上扣螺纹接头

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DE19803304C5 (de) 1997-05-29 2010-09-30 Boart Longyear Gmbh & Co. Kg Hartmetallwerkzeugfabrik Bohrgestänge zum Drehschlagbohren, insbesondere zum Überlagerungsbohren
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE820657C (de) 1948-05-15 1951-11-12 Hughes Tool Co Gewindeverbindung
US3129963A (en) 1960-06-30 1964-04-21 Robbins Machine & Mfg Co Low release torque threaded joint
DE1290106B (de) 1965-08-09 1969-03-06 Drilco Oil Tools Inc Schraubverbindung fuer Bohrgestaenge
CA1069881A (fr) * 1976-06-28 1980-01-15 Warren E. Askew Piece filetee resistant aux couples eleves
DE7739844U1 (de) 1977-12-28 1979-08-30 Ing. Guenter Klemm, Spezialunternehmen Fuer Bohrtechnik, 5962 Drolshagen Bohrgestaenge
DE3426725A1 (de) 1983-06-20 1986-01-23 Reed Tubular Products Co., Sugar Land, Tex. Gestaengeverbindung
DE3873414T2 (de) 1987-05-12 1993-02-04 Diamant Boart Stratabit Sa Schraubverbindung fuer bohrgestaenge.
US5127784A (en) 1989-04-19 1992-07-07 Halliburton Company Fatigue-resistant buttress thread
US5060740A (en) 1990-05-29 1991-10-29 Sandvik Rock Tools, Inc. Screw thread coupling
US6030004A (en) * 1997-12-08 2000-02-29 Shaw Industries High torque threaded tool joint for drill pipe and other drill stem components
WO2000020720A1 (fr) 1998-10-01 2000-04-13 Boart Longyear Gmbh & Co. Kg Hartmetallwerkzeug- Fabrik Train de sonde pour realiser un forage par rotation-percussion, notamment pour forage a tubage de sonde simultane
US6467818B1 (en) 1999-10-01 2002-10-22 Grant Prideco, L.P. Drill collar box
DE19955377A1 (de) 1999-11-10 2001-06-07 Mannesmann Ag Rohrverbindung
US20030038476A1 (en) 2001-08-24 2003-02-27 Galle Edward M. Production riser connector
EP1511911B1 (fr) 2002-05-22 2014-11-19 Atlas Copco Secoroc AB Joint filete pour train de tiges pour forage de roches par percussion
US7210710B2 (en) 2004-03-01 2007-05-01 Omsco, Inc. Drill stem connection
WO2006092649A1 (fr) 2005-03-02 2006-09-08 Vallourec Mannesmann Oil & Gas France Raccordement de masse-tige
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CN103216197A (zh) 2013-04-28 2013-07-24 江苏曙光石油钻采设备有限公司 快旋式石油钻杆接头螺纹强化结构
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