EP1117897B1 - String of drill pipes for rotary percussion drilling, especially for simultaneous drilling - Google Patents

String of drill pipes for rotary percussion drilling, especially for simultaneous drilling Download PDF

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Publication number
EP1117897B1
EP1117897B1 EP98954318A EP98954318A EP1117897B1 EP 1117897 B1 EP1117897 B1 EP 1117897B1 EP 98954318 A EP98954318 A EP 98954318A EP 98954318 A EP98954318 A EP 98954318A EP 1117897 B1 EP1117897 B1 EP 1117897B1
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EP
European Patent Office
Prior art keywords
thread
connection system
external
drill pipes
threads
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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EP98954318A
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German (de)
French (fr)
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EP1117897A1 (en
Inventor
Friedrich Flemming
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Boart Longyear GmbH and Co KG
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Boart Longyear GmbH and Co KG Hartmetallwerkzeugfabrik
Boart HWF GmbH and Co KG Hartmetallwerkzeugfabrik
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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
    • 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 present invention relates to a connection system for drill rods for rotary impact drilling, especially for Overlay drilling, with an external thread and a Internal thread, the profile of the external thread a flattened thread tip and a circular arc Has thread root, while the profile of the internal thread has an arcuate thread tip, and the external thread and the internal thread, respectively an unthreaded insertion section is in front of which the external or internal thread connects, and wherein a circumferential shoulder in the area of the external thread is trained.
  • connection system is from the utility model DE 297 21 748 U1 known.
  • the present invention is based on the object a connection system for drill pipe of the beginning to improve the type mentioned so that the aforementioned Disadvantages are largely eliminated.
  • the invention Connection system is characterized in that the external thread and the internal thread one each larger load-bearing flank and a smaller non-load-bearing flank Have flank, the profile of the Internal thread has a flat thread root, and where the non-load-bearing flank is each arc-shaped is formed and the same radius as the circular arc-shaped thread tip of the internal thread or like the arcuate thread base of the Has external thread.
  • connection system stands out due to a long service life, especially a minimal one Thread wear when connecting the provided Boring bars.
  • the design of its thread represents sure that self-locking even with larger ones Thread diameters is prevented.
  • the length is of the insertion section upstream of the external thread at least 0.3 to 0.35 times the outer diameter of the respective boring bar, the one of the external thread upstream insertion section preferably at least twice as long as the one upstream of the thread Introductory section is.
  • the circumferential shoulder is on a conical rod end with an external thread is undercut in the direction of the other rod end and the other rod end a complementary one Has end face.
  • the angle of inclination of the shoulder is preferably between 10 ° and 20 ° related to the radial plane there the respective boring bar.
  • Boring bars having the connection system according to the invention can be quickly and easily without self-locking connect and disconnect if the pitch angle of the External or internal thread over the entire size range the rods between 12 ° and 16 °, preferably between 12.3 ° and 15.8 °.
  • a further advantageous embodiment provides that the load-bearing flank of the thread by 25 ° to 35 ° is inclined relative to the central axis of the boring bar. This not only creates a relatively large touch area for the load-bearing flank, but also supports the Alignment of the threads when inserting the Threaded boring bar end in that corresponding end with an internal thread subsequent boring bar. In this way the Wear further minimized.
  • all Boring bars on the same thread depth that between 1.5 mm and 2.5 mm, preferably about 2 mm. This minimizes tool costs.
  • boring bars with respect to their outer and Inner diameter are graded so that a Boring bar of specified size inside one by two Larger boring bar is insertable.
  • a Boring bar of specified size inside one by two Larger boring bar is insertable.
  • To this Way can with the drill string according to the invention two or three telescopically arranged one inside the other Boring bars are drilled.
  • the maximum Outside diameter 1.15 to 1.55 times, preferably 1.25 to 1.45 times the minimum inside diameter.
  • the flank diameter of the external or internal thread has preferably a value in the range between 1 / 1.25 x AD and 1 / 1.05 x AD, where AD is for the outside diameter the boring bar is standing. This ensures that Boring bars in next largest size boring bars can be introduced and yet sufficient Have strength because the cross-sectional area of the Boring bars are at the inner end of the internal thread larger with increasing outside diameter of the boring bars.
  • the cross-sectional area on inner end of the internal thread is larger than that Cross-sectional area at the inner end of the External thread, as for boring bars in which the Impact effect is transmitted via the outer shoulder, the the internally threaded end of a higher one Bending stress is subject to that than the external thread having end.
  • the radius of the circular arc of the non-load-bearing flank one Value in the range between 3.2 mm and 4.5 mm, preferably about 3.8 mm.
  • the radius of the circular arc is for the entire size range of the boring bars maintained. This configuration, together with the unchangeable flank angle and the unchangeable Thread depth ensures that the same Tapping tool for the entire size range of Boring bars can be used.
  • Another preferred embodiment is thereby characterized in that the number of threads with increases the outside diameter of the boring bar.
  • boring bars with an outer diameter less than 75 mm a thread, boring bars with an outer diameter between 75 mm and 105 mm two Threads, boring bars with an outer diameter between 105 mm and 140 mm three threads and Boring bars with an outer diameter larger than 140 mm have four threads. This also helps increasing outside diameter of the boring bars Enlargement of the load-bearing area of the Thread flanks achieved. This ensures that when using the same thread profile for the the entire size range of the boring bars Pitch angle not excessive with increasing Outside diameter (AD) changes.
  • AD Outside diameter
  • FIG. 1a and 1b show the ends of a boring bar with a cylindrical external thread 1 and a corresponding internal thread 2 in longitudinal section.
  • the Boring bar ends each have a threadless Insertion section 3 or 4, to which the respective Thread connects.
  • the length of the external thread 1 upstream insertion section 3 is approximately 0.3 up to 0.35 times the outside diameter AD of the boring bar and is about twice as long as that of the internal thread 2 upstream insertion section 4.
  • a circumferential outer shoulder 5 is that of transferring the impact to a subsequent boring bar or the drill bit is used.
  • the Shoulder 5 is conical, with one Angle of inclination of about 15 ° to the radial plane, the other boring bar end being a complementary one has bevelled end face 6.
  • To be telescopically arranged with two or more To be able to drill boring bars are the boring bars in terms of their outer and inner diameters graded so that a boring bar of a given size inside a boring bar two sizes bigger can be introduced.
  • For boring bars with one Outside diameter AD is between 75 and 180 mm maximum outer diameter AD of a boring bar about 1.15 to 1.55 times their minimum ID ID.
  • the flank diameter FD of the External or internal thread is between 1 / 1.25 x AD and 1 / 1.05 x AD.
  • the cross-sectional area thus increases inner end of the internal thread 2 with increasing Boring bar outside diameter AD too. It can also be seen that the cross-sectional area at the inner end of the Internal thread 2 is larger than the cross-sectional area on inner end of the external thread 1.
  • the most inner end of the internal thread 2 adjacent Section 8 and the corresponding Section 7 of the External thread 1 have essentially the same Wall thickness WA or WI, the inside diameter ID the conical boring bar in the direction of the internal thread 2 expands.
  • Figures 2a and 2b show an enlarged view the thread profile of the drill pipe according to the invention.
  • the external thread 1 and the internal thread 2 each have a load-bearing outer flank 9 and a non-load-bearing one Inner flank 10 on.
  • the external thread 1 pin thread
  • the internal thread 2 Socket thread
  • the load-bearing outer flank 9 is in each case one Angle ( ⁇ F of about 30 ° to the Boring bar center axis M inclined.
  • the non-load bearing Inner flank 10 is circular arc shaped and has the same radius R as the circular arc-shaped thread tip 13 of the Internal thread 2 or like the circular arc Thread root 12 of the external thread 1.
  • the radius R of the Circular arc is between 3.2 mm and 4.5 mm, preferably about 3.8 mm.
  • the transitions are from flat Thread base 14 to the thread flanks 9, 10 as Fillet fillets 15 formed.
  • the radius of this Fillet fillet 15 is approximately 1 mm.
  • the transitions 16 from the external thread 1 flattened thread tip 11 to the thread flanks 9, 10 circular arc-shaped rounded, the Radius of the circular arc corresponds to that of the fillet curves.
  • the thread depth of one Thread pitch is between 8.5 mm and 10.5 mm, preferably about 9.5 mm.
  • Fig. 3a is a side view schematically External thread shown, the pitch angle ( ⁇ 1 for a catchy thread is applied.
  • Fig. 3b is in Side view schematically shown an external thread, wherein the pitch angle ( ⁇ 2 for a two-start thread is registered.
  • the number of threads depends on the outside diameter the boring bar. Boring bars with an outer diameter For example, OD ⁇ 75 mm have a thread, during boring bars with an outer diameter AD ⁇ 75 mm and OD ⁇ 105 mm two threads, boring bars with one Outside diameter AD ⁇ 105 and AD ⁇ 140 mm three Threads and boring bars with an outer diameter AD> 140 mm have four threads.
  • the thread profile the boring bars not only cylindrical but also be conical.

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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)
  • Drilling Tools (AREA)

Abstract

The invention relates to a string of drill pipes for rotary percussion drilling, especially for simultaneous drilling. One of the ends of the individual pipes of the string of drill pipes has a male thread (1) and the other end has a female thread (2). Both threads have a larger, load-bearing flank and a smaller, non-load bearing flank. The aim of the invention is to reduce thread wear to a minimum for a string of drill pipes, especially the wear that occurs when the drill pipes are assembled. To this end, the pipe ends are provided with an non-threaded insertion section (3) which is followed by the male or female thread. The profile of the male thread (1) has a flat thread crest and a thread root in the shape of a circular arc while the profile of the female thread (2) has a thread crest in the shape of a circular arc and a flat thread root. The pipe end which is provided with the male thread (1) has a circumferential shoulder (5) which serves to transmit the impact effect to a subsequent drill pipe.

Description

Die vorliegende Erfindung betrifft ein Verbindungssystem für Bohrgestänge zum Drehschlagbohren, insbesondere zum Überlagerungsbohren, mit einem Außengewinde und einem Innengewinde, wobei das Profil des Außengewindes eine abgeflachte Gewindespitze und einen kreisbogenförmigen Gewindegrund aufweist, während das Profil des Innengewindes eine kreisbogenförmige Gewindespitze aufweist, und wobei dem Außengewinde und dem Innengewinde jeweils ein gewindeloser Einführabschnitt vorgelagert ist, an den sich das Außen- bzw. Innengewinde anschließt, und wobei im Bereich des Außengewindes eine umlaufende Schulter ausgebildet ist.The present invention relates to a connection system for drill rods for rotary impact drilling, especially for Overlay drilling, with an external thread and a Internal thread, the profile of the external thread a flattened thread tip and a circular arc Has thread root, while the profile of the internal thread has an arcuate thread tip, and the external thread and the internal thread, respectively an unthreaded insertion section is in front of which the external or internal thread connects, and wherein a circumferential shoulder in the area of the external thread is trained.

Ein derartiges Verbindungssystem ist aus dem Gebrauchsmuster DE 297 21 748 U1 bekannt.Such a connection system is from the utility model DE 297 21 748 U1 known.

Große Bauwerke erfordern eine gute Gründung, jedoch ist der Untergrund oftmals nicht fest genug, um eine sichere Gründung herzustellen. In diesen Fällen muß der Untergrund durch das Einbringen von Ankern in in den Untergrund gebohrte Löcher verfestigt werden. Das Bohren dieser Löcher wird als Überlagerungsbohren bezeichnet.Large structures require good foundation, however the subsurface is often not firm enough to be safe Establish foundation. In these cases the By introducing anchors into the Holes drilled underground are solidified. The drilling these holes are referred to as overlay drilling.

Obwohl verschiedene Verfahren existieren, wird das Überlagerungsbohren üblicherweise drehschlagend ausgeführt, wobei ein Kopfhammer (Bohrhammer) und ein Doppelbohrgestänge verwendet werden. Die Bohrstangen müssen somit imstande sein, Schläge (Stöße) und das Drehmoment vom Hammer auf den Bohrmeißel zu übertragen. Although there are different methods, it will Overlay drilling is usually rotationally impacting executed, a head hammer (hammer drill) and a Double drill pipe can be used. The boring bars must therefore be able to take blows (bumps) and that Transfer torque from the hammer to the drill bit.

Auch müssen sie imstande sein, ineinandergeschoben zu werden.They also have to be able to be pushed together become.

Für das Überlagerungsbohren ausgebildete Bohrstangen werden durch zylindrische oder konische Gewinde miteinander verbunden. Obwohl sie für diese Anwendung speziell entwickelt worden sind, weisen sie zahlreiche Schwachpunkte auf. Die wichtigsten sind:

  • a) Gewindeverschleiß während der Kopplung;
  • b) Selbsthemmung bei größeren Gewindedurchmessern;
  • c) Materialbrüche bei kleineren Gewindedurchmessern nahe dem innenliegenden Ende des Innengewindes.
    • Boring bars designed for overlay drilling are connected to each other by cylindrical or conical threads. Although they have been specially developed for this application, they have numerous weak points. The most important are:
  • a) thread wear during coupling;
  • b) self-locking with larger thread diameters;
  • c) Material breaks in the case of smaller thread diameters near the inner end of the internal thread.

    • Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Verbindungssystem für Bohrgestänge der eingangs genannten Art so zu verbessern, daß die vorgenannten Nachteile weitestgehend beseitigt sind.The present invention is based on the object a connection system for drill pipe of the beginning to improve the type mentioned so that the aforementioned Disadvantages are largely eliminated.

    Diese Aufgabe wird erfindungsgemäß durch die in Anspruch 1 angegebenen Merkmale gelöst. Das erfindungsgemäße Verbindungssystem ist dadurch gekennzeichnet, daß das Außengewinde und das Innengewinde jeweils eine größere lastaufnehmende Flanke und eine kleinere nicht-lastaufnehmende Flanke aufweisen, wobei das Profil des Innengewindes einen flachen Gewindegrund aufweist, und wobei die nicht-lastaufnehmende Flanke jeweils kreisbogenförmig ausgebildet ist und den gleichen Radius wie die kreisbogenförmige Gewindespitze des Innengewindes bzw. wie der kreisbogenförmige Gewindegrund des Außengewindes aufweist.This object is achieved by the in Features specified claim 1 solved. The invention Connection system is characterized in that the external thread and the internal thread one each larger load-bearing flank and a smaller non-load-bearing flank Have flank, the profile of the Internal thread has a flat thread root, and where the non-load-bearing flank is each arc-shaped is formed and the same radius as the circular arc-shaped thread tip of the internal thread or like the arcuate thread base of the Has external thread.

    Das erfindungsgemäße Verbindungssystem zeichnet sich durch eine hohe Lebensdauer, insbesondere einen minimalen Gewindeverschleiß beim Verbinden der damit versehenen Bohrstangen aus. Die Ausgestaltung seines Gewindes stellt sicher, daß eine Selbsthemmung auch bei größeren Gewindedurchmessern verhindert wird.The connection system according to the invention stands out due to a long service life, especially a minimal one Thread wear when connecting the provided Boring bars. The design of its thread represents sure that self-locking even with larger ones Thread diameters is prevented.

    Nach einer vorteilhaften Ausgestaltung beträgt die Länge des dem Außengewinde vorgeordneten Einführabschnitts mindestens das 0,3- bis 0,35-fache des Außendurchmessers der jeweiligen Bohrstange, wobei der dem Außengewinde vorgeordnete Einführabschnitt vorzugsweise mindestens doppelt so lang wie der dem Gewinde vorgeordnete Einführabschnitt ist. Diese relativ langen Einführabschnitte tragen dazu bei, den Verschleiß an den Außenflanken der Gewinde zu minimieren.According to an advantageous embodiment, the length is of the insertion section upstream of the external thread at least 0.3 to 0.35 times the outer diameter of the respective boring bar, the one of the external thread upstream insertion section preferably at least twice as long as the one upstream of the thread Introductory section is. These relatively long insertion sections contribute to the wear on the outer flanks to minimize the thread.

    Vorteilhaft ist es auch, wenn die umlaufende Schulter an einem das Außengewinde aufweisenden Stangenende konisch in Richtung des anderen Stangenendes hinterschnitten ist und das andere Stangenende eine komplementär gestaltete Stirnseite aufweist. Hierdurch wird die Kontaktfläche der Schulter vergrößert, so daß eine gute Schlagübertragung vom Bohrhammer auf den Bohrmeißel sichergestellt wird. Der Neigungswinkel der Schulter liegt dabei vorzugsweise zwischen 10° und 20° bezogen auf die dortige Radialebene der jeweiligen Bohrstange.It is also advantageous if the circumferential shoulder is on a conical rod end with an external thread is undercut in the direction of the other rod end and the other rod end a complementary one Has end face. As a result, the contact area of the Shoulder enlarged, so that good impact transmission is ensured by the hammer drill on the drill bit. The angle of inclination of the shoulder is preferably between 10 ° and 20 ° related to the radial plane there the respective boring bar.

    Das erfindungsgemäße Verbindungssystem aufweisende Bohrstangen lassen sich schnell und einfach ohne Selbsthemmung verbinden sowie lösen, wenn der Steigungswinkel des Außen- bzw. Innengewindes über den gesamten Größenbereich der Stangen zwischen 12° und 16°, vorzugsweise zwischen 12,3° und 15,8° liegt. Boring bars having the connection system according to the invention can be quickly and easily without self-locking connect and disconnect if the pitch angle of the External or internal thread over the entire size range the rods between 12 ° and 16 °, preferably between 12.3 ° and 15.8 °.

    Eine weitere vorteilhafte Ausgestaltung sieht vor, daß die lastaufnehmende Flanke der Gewinde um 25° bis 35° gegenüber der Bohrstangenmittelachse geneigt ist. Dies schafft nicht nur eine relativ große Berührungsfläche für die lastaufnehmende Flanke, sondern unterstützt auch die Ausrichtung der Gewinde beim Einführen des das Außengewinde aufweisenden Bohrstangenendes in das das entsprechende Innengewinde aufweisende Ende einer nachfolgenden Bohrstange. Auf diese Weise wird der Verschleiß weiter minimiert.A further advantageous embodiment provides that the load-bearing flank of the thread by 25 ° to 35 ° is inclined relative to the central axis of the boring bar. This not only creates a relatively large touch area for the load-bearing flank, but also supports the Alignment of the threads when inserting the Threaded boring bar end in that corresponding end with an internal thread subsequent boring bar. In this way the Wear further minimized.

    Gemäß einer weiteren Lehre der Erfindung weisen alle Bohrstangen die gleiche Gewindetiefe auf, die zwischen 1,5 mm und 2,5 mm, vorzugsweise ungefähr 2 mm, beträgt. Dadurch werden die Werkzeugkosten minimiert.According to a further teaching of the invention, all Boring bars on the same thread depth that between 1.5 mm and 2.5 mm, preferably about 2 mm. This minimizes tool costs.

    Eine andere bevorzugte Ausgestaltung besteht ferner darin, daß die Bohrstangen bezüglich ihres Außen- und Innendurchmessers derart abgestuft sind, daß eine Bohrstange vorgegebener Größe in das Innere einer um zwei Größen größeren Bohrstange einführbar ist. Auf diese Weise kann mit dem erfindungsgemäßen Bohrgestänge mit zwei oder drei teleskopartig ineinander angeordneten Bohrstangen gebohrt werden.Another preferred embodiment also exists in that the boring bars with respect to their outer and Inner diameter are graded so that a Boring bar of specified size inside one by two Larger boring bar is insertable. To this Way can with the drill string according to the invention two or three telescopically arranged one inside the other Boring bars are drilled.

    Vorzugsweise beträgt für Bohrstangen mit einem Außendurchmesser zwischen 75 und 180 mm der maximale Außendurchmesser das 1,15 bis 1,55-fache, vorzugsweise das 1,25 bis 1,45-fache, des minimalen Innendurchmessers. Der Flankendurchmesser des Außen- bzw. Innengewindes hat dabei vorzugsweise einen Wert im Bereich zwischen 1/1,25 x AD und 1/1,05 x AD, wobei AD für den Außendurchmesser der Bohrstange steht. Dadurch ist sichergestellt, daß Bohrstangen in Bohrstangen der nächst größeren Größe eingeführt werden können und gleichwohl eine ausreichende Festigkeit aufweisen, denn die Querschnittsfläche der Bohrstangen wird am innenliegenden Ende des Innengewindes mit zunehmendem Außendurchmesser der Bohrstangen größer.Preferably for boring bars with a Outside diameter between 75 and 180 mm the maximum Outside diameter 1.15 to 1.55 times, preferably 1.25 to 1.45 times the minimum inside diameter. The flank diameter of the external or internal thread has preferably a value in the range between 1 / 1.25 x AD and 1 / 1.05 x AD, where AD is for the outside diameter the boring bar is standing. This ensures that Boring bars in next largest size boring bars can be introduced and yet sufficient Have strength because the cross-sectional area of the Boring bars are at the inner end of the internal thread larger with increasing outside diameter of the boring bars.

    Auch ist es vorteilhaft, wenn die Querschnittsfläche am innenliegenden Ende des Innengewindes größer ist als die Querschnittsfläche am innenliegenden Ende des Außengewindes, da bei Bohrstangen, bei denen die Schlagwirkung über die Außenschulter übertragen wird, das das Innengewinde aufweisende Ende einer höheren Biegespannung unterworfen ist als das das Außengewinde aufweisende Ende.It is also advantageous if the cross-sectional area on inner end of the internal thread is larger than that Cross-sectional area at the inner end of the External thread, as for boring bars in which the Impact effect is transmitted via the outer shoulder, the the internally threaded end of a higher one Bending stress is subject to that than the external thread having end.

    Um eine Selbstreinigung des Gewindes zu erzielen, ist nach einer weiteren Ausgestaltung vorgesehen, daß der Radius des Kreisbogens der nicht-lastaufnehmende Flanke einen Wert im Bereich zwischen 3,2 mm und 4,5 mm, vorzugsweise ungefähr 3,8 mm, aufweist. Der Radius des Kreisbogens wird für den gesamten Größenbereich der Bohrstangen beibehalten. Diese Ausgestaltung, zusammen mit dem unveränderlichen Flankenwinkel und der unveränderlichen Gewindetiefe gewährleistet, daß dasselbe Gewindeschneidwerkzeug für den gesamten Größenbereich der Bohrstangen verwendet werden kann.To achieve self-cleaning of the thread, is according to a further embodiment provided that the radius of the circular arc of the non-load-bearing flank one Value in the range between 3.2 mm and 4.5 mm, preferably about 3.8 mm. The radius of the circular arc is for the entire size range of the boring bars maintained. This configuration, together with the unchangeable flank angle and the unchangeable Thread depth ensures that the same Tapping tool for the entire size range of Boring bars can be used.

    Eine andere bevorzugte Ausgestaltung ist dadurch gekennzeichnet, daß die Anzahl der Gewindegänge mit zunohmondem Außendurchmesser der Bohrstange zunimmt. wobei vorzugsweise Bohrstangen mit einem Außendurchmesser kleiner als 75 mm einen Gewindegang, Bohrstangen mit einem Außendurchmesser zwischen 75 mm und 105 mm zwei Gewindegänge, Bohrstangen mit einem Außendurchmesser zwischen 105 mm und 140 mm drei Gewindegänge und Bohrstangen mit einem Außendurchmesser größer als 140 mm vier Gewindegänge aufweisen. Auch hierdurch wird bei zunehmendem Außendurchmesser der Bohrstangen eine Vergrößerung der lastaufnehmenden Fläche der Gewindeflanken erzielt. Hierdurch wird gewährleistet, daß bei der Anwendung desselben Gewindeprofils für den gesamten Größenbereich der Bohrstangen sich der Steigungswinkel nicht übermäßig mit größer werdendem Außendurchmesser (AD) ändert.Another preferred embodiment is thereby characterized in that the number of threads with increases the outside diameter of the boring bar. preferably boring bars with an outer diameter less than 75 mm a thread, boring bars with an outer diameter between 75 mm and 105 mm two Threads, boring bars with an outer diameter between 105 mm and 140 mm three threads and Boring bars with an outer diameter larger than 140 mm have four threads. This also helps increasing outside diameter of the boring bars Enlargement of the load-bearing area of the Thread flanks achieved. This ensures that when using the same thread profile for the the entire size range of the boring bars Pitch angle not excessive with increasing Outside diameter (AD) changes.

    Um die Gefahr von Materialbrüchen aufgrund von Spannungskonzentrationen zu minimieren, wird ferner vorgeschlagen, daß sowohl das Außen- als auch das Innengewinde Übergangsradien von ungefähr 1 mm bei allen Übergängen aufweisen.The danger of material breakage due to stress concentrations to minimize, it is also proposed that both the external and internal threads Transition radii of approximately 1 mm for all transitions exhibit.

    Weitere vorteilhafte Ausgestaltungen und Merkmale der Erfindung sind in den Unteransprüchen angegeben. Further advantageous configurations and features of the Invention are specified in the subclaims.

    Im folgenden wird die Erfindung anhand einer lediglich ein bevorzugtes Ausführungsbeispiel schematisch darstellenden Zeichnung näher erläutert. In der Zeichnung zeigen:

    Fig. 1a
    ein erfindungsgemäßes Bohrstangenende mit Außengewinde im Längsschnitt,
    Fig. 1b
    ein erfindungsgemäßes Bohrstangenende mit Innengewinde im Längsschnitt,
    Fig. 2a
    eine Profildarstellung des Außengewindes in vergrößertem Maßstab,
    Fig. 2b
    eine Profildarstellung des Innengewindes in vergrößertem Maßstab,
    Fig. 3a
    einen Abschnitt eines Außengewindes einer erfindungsgemäßen Bohrstange mit einem eingängigen Gewinde mit gegenüber Fig. 2a abweichendem Durchmesser in Seitenansicht, und
    Fig. 3b
    einen Abschnitt eines Außengewindes einer erfindungsgemäßen Bohrstange mit einem zweigängigen Gewinde mit gegenüber Fig. 2a abweichendem Durchmesser in Seitenansicht.
    In the following, the invention is explained in more detail with reference to a drawing schematically illustrating only a preferred exemplary embodiment. The drawing shows:
    Fig. 1a
    an inventive boring bar end with an external thread in longitudinal section,
    Fig. 1b
    an inventive boring bar end with internal thread in longitudinal section,
    Fig. 2a
    a profile representation of the external thread on an enlarged scale,
    Fig. 2b
    a profile representation of the internal thread on an enlarged scale,
    Fig. 3a
    a portion of an external thread of a boring bar according to the invention with a single-start thread with a different diameter compared to Fig. 2a in side view, and
    Fig. 3b
    a side view of a portion of an external thread of a boring bar according to the invention with a two-start thread with a diameter that differs from FIG. 2a.

    Die Fig. 1a und Fig. 1b zeigen die Enden einer Bohrstange mit einem zylindrischen Außengewinde 1 und einem entsprechenden Innengewinde 2 im Längsschnitt. Die Bohrstangenenden weisen jeweils einen gewindelosen Einführabschnitt 3 bzw. 4 auf, an den sich das jeweilige Gewinde anschließt. Die Länge des dem Außengewinde 1 vorgeordneten Einführabschnitts 3 beträgt etwa das 0,3 bis 0,35-fache des Außendurchmessers AD der Bohrstange und ist etwa doppelt so lang wie der dem Innengewinde 2 vorgeordnete Einführabschnitt 4. 1a and 1b show the ends of a boring bar with a cylindrical external thread 1 and a corresponding internal thread 2 in longitudinal section. The Boring bar ends each have a threadless Insertion section 3 or 4, to which the respective Thread connects. The length of the external thread 1 upstream insertion section 3 is approximately 0.3 up to 0.35 times the outside diameter AD of the boring bar and is about twice as long as that of the internal thread 2 upstream insertion section 4.

    Ferner ist zu erkennen, daß an dem in Fig. 1a dargestellten Ende der zum Drehschlagbohren bestimmten Bohrstange eine umlaufende Außenschulter 5 ausgebildet ist, die der Übertragung der Schlagwirkung auf eine nachfolgende Bohrstange bzw. den Bohrmeißel dient. Die Schulter 5 ist konisch ausgebildet, und zwar mit einem Neigungswinkel von etwa 15° gegenüber der Radialebene, wobei das andere Bohrstangenende eine komplementär abgeschrägte Stirnseite 6 aufweist.It can also be seen that on the in Fig. 1a shown end of the intended for rotary impact drilling Boring bar formed a circumferential outer shoulder 5 is that of transferring the impact to a subsequent boring bar or the drill bit is used. The Shoulder 5 is conical, with one Angle of inclination of about 15 ° to the radial plane, the other boring bar end being a complementary one has bevelled end face 6.

    Um mit zwei oder mehr teleskopartig angeordneten Bohrstangen bohren zu können, sind die Bohrstangen bezüglich ihres Außen- und Innendurchmessers größenmäßig derart abgestuft, daß eine Bohrstange vorgegebener Größe in das Innere einer um zwei Größen größeren Bohrstange einführbar ist. Für Bohrstangen mit einem Außendurchmesser AD zwischen 75 und 180 mm beträgt der maximale Außendurchmesser AD einer Bohrstange beträgt dabei etwa das 1,15 bis 1,55-fache ihres minimalen Innendurchmessers ID. Der Flankendurchmesser FD des Außen- bzw. Innengewindes liegt zwischen 1/1,25 x AD und 1/1,05 x AD. Somit nimmt die Querschnittsfläche am innenliegenden Ende des Innengewindes 2 mit zunehmendem Bohrstangenaußendurchmesser AD zu. Auch ist zu erkennen, daß die Querschnittsfläche am innenliegenden Ende des Innengewindes 2 größer ist als die Querschnittsfläche am innenliegenden Ende des Außengewindes 1. Der am innenliegenden Ende des Innengewindes 2 angrenzende Abschnitt 8 und der entsprechende Abschnitt 7 des Außengewindes 1 haben dabei im wesentlichen die gleiche Wandstärke WA bzw. WI, wobei sich der Innendurchmesser ID der Bohrstange konisch in Richtung des Innengewindes 2 hin aufweitet.To be telescopically arranged with two or more To be able to drill boring bars are the boring bars in terms of their outer and inner diameters graded so that a boring bar of a given size inside a boring bar two sizes bigger can be introduced. For boring bars with one Outside diameter AD is between 75 and 180 mm maximum outer diameter AD of a boring bar about 1.15 to 1.55 times their minimum ID ID. The flank diameter FD of the External or internal thread is between 1 / 1.25 x AD and 1 / 1.05 x AD. The cross-sectional area thus increases inner end of the internal thread 2 with increasing Boring bar outside diameter AD too. It can also be seen that the cross-sectional area at the inner end of the Internal thread 2 is larger than the cross-sectional area on inner end of the external thread 1. The most inner end of the internal thread 2 adjacent Section 8 and the corresponding Section 7 of the External thread 1 have essentially the same Wall thickness WA or WI, the inside diameter ID the conical boring bar in the direction of the internal thread 2 expands.

    Die Figuren 2a und 2b zeigen in vergrößerter Darstellung das Gewindeprofil des erfindungsgemäßen Bohrgestänges. Das Außengewinde 1 und das Innengewinde 2 weisen jeweils eine lastaufnehmende Außenflanke 9 und eine nicht-lastaufnehmende Innenflanke 10 auf.Figures 2a and 2b show an enlarged view the thread profile of the drill pipe according to the invention. The external thread 1 and the internal thread 2 each have a load-bearing outer flank 9 and a non-load-bearing one Inner flank 10 on.

    Das Außengewinde 1 (Zapfengewinde) hat eine abgeflachte Gewindespitze 11 und einen kreisbogenförmigen Gewindegrund 12, während das Innengewinde 2 (Muffengewinde) eine kreisbogenförmige Gewindespitze 13 und einen flachen Gewindegrund 14 besitzt.The external thread 1 (pin thread) has a flattened one Thread tip 11 and an arcuate Thread root 12, while the internal thread 2 (Socket thread) an arcuate thread tip 13 and has a flat thread bottom 14.

    Die lastaufnehmende Außenflanke 9 ist jeweils um einen Winkel (αF von etwa 30° gegenüber der Bohrstangenmittelachse M geneigt. Die nicht-lastaufnehmende Innenflanke 10 ist dagegen jeweils kreisbogenförmig ausgebildet und hat den gleichen Radius R wie die kreisbogenförmige Gewindespitze 13 des Innengewindes 2 bzw. wie der kreisbogenförmige Gewindegrund 12 des Außengewindes 1. Der Radius R des Kreisbogens liegt zwischen 3,2 mm und 4,5 mm, vorzugsweise bei ungefähr 3,8 mm.The load-bearing outer flank 9 is in each case one Angle (αF of about 30 ° to the Boring bar center axis M inclined. The non-load bearing Inner flank 10, however, is circular arc shaped and has the same radius R as the circular arc-shaped thread tip 13 of the Internal thread 2 or like the circular arc Thread root 12 of the external thread 1. The radius R of the Circular arc is between 3.2 mm and 4.5 mm, preferably about 3.8 mm.

    Beim Innengewinde 2 sind die Übergänge vom flachen Gewindegrund 14 zu den Gewindeflanken 9, 10 als Kehlrundungen 15 ausgebildet. Der Radius dieser Kehlrundungen 15 beträgt ungefähr 1 mm. Dementsprechend sind am Außengewinde 1 die Übergänge 16 von der abgeflachten Gewindespitze 11 zu den Gewindeflanken 9, 10 kreisbogenförmig abgerundet ausgestaltet, wobei der Radius des Kreisbogens dem der Kehlrundungen entspricht.In the internal thread 2, the transitions are from flat Thread base 14 to the thread flanks 9, 10 as Fillet fillets 15 formed. The radius of this Fillet fillet 15 is approximately 1 mm. Accordingly are the transitions 16 from the external thread 1 flattened thread tip 11 to the thread flanks 9, 10 circular arc-shaped rounded, the Radius of the circular arc corresponds to that of the fillet curves.

    Um Werkzeugkosten zu minimieren, weisen alle Bohrstangen denselben Gewindegang auf. Die Gewindetiefe eines Gewindegangs liegt zwischen 8,5 mm und 10,5 mm, vorzugsweise bei ungefähr 9,5 mm.In order to minimize tool costs, all boring bars have same thread. The thread depth of one Thread pitch is between 8.5 mm and 10.5 mm, preferably about 9.5 mm.

    In Fig. 3a ist in Seitenansicht schematisch ein Außengewinde gezeigt, wobei der Steigungswinkel (α1 für ein eingängiges Gewinde angetragen ist. In Fig. 3b ist in Seitenansicht schematisch ein Außengewinde gezeigt, wobei der Steigungswinkel (α2 für ein zweigängiges Gewinde angetragen ist.In Fig. 3a is a side view schematically External thread shown, the pitch angle (α1 for a catchy thread is applied. In Fig. 3b is in Side view schematically shown an external thread, wherein the pitch angle (α2 for a two-start thread is registered.

    Die Anzahl der Gewindegänge hängt vom Außendurchmesser der Bohrstange ab. Bohrstangen mit einem Außendurchmesser AD < 75 mm haben beispielsweise einen Gewindegang, während Bohrstangen mit einem Außendurchmesser AD ≥ 75 mm und AD < 105 mm zwei Gewindegänge, Bohrstangen mit einem Außendurchmesser AD ≥ 105 und AD < 140 mm drei Gewindegänge und Bohrstangen mit einem Außendurchmesser AD > 140 mm vier Gewindegänge aufweisen.The number of threads depends on the outside diameter the boring bar. Boring bars with an outer diameter For example, OD <75 mm have a thread, during boring bars with an outer diameter AD ≥ 75 mm and OD <105 mm two threads, boring bars with one Outside diameter AD ≥ 105 and AD <140 mm three Threads and boring bars with an outer diameter AD> 140 mm have four threads.

    Die Erfindung beschränkt sich in ihrer Ausführung nicht auf das vorstehend angegebene bevorzugte Ausführungsbeispiel. Insbesondere kann das Gewindeprofil der Bohrstangen nicht nur zylindrisch, sondern auch konisch ausgeführt sein.The invention is not restricted in its implementation to the preferred given above Embodiment. In particular, the thread profile the boring bars not only cylindrical but also be conical.

    Claims (22)

    1. A connection system for drill pipes for rotary percussion drilling, in particular for overburden drilling, said connection system having an external thread (1) and an internal thread (2), the profile of the external thread (1) comprising a flat topped thread crest (11) and a circular arc-shaped thread root (12) whereas the profile of the internal thread (2) comprises a circular arc-shaped thread crest (13), a threadless insertion segment (3, 4) being provided upstream of a respective one of the external thread (1) and of the internal thread (2) and being adjoined with the external thread and with the internal thread respectively and a circumferential shoulder (5) being formed in the region of the external thread (1),
      characterized in that
      both threads (1, 2) are each comprised of a greater load-carrying flank (9) and of a smaller non-load-carrying flank (10), the profile of the internal thread (2) being comprised of a flat thread root (14) and the non-load-carrying flank (10) being configured as a shape corresponding to an arc of a circle and having the same radius (R) than the circular arc-shaped thread crest (13) of the internal thread (2) or as the circular arc-shaped thread root (12) of the external thread (1) respectively.
    2. The connection system according to claim 1,
      characterized in that
      the insertion segment (3) disposed upstream of the external thread (1) has a length of from at least 0.3 to 0.35 times the outside diameter (AD) of the respective one of the drill pipes.
    3. The connection system according to claim 1 or 2,
      characterized in that
      the insertion segment (3) disposed upstream of the external thread (1) has at least twice the length of the insertion segment disposed upstream of the internal thread (2).
    4. The connection system according to any of claims 1 to 3,
      characterized in that,
      at a pipe end provided with the external thread (1), the circumferential shoulder (5) has a conical undercut.
    5. The connection system according to any of claims 1 to 4,
      characterized in that,
      at a pipe end provided with the external thread (1), the circumferential shoulder (5) is undercut at an angle of inclination of between 10 degree and 20 degree relative to a radial plane so as to taper in the direction towards the other pipe end.
    6. The connection system according to any of claims 1 to 5,
      characterized in that
      the lead angle for the respective one of the external and internal threads (1, 2) is between 12 degree and 16 degree.
    7. The connection system according to claim 6,
      characterized in that
      the lead angle for the respective one of the external and internal threads (1, 2) is between 12.3 degree and 15.8 degree.
    8. The connection system according to any of claims 1 to 7,
      characterized in that
      the load-carrying flanks (9) respectively are the outside flanks facing the nearest drill pipe end of the threads (1, 2).
    9. The connection system according to any of claims 1 to 8,
      characterized in that
      each load-carrying flank (9) of the threads (1, 2) is inclined at an angle of from 25 degree to 35 degree to the center line (M) of the drill pipe.
    10. The connection system according to any of claims 1 to 9,
      characterized in that
      the drill pipes have a thread depth (GT) of between 1.5 mm and 2.5 mm, preferably of about 2 mm.
    11. The connection system according to any of claims 1 to 10,
      characterized in that,
      with respect to their outside and their inside diameter, the drill pipes are of graduated dimensions so that a drill pipe of a given size may be inserted into a two sizes greater drill pipe.
    12. The connection system according to any of claims 1 to 11,
      characterized in that
      the outside diameter of drill pipes having an outside diameter (AD) of between 75 and 180 mm is from 1.15 to 1.55 times, preferably from 1.25 to 1.45 times, the minimum inside diameter thereof.
    13. The connection system according to any of claims 1 to 12,
      characterized in that
      the flank diameter (FD) of the respective one of the external and internal threads ranges between 1/1.25 times AD and 1/1.05 times AD, wherein AD is the outside diameter of the drill pipe.
    14. The connection system according to any of claims 1 to 13,
      characterized in that
      the cross-sectional area at the inside end of the internal thread (2) is greater than the cross-sectional area at the inside end of the external thread (1).
    15. The connection system according to any of claims 1 to 14,
      characterized in that
      the circular arc of the non-load-carrying flank (10) has a radius (R1) of between 3.2 mm and 4.5 mm, preferably of about 3.8 mm.
    16. The connection system according to any of claims 1 to 15,
      characterized in that
      the external thread (1) and the internal thread (2) are configured to be multiple-start threads.
    17. The connection system for drill pipes according to claim 16,
      characterized in that
      the number of thread convolutions increases with the external diameter of the drill pipe.
    18. The connection system according to claim 17,
      characterized in that
      the drill pipes having an outside diameter of less than 75 mm comprise one thread convolution, the drill pipes having an outside diameter greater than or equal to 75 mm and less than 105 mm, two thread convolutions, the drill pipes having an outside diameter greater than or equal to 105 mm and less than 140 mm, three thread convolutions and the drill pipes having an outside diameter greater than 140 mm, four thread convolutions.
    19. The connection system according to any of claims 1 to 18,
      characterized in that,
      at the internal thread (2), the fillet of the thread root (14) with respect to the thread flanks (9, 10) is configured to be a rounded groove (15) having a radius of about 1 mm.
    20. The connection system according to any of claims 1 to 19,
      characterized in that,
      at the external thread (1), the transition of the flat topped thread crest (11) with respect to the thread flanks (9, 10) is rounded in the shape of a circular arc, with said circular arc having a radius of about 1 mm.
    21. The connection system according to any of claims 1 to 20,
      characterized in that
      the threads (1, 2) are configured as a cylindrical thread.
    22. The connection system according to any of claims 1 to 20,
      characterized in that
      the threads (1, 2) are configured as a conical thread.
    EP98954318A 1998-10-01 1998-10-01 String of drill pipes for rotary percussion drilling, especially for simultaneous drilling Expired - Lifetime EP1117897B1 (en)

    Applications Claiming Priority (1)

    Application Number Priority Date Filing Date Title
    PCT/EP1998/006264 WO2000020720A1 (en) 1998-10-01 1998-10-01 String of drill pipes for rotary percussion drilling, especially for simultaneous drilling

    Publications (2)

    Publication Number Publication Date
    EP1117897A1 EP1117897A1 (en) 2001-07-25
    EP1117897B1 true EP1117897B1 (en) 2004-05-12

    Family

    ID=8167084

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP98954318A Expired - Lifetime EP1117897B1 (en) 1998-10-01 1998-10-01 String of drill pipes for rotary percussion drilling, especially for simultaneous drilling

    Country Status (6)

    Country Link
    EP (1) EP1117897B1 (en)
    JP (1) JP3961769B2 (en)
    KR (1) KR100556271B1 (en)
    AT (1) ATE266796T1 (en)
    DE (1) DE59811400D1 (en)
    WO (1) WO2000020720A1 (en)

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    WO2016018997A1 (en) * 2014-07-31 2016-02-04 Baker Hughes Incorporated Fatigue resistant thread profile with combined curve rounding
    US11230891B2 (en) 2015-08-27 2022-01-25 Diversity Technologies Corporation Threaded joint

    Families Citing this family (11)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE102006062882B4 (en) * 2006-04-24 2013-03-28 Tracto-Technik Gmbh Drill rod for manufacturing earth drilling, comprises pipe sections connected with each other by plug in couplings, and housing that is closed along its longitudinal direction and interior couplings that can be actuated from inside
    DE102006019396B4 (en) * 2006-04-24 2014-10-16 Tracto-Technik Gmbh drill pipe
    FR2969738B1 (en) * 2010-12-28 2016-03-25 Vallourec Mannesmann Oil & Gas THREADED JOINT FOR DRILLING AND OPERATING HYDROCARBON WELLS
    US10557316B2 (en) 2011-01-26 2020-02-11 Bly Ip Inc. Drill string components having multiple-thread joints
    US9810029B2 (en) 2011-01-26 2017-11-07 Bly Ip Inc. Drill string components resistant to jamming
    US9850723B2 (en) 2011-01-26 2017-12-26 Bly Ip Inc. Drill string components having multiple-thread joints
    EP2653706A1 (en) 2012-04-20 2013-10-23 Caterpillar Motoren GmbH & Co. KG Monitoring the fuel injection system of dual fuel engines
    JP6137115B2 (en) * 2014-10-27 2017-05-31 Ｊｆｅスチール株式会社 Steel pipe joints
    US10041307B2 (en) 2015-01-22 2018-08-07 National Oilwell Varco, L.P. Balanced thread form, tubulars employing the same, and methods relating thereto
    DE202015104842U1 (en) 2015-09-11 2015-09-18 Sysbohr Gmbh - Bohrtechnik Für Den Spezialtiefbau Threaded connection and drill pipe with threaded connection
    PL3712374T3 (en) * 2019-03-18 2023-01-16 Sandvik Mining And Construction Tools Ab Drill string rod

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    DE1173046B (en) * 1958-12-30 1964-07-02 Boehler & Co Ag Geb Connection of the drill rods of percussion drills
    US4799844A (en) * 1988-01-11 1989-01-24 Trw Inc Elliptical thread design
    DE19803304C5 (en) * 1997-05-29 2010-09-30 Boart Longyear Gmbh & Co. Kg Hartmetallwerkzeugfabrik Drill pipe for rotary impact drilling, in particular for overlay drilling
    DE29721748U1 (en) * 1997-12-09 1998-01-29 Bauer Spezialtiefbau Gmbh, 86529 Schrobenhausen Tillage tool

    Cited By (2)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    WO2016018997A1 (en) * 2014-07-31 2016-02-04 Baker Hughes Incorporated Fatigue resistant thread profile with combined curve rounding
    US11230891B2 (en) 2015-08-27 2022-01-25 Diversity Technologies Corporation Threaded joint

    Also Published As

    Publication number Publication date
    DE59811400D1 (en) 2004-06-17
    EP1117897A1 (en) 2001-07-25
    JP3961769B2 (en) 2007-08-22
    KR20010106500A (en) 2001-11-29
    KR100556271B1 (en) 2006-03-03
    JP2002526701A (en) 2002-08-20
    ATE266796T1 (en) 2004-05-15
    WO2000020720A1 (en) 2000-04-13

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