瑞典专利SE0900388A1 Threaded thin walled drill pipe joint

专利PDF首页>>瑞典专利

专利附录

专利说明

权利要求

类似技术

同族专利

引用文献

法律状态

优先权

专利摘要:
A part of a joint for a thin-walled drill pipe has a central axis (A) and comprises a thread (4) for forming a screw connection. The thread has a threaded bottom (6), a threaded top (7), a pressure ﬂ ankle (8) and a clearance ﬂ ankle (9). The pressure ken anchor (8) has a portion having a negative angle (21) which is less than 7,5 °, but at least 0 °, relative direction which is perpendicular to the central axis (A). Publication "gur". Fi g 1b.
公开号:SE0900388A1
申请号:SE0900388
申请日:2009-03-26
公开日:2010-09-27
发明作者:Goeran Baeck
申请人:Sandvik Intellectual Property；
IPC主号:

专利说明:

The pressure flank has a portion which has a negative angle of less than 7.5 °, but greater than 0 °, relative to a direction perpendicular to the central axis.
When angles of ﬂ anchors and thread peaks are discussed, it will be appreciated that it is the main angle of the respective surface that is intended, and that radii at edges of the respective surface should be disregarded.
The strength of the joint depends in part on the wall thickness of the joint parts. A shallow thread depth allows a greater wall thickness of the joint parts. With such a solution, the thread depth can be reduced and the wall thickness increased, which provides a stronger joint for deeper drilling. An increase in the tensile load from 424000N to 479000N is possible, which corresponds to about 300 m of additional drilling.
A negative angle is defined as an angle that produces an undercut ﬂ ankle surface. By thin-walled drill pipe is meant a pipe with a wall thickness, excluding the thread, of from about 3 to 6.4 mm, from about 3 to 5.6 mm, or from about 3 to 4.2 mm. In further embodiments, the negative angle of the pressure portion may be from about 1 ° to 6 °, from about 2 ° to 5 °, from about 4 ° to 5 °, or about 5 ° relative to the direction perpendicular to the central axis.
To enable a reduced thread depth for increased wall thickness, the material of the part must be strong enough to handle the increased tensile load on the thread caused by the decreased depth. One embodiment has a joint part made of substantially hardened steel.
When the steel is fully hardened and not only surface hardened, no heat-affected area is formed which can cause cracks in the thread tip.
The thread depth, defined as the radial distance between the thread bottom and the thread top, may, in further embodiments, be from about 0.5 to 0.8 mm, from about 0.5 to 0.7 mm, or about 0.5-0.6. mm.
In order to enable more efficient use of the thread depth for more efficient power transmission and better tensile load capacity, in one embodiment, the material thickness at at least one of the thread bottom and the thread top may be tapered towards an end portion of the part. This means that the thread depth is not constant along the surface of the part over which the thread extends. This solution, when the trade is connected to a female part, results in a tapered free space between the male and female parts. An additional advantage of this effect is that more space is offered for dirt and grease between the threads, which could otherwise cause disturbances and reduced tensile load capacity in the connection.
In a further embodiment, the thread bottom may be substantially parallel to the center axis and the material thickness of the thread tip tapered towards the end portion of the part.
In one embodiment, the freewheel of the thread may have a portion with an angle of less than 45 ° relative to the drawing perpendicular to the central axis. In a further embodiment, the freewheel of the thread may have a portion with an angle which differs at different sections of the thread. A fairly large angle on a first thread section located near the end portion of the part can facilitate the assembly of the trade with a female part. The clearance anchor can then in one embodiment have an angle of from about 10 ° to 40 °, from about 20 ° to 35 °, or about 30 ° relative to the direction perpendicular to the central axis.
The first thread section may be located closer to an end portion of the part than a second thread section. The second section may have an anchorage portion of a clearance med having an angle of from about 0 ° to 15 °, from about 1 ° to 10 °, or about 5 ° relative to the direction perpendicular to the central axis. The clearance angles of the different thread sections can be combined in different embodiments according to Table 1. X indicates explicit indication of a combination of a clearance angle of a first and second section. 0 ° to 15 ° 1 ° to 10 ° 5 ° 10 ° to 40 ° xxx 20 ° to 35 ° xxx 30 ° xxx Table 1 A thread pitch of the part can be from about 0.8 to 1.6 threads per centimeter, from approx. 0.8 to 1.2 threads per centimeter, or about 1 thread per centimeter. At least one of the pressure ﬂ anchor and the clearance ﬂ anchor may be connected to the threaded bottom via a radius greater than about 0.10 mm or greater than about 0.15 mm. 10 15 20 25 30 4 At least one of the pressure ﬂ anchor and the clearance ﬂ anchor may be connected to the thread top via a radius greater than about 0.10 mm or greater than about 0.15 mm or greater than about 0.20 mm.
The part may be a trade, the thread extending along an outer portion of the part. Alternatively, the part may be a female part, the thread extending along an inner portion of the part.
The female part exhibits essentially the same features as the trade in different embodiments. The two parts can have the same pressure ﬂ anchor and clearance ﬂ angle angles, thread depth and material.
In one embodiment, the thread tip, for trade, may taper at an angle of from about 0.2 ° to 0.6 °, from about 0.3 ° to 0.5 °, from about 0.3 ° to 0.4 °. or about 0.34 ° relative to the central axis. In another embodiment, the material thickness of the thread tip, for trade, may taper at an angle of about 1.7 ° to 2.5 ° or about 2 ° to 2.5 ° relative to the center axis.
In one embodiment, the material thickness of the thread tip, for a female part, may taper at an angle of from about 0.2 ° to 0.6 °, from about 0.2 ° to 0.4 °, from about 0.2 ° to 0 °. 3 °, or about 0.28 ° relative to the central axis. At the same time, the threaded bottom can be substantially parallel to the central axis.
A second aspect provides a casing system for a drill pipe comprising a handle and a female part according to any of the previously shown embodiments. The dressing system may, in one embodiment, have a tapered free space between the thread top of one of the parts and the thread bottom of the other of the parts. This feature has the effect that a maximum part of the thread depth is used when the pressure tryck anchors of the two parts are connected to each other. It also allows more space for dirt and grease in the threaded connection. In practice, the thread depth may vary and / or the material thickness at the thread bottom may vary.
In a further embodiment of the invention, the tapered free space is present at least along two adjacent threads. With as much connection area as possible between the pressure ﬂ anchors of the two parts, the more the thread depth can be reduced, which enables increased wall thickness, while maintaining the tensile load capacity of the connection. Therefore, it is an advantage if all the threads have a tapered free space at the connection between the two parts.
According to a third aspect, a thin-walled pipe drilling system is provided, comprising a connecting system as described above, wherein the trade is arranged on a first thin-walled drill pipe and the female part is arranged on a second thin-walled drill pipe.
According to a fourth aspect, a male or female part of a connection for a drill pipe is provided, having a center axis and comprising a thread for forming a screw connection, the thread having a threaded bottom, a thread top, a pressure ankle and a clearance ankle, the material thickness at least one of the thread bottom and the thread tip tapers towards an end portion of the part.
According to a fifth aspect, a male or female part of a connection for a drill pipe is provided, having a center axis and comprising threads for forming a screw connection, the thread having a threaded bottom, a threaded top, a pressure anchor and a clearance anchor, at least one of the pressure anchor and the clearance ﬂ anken is connected to the threaded bottom via a radius of approx. 0.15 mm.
According to a sixth aspect, there is provided a male or female part of a connection for a drill pipe, having a center axis and comprising a thread for forming a screw connection, the thread having a threaded bottom, a thread tip, a pressure ankle and a clearance ankle, wherein at least one of the pressure duct and the clearance duct are connected to the threaded top via a radius of approx. 0.20 mm.
It will be appreciated that each of the fourth to sixth aspects may be used in combination with any of the embodiments during the first and second of aspects, or independently thereof.
Brief Description of the Drawings In the following, an embodiment will be described in more detail with reference to the accompanying drawings.
Fig. 1a is a perspective view in section of a trade.
Fig. 1b is a sectional view of a trade. Fig. 2 is a sectional view of one half of the connection with a trade and a female part.
Fig. 3 is a detail sectional view of the connection between a trade and a female part.
Detailed Description Referring to Figures 1a and 1b, a trade 1 of a connection for a drill pipe is shown. The inner diameter 30 of the tubular tube and the connection, as well as the outer diameter 31, can be specified for an industry standard. A base portion 2 of the cylindrical portion has the same outer diameter 31 as the drill pipe, and a base lug 3 connects the base portion 2 to the outer portion of the portion provided with a thread 4. The thread extends along the axial length of the portion 1, and terminates at a end portion 5.
The thread 4 has a thread bottom 6, a thread top 7, a pressure ﬂ ank 8 and a clearance ﬂ ank 9. The thread bottom 6 is defined as the part of the thread with the shortest radial distance from the center axis A. The part with the longer radial distance from the center axis is the thread top 7. The largest radial distance between the thread bottom 6 and the thread top 7, the thread depth 32 is defined. An inner cylindrical surface 10 of the part 1, together with the thread bottom 6, defines the wall 11 of the part 1.
The base lug 3 is undercut and tapers towards the threaded portion of the part at an angle of about 15 ° relative to a direction perpendicular to the center axis A. Pressure ﬂ anchor 8 is the ﬂank of thread 4 facing the base portion 2. Pressure ﬂ anchor 8 has an undercut surface with a negative angle 21 of about 5 ° relative to a direction perpendicular to the center axis A.
The clearance 9 anch 9 faces the end portion 5. The clearance ﬂ anch 9 may have different angles at different sections of the thread 4. A first section 15 of the thread is arranged closest to the end portion 5 of the section. This first section 15 may have an entrance clearance angle 12 with a positive angle 22 of about 30 ° relative to a direction perpendicular to the center axis A. In a second section 16 of the thread, clearance clearance 9 may have a positive angle 23 of about 5 ° relative to a direction perpendicular to the center axis A. A larger angle in the first thread section 15 can facilitate the assembly of the handle 1 in a dog | in a connection, and reduces the risk of the threads being damaged.
The part 1 and the end portion 5 of the part end at an end lug 13. The end lug 13 tapers with a negative angle 24 of about 15 ° relative to a direction perpendicular to the center axis A. The end lug is connected to the inner cylindrical surface 10 of the part via a chamfer 14 at an angle of about 15 ° relative to the center axis A.
The threaded bottom 6 can be substantially parallel to the center axis A.
The thread tip 7 tapers towards the end portion 5 of the trade 1 at an angle 26 of about 0.34 ° relative to the center axis A. This results in a non-constant thread thickness 32. To increase the strength of the joint, it is desirable to make the wall 11 as thick as possible, and therefore it is desirable to make the thread thickness as shallow as possible. In this embodiment of the invention, the thread depth 32 may be from about 0.5 to 0.7 mm.
The pressure flank 8 has the angle 21. The pressure ﬂ 8 is connected to the thread tip 7 via a radius 40, which can be approx. 0.2 mm. The pressure flank is further connected to the threaded bottom 6 via a radius 41, which can be about 0.15 mm.
Similarly, the clearance anchor 9 of the second thread section 16 may be connected to the thread tip 7 via a radius 42, which may be about 0.2 mm, and connected to the thread bottom 6 via a radius 43, which may be about 0.15 mm. The entrance clearance flank 12 is connected to the end portion 5 via a radius 44, which may be about 0.4 mm. The different radii at the ﬂ anchors have the effect that the loads on the connections are distributed over a larger area. The size of the radii can be adapted for optimal effect. The radii can also make it easier to achieve a tight connection surface between the anchors.
The restraint system according to the invention comprises a trade 1 and a dog | 101, the trade comprising a thread extending along an outer portion of the part, and the female part 101 comprising a thread extending along an inner surface portion of the part.
Fig. 2 shows the trade 1 in connection connection with the female part 101.
The female part 101 has corresponding parts as the trade 1 including a base portion 102, an end portion 103, a base lug 104, an end lug 105 and a threaded portion having a thread bottom 106, a thread top 107, a pressure ﬂ ank 10 15 20 25 30 8 108, a clearance 109 ank 109 and radii. The base lug 104 tapers towards the threaded portion of the female part 101 at a negative angle of about 15 ° relative to a direction perpendicular to the center axis A. The base lug 104 is connected to the mantle surface of the base portion 102 via a chamfer 110 of about 15 ° relative to the center axis A. The end portion 103 terminates at the end lug 105 which tapers at a negative angle of about 15 ° relative to a direction perpendicular to the center axis A, and is connected to an outer surface 111 of the female part.
Pressure anchor 108 and clearance anchor 109 have the same positive and negative angles as the corresponding angles for trade 1.
The thread bottom 106 of the female portion 101 may be substantially parallel to the center axis A, providing a constant wall thickness of the female portion wall 112. The thread tip 107 may taper toward the female end portion 103 at an angle 120 of about 0.28 ° relative to the center axis A. Therefore, the thread depth of the thread portion is axially closer to the base portion of each part different from the thread depth of the thread part which is axially closer to the end portion of each part.
The thread pitch of the trade 1 and the female part 101, respectively, can be about 2.5 threads per inch.
In the connection connection between the trade 1 and the female part 101, the pressure anchor 8, 108 of the two parts is connected and provides the tensile load capacity of the connection. The difference between the angles 26 and 120 of the two thread peaks 27 and 107 and the two thread bottoms 6 and 106 creates, as seen in Fig. 3, tapered free spaces 201, 202, between the female thread bottom 106 and the hanger thread top 7, and between the female thread top 107 and the hanger thread bottom 6. The threaded bottoms 6, 106 can be substantially parallel to the center axis A. This feature provides a good and effective connection surface between the pressure anchors 8 and 108. In addition, the radii 40, 41 connected to the pressure anchors help to provide a more efficient connection surface. The tapered free spaces 201, 202, together with the free space 203 between the clearance anchors 9, 109, form space for dirt and grease in the thread. This has the positive effect of reducing grease and dirt interference on the pressure connection connection. To enable the solution in this embodiment, with reduced thread depth and increased wall 11, 112 thickness, the material of the walls 11, 112 and the threads may be of hardened steel. With a material that is not fully hardened, for example surface hardened, there is a risk of weaker threads due to heat-affected areas.

权利要求:
Claims (24)
[1]
1. PATENT REQUIREMENTS
[2]
2.. A part (1, 101) of a joint for a thin-walled drill pipe, having a central axis (A) and comprising a thread (4) for forming a screw joint, the thread having: a thread bottom (6, 106), a thread top (7 , 107), a pressure ﬂ ank (8, 108) and a clearance ﬂ ank (9, 109), characterized in that the pressure ﬂ ank (8, 108) has a portion having a negative angle (21) of less than 7, 5 °, but greater than 0 °, relative to a direction perpendicular to the central axis (A).
[3]
3.. A part according to claim 1, wherein the negative angle (21) is from about 1 ° to 6 °, about 2 ° to 5 °, or from about 4 ° to 5 ° relative to the angular direction to the central axis (A).
[4]
4.. Part according to any one of the preceding claims, wherein the part is made of substantially hardened steel. Part according to any one of the preceding claims, wherein the radial distance (32) between the thread bottom (6, 106) and the thread top (7, 107) is from about 0.5 to 0.8 mm, from about 0.5 to 0.7 mm, or from about 0.5 to 0.6 mm.
[5]
5.. A part according to any one of the preceding claims, wherein a material thickness at at least one of the thread bottom (6, 106) and the thread top (7, 107) tapers towards an end portion (5, 105) of the part.
[6]
6.. A part according to claim 5, wherein the thread bottom (6, 106) is substantially parallel to the central axis, and the material thickness of the thread top (7, 107) tapers towards an end portion (5, 105) of the part. 10 15 20 25 30 35 11
[7]
A part according to any one of the preceding claims, wherein a section of the thread has a portion of the clearance anchor (9, 109) with an angle (23) which is less than 45 ° relative to the direction perpendicular to the central axis.
[8]
A part according to any one of the preceding claims, wherein the thread has a first section and a second section having different clearance angles.
[9]
A part according to claim 8, wherein the first section is located closer to an end portion (5, 105) of the part than the second section, and has a clearance flank portion (12) with an angle (22) of from about 10 ° to 40 °, from about 20 ° to 35 °, or about 30 ° relative to a direction perpendicular to the central axis, and the second section has a clearance portion (9, 109) with an angle (23) of from about 0 ° to 15 °, from about 1 ° to 10 °, or about 5 ° relative to a direction perpendicular to the central axis.
[10]
A part according to any one of the preceding claims, wherein the thread pitch is from about 1.8 to 1.6 threads per centimeter, from about 0.8 to 1.2 threads per centimeter, or about 1 thread per centimeter.
[11]
A part according to any one of the preceding claims, wherein at least one of the pressure ﬂ anchor and clearance ﬂ anchor is connected to the thread bottom via a radius «which is greater than about 0.10 mm or greater than about 0.15 mm.
[12]
A part according to any one of the preceding claims, wherein at least one of the pressure ﬂ anchor and the clearance ﬂ anchor is connected to the thread tip via a radius greater than about 0.10 mm or greater than about 0.15 mm or greater than about 0.20 mm.
[13]
A part according to any one of the preceding claims, wherein the part is a trade, and the thread extends along an outer portion of the part. 10 15 20 25 30 35 12
[14]
A part according to claim 13, wherein the material thickness of the thread tip (7) tapers at an angle (26) of from about 1.7 ° to 2.5 °, or from about 2 ° to 2.5 ° relative to the center axis.
[15]
A part according to claim 13, wherein the material thickness of the thread tip (7) tapers at an angle (26) of from about 0.2 ° to 0.6 °, from about 0.3 ° to 0.5 °, from about 0 °. 3 ° to 0.4 °, or about 0.34 ° relative to the central axis.
[16]
A part according to any one of claims 1-12, wherein the part is a female part, and the thread extends at an inner portion of the part.
[17]
The part of claim 16, wherein the material thickness of the thread tip (107) tapers at an angle (120) of from about 0.2 ° to 0.6 °, from about 0.2 ° to 0.4 °, from about 0 °. 2 ° to 0.3 °, or about 0.28 ° relative to the central axis.
[18]
A connection system for a drill pipe, comprising a handle according to any one of claims 13-15, and a female part according to claim 16 or 17.
[19]
A dressing system according to claim 18, wherein a tapered free space (201, 202) is provided between a threaded top of one of said parts and a threaded bottom of the outer of said parts.
[20]
A dressing system according to claim 19, wherein the free space is restored over at least two adjacent threads.
[21]
A thin-walled drill pipe system, comprising a dressing system according to any one of claims 18-20, wherein the trade is arranged on a first thin-walled drill pipe and the female part is arranged on a second thin-walled drill pipe.
[22]
A part (1, 101) of a joint for a thin-walled drill pipe, having a central axis and comprising a thread for forming a screw connection, the thread having: a thread bottom (6, 106), a thread top (7, 107), a pressure ﬂ ank (8, 108) and a clearance ﬂ ank (9, 109), characterized in that the material thickness at at least one of the thread bottom (6, 106) and the thread top (7, 107) tapers towards an end portion (5, 105) of the part (1, 101).
[23]
A part (1, 101) of a joint for a thin-walled drill pipe, having a central axis (A) and comprising a thread (4) for forming a screw connection, the thread having: a thread bottom (6, 106), a thread tip ( 7, 107), a pressure ﬂ anchor (8, 108) and a clearance ﬂ ankle (9, 109), characterized in that at least one of the pressure ﬂ anchor (8, 108) and the clearance 109 anchor (9, 109) is connected to the threaded bottom via a radius (41 , 43) about 0.15 mm.
[24]
A part (1, 101) of a joint for a thin-walled drill pipe, having a central axis (A) and comprising a thread (4) for forming a screw joint, the thread having: a thread bottom (6, 106), a thread tip ( 7, 107), a pressure ﬂ anchor (8, 108) and a clearance ﬂ ankle (9, 109), characterized in that at least one of the pressure ﬂ anchor (8, 108) and the clearance ång anchor (9, 109) is connected to the thread top via a radius (40, 42) about 0.20 mm.

类似技术:

公开号 | 公开日 | 专利标题

SE0900388A1|2010-09-27|Threaded thin walled drill pipe joint

JP6518188B2|2019-05-22|Tool fixing structure

SE521790C2|2003-12-09|Threaded connection for straight hole drilling system

CA2763704C|2017-03-21|Connection between a drill pipe and a connector

FI125990B|2016-05-13|Pile

KR100556271B1|2006-03-03|Connection device for string of drill pipes for rotary percussion drilling, especially for simultaneous drilling

US660308A|1900-10-23|Dowel-pin for tiles or bricks.

CN105696836A|2016-06-22|Super-strength composite material electric pole

US10221570B2|2019-03-05|Anchorage device

EP3095955A1|2016-11-23|Threaded coupling end for drill string component

US6514013B2|2003-02-04|Anchor rod with surface areas and friction

KR101616353B1|2016-04-28|Joint structure for connecting pipe

CN205960571U|2017-02-15|Interior copper wire formula bellows that partly buries

JP2013053425A|2013-03-21|Connection structure of different-diameter steel pipes

RU2440481C1|2012-01-20|Tight threaded connection of pipes in process string of geological exploration drilling device

NL2015529B1|2017-04-20|A combination of a first pipe section and a second pipe section, a pipe, a method to construct a pipe, and a pipe section.

KR102070888B1|2020-01-29|Self-forming Screw

CN210179079U|2020-03-24|Composite stainless steel pipe

CN214383924U|2021-10-12|Filling pile grouting pipe adapter

US9982702B2|2018-05-29|Threaded sleeve

RU25557U1|2002-10-10|PUMP BAR

JP2000008760A|2000-01-11|Linear boring system

CN113983077A|2022-01-28|Circumferential sectional type expansion sleeve or expansion piece

JP5393319B2|2014-01-22|Gripping member

RU2294476C1|2007-02-27|Pipe joint

同族专利:

公开号 | 公开日

EP2411619A1|2012-02-01|

AU2010229427B2|2014-12-11|

US8919824B2|2014-12-30|

ZA201106992B|2018-11-28|

CA2756220A1|2010-09-30|

CN102365417A|2012-02-29|

WO2010110720A1|2010-09-30|

SE534883C2|2012-01-31|

AU2010229427A1|2011-10-20|

EP2411619A4|2017-07-26|

CN102365417B|2014-03-26|

US20120013123A1|2012-01-19|

CA2756220C|2017-05-23|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US2893759A|1957-05-06|1959-07-07|Smith Corp A O|Conically tapered screw-type casing joint with metal-to-metal seal|

LU51742A1|1966-08-10|1968-03-25|

US4429904A|1981-07-06|1984-02-07|Dril-Quip, Inc.|Self-aligning connector|

CA1322773C|1989-07-28|1993-10-05|Erich F. Klementich|Threaded tubular connection|

JP3057857B2|1991-11-08|2000-07-04|日本鋼管株式会社|High torque tool joint|

US5788401A|1996-12-24|1998-08-04|Boart Longyear International Holdings, Inc.|Rod joint|

AR020201A1|1998-09-07|2002-05-02|Sumitomo Metal Ind|THREADED CONNECTION OF TWO METAL PIPES AND USE OF TWO THREADED CONNECTIONS.|

AU2003100222B4|2000-07-21|2003-06-19|Todd Andrew Haines|Couplings for rotary drill strings|

FR2813375B1|2000-08-31|2003-06-20|Vallourec Mannesmann Oil & Gas|THREADED ELEMENT FOR TUBULAR THREAD-RESISTANT THREADED JOINT|

FR2820806B1|2001-02-09|2004-02-20|Vallourec Mannesmann Oil & Gas|TUBULAR THREAD JOINT WITH CONVEXED BOMBED THREAD SIDE|

US6767035B2|2002-03-11|2004-07-27|Weatherford/Lamb, Inc.|High torque modified profile threaded tubular connection|

CA2481609A1|2004-09-28|2006-03-28|Argus Machine Co. Ltd.|Threaded connection for drill pipes|

PL2002165T3|2006-03-31|2017-12-29|Nippon Steel & Sumitomo Metal Corporation|Tubular threaded joint|WO2016033687A1|2014-09-03|2016-03-10|Diversity Technologies Corporation|Threaded joint for coupling rods|

US10041307B2|2015-01-22|2018-08-07|National Oilwell Varco, L.P.|Balanced thread form, tubulars employing the same, and methods relating thereto|

US11230891B2|2015-08-27|2022-01-25|Diversity Technologies Corporation|Threaded joint|

US9683684B1|2015-12-09|2017-06-20|Certus Energy Solutions, Llc|Tubular coupling|

法律状态:
2020-01-02| CANC| Patent cancelled, revoked after opposition|

2020-01-02| NAV| Patent application has lapsed|

优先权:

申请号 | 申请日 | 专利标题

SE0900388A|SE534883C2|2009-03-26|2009-03-26|Part of a joint in a thin wall drill pipe, joint system and thin wall drill pipe system.|SE0900388A| SE534883C2|2009-03-26|2009-03-26|Part of a joint in a thin wall drill pipe, joint system and thin wall drill pipe system.|

EP10756417.1A| EP2411619A4|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

PCT/SE2010/050173| WO2010110720A1|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

AU2010229427A| AU2010229427B2|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

US13/258,749| US8919824B2|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

CN201080014010.0A| CN102365417B|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

CA2756220A| CA2756220C|2009-03-26|2010-02-16|Threaded thin-walled drill tube joint|

ZA2011/06992A| ZA201106992B|2009-03-26|2011-09-23|Threaded thin-walled drill tube joint|

[返回顶部]