JP2001124253A - Screw joint for steel pipe - Google Patents

Screw joint for steel pipe

Info

Publication number
JP2001124253A
JP2001124253A JP30840399A JP30840399A JP2001124253A JP 2001124253 A JP2001124253 A JP 2001124253A JP 30840399 A JP30840399 A JP 30840399A JP 30840399 A JP30840399 A JP 30840399A JP 2001124253 A JP2001124253 A JP 2001124253A
Authority
JP
Japan
Prior art keywords
screw
pin
threaded joint
contact
gap
Prior art date
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.)
Pending
Application number
JP30840399A
Other languages
Japanese (ja)
Inventor
Masao Yamaguchi
正男 山口
Kazuhiro Uozumi
一裕 魚住
Original Assignee
Kawasaki Steel Corp
川崎製鉄株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kawasaki Steel Corp, 川崎製鉄株式会社 filed Critical Kawasaki Steel Corp
Priority to JP30840399A priority Critical patent/JP2001124253A/en
Publication of JP2001124253A publication Critical patent/JP2001124253A/en
Pending legal-status Critical Current

Links

Abstract

PROBLEM TO BE SOLVED: To provide a screw joint for a steel pipe which causes no fluid leakage even when not only the compression but also the tension or the bending is loaded during the execution. SOLUTION: In the screw joint for the steel pipe comprising a pin which is reduced in outside diameter toward the tip and has a lip part having a male screw on an outer circumferential surface and a seal surface on the tip, and a box having a female screw screwed in the male screw of the pin on the inner circumference and a shoulder part in contact with the lip part to the distal side of the inner circumference, load surfaces formed by the male screw and the female screw are brought into contact with each other, and a gap of 0.035-0.170 mm is formed in an insertion surface.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION
【0001】[0001]
【発明の属する技術分野】本発明は、鋼管用ネジ継手に
係わり、特に、外圧、引張力、圧縮力及び曲げ応力等が
作用しても、流体漏れが生じない技術に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a threaded joint for steel pipes, and more particularly to a technique for preventing fluid leakage even when an external pressure, a tensile force, a compressive force, a bending stress or the like is applied.
【0002】[0002]
【従来の技術】今日、深さ数千mにも及ぶ天然ガス田や
原油田等の探査・生産に使用される鋼管(例えば、油井
管)を接続する技術としてネジ継手が広く用いられてい
る。このネジ継手は、油井管(以下、単に管ということ
あり)が高圧,高荷重及び悪環境下で使用されるため、
接続された管の自重による軸方向の引張力に耐え得るこ
と、外圧に耐え得ること、数十回の繰り返し使用ができ
ること等の性能が要求されている。また、このネジ継手
には、管の一端に雄ネジを有するピン部を,他端に雌ネ
ジを有するボックス部を設けて、それらを介して管同士
を接続するインテグラル方式と、図3に示すように、両
端に二つのボックス部1を設けたカップリング2を使用
して、両端にピン部3を設けた油井管4を互いに接続す
るカップリング方式とがある。
2. Description of the Related Art Today, threaded joints are widely used as a technique for connecting steel pipes (for example, oil well pipes) used for exploration and production of natural gas fields, crude oil fields and the like having a depth of several thousand meters. . This threaded joint is used for oil country tubular goods (hereinafter sometimes simply referred to as pipes) under high pressure, high load and bad environment.
There is a demand for performance such as the ability to withstand the tensile force in the axial direction due to the weight of the connected pipe, the ability to withstand external pressure, and the ability to be used repeatedly several tens of times. In addition, this screw joint is provided with a pin portion having a male thread at one end of the pipe and a box portion having a female thread at the other end, and an integral type in which the pipes are connected to each other through them. As shown, there is a coupling method in which a coupling 2 having two box portions 1 at both ends is used, and an oil country tubular good 4 having pin portions 3 at both ends is connected to each other.
【0003】このボックス部1の内周は、先端から軸線
方向に沿い奥へ進むにつれ、テーパをもって内径が減少
し、図4に示すような雌ネジ5が刻設され、内奥の周壁
には、図5に示すように、軸心に向かって突出した環状
の肩部6(ショルダという)が形成されている。他方、
該ボックス部1に螺合されるピン部3には、前記雌ネジ
5に螺合される雄ネジ7が刻設されていると共に、該雄
ネジ7の先にネジのない部分(リップ部8という)が設
けられている。このリップ部8の外周面も、テーパ状に
なっており、図5で明らかなように、その突端はオーバ
ハング状になっている。従って、このリップ部8が、前
記ボックス部1の内周奥と接すると、そこに突き当てに
よるシール面(金属面対金属面のシールと称される)が
形成される。
[0003] The inner circumference of the box portion 1 is tapered, and the inner diameter is reduced as it progresses in the axial direction from the tip to the back, and a female screw 5 as shown in FIG. As shown in FIG. 5, an annular shoulder 6 (referred to as a shoulder) protruding toward the axis is formed. On the other hand,
A male screw 7 to be screwed to the female screw 5 is engraved on the pin portion 3 screwed to the box portion 1, and a screwless portion (lip portion 8) is provided at the tip of the male screw 7. Is provided). The outer peripheral surface of the lip portion 8 is also tapered, and its protruding end is overhanging, as apparent from FIG. Therefore, when the lip portion 8 comes into contact with the inner peripheral portion of the box portion 1, a seal surface (referred to as a metal surface-to-metal surface seal) is formed by abutting therewith.
【0004】一方、ネジは、図4に示したように、雄ネ
ジ7と雌ネジ5の締結時の噛合いにより、雄ネジ7及び
雌ネジ5が互いに接触する面をそれぞれの荷重面9とい
い、該面9の傾斜を管軸線と垂直な線を基準にして、ロ
ード・フランク角α(反時計方向を負)と称している。
また、雄ネジ7と雌ネジ5との間に隙間13が生じる側
の面を、それぞれの挿入面10といい、この面10の傾
斜は、スタッビング・フランク角θ(反時計方向を正)
という。さらに、締結時のネジ面の接触状態は、前記図
4に示したように、荷重面9で接触、挿入面10で非接
触、頂面11及び底面12の少なくとも一方で接触とな
り、これらネジ面の接触でもシールが確保できる。つま
り、かかるネジ継手は、ピン部3及びボックス部1のネ
ジ同士の接触と突き当てシール面の接触によって、高い
機密性を保持するようになっている。
On the other hand, as shown in FIG. 4, the surfaces of the male screw 7 and the female screw 5 that come into contact with each other by the engagement of the male screw 7 and the female screw 5 at the time of fastening, as shown in FIG. In other words, the inclination of the surface 9 is referred to as a load flank angle α (counterclockwise is negative) with reference to a line perpendicular to the tube axis.
The surface on the side where the gap 13 is formed between the male screw 7 and the female screw 5 is referred to as the respective insertion surface 10, and the inclination of the surface 10 is the stubbing flank angle θ (positive in the counterclockwise direction).
That. Further, as shown in FIG. 4, the contact state of the screw surface at the time of fastening is such that the load surface 9 makes contact, the insertion surface 10 makes no contact, and at least one of the top surface 11 and the bottom surface 12 makes contact. The seal can be ensured even in contact with. In other words, such a threaded joint maintains high confidentiality due to the contact between the screws of the pin portion 3 and the box portion 1 and the contact of the abutting seal surface.
【0005】しかしながら、最近は、油井管4の施工時
に、該油井管4やネジ継手の軸方向に圧縮力の負荷され
る頻度が高くなってきた。この場合、圧縮後、さらに油
井管4の自重でネジに引張力あるいは曲げ力が負荷され
ることになる。そのためか、前記したシール性に優れた
ネジ継手でも、内部流体(天然ガス、原油)が外部に漏
れるという不具合が生じることが多い。また、この現象
が生じている状態で、接合を緩める方向にトルクが作用
すると、継手が外れ、油井管4が井戸の中に落ち込むこ
とがある。そのようになると、継手の再接続は極めて難
しいので、開発中あるいは生産中の井戸掘りをあきらめ
ることになる。
[0005] However, recently, when the oil country tubular goods 4 are constructed, the frequency of applying a compressive force in the axial direction of the oil country pipes 4 and the threaded joints has increased. In this case, after the compression, a tensile force or a bending force is further applied to the screw by its own weight of the oil country tubular good 4. For this reason, even with the above-mentioned threaded joint having excellent sealing properties, a problem often occurs in that the internal fluid (natural gas, crude oil) leaks to the outside. In addition, if a torque acts in a direction in which the joining is loosened in a state where this phenomenon occurs, the joint may come off, and the oil country tubular good 4 may fall into the well. In such a case, reconnection of the joints is extremely difficult, so that the well digging during development or production is abandoned.
【0006】[0006]
【発明が解決しようとする課題】本発明は、かかる事情
に鑑み、油井管の施工時に、圧縮ばかりでなく引張や曲
げが負荷されても、流体漏れの生じない鋼管用ネジ継手
を提供することを目的としている。
SUMMARY OF THE INVENTION In view of the above circumstances, the present invention provides a threaded joint for a steel pipe which does not leak even if it is subjected not only to compression but also to tension or bending during construction of an oil country tubular good. It is an object.
【0007】[0007]
【課題を解決するための手段】発明者は、上記目的を達
成するため流体漏れの原因を検討し、「強力な圧縮力が
加わった時に、ネジ継手の前記シール面に変形が生じ、
次に引張力が加わっても元に戻らず、隙間として残るこ
とにある」と結論した。つまり、油井管(ピン側)に大
きな圧縮力がかかると、ピン先端とボックス内周奥との
突合せたシール面を境にして力が反発し合い、材料自体
の移動が起きて、ピン側及びボックス側のシール面がと
もに塑性変形する。その後、引張力がかかると、塑性変
形された部分はそのまま保持されているので、隙間13
が形成される。そこで、発明者は、引き続き流体漏れの
対策を鋭意研究し、ネジ山の刻設位置の変更で解決でき
ることを見出し、それを本発明に具現化したのである。
The inventor of the present invention has studied the causes of fluid leakage in order to achieve the above object, and stated that "when a strong compressive force is applied, the seal surface of the threaded joint is deformed,
Next, even if a tensile force is applied, it does not return to its original state and remains as a gap. " In other words, when a large compressive force is applied to the oil country tubular goods (pin side), the forces repel each other at the sealing surface where the tip of the pin and the inner periphery of the box abut, and the movement of the material itself occurs. Both the sealing surfaces on the box side are plastically deformed. Thereafter, when a tensile force is applied, the plastically deformed portion is held as it is, so that the gap 13
Is formed. Then, the inventor continued to study diligently for measures against fluid leakage, and found that it could be solved by changing the engraved position of the screw thread, and embodied it in the present invention.
【0008】すなわち、本発明は、先端に向けて外径が
小さくなり、外周面に雄ネジ、先端にシール面を形成す
るリップ部を有するピンと、内周に前記ピンの雄ネジに
螺合される雌ネジ、内周奥に前記リップ部と接する肩部
を有するボックスとを備えた鋼管用ネジ継手において、
前記雄ネジと雌ネジとが形成する荷重面は互いに接触
し、挿入面が0.035〜0.170mmの隙間を形成
してなるとを特徴とする鋼管用ネジ継手である。
That is, according to the present invention, the outer diameter is reduced toward the tip, and a pin having a male screw on the outer peripheral surface and a lip portion forming a sealing surface at the tip is screwed into the male screw of the pin on the inner circumference. Female screw, a box having a shoulder portion in contact with the lip portion at the inner periphery,
A load joint formed by the male screw and the female screw is in contact with each other, and the insertion surface forms a gap of 0.035 to 0.170 mm.
【0009】また、本発明は、前記雄ネジ及び雌ネジの
ネジ山が台形であることを特徴とする鋼管用ネジ継手で
ある。
The present invention is also a threaded joint for steel pipes, wherein the thread of the male screw and the female screw is trapezoidal.
【0010】本発明によれば、圧縮後に引っ張りが負荷
されても、ネジやシール面の塑性変形が緩和されるよう
になるので、ネジ継手のシール性は、良好に保持され
る。
According to the present invention, even if a tensile force is applied after the compression, the plastic deformation of the screw and the sealing surface is alleviated, so that the sealing property of the threaded joint is well maintained.
【0011】[0011]
【発明の実施の形態】以下、発明をなす経緯も交え、本
発明の実施の形態を説明する。
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with the background of the invention.
【0012】まず、発明者は、前記流体漏れの原因を配
慮し、ネジ継手の従来の構造を詳細に調査した。そし
て、図4に示したように、ピン3の雄ネジ7とボックス
1の雌ネジ5とが形成する挿入面9の隙間13に着眼し
た。着眼した理由は、そこに隙間13があると、油井管
4やネジ継手に圧縮力や引張力がかかった場合、ネジや
シール面に変形が生じる恐れがあるからである。調査結
果は、構造が類似した多くのネジ継手は、該挿入面9に
0.200〜0.350mmの隙間13があった。なか
には、特許第2705506号公報に開示されている
0.03mm以下という例もあったが、この寸法は、現
在のネジ切り加工技術では、実施不可能なので、考慮対
象にならない。また、例え製作できたとしても、そのよ
うに狭いと、油井管4の施工時にネジ山の「むしれ」
(ゴーリングという)が生じ、実用し難いと考えられ
る。
First, the inventor examined the conventional structure of the threaded joint in detail in consideration of the cause of the fluid leakage. Then, as shown in FIG. 4, attention was paid to the gap 13 between the insertion surface 9 formed by the male screw 7 of the pin 3 and the female screw 5 of the box 1. The reason for focusing on this is that if there is a gap 13 in the oil well pipe 4 or the threaded joint, the screw or the sealing surface may be deformed when a compressive force or a tensile force is applied to the oil country tubular good 4 or the screw joint. The result of the investigation showed that many screw joints having similar structures had a gap 13 of 0.200 to 0.350 mm on the insertion surface 9. Among them, there is an example of 0.03 mm or less disclosed in Japanese Patent No. 2705506, but this dimension is not considered because it cannot be implemented with the current thread cutting technology. Also, even if it can be manufactured, if it is so narrow, the thread "Murashi" at the time of construction of the oil well pipe 4
(Referred to as galling), which is considered to be difficult to use.
【0013】そこで、発明者は、上記隙間13の大きさ
を如何にしたら、圧縮時にシール面に塑性変形が生じな
い、つまり材料自体が弾性限界内の変形におさまるかに
ついて鋭意考察した。そして、現在の油井管やネジ継手
の材質、寸法(外径、肉厚及び長さ)や負荷される圧縮
力の大きさに基づき、材料力学的な考察を行ない、0.
035〜0.170mmが好ましいことを知見した。そ
して、多種の材料で多くの材料試験を行い、この隙間1
3範囲で良いとの確証を得、本発明を完成させたのであ
る。該隙間13が0.035mm未満のネジ継手は、塑
性変形を回避する点では好ましいが、実際には製作でき
ないので、本発明の範囲から除外し、0.170mm超
えのネジ継手は、塑性変形が避けられないので、除外す
ることにしたのである。
Therefore, the inventor of the present invention has studied diligently whether the size of the gap 13 does not cause plastic deformation of the sealing surface during compression, that is, whether the material itself can be deformed within the elastic limit. Based on the current materials and dimensions (outer diameter, wall thickness, and length) of the oil country tubular goods and threaded joints and the magnitude of the applied compressive force, material dynamics are considered.
It has been found that 035 to 0.170 mm is preferable. Then, many material tests were conducted with various kinds of materials, and this gap 1
It was confirmed that three ranges were sufficient, and the present invention was completed. The threaded joint having the gap 13 of less than 0.035 mm is preferable from the viewpoint of avoiding plastic deformation, but cannot be actually manufactured. Therefore, the threaded joint is excluded from the scope of the present invention. It was inevitable, so we decided to exclude it.
【0014】ネジ山の形状については、本発明では、特
に限定しない。つまり、ネジには、荷重面9の傾斜(ロ
ード・フランク角という)が、図1に示すように、負に
したものもあるが、本発明は、挿入面10の隙間13の
みを問題にしているので、API(American
Petroleam Institute)規格に規定
された台形ネジにも有効である。
The shape of the thread is not particularly limited in the present invention. That is, as shown in FIG. 1, some screws have a negative inclination (referred to as a load flank angle) of the load surface 9, but the present invention takes only the gap 13 of the insertion surface 10 into consideration. API (American)
It is also effective for trapezoidal screws specified in the Petroleum Institute standard.
【0015】[0015]
【実施例】油井管先端に設けたピン3の外周、及びカッ
プリング2の両端に設けたボックス1の内周に、図1に
示した形状の各ネジと図2に示した各シール面とを有す
るネジ継手を設け、ピン3とカップリング2とを接続し
て流体漏れの調査を行った。その際使用した油井管4及
びカップリング2のサイズは、表1の通りである。ま
た、同じ油井管4及びカップリング2に従来通りのネジ
継手(挿入面の隙間13が0.274mmと広い)を設
けたものでの調査も行った。いずれの調査も、流体とし
て原油や天然ガスに代えて高圧の水及びガスを採用し、
漏れ程度の評価は、API規格別でA1クラス(最上
級)に準ずる方法で行った。なお、各継手の荷重面9及
び挿入面10のロード・フランク角α及びスタビング・
フランク角θは、種々の値を組み合わせるようにした。
DESCRIPTION OF THE PREFERRED EMBODIMENTS On the outer periphery of a pin 3 provided at the tip of an oil country tubular good and on the inner periphery of a box 1 provided at both ends of a coupling 2, each screw having the shape shown in FIG. 1 and each sealing surface shown in FIG. Was provided, and the pin 3 and the coupling 2 were connected to investigate the fluid leakage. Table 1 shows the sizes of the oil country tubular goods 4 and the couplings 2 used at that time. In addition, an investigation was conducted using the same oil well pipe 4 and coupling 2 provided with a conventional threaded joint (the gap 13 on the insertion surface was as large as 0.274 mm). Both studies used high-pressure water and gas instead of crude oil and natural gas as the fluid,
The evaluation of the degree of leakage was performed according to the A1 class (highest grade) according to API standards. In addition, the load flank angle α of the load surface 9 and the insertion surface 10 of each joint and the stubbing angle
The flank angle θ is made to combine various values.
【0016】調査の結果を表2に一括して示す。表2よ
り明らかなように、本発明に係るネジ継手は、ネジの挿
入面10の隙間13が塑性変形を防止するので、いずれ
の場合も、施工時にシール面に隙間が生じることがな
い。その結果、流体(ガス及び液)漏れが生じなかっ
た。それに対して、従来のネジ継手の場合は、やはり損
傷や流体漏れが生じていた。なお、表2の損傷率、ある
いは流体漏れ率は、各実施例でそれぞれ油井管の接続を
50本行い、それらの発生率で示している。
Table 2 shows the results of the survey. As is clear from Table 2, in the threaded joint according to the present invention, the gap 13 in the screw insertion surface 10 prevents plastic deformation, and in any case, no gap is generated in the sealing surface during construction. As a result, fluid (gas and liquid) leakage did not occur. On the other hand, in the case of the conventional threaded joint, damage and fluid leakage also occurred. In addition, the damage rate or the fluid leakage rate in Table 2 is shown by the occurrence rate of each connection of 50 oil country tubular goods in each example.
【0017】[0017]
【表1】 [Table 1]
【0018】[0018]
【表2】 [Table 2]
【0019】なお、上記実施例では、ネジ継手をカップ
リング方式のものとしたが、本発明は、インテグラル方
式のものにも適用できることは言うまでもない。
In the above embodiment, the threaded joint is of the coupling type, but it goes without saying that the present invention can be applied to the integral type.
【0020】[0020]
【発明の効果】以上述べたように、本発明により、油井
管の接続時に大きな圧縮力の後に、引張りや曲げが作用
しても、従来のような損傷及び液漏れは生じなくなっ
た。
As described above, according to the present invention, even if a tensile force or a bending force acts after a large compressive force at the time of connecting an oil country tubular good, damage and liquid leakage as in the prior art do not occur.
【図面の簡単な説明】[Brief description of the drawings]
【図1】挿入面の隙間を0.03〜0.170mmとし
た本発明に係るネジ部の一例を示す図である。
FIG. 1 is a view showing an example of a screw portion according to the present invention in which a gap between insertion surfaces is set to 0.03 to 0.170 mm.
【図2】図1のネジ部につながったシール部を示す図で
ある。
FIG. 2 is a view showing a seal part connected to a screw part of FIG. 1;
【図3】従来のカップリング方式のネジ継手を示す図で
ある。
FIG. 3 is a view showing a conventional coupling type screw joint.
【図4】図3に示したネジ継手のネジ部を拡大した図で
ある。
FIG. 4 is an enlarged view of a thread portion of the threaded joint shown in FIG. 3;
【図5】図3に示したネジ継手のシール部を拡大した図
である。
FIG. 5 is an enlarged view of a seal portion of the threaded joint shown in FIG.
【符号の説明】[Explanation of symbols]
1 ボックス部(ボックス) 2 カップリング 3 ピン部(ピン) 4 油井管(管) 5 雌ネジ 6 肩部(ショルダ) 7 雄ネジ 8 リップ部 9 荷重面 10 挿入面 11 頂面 12 底面 13 隙間 DESCRIPTION OF SYMBOLS 1 Box part (box) 2 Coupling 3 Pin part (pin) 4 Oil well pipe (pipe) 5 Female screw 6 Shoulder (shoulder) 7 Male screw 8 Lip part 9 Load surface 10 Insertion surface 11 Top surface 12 Bottom surface 13 Clearance

Claims (2)

    【特許請求の範囲】[Claims]
  1. 【請求項1】 先端に向けて外径が小さくなり、外周面
    に雄ネジ、先端にシール面を形成するリップ部を有する
    ピンと、内周に前記ピンの雄ネジに螺合される雌ネジ、
    内周奥に前記リップ部と接する肩部を有するボックスと
    を備えた鋼管用ネジ継手において、 前記雄ネジと雌ネジとが形成する荷重面は互いに接触
    し、挿入面が0.035〜0.170mmの隙間を形成
    してなるとを特徴とする鋼管用ネジ継手。
    A pin having a male thread on an outer peripheral surface and a lip portion forming a sealing surface at a distal end, and a female screw screwed on an inner periphery with a male screw of the pin,
    In a threaded joint for steel pipes provided with a box having a shoulder portion in contact with the lip portion at the inner periphery, a load surface formed by the male screw and the female screw is in contact with each other, and an insertion surface is 0.035-0. A threaded joint for steel pipes, wherein a 170 mm gap is formed.
  2. 【請求項2】 前記雄ネジ及び雌ネジのネジ山が台形で
    あることを特徴とする請求項1記載の鋼管用ネジ継手。
    2. The threaded joint for a steel pipe according to claim 1, wherein the threads of the male screw and the female screw are trapezoidal.
JP30840399A 1999-10-29 1999-10-29 Screw joint for steel pipe Pending JP2001124253A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP30840399A JP2001124253A (en) 1999-10-29 1999-10-29 Screw joint for steel pipe

Publications (1)

Publication Number Publication Date
JP2001124253A true JP2001124253A (en) 2001-05-11

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ID=17980654

Family Applications (1)

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007114460A1 (en) * 2006-03-31 2007-10-11 Sumitomo Metal Industries, Ltd. Tubular threaded joint
JP2008527256A (en) * 2004-12-30 2008-07-24 ハイドリル・カンパニー・エルピー Floating wedge screw for cylindrical connection
WO2012002409A1 (en) 2010-06-30 2012-01-05 Jfeスチール株式会社 Pipe screw coupling
JP2012510009A (en) * 2008-11-24 2012-04-26 ヴァム・ユーエスエー.エルエルシー Screw connection for oil field
CN102691481A (en) * 2011-03-22 2012-09-26 杰富意钢铁株式会社 Screw joint for steel piping
JP2013511672A (en) * 2009-11-20 2013-04-04 ヴァルレック・マンネスマン・オイル・アンド・ガス・フランス Threaded connection
WO2021145161A1 (en) * 2020-01-17 2021-07-22 日本製鉄株式会社 Threaded joint for pipe

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4937137B2 (en) * 2004-12-30 2012-05-23 ハイドリル・カンパニー Floating wedge screw for cylindrical connection
JP2008527256A (en) * 2004-12-30 2008-07-24 ハイドリル・カンパニー・エルピー Floating wedge screw for cylindrical connection
EA014091B1 (en) * 2006-03-31 2010-08-30 Сумитомо Метал Индастриз, Лтд. Tubular threaded joint
AU2007232748B2 (en) * 2006-03-31 2010-10-28 Nippon Steel Corporation Tubular threaded joint
US7823931B2 (en) 2006-03-31 2010-11-02 Sumitomo Metal Industries, Ltd. Tubular threaded joint
WO2007114460A1 (en) * 2006-03-31 2007-10-11 Sumitomo Metal Industries, Ltd. Tubular threaded joint
JP2012510009A (en) * 2008-11-24 2012-04-26 ヴァム・ユーエスエー.エルエルシー Screw connection for oil field
JP2013511672A (en) * 2009-11-20 2013-04-04 ヴァルレック・マンネスマン・オイル・アンド・ガス・フランス Threaded connection
WO2012002409A1 (en) 2010-06-30 2012-01-05 Jfeスチール株式会社 Pipe screw coupling
US9194190B2 (en) 2010-06-30 2015-11-24 Jfe Steel Corporation Threaded joint for pipe
EP3196524A1 (en) 2010-06-30 2017-07-26 JFE Steel Corporation Threaded joint for pipe
CN102691481A (en) * 2011-03-22 2012-09-26 杰富意钢铁株式会社 Screw joint for steel piping
JP2012211683A (en) * 2011-03-22 2012-11-01 Jfe Steel Corp Screw joint for steel piping
WO2021145161A1 (en) * 2020-01-17 2021-07-22 日本製鉄株式会社 Threaded joint for pipe

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