JP5924152B2 - Threaded joints for steel pipes - Google Patents

Threaded joints for steel pipes Download PDF

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JP5924152B2
JP5924152B2 JP2012138443A JP2012138443A JP5924152B2 JP 5924152 B2 JP5924152 B2 JP 5924152B2 JP 2012138443 A JP2012138443 A JP 2012138443A JP 2012138443 A JP2012138443 A JP 2012138443A JP 5924152 B2 JP5924152 B2 JP 5924152B2
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thread
box
taper
screw
pin
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JP2014001820A (en
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順 高野
順 高野
拓也 長濱
拓也 長濱
博 近常
博 近常
吉川　正樹
正樹 吉川
孝将 川井
孝将 川井
植田　正輝
正輝 植田
高橋　一成
一成 高橋
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JFE Steel Corp
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Description

本発明は、鋼管用ねじ継手、特に、相対応する雌雄のテーパねじにて締結する鋼管用ねじ継手に関し、詳しくは、テーパ雄ねじ部および該テーパ雄ねじ部より先端側に非ねじ部を有するピンと、該テーパ雄ねじ部および該非ねじ部それぞれに対応するテーパ雌ねじ部および非ねじ部を有するボックスとがねじ締結されて、前記ピンの非ねじ部と前記ボックスの非ねじ部とが管軸方向の少なくとも１箇所で円周方向に金属接触して管内流体をシールする構成とされた、プレミアムジョイントと通称される、鋼管用ねじ継手に関する。   The present invention relates to a threaded joint for steel pipes, and in particular, to a threaded joint for steel pipes to be fastened by corresponding male and female tapered screws, and more specifically, a tapered male threaded portion and a pin having a non-threaded portion on the tip side from the tapered male threaded portion, The taper male thread part and the box having the taper female thread part and the non-thread part corresponding to the non-thread part are screwed together, and the non-thread part of the pin and the non-thread part of the box are at least one in the tube axis direction. The present invention relates to a threaded joint for steel pipes, commonly referred to as a premium joint, which is configured to seal a fluid in a pipe by metal contact in a circumferential direction at a location.

特許文献１には、管の先端部の外周面に１条ねじのテーパ雄ねじ部を形成したピンと、管の先端部の内周面に前記テーパ雄ねじ部に螺合するテーパ雌ねじ部を形成したボックスとをねじ込む管継手において、前記テーパ雄ねじ部の雄ねじ山のねじ山頂面と前記テーパ雌ねじ部の雌ねじ山のねじ山頂面は、角ねじ、台形ねじ又はバットレスねじのように所定の幅を有し、前記両ねじ山頂面を、管軸に平行な面に対してねじ列テーパ面と反対方向に傾斜させる旨（特許文献１[請求項１]参照）、及びこれで以て、テーパ雄ねじ部を３６０°のどの位置で差し込んでも差し込み及びそれに続くねじ込みの連続作業が可能である旨（特許文献１[0040]参照）記載されている。   Patent Document 1 discloses a box in which a taper male screw portion having a single thread is formed on the outer peripheral surface of the tube tip portion, and a taper female screw portion that is screwed to the taper male screw portion on the inner peripheral surface of the tube tip portion. And the thread top surface of the male thread of the taper male thread part and the thread top surface of the female thread of the taper female thread part have a predetermined width like a square thread, a trapezoidal thread or a buttress thread, The fact that both the thread crest surfaces are inclined in the direction opposite to the thread row taper surface with respect to the surface parallel to the tube axis (see Patent Document 1 [Claim 1]), and with this, the taper male thread portion is 360. It is described that continuous operation of insertion and subsequent screwing is possible (see Patent Document 1 [0040]) regardless of the position of the angle.

特開第３８６９５６５号公報Japanese Patent No. 3869565

鋼管（以下、単に管とも云う）が使用される油井、ガス井では、生産流体による内圧のほか、管の自重や熱膨張による引張力や圧縮力が付与される。引張力はねじの干渉が緩む方向の力であり、圧縮力はねじの干渉が強まる方向の力である。
従来のテーパねじにて締結する管用ねじ継手（管用テーパねじ継手と云う）では、通常、従来例Ａとして図２(a)(b)に示す様に、テーパ雄ねじ部１１を有するピン１と、該テーパ雄ねじ部１１に対応するテーパ雌ねじ部２１を有するボックス２とがねじ結合し、ピンのねじ部先端側の非ねじ部３とこれに対応するボックスの非ねじ部３とが管軸方向４の少なくとも１箇所で円周方向に金属接触して管内流体をシールする構成とされ、ピンねじ底とボックスねじ山の接触面７がねじテーパ面８（詳しくはねじ有効径のテーパ面；特許文献１に云うねじ列テーパ面と同義）との平行面９とされ（図２(a)参照）、若しくは管軸方向４との平行面とされ（図示省略）ている。ＡＰＩバットレスねじでいうと、管外径が１３．３７５インチ以下は前者の例、１３．３７５インチ超が後者の例として挙げられる。 In oil wells and gas wells in which steel pipes (hereinafter simply referred to as pipes) are used, in addition to the internal pressure due to the production fluid, tensile forces and compressive forces due to the pipe's own weight and thermal expansion are applied. The tensile force is a force in a direction in which screw interference is loosened, and the compressive force is a force in a direction in which screw interference is increased.
In a pipe threaded joint (called a pipe taper threaded joint for pipes) fastened with a conventional taper screw, as shown in FIGS. The box 2 having the taper female thread portion 21 corresponding to the taper male thread portion 11 is screw-coupled, and the non-thread portion 3 on the distal end side of the screw portion of the pin and the non-thread portion 3 of the box corresponding thereto are in the tube axis direction 4. The contact surface 7 between the pin screw bottom and the box screw thread is a screw taper surface 8 (specifically, a taper surface with an effective screw diameter; specifically, patent document). 1 (synonymous with a thread row taper surface referred to as 1) (see FIG. 2 (a)) or parallel to the tube axis direction 4 (not shown). In terms of API buttress screws, the tube outer diameter of 13.375 inches or less is the former example, and 13.375 inches or more is the latter example.

尚、ピンねじ山とボックスねじ底の対向面１０もねじテーパ面８との平行面９Ａとされ（図２(a)参照）、若しくは管軸方向との平行面とされ（図示省略）ている。
又、図２(b)の様に、非ねじ部３においては、管軸方向端面が、ねじ締結時の締付け反力礎になるショルダ部６とされ、ショルダ部６とねじ部の間に、ねじ締結時に金属接触させる部位として、シール部５が設けられている。 The opposing surface 10 of the pin screw thread and the box screw bottom is also a parallel surface 9A with the screw taper surface 8 (see FIG. 2 (a)) or a parallel surface with the pipe axis direction (not shown). .
Further, as shown in FIG. 2 (b), in the non-threaded portion 3, the end surface in the tube axis direction is a shoulder portion 6 that serves as a foundation for a tightening reaction force at the time of screw fastening, and between the shoulder portion 6 and the threaded portion, A seal portion 5 is provided as a portion that is brought into metal contact when the screw is fastened.

又、従来例Ｂとしては、特許文献１に記載されたものが挙げられる。これは図３(a)の様に、ピンねじ底とボックスねじ山の接触面７が管軸方向４に対してねじテーパ面８とは逆向きのテーパ面１４Ａ（或いは１４Ｂ）とされ、且つ、ピンねじ山とボックスねじ底の対向面１０も管軸方向４に対してねじテーパ面８とは逆向きのテーパ面１４とされている（特許文献１[図１]参照）。   Moreover, as the conventional example B, what was described in patent document 1 is mentioned. As shown in FIG. 3 (a), the contact surface 7 between the pin screw bottom and the box thread is a tapered surface 14A (or 14B) opposite to the thread tapered surface 8 with respect to the tube axis direction 4, and The opposing surface 10 of the pin screw thread and the box screw bottom is also a tapered surface 14 opposite to the thread tapered surface 8 with respect to the tube axis direction 4 (see Patent Document 1 [FIG. 1]).

然しながら、前記従来例Ａの類の管用テーパねじ継手は、管軸方向引張力１５に対しては、図２(c)(d)の様に、ねじ部においてロードフランク面１２以外には抵抗役ＳＲが無い為、ピン１がボックス２に対し管軸方向４のねじ後進側に移動し易く、ピン１とボックス２のシール部５乃至ショルダ部６の干渉弱化３０が生じ、其部位でピン１とボックス２の間に隙間ができてシール性が低下する問題を孕む。   However, the tapered threaded joint for pipes of the above-mentioned conventional example A has a resistance against the tensile force 15 in the axial direction of the pipe other than the load flank 12 as shown in FIGS. 2 (c) and 2 (d). Since there is no SR, the pin 1 is easy to move backward in the tube axis direction 4 with respect to the box 2, and the interference weakening 30 between the pin 1 and the seal portion 5 to the shoulder portion 6 of the box 2 occurs. And a gap between the box 2 and the sealing performance is reduced.

管軸方向圧縮力１６に対しては、図２(e)(f)の様に、ねじ部においてスタビングフランク面１３が抵抗主役ＳＲ１になるに加え、ピンねじ底とボックスねじ山の接触面７或いは更にピンねじ山とボックスねじ底の対向面１０が抵抗脇役ＳＲ２になるから、シール部５乃至ショルダ部６への悪影響は小さくて、シール性は保持される。
一方、前記従来例Ｂの類の管用テーパねじ継手は、管軸方向引張力１５に対しては、図３(c)(d)の様に、ねじ部においてロードフランク面１２が抵抗主役ＳＲ１になるに加え、ピンねじ底とボックスねじ山の接触面７或いは更にピンねじ山とボックスねじ底の対向面１０が抵抗脇役ＳＲ２になるから、シール部５乃至ショルダ部６への悪影響は小さくて、シール性は保持される。 As shown in FIGS. 2 (e) and 2 (f), for the tube axial compression force 16, in addition to the stubbing flank surface 13 serving as a resistance main role SR1, the contact surface between the pin screw bottom and the box screw thread. 7 or further, the opposing surface 10 of the pin screw thread and the box screw bottom serves as the resistance supporting role SR2, so that the adverse effect on the seal portion 5 to the shoulder portion 6 is small and the sealing performance is maintained.
On the other hand, in the conventional taper threaded joint of the type B, the load flank surface 12 becomes the resistance main role SR1 in the thread portion as shown in FIGS. In addition, since the contact surface 7 between the pin screw bottom and the box screw thread or the opposing surface 10 between the pin screw thread and the box screw bottom serves as the resistance supporting role SR2, the adverse effect on the seal portion 5 to the shoulder portion 6 is small. Sealability is maintained.

然し、管軸方向圧縮力１６に対しては、図３(e)(f)の様に、ねじ部においてスタビングフランク面１３以外には抵抗役ＳＲが無い為、シール部５乃至ショルダ部６に過大な圧力がかかり易く、塑性変形３１を生じ、シール性が低下する問題を孕む。
以上の様に、従来技術では、ねじ部が管軸方向の引張力と圧縮力の双方に対し十分抵抗できるとは云えず、何れか一方に対し抵抗し得ずにシール性の保持が困難になると云う課題があった。 However, as shown in FIGS. 3 (e) and 3 (f), there is no resistance SR other than the stubbing flank surface 13 in the threaded portion against the compressive force 16 in the tube axial direction. An excessive pressure is likely to be applied to the resin, and plastic deformation 31 is generated, resulting in a problem that the sealing performance is deteriorated.
As described above, in the conventional technology, the threaded portion cannot sufficiently resist both the tensile force and the compressive force in the tube axis direction, and it cannot resist either one, and it is difficult to maintain the sealing performance. There was a problem of becoming.

前記課題を解決する為になされた本発明は、
テーパ雄ねじ部および該テーパ雄ねじ部より先端側に非ねじ部を有するピンと、該テーパ雄ねじ部および該非ねじ部それぞれに対応するテーパ雌ねじ部および非ねじ部を有するボックスとがねじ結合し、前記ピンの非ねじ部と前記ボックスの非ねじ部とが管軸方向の少なくとも１箇所で円周方向に金属接触して管内流体をシールする構成とされた鋼管用ねじ継手において、ピンねじ底とボックスねじ山の接触面が、ピン側とボックス側の双方とも、管軸方向に対し互いに逆向きに傾斜した２つの部分からなる組を１組以上含む、くさび型、鋸歯型、波型のいずれかの起伏面形状とされたことを特徴とする鋼管用ねじ継手である。 The present invention has been made to solve the above problems,
A taper male screw portion and a pin having a non-threaded portion on the tip side from the taper male screw portion and a box having a taper female screw portion and a non-thread portion corresponding to each of the taper male screw portion and the non-thread portion are screw-coupled to each other. In a threaded joint for a steel pipe in which a non-threaded portion and a non-threaded portion of the box are in metal contact in a circumferential direction at least at one place in the tube axis direction to seal fluid in the tube, a pin screw bottom and a box thread contact surfaces, both of the pin side and the box side, a set of two portions inclined in opposite directions with respect to the tube axis direction comprises one or more pairs, the wedge-type, saw-tooth, any undulations of corrugated a tubular threaded joint, characterized in that it is the surface shape.

本発明によれば、管軸方向の引張力、圧縮力の何れに対しても、ねじ部が十分に抵抗できて、シール性が保持できると云う効果を奏する。   According to the present invention, there is an effect that the threaded portion can sufficiently resist both the tensile force and the compressive force in the tube axis direction and the sealing performance can be maintained.

本発明の鋼管用ねじ継手の一例を示す概略図である。It is the schematic which shows an example of the threaded joint for steel pipes of this invention. 従来例Ａの管用テーパねじ継手を示す概略図である。It is the schematic which shows the taper threaded joint for pipes of the prior art example A. 従来例Ｂの管用テーパねじ継手を示す概略図である。It is the schematic which shows the taper threaded joint for pipes of the prior art example B. 種々の起伏面形状の例を示す概略図である。It is the schematic which shows the example of various undulating surface shapes.

図１は本発明の鋼管用ねじ継手の一例を示す概略図である。本発明において、テーパ雄ねじ部１１を有するピン１と、該テーパ雄ねじ部１１に対応するテーパ雌ねじ部２１を有するボックス２とがねじ結合し、ピン１のねじ部１１より先端側の非ねじ部３とこれに対応するボックス２の非ねじ部３とが管軸方向４の少なくとも１箇所、例えばシール部５で円周方向に金属接触して管内流体をシールする構成とされた鋼管用ねじ継手である点は、従来と同じである。ねじ締結時の締付け反力礎としてショルダ部６を有する点も従来と同じである。   FIG. 1 is a schematic view showing an example of a threaded joint for steel pipes of the present invention. In the present invention, the pin 1 having the tapered male threaded portion 11 and the box 2 having the tapered female threaded portion 21 corresponding to the tapered male threaded portion 11 are screw-coupled, and the non-threaded portion 3 on the tip side from the threaded portion 11 of the pin 1. And a threaded joint for a steel pipe in which the non-threaded portion 3 of the box 2 corresponding to this is in contact with the metal in the circumferential direction at at least one location in the tube axis direction 4, for example, the seal portion 5 to seal the fluid in the tube. Some points are the same as before. The point which has the shoulder part 6 as a fastening reaction force foundation at the time of screw fastening is the same as the past.

尚、ピンねじ山とボックスねじ底の対向面１０については、図１の例では従来例Ａと同様の面形態としたが、従来例Bと同様の面形態としてもよく、又、これら以外の公知又は公用の面形態としてもよい。
然し、本発明では、ピンねじ底とボックスねじ山の接触面７が、管軸方向４に対し互いに逆向きに傾斜した２つの部分７Ａ，７Ｂからなる組を１組（或いは２組以上）含む起伏面形状とされており、この点は従来に無いものである。 In addition, about the opposing surface 10 of a pin screw thread and a box screw bottom, although it was set as the surface form similar to the prior art example A in the example of FIG. 1, it is good also as a surface form similar to the prior art example B, and other than these It is good also as a well-known or public surface form.
However, in the present invention, the contact surface 7 of the pin screw bottom and the box thread includes one set (or two or more sets) composed of two portions 7A and 7B inclined in opposite directions with respect to the tube axis direction 4. The shape is an undulating surface, which is not present in the past.

図１の例では、管軸方向４に対し互いに逆向きに傾斜した２つの部分７Ａ，７Ｂの組が計１組である場合の起伏面形状を示したが、これはその管軸方向プロフィルが図４(a)に示される折れ線状を呈する所謂くさび型に相当する。これ以外の起伏面形状として、例えば、図４(b)に示される鋸歯型（前記組は計２組である）や図４(c)に示される波型（前記組は計２組である）などが挙げられ、これらの何れも好ましく適用できる。   In the example of FIG. 1, the shape of the undulating surface in the case where there are a total of one set of two portions 7A and 7B inclined in opposite directions with respect to the tube axis direction 4 is shown. This corresponds to a so-called wedge shape having a polygonal line shape shown in FIG. As other undulating surface shapes, for example, sawtooth type shown in FIG. 4 (b) (the set is two sets in total) and wave shape shown in FIG. 4 (c) (the set is two sets in total). And any of these can be preferably applied.

これにより、管軸方向引張力１５に対しては、図１(c)(d)の様に、ロードフランク面１２が抵抗主役ＳＲ１になるに加え、起伏面形状とされた前記接触面７内で、管軸方向４に対し互いに逆向きに傾斜した２つの部分７A,7Bのうち、管軸方向４のピンの先端側に進むほど径が拡大する方向に傾斜した部分７Bが新たな抵抗脇役ＳＲ２になるから、シール部５乃至ショルダ部６への悪影響は小さくて、シール性は保持される。   Thereby, with respect to the tensile force 15 in the tube axial direction, the load flank surface 12 becomes the resistance main role SR1 as shown in FIGS. Of the two portions 7A and 7B inclined in opposite directions with respect to the tube axis direction 4, the portion 7B inclined in a direction in which the diameter increases toward the tip end side of the pin in the tube axis direction 4 is a new resistance supporting role. Since SR2, the adverse effect on the seal part 5 to the shoulder part 6 is small, and the sealing performance is maintained.

又、管軸方向圧縮力１６に対しては、図１(e)(f)の様に、ねじ部においてスタビングフランク面１３が抵抗主役ＳＲ１になるに加え、起伏面形状とされた前記接触面７内で、管軸方向４に対し互いに逆向きに傾斜した２つの部分７A,7Bのうち、管軸方向４のピンの先端側に進むほど径が縮小する方向に傾斜した部分７Aが新たな抵抗脇役ＳＲ２になるから、シール部５乃至ショルダ部６への悪影響は小さくて、シール性は保持される。   Further, as shown in FIGS. 1 (e) and 1 (f), in addition to the stubborn flank surface 13 serving as a resistance main role SR1 in the threaded portion, the contact with the undulating surface shape is applied to the compressive force 16 in the tube axial direction. Among the two portions 7A and 7B inclined in the direction opposite to the tube axis direction 4 in the plane 7, a portion 7A inclined in a direction in which the diameter decreases as it goes to the tip end side of the pin in the tube axis direction 4 is newly added. Therefore, the adverse effect on the seal portion 5 through the shoulder portion 6 is small, and the sealing performance is maintained.

よって、本発明によれば、管軸方向の引張力、圧縮力の何れに対しても、ねじ部が十分に抵抗できて、シール性が保持できる。
上述の実施形態は、ねじ継手のねじが１条ねじである場合について示したが、前記ねじは２条以上の多条ねじであってもよい。多条ねじである場合に、少なくとも何れか１条のねじに対して本発明を適用する実施形態によって、１条ねじの場合と同様の作用効果が得られる事は自明である。従って、斯かる実施形態も本発明に属する。 Therefore, according to the present invention, the threaded portion can sufficiently resist both the tensile force and the compressive force in the tube axis direction, and the sealing performance can be maintained.
Although the above-mentioned embodiment showed about the case where the screw of a threaded joint is a single thread, the above-mentioned thread may be two or more multiple threads. In the case of a multi-threaded screw, it is obvious that the same effect as in the case of a single-threaded screw can be obtained by applying the present invention to at least one thread. Therefore, such an embodiment also belongs to the present invention.

表１に諸元を示すピンとボックスを使用し、図１に示した形態おいて、ピンねじ底とボックスねじ山の接触面７の面形状を表２に示す複数通りの形状とし、前記対向面１０のテーパはねじテーパに合わせた形態として構成した処の鋼管用ねじ継手を供試材として、「ＩＳＯ１３６７９ ＣＡＬ４，８０％圧縮」と呼称されるねじ継手試験規格に則したねじ継手試験を行って、ねじ継手性能を評価した。   In the form shown in FIG. 1, the surface shape of the contact surface 7 of the pin screw bottom and the box thread is a plurality of shapes shown in Table 2 in the form shown in FIG. The threaded joint test according to the threaded joint test standard called “ISO 13679 CAL4, 80% compression” was performed using a threaded joint for steel pipes configured as a thread taper for the 10 taper as a test material. The threaded joint performance was evaluated.

此処で前記各テーパは、対応テーパ面内の１点(点Ｐ)から管軸線に下ろした垂線の足（点Ｑ）までの距離（線分ＰＱの長さ）をrとし、点Ｑから管軸線内のショルダ部相当位置に設けた原点（点Ｏ）までの距離（線分ＯＱの長さ）をｚとして、ｚの増分Δｚ（正値）に対応するｒの変分Δｒ（増分ならば正値、減分ならば負値）から、
テーパ＝（Δｒ/Δｚ）*100（％）、
なる式で算出した。 Here, for each taper, r is the distance (the length of the line segment PQ) from one point (point P) in the corresponding taper surface to the foot of the perpendicular (point Q) down to the pipe axis, and the pipe from the point Q If the distance (the length of the line segment OQ) to the origin (point O) provided at the position corresponding to the shoulder portion in the axis is z, the variation Δr of r corresponding to the increment Δz (positive value) of z (if it is an increment) From positive value, negative value if decrementing)
Taper = (Δr / Δz) * 100 (%),
It was calculated by the following formula.

又、前記接触面７を前記起伏面形状としたものにおいて、前記部分７A,7Bについては、該部分７A,7Bの管軸方向プロフィルが直線状のときは、其の直線を母線とするテーパ面を対応テーパ面とし、曲線状のときは、其の各曲線の長さ範囲の中心点で該曲線に接する接線を母線とするテーパ面を対応テーパ面として、上記同様に算出した。尚、部分７A,7Bが夫々複数ずつ存在する場合、表２には部分７A,7Bの夫々で、複数ずつ存在するテーパのうち絶対値が最大を示すテーパを示した。   Further, in the case where the contact surface 7 has the undulating surface shape, the portions 7A and 7B are tapered surfaces having the straight line as a generating line when the profile in the tube axis direction of the portions 7A and 7B is linear. Is a corresponding tapered surface, and in the case of a curved shape, a taper surface having a tangent line in contact with the curve at the center point of the length range of each curve as a corresponding tapered surface was calculated in the same manner as described above. When there are a plurality of portions 7A and 7B, Table 2 shows a taper having the maximum absolute value among the plurality of portions 7A and 7B.

前記試験の結果を表２に示す。表２より、本発明例では良好な結果が得られた。   The results of the test are shown in Table 2. From Table 2, good results were obtained in the inventive examples.

Figure 0005924152
Figure 0005924152

Figure 0005924152
Figure 0005924152

１ ピン
２ ボックス
３ 非ねじ部
４ 管軸方向
５ シール部
６ ショルダ部
７ ピンねじ底とボックスねじ山の接触面
７A,7B 起伏面形状の接触面内で管軸方向に対し互いに逆向きに傾斜した２つの部分のうちの一方と他方
８ ねじテーパ面
９，９Ａ ねじテーパ面との平行面
１０ ピンねじ山とボックスねじ底の対向面
１１ テーパ雄ねじ部
１２ ロードフランク面
１３ スタビングフランク面
１４，１４Ａ，１４Ｂ 管軸方向に対してねじテーパ面とは逆向きのテーパ面
１５ 管軸方向引張力
１６ 管軸方向圧縮力
２１ テーパ雌ねじ部
３０ 干渉弱化
３１ 塑性変形
ＳＲ 抵抗役
ＳＲ１ 抵抗主役
ＳＲ２ 抵抗脇役 1 Pin 2 Box 3 Non-threaded part 4 Pipe axis direction 5 Sealing part 6 Shoulder part 7 Contact surface 7A, 7B of pin screw bottom and box screw thread One of the two parts and the other 8 Thread taper surface 9, 9A Parallel surface with the thread taper surface 10 Pin thread and opposed surface of the box screw bottom 11 Tapered male thread portion 12 Load flank surface 13 Stubbing flank surface 14, 14A, 14B Tapered surface opposite to the thread taper surface with respect to the tube axis direction 15 Tube axis direction tensile force 16 Tube axis direction compression force 21 Tapered female screw portion 30 Interference weakening 31 Plastic deformation SR Resistance role SR1 Resistance main role SR2 Resistance side role

Claims (1)

テーパ雄ねじ部および該テーパ雄ねじ部より先端側に非ねじ部を有するピンと、該テーパ雄ねじ部および該非ねじ部それぞれに対応するテーパ雌ねじ部および非ねじ部を有するボックスとがねじ結合し、前記ピンの非ねじ部と前記ボックスの非ねじ部とが管軸方向の少なくとも１箇所で円周方向に金属接触して管内流体をシールする構成とされた鋼管用ねじ継手において、ピンねじ底とボックスねじ山の接触面が、ピン側とボックス側の双方とも、管軸方向に対し互いに逆向きに傾斜した２つの部分からなる組を１組以上含む、くさび型、鋸歯型、波型のいずれかの起伏面形状とされたことを特徴とする鋼管用ねじ継手。
A taper male screw portion and a pin having a non-threaded portion on the tip side from the taper male screw portion and a box having a taper female screw portion and a non-thread portion corresponding to each of the taper male screw portion and the non-thread portion are screw-coupled to each other. In a threaded joint for a steel pipe in which a non-threaded portion and a non-threaded portion of the box are in metal contact in a circumferential direction at least at one place in the tube axis direction to seal fluid in the tube, a pin screw bottom and a box thread contact surfaces, both of the pin side and the box side, a set of two portions inclined in opposite directions with respect to the tube axis direction comprises one or more pairs, the wedge-type, saw-tooth, any undulations of corrugated A threaded joint for steel pipes characterized by having a surface shape.
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JP3401859B2 (en) * 1993-09-29 2003-04-28 住友金属工業株式会社 Threaded joints for oil country tubular goods with excellent fatigue properties
DE29721200U1 (en) * 1997-11-29 1998-01-22 Bümach Engineering International B.V., Emmen Sealing thread pairing
FR2863681B1 (en) * 2003-12-11 2006-02-24 Vallourec Mannesmann Oil & Gas FATIGUE-RESISTANT THREADED TUBULAR JOINT
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