JPH10148281A - Steel tube screw joint - Google Patents

Steel tube screw joint

Info

Publication number
JPH10148281A
JPH10148281A JP30916496A JP30916496A JPH10148281A JP H10148281 A JPH10148281 A JP H10148281A JP 30916496 A JP30916496 A JP 30916496A JP 30916496 A JP30916496 A JP 30916496A JP H10148281 A JPH10148281 A JP H10148281A
Authority
JP
Japan
Prior art keywords
seal
pin
coupling
sealing
steel pipe
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
JP30916496A
Other languages
Japanese (ja)
Inventor
Hiroyuki Matsui
博之 松井
Takeo Ueno
雄夫 上野
Takaaki Toyooka
高明 豊岡
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 JP30916496A priority Critical patent/JPH10148281A/en
Publication of JPH10148281A publication Critical patent/JPH10148281A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/001Screw-threaded joints; Forms of screw-threads for such joints with conical threads
    • F16L15/004Screw-threaded joints; Forms of screw-threads for such joints with conical threads with axial sealings having at least one plastically deformable sealing surface

Abstract

PROBLEM TO BE SOLVED: To provide high galling resistance by forming a pin side seal face and a coupling side seal face into a conical face, and setting the seal taper angle defined as the angle between the bus and tube axis larger o the coupling side than on the pin side. SOLUTION: The seal taper angle αc on a coupling 2 side is set larger than the seal taper angle αp on a pin 1 side. When the coupling 2 is coupled with the pin 1 and fastened under the existence of a seal interference quantity 10, a displacement in the radial direction occurs to negate the seal interference quantity 10. Since αc >αp , a pin side seal section 4 having weak rigidity is shrunk in diameter, a coupling side seal section 5 having strong rigidity is slightly expanded in diameter, αp and αc are changed to the approaching side to each other, and a nearly ideal seal state is obtained that a pin side seal face 4S and a coupling side seal face 5S are closely stuck together in the desired range when fastening is completed. The occurrence of galling caused by offset contact can be suppressed.

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、鋼管ネジ継手に関
し、特に、石油、ガス等の採掘に使用され耐リーク性が
要求される鋼管を接続するための鋼管ネジ継手に関する
ものである。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a threaded steel pipe joint, and more particularly to a threaded steel pipe joint for connecting a steel pipe which is used for mining oil and gas and which is required to have leak resistance.
【0002】[0002]
【従来の技術】近年、石油、ガス等の資源の枯渇や掘削
技術の進歩に伴い、油井、ガス井等(以下「資源採掘
井」と総称する)の深さは数千メートルから1万メート
ルにも達しようとしており、このような資源採掘井内に
建て込むために膨大な本数の資源採掘井管が使用され
る。また、そのような膨大な数の資源採掘井管は、管軸
端に設けられた雄ネジ部を有するピンが雄ネジ部を有す
るカップリングによって順次直列に接続されて建て込ま
れる。かかるピンおよびカップリングからなる管継手部
には、管本体および管継手部の重量に起因する軸方向の
引張力、周囲から外周面に及ぼされる地圧力、内部を流
通する流体による内周面への押圧力等、各種の過酷な力
が働き、これらの力は、資源採掘井深度の増大に伴い、
一層過酷なものとなることは言うまでもない。
2. Description of the Related Art In recent years, with the depletion of resources such as oil and gas and the progress of drilling techniques, the depth of oil wells, gas wells, etc. (hereinafter collectively referred to as "resource mining wells") is several thousand meters to 10,000 meters. And a huge number of wells are used to build such wells. Further, such a huge number of resource mining well pipes are built by connecting pins having a male screw portion provided at the pipe shaft end in series by a coupling having a male screw portion. The pipe joint portion including the pin and the coupling has an axial tensile force due to the weight of the pipe body and the pipe joint portion, a ground pressure applied from the periphery to the outer peripheral surface, and an inner peripheral surface due to a fluid flowing inside. Various kinds of severe forces such as the pressing force of the
Needless to say, it will be even more severe.
【0003】そして、このような厳しい条件下で使用で
きるように、前記管継手部に対しては、強大な引張荷重
に耐えうると同時に確実なシール性(耐リーク性)が要
求される。この要求に応じて従来多くの提案がなされて
おり、図5に示すように、耐引張荷重性に関しては、管
継手部(以下、「鋼管ネジ継手」という)における管側
すなわちピン1の雄ネジ部1aおよびカップリング2の雌
ネジ部2aからなるネジ部3のネジ形状やピッチ等を改良
することで所定の継手引張強度を確保し、他方、シール
性に関しては、ピン1の雄ネジ部1aに続く先端部に設け
られたピン側シール部4とカップリング2の最奥部に設
けられたカップリング側シール部5とからなるシール部
(メタルシール部)6によって気密性を確保している。
[0003] In order to be able to use under such severe conditions, the pipe joint section is required to be able to withstand a strong tensile load and at the same time to have a reliable sealing property (leak resistance). Conventionally, many proposals have been made in response to this demand. As shown in FIG. 5, with respect to the tensile load resistance, the male screw of the pin 1 on the pipe side (hereinafter referred to as a "steel pipe screw joint") is used. A predetermined joint tensile strength is secured by improving the thread shape, pitch, and the like of the threaded portion 3 composed of the portion 1a and the female threaded portion 2a of the coupling 2, while the male threaded portion 1a of the pin 1 The airtightness is secured by a seal portion (metal seal portion) 6 including a pin-side seal portion 4 provided at the leading end portion and a coupling-side seal portion 5 provided at the innermost portion of the coupling 2. .
【0004】すなわち、このような従来の鋼管ネジ継手
は、これを指定された範囲の高トルクTで締めつけ、理
想的には図6に示すように、シール部6のピン側シール
部4とカップリング側シール部5との間に所定の接触面
圧Pを発生させることにより耐リーク性が確保できると
されている。
That is, such a conventional steel pipe threaded joint is tightened with a high torque T in a specified range, and ideally, as shown in FIG. It is described that leak resistance can be ensured by generating a predetermined contact surface pressure P between the ring-side seal portion 5 and the ring-side seal portion 5.
【0005】[0005]
【発明が解決しようとする課題】しかしながら、図6に
示したのは理想的な形態であり、実際にはこうはならな
い。というのは、従来のシール部6のピン側シール部4
とカップリング側シール部5は、図7に示すように、そ
れぞれのシール面を頂角の相等しい(但し、寸法公差
内)凸と凹の円錐面状に加工され、さらに、所定の接触
面圧を発生させるために、接触面圧がないものとした仮
想状態で両者の間に所定のシール径食い込み代(シール
干渉量という)10を持たせるように設計される。なお、
円錐面状のシール面の半頂角をシールテーパ角、該シー
ルテーパ角の正接(tan )をシールテーパといい、図7
ではピン側、カップリング側のシールテーパ角をそれぞ
れαP、αC で表しており、上記したようにαP ≒αC
である。
However, what is shown in FIG. 6 is an ideal form, and this is not the case in practice. This is because the pin-side seal portion 4 of the conventional seal portion 6
As shown in FIG. 7, the coupling side seal portion 5 is formed such that each seal surface is formed into a convex and concave conical surface having the same apex angle (within dimensional tolerance), and further, a predetermined contact surface. In order to generate pressure, it is designed so as to have a predetermined seal diameter biting allowance (referred to as seal interference amount) 10 between the two in a virtual state where there is no contact surface pressure. In addition,
The half apex angle of the conical seal surface is called a seal taper angle, and the tangent (tan) of the seal taper angle is called a seal taper.
In the figures, the seal taper angles on the pin side and the coupling side are represented by α P and α C , respectively, and as described above, α P ≒ α C
It is.
【0006】このシール干渉量10の存在下でピン1にカ
ップリング2を係合(雄ネジ部1aと雌ネジ部2aを螺合)
して締め付けていくと、シール干渉量10が打ち消される
ように径方向の変位が生じ、その際、剛性の低いピン1
の方が抑え込まれ、図8に示すように、ピン側シール部
4とカップリング側シール部5とが、メタルシール部6
の全域ではなく局所でのみ強く接触する所謂「片当た
り」が発生する。これは、シール性能を低下させるだけ
でなく、ゴーリングと呼ばれる焼付きの発生原因とな
る。
The coupling 2 is engaged with the pin 1 in the presence of the seal interference amount 10 (the male screw portion 1a and the female screw portion 2a are screwed).
And radial displacement occurs so that the seal interference amount 10 is canceled out.
8, the pin-side seal portion 4 and the coupling-side seal portion 5 are connected to the metal seal portion 6 as shown in FIG.
In other words, a so-called "one-sided contact" occurs in which a strong contact is made only in a local area, not in the entire area. This not only lowers the sealing performance but also causes seizure called galling.
【0007】この片当たりをなくすために、本出願人は
特開平8-93972 号公報において、カップリング側シール
面をピン側シール面に接するようにその曲率中心および
半径を定めた凸曲面形状とすることを提案したが、その
後の検討により、この対策のみではゴーリング発生を完
全には抑止できないことがわかった。そこで、本発明
は、上記従来技術の問題を解決し、従来よりも一段と高
い耐リーク性および耐ゴーリング性を有する鋼管ネジ継
手を提供することを目的とする。
In order to eliminate this one-sided contact, the applicant of the present invention disclosed in Japanese Patent Application Laid-Open No. 8-93972 a convex curved surface shape having a center of curvature and a radius determined so that the coupling-side sealing surface is in contact with the pin-side sealing surface. However, subsequent studies have shown that this measure alone cannot completely suppress the occurrence of galling. Then, an object of the present invention is to solve the above-mentioned problem of the prior art, and to provide a steel pipe threaded joint having much higher leak resistance and galling resistance than the conventional art.
【0008】[0008]
【課題を解決するための手段】本発明は、鋼管端部に設
けられ雄ネジ部および該雄ネジ部から管端側に延在する
ピン側シール部とを有するピンと、前記雄ネジ部に螺合
可能な雌ネジ部および前記ピン側シール部に対応するカ
ップリング側シール部とを有するカップリングとからな
り、該カップリングを前記ピンに係合させ前記雄ネジ部
と前記雌ネジ部とを螺合させて締め付けた際に、前記ピ
ン側シール部の外径面であるピン側シール面と前記カッ
プリング側シール部の内径面であるカップリング側シー
ル面とが密着してメタルシール部が形成される鋼管ネジ
継手において、ピン側シール面とカップリング側シール
面とが円錐面で形成されその母線と管軸とのなす角とし
て定義されるシールテーパ角に関しカップリング側をピ
ン側よりも大きく設けてなることを特徴とする鋼管ネジ
継手である。
According to the present invention, there is provided a pin provided at an end of a steel pipe and having a male screw portion and a pin-side seal portion extending from the male screw portion toward the pipe end, and a screw provided on the male screw portion. And a coupling having a coupling side seal portion corresponding to the female screw portion and the pin side seal portion.The coupling is engaged with the pin, and the male screw portion and the female screw portion are connected to each other. When screwed together and tightened, the pin-side sealing surface, which is the outer diameter surface of the pin-side sealing portion, and the coupling-side sealing surface, which is the inner diameter surface of the coupling-side sealing portion, are brought into close contact with each other, so that the metal sealing portion is formed. In the formed steel pipe threaded joint, the coupling side is closer to the pin side with respect to the seal taper angle defined as the angle formed between the pin-side sealing surface and the coupling-side sealing surface with a conical surface and the bus line and the tube axis. big Only with a steel threaded joint characterized by comprising.
【0009】本発明においては、カップリング側シール
面のプロフィルを、直線状に代えてピン側に凸の円弧状
とすることがさらに好ましい。
In the present invention, it is more preferable that the profile of the coupling-side sealing surface is formed in an arc shape convex to the pin side instead of a linear shape.
【0010】[0010]
【発明の実施の形態】図1は、本発明の鋼管ネジ継手の
締め付け時の要部縦断面図であり、1はピン、1aは雄ネ
ジ部、2はカップリング、2aは雌ネジ部、4はピン側シ
ール部、4Sはピン側シール面、5はカップリング側シー
ル部、5Sはカップリング側シール部、6はメタルシール
部(シール部)である。
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a longitudinal sectional view of a main part of a steel pipe threaded joint according to the present invention when tightened, wherein 1 is a pin, 1a is a male thread, 2 is a coupling, 2a is a female thread, Reference numeral 4 denotes a pin side seal portion, 4S denotes a pin side seal surface, 5 denotes a coupling side seal portion, 5S denotes a coupling side seal portion, and 6 denotes a metal seal portion (seal portion).
【0011】同図に示すように、本発明の鋼管ネジ継手
は、鋼管端部に設けられ雄ネジ部1aおよび該雄ネジ部1a
から管端側に延在するピン側シール部4とを有するピン
1と、前記雄ネジ部1aに螺合可能な雌ネジ部2aおよび前
記ピン側シール部4に対応するカップリング側シール部
5とを有するカップリング2とからなるという点、なら
びに、該カップリング2を前記ピン1に係合させ前記雄
ネジ部1aと前記雌ネジ部2aとを螺合させて締め付けた際
に、前記ピン側シール部4の外径面であるピン側シール
面4Sと前記カップリング側シール部5の内径面であるカ
ップリング側シール面5Sとが密着してシール部6が形成
される点については、従来と同様である。
As shown in FIG. 1, a threaded steel pipe joint according to the present invention is provided at an end of a steel pipe with a male thread 1a and a male thread 1a.
A pin 1 having a pin-side seal portion 4 extending from the end to the pipe end, a female screw portion 2a screwable to the male screw portion 1a, and a coupling-side seal portion 5 corresponding to the pin-side seal portion 4. And when the coupling 2 is engaged with the pin 1 and the male screw portion 1a and the female screw portion 2a are screwed together and tightened, Regarding the point that the pin-side sealing surface 4S, which is the outer diameter surface of the side sealing portion 4, and the coupling-side sealing surface 5S, which is the inner diameter surface of the coupling-side sealing portion 5, come into close contact with each other to form the sealing portion 6. It is the same as the conventional one.
【0012】しかしながら、本発明の鋼管ネジ継手は、
接触面圧がないものとした仮想状態での係合関係を表現
した図2に示すように、ピン側シール面4Sとカップリン
グ側シール面5Sとが円錐面で形成されその母線と管軸と
のなす角として定義されるシールテーパ角に関し、カッ
プリング2側のシールテーパ角(αC )をピン1側のシ
ールテーパ角(αP )よりも大きく設けてなること、す
なわちαC >αP となるように設計されてなることを特
徴とする。これらのシールテーパ角αC 、αPがそれぞ
れ加工寸法公差内で変動した場合にもかかる大小関係
(αC >αP )が維持されるように設計すべきことはい
うまでもない。
However, the steel pipe threaded joint of the present invention
As shown in FIG. 2, which represents an engagement relationship in a virtual state where there is no contact surface pressure, the pin-side sealing surface 4S and the coupling-side sealing surface 5S are formed as conical surfaces, and the bus and tube axis thereof are The seal taper angle (α C ) on the coupling 2 side is set to be larger than the seal taper angle (α P ) on the pin 1 side, that is, α C > α P. It is characterized by being designed to be. Needless to say, the design should be such that the magnitude relationship (α C > α P ) is maintained even when these seal taper angles α C and α P vary within the processing dimension tolerance.
【0013】ここでも従来同様、シール干渉量10が設定
され、このシール干渉量10の存在下でピン1にカップリ
ング2を係合(雄ネジ部1aと雌ネジ部2aを螺合)して締
め付けていくと、シール干渉量10が打ち消されるように
径方向の変位が生じるが、本発明においては、αC >α
P としているので、剛性の弱いピン側シール部4が縮径
し、同時に剛性の強いカップリング側シール部5がわず
かながら拡径するにつれて、αP とαC とは互いに近づ
く側に変化し、締め付け完了時には、図3に示すよう
に、ピン側シール面4Sとカップリング側シール面5Sとが
所望の範囲で密着するという理想に近いシール状態が得
られる。よって図8に示したような片当たりによるゴー
リングの発生を抑制できる。
Here, as in the prior art, a seal interference amount 10 is set, and in the presence of the seal interference amount 10, the coupling 2 is engaged with the pin 1 (the male screw portion 1a and the female screw portion 2a are screwed). When tightening, a radial displacement occurs such that the seal interference amount 10 is canceled, but in the present invention, α C > α
Since is P, and a weak pin side sealing portion 4 is reduced in diameter rigidity, at the same time as the diameter increases while the stiffness strong coupling sealing section 5 slightly, the alpha P and alpha C were changed to the side close to each other, Upon completion of the tightening, as shown in FIG. 3, a near-ideal sealing state in which the pin-side sealing surface 4S and the coupling-side sealing surface 5S adhere to each other in a desired range is obtained. Therefore, it is possible to suppress the occurrence of galling due to one-side contact as shown in FIG.
【0014】ところで、シール干渉量10は、耐リーク性
を確保するためのシール面圧を発生させるために必要な
弾性変形量に対応する下限値を有し、これに歩留を考慮
した公差を上乗せすることにより、シール干渉量の製造
公差範囲が決められる。そして、この製造公差範囲の中
央値がシール干渉量の代表値(ノミナル値)として採用
されその値に基づいてシールテーパが定められる。従っ
て、ノミナル値で適合するシールテーパをもつようにピ
ンおよびカップリングを製作しても、実際は製作のバラ
ツキによりシール干渉量の上限と下限に相当するものが
係合することもあって、その場合には片当たりが生じて
しまうことが懸念される。そこで、前述のようにαC
αP とした上で、前記特開平8-93972 号公報で提案した
ように、カップリング側シール面5Sのプロフィルを、直
線状(円錐面の母線7)に代えてピン1側に凸の(例え
ば凸部区間8内に有向線分9で示す曲率半径Rを有す
る)円弧状とすることがさらに好ましい。これにより係
合時に前記バラツキが吸収され、図4に2点鎖線で示す
通り、シール干渉量の変化によりピン側の変形量(縮径
量)が変化したとしてもその変化を吸収でき、シール面
同士の密着性が低下することなく理想に近いシール状態
を確保できる。
Incidentally, the seal interference amount 10 has a lower limit corresponding to the amount of elastic deformation required to generate the seal surface pressure for ensuring leak resistance, and the tolerance taking into account the yield is set to this. By adding, the manufacturing tolerance range of the seal interference amount is determined. The central value of the manufacturing tolerance range is adopted as a representative value (nominal value) of the seal interference amount, and the seal taper is determined based on the value. Therefore, even if the pins and couplings are manufactured so as to have a seal taper that is compatible with the nominal value, actually, the ones corresponding to the upper and lower limits of the seal interference amount may be engaged due to manufacturing variations. There is a concern that a singularity may occur. Therefore, as described above, α C >
on which the alpha P, as proposed in the Japanese Patent Laid-Open 8-93972 discloses a profile of the coupling-side sealing surface 5S, linear convex pin 1 side instead of the (bus line 7 of the conical surface) ( For example, it is more preferable to have an arc shape (having a radius of curvature R indicated by a directed line segment 9 in the convex section 8). As a result, the variation can be absorbed at the time of engagement, and as shown by the two-dot chain line in FIG. An ideal seal state can be secured without lowering the adhesion between the two.
【0015】[0015]
【実施例】API規格でL80、外径88.9mmφ、肉厚6.
452mm の仕様の油井管用の鋼管ネジ継手を、ピン側につ
いてはシール面のシールテーパ(tan αP )を1/16に、
長さを6.5mm に、シール径(カップリング側で設定する
シール長の定義区間に設計上対応する部位の中央位置に
おける外径)を84.02mm に設計・製作し、カップリング
側についてはシール面のシールテーパ(tan αC )を本
発明の規定(αC >αP )に従い1/12に、シール長を4.
1mm に、該シール長の定義区間(図4の凸部区間8に該
当)におけるプロフィルを直線状に代えて本発明のより
好ましい形態であるピン側に凸の円弧状(曲率半径R=
50.0mm)とし該定義区間の中央での内径であるシール径
を83.69mm に設計・製作して実施例とした。なお、シー
ル干渉量は両者のシール径の差0.33mmである。
[Example] API standard L80, outer diameter 88.9mmφ, wall thickness 6.
Threaded pipe thread fittings for oil country tubular goods of 452mm specification, the seal taper (tan α P ) of the sealing surface on the pin side to 1/16,
Design and manufacture the length to 6.5mm and the seal diameter (outer diameter at the center position of the part corresponding to the design section of the seal length set on the coupling side) to 84.02mm. The seal taper (tan α C ) is reduced to 1/12 according to the provisions of the present invention (α C > α P ), and the seal length is set to 4.
At 1 mm, the profile in the defined section of the seal length (corresponding to the convex section 8 in FIG. 4) is changed to a linear shape, and a pin-shaped convex arc (curvature radius R =
50.0 mm), and the seal diameter, which is the inner diameter at the center of the defined section, was designed and manufactured to be 83.69 mm, and an example was made. In addition, the seal interference amount is a difference of 0.33 mm between the two seal diameters.
【0016】一方、実施例と同一仕様の油井管用でシー
ルテーパがピン側、カップリング側とも同じ値(1/1
6)、かつ、ピン、カップリング両者ともプロフィルが
直線状である他は実施例と同じ寸法諸元の鋼管ネジ継手
を設計・製作し従来例とした。これら実施例、従来例の
鋼管ネジ継手を450kgf・m のトルクで締め付けたとこ
ろ、従来例では、軸方向引張荷重65.8tonf(軸方向応力
39.4kgf/mm2 で70%SMYS(規格最小降伏応力)に相
当)と内圧490kgf/cm2(60%SMYSに相当)の組み合
わせ負荷でリークしたのに対し、実施例では、軸方向引
張荷重89.2tonf(軸方向応力53.4kgf/mm2 で95%SMY
Sに相当)、内圧780kgf/cm2(95%SMYSに相当)と
従来例よりも高い組み合わせ負荷においてもリークが発
生しないという優れた耐リーク性が得られた。
On the other hand, for oil country tubular goods having the same specifications as those of the embodiment, the seal taper is the same on both the pin side and the coupling side (1/1).
6) In addition, a steel pipe threaded joint having the same dimensions as the embodiment was designed and manufactured except that the profile of both the pin and the coupling was linear, and the conventional example was used. When the steel pipe threaded joints of these examples and the conventional example were tightened with a torque of 450 kgf · m, in the conventional example, the axial tensile load was 65.8 tonf (axial stress).
While 39.4 kgf / mm 2 leaked under the combined load of 70% SMYS (corresponding to the standard minimum yield stress) and internal pressure of 490 kgf / cm 2 (corresponding to 60% SMYS), in the embodiment, the axial tensile load was 89.2%. tonf (axial stress 53.4kgf / mm 2 at 95% SMY
S) and an internal pressure of 780 kgf / cm 2 (corresponding to 95% SMYS), and excellent leak resistance was obtained in which no leakage occurred even under a combination load higher than the conventional example.
【0017】また、ピンのシール径を84.09mm 、カップ
リングのシール径を83.52mm とシール干渉量を大きく
(0.57mm)し、締め付けトルク580kgf・m でゴーリング
試験を行ったところ、従来例では4回のMake/Break(締
め付け/除荷)で片当たりによるゴーリングが発生した
のに対し、実施例では10回のMake/Breakでもゴーリング
が発生しなかった。
A galling test was conducted with a pin seal diameter of 84.09 mm, a coupling seal diameter of 83.52 mm, a large seal interference (0.57 mm), and a tightening torque of 580 kgf · m. While make / break (tightening / unloading) caused galling due to one-sided hit, in the example, no make / break occurred even with 10 make / breaks.
【0018】[0018]
【発明の効果】以上のように本発明によれば、従来より
も一段と高い耐リーク性および耐ゴーリング性を有する
鋼管ネジ継手が得られるという格段の効果を奏する。
As described above, according to the present invention, a remarkable effect that a steel pipe threaded joint having much higher leak resistance and galling resistance than conventional ones can be obtained.
【図面の簡単な説明】[Brief description of the drawings]
【図1】本発明の鋼管ネジ継手の締め付け時の要部縦断
面図である。
FIG. 1 is a longitudinal sectional view of a main part when a steel pipe threaded joint according to the present invention is tightened.
【図2】接触面圧がないものとした仮想状態における本
発明の鋼管ネジ継手のピン側シール部とカップリング側
シール部との係合関係を示す図である。
FIG. 2 is a view showing an engagement relationship between a pin side seal portion and a coupling side seal portion of the steel pipe threaded joint of the present invention in a virtual state where there is no contact surface pressure.
【図3】本発明の鋼管ネジ継手のシール状態の説明図で
ある。
FIG. 3 is an explanatory diagram of a sealed state of the threaded steel pipe joint of the present invention.
【図4】本発明の鋼管ネジ継手のさらに好ましい形態の
説明図である。
FIG. 4 is an explanatory view of a further preferred embodiment of the steel pipe threaded joint of the present invention.
【図5】メタルシール部を有する鋼管ネジ継手の説明図
である。
FIG. 5 is an explanatory diagram of a steel pipe threaded joint having a metal seal portion.
【図6】メタルシール部の理想的なシール形態の説明図
である。
FIG. 6 is an explanatory diagram of an ideal sealing form of a metal seal portion.
【図7】接触面圧がないものとした仮想状態における従
来の鋼管ネジ継手のピン側シール部とカップリング側シ
ール部との係合関係を示す図である。
FIG. 7 is a diagram showing an engagement relationship between a pin-side seal portion and a coupling-side seal portion of a conventional steel pipe threaded joint in a virtual state where there is no contact surface pressure.
【図8】片当たりの説明図である。FIG. 8 is an explanatory diagram of one-side contact.
【符号の説明】[Explanation of symbols]
1 ピン 1a 雄ネジ部 2 カップリング 2a 雌ネジ部 3 ネジ部 4 ピン側シール部 4S ピン側シール面 5 カップリング側シール部 5S カップリング側シール面 6 シール部(メタルシール部) 7 円錐面の母線 8 凸部区間 9 曲率半径を表す有向線分 10 シール径食い込み代(シール干渉量) 1 Pin 1a Male screw part 2 Coupling 2a Female screw part 3 Screw part 4 Pin side seal part 4S Pin side seal surface 5 Coupling side seal part 5S Coupling side seal surface 6 Seal part (metal seal part) 7 Conical surface Bus 8 Convex section 9 Directed line segment representing radius of curvature 10 Seal diameter penetration (seal interference amount)

Claims (2)

    【特許請求の範囲】[Claims]
  1. 【請求項1】 鋼管端部に設けられ雄ネジ部および該雄
    ネジ部から管端側に延在するピン側シール部とを有する
    ピンと、前記雄ネジ部に螺合可能な雌ネジ部および前記
    ピン側シール部に対応するカップリング側シール部とを
    有するカップリングとからなり、該カップリングを前記
    ピンに係合させ前記雄ネジ部と前記雌ネジ部とを螺合さ
    せて締め付けた際に、前記ピン側シール部の外径面であ
    るピン側シール面と前記カップリング側シール部の内径
    面であるカップリング側シール面とが密着してメタルシ
    ール部が形成される鋼管ネジ継手において、ピン側シー
    ル面とカップリング側シール面とが円錐面で形成されそ
    の母線と管軸とのなす角として定義されるシールテーパ
    角に関しカップリング側をピン側よりも大きく設けてな
    ることを特徴とする鋼管ネジ継手。
    1. A pin provided at an end of a steel pipe and having a male screw part and a pin-side seal part extending from the male screw part toward the pipe end, a female screw part capable of being screwed to the male screw part, and A coupling having a coupling-side seal portion corresponding to the pin-side seal portion, and when the coupling is engaged with the pin and the male screw portion and the female screw portion are screwed together and tightened. A steel pipe threaded joint in which a metal seal portion is formed by tightly contacting a pin side seal surface which is an outer diameter surface of the pin side seal portion and a coupling side seal surface which is an inner diameter surface of the coupling side seal portion, The pin-side sealing surface and the coupling-side sealing surface are formed as conical surfaces, and the coupling side is provided to be larger than the pin side with respect to a seal taper angle defined as an angle between the generating line and the tube axis. Do Steel pipe screw joint.
  2. 【請求項2】 カップリング側シール面のプロフィル
    を、直線状に代えてピン側に凸の円弧状とした請求項1
    記載の鋼管ネジ継手。
    2. The profile of the coupling-side sealing surface is formed in an arc shape convex to the pin side instead of being straight.
    The described steel pipe screw joint.
JP30916496A 1996-11-20 1996-11-20 Steel tube screw joint Pending JPH10148281A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP30916496A JPH10148281A (en) 1996-11-20 1996-11-20 Steel tube screw joint

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP30916496A JPH10148281A (en) 1996-11-20 1996-11-20 Steel tube screw joint

Publications (1)

Publication Number Publication Date
JPH10148281A true JPH10148281A (en) 1998-06-02

Family

ID=17989708

Family Applications (1)

Application Number Title Priority Date Filing Date
JP30916496A Pending JPH10148281A (en) 1996-11-20 1996-11-20 Steel tube screw joint

Country Status (1)

Country Link
JP (1) JPH10148281A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001094831A1 (en) * 2000-06-07 2001-12-13 Sumitomo Metal Industries, Ltd. Taper threaded joint
JP2005308201A (en) * 2004-03-26 2005-11-04 Jfe Steel Kk Joint for oil well steel pipe
JP2008089568A (en) * 2006-09-07 2008-04-17 Sumitomo Metal Ind Ltd Method for evaluating fastening state of threaded joint for pipe and method for fastening threaded joint for pipe using this method
GB2479259A (en) * 2010-03-29 2011-10-05 High Sealed And Coupled Hsc Fzco A screw-threaded joint for pipes
WO2014045973A1 (en) * 2012-09-21 2014-03-27 新日鐵住金株式会社 Threaded joint for steel pipe
US8973953B2 (en) 2010-11-17 2015-03-10 Hsc High Sealed & Coupled Pte. Ltd. Seal between pipe sections

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001094831A1 (en) * 2000-06-07 2001-12-13 Sumitomo Metal Industries, Ltd. Taper threaded joint
JP2005308201A (en) * 2004-03-26 2005-11-04 Jfe Steel Kk Joint for oil well steel pipe
JP4691904B2 (en) * 2004-03-26 2011-06-01 Jfeスチール株式会社 Oil well steel pipe fittings
JP2008089568A (en) * 2006-09-07 2008-04-17 Sumitomo Metal Ind Ltd Method for evaluating fastening state of threaded joint for pipe and method for fastening threaded joint for pipe using this method
GB2479259A (en) * 2010-03-29 2011-10-05 High Sealed And Coupled Hsc Fzco A screw-threaded joint for pipes
GB2479259B (en) * 2010-03-29 2012-05-16 High Sealed And Coupled Hsc Fzco An improved seal between pipes
US8840151B2 (en) 2010-03-29 2014-09-23 Hsc High Sealed & Coupled Pte. Ltd. Seal between pipe sections
US8973953B2 (en) 2010-11-17 2015-03-10 Hsc High Sealed & Coupled Pte. Ltd. Seal between pipe sections
WO2014045973A1 (en) * 2012-09-21 2014-03-27 新日鐵住金株式会社 Threaded joint for steel pipe
CN104583662A (en) * 2012-09-21 2015-04-29 新日铁住金株式会社 Threaded joint for steel pipe
AU2013319233B2 (en) * 2012-09-21 2016-12-01 Nippon Steel Corporation Screw Joint for Steel Pipe
EA030268B1 (en) * 2012-09-21 2018-07-31 Ниппон Стил Энд Сумитомо Метал Корпорейшн Screw joint for steel pipe
US10077612B2 (en) 2012-09-21 2018-09-18 Nippon Steel & Sumitomo Metal Corporation Screw joint for steel pipe

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