WO2012003645A1 - 石油天然气工业用管螺纹接头 - Google Patents

石油天然气工业用管螺纹接头 Download PDF

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Publication number
WO2012003645A1
WO2012003645A1 PCT/CN2010/075334 CN2010075334W WO2012003645A1 WO 2012003645 A1 WO2012003645 A1 WO 2012003645A1 CN 2010075334 W CN2010075334 W CN 2010075334W WO 2012003645 A1 WO2012003645 A1 WO 2012003645A1
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WO
WIPO (PCT)
Prior art keywords
sealing
tapered
cylindrical
thread
transition
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Application number
PCT/CN2010/075334
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English (en)
French (fr)
Inventor
李淑琴
张宝
Original Assignee
天津天钢石油专用管制造有限公司
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Publication date
Application filed by 天津天钢石油专用管制造有限公司 filed Critical 天津天钢石油专用管制造有限公司
Publication of WO2012003645A1 publication Critical patent/WO2012003645A1/zh
Priority to US13/734,977 priority Critical patent/US9057464B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/06—Screw-threaded joints; Forms of screw-threads for such joints characterised by the shape of the screw-thread
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
    • F16L15/004—Screw-threaded joints; Forms of screw-threads for such joints with conical threads with axial sealings having at least one plastically deformable sealing surface

Definitions

  • the invention relates to a pipe thread joint for oil and gas industry.
  • Pipe threaded joints for the oil and gas industry generally consist of a threaded, sealed and torque shoulder. Over the years, the thread and seal of the joint have been continuously improved to achieve strength and hermetic design requirements.
  • the AP I trapezoidal thread is completely used.
  • thread slippage occurs, so it is extremely important to choose the appropriate thread side angle and the tooth height to pitch ratio.
  • the coupling type thread has two types of single seal and multiple seal.
  • the seal design disclosed in China mainly adopts single seal structure.
  • the number of seal structures has gradually increased, and the United States adopts multiple seal structures.
  • the use of a single seal must increase the seal interference, increase the seal length, or both, which requires extremely high processing precision and is prone to sticking.
  • the use of a multi-seal structure can reduce the drawbacks of a single seal, but the existing multi-seal structure does not isolate the two seal faces, the effect is the same as a single seal, and the reliability of the seal is insufficient.
  • the multi-sealing with a double torque shoulder separates the sealing surface, but the processing is difficult and the yield is low.
  • the invention is to overcome the deficiencies in the prior art, and to provide a pipe joint for oil and gas industry with high connection performance, small processing difficulty and good sealing stability.
  • a pipe thread joint for oil and gas industry which is formed by connecting a pipe body with an external thread at the end and a coupling with an internal thread at the end, wherein the external thread of the pipe body and the inside of the coupling are
  • the thread is a trapezoidal thread with a mutual fit, and the ratio of the tooth height to the pitch is 0. 25 ⁇ 0. 35 , the bearing surface angle is -15 ⁇ 3 °, and the guiding surface angle is 10 ⁇ 50.
  • the sealing part between the pipe body and the coupling on the side of the thread is sequentially set a first cylindrical transition zone, a cylindrical sealing zone, a second cylindrical transition zone, a conical sealing zone, and a tapered transition zone, wherein the tapered surfaces of the tapered sealing zone have the same taper; the tapered transition zone The end is a torque shoulder.
  • the sealing portion on the side of the external thread on the pipe body is a first outer cylindrical transition surface, an outer cylindrical sealing surface, a second outer cylindrical transition surface, an outer tapered sealing surface, and an outer tapered transition surface, respectively.
  • the tapered transition surface is connected to the outer torque shoulder surface
  • the sealing portion on the side of the internal thread on the coupling is a first inner cylindrical surface, a second inner cylindrical surface and an inner tapered surface, and the inner tapered surface Connecting with the inner torque shoulder surface, a gap is left between the first outer cylindrical transition surface and the first inner cylindrical surface to form the first cylindrical transition region
  • the outer cylindrical sealing surface Forming the cylindrical sealing region between the second inner cylindrical surfaces by an interference fit, leaving a gap between the second outer cylindrical transition surface and the second inner cylindrical surface to form the second transition a tapered sealing zone formed by an interference fit between the outer tapered sealing surface and the inner tapered surface, wherein a gap is formed between the outer tapered transition surface and the inner tapered surface In the tapered transition zone, the outer tapered sealing surface has the same tape
  • the cylindrical sealing zone is a high interference, small sealing length structure
  • the tapered sealing zone is a low interference, large sealing length structure.
  • the taper of the threaded portion is 1 : 20 ⁇ 1 : 10 in diameter.
  • the outer tapered transition surface has a taper angle of 30 to 60. .
  • the gap between the tooth tip and the bottom of the tooth is 0. 05 ⁇ 0. 2mm.
  • the taper angle of the outer tapered sealing surface and the inner tapered surface is 10-20. .
  • the pipe thread joint of the present invention improves the strength of the threaded connection by adopting the improved API trapezoidal thread, thereby avoiding the phenomenon of thread slippage.
  • the pipe thread joint of the invention adopts a cylindrical sealing surface and a tapered sealing structure, and effectively isolates the two sealing surfaces through the cylinder transition zone, thereby ensuring the reliability of the sealing.
  • the discontinuous surface of the pipe thread joint of the invention adopts a circular arc transition, which reduces the stress concentration, avoids causing the brittle material to break and causes fatigue cracking of the object, and improves the joint strength.
  • the pipe thread joint of the invention adopts a cylindrical sealing surface and a tapered sealing structure, which has low requirements on processing precision, reduces processing difficulty, and is convenient for large-scale implementation, which is beneficial to improving production efficiency, reducing production cost and improving yield. .
  • the threaded joint of the present invention has a certain gap in addition to the sealing portion, and the thread sticking tendency can be reduced.
  • FIG. 1 is a schematic overall view of a pipe joint of the oil and gas industry of the present invention
  • FIG. 2 is a partially enlarged schematic view of the sealing portion of the present invention
  • Figure 3 is a schematic view showing the internal thread structure of the coupling portion
  • Figure 4 is a schematic view showing the external thread structure of the pipe body portion
  • Figure 5 is a schematic view of the shape of the thread
  • Figure 6 is a schematic view of the thread engagement.
  • FIG. 1 to 6 A schematic view of the pipe joint of the oil and gas industry of the present invention is shown in Figs. 1 to 6, and is formed by connecting a pipe body 2 having an external thread 15 at the end and a coupling 1 having an internal thread 10 at the end.
  • the external thread 15 on the tubular body 2 and the internal thread 10 on the coupling 1 are mutually trapezoidal trapezoidal threads, and the ratio of the tooth height to the pitch is 0. 25 ⁇ 0. 35 , and the bearing surface angle t 2 is -15 ⁇ 3 .
  • the guide surface angle tl is 10 ⁇ 50. , to ensure different specifications and different steel grade thread connection performance.
  • the sealing portion between the threaded side pipe body and the coupling is sequentially provided with a first cylindrical transition zone 4, a cylindrical sealing zone 5, a second cylindrical transition zone 6, a conical sealing zone 7, and a tapered transition zone 8, The tapered surfaces of the tapered sealing regions have the same taper.
  • the end of the tapered transition zone 8 is a torque shoulder 9.
  • the first cylindrical transition zone 4 effects the transition of the external thread 15 of the tubular body and the internal thread 10 of the coupling to the cylindrical sealing zone 5 to avoid damage to the threaded surface by the engagement.
  • the second cylindrical transition zone 6 achieves effective isolation of the cylindrical seal zone 5 from the tapered seal zone 7.
  • the tapered transition zone 8 achieves a smooth transition between the tubular body and the coupling to ensure joint quality.
  • Torque shoulder 9 is used for the positioning of the threaded connection and And absorb too high the buckle torque. All excess surfaces absorb excess thread grease and reduce the effect of thread grease on the metal seal.
  • the sealing portion of the side of the external thread 15 of the pipe body 2 is a first outer cylindrical transition surface 16 and an outer cylindrical sealing surface 17,
  • the second outer cylindrical transition surface 18, the outer tapered sealing surface 19, and the outer tapered transition surface 20 are connected to the outer torque shoulder surface 21.
  • the sealing portion on the side of the internal thread 10 of the coupling 1 is a first inner cylindrical surface 11 and a second inner cylindrical surface 12 inner tapered surface 13 , and the inner tapered surface 13 and the inner torque shoulder surface 14 connection.
  • a gap is left between the first outer cylindrical transition surface 16 and the first inner cylindrical surface 11 to form the first cylindrical transition region 4.
  • the cylindrical sealing surface 5 is formed between the outer cylindrical sealing surface 17 and the second inner cylindrical surface 12 by an interference fit to achieve metal-to-metal sealing.
  • a gap is left between the second outer cylindrical transition surface 18 and the second inner cylindrical surface 12 to form the second transition zone 6.
  • the tapered sealing portion 7 is formed between the outer tapered sealing surface 19 and the inner tapered surface 13 by an interference fit to achieve metal-to-metal sealing.
  • a gap is left between the outer tapered transition surface 20 and the inner tapered surface 13 to form the tapered transition zone 8, the outer tapered sealing surface 19 having the same taper angle as the inner tapered surface 13
  • the angle between the outer torque shoulder surface 21 and the vertical plane of the pipe body axis is ps l
  • the angle between the inner torque shoulder surface 14 and the vertical plane of the pipe body axis is bs l
  • the cylindrical sealing zone has a high interference and small sealing length structure to avoid a decrease in sealing performance due to axial load.
  • the radial interference of the cylindrical sealing zone 12 is generally 0.3 to 1.5.
  • the sealing length b2 of the cylindrical sealing zone is greater than half of the pitch.
  • the tapered sealing zone has a low interference and a large sealing length structure, and the tapered sealing can reduce the bonding tendency of the sealing surface.
  • the radial interference I I of the conical sealing zone is generally 0.1 to 0.5 mm, and the sealing length of the conical sealing zone is 2 to 10 mm.
  • the taper angle ps2 of the outer tapered transition surface 20 is 30 ⁇ 60
  • Example 1 88.9 x 6.45mm tubing
  • the pitch is 4 ⁇ 2 ⁇
  • the external thread height is 1 ⁇
  • the internal thread height is 1.1 ⁇
  • the internal thread height to pitch ratio is 0.26
  • Bearing surface angle U - 10.
  • the guide surface angle tl 30.
  • the taper portion has a taper of 1/16 in the diameter direction.
  • the pitch is 5.08mm
  • the external thread height is 1.47mm
  • the internal thread height is 1.57mm
  • the internal thread height to pitch ratio is 0.31
  • the internal thread and the external thread are different by 0.1 ⁇ .
  • the taper portion has a taper diameter of 1/16.
  • the pipe thread joint of the invention is suitable for oil pipes and casings for oil and gas industry, and can be used for high pressure oil wells and high pressure gas wells. Because the invention has reliable performance and low processing difficulty, it can be used for all oil and gas wells with high sealing requirements, especially high pressure oil and gas wells. In addition, it is more effective for high steel grade and large wall thickness casing, and has broad application prospects.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
  • Earth Drilling (AREA)

Abstract

公开了一种用于石油天然气工业的管螺纹接头。该接头包括一个管体（2）和一个接箍（1）。管体（2）上设置外螺纹，接箍（1）上设置内螺纹。内、外螺纹为偏梯形螺纹。齿高与节距的比是0.25-0.35，承载角是-15~3°，导向角是10~50°。螺纹啮合后齿顶和齿底之间存在间隙。管体（2）与接箍（1）之间的密封部分依次设置有第一柱面过渡区（4）、柱形密封区（5）、第二柱面过渡区（6）、锥形密封区（7）、锥面过渡区（8），锥面过渡区（8）的端部为扭矩台肩（9）。本发明采用改进的API偏梯形螺纹，提高了螺纹连接强度；采用柱形密封区（5）和锥形密封区（7）形成复合密封结构，并用第二柱面过渡区（6）将两个密封区（5、7）有效隔离，保证密封的可靠性。本发明具有连接性能高、加工容易、密封可靠、生产效率和成品率高、成本低的优点。

Description

说 明 书 石油天然气工业用管螺纹接头 技术领域
本发明涉及一种石油天然气工业用管螺紋接头。
背景技术
石油天然气工业用管螺紋接头一般由螺纹、 密封以及扭矩台肩三 部分的结构构成。 多年来， 人们一直通过不断的改进接头的螺纹、 密 封及扭矩台肩， 以达到强度和气密封设计要求。
在螺紋设计方面， 完全采用 AP I 偏梯形螺纹， 对于大直径厚壁高 钢级套管， 会出现螺纹滑脱现象， 因此选择合适的螺纹侧面角和齿高 与螺距比极为重要。
在密封设计方面， 接箍型螺纹有单密封和多密封两种， 国内公布 的密封设计主要采用单密封结构， 近年来多密封结构逐渐增多， 美国 多采用多密封结构。 为了保证良好的密封性能， 采用单密封必须增加 密封过盈量、 增加密封长度或两者同时增加， 这就要求极高的加工精 度， 而且易发生粘扣现象。 采用多密封结构可以减少单密封的弊端， 但现有多密封结构未将两个密封面进行隔离， 其效果与单密封相同， 密封的可靠性不足。 采用双扭矩台肩的多密封虽然分开了密封面， 但 加工难度大， 成品率低。
发明内容
本发明是为了克服现有技术中的不足之处， 提供一种连接性能高， 加工难度小， 密封稳定性好的石油天然气工业用管螺紋接头。
本发明通过下述技术方案实现：
一种石油天然气工业用管螺紋接头， 由端部带有外螺纹的管体和 端部带有内螺纹的接箍连接而成， 其特征在于， 所述管体的外螺纹和 接箍的内螺纹为相互配合的偏梯形螺纹， 齿高与螺距的比为 0. 25 ~ 0. 35 , 承载面角为 -15 ~ 3° , 导向面角为 10 ~ 50。 ， 螺纹啮合后齿顶 与齿底之间存在间隙； 在螺纹侧面管体与接箍之间的密封部分依次设 置有第一柱面过渡区、 柱形密封区、 第二柱面过渡区、 锥形密封区、 锥面过渡区， 所述锥形密封区两锥面的锥度相同； 所述锥面过渡区的 端部为扭矩台肩。
所述管体上外螺纹侧面的密封部分依次为第一外柱形过渡面、 外 柱形密封面、 第二外柱形过渡面、 外锥形密封面、 外锥形过渡面， 所 述外锥形过渡面与外扭矩台肩面连接， 所述接箍上内螺纹侧面的密封 部分依次为第一内柱形面、 第二内柱形面、 内锥形面， 所述内锥形面 与内扭矩台肩面连接， 所述第一外柱形过渡面与所述第一内柱形面之 间留有间隙形成所述第一柱面过渡区， 所述外柱形密封面与所述第二 内柱形面之间通过过盈配合形成所述柱形密封区， 所述第二外柱形过 渡面与所述第二内柱形面之间留有间隙形成所述第二过渡区， 所述外 锥形密封面与所述内锥形面之间通过过盈配合形成所述锥形密封区， 所述外锥形过渡面与所述内锥形面之间留有间隙形成所述锥面过渡 区， 所述外锥形密封面与所述内锥形面的锥度角相同， 所述外扭矩台 肩面和内扭矩台肩面与管体轴线垂直面的夹角分别为 -30 ~ 0° 。
所述柱形密封区为高过盈、 小密封长度结构， 所述锥形密封区为 低过盈、 大密封长度结构。
所述柱形密封区的径向过盈量为 0. 3 ~ 1. 5mm, 柱形密封区的密封 长度大于螺距的一半； 所述锥形密封区的径向过盈量为 0. 1 ~ 0. 5匪， 锥形密封区的密封长度为 2 ~ 10mm。
螺纹部分直径方向上锥度为 1 : 20 ~ 1 : 10。
所述外锥形过渡面的锥度角为 30 ~ 60。 。
所有不连续面均采用圓弧过渡， 过渡半径为 0. 3 ~ 1匪。
螺纹啮合后齿顶与齿底之间的间隙大小为 0. 05 ~ 0. 2mm。
所述外锥形密封面与所述内锥形面的锥度角均为 10 ~ 20。 。
本发明具有下述技术效果：
1、 本发明的管螺紋接头通过采用改进的 API偏梯形螺纹， 提高了 螺纹连接的强度， 能够避免出现螺纹滑脱现象。
2、 本发明的管螺紋接头采用柱面和锥面的复合密封结构， 并通过 柱面过渡区将两个密封面有效隔离， 保证了密封的可靠性。 3、 本发明的管螺紋接头所有不连续面采用圓弧过渡， 减小了应力 集中，避免引起脆性材料断裂使物体产生疲劳裂纹，提高了连接强度。
4、 本发明的管螺紋接头采用柱面和锥面的复合密封结构， 对加工 的精度要求不高， 降低了加工难度， 便于大规模实施， 有利于提高生 产效率， 降低生产成本， 提高成品率。
5、 本发明的管螺紋接头当内螺纹和外螺纹啮合时， 除密封部分存 在干涉外， 其它部分均存在一定的间隙， 可以减小螺纹粘扣趋势。 附图说明
图 1是本发明石油天然气工业用管螺紋接头的整体示意图； 图 2是本发明密封部位局部放大示意图；
图 3是接箍部分的内螺纹结构示意图；
图 4是管体部分的外螺纹结构示意图；
图 5是螺纹形状结构示意图；
图 6是螺纹啮合示意图。
具体实施方式
以下结合附图和具体实施例对本发明进行详细说明。
本发明石油天然气工业用管螺紋接头的示意图如图 1-图 6所示， 由端部带有外螺纹 15的管体 2和端部带有内螺纹 10的接箍 1连接而 成。 所述管体 2上的外螺纹 15和接箍 1上的内螺纹 10为相互配合的 偏梯形螺纹， 齿高与螺距的比为 0. 25 ~ 0. 35 , 承载面角 t 2 为 -15 ~ 3 。 ，导向面角 t l为 10 ~ 50。 ， 以保证不同规格尺寸和不同钢级螺纹连 接性能。 外螺纹和内螺纹啮合后齿顶与齿底之间存在间隙 13 , 间隙 13 的大小为 0. 05 ~ 0. 2 螺纹部分直径方向上锥度为 1 : 20 ~ 1: 10。 在 螺纹侧面管体与接箍之间的密封部分依次设置有第一柱面过渡区 4、柱 形密封区 5、 第二柱面过渡区 6、 锥形密封区 7、 锥面过渡区 8 , 所述 锥形密封区两锥面的锥度相同。 所述锥面过渡区 8 的端部为扭矩台肩 9。 第一柱面过渡区 4实现管体外螺纹 15和接箍内螺纹 10与柱形密封 区 5的过渡， 避免啮合对螺纹面的损伤。 第二柱面过渡区 6实现柱面 密封区 5与锥形密封区 7的有效隔离。 锥面过渡区 8实现管体与接箍 的光滑过渡， 保证接头密封质量。 扭矩台肩 9用于螺纹连接的定位并 且吸收过高的上扣扭矩。 所有过度面均可吸收多余螺纹脂， 降低螺纹 脂对金属密封的影响。
为了避免应力集中， 所有不连续面均采用圓弧过渡， 过渡半径 Rl R2 R3为 0. 3 ~ lmm
过渡区和密封区的设计通过管体和接箍的下述结构实现： 所述管 体 2上外螺纹 15侧面的密封部分依次为第一外柱形过渡面 16、外柱形 密封面 17、 第二外柱形过渡面 18、 外锥形密封面 19、 外锥形过渡面 20 , 所述外锥形过渡面 20与外扭矩台肩面 21连接。 所述接箍 1上内 螺纹 10侧面的密封部分依次为第一内柱形面 11、 第二内柱形面 12 内锥形面 13 , 所述内锥形面 13与内扭矩台肩面 14连接。 所述第一外 柱形过渡面 16与所述第一内柱形面 11之间留有间隙形成所述第一柱 面过渡区 4。所述外柱形密封面 17与所述第二内柱形面 12之间通过过 盈配合形成所述柱形密封区 5 , 实现金属对金属的密封作用。 所述第二 外柱形过渡面 18与所述第二内柱形面 12之间留有间隙形成所述第二 过渡区 6。所述外锥形密封面 19与所述内锥形面 13之间通过过盈配合 形成所述锥形密封区 7 , 实现金属对金属的密封作用。 所述外锥形过渡 面 20与所述内锥形面 13之间留有间隙形成所述锥面过渡区 8 ,所述外 锥形密封面 19与所述内锥形面 13的锥度角相同， 所述外锥形密封面 与所述内锥形面的锥度角均为 10 ~ 20° , 即 ps 3=bs 3=10 ~ 20。 。 所述 外扭矩台肩面 21 与管体轴线垂直面的夹角为 ps l , 内扭矩台肩面 14 与管体轴线垂直面的夹角为 bs l , bs l=ps l= -30 - 0°
其中， 所述柱形密封区为高过盈、 小密封长度结构， 以避免因轴 向载荷导致的密封性能降低。 所述柱形密封区的径向过盈量 12—般为 0. 3 ~ 1. 5 柱形密封区的密封长度 b2大于螺距的一半。 所述锥形密 封区为低过盈、 大密封长度结构， 锥面密封可以降低密封面粘接趋势。 所述锥形密封区的径向过盈量 I I一般为 0. 1 ~ 0. 5mm,锥形密封区的密 封长度 bl为 2 ~ 10mm
所述外锥形过渡面 20的锥度角 ps2为 30 ~ 60
以下分别以 88. 9 6. 45mm油管和 177. 8 9. 19mm套管作为实施例 进行详细说明。 实施例 1： 88.9 x 6.45mm油管
螺距为 4· 2匪， 外螺纹齿高为 1匪， 内螺纹齿高 1.1匪， 内螺纹齿 高与螺距的比为 0.26, 内螺纹与外螺紋之间相差 0.1匪， 当内螺纹与 外螺纹啮合时， 由于齿高存在差异， 使得内螺纹齿底与外螺纹齿顶存 在间隙 13=0.1匪。 承载面角 U=- 10。 ， 导向面角 tl=30。 ， 倒角 R1=0.3mm, R2=0.6mm, psl=bsl= -10° , ps2=30° , ps3=bs3=10° , bl = 3mm, b2=2.5mm, R3=0.5mm, 11=0.2mm, 12=0.3mm。 螺纹部分直径 方向上锥度为 1/16。
实施例 2: 177.8 X 9.19mm套管
螺距为 5.08mm, 外螺纹齿高为 1.47mm, 内螺纹齿高 1.57mm, 内螺 纹齿高与螺距比为 0.31, 内螺纹与外螺紋之间相差 0.1匪， 当内螺纹 与外螺纹啮合时， 由于齿高存在差异， 使得内螺纹齿底与外螺纹齿顶 存在间隙 13=0.1匪， 承载面角 t2=3。 ， 导向面角 tl = 10。 ， 倒角 R1=0.5mm, R2=0.8mm, psl=bsl=0° , ps2=45° , ps3=bs3=14° , bl=5mm, b2=3mm, R3=0.5mm, 11=0.4mm, 12=0.6mm。 螺纹部分直径方向上锥度 为 1/16。
本发明的管螺紋接头适用于石油天然气工业用油管、 套管， 可用 于高压油井及高压气井。 由于本发明性能可靠、 加工难度小， 可用于 所有对密封性要求较高的油、 气井， 尤其高压油、 气井， 此外， 对于 高钢级和大壁厚套管更为有效， 应用前景广阔。

Claims

权 利 要 求 书
1、 一种石油天然气工业用管螺紋接头， 由端部带有外螺纹的管体 和端部带有内螺纹的接箍连接而成， 其特征在于， 所述管体的外螺纹 和接箍的内螺纹为相互配合的偏梯形螺纹， 齿高与螺距的比为 0. 25 ~ 0. 35 , 承载面角为 -15 ~ 3° , 导向面角为 10 ~ 50。 ， 螺纹啮合后齿顶 与齿底之间存在间隙； 在螺纹侧面管体与接箍之间的密封部分依次设 置有第一柱面过渡区、 柱形密封区、 第二柱面过渡区、 锥形密封区、 锥面过渡区， 所述锥形密封区两锥面的锥度相同； 所述锥面过渡区的 端部为扭矩台肩。
2、 根据权利要求 1所述的石油天然气工业用管螺紋接头， 其特征 在于， 所述管体上外螺纹侧面的密封部分依次为第一外柱形过渡面、 外柱形密封面、 第二外柱形过渡面、 外锥形密封面、 外锥形过渡面， 所述外锥形过渡面与外扭矩台肩面连接， 所述接箍上内螺纹侧面的密 封部分依次为第一内柱形面、 第二内柱形面、 内锥形面， 所述内锥形 面与内扭矩台肩面连接， 所述第一外柱形过渡面与所述第一内柱形面 之间留有间隙形成所述第一柱面过渡区， 所述外柱形密封面与所述第 二内柱形面之间通过过盈配合形成所述柱形密封区， 所述第二外柱形 过渡面与所述第二内柱形面之间留有间隙形成所述第二过渡区， 所述 外锥形密封面与所述内锥形面之间通过过盈配合形成所述锥形密封 区， 所述外锥形过渡面与所述内锥形面之间留有间隙形成所述锥面过 渡区， 所述外锥形密封面与所述内锥形面的锥度角相同， 所述外扭矩 台肩面和内扭矩台肩面与管体轴线垂直面的夹角分别为 -30 ~ 0° 。
3、 根据权利要求 1或 2所述的石油天然气工业用管螺紋接头， 其 特征在于， 所述柱形密封区为高过盈、 小密封长度结构， 所述锥形密 封区为低过盈、 大密封长度结构。
4、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 所述柱形密封区的径向过盈量为 0. 3 ~ 1. 5mm, 柱形密封区的密 封长度大于螺距的一半；所述锥形密封区的径向过盈量为 0. 1 ~ 0. 5mm, 锥形密封区的密封长度为 2 ~ 10mm。
5、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 螺纹部分直径方向上锥度为 1 : 20 ~ 1: 10。
6、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 所述外锥形过渡面的锥度角为 30 ~ 60。 。
7、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 所有不连续面均采用圓弧过渡， 过渡半径为 0. 3 ~ 1匪。
8、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 螺纹啮合后齿顶与齿底之间的间隙大小为 0. 05 ~ 0. 2匪。
9、 根据权利要求 3所述的石油天然气工业用管螺紋接头， 其特征 在于， 所述外锥形密封面与所述内锥形面的锥度角均为 10 ~ 20。 。
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