WO2017215183A1 - 一种高抗扭钻杆接头 - Google Patents

一种高抗扭钻杆接头 Download PDF

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Publication number
WO2017215183A1
WO2017215183A1 PCT/CN2016/104802 CN2016104802W WO2017215183A1 WO 2017215183 A1 WO2017215183 A1 WO 2017215183A1 CN 2016104802 W CN2016104802 W CN 2016104802W WO 2017215183 A1 WO2017215183 A1 WO 2017215183A1
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Prior art keywords
cylindrical section
threaded joint
joint
externally threaded
section
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PCT/CN2016/104802
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English (en)
French (fr)
Inventor
刘永刚
赵向坤
张献才
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东营威玛石油钻具有限公司
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Publication of WO2017215183A1 publication Critical patent/WO2017215183A1/zh

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    • 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

Definitions

  • the invention relates to the field of drilling tools, in particular to a high torsion resistant drill pipe joint.
  • Drilling tools are important tools in oil and gas exploration and development, and are an important part of the drill string system.
  • Various drilling tools such as drill pipes, weighted drill pipes, drill collars, adapters, etc., are formed by thread connection.
  • Root drill string The drill string is not only the circulation channel of the drilling fluid, but also transmits torque in the drilling, and is subjected to the combined action of various loads such as tension, bending, torsion, vibration and shock.
  • the drill string In addition to the rotation of the drill string in the drilling operation, the drill string often revolves with the axis of the wellbore as the axis, which causes the friction and wear of the drill joint and the well wall or casing to generate reverse motion, so that the drill There is a risk of loosening the threads.
  • the boring of the drill bit caused by the staggering of the soft and hard formations produces a momentary counter-torque to the drill string, causing the thread of the drill to loosen.
  • the drill string is subjected to longitudinal shock shock loads from the formation reaction force, and the drilled threaded joint is at risk of loosening.
  • the loosening of the drill string during the drilling operation occurs, resulting in gluing failure and friction and wear failure of the drill pipe joint. Due to the loose connection of the threaded connection, the contact pressure of the torque shoulder surface is reduced, resulting in failure of the piercing of the threaded torque shoulder surface of the drill.
  • the present invention provides a high torsion resistant drill pipe joint.
  • the technical solution of the present invention is: a high torsion-resistant drill pipe joint comprising an internally threaded joint and an externally threaded joint, the internally threaded joint comprising a first torque shoulder surface, a first cylindrical section, an internal thread section, and a second a cylindrical section, a second torque shoulder surface;
  • the male threaded joint includes a first torque shoulder surface, a first cylindrical section, an externally threaded section, a second cylindrical section, a second torque shoulder surface, and an internal thread of the female threaded joint
  • the second cylindrical section of the segment and the externally threaded joint has a taper range of 1:6-1:12; the outer diameter of the second cylindrical section of the male threaded joint is larger than the inner diameter of the second cylindrical section of the internally threaded joint; the externally threaded joint a gap fit between the first cylindrical section and the first cylindrical section of the female threaded joint; an interference fit between the second cylindrical section of the externally threaded joint and the second cylindrical section of the internally threaded
  • the value of the radius of the nose of the second cylindrical section of the externally threaded joint is R1.5; the diameter of the outer surface of the second cylindrical section of the externally threaded joint is 0.02-0.18 mm larger than the diameter of the inner surface of the second cylindrical section of the internally threaded joint.
  • the lubrication groove of the externally threaded joint is a spiral groove.
  • the outer threaded joint has a lubrication groove width of 3 mm.
  • the externally threaded joint has a lubrication groove depth of 0.3 mm.
  • the threaded groove of the externally threaded joint has a pitch of 6 mm.
  • the outer diameter of the second cylindrical section of the externally threaded joint is 0.12 mm larger than the inner surface diameter of the second cylindrical section of the internally threaded joint.
  • the taper ratio of the threaded section of the internally threaded section of the internally threaded joint to the externally threaded joint is 1:12.
  • the invention has the beneficial effects that after the inner and outer threaded joints are buckled, an interference fit between the outer surface of the second cylindrical section of the external thread and the contact surface of the inner surface of the second cylindrical section of the internal thread will generate radial Force, the elastic deformation energy is generated, the shackle torque is increased, and the drill pipe joint is effectively reduced during the use process.
  • the risk of the buckle is to improve the safety and reliability of the drill pipe joint; in the process of fastening the inner and outer threaded joints, the threaded grease passes through the lubrication groove of the externally threaded joint and the outer surface of the second cylindrical section of the external thread and the internal thread
  • the inner surface of the second cylindrical section is lubricated to avoid the bonding of the contact surface due to the frictional heat generated by the interference fit.
  • the inner and outer threaded joints are buckled, the first torque shoulder surface and the first The two torque table shoulders are in effective contact, so that the threaded joint has high torsion resistance; after the inner and outer threaded joints are buckled, the torsional strength is improved by more than 50% compared with the API thread joint of the same specification.
  • the joint is not only suitable for drilling operations in normal working conditions, but also for complex working wells such as ultra-deep wells, super-long horizontal wells, large-displacement wells, long-distance directional crossings that require high torque.
  • FIG. 1 is a top buckle torque diagram of a conventional drill threaded joint
  • FIG. 2 is a structural view of a conventional double shoulder drill threaded joint
  • FIG. 3 is a structural view of the inner and outer threaded joint of the present invention
  • 1 is an externally threaded joint
  • 11 is a first torque shoulder surface
  • 12 is a first cylindrical section
  • 13 is an externally threaded section
  • 14 is a second cylindrical section
  • 15 is a second torque shoulder surface
  • 16 is a threaded tooth
  • the bottom 17 is the lubrication groove
  • 18 is the outer surface of the second cylindrical section
  • 19 is the nose end chamfer radius
  • 2 is the female threaded joint
  • 21 is the first torque shoulder surface
  • 22 is the first cylindrical section
  • 23 is The internal thread section
  • 24 is the second cylindrical section
  • 25 is the second torque shoulder surface.
  • a high torsion drill pipe joint comprising an internally threaded joint 2 and an externally threaded joint 1 comprising a first torque shoulder surface 21, a first cylindrical section 22, an internally threaded section 23, a second cylinder Section 24, a second torque shoulder surface 25;
  • the male threaded joint 1 includes a first torque shoulder surface 11, a first cylindrical section 12, an externally threaded section 13, a second cylindrical section 14, and a second torque shoulder surface 15,
  • the inner thread section 23 of the female threaded joint 2 and the second cylindrical section (14) of the male threaded joint 1 have a taper range of 1:6-1:16;
  • the outer portion of the second cylindrical section 14 of the male threaded joint 1 The diameter is larger than the inner diameter of the second cylindrical section 24 of the female threaded joint 2;
  • the first cylindrical section 12 of the male joint 1 and the first cylindrical section 22 of the female joint 2 are clearance fit;
  • the second cylindrical section 24 of the joint 2 is an interference
  • the externally threaded joint 1 has a second cylindrical section 14 whose nose end chamfer radius 19 has a value of R1.5; the externally threaded joint 1 has a second cylindrical section outer surface 18 which is larger in diameter than the inner diameter of the second cylindrical section 24 of the internally threaded joint 2 Large 0.02-0.18mm.
  • the lubrication groove 17 of the second cylindrical section 14 of the externally threaded joint 1 is a spiral groove.
  • the outer threaded joint 1 has a lubricating groove 17 having a width of 3 mm.
  • the externally threaded joint 1 has a lubricating groove 17 having a depth of 0.3 mm.
  • the outer threaded joint 1 has a lubricating groove 17 having a pitch of 6 mm.
  • the outer diameter 18 of the second cylindrical section of the male connector 1 is 0.12 mm larger than the diameter of the inner surface of the second cylindrical section 24 of the female fitting 2.
  • the taper ratio of the threaded section of the female threaded section 23 of the female threaded joint 2 to the male threaded joint 1 is 1:12.
  • the outer surface 18 of the second cylindrical section of the external thread contacts the inner surface of the second cylindrical section 24 of the internal thread to form an interference fit, which increases the upper buckle torque.
  • the threaded grease lubricates the outer surface 18 of the second cylindrical section and the inner surface 24 of the second cylindrical section of the internal thread through the helical lubrication groove 17 of the outer surface of the second cylindrical section to avoid bonding of the contact faces.
  • the contact surface of the second cylindrical section outer surface 18 of the external thread with the inner surface of the second cylindrical section 24 of the internal thread increases, and the upper buckle torque gradually increases.
  • the second torque shoulder surface of the inner and outer threaded joints is in contact with the first torque shoulder surface, and the torque value reaches a preset value to complete the upper buckle.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Abstract

一种高抗扭钻杆接头，包括内螺纹接头(2)和外螺纹接头(1)，内螺纹接头的内螺纹段(23)与外螺纹接头的螺纹段锥度范围为1:6-1:12；外螺纹接头第一圆柱段(12)与内螺纹接头第一圆柱段(22)间为间隙配合；外螺纹接头的第二圆柱段(14)的外径大于内螺纹接头的第二圆柱段(24)的内径；外螺纹接头第二圆柱段与内螺纹接头第二圆柱段间为过盈配合；外螺纹接头第二圆柱段有润滑槽(17)；外螺纹接头润滑槽的宽度为2-4mm；深度为0.2-0.4mm；螺距为5-7mm；外螺纹接头第二圆柱段鼻端圆弧倒角半径(19)的值为R1.5；外螺纹接头第二圆柱段的外表面直径比内螺纹接头第二圆柱段的内表面直径大0.02-0.18mm。所述钻杆接头连接后稳定性好，抗扭强度高，不仅适用于常规工况的钻井作业，也适用于需要大扭矩的超深井、超长水平井、大位移井、长距离定向穿越等复杂工况井。

Description

一种高抗扭钻杆接头 技术领域
本发明涉及钻具领域，具体涉及一种高抗扭钻杆接头。
背景技术
钻具是石油天然气勘探与开发中的重要工具，是钻柱系统的重要组成部分，各种钻具，如钻杆、加重钻杆、钻铤、转换接头等，通过螺纹连接的方式，形成整根钻柱。钻柱不仅是钻井液的循环通道，而且在钻井中传递扭矩，承受拉压，弯曲，扭转以及振动、冲击等多种载荷的复合作用。钻柱在钻井作业中的运动方式除了绕自身轴线自转外，还常常以井眼轴线为轴线进行公转，从而导致钻具接头与井壁或套管发生摩擦磨损，产生反转运动，使钻具螺纹存在松扣的风险。软硬地层交错引发的钻头的憋钻会对钻柱产生瞬时的反扭矩，使钻具螺纹发生松扣。此外，因钻头破碎岩石的不均匀性导致钻柱承受来自地层反作用力的纵向震动冲击载荷，也使钻柱螺纹接头存在松扣的风险。事实上，钻柱在钻井作业过程中的松扣现象时有发生，从而导致钻杆接头发生粘扣失效和摩擦磨损失效。由于螺纹连接的松扣，扭矩台肩面的接触压力降低，从而导致钻具螺纹扭矩台肩面的刺漏失效。此外，由于螺纹连接的松扣，相互啮合的螺纹连接的应力发生变化，出现局部的高应力区域，使螺纹连接发生疲劳失效，导致螺纹接头的刺漏或断裂。上述的这些失效在公开报道的文献资料里有大量的记载。钻杆接头发生松扣的原因主要有以下几方面的因素：(1)钻杆接头承受的如上所述的复杂的载荷工况；(2)在上扣操作中，上扣扭矩低于接头的名义最小上扣矩值；(3)目前钻杆接头的自身结构。目前普遍所用的钻杆接头，无论是单台肩螺纹接头还是双台肩的螺纹接头，采用的是粗牙螺纹。在扭矩台肩接触之前，上扣扭矩值很小，当扭矩台肩接触后，扭矩值迅速飙升到设定的上扣扭矩值，如附图1所示。也就是说，当震动或瞬时的反扭矩等其他因素导致相互啮合的接头台肩面发生微小的反向位移时，螺纹接头的扭矩值会迅速下降，尤其是已有一定磨损后的螺纹接头，这是钻具螺纹松扣的结构设计因素。
技术问题
问题的解决方案
技术解决方案
为解决现有技术的不足，本发明提供一种高抗扭钻杆接头。
本发明的技术方案是：一种高抗扭钻杆接头，包括内螺纹接头和外螺纹接头，所述的内螺纹接头包括第一扭矩台肩面，第一圆柱段，内螺纹段，第二圆柱段，第二扭矩台肩面；外螺纹接头包括第一扭矩台肩面，第一圆柱段，外螺纹段，第二圆柱段，第二扭矩台肩面，所述内螺纹接头的内螺纹段与外螺纹接头的第二圆柱段螺纹段锥度范围为1∶6-1∶12；所述外螺纹接头的第二圆柱段的外径大于内螺纹接头第二圆柱段的内径；外螺纹接头第一圆柱段与内螺纹接头第一圆柱段间为间隙配合；外螺纹接头第二圆柱段与内螺纹接头第二圆柱段间为过盈配合；外螺纹接头第二圆柱段上有润滑槽；外螺纹接头的润滑槽宽度为2-4mm；外螺纹接头的润滑槽深度为0.2-0.4mm；外螺纹接头润滑槽的螺距为4-6mm。外螺纹接头第二圆柱段鼻端圆弧倒角半径的值为R1.5；外螺纹接头第二圆柱段的外表面直径比内螺纹接头第二圆柱段的内表面直径大0.02-0.18mm。
所述外螺纹接头的润滑槽为螺旋槽。
所述外螺纹接头的润滑槽宽度为3mm。
所述外螺纹接头的润滑槽深度为0.3mm。
所述外螺纹接头的润滑槽螺距为6mm。
所述外螺纹接头第二圆柱段外表面直径比内螺纹接头第二圆柱段的内表面直径大0.12mm。
所述内螺纹接头的内螺纹段与外螺纹接头的螺纹段锥度比为1∶12。。
发明的有益效果
有益效果
发明的有益效果是：所述的内、外螺纹接头在上扣后，外螺纹的第二圆柱段外表面与内螺纹的第二圆柱段内表面的接触面间的过盈配合将产生径向力，产生弹性变形能，使卸扣扭矩增加，有效的降低钻杆接头在使用过程中产生“二次上 扣”的风险，提高钻杆接头的安全可靠性；所述的内、外螺纹接头在上扣过程中，螺纹脂通过外螺纹接头的润滑槽对外螺纹的第二圆柱段外表面和内螺纹的第二圆柱段内表面进行润滑，避免了接触面因过盈配合产生的摩擦热而产生接触面的粘结。所述的内、外螺纹接头在上扣后，第一扭矩台肩面和第二扭矩台肩面有效接触，使螺纹接头具有高抗扭性能；所述的内、外螺纹接头在上扣后，经试验，抗扭强度比同规格的API螺纹接头提高50％以上。该螺纹接头不仅适用于常规工况的钻井作业，也适用于需要大扭矩的超深井、超长水平井、大位移井、长距离定向穿越等复杂工况井。
对附图的简要说明
附图说明
图1是常规钻具螺纹接头的上扣扭矩曲线图；图2是常规双台肩钻具螺纹接头结构图；图3是本发明的内、外螺纹接头连接后的结构图；图4是外螺纹接头第二圆柱段的局部放大图。
其中：1为外螺纹接头、11为第一扭矩台肩面、12为第一圆柱段、13为外螺纹段、14为第二圆柱段、15为第二扭矩台肩面、16为螺纹齿底、17为润滑槽、18为第二圆柱段外表面、19为鼻端圆弧倒角半径、2为内螺纹接头、21为第一扭矩台肩面、22为第一圆柱段、23为内螺纹段、24为第二圆柱段、25为第二扭矩台肩面。
发明实施例
本发明的实施方式
下面结合附图对本发明作进一步的说明。
一种高抗扭钻杆接头，包括内螺纹接头2和外螺纹接头1，所述的内螺纹接头2包括第一扭矩台肩面21，第一圆柱段22，内螺纹段23，第二圆柱段24，第二扭矩台肩面25；外螺纹接头1包括第一扭矩台肩面11，第一圆柱段12，外螺纹段13，第二圆柱段14，第二扭矩台肩面15，所述内螺纹接头2的内螺纹段23与外螺纹接头1的第二圆柱段(14)螺纹段锥度范围为1∶6-1∶16；所述外螺纹接头1的第二圆柱段14的外径大于内螺纹接头2第二圆柱段24的内径；外螺纹接头1第一圆柱段12与内螺纹接头2第一圆柱段22间为间隙配合；外螺纹接头1第二圆柱段14与内螺 纹接头2第二圆柱段24间为过盈配合；外螺纹接头1第二圆柱段14有润滑槽17；外螺纹接头1的润滑槽17的宽度为2-4mm；外螺纹接头1的润滑槽17的深度为0.2-0.4mm；外螺纹接头1润滑槽17的螺距为4-6mm。；外螺纹接头1第二圆柱段14鼻端圆弧倒角半径19的值为R1.5；外螺纹接头1第二圆柱段外表面18直径比内螺纹接头2第二圆柱段24的内表面直径大0.02-0.18mm。
所述的外螺纹接头1的第二圆柱段14的润滑槽17为螺旋槽。
所述外螺纹接头1润滑槽17的宽度为3mm。
所述外螺纹接头1润滑槽17的深度为0.3mm。
所述外螺纹接头1润滑槽17的螺距为6mm。
所述外螺纹接头1第二圆柱段外表面18直径比内螺纹接头2第二圆柱段24的内表面直径大0.12mm。
所述内螺纹接头2的内螺纹段23与外螺纹接头1的螺纹段锥度比为1∶12。
采用以上实施参数，内、外螺纹接头在上扣时，外螺纹的第二圆柱段外表面18与内螺纹的第二圆柱段24内表面接触，形成过盈配合，增加上扣扭矩。螺纹脂通过第二圆柱段外表面的螺旋形润滑槽17对第二圆柱段的外表面18和内螺纹的第二圆柱段内表面24进行润滑，避免接触面的粘结。随着螺纹的旋合，外螺纹的第二圆柱段外表面18与内螺纹的第二圆柱段24内表面的接触面增加，上扣扭矩逐渐增大。随后，内外螺纹接头的第二扭矩台肩面和第一扭矩台肩面先后接触，扭矩值达到预设值，完成上扣。
采用以上实施参数，内、外螺纹接头在上扣后，外螺纹的第二圆柱段外表面18与内螺纹的第二圆柱段24内表面的接触面间的过盈配合将产生径向力，产生弹性变形能，使卸扣扭矩增加，有效的降低钻杆接头在使用过程中产生“二次上扣“的风险，提高钻杆接头的安全可靠性。
采用以上实施参数，内、外螺纹接头在上扣后，第一扭矩台肩面和第二扭矩台肩面有效接触，使螺纹接头具有高抗扭性能。
采用以上实施参数，内、外螺纹接头在上扣后，经试验，抗扭强度比同规格的API螺纹接头提高55％。

Claims (7)

  1. 一种高抗扭钻杆接头，包括内螺纹接头(2)和外螺纹接头(1)，其特征在于：所述的内螺纹接头(2)包括第一扭矩台肩面(21)，第一圆柱段(22)，内螺纹段(23)，第二圆柱段(24)，第二扭矩台肩面(25)；外螺纹接头(1)包括第一扭矩台肩面(11)，第一圆柱段(12)，外螺纹段(13)，第二圆柱段(14)，第二扭矩台肩面(15)，所述内螺纹接头(2)的内螺纹段(23)与外螺纹接头(1)的第二圆柱段(14)螺纹段锥度范围为1∶6-1∶12；所述外螺纹接头(1)的第二圆柱段(14)的外径大于内螺纹接头(2)第二圆柱段(24)的内径；外螺纹接头(1)第一圆柱段(12)与内螺纹接头(2)第一圆柱段(22)间为间隙配合；外螺纹接头(1)第二圆柱段(14)与内螺纹接头(2)第二圆柱段(24)间为过盈配合；外螺纹接头(1)第二圆柱段(14)有润滑槽(17)；外螺纹接头(1)润滑槽(17)的宽度为2-4mm；外螺纹接头(1)润滑槽(17)的深度为0.2-0.4mm；外螺纹接头(1)润滑槽(17)的螺距为4-6mm。外螺纹接头(1)第二圆柱段(14)鼻端圆弧倒角半径(19)的值为R1.5；外螺纹接头(1)第二圆柱段外表面(18)直径比内螺纹接头(2)第二圆柱段(24)的内表面直径大0.02-0.18mm。
  2. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述的外螺纹接头(1)的第二圆柱段(14)的润滑槽(17)为螺旋槽。
  3. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述外螺纹接头(1)润滑槽(17)的宽度为3mm。
  4. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述外螺纹接头(1)润滑槽(17)的深度为0.3mm。
  5. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述外螺纹接头(1)润滑槽(17)的螺距为6mm。
  6. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述外螺纹接头(1)第二圆柱段外表面(18)直径比内螺纹接头(2)第二圆柱段(24)的内表面直径大0.12mm。
  7. 根据权利要求1所述的一种高抗扭钻杆接头，其特征在于：所述内螺纹接头(2)的内螺纹段(23)与外螺纹接头(1)的螺纹段锥度比为1∶12。
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