WO2013143023A1 - Eccentric constant-width bearing seal groove of cone bit - Google Patents

Eccentric constant-width bearing seal groove of cone bit Download PDF

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Publication number
WO2013143023A1
WO2013143023A1 PCT/CN2012/000418 CN2012000418W WO2013143023A1 WO 2013143023 A1 WO2013143023 A1 WO 2013143023A1 CN 2012000418 W CN2012000418 W CN 2012000418W WO 2013143023 A1 WO2013143023 A1 WO 2013143023A1
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WO
WIPO (PCT)
Prior art keywords
bearing
cylinder
seal
cone
sealing
Prior art date
Application number
PCT/CN2012/000418
Other languages
French (fr)
Chinese (zh)
Inventor
幸发芬
Original Assignee
Xing Fafen
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 Xing Fafen filed Critical Xing Fafen
Priority to PCT/CN2012/000418 priority Critical patent/WO2013143023A1/en
Publication of WO2013143023A1 publication Critical patent/WO2013143023A1/en

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B10/00—Drill bits
    • E21B10/08—Roller bits
    • E21B10/22—Roller bits characterised by bearing, lubrication or sealing details
    • E21B10/25—Roller bits characterised by bearing, lubrication or sealing details characterised by sealing details
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7836—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members floating with respect to both races
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2352/00—Apparatus for drilling

Definitions

  • the invention belongs to the technical field of roller cone bit bearing sealing. It is suitable for sealed roller cone drills for petroleum, geology and engineering. Background technique
  • the life of a roller cone bit depends primarily on the bearing.
  • the life of the bearing is mainly determined by the seal.
  • the first task of the seal is to prevent grease leakage inside the bearing, and the other is to prevent the mud which is corrosive and abrasive outside the drill bit from invading the bearing. Once the seal fails, the bearing wears out quickly, causing the drill to fail.
  • the roller bit bearing has a gap in the radial direction.
  • the presence of these gaps results in inconsistent compression ratios of the elastomeric seals in the circumferential direction.
  • the bearing is in contact on the force side, and the radial clearance is concentrated on the non-stress side. Therefore, the compression ratio of the elastic sealing ring on the force receiving side reaches an extremely large state, and the compression ratio on the non-stress side reaches an extremely small state.
  • the current practice is to increase the design compression ratio of the elastic seal.
  • the invention aims at the deficiencies in the above bearing seal of the roller bit, and adopts an eccentrically wide bearing seal groove, which eliminates the change of the seal groove width caused by the existence of the bearing gap, and realizes the equal compression of the bearing seal ring in the circumferential direction. Therefore, the design requirement of the bearing ring compression ratio is reduced, the sealing ring is adapted to the high rotation speed, and the sealing life is prolonged.
  • Figure 1 is a typical structural view of the present invention.
  • Figure 2 is a schematic view of the circumferential direction of the present invention.
  • Figure 3 is a second typical structural diagram of the present invention.
  • Figure 4 is a third exemplary structural view of the present invention.
  • FIG. 5 is a fourth typical structural view of the present invention. detailed description
  • FIG. 1 is a view showing a typical structure of the present invention.
  • the palm bearing 1 cooperates with the inner bore 2 of the cone to form a bearing for the roller cone bit.
  • the palm bearing comprises a radially pressurized cylinder 5 and a sealing cylinder 7.
  • the inner bore of the cone includes a radially pressurized cylinder 6 and a sealed cylindrical body 8.
  • the sealing groove 3 is formed by a tooth bearing sealing cylinder and a cone inner sealing cylinder.
  • the sealing groove 3 is provided with an elastic sealing ring 4. When the roller bit is working, it is forced in the direction of the force side F.
  • the palm bearing is in contact with the inner bore of the cone on the F side and a radial gap A on the other side.
  • the palm seal body 7 and the palm-bearing cylinder 5 have an eccentricity C and a diameter difference B.
  • the diameter difference B is equal to the radial gap A.
  • the direction of the eccentricity is the same as the direction of the force.
  • Figure 2 is a schematic view of the circumferential direction of the present invention.
  • 11 is a projection of the inner ring sealing cylinder 8 of the cone.
  • 12 is a projection of the bearing cylinder 5 of the tooth bearing.
  • ⁇ is the projection of the palm seal cylinder 7.
  • 14 is an elastic seal. Due to the existence of eccentricity C, When the roller bit is in operation, 11 and 13 are two concentric circles, and the seal grooves formed by 11 and 13 have a width which is constant in the circumferential direction.
  • the sealing ring 14 is compressed and mounted in the sealing groove, and its compression ratio is also fixed. That is to say, the compression ratio of the seal ring is uniform on the force side and the non-force side.
  • the compression ratio of the sealing ring can be designed to be in a small range.
  • the small compression ratio increases the ability of the seal to accommodate high speeds and extends the life of the seal.
  • Figure 3 is a second typical structural view of the present invention. Compared with the structure of Fig. 1, the difference is that the diameter of the crown bearing sealing cylinder 7 is not larger than the diameter of the bearing cylinder 5, but smaller than the diameter of the bearing cylinder 5, and the small value B is equal to the radial direction. Eight gaps.
  • Figure 4 is a third exemplary structural view of the present invention. The difference from Figure 1 is that the seal is not a single seal but a mechanical seal assembly 15.
  • Figure 5 is a fourth exemplary structural diagram of the present invention. The difference from Figure 1 is that the seal is not a single seal but a seal assembly 16 consisting of two seals.

Abstract

A bearing seal structure of a cone bit is formed by a cone leg bearing (1), a cone inner hole (2), a seal groove (3), and a seal member (4). The seal groove (3) is formed by a seal cylinder (7) of the cone leg bearing and a seal cylinder (8) of the cone inner hole. A radial gap A is arranged between the cone leg bearing and the cone inner hole. An eccentricity C is provided between the seal cylinder of the cone leg bearing and a pressure-bearing cylinder, and a diameter difference B is provided. The diameter difference B = the radial gap A. The eccentric direction is the same as the direction of the force applying on the cone, and the size of the eccentricity is equal to half of the diameter difference, that is, C = (1/2)B. With the design of the eccentricity and the diameter difference, the circumferential width of the seal groove and the compression rate of a seal ring in the entire circumference are not changed by the bearing gap during operation of the cone bit. The width of the seal groove and the compression rate of the seal ring are stable, so that the compression rate of the elastic seal member can be designed within a low range. In this way, the adaptability of the bearing seal member to high-speed rotation is improved, and the service life of the bearing seal ring is prolonged.

Description

牙轮钻头偏心等宽轴承密封槽  Cone bit eccentric bearing seal groove
技术领域 Technical field
本发明属于牙轮钻头轴承密封技术领域。适应于石油、地质、工程用的密封型牙轮钻头。 背景技术  The invention belongs to the technical field of roller cone bit bearing sealing. It is suitable for sealed roller cone drills for petroleum, geology and engineering. Background technique
牙轮钻头的寿命主要取决于轴承。 而轴承的寿命主要取决于密封。 密封的任务一是防止 轴承内的润滑脂泄漏， 二是阻止钻头外部具有腐蚀性和研磨性的泥浆侵入轴承。 密封一旦失 效， 轴承就会很快地被磨损， 从而导致钻头失效。  The life of a roller cone bit depends primarily on the bearing. The life of the bearing is mainly determined by the seal. The first task of the seal is to prevent grease leakage inside the bearing, and the other is to prevent the mud which is corrosive and abrasive outside the drill bit from invading the bearing. Once the seal fails, the bearing wears out quickly, causing the drill to fail.
牙轮钻头的密封一般都依靠弹性密封元件的径向压缩实现其密封功能。 如专利 The sealing of the roller cone bit generally relies on the radial compression of the elastomeric sealing element to achieve its sealing function. Such as patent
US5524718、 US5655611采用的是一个 0形密封圈， 专利 US 3765495、 US 4037673釆用的是 一个矩形密封圈， 专利 CN 201080787Y说、 US 6033117、 US 6254275 B1采用的是双密封圈， 专利 CN 2259868Y采用的是一个 X形密封圈。在这些专利中， 密封元件都是靠径向压缩实现 其密封功能的。 专利 US4516641、 US466600 US4923020采用的虽然是以机械密封为动密 封的密封装置， 但是它们也含有给机械密封面提书供压力的弹性静密封元件。 这些弹性静密封 元件也同样依靠径向压缩实现其密封和供压的需要。 US5524718 and US5655611 use a 0-shaped sealing ring. Patent US 3765495 and US 4037673 use a rectangular sealing ring. The patent CN 201080787Y says that US 6033117 and US 6254275 B1 use a double sealing ring, which is adopted by the patent CN 2259868Y. It is an X-shaped seal. In these patents, the sealing element is sealed by radial compression. U.S. Patent No. 4,156, 641, U.S. Patent No. 4,664, 640, and U.S. Patent No. 4,923,020, both of which are incorporated herein by reference to each other, the utility of the utility of the utility of These elastic static sealing elements also rely on radial compression for their sealing and pressure supply requirements.
牙轮钻头轴承在径向是有间隙的。 这些间隙的存在， 导致弹性密封圈在圆周方向的压缩 率不一致。 当钻头工作时， 轴承在受力侧接触， 径向间隙全部集中到非受力侧。 所以， 弹性 密封圈在受力侧的压缩率达到极大状态， 在非受力侧的压縮率达到极小状态。 为了保证非受 力侧的密封不发生泄漏现象， 现行的做法是加大弹性密封圈的设计压缩率。  The roller bit bearing has a gap in the radial direction. The presence of these gaps results in inconsistent compression ratios of the elastomeric seals in the circumferential direction. When the drill bit is working, the bearing is in contact on the force side, and the radial clearance is concentrated on the non-stress side. Therefore, the compression ratio of the elastic sealing ring on the force receiving side reaches an extremely large state, and the compression ratio on the non-stress side reaches an extremely small state. In order to ensure that the seal on the non-stress side does not leak, the current practice is to increase the design compression ratio of the elastic seal.
加大压缩率后的弊端是明显的。 大的压缩率， 产生大的摩擦阻力和摩擦热， 降低了密封 圈适应高转速的能力， 也縮短了密封圈的使用寿命。 发明内容  The drawbacks of increasing the compression ratio are obvious. The large compression ratio produces large frictional resistance and frictional heat, which reduces the ability of the seal to accommodate high speeds and shortens the life of the seal. Summary of the invention
本发明针对牙轮钻头上述轴承密封中的不足， 采用偏心等宽轴承密封槽， 消除了因轴承 间隙的存在而带来的密封槽宽度的变化， 实现了轴承密封圈在圆周方向的等压缩。 从而降低 了轴承密封圈压缩率的设计要求， 提高了密封圈适应高转速的能力， 延长了密封寿命。 附图说明  The invention aims at the deficiencies in the above bearing seal of the roller bit, and adopts an eccentrically wide bearing seal groove, which eliminates the change of the seal groove width caused by the existence of the bearing gap, and realizes the equal compression of the bearing seal ring in the circumferential direction. Therefore, the design requirement of the bearing ring compression ratio is reduced, the sealing ring is adapted to the high rotation speed, and the sealing life is prolonged. DRAWINGS
图 1 是本发明的一种典型结构图。  BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a typical structural view of the present invention.
图 2 是本发明的圆周方向示意图。  Figure 2 is a schematic view of the circumferential direction of the present invention.
图 3 是本发明的第二种典型结构图。  Figure 3 is a second typical structural diagram of the present invention.
图 4 是本发明的第三种典型结构图。  Figure 4 is a third exemplary structural view of the present invention.
图 5 是本发明的第四种典型结构图。 具体实施方式  Figure 5 is a fourth typical structural view of the present invention. detailed description
图 1是本发明的一种典型结构图。牙掌轴承 1与牙轮内孔 2配合，形成牙轮钻头的轴承。 牙掌轴承包括径向承压圆柱体 5和密封圆柱体 7。 牙轮内孔包括径向承压圆柱体 6和密封圆 柱体 8。 密封槽 3由牙掌轴承密封圆柱体和牙轮内孔密封圆柱体形成。 密封槽 3内装的是一 弹性密封圈 4。当牙轮钻头工作时，在受力侧 F方向受力。牙掌轴承与牙轮内孔在 F侧接触， 在另一侧产生径向间隙 A。 牙掌密封体 7与牙掌承压圆柱体 5间有偏心 C和直径差 B。 直径 差 B等于径向间隙 A。 偏心的方向与受力的方向相同。 偏心的大小 C等于直径差 B的一半。 即， A=B=2C。  BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a view showing a typical structure of the present invention. The palm bearing 1 cooperates with the inner bore 2 of the cone to form a bearing for the roller cone bit. The palm bearing comprises a radially pressurized cylinder 5 and a sealing cylinder 7. The inner bore of the cone includes a radially pressurized cylinder 6 and a sealed cylindrical body 8. The sealing groove 3 is formed by a tooth bearing sealing cylinder and a cone inner sealing cylinder. The sealing groove 3 is provided with an elastic sealing ring 4. When the roller bit is working, it is forced in the direction of the force side F. The palm bearing is in contact with the inner bore of the cone on the F side and a radial gap A on the other side. The palm seal body 7 and the palm-bearing cylinder 5 have an eccentricity C and a diameter difference B. The diameter difference B is equal to the radial gap A. The direction of the eccentricity is the same as the direction of the force. The size of the eccentricity C is equal to half of the diameter difference B. That is, A = B = 2C.
图 2是本发明的圆周方向示意图。 11是牙轮内孔密封圆柱体 8的投影。 12是牙掌轴承承 压圆柱体 5的投影。 Π是牙掌密封圆柱体 7的投影。 14是弹性密封圈。 因偏心 C的存在， 在牙轮钻头工作时， 11和 13是两个同心圆， 由 11和 13形成的密封槽， 其宽度在圆周方向 是不变的。 密封圈 14被压缩安装在密封槽中， 其压缩率也是固定不变的。 也就是说， 密封圈 的压缩率在受力侧和非受力侧是一致的。 设计时不需要为了保证非受力侧的极小压缩率而加 大压缩量。 从而可以将密封圈的压缩率设计在一个较小的范围内。 较小的压缩率， 提高了密 封圈适应高转速的能力， 延长了密封圈的使用寿命。 Figure 2 is a schematic view of the circumferential direction of the present invention. 11 is a projection of the inner ring sealing cylinder 8 of the cone. 12 is a projection of the bearing cylinder 5 of the tooth bearing. Π is the projection of the palm seal cylinder 7. 14 is an elastic seal. Due to the existence of eccentricity C, When the roller bit is in operation, 11 and 13 are two concentric circles, and the seal grooves formed by 11 and 13 have a width which is constant in the circumferential direction. The sealing ring 14 is compressed and mounted in the sealing groove, and its compression ratio is also fixed. That is to say, the compression ratio of the seal ring is uniform on the force side and the non-force side. It is not necessary to increase the amount of compression in order to ensure a very small compression ratio on the non-stress side. Thereby, the compression ratio of the sealing ring can be designed to be in a small range. The small compression ratio increases the ability of the seal to accommodate high speeds and extends the life of the seal.
图 3是本发明的第二种典型结构图。 与图 1的结构相比， 其区别是， 牙掌轴承密封圆柱 体 7的直径不是大于承压圆柱体 5的直径， 而是小于承压圆柱体 5的直径， 小的值 B也等于 径向间隙八。  Figure 3 is a second typical structural view of the present invention. Compared with the structure of Fig. 1, the difference is that the diameter of the crown bearing sealing cylinder 7 is not larger than the diameter of the bearing cylinder 5, but smaller than the diameter of the bearing cylinder 5, and the small value B is equal to the radial direction. Eight gaps.
图 4 是本发明的第三种典型结构图。 与图 1的区别是， 密封件不是单一的密封圈， 而是 机械密封组件 15。  Figure 4 is a third exemplary structural view of the present invention. The difference from Figure 1 is that the seal is not a single seal but a mechanical seal assembly 15.
图 5 是本发明的第四种典型结构图说。 与图 1的区别是， 密封件不是单一的密封圈， 而是 由两个密封圈组成的密封组件 16。  Figure 5 is a fourth exemplary structural diagram of the present invention. The difference from Figure 1 is that the seal is not a single seal but a seal assembly 16 consisting of two seals.
书  Book

Claims

权 利 要 求 书 Claims
、 一种牙轮钻头轴承密封结构， 主要由牙掌轴承、 牙轮内孔、 密封槽、 密封件组成。 The utility model relates to a roller cone bit bearing sealing structure, which mainly comprises a tooth bearing, a toothed inner hole, a sealing groove and a sealing member.
、根据权利要求 1所述的轴承密封结构， 其牙掌轴承上有径向承压圆柱体和位于其根部的密 封圆柱体。 The bearing seal structure according to claim 1, wherein the palm bearing has a radially bearing cylinder and a sealing cylinder at the root thereof.
、根据权利要求 1所述的轴承密封结构， 其牙轮内孔上有径向承压圆柱体和位于其孔口的密 封圆柱体。 ' The bearing sealing structure according to claim 1, wherein the inner bore of the cone has a radially bearing cylinder and a sealing cylinder at the orifice thereof. '
、根据权利要求 2和 3所述的轴承密封结构， 其牙掌轴承径向承压圆柱体与牙轮内孔径向承 压圆柱体之间有一径向间隙 A。 The bearing sealing structure according to claims 2 and 3, wherein the radial bearing cylinder of the crown bearing has a radial gap A between the radially bearing cylinder of the inner bore of the cone.
、根据权利要求 1所述的轴承密封结构， 其密封槽由牙掌轴承密封圆柱体和牙轮内孔密封圆 柱体组成。 The bearing sealing structure according to claim 1, wherein the sealing groove is composed of a palm bearing seal cylinder and a cone inner bore sealing cylinder.
、 根据权利要求 2所述的牙掌轴承， 其径向承压圆柱体与密封圆柱体之间有一偏心 C， 偏心 的方向与牙轮受力方向相同， 偏心的大小等于轴承径向间隙值的一半。 即 C= ( 1/2)A。 、 根据权利要求 6所述的牙掌轴承， 其密封圆柱体直径与径向承压圆柱体直径有差异 B。 差 异值 B等于轴承径向间隙 A。 即 B=A。 The shank bearing according to claim 2, wherein the radial bearing cylinder and the sealing cylinder have an eccentricity C, the direction of the eccentricity is the same as the direction of the force of the cone, and the magnitude of the eccentricity is equal to the radial clearance value of the bearing. half. That is, C = ( 1/2) A. The socket bearing according to claim 6, wherein the diameter of the sealing cylinder differs from the diameter of the radially bearing cylinder B. The difference value B is equal to the bearing radial clearance A. That is, B=A.
PCT/CN2012/000418 2012-03-30 2012-03-30 Eccentric constant-width bearing seal groove of cone bit WO2013143023A1 (en)

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN104948114A (en) * 2015-07-22 2015-09-30 江汉石油钻头股份有限公司 Seal ring with lubricating channel

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US4277110A (en) * 1979-09-24 1981-07-07 Dresser Industries, Inc. Earth boring bit with eccentric seal groove
US4279316A (en) * 1979-10-09 1981-07-21 Dresser Industries, Inc. Earth boring bit with eccentric seal boss
CN2259868Y (en) * 1995-07-31 1997-08-20 江汉石油管理局钻头厂 Teethed wheel type tooth drill bit
CN2727377Y (en) * 2004-06-07 2005-09-21 江汉石油钻头股份有限公司 Roller bit with reinforced palm tip structure
CN201202404Y (en) * 2008-01-30 2009-03-04 天津立林钻头有限公司 Seal device for petroleum drill bearing
CN201358715Y (en) * 2008-12-30 2009-12-09 天津立林钻头有限公司 Oil roller bit floating sealing device
CN101629475A (en) * 2009-08-05 2010-01-20 天津立林钻头有限公司 Floating composite seal device of oil cone bit

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4277110A (en) * 1979-09-24 1981-07-07 Dresser Industries, Inc. Earth boring bit with eccentric seal groove
US4279316A (en) * 1979-10-09 1981-07-21 Dresser Industries, Inc. Earth boring bit with eccentric seal boss
CN2259868Y (en) * 1995-07-31 1997-08-20 江汉石油管理局钻头厂 Teethed wheel type tooth drill bit
CN2727377Y (en) * 2004-06-07 2005-09-21 江汉石油钻头股份有限公司 Roller bit with reinforced palm tip structure
CN201202404Y (en) * 2008-01-30 2009-03-04 天津立林钻头有限公司 Seal device for petroleum drill bearing
CN201358715Y (en) * 2008-12-30 2009-12-09 天津立林钻头有限公司 Oil roller bit floating sealing device
CN101629475A (en) * 2009-08-05 2010-01-20 天津立林钻头有限公司 Floating composite seal device of oil cone bit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104948114A (en) * 2015-07-22 2015-09-30 江汉石油钻头股份有限公司 Seal ring with lubricating channel
CN104948114B (en) * 2015-07-22 2018-01-02 江汉石油钻头股份有限公司 A kind of sealing ring with lubrication channel

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