WO1987004486A1 - Tapered friction bearing assembly - Google Patents

Tapered friction bearing assembly Download PDF

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Publication number
WO1987004486A1
WO1987004486A1 PCT/US1986/002319 US8602319W WO8704486A1 WO 1987004486 A1 WO1987004486 A1 WO 1987004486A1 US 8602319 W US8602319 W US 8602319W WO 8704486 A1 WO8704486 A1 WO 8704486A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
bearing
radial
bearing means
fluid flow
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.)
Ceased
Application number
PCT/US1986/002319
Other languages
French (fr)
Inventor
Bela Geczy
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Smith International Inc
Original Assignee
Smith International Inc
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 Smith International Inc filed Critical Smith International Inc
Priority to BR8607097A priority Critical patent/BR8607097A/en
Publication of WO1987004486A1 publication Critical patent/WO1987004486A1/en
Priority to NO873983A priority patent/NO873983L/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • 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
    • E21B23/00—Apparatus for displacing, setting, locking, releasing or removing tools, packers or the like in boreholes or wells
    • E21B23/04—Apparatus for displacing, setting, locking, releasing or removing tools, packers or the like in boreholes or wells operated by fluid means, e.g. actuated by explosion
    • E21B23/0419—Apparatus for displacing, setting, locking, releasing or removing tools, packers or the like in boreholes or wells operated by fluid means, e.g. actuated by explosion using down-hole motor and pump arrangements for generating hydraulic pressure
    • 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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/003—Bearing, sealing, lubricating 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
    • 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 subject invention pertains generally to drilling tools and more particularly to a bearing assembly for accomodating the forces generated in a down hole motor used for example, in the oil drilling arts.
  • Typical bearing materials have included poly-crystalline diamonds, ceramics, and tungsten carbide matrix. It has appeared desirable to the inventor to improve over the prior art bearing structures in order to extend the lifetime of bearings in such apparatus.
  • a bearing assembly having tapered or canted bearing surfaces which absorb both radial and thrust loads.
  • the design provides for a certain amount of fluid flow through the bearing structure with a central radial bearing serving to restrict fluid flow and to eliminate drive shaft deformation in the preferred embodiment.
  • FIG. 1 is a diagramatic illustration of a down hole drill motor according to the prior art.
  • FIG. 2 is a cross sectional drawing illustrating the preferred embodiment of the invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
  • FIG. 1 illustrates a prior art down hole motor structure wherein the preferred embodiment finds application.
  • the structure includes a progressive cavity motor 13, a coupling 15, a drive shaft 17, and a drill bit 19.
  • the drive shaft 17 is born by a bearing assembly comprising bearings 21 and 23.
  • bearings 21 and 23 typically one of these bearings is a radial bearing and the other is a thrust bearing.
  • radial forces arise from the eccentric motion of the coupling 15 as it is driven by a progressive cavity motor and from the drilling force on the drill bit 19.
  • Thrust forces are generated for example by the pressure differential between points P2 and P3 in FIG. 1.
  • the pressure differential across the bearing assembly is for example, on the order of 200 to 2,000 pounds per square inch (PSI) .
  • PSI pounds per square inch
  • FIG. 2 illustrates the preferred embodiment of a tapered friction bearing assembly.
  • the assembly includes an off-bottom thrust and radial bearing 25, 27; a flow restrictor radial bearing 29, 31; and an on-bottom thrust and radial bearing 33 and 35.
  • Each inner bearing element 25, 29, 35 is attached to the drive shaft 17 of the down hole motor.
  • the outer bearing elements 27, 31, 33 are attached to a housing 39 which is threadably connected to a bottom nut 41.
  • Locks 43 and a lock ring 45 serve to attach the bearings.
  • the inner bearing elements 25, 29, and 35 are further held in position by a shaft cap 47 and are locked to the drive shaft 17 by the eccentric lock surface 50.
  • the opposing bearing surfaces 49 may be of any suitable bearing surface construction. Such construc ⁇ tions include poly-crystalline diamond, ceramic and tungsten carbide matrix.
  • Flow grooves 53 are formed in the surfaces 49, 51. These grooves 53 have a width selected to provide sufficient flow of drilling fluid ("mud") to cool and lubricate the bearings.
  • the flow gap 54 between the middle radial bearing elements 29, 31 determines the maximum flow possible. Sufficient pressure drop across the bearings, on the order of minimum 200 PSI, is required to assure sufficient flow of cooling fluid.
  • the off-bottom thrust and radial bearing 25, 27 accomodates the forces on the drive shaft 17 when the drive shaft is driven while the drill bit 19 is off-bottom, i.e. , disengaged from a drilling opera ⁇ tion.
  • the on-bottom thrust and radial bearing 33, 35 accomodates the forces on the drive shaft 17 when the drill bit 19 is on-bottom, engaged in a drilling operation.
  • the radial bearing 29, 31 serves to prevent bending of the drive shaft 17- which would otherwise occur as a result of the varying force pattern to which the drive shaft 17 is exposed. Prevention of bending increases the fatigue lifetime of the system.
  • the angle of the taper of the bearing elements 25, 27 is determined by the angle with respect to vertical of the resultant force vector on the drive shaft 17 in the off-bottom position.
  • the angle of the on-bottom thru.st and radial bearing 33, 35 with respect to vertical is determined to match the angle of the resultant force vector typically expected to be experienced .by the drive shaft 17 in its running, on-bottom mode. It will be observed that the drive shaft 17 will ride up o ⁇ down with respect to the housing 39, depending on whether the drill string" is in the off-bottom or on-bottom mode and otherwise in response to the forces experienced by the drive shaft 17.
  • the optimum force balance of course is where the drilling parameters are such that the bearings are required to carry no load, i.e. , where the drive shaft "floats.”
  • the structure just described thus accomodates both radial and thrust forces, while preventing bending of the drive shaft 17.
  • the structure is usable in a wide variety of applications including both turbine driven and progressive cavity down hole motors.
  • the just described preferred embodiment is susceptible to numerous modifications and adaptations without departing from the scope and spirit of the invention. Therefore, it is to be understood, that with ⁇ in the scope of the appended claims, the invention may be practiced other than as specifically described herein.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Geochemistry & Mineralogy (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

A bearing structure including first (33, 35) and second (25, 27) tapered bearing surfaces for accommodating on-bottom and off-bottom thrust and radial forces on a drive shaft (17) in a down hole drilling environment and further including a radial bearing (29, 31) mounted between the first (33, 35) and second (25, 27) tapered bearings for restricting bending of the drive shaft (17).

Description

Λ
TAPERED FRICTION BEARING ASSEMBLY
BACKGROUND OF THE INVENTION
5 1. Field of the Invention
The subject invention pertains generally to drilling tools and more particularly to a bearing assembly for accomodating the forces generated in a down hole motor used for example, in the oil drilling arts.
10 The design of bearing assemblies which will withstand the hostile environments and force loads typically encountered in down hole well drilling present a continuing challenge to the industry. The extremely high temperatures encountered preclude the successful
15 application of sealed bearing technology as it currently exists. Thus, the prior art has turned to bearing structures exposed to the drilling fluids passing through the motor.
20 2. Description of the Prior Art
In the prior art, a pair of bearings have typically been provided to accomodate the drive shaft and attendant forces thereon. The bearings have been separated such that one bearing accomodates radial forces
25 only and the second accomoda es thrust loads only.
Typical bearing materials have included poly-crystalline diamonds, ceramics, and tungsten carbide matrix. It has appeared desirable to the inventor to improve over the prior art bearing structures in order to extend the lifetime of bearings in such apparatus.
SUMMARY OF THE INVENTION
It is therefore an object of the invention to provide an improved bearing structure.
It is another object of the invention to provide a bearing structure capable of handling both the radial and thrust loads created in a down hole motor.
It is yet another object of the invention to provide a bearing assembly with a longer life than those currently available in the state of the art.
These and other objects are achieved by a bearing assembly having tapered or canted bearing surfaces which absorb both radial and thrust loads. The design provides for a certain amount of fluid flow through the bearing structure with a central radial bearing serving to restrict fluid flow and to eliminate drive shaft deformation in the preferred embodiment.
BRIEF DESCRIPTION OF THE DRAWINGS The preferred embodiment for implementing the just summarized invention will now be described in conjunction with the drawings of which:
FIG. 1 is a diagramatic illustration of a down hole drill motor according to the prior art; and
FIG. 2 is a cross sectional drawing illustrating the preferred embodiment of the invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
FIG. 1 illustrates a prior art down hole motor structure wherein the preferred embodiment finds application. As known in the art, the structure includes a progressive cavity motor 13, a coupling 15, a drive shaft 17, and a drill bit 19. The drive shaft 17 is born by a bearing assembly comprising bearings 21 and 23. Typically one of these bearings is a radial bearing and the other is a thrust bearing. In the structure of FIG. 1, radial forces arise from the eccentric motion of the coupling 15 as it is driven by a progressive cavity motor and from the drilling force on the drill bit 19. Thrust forces are generated for example by the pressure differential between points P2 and P3 in FIG. 1. The pressure differential across the bearing assembly is for example, on the order of 200 to 2,000 pounds per square inch (PSI) .
FIG. 2 illustrates the preferred embodiment of a tapered friction bearing assembly. The assembly includes an off-bottom thrust and radial bearing 25, 27; a flow restrictor radial bearing 29, 31; and an on-bottom thrust and radial bearing 33 and 35. Each inner bearing element 25, 29, 35, is attached to the drive shaft 17 of the down hole motor. The outer bearing elements 27, 31, 33 are attached to a housing 39 which is threadably connected to a bottom nut 41. Locks 43 and a lock ring 45 serve to attach the bearings. The inner bearing elements 25, 29, and 35 are further held in position by a shaft cap 47 and are locked to the drive shaft 17 by the eccentric lock surface 50.
The opposing bearing surfaces 49 may be of any suitable bearing surface construction. Such construc¬ tions include poly-crystalline diamond, ceramic and tungsten carbide matrix. Flow grooves 53 are formed in the surfaces 49, 51. These grooves 53 have a width selected to provide sufficient flow of drilling fluid ("mud") to cool and lubricate the bearings. The flow gap 54 between the middle radial bearing elements 29, 31 determines the maximum flow possible. Sufficient pressure drop across the bearings, on the order of minimum 200 PSI, is required to assure sufficient flow of cooling fluid. In operation, the off-bottom thrust and radial bearing 25, 27 accomodates the forces on the drive shaft 17 when the drive shaft is driven while the drill bit 19 is off-bottom, i.e. , disengaged from a drilling opera¬ tion. The on-bottom thrust and radial bearing 33, 35 accomodates the forces on the drive shaft 17 when the drill bit 19 is on-bottom, engaged in a drilling operation. The radial bearing 29, 31 serves to prevent bending of the drive shaft 17- which would otherwise occur as a result of the varying force pattern to which the drive shaft 17 is exposed. Prevention of bending increases the fatigue lifetime of the system. ,
The angle of the taper of the bearing elements 25, 27 is determined by the angle with respect to vertical of the resultant force vector on the drive shaft 17 in the off-bottom position. Similarly, the angle of the on-bottom thru.st and radial bearing 33, 35 with respect to vertical is determined to match the angle of the resultant force vector typically expected to be experienced .by the drive shaft 17 in its running, on-bottom mode. It will be observed that the drive shaft 17 will ride up oτ down with respect to the housing 39, depending on whether the drill string" is in the off-bottom or on-bottom mode and otherwise in response to the forces experienced by the drive shaft 17. The optimum force balance of course is where the drilling parameters are such that the bearings are required to carry no load, i.e. , where the drive shaft "floats."
The structure just described thus accomodates both radial and thrust forces, while preventing bending of the drive shaft 17. The structure is usable in a wide variety of applications including both turbine driven and progressive cavity down hole motors. As will be appreciated, the just described preferred embodiment is susceptible to numerous modifications and adaptations without departing from the scope and spirit of the invention. Therefore, it is to be understood, that with¬ in the scope of the appended claims, the invention may be practiced other than as specifically described herein.

Claims

CLAIMSWhat is Claimed is:
1. A drive assembly comprising; a drive shaft; a first bearing means for mounting said drive shaft having respective moving and stationary bearing surfaces angled with respect to the axis of said drive shaft for accomodating both thrust and radial forces on said dr.ive shaft .
2. The drive assembly of claim 1 further including a second bearing means for mounting said drive shaft having respective first and second adjacent bearing surfaces angled with respect to said drive shaft.
3. The drive assembly of claim 2 further including a radial bearing means for mounting said drive shaft.
4. The bearing assembly of claim 3 wherein said radial bearing means is mounted between said first and second bearing means.
5. The drive assembly of claim 4 wherein the respective moving and stationary surfaces and respective first and second surfaces are spaced to provide for fluid flow and wherein said radial bearing means provides a fluid flow path for communicating fluid flow between said first and second radial bearing means.
6. The drive assembly of claim 5 wherein said bearing means includes respective bearing faces and wherein the separation between said bearing faces determines the flow of fluid through said first and second radial bearing means.
7. The drive assembly of claim 6 wherein said drive shaft is hollow and wherein fluid is provided to said fluid flow path from a flow channel means for conducting fluid flow into the interior of said drive shaft.
8. Drilling apparatus comprising: a progressive cavity motor; a drive shaft having a central axis; a coupling means connecting said motor to said drive shaft; and a first bearing having a first rotating bearing surface attached to said drive shaft and a first stationary bearing surface, said first surfaces being substantially parallel and canted at a first angle with respect to the axis of said drive shaft for absorbing both radial and thrust loads on said drive shaft.
9. The drilling apparatus of claim 8 further including a second bearing having a second rotating bearing surface attached to said drive shaft and a second stationary bearing surface, said second surfaces being substantially parallel to one another and canted at a second angle with respect to the axis of said drive shaft.
10. The drilling apparatus of claim 9 wherein said first and second angles are respectively selected to accomodate off-bottom and on-bottom forces on said drive shaft .
11. The drilling apparatus of claim 10 further including a radial bearing means mounted between said first and second bearings.
12. The drilling apparatus of claim 11 wherein said radial bearing means functions to prevent bending of said drive shaft.
13. The drilling apparatus of claim 12 wherein said first and second bearings and said bearing means include respective communicating fluid flow channels.
PCT/US1986/002319 1986-01-28 1986-10-27 Tapered friction bearing assembly Ceased WO1987004486A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
BR8607097A BR8607097A (en) 1986-01-28 1986-10-27 DRIVE SET AND DRILLING EQUIPMENT
NO873983A NO873983L (en) 1986-01-28 1987-09-23 CONIC FRICTION STORAGE UNIT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/823,344 US4657090A (en) 1986-01-28 1986-01-28 Tapered friction bearing assembly
US823,344 1986-01-28

Publications (1)

Publication Number Publication Date
WO1987004486A1 true WO1987004486A1 (en) 1987-07-30

Family

ID=25238496

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1986/002319 Ceased WO1987004486A1 (en) 1986-01-28 1986-10-27 Tapered friction bearing assembly

Country Status (5)

Country Link
US (1) US4657090A (en)
EP (1) EP0263109A4 (en)
BR (1) BR8607097A (en)
CA (1) CA1265783A (en)
WO (1) WO1987004486A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2313633A (en) * 1996-05-30 1997-12-03 Samsung Electronics Co Ltd Conic fluid bearing
RU2132980C1 (en) * 1998-06-01 1999-07-10 Дальневосточный государственный технический рыбохозяйственный университет Bearing unit

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8709380D0 (en) * 1987-04-21 1987-05-28 Shell Int Research Downhole drilling motor
KR960000986B1 (en) * 1989-10-02 1996-01-15 가부시끼가이샤 윙· 하이세라 Ceramic bearing
USH1192H (en) 1990-10-26 1993-06-01 Exxon Production Research Company Low-torque centralizer
US5253939A (en) * 1991-11-22 1993-10-19 Anadrill, Inc. High performance bearing pad for thrust bearing
GB9400362D0 (en) * 1994-01-11 1994-03-09 Brewis Roderick C Drilling apparatus
US6481894B1 (en) * 2001-02-23 2002-11-19 Lord Corporation Pitch bearing
US8210747B2 (en) * 2005-08-26 2012-07-03 Us Synthetic Corporation Bearing elements
US7703982B2 (en) * 2005-08-26 2010-04-27 Us Synthetic Corporation Bearing apparatuses, systems including same, and related methods
US8764295B2 (en) 2006-08-16 2014-07-01 Us Synthetic Corporation Bearing elements, bearing assemblies and related methods
US7998573B2 (en) * 2006-12-21 2011-08-16 Us Synthetic Corporation Superabrasive compact including diamond-silicon carbide composite, methods of fabrication thereof, and applications therefor
US7870913B1 (en) 2007-07-18 2011-01-18 Us Synthetic Corporation Bearing assemblies, and bearing apparatuses and motor assemblies using same
US8496075B2 (en) * 2007-07-18 2013-07-30 Us Synthetic Corporation Bearing assemblies, bearing apparatuses using the same, and related methods
RU2397379C1 (en) * 2009-04-23 2010-08-20 Николай Лейбович Полей Downhole motor spindle support
EP3626928B1 (en) 2010-01-28 2023-05-17 Halliburton Energy Services, Inc. Bearing assembly
US8899356B2 (en) 2010-12-28 2014-12-02 Dover Bmcs Acquisition Corporation Drill bits, cutting elements for drill bits, and drilling apparatuses including the same
US9840325B2 (en) * 2012-06-26 2017-12-12 Bell Helicopter Textron Inc. Dual series pitch link bearing
US9010679B2 (en) * 2012-06-26 2015-04-21 Bell Helicopter Textron Inc. Hybrid spherical and thrust bearing
WO2015139107A1 (en) * 2014-03-21 2015-09-24 Halliburton Energy Services, Inc. Bearing assembly including a focal bearing and load sharing thrust bearings
US10538983B2 (en) * 2014-08-06 2020-01-21 Schlumberger Technology Corporation Milling tools with a secondary attrition system

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FR1171398A (en) * 1957-01-14 1959-01-26 Turbine for soil drilling
US2919960A (en) * 1958-10-15 1960-01-05 Gen Motors Corp Precision spindle
CA620490A (en) * 1961-05-23 Tiraspolsky Wladimir Motor or turbine for sub-surface work
US3391965A (en) * 1967-09-06 1968-07-09 Sealol Fluid radial and thrust bearing
US3484143A (en) * 1968-08-16 1969-12-16 Skf Ind Inc Elastohydrodynamic sliding bearings
US3606501A (en) * 1968-12-24 1971-09-20 Gamet Products Ltd Hydrostatic bearing assemblies
US4410054A (en) * 1981-12-03 1983-10-18 Maurer Engineering Inc. Well drilling tool with diamond radial/thrust bearings
US4518049A (en) * 1981-05-01 1985-05-21 Vsesojuzny Nauchno-Issledovatelsky Institut Burovoi Tekhniki Bottom hole motor for driving rock-breaking tool

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GB1143960A (en) * 1966-09-21 1969-02-26 Arneson Harold Elias Grant Improved hydrostatic bearing
US4546836A (en) * 1983-10-26 1985-10-15 Dresser Industries, Inc. Downhole motor fluid flow restrictor

Patent Citations (8)

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Publication number Priority date Publication date Assignee Title
CA620490A (en) * 1961-05-23 Tiraspolsky Wladimir Motor or turbine for sub-surface work
FR1171398A (en) * 1957-01-14 1959-01-26 Turbine for soil drilling
US2919960A (en) * 1958-10-15 1960-01-05 Gen Motors Corp Precision spindle
US3391965A (en) * 1967-09-06 1968-07-09 Sealol Fluid radial and thrust bearing
US3484143A (en) * 1968-08-16 1969-12-16 Skf Ind Inc Elastohydrodynamic sliding bearings
US3606501A (en) * 1968-12-24 1971-09-20 Gamet Products Ltd Hydrostatic bearing assemblies
US4518049A (en) * 1981-05-01 1985-05-21 Vsesojuzny Nauchno-Issledovatelsky Institut Burovoi Tekhniki Bottom hole motor for driving rock-breaking tool
US4410054A (en) * 1981-12-03 1983-10-18 Maurer Engineering Inc. Well drilling tool with diamond radial/thrust bearings

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See also references of EP0263109A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2313633A (en) * 1996-05-30 1997-12-03 Samsung Electronics Co Ltd Conic fluid bearing
GB2313633B (en) * 1996-05-30 1998-04-15 Samsung Electronics Co Ltd Conic fluid bearing & head drum & spindle motor each including the same
US5873657A (en) * 1996-05-30 1999-02-23 Samsung Electronics Co., Ltd. Conic fluid bearing and head drum and spindle motor each including the same
RU2132980C1 (en) * 1998-06-01 1999-07-10 Дальневосточный государственный технический рыбохозяйственный университет Bearing unit

Also Published As

Publication number Publication date
BR8607097A (en) 1988-04-19
EP0263109A4 (en) 1990-01-11
CA1265783A (en) 1990-02-13
US4657090A (en) 1987-04-14
EP0263109A1 (en) 1988-04-13

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