US3598187A - Turbodrill - Google Patents

Turbodrill Download PDF

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Publication number
US3598187A
US3598187A US35514A US3598187DA US3598187A US 3598187 A US3598187 A US 3598187A US 35514 A US35514 A US 35514A US 3598187D A US3598187D A US 3598187DA US 3598187 A US3598187 A US 3598187A
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US
United States
Prior art keywords
vanes
rotor
stator
fluid
sets
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.)
Expired - Lifetime
Application number
US35514A
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English (en)
Inventor
Jean Mothre
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.)
Entreprise de Recherches et dActivites Petrolieres SA
Original Assignee
Erap
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Filing date
Publication date
Application filed by Erap filed Critical Erap
Application granted granted Critical
Publication of US3598187A publication Critical patent/US3598187A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • E21B4/02—Fluid rotary type drives
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/903—Well bit drive turbine

Definitions

  • ABSTRACT A turbodrill in which the hydraulic power unit consists of a rotor which is centered within a cylindrical stator by an axial thrust bearing, the forces exerted on said axial thrust bearing being balanced irrespective of the nature of the formation by virtue of two systems of vanes separated by a baffle for reversing the direction of flow of the driving fluid. Since the entire quantity of fluid passes successively through the two sets of vanes in opposite directions, the axial thrust forces are balanced on the thrust bearing which centers the rotor irrespective of the variations in loss of load on the drilling head.
  • a turbodrill is driven by means of a drilling fluid which is injected into a drill pipe by means of a pump located at the surface of a well bore and that a turbodrill usually carries a rotor which is attached to a cutting tool or roller bit, said rotor being capable of moving inside a cylindrical stator and being maintained within this latter by means of a thrust bearing.
  • the stator and rotor are intended to support a number of axial turbine stages which operate u nder conditions of constant flow.
  • the turbine therefore exerts on the tool an axial thrust which is the sum of the hydraulic pressure of the fluid and of the weight of the rotor.
  • the stator is attached to a string of drill pipe sections which do not rotate and transmits to the roller bit a thrust which varies as a function of the weight to be applied to said bit.
  • the thrust bearing must accordingly withstand the variations in said thrust.
  • the present invention is intended to avoid such a loss of efficiency by eliminating the axial thrust of the driving portion of the turbine and combining the components which are subject to wear, namely the roller bit and thrust bearing, in a detachable drilling head.
  • This invention is concerned with a turbodrill which is driven by the drilling fluid itself and comprises a hydraulic power unit constituted by a rotor which is centered in a cylindrical stator by means of an axial thrust bearing.
  • Said turbodrill essentially comprises two sets of stationary vanes carried by the stator and each corresponding to one set of moving vanes carried by the rotor and a baffle for reversing the direction of flow of the fluid between the two sets of vanes.
  • the fluid is caused to flow successively and in opposite directions through both sets of vanes prior to arriving at a detachable drilling head which is placed in a removable extension of the stator and coupled for rotation with the rotor only.
  • the number of vanes of each set is such that the resultant axial thrust of the power unit on the thrust bearing is zero.
  • the turbodrill comprises a first set of vanes fixed between the rotor and a sleeve which is coaxial with the stator and which defines a U- shaped passageway for the flow of fluid between said rotor and said stator.
  • the drilling head comprises a rotary shaft having an extension in the form of a splined endpiece disposed in interengaged relation with longitudinal grooves of a recess which is bored in the extremity of the rotor.
  • FIG. 1 is a longitudinal sectional view of a turbodrill
  • FIG. 2 is an enlarged view of the upper portion of said turbodrill
  • FIGS. 3 and 4 are enlarged longitudinal sectional views of two forms of construction of the lower portion of the turbodrill.
  • the turbodrill according to the invention comprises two basic components as shown in FIG. 1, namely a hydraulic power unit 1 and a drilling head 2.
  • the hydraulic power unit comprises a cylindrical body 3 having a top extension in the form of an endpiece 4 for attachment to a drill pipe (not shown in the drawings).
  • Said cylindrical body 3 is adapted to carry two stationary sets of. vanes 5 and 7 and constitutes a stator in conjunction with said vanes.
  • By means of a thrust bearing 6, said cylindrical body is also adapted to support a shaft 8 fitted with two sets of moving vanes 10 and 12 which constitute a rotor.
  • the shaft 8 is pierced at the top and in central alignment with the endpiece 4 by an axial passageway 14 for guiding the drilling fluid which is admitted through said endpiece 4 and is placed at this point within a bearing 16 which seals off the space formed between said shaft and the cylindrical body 3.
  • the passageway 14 opens via curved ducts 18 into a space which is defined around the shaft 8 by a sleeve 20, said sleeve being coaxial with the cylindrical body 3 and attached to this latter by means of spacer members 21 so as to form an annular space 24 between said sleeve and said cylindrical body.
  • Said sleeve 20 is adapted to carry the stationary vanes 5 internally thereof while the shaft 8 is adapted to carry the moving vanes 10 externally thereof, said vanes 5 and 10 being interengaged so as to form at least one axial turbine stage.
  • a communica-' tion is established between said turbine 510 and the space 24 at the top of the sleeve 20 so that the fluid which has entered through the endpiece 4 should thus flow through a double U-shaped loop.
  • Ducts 26 form an extension of the space 24 through a bearing 28 in which the shaft 8 is rotatably mounted and to which the sleeve 20 is rigidly fixed. Said ducts open into the top portion of a second turbine which is formed by the stationary vanes 7 and moving vanes 12 which are carried respectively by the cylindrical body 3 and the shaft 8.
  • the fluid which has entered the top portion of the turbine via the endpiece 4 flows through the passageway 14 within the shaft 8, then upwards within the turbine 5-10, returns in the opposite direction within the spacer 24 and the ducts 26, then passes downwards through the turbine 7-12.
  • the fluid therefore produces an upwardly directed axial thrust within one of said turbines and a downwardly directed thrust within the other turbine.
  • the number of vanes of each set is chosen so that the upwardly directed axial thrust produced by the flow of fluid within the upper set of vanes counterbalances the downwardly directed axial thrust exerted by the fluid which circulates within the second set of vanes as well as the specific weight of the rotor in the drilling fluid.
  • the resultant thrust load on the thrust'bearing 6 is thus practically zero.
  • the essential design function of said thrust bearing is to center the rotor within the cylindrical body 3.
  • the drilling head 2 is coupled to the hydraulic power unit which is formed by the combined assembly of both turbines through which fluid circulates in opposite directions. Accordingly, an axial recess is formed in the extremity of the rotor 8 and provided with longitudinal grooves in which is engaged a splined endpiece 32, said endpiece being rigidly fixed to a shaft 34 which carries the roller bit 35.
  • Said shaft 34 is supported within a cylinder 36 which forms an extension of the cylinder 3 and is screwed on this latter at 38, the top end of said shaft 34 being maintained by a thrust bearing 40 which is similar to the thrust bearing 6 and the bottom end of said shaft being maintained by a bearing 42.
  • the shaft 34 is pierced beneath said thrust bearing 40 so as to form inclined ducts 44 which are extended by an axial passageway 46 and this latter opens into the endpiece to which the roller bit 35 is attached, the fluid which passes out of the lower turbine 7-12 being thus discharged towards said bit by means of said inclined ducts.
  • the bearing 42 serves to guide the shaft 34 within the extension 36 and also to ensure leaktight closure of the fluid circuit beneath the ducts 44.
  • the weight which is applied to the thrust bearing 40 by means of the cylindrical body 3 and its extension 36 and which is reduced by the hydrostatic pressure applied by the driving fluid to that section of the shaft which is located at the level of the bottom bearing 42 is transmitted to the drilling bit 35 by said thrust bearing but this latter is not subjected to any axial force produced by the power unit, only the driving torque being transmitted to the shaft 34.
  • the thrust bearing is subjected to the variations in the load applied to the drilling bit and to the friction forces arising from such variations, thus resulting in a tendency to wear, which is not the case with the thrust bearing 6.
  • the assembly which consists of the drilling head 2 can readily be removed by unscrewing the extension 36 and withdrawing the splined endpiece 32 by sliding as soon as the wear of the thrust bearing 40 is found to be excessive. The thrust bearing can then be replaced.
  • the passageway 44 which passes axially through the shaft 34 of the drilling head is in this case extended to the lower extremity of said head as shown in FIG. 4 and passes through the splined endpiece 32. Said passageway even extends into the rotor 8 by way of a passageway 43 which communicates with the lower set of vanes 7-12 by way ofinclined ducts 45.
  • the lower portion of the cylindrical body 3 is provided in this case above the thrust bearing 6 with a bearing for the leaktight closure of the fluid circuit.
  • the shaft 34 is guided within the interior of the extension 36 both by the thrust bearing 40 and the bearing 42 and by a ball bearing 52 which is disposed at the top end of said shaft.
  • the bearings can be either of the rubber type or of the baffle type and the thrust bearing can consist of rubber discs, balls,
  • rollers or can be ofany other type.
  • the complete drilling head assembly can readily be removed by unscrewing the extension 36 and then withdrawing the splined endpiece 32 by sliding within the recess 30, said drilling head can readily be withdrawn and replaced by another head of the same type without thereby entailing the need to return the turbodrill to the factory.
  • the hydraulic power unit does not have any component which is subject to veritable wear and operates independently of the drilling parameter, namely the weight applied to the bit, said power unit can be employed over an extremely long period of time irrespective of the nature of the operation which is being performed.
  • the stationary and moving sets of vanes can be moved towards each other in order to obtain enhanced efficiency.
  • this turbine can have a lesser number of vanes and consequently be shorter in length than a conventional turbine. Losses of driving torque arising from friction forces are also eliminated and startup operations are made easy.
  • a turbodrill according to claim I wherein the first set of vanes is fixed between the rotor and a sleeve which is coaxial with the stator and which defines a U-shaped passageway for the flow of fluid between said rotor and said stator.
  • a turbodrill according to claim 3 wherein the rotor is pierced by an axial duct for the admission of the fluid and by lateral outlets which are curved in the direction of the first set of vanes or specifically of the U-shaped passageway.
  • a turbodrill according to claim I wherein the space between the sleeve and the stator is adapted to communicate with the second set of vanes.

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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)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Drilling And Boring (AREA)
US35514A 1969-05-13 1970-05-07 Turbodrill Expired - Lifetime US3598187A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR6915506A FR2044241A5 (enrdf_load_stackoverflow) 1969-05-13 1969-05-13

Publications (1)

Publication Number Publication Date
US3598187A true US3598187A (en) 1971-08-10

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Family Applications (1)

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US35514A Expired - Lifetime US3598187A (en) 1969-05-13 1970-05-07 Turbodrill

Country Status (4)

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US (1) US3598187A (enrdf_load_stackoverflow)
DE (1) DE2023484B2 (enrdf_load_stackoverflow)
FR (1) FR2044241A5 (enrdf_load_stackoverflow)
SU (1) SU374855A3 (enrdf_load_stackoverflow)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832088A (en) * 1971-09-20 1974-08-27 Baxter Laboratories Inc Modular pneumatic surgical drill
US3882946A (en) * 1974-04-24 1975-05-13 Rolen Arsenievich Ioannesian Turbodrill
US3930749A (en) * 1974-12-12 1976-01-06 Moisei Timofeevich Gusman Turbodrill
US3938596A (en) * 1972-03-15 1976-02-17 Evgeny Illarinovich Ivanov Turbo-drill
US4646856A (en) * 1983-09-26 1987-03-03 Dismukes Newton B Downhole motor assembly
US4819739A (en) * 1984-08-31 1989-04-11 Dresser Industries, Inc. Fluid actuated rock drill hammer
US4926949A (en) * 1988-12-07 1990-05-22 Drilex Systems, Inc. Thermal shield for drilling motors
US6129160A (en) * 1995-11-17 2000-10-10 Baker Hughes Incorporated Torque compensation apparatus for bottomhole assembly
US20060113114A1 (en) * 2003-04-15 2006-06-01 Feng Jin Drilling tool and method

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4047581A (en) * 1976-12-01 1977-09-13 Kobe, Inc. Multistage, downhole, turbo-powered intensifier for drilling petroleum wells
DE2840809C3 (de) * 1978-09-20 1981-10-29 Christensen, Inc., 84114 Salt Lake City, Utah Meißeldirektantrieb für Tiefbohrwerkzeuge

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3039735A (en) * 1956-10-31 1962-06-19 Turbodrill Internat Corp Motor for subterranean work
US3362488A (en) * 1965-07-12 1968-01-09 Ioanesyan Jury Rolenovich Well drilling system
US3405912A (en) * 1965-06-08 1968-10-15 Mini Petrolului Turbine for drilling oil wells and gas wells

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3039735A (en) * 1956-10-31 1962-06-19 Turbodrill Internat Corp Motor for subterranean work
US3405912A (en) * 1965-06-08 1968-10-15 Mini Petrolului Turbine for drilling oil wells and gas wells
US3362488A (en) * 1965-07-12 1968-01-09 Ioanesyan Jury Rolenovich Well drilling system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832088A (en) * 1971-09-20 1974-08-27 Baxter Laboratories Inc Modular pneumatic surgical drill
US3938596A (en) * 1972-03-15 1976-02-17 Evgeny Illarinovich Ivanov Turbo-drill
US3882946A (en) * 1974-04-24 1975-05-13 Rolen Arsenievich Ioannesian Turbodrill
US3930749A (en) * 1974-12-12 1976-01-06 Moisei Timofeevich Gusman Turbodrill
US4646856A (en) * 1983-09-26 1987-03-03 Dismukes Newton B Downhole motor assembly
US4819739A (en) * 1984-08-31 1989-04-11 Dresser Industries, Inc. Fluid actuated rock drill hammer
US4926949A (en) * 1988-12-07 1990-05-22 Drilex Systems, Inc. Thermal shield for drilling motors
US6129160A (en) * 1995-11-17 2000-10-10 Baker Hughes Incorporated Torque compensation apparatus for bottomhole assembly
US20060113114A1 (en) * 2003-04-15 2006-06-01 Feng Jin Drilling tool and method

Also Published As

Publication number Publication date
SU374855A3 (enrdf_load_stackoverflow) 1973-03-20
DE2023484A1 (enrdf_load_stackoverflow) 1971-11-11
DE2023484B2 (de) 1971-11-11
FR2044241A5 (enrdf_load_stackoverflow) 1971-02-19

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