EP0265521B1 - Rotor eines bohrlochschneckenmotors und dessen herstellung - Google Patents

Rotor eines bohrlochschneckenmotors und dessen herstellung Download PDF

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Publication number
EP0265521B1
EP0265521B1 EP86902578A EP86902578A EP0265521B1 EP 0265521 B1 EP0265521 B1 EP 0265521B1 EP 86902578 A EP86902578 A EP 86902578A EP 86902578 A EP86902578 A EP 86902578A EP 0265521 B1 EP0265521 B1 EP 0265521B1
Authority
EP
European Patent Office
Prior art keywords
rotor
tubular blank
screw
forming element
housing
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
EP86902578A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0265521A1 (de
EP0265521A4 (de
Inventor
Anatoly Mikhailovich Kochnev
Andrei Nikolaevich Vshivkov
Vladimir Borisovich Goldobin
Samuil Solomonovich Nikomarov
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.)
PERMSKY FILIAL VSESOJUZNOGO NAUCHNO-ISSLEDOVATELSKOGO INSTITUTA BUROVOI TEKHNIKI
Original Assignee
PERMSKY FILIAL VSESOJUZNOGO NAUCHNO-ISSLEDOVATELSKOGO INSTITUTA BUROVOI TEKHNIKI
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 PERMSKY FILIAL VSESOJUZNOGO NAUCHNO-ISSLEDOVATELSKOGO INSTITUTA BUROVOI TEKHNIKI filed Critical PERMSKY FILIAL VSESOJUZNOGO NAUCHNO-ISSLEDOVATELSKOGO INSTITUTA BUROVOI TEKHNIKI
Priority to AT86902578T priority Critical patent/ATE75521T1/de
Publication of EP0265521A1 publication Critical patent/EP0265521A1/de
Publication of EP0265521A4 publication Critical patent/EP0265521A4/de
Application granted granted Critical
Publication of EP0265521B1 publication Critical patent/EP0265521B1/de
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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/101—Moineau-type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/27—Manufacture essentially without removing material by hydroforming
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49236—Fluid pump or compressor making
    • Y10T29/49242—Screw or gear type, e.g., Moineau type
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/49336—Blade making
    • Y10T29/49339—Hollow blade
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49805—Shaping by direct application of fluent pressure

Definitions

  • the present invention relates to drilling technology and relates in particular to screw bottom drive units for drilling oil and gas wells, namely a method and an apparatus for producing a rotor of a screw bottom drive unit and the rotor itself.
  • a screw-type soleplate drive with a multi-start rotor which is designed in the form of a multi-start all-metal screw in which the number of turns of the screw surface (the screw teeth) is more than one (SU copyright document No. 926209).
  • the rotor is housed in a stator that has a multi-start internal helical surface with a number of gears that exceeds the number of gears of the rotor by one; this screw surface is produced on a covering from a resiliently elastic material, such as rubber, glued to the inner surface of the stator housing.
  • the rotor axis is offset relative to the stator axis coinciding with the drive axis by an eccentricity amount that is half the height of the rotor and stator teeth, while the axial pitch ratio of the screw teeth of the rotor and the stator is equal to the number of teeth ratio of these parts.
  • the rotor executes an orbital movement, the rotor axis rotating counterclockwise relative to the stator axis at an angular velocity ⁇ 1 while the rotor itself rotates clockwise around its own axis at an angular velocity of ⁇ 2.
  • the angular velocity ⁇ 1 is equal to the angular velocity ⁇ 2 multiplied by the number of rotor teeth, and the centrifugal force acting on the rotor is proportional to the rotor mass and the square of the angular velocity ⁇ 1.
  • the multi-speed rotor of the drive described above is manufactured according to a gear milling method using a metal-cutting tool, such as a hob cutter. This method is expensive, not powerful enough, it does not guarantee a high surface quality of the rotor teeth and requires complicated and expensive methods to carry it out Equipment - machine tools and tools. To improve the surface quality of the rotor, the working surfaces of the rotor must then be polished or ground, which is what a complicated configuration of the rotor surface and a large length of the rotor is a difficult technological task.
  • a screw downhole sole drive with a multi-start hollow rotor is also known.
  • the rotor is rigidly connected to a coupling by means of a threaded connection (see the book by Gusman MT, inter alia, "screw-borehole sole drives for drilling holes", 1981, “Nedra”, (Moscow), p . 125 to 188).
  • the metal in the middle of the rotor is removed.
  • the metal is removed by drilling a central hole in the rotor. This can also be achieved by using a thick-walled tube block for the manufacture of the rotor.
  • the centrifugal forces acting on the rotor can be somewhat reduced by reducing the dynamics of the transverse vibrations of the rotor and of the entire drive.
  • a significant amount of metal remains in the body of the teeth of the rotor in its peripheral area, which leads to the creation of significant centrifugal forces during operation of the drive and to a shortening of its service life.
  • the connection of the rotor with an articulated or a flexible shaft by means of a coupling provided with threaded connections is not reliable, because during operation of the drive under the action of dynamic forces a decoupling can take place.
  • the screw teeth of the rotor of the drive mentioned are also produced in the gear milling process, which has the disadvantages mentioned above.
  • the design of the rotor as a closed whole part or from a thick-walled tube also requires a high consumption of stainless steel.
  • the drives equipped with the rotor described above are characterized by a relatively low efficiency and not a high output, because the work of these drives results in high mechanical losses caused by the self-heating of the stator rubber.
  • a more efficient method for producing a single-start rotor for Moineau screw pumps is known (US-A-2 464 011).
  • the method consists in the deformation of a pipe block on a shaping screw surface due to the pressure of a flowing medium on the pipe block.
  • the method is carried out with the aid of a device in whose housing a shaping element with a shaping surface is accommodated, within which the tube block is located.
  • the shaping screw surface is provided on the inner surface of the shaping element, which simultaneously fulfills the function of the housing and consists of several axial partial surfaces.
  • the pressure of the flowing medium is generated in the cavity of the tube block arranged within the sealed shaping element.
  • the shaping of the rotor of a single screw pump takes place in several stages, with the tube block being lifted out of the shaping element for annealing treatment after each stage in order to reduce the hardness and to remove internal stresses.
  • the disadvantages of the known method and the devices for its implementation are low quality counted the outer working surface of the rotor, on which traces of the division of the shaping element are left, an additional machining of the outer surface of the rotor using special equipment being required to eliminate these traces.
  • Another disadvantage of the above-mentioned method and the device is the complicated production of the inner surfaces of the divisible shaping element as well as a complicated covering of the shaping screw surfaces in parting planes. These disadvantages are particularly noticeable in the manufacture of rotors with a large ratio of length to diameter, which makes it impossible to manufacture multi-speed rotors using the method described above.
  • Another disadvantage of the known method is that a high hydrostatic pressure of the flowing medium is required because the tube block is subjected to significant tensile deformations. This also results in a high energy intensity of the process.
  • the invention has for its object to provide a method and an apparatus for producing a rotor of a bottom hole drive and a rotor, which make it possible to simplify the manufacture of the rotor and to increase the manufacturing performance by realizing design features of the rotor, and by the rotor to improve the energy characteristic of the drive, to reduce friction losses.
  • the essence of the method for producing the rotor, according to which a tube block is deformed on a shaping surface by the pressure action of a flowing medium is that a shaping element, the outer surface of which constitutes a shaping surface, is arranged inside the tube block, and the Pressure of the flowing medium is applied to the pipe block from the outside.
  • the tube block is preferably formed in two stages, in the first stage the tube block is given the shape of a screw polyhedron with rounded tips, in which the diameter of the circumference is slightly larger than the diameter of the circumference of the finished rotor and the number of the side surfaces is equal to the number of gears of the screw surface of the rotor, and the final shaping of the rotor screw surface is carried out in the second stage.
  • the essence of the device for producing the rotor according to the method set out above in the housing of which a shaping element with a shaping surface and housings are accommodated, which together with the housing form a cavity for the supply of a flowing medium under pressure, that the shaping element is attached to centering bushings within the housing and that the shaping surface is carried out on the outer surface of the shaping element, the centering bushings having fitting sections which are arranged for a sliding fit of the ends of the tube block.
  • each centering bushing has a shoulder adjoining its fitting section, against which the pipe block located on the fitting section is supported and in which an annular groove is provided, in which the width of the pipe block is essentially the same, and in which one Seal is housed.
  • the shaping element in the housing and to provide a shaping element which serves for pre-shaping and which is designed in the form of a screw polyhedron with rounded tips, in which the diameter of the circumference is somewhat larger than the diameter of the circumference of the shaping element Element for final shaping and the number of side surfaces of the number of gears of the rotor screw surface is the same.
  • the essence of the invention is also that in a rotor of a bottom hole drive, which is designed as a hollow body with a substantially constant wall thickness in the form of a multi-start screw with a number of teeth of the screw surface of over 1 and rigidly connected with a coupling, according to the invention
  • the ratio between the length of the outer line of the rotor cross section and the length of the circumference described relative to this outer line is essentially in a range from 0.9 to 1.05.
  • Such an embodiment of the rotor enables an improvement in the energy characteristic of the drive, a reduction in the transverse vibrations, an increase in the strength of the rotor under torsional and bending stresses, a reduction in the mass and the metal intensity of the rotor, a reduction in the consumption of stainless steel and a Improving the quality of the rotor to be manufactured.
  • the rotor 1 is one of the main parts of a screw-hole sole drive (FIG. 1) and is designed in the form of a multi-start screw provided with external screw teeth 2 with a number of gears (teeth) of the screw surface of more than 1.
  • the rotor 1 is arranged within a stator 3, which has a coating 4 made of a resilient, elastic material such as rubber.
  • the Inner screw surface of the lining 4 forms screw teeth 5, the number of which exceeds the number of teeth of the rotor 1 by one.
  • the axis O1 (Fig. 2) of the rotor 1 is offset relative to the axis O2 of the stator 3 by the eccentricity "e".
  • the rotor 1 (FIG. 1)
  • the rotor 1 (FIGS. 3, 4) is designed as a hollow body according to the present invention and contains a tubular casing 12 (housing) and a coupling 13 (FIG. 3) rigidly connected thereto for connection to the flexible shaft 8 (FIG. 1 ).
  • the coupling 13 (FIG. 3) is provided with elements 14, for example with threads, for the connection of the flexible shaft 8.
  • the attachment can also be carried out by other known methods, for example by welding, using a cone.
  • the coupling 13 is preferably fastened in the tubular casing 12 by compressing the tubular casing 12 on the profiled outer surface of the coupling 13, on which recesses 15 are provided. This is done according to the procedure described above.
  • the recesses 15 can have different shapes, ie they can be designed as radial, non-continuous openings, longitudinal or transverse grooves or flattenings, ring or spiral grooves and their combinations. It is important that those formed on the profiled outer surface of the coupling 13 during the compression of the end section of the tubular casing 12 Approaches 16 with the recesses 15 of the coupling 13 for transmitting the torsional moment and the axial load in engagement.
  • an embodiment of the recess 15 is shown as an annular groove with a diameter d 1, which is arranged eccentrically with respect to the cylindrical outer surface 17 of the clutch 13.
  • the ratio between the length of the outer line 18 in the cross section of the rotor 1 and the length of the circumference 19 described relative to this outer line is essentially in a range from 0.9 to 1.05.
  • the rotor according to the invention has the following mode of operation.
  • a rinsing liquid is supplied from the surface of the day via the drill pipe 11 (FIG. 1)
  • the rotor 1 is set in rotation under the action of an unbalanced liquid pressure on its side screw surface, and it rolls on the teeth of the stator 3.
  • the torsional moment to be generated on the rotor and the axial load are transmitted to the shaft 6 of the support assembly 7 via the flexible shaft 8, which is connected to the rotor 1 via the coupling 13.
  • the rotation is transmitted from the shaft 6 of the support group 7 to the rock destruction tool 9.
  • the above-described screw bottom drive rotor is made as follows.
  • the shaping element with the shaping multi-start external screw surface is inserted into a tube shell, which has previously been machined on the outer surface to the required surface quality (ground, polished), the ends of the tube shell are hermetically sealed against the shaping element, while simultaneously centering them guaranteed and pressure is generated from the outside around the pipe shell by a flowing medium, eg mineral oil.
  • a flowing medium eg mineral oil
  • the shaping of the rotor teeth is expedient according to the present method performed in two stages.
  • the tube shell is partially deformed to the incomplete tooth height, giving the tube block the shape of a screw polyhedron with rounded tips, and in the second stage, the final shape of the screw surface of the rotor is carried out.
  • the use of a reduced size of the radial deformation ensures that the screw surface is produced in a quality-appropriate form, which has no folds and no other injuries.
  • the first stage can be carried out at a reduced pressure of the flowing medium, because in this stage the task of overcoming the stability of the cylindrical shape of the tube block and preforming the screw surface, which has the same number of gears and the same pitch of the helical line as in the finished rotor, is solved.
  • the tube block in the form of a screw polyhedron obtained after machining in the first stage is subjected to a final shaping for the production of the screw surface of the rotor by the same method, uz a pressure of the flowing medium is generated from the outside around the tube block with the shaping element located therein.
  • a method for producing the rotor proves to be optimal, in which, at the same time as the screw surface of the rotor is shaped, its tubular casing 12 is connected to the coupling 13.
  • the coupling 13 with a profiled outer surface is inserted into the tubular casing before it is compressed; the outer surface is provided with recesses of this or that shape, for example with radial non-through openings, longitudinal or transverse grooves or flats, ring or screw grooves or combinations thereof.
  • lugs are formed on the inner surface thereof which engage with the cutouts engage the clutch, thereby ensuring transmission of the torsional moment generated on the tube shell of the rotor and the axial forces to the clutch and then to the flexible shaft.
  • the method described above for producing the rotor of a screw-type borehole sole drive can be carried out by means of a device which is shown in longitudinal section in FIG. 6 and in cross section in FIG. 7.
  • the device contains a thick-walled tubular housing 20, in which a shaping element 21 is arranged, which is centered relative to the housing 20 by means of centering bushes 22, 22 '(FIG. 6).
  • the shaping outer surface of the shaping element 21 is designed in the form of screw teeth 23, which have the same direction and pitch of the helix with the rotor to be manufactured, the equidistant size being equal to the wall thickness ⁇ (FIG. 4) of the tube block 24.
  • On the outer surface of the centering bushes 22 (Fig.
  • fitting sections 25 are provided, on which the tube blocks 24 are placed with their ends.
  • the centering bushes 22, 22 ' are provided at the points of their coupling with the housing 20 with seals 26, 26', which are designed, for example, in the form of O-shaped rubber rings.
  • the centering bushing 22 has a shoulder adjoining the fitting section 25 with an annular end groove 27, in which there is a seal 28 made of rubber or another elastic material. The width of the groove is essentially the same as the thickness " ⁇ " of the tube block 24.
  • the pipe block 24 is arranged on the fitting sections 25 (only one fitting section is shown in FIG.
  • the shaping element 21 (FIG. 6) is designed to be replaceable in two stages during the manufacture of the rotor.
  • the pre-shaping element 21 '(Fig. 8) is in the form of a screw polyhedron, which has the shape of a polyhedron with rounded tips in cross section and a reduced height h1 of the screw teeth and an enlarged outer diameter d2 compared to the sizes h2 and d3 of the final shaping element 21 has.
  • 8 shows superimposed outer lines of the cross sections of the shaping elements 21 'and 21 for the preliminary and final shaping. The device is assembled and operated as follows.
  • the shaping element 21 is introduced into the tube block 24 of the rotor, the surface of which has previously been machined (ground, polished) to the surface quality required for the rotor.
  • a centering bushing 22 ′ is attached to one end of the shaping element 21, the end section of the tube block 24 being brought up to the fitting section on the centering bushing 22 ′ at the same time.
  • the second centering bushing 22 is attached to the free end of the shaping element 21, the fitting section of this centering bushing being inserted into the tube block 24, but the outer surface of the centering bushing 22 being inserted into the housing 20.
  • the assembled parts are fastened in the housing 20 by means of the nuts 30 until the end faces of the tube block 24 are pressed into the body of the rubber seals 28 to a certain extent.
  • a flowing medium for example a mineral oil
  • the cylindrical tube block 24 loses its stability under the influence of the external pressure and is compressed over the shaping screw surfaces of the shaping element 21 to form rotor screw teeth on the outer surface of the tube block 24.
  • the gaps 26 between the housing 20 and the centering bushes 22 are hermetically sealed (similar to the bushing 22 '), while the hermetic sealing of the gaps between the centering bushings 22, 22' and the pipe block 24 is thereby achieved in the initial stage that the end faces of the tube block 24 are pressed into the rubber seals 28 with force.
  • the gap between the pipe block 24 and the fitting sections 25 of the centering bushings 22, 22 ' is sealed as a result of the hydraulic compression of the pipe block 24 on these fitting sections.
  • the pressure is released; the device is disassembled and the shaping element 21 is removed from the tubular casing of the rotor.
  • Fig. 9 shows an embodiment of the method for producing the rotor of a bottom hole drive while simultaneously pressing the clutch 13.
  • one end of the shaping element 21 is attached in the housing 20 by means of the centering bush 34, in which the clutch 13 is located, the The outer surface serves as a seat for the tube block 24 and is provided with a recess in the form of an eccentric groove.
  • the coupling is compressed at the same time; an extension is formed on the inner surface of the tubular casing, which fills the recess 15 of the coupling 13 and engages with it during the transmission of the torsional moment and the axial load.
  • the compression of the outer surface of the coupling 13 by means of the tube block 24 under the high pressure effect ensures a hermetic seal of the connection.
  • the present invention can be used to provide high-speed screw-bottomed drives with improved energy characteristics and operating characteristics for drilling oil and gas wells with high efficiency.

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  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (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)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Cereal-Derived Products (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Drilling And Boring (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Hydraulic Motors (AREA)
  • Press Drives And Press Lines (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Earth Drilling (AREA)
  • Supercharger (AREA)
  • Turning (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP86902578A 1986-01-31 1986-01-31 Rotor eines bohrlochschneckenmotors und dessen herstellung Expired - Lifetime EP0265521B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86902578T ATE75521T1 (de) 1986-01-31 1986-01-31 Rotor eines bohrlochschneckenmotors und dessen herstellung.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SU1986/000008 WO1987004753A1 (en) 1986-01-31 1986-01-31 Rotor of downhole screw motor, method and device for making thereof

Publications (3)

Publication Number Publication Date
EP0265521A1 EP0265521A1 (de) 1988-05-04
EP0265521A4 EP0265521A4 (de) 1989-03-14
EP0265521B1 true EP0265521B1 (de) 1992-04-29

Family

ID=21616965

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86902578A Expired - Lifetime EP0265521B1 (de) 1986-01-31 1986-01-31 Rotor eines bohrlochschneckenmotors und dessen herstellung

Country Status (9)

Country Link
US (1) US4909337A (ru)
EP (1) EP0265521B1 (ru)
JP (1) JPH0633702B2 (ru)
AT (1) ATE75521T1 (ru)
DE (1) DE3685113D1 (ru)
DK (1) DK476087A (ru)
NO (1) NO172003C (ru)
PT (1) PT82181B (ru)
WO (1) WO1987004753A1 (ru)

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US5135059A (en) * 1990-11-19 1992-08-04 Teleco Oilfield Services, Inc. Borehole drilling motor with flexible shaft coupling
JP3650183B2 (ja) * 1995-10-13 2005-05-18 栃木富士産業株式会社 スクリューロータの加工方法
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ATE485128T1 (de) 2007-04-18 2010-11-15 Nat Oilwell Varco Lp Antriebssysteme und-verfahren mit einer spindel mit langer reichweite
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US8777598B2 (en) 2009-11-13 2014-07-15 Schlumberger Technology Corporation Stators for downwhole motors, methods for fabricating the same, and downhole motors incorporating the same
US9347266B2 (en) * 2009-11-13 2016-05-24 Schlumberger Technology Corporation Stator inserts, methods of fabricating the same, and downhole motors incorporating the same
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US9309884B2 (en) 2010-11-29 2016-04-12 Schlumberger Technology Corporation Downhole motor or pump components, method of fabrication the same, and downhole motors incorporating the same
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CN104563972B (zh) * 2015-01-12 2017-11-14 重庆科技学院 小功率深井抽油机
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JP6818324B2 (ja) * 2017-06-29 2021-01-20 国立大学法人 東京大学 海洋資源揚鉱装置およびこれを用いた海洋資源の揚鉱方法
JP6810937B2 (ja) * 2017-06-29 2021-01-13 国立大学法人 東京大学 海洋資源揚鉱装置およびこれを用いた海洋資源の揚鉱方法
EP3499038B1 (en) * 2017-12-14 2020-07-08 Services Pétroliers Schlumberger Stator and rotor profile for improved power section performance and reliability
CN109915044B (zh) * 2019-03-22 2023-11-21 中国地质大学（北京） 一种装配式螺杆钻具金属定子轴向加工装配工艺

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Publication number Publication date
DE3685113D1 (de) 1992-06-04
PT82181B (pt) 1992-05-29
ATE75521T1 (de) 1992-05-15
DK476087D0 (da) 1987-09-11
US4909337A (en) 1990-03-20
DK476087A (da) 1987-09-11
JPS63502292A (ja) 1988-09-01
PT82181A (pt) 1986-09-16
EP0265521A1 (de) 1988-05-04
NO873890L (no) 1987-09-16
NO172003C (no) 1993-05-26
EP0265521A4 (de) 1989-03-14
WO1987004753A1 (en) 1987-08-13
JPH0633702B2 (ja) 1994-05-02
NO172003B (no) 1993-02-15
NO873890D0 (no) 1987-09-16

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