EP2865894B1 - Dispositif de pompage submersible destiné à être utilisé dans un trou de forage - Google Patents

Dispositif de pompage submersible destiné à être utilisé dans un trou de forage Download PDF

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Publication number
EP2865894B1
EP2865894B1 EP14003254.1A EP14003254A EP2865894B1 EP 2865894 B1 EP2865894 B1 EP 2865894B1 EP 14003254 A EP14003254 A EP 14003254A EP 2865894 B1 EP2865894 B1 EP 2865894B1
Authority
EP
European Patent Office
Prior art keywords
screw pump
bearing
submersible pump
eccentric screw
drive
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.)
Not-in-force
Application number
EP14003254.1A
Other languages
German (de)
English (en)
Other versions
EP2865894A1 (fr
Inventor
Eudes Borchardt
Arthur Zinke
Klaus Heizinger
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.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme GmbH
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 Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP2865894A1 publication Critical patent/EP2865894A1/fr
Application granted granted Critical
Publication of EP2865894B1 publication Critical patent/EP2865894B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/128—Adaptation of pump systems with down-hole electric drives
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/008—Pumps for submersible use, i.e. down-hole pumping
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps 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
    • F04C2/103—Rotary-piston machines or pumps 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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps 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
    • F04C2/107—Rotary-piston machines or pumps 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 with helical teeth
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps 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
    • F04C2/107—Rotary-piston machines or pumps 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 with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps 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 with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type

Definitions

  • the present invention relates to a submersible pump unit for use in a well according to the features of the preamble of claim 1.
  • ESPCP electric submersible screw pump
  • a submersible motor located at the lower end is provided, which drives an eccentric screw pump located above by means of a coupling rod.
  • eccentric screw pumps has the advantage over the conventionally used centrifugal pumps that products with higher viscosity, for example, with higher sand and Paraphinan turnover can be promoted.
  • a bearing arrangement for mounting the coupling rod is usually arranged directly above the submersible motor or above a transmission unit connected to the submersible motor.
  • DE 10258666 A1 describes a submersible pump device for use in a wellbore with a worm or eccentric screw, wherein between the slowly rotating drive and the worm or eccentric screw pump, an axially and radially force-absorbing coupling member is arranged.
  • DE 19848792 C1 describes a submersible pump device for use in a borehole, which comprises a gear and a compensator between the drive and the eccentric screw pump.
  • a gear stage is used to slow down the rotational movement of the input shaft in the transmission housing.
  • the compensator equalizes the lubrication fluid pressure in the transmission housing to the ambient pressure.
  • the compensator is disposed within the gear housing next to the gear stage and integrated into the lubricating fluid circuit.
  • a major disadvantage of these arrangements is that slender and fast-running coupling rods tend to buckle between the drive and screw or eccentric screw due to the prevailing axial force and then start on the housing tube. This leads to friction between coupling rod and housing tube and thus wear of these components, which must be replaced or replaced accordingly frequently.
  • the object of the invention is to eliminate the disadvantages of the prior art, in particular a buckling of the coupling rods is to be prevented due to acting on the coupling rods axial forces.
  • the invention relates to a submersible pump unit for use in a borehole.
  • drill hole is a hole in the ground in order to promote oil and natural gas to understand.
  • the submersible pump unit comprises a screw pump and / or an eccentric screw pump with a longitudinal axis for conveying medium within a riser arranged in the borehole in an upwardly directed conveying direction, that is to say in a conveying direction directed towards the earth's surface.
  • the screw pump and / or eccentric screw pump is preferably driven by a drive, in particular a motor.
  • the submersible pump assembly further includes a bearing assembly. The bearing assembly serves to receive and derive the occurring during operation of the screw pump and / or eccentric screw axial and / or radial forces.
  • the drive via a first coupling rod at one end of the screw pump and / or eccentric screw pump along the longitudinal axis arranged.
  • the bearing assembly is associated with the opposite end of the screw pump and / or eccentric screw along the longitudinal axis via a second coupling rod.
  • the bearing arrangement is thus assigned to the end of the rotor of the worm pump and / or eccentric worm pump facing away from the drive.
  • the drive is preferably arranged below the screw pump and / or eccentric screw pump.
  • a first coupling rod is arranged between the drive and the rotor of the screw pump and / or eccentric screw pump, which transmits the drive energy to the rotor.
  • the bearing arrangement of the submersible pump unit is arranged within the borehole above the screw pump and / or eccentric screw pump.
  • an employed support bearing in O-form This can absorb both axial and radial forces and divert into the surrounding structure, wherein the function of receiving axial and radial forces is divided into a thrust bearing and a radial bearing.
  • the two bearings are braced against each other and there is only a slight tilting play.
  • the bearing arrangement is part of a storage unit.
  • the screw pump and / or eccentric screw pump has a rotor and a stator, wherein a first coupling rod for transmitting the drive energy of the drive is arranged on the rotor between the drive arranged in the downhole and the rotor arranged above the screw pump and / or eccentric screw. Furthermore, a second coupling rod is arranged between the end of the rotor facing away from the drive and the bearing unit.
  • the bearing unit is connected via a fastening device with the second coupling rod and / or with a housing tube surrounding the second coupling rod.
  • the bearing unit may comprise a mechanical seal for sealing the interior of the bearing unit.
  • the sliding ring direction hermetically seals the bearing interior at the lower end of the bearing unit with respect to the conveyed medium.
  • the storage unit is flowed around in the well of funded medium, whereby heat of the bearing assembly is discharged.
  • the bearing unit may further comprise a pressure compensating piston for equalizing the differential pressure between a lubricant of the bearing assembly and the conveyed medium.
  • the pressure balance piston prevents the oil-lubricated bearing unit from being contaminated by contaminated fluid by compensating for the differential pressure between the bearing unit lubricating oil and the pumped fluid.
  • the axial and / or radial forces of the screw pump and / or eccentric screw pump are converted by the bearing unit into a tensile force.
  • the bearing unit instead of supporting the axial force as a compressive force on a bearing arrangement located under the eccentric screw pump, between eccentric screw pump and submersible motor - as conventionally known - this is intercepted in the submersible pump unit according to the invention as a pulling force on a bearing arrangement of the bearing unit located above the screw pump and / or eccentric screw pump and in the flow ,
  • the bearing unit thus serves in particular to protect the coupling rods, since they are relieved of the buckling force.
  • FIG. 1 shows a submersible pump unit 1 with bearing unit 10 for use in a borehole BL.
  • a lining 30 is often provided which stabilizes the borehole BL.
  • the submersible pump unit 1 comprises an eccentric screw pump 3 with a longitudinal axis L, a drive 2, for example a motor M for driving the eccentric screw pump 3, and a bearing assembly 12 for receiving and discharging the axial and / or radial forces occurring during operation of the eccentric screw pump 3.
  • the submersible pump unit 1 is arranged in particular in the borehole BL such that the drive 2 forms the lower end of the submersible pump assembly 1.
  • a riser SR is arranged, in which the liquid flow FS of the pumped medium rises in the conveying direction FR upwards.
  • the eccentric screw pump 3 comprises a pump housing 4 with suction openings 5 for the medium to be conveyed in the conveying direction FR. Furthermore, the eccentric screw pump 3 comprises a stator 7 and a rotor 6. The rotor 6 is connected via a directly driven, arranged in the pump housing 4 coupling rod 8 with the external drive 2. The opposite end of the rotor 6 is connected to the bearing unit 10 via a further coupling rod 9, which is surrounded by a housing tube 20. In particular, the bearing unit 10 thus forms within the borehole BL the upper end of the submersible pump unit 1 and directly adjoins the riser SR.
  • the upper coupling rod 9 is bathed within the housing tube 20 by the liquid flow FS of the pumped medium.
  • the bearing unit 10 is arranged, which in FIG. 2 is shown in detail.
  • a fastening device 40 is provided, which connects the housing tube 20 with the bearing unit 10.
  • FIG. 2 shows a storage unit 10 of a submersible pump unit 1 according to FIG. 1 ,
  • the bearing unit 10 serves in particular to guide the upper coupling rod 9 and to initiate the operation of the eccentric screw pump 3 (cf. FIG. 1 ) occurring axial forces in the surrounding structure.
  • the bearing unit 10 comprises a bearing housing 11 with a bearing arrangement 12 arranged therein.
  • the bearing arrangement 12 causes an axial and radial force-absorbing coupling, which is necessary for the safe operation of the eccentric screw pump 3.
  • This may be, for example, a so-called fixed bearing that can absorb both axial and radial forces and in the surrounding structure, in particular in the bearing housing 11, can derive.
  • a so-called separate bearing arrangement can be used, in which the function recording axial and radial forces is divided into a thrust bearing and a radial bearing.
  • a so-called employed support bearing 13 is used as a bearing assembly 12.
  • thrust bearings and radial bearings is meant a defined bracing of the two bearings against each other.
  • the bearing arrangement 12, 13 can accommodate a greater tilting moment than in an X-arrangement (not shown), since in the O-arrangement the distance of the pressure centers is greater.
  • the upper free end of the bearing unit 10 is arranged and fixed at the lower end of a riser SR. Between bearing assembly 12 and riser SR a pressure compensation piston 15 is provided. With the pressure equalizing piston 15, the differential pressure between the lubricating oil of the bearing assembly 12 and the conveyed medium is compensated. This effectively prevents the oil-lubricated bearing unit 10 is contaminated by contaminated fluid.
  • a slide ring 16 is arranged at the shaft input, that is adjacent to the upper end of the coupling rod 9 and at the lower end or in the lower region of the bearing unit 10.
  • the mechanical seal 16 hermetically seals the interior of the bearing unit 10 to the flow FS of the pumped medium.
  • the storage unit 10 is flowed around by conveying medium, whereby the heat of the bearing assembly 12 of the storage unit 10 is discharged.
  • the axial force is trapped as a tensile force on a located above the eccentric screw 3 and the liquid flow FS bearing unit 10 and thus the underlying coupling rods 8, 9 relieved of the buckling force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (9)

  1. Groupe de pompe submersible (1) destiné à être utilisé dans un trou de forage (BL), comprenant une pompe à vis sans fin et/ou une pompe à vis sans fin excentrique (3) avec un axe longitudinal (L), un entraînement (2) et un agencement de palier (12) pour recevoir et dériver les forces axiales et/ou radiales se produisant lorsque la pompe à vis sans fin et/ou pompe à vis sans fin excentrique (3) fonctionne (nt), caractérisé en ce que l'entraînement est disposé le long de l'axe longitudinal (L) à une extrémité de la pompe à vis sans fin et/ou pompe à vis sans fin excentrique (3) par le biais d'une première barre de couplage (8) et que l'agencement de palier (12) correspond à l'extrémité opposée de la pompe à vis sans fin et/ou pompe à vis sans fin excentrique (3) le long de l'axe longitudinal (L) par le biais d'une seconde barre de couplage (9).
  2. Groupe de pompe submersible (1) selon la revendication 1, dans lequel le groupe de pompe submersible (1) est ainsi disposé dans le trou de forage (BL) que l'entraînement (2) dans le trou de forage (BL) est disposé en-dessous de la pompe à vis sans fin et/ou de la pompe à vis sans fin excentrique (3) et que l'agencement de palier (12) du groupe de pompe submersible (1) à l'intérieur du trou de forage (BL) est disposé au-dessus de la pompe à vis sans fin et/ou de la pompe à vis sans fin excentrique (3).
  3. Groupe de pompe submersible (1) selon la revendication 1 ou 2, dans lequel l'agencement de palier (12) est un palier d'appui (13) mis en place en forme de O.
  4. Groupe de pompe submersible (1) selon l'une des revendications précédentes, dans lequel l'agencement de palier (12) fait partie d'une unité de palier (10).
  5. Groupe de pompe submersible (1) selon la revendication 4, dans lequel la pompe à vis sans fin et/ou la pompe à vis sans fin excentrique (3) présente un rotor (6) et un stator (7), sachant qu'une première barre de couplage (8) est disposée entre le palier (2) et le rotor (6) de la pompe à vis sans fin et/ou de la pompe à vis sans fin excentrique (3) pour transmettre l'énergie d'entraînement de l'entraînement (2) sur le rotor (6), sachant qu'une seconde barre de couplage (9) est disposée entre l'extrémité du rotor (6) de la pompe à vis sans fin et/ou de la pompe à vis sans fin excentrique (3) détourné de l'entraînement (2) et l'unité de palier (10).
  6. Groupe de pompe submersible (1) selon la revendication 5, dans lequel l'unité de palier (10) est reliée à la seconde barre de couplage (9) par le biais d'un dispositif de fixation (40) et/ou à un tube de logement (20) entourant la seconde barre de couplage (9).
  7. Groupe de pompe submersible (1) selon la revendication 6, dans lequel l'unité de palier (10) présente une garniture étanche à anneau glissant (16) entre le dispositif de fixation (40) et l'agencement de palier (12), pour étanchéifier l'espace intérieur de l'unité de palier (10).
  8. Groupe de pompe submersible (1) selon l'une des revendications 4 à 7, dans lequel l'unité de palier (10) dans le trou de forage (BL) est entourée par du fluide transporté, ce par quoi de la chaleur peut être évacuée de l'agencement de palier (12).
  9. Groupe de pompe submersible (1) selon l'une des revendications 4 à 8, dans lequel l'unité de palier (10) comprend un piston de compensation de pression (15) pour compenser la pression différentielle entre un lubrifiant de l'agencement de palier (12) et le fluide transporté.
EP14003254.1A 2013-10-01 2014-09-19 Dispositif de pompage submersible destiné à être utilisé dans un trou de forage Not-in-force EP2865894B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013110849.0A DE102013110849B3 (de) 2013-10-01 2013-10-01 Tauchpumpenaggregat zur Verwendung in einem Bohrloch

Publications (2)

Publication Number Publication Date
EP2865894A1 EP2865894A1 (fr) 2015-04-29
EP2865894B1 true EP2865894B1 (fr) 2016-03-09

Family

ID=51589060

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14003254.1A Not-in-force EP2865894B1 (fr) 2013-10-01 2014-09-19 Dispositif de pompage submersible destiné à être utilisé dans un trou de forage

Country Status (6)

Country Link
US (1) US9670779B2 (fr)
EP (1) EP2865894B1 (fr)
CN (1) CN104514704A (fr)
AU (1) AU2014240219B2 (fr)
BR (1) BR102014024172A2 (fr)
DE (1) DE102013110849B3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11248603B2 (en) * 2019-05-13 2022-02-15 Baker Hughes Oilfield Operations Llc Thrust runner vibration dampening spring in electrical submersible pump
RU206362U1 (ru) * 2021-06-23 2021-09-07 Сергей Александрович Трушков Устройство разгрузки винтового погружного насоса

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3802803A (en) * 1971-10-13 1974-04-09 A Bogdanov Submersible screw pump
DE3345233C2 (de) * 1983-12-14 1985-10-31 Joh. Heinrich Bornemann GmbH & Co KG, 3063 Obernkirchen Exzenterschneckenpumpe zum Fördern von Flüssigkeiten aus Bohrlöchern, insbesondere aus Erdöl-Bohrlöchern
CA2049502C (fr) * 1991-08-19 1994-03-29 James L. Weber Dispositif de positionnement de rotor pour pompe utilisee dans une colonne de production
CN2237712Y (zh) * 1995-05-26 1996-10-16 大庆石油管理局 空心杆旋转螺杆泵套抽汲配套装置
DE19848792C1 (de) * 1998-10-22 2000-05-04 Netzsch Mohnopumpen Gmbh Tauchpumpeneinrichtung zur Verwendung in einem Bohrloch
JP2000290308A (ja) * 1999-04-09 2000-10-17 Shin Etsu Chem Co Ltd 塩化ビニル系重合体の製造方法
JP4277096B2 (ja) * 2002-07-19 2009-06-10 兵神装備株式会社 一軸偏心ねじポンプ
DE10258666B4 (de) * 2002-12-13 2007-10-18 Netzsch Oilfield Products Gmbh Tauchpumpeneinrichtung zur Verwendung in einem Bohrloch
CN2695700Y (zh) * 2004-04-19 2005-04-27 西安海兴曲杆泵业工程有限公司 高压、大流量单螺杆泵连接结构
US8132618B2 (en) * 2006-09-08 2012-03-13 National Oilwell Varco, L.P. Systems for retarding rod string backspin
NO327503B1 (no) * 2007-09-20 2009-07-27 Agr Subsea As Eksenterskruepumpe med flere pumpeseksjoner
DE202008011078U1 (de) * 2008-08-20 2008-10-23 Armatec Fts-Armaturen Gmbh & Co. Kg Doppeltbewegliche Kuppelstange
US8726981B2 (en) * 2011-06-01 2014-05-20 Baker Hughes Incorporated Tandem progressive cavity pumps

Also Published As

Publication number Publication date
CN104514704A (zh) 2015-04-15
US20150093277A1 (en) 2015-04-02
BR102014024172A2 (pt) 2015-10-06
US9670779B2 (en) 2017-06-06
AU2014240219A1 (en) 2015-04-16
EP2865894A1 (fr) 2015-04-29
DE102013110849B3 (de) 2014-12-11
AU2014240219B2 (en) 2017-08-10

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