EP0100627A1 - Pompe hélicoidale - Google Patents

Pompe hélicoidale Download PDF

Info

Publication number
EP0100627A1
EP0100627A1 EP83304217A EP83304217A EP0100627A1 EP 0100627 A1 EP0100627 A1 EP 0100627A1 EP 83304217 A EP83304217 A EP 83304217A EP 83304217 A EP83304217 A EP 83304217A EP 0100627 A1 EP0100627 A1 EP 0100627A1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
pump
shaft
stators
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.)
Granted
Application number
EP83304217A
Other languages
German (de)
English (en)
Other versions
EP0100627B1 (fr
Inventor
Stanley Ashbourne Eaton Payne
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.)
NOV Process and Flow Technologies UK Ltd
Original Assignee
Mono Pumps Ltd
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 Mono Pumps Ltd filed Critical Mono Pumps Ltd
Publication of EP0100627A1 publication Critical patent/EP0100627A1/fr
Application granted granted Critical
Publication of EP0100627B1 publication Critical patent/EP0100627B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F04C2/1076—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 where one member orbits or wobbles relative to the other member which rotates around a fixed axis
    • 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

Definitions

  • Each of these types includes an inner member, usually a rotor, and an outer member, which is usually in the form of a stator.
  • the rotor has an external helical gear form with n starts.
  • the stator has a complementary internal helical gear form with n ⁇ 1 starts.
  • One of the said members, usually the stator, is of resilient material.
  • Such pumps are capable of delivering against high delivery pressures, and are suitable for borehole pumps. They require good sealing and hence adequate initial interference between inner and outer members, so that interference and hence sealing will not be lost completely when the resilient member deforms under pump delivery pressure. However, such adequate initial interference may result in a high starting torque being required. Such a high starting torque may be a drawback when the pump is to be hand-operated.
  • the invention provides a helical gear pump having an inlet and an outlet, and which includes
  • the stators may be mounted in an outer sleeve having connecting means for connection to a delivery outlet. It may be a stator remote from the connecting means which has its outer wall unconstrained along a portion of its length. There may be provided a plurality of stators which have their outer walls unconstrained against radial inward movement along portions of their lengths.
  • the invention extends to a borehole pump installation, which includes
  • the source of rotary power may be provided by manually-operable means which includes an arm operatively connected to the shaft, the arm having a handle whereby the shaft may be rotated about its axis relative to the rising main.
  • the manually-operable means may include a pedestal mounted over and connected to the upper end of the rising main, the upper end of the pedestal supporting a bearing for the arm and having a clutch device to permit rotation of the arm in one direction only, about the rotational axis of the rotor.
  • the pedestal may have a water outlet below the level of the bearing, and a sealing gland below the bearing, but above the water outlet, the shaft being adapted to pass sealingly through the sealing gland.
  • the water outlet may be in the form of a spout directed downwardly from the pedestal.
  • An upwardly directed baffle may be provided at the inner end of the spout.
  • the invention extends to manually-operable means which includes a pedestal having mounting means for mounting it over the mouth of a borehole, and over the upper end of the rising main of an installation as described, and which has an arm operatively connectable via the connecting means to the shaft of the said installation, the arm being rotatably supported at the upper end of the pedestal about an axis which in use is co-axial with the shaft of the said installation.
  • the rotational support of the arm by the pedestal may be provided by a bearing, and the pedestal may have a sealing gland below the bearing to permit the shaft to pass sealingly therethrough.
  • the arm may be provided with gripping means for co- operating with the connecting means, the gripping means including two bushes in a transverse bore intersected by a longitudinal bore to accommodate the shaft, and the two bushes in use being urged together by a bolt passing through them to grip the shaft where it intersects the transverse bore.
  • the source of rotary power may be provided by a windmill-operated rotary drive having its output operatively connected to the shaft.
  • a helical gear pump which includes at least two resilient outer members arranged in series around an inner member, the inner and outer members being adapted to rotate and orbit relative to each other about a longitudinal axis
  • the outer members may be stators and the inner member may be a rotor, the rotor being adapted to rotate and orbit inside the stators.
  • a borehole generally indicated by reference numeral 10. It has a borehole casing 12 within which a rising main 14 is centrally located by stabilizers 16 arranged at axially spaced intervals within the casing 12.
  • a helical gear pump 18, according to the invention, is mounted at the lower end of the rising main 14.
  • a foot valve and strainer 20 is provided below the pump 18.
  • the pump 18 has a shaft 22 located centrally within the rising main 14 by bobbin bearings 24. Rotary power is applied to the shaft 22 by means of manually-operable means in the form of a hand pump arm 26 of a hand pump head, generally indicated by reference numeral 27.
  • the hand pump arm 26 is rotatably mounted on pedestal 28 which is mounted by means of a base member 30 over the borehole 10.
  • the pedestal 28 has a delivery or outlet pipe 32 which is provided with a baffle 34 on the inside of the pedestal so as to prevent the introduction of foreign matter into the pedestal 28 from outside, via the outlet pipe 32.
  • the base member 30 is mounted on a concrete block 36 cast into the soil 38 around the mouth of the borehole 10.
  • the pump 18 comprises a cylindrical casing 40 connected to the lower end of the rising main 14 (not shown).
  • stators 42.1 and 42.2 are mounted sealingly in tandem around the rotor 44.
  • the ring 45 is arranged at the suction end of the stator 42.2.
  • the rotor 44 is connected to the lower end of the shaft 22.
  • the stator 42.1 is moulded into casing 42.11 which is attached to the casing 40.
  • the stator 42.2 is moulded into ring 45 which is attached to the casing.
  • a clearance space 48 is provided around the upper end of the stator 42.2.
  • the rotor 44 will be arranged to have conventional radial interference with the stator 42.1, and little radial interference with the stator 42.2.
  • the stators 42.1 and 42.2 are also arranged in timed relationship with each other relative to the rotor 44 and are held in position in the casing 40. Under no load, the radial interference between the rotor 44 and the inner surface of the stator 42.2 will be less than the radial interference between the rotor 44 and the inner surface of the stator 42.1.
  • the shaft 22 is sufficiently flexible to take up the eccentricity of the rotor orbiting within the stator. It is therefore not necessary to have flexible connectors, such as universal joints and so on, in line with shaft 22.
  • the shaft 22 is made up of a number of sections joined end-to-end.
  • stator 42.3 is also sealingly mounted in similar fashion to the stator 42.2 within the casing 40.
  • Rotor 44 and stator 42.2 of Figure 3 operate in the same way as described for the stator 42.2 and the rotor 44 of Figure 2.
  • the stators 42.2 and 42.3 of Figure 3 are also arranged in timed relationship relative to each other and relative to the rotor 44, and are held in position in the casing 40.
  • the delivery pressure at the outlet from the stator 42.3 will act on the outside of the stator in the clearance space 48 and will balance to some degree the internal pressure inside the stator 42.3. Thus, sealing interference between the stator 42.3 and the rotor 44 will be substantially maintained so that delivery can take place even under a high head.
  • a hand pump head 27 which includes the pedestal 28 rotatably supporting the arm 26 via anti-friction bearing 60.
  • the arm 26 has a ratchet device 62 to prevent it from being turned in the wrong direction.
  • the teeth for the ratchet device 62 and bearing 60 are mounted in a plug 64 which is located in the upper end of the pedestal 28.
  • the shaft 22 passes through seals 66 which engage sealingly with the shaft 22 along its outer surface.
  • the shaft 22 is locked in relation to. the arm 26 by gripping means which includes bushes 68 and 70 urged together by a bolt 72 passing with clearance through them.
  • the bushes have faces 68.1 and 70.1 urged into gripping relationship with the shaft 22 by means of the bolt 72.
  • the bushes are located axially in a bore 74 which is intersected by the shaft 22. If desired, the ends of the bore 72 are closed off by plugs 76 and 78 to prevent tampering with the locking arrangement on the shaft 22.
  • the bolt 72 is provided with a socket head 72.1, further to discourage tampering if the cover 76 should be removed. In Figure 4 the plug 78 is shown removed.
  • the stator has three starts and the rotor has two starts.
  • the lower ends of the casing is conveniently threaded to engage with a foot valve or a foot valve and strainer 20.
  • the direction of rotation of the rotor is arranged to take place in such a direction that water will be pumped upwardly.
  • the upper ends of the stators 42.2 will be subjected to partial delivery pressure.
  • the upper ends of the stators 42.1 and 42.3 will, on the other hand, be subjected to full delivery pressure. This is the pressure which is applied to the clearance spaces 48.
  • the interference between the rotor and the stators 42.2 and 42.3 can be minimal.
  • pressure builds up however, a tendency for the stators to expand under internal pressure can be cancelled or counteracted or compensated for by the external pressure around the outside of the stators, in the clearance spaces mentioned. It is thus possible to start with minimal interference between the rotor and the stators, yet without the danger of losing necessary sealing interference, as pressure builds up inside the stators.
  • compensating stators 42.2 and 42.3 Because of the compensating effect which the delivery pressure has on the outer surfaces of the stators 42.2 and 42.3, they may for brevity be referred to as compensating stators.
  • the hand pump embodiment shown in the drawings shows the handle connected directly to the pump shaft without an intermediate gear ratio. It is possible to have the pump shaft driven via a step-down or step-up drive to drive it slower or faster than the handle. Such a drive may be provided by chain and sprockets, V-belts and pulleys, or a gear drive with toothed gearwheels.
  • the pump shaft may also be driven by a rotary windmill-driven shaft directly or via a step-up or step- down drive.
  • a pump according to the invention having a compensating stator, also has advantages in pumping hot liquids or in pumping cold liquids which later become hot.
  • the moulded-to metal stator 42.1 In order to allow for temperature, the moulded-to metal stator 42.1 must have greater initial clearance at low temperature. This would result in poor performance in the cold condition, if used alone, because of excessive clearance.
  • the addition of a compensating stator 42.2 ensures adequate performance in the cold condition. As temperature rises, so the stator 42.1 expands, thereby taking up the greater initial clearance and providing required interference and hence good sealing at the final operating temperature.
  • helical gear pumps having stators arranged in series in accordance with the invention, have low starting torques in practice yet have adequate deliveries even at high heads and at low speeds, without excessive torque requirements.
  • helical gear pumps are very suitable for use as hand pumps on boreholes.
  • a pump having a series mounting of compensating stators has an increased efficiency over a pump having a single compensating stator of a length equivalent to the series-mounted compensating stators.

Landscapes

  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP83304217A 1982-07-20 1983-07-20 Pompe hélicoidale Expired EP0100627B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA825185 1982-07-20
ZA825185 1982-07-20

Publications (2)

Publication Number Publication Date
EP0100627A1 true EP0100627A1 (fr) 1984-02-15
EP0100627B1 EP0100627B1 (fr) 1987-05-20

Family

ID=25576174

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83304217A Expired EP0100627B1 (fr) 1982-07-20 1983-07-20 Pompe hélicoidale

Country Status (10)

Country Link
EP (1) EP0100627B1 (fr)
JP (1) JPS5974385A (fr)
AU (1) AU554747B2 (fr)
BR (1) BR8303901A (fr)
DE (1) DE3371674D1 (fr)
ES (1) ES524252A0 (fr)
GB (1) GB2124305B (fr)
MW (1) MW3283A1 (fr)
NZ (1) NZ204931A (fr)
ZW (1) ZW16083A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2696792A1 (fr) * 1992-10-13 1994-04-15 Inst Francais Du Petrole Système de pompage comportant une pompe volumétrique à grand débit.
RU2249726C2 (ru) * 2003-03-24 2005-04-10 Брот Александр Робертович Погружная насосная установка
WO2009040442A1 (fr) * 2007-09-28 2009-04-02 Shell Internationale Research Maatschappij B.V. Procédé pour améliorer une récupération d'un fluide d'hydrocarbures
US11759212B2 (en) 2015-01-27 2023-09-19 Michael Zhadkevich Devices and techniques for vascular compression

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5820354A (en) * 1996-11-08 1998-10-13 Robbins & Myers, Inc. Cascaded progressing cavity pump system
GB2338268A (en) * 1998-02-24 1999-12-15 Orbit Pumps Ltd Stator assembly
RU2247264C2 (ru) * 2003-03-24 2005-02-27 Брот Александр Робертович Погружная насосная установка
US7214042B2 (en) * 2004-09-23 2007-05-08 Moyno, Inc. Progressing cavity pump with dual material stator
CN109763978A (zh) * 2019-03-12 2019-05-17 北京雷神博峰信息技术有限责任公司 一种车载电动手摇一体泵
CN114320884B (zh) * 2021-11-10 2024-06-14 浙江环誉泵业科技有限公司 一种航空航天用高速高温高效燃油泵

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2408109A (en) * 1945-03-13 1946-09-24 Alden Speare S Sons Co Pump
US2621605A (en) * 1945-10-12 1952-12-16 Clayton Mark & Company Pump
US2826152A (en) * 1955-08-30 1958-03-11 Robbins & Myers Helical gear pump with bellows stator
US3347169A (en) * 1966-09-26 1967-10-17 Sargent Industries Rotary well pump
DE2418967A1 (de) * 1974-04-19 1975-10-30 Netzsch Mohnopumpen Gmbh Verdraengerpumpe
US3982858A (en) * 1973-11-14 1976-09-28 Smith International Corporation, Inc. Segmented stator for progressive cavity transducer
US3999901A (en) * 1973-11-14 1976-12-28 Smith International, Inc. Progressive cavity transducer
FR2385919A1 (fr) * 1977-03-30 1978-10-27 Roth Peter Pompe pour l'extraction de liquides d'un recipient
FR2463299A1 (fr) * 1979-08-13 1981-02-20 Michel Durand Pompe verticale a traction manuelle, eolienne, a moteur ou autre pour pompe a grande profondeur

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB446291A (en) * 1933-10-30 1936-04-27 Alfred Lanser Improvements in rotary pumps
GB1067014A (en) * 1964-10-30 1967-04-26 Unitex Ltd Improvements in helical gear pumps
DE1728143A1 (de) * 1968-08-30 1972-03-30 Max Streicher Exzenterschneckenpumpe
DE2817280A1 (de) * 1978-04-20 1979-10-25 Streicher Foerdertech Stator fuer exzenterschneckenpumpen

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2408109A (en) * 1945-03-13 1946-09-24 Alden Speare S Sons Co Pump
US2621605A (en) * 1945-10-12 1952-12-16 Clayton Mark & Company Pump
US2826152A (en) * 1955-08-30 1958-03-11 Robbins & Myers Helical gear pump with bellows stator
US3347169A (en) * 1966-09-26 1967-10-17 Sargent Industries Rotary well pump
US3982858A (en) * 1973-11-14 1976-09-28 Smith International Corporation, Inc. Segmented stator for progressive cavity transducer
US3999901A (en) * 1973-11-14 1976-12-28 Smith International, Inc. Progressive cavity transducer
DE2418967A1 (de) * 1974-04-19 1975-10-30 Netzsch Mohnopumpen Gmbh Verdraengerpumpe
FR2385919A1 (fr) * 1977-03-30 1978-10-27 Roth Peter Pompe pour l'extraction de liquides d'un recipient
FR2463299A1 (fr) * 1979-08-13 1981-02-20 Michel Durand Pompe verticale a traction manuelle, eolienne, a moteur ou autre pour pompe a grande profondeur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2696792A1 (fr) * 1992-10-13 1994-04-15 Inst Francais Du Petrole Système de pompage comportant une pompe volumétrique à grand débit.
RU2249726C2 (ru) * 2003-03-24 2005-04-10 Брот Александр Робертович Погружная насосная установка
WO2009040442A1 (fr) * 2007-09-28 2009-04-02 Shell Internationale Research Maatschappij B.V. Procédé pour améliorer une récupération d'un fluide d'hydrocarbures
US11759212B2 (en) 2015-01-27 2023-09-19 Michael Zhadkevich Devices and techniques for vascular compression

Also Published As

Publication number Publication date
JPS5974385A (ja) 1984-04-26
GB2124305A (en) 1984-02-15
DE3371674D1 (en) 1987-06-25
AU1692783A (en) 1984-01-26
EP0100627B1 (fr) 1987-05-20
BR8303901A (pt) 1984-02-28
ES8405901A1 (es) 1984-06-16
ZW16083A1 (en) 1984-02-08
GB2124305B (en) 1985-08-29
AU554747B2 (en) 1986-09-04
MW3283A1 (en) 1985-02-13
GB8319576D0 (en) 1983-08-24
NZ204931A (en) 1986-06-11
ES524252A0 (es) 1984-06-16

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