US20100092317A1 - Uniaxial Eccentric Screw Pump - Google Patents

Uniaxial Eccentric Screw Pump Download PDF

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Publication number
US20100092317A1
US20100092317A1 US12/519,964 US51996407A US2010092317A1 US 20100092317 A1 US20100092317 A1 US 20100092317A1 US 51996407 A US51996407 A US 51996407A US 2010092317 A1 US2010092317 A1 US 2010092317A1
Authority
US
United States
Prior art keywords
rotor
stator
driving
uniaxial eccentric
screw pump
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.)
Abandoned
Application number
US12/519,964
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English (en)
Inventor
Nobuhisa Suhara
Tetsuo Nomachi
Teruaki Akamatsu
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.)
Heishin Sobi KK
Original Assignee
Heishin Sobi KK
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 Heishin Sobi KK filed Critical Heishin Sobi KK
Assigned to HEISHIN SOBI KABUSHIKI KAISHA reassignment HEISHIN SOBI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NOMACHI, TETSUO, AKAMATSU, TERUAKI, SUHARA, NOBUHISA
Publication of US20100092317A1 publication Critical patent/US20100092317A1/en
Abandoned 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/0408—Passive magnetic bearings
    • F16C32/0423—Passive magnetic bearings with permanent magnets on both parts repelling each other
    • F16C32/0429—Passive magnetic bearings with permanent magnets on both parts repelling each other for both radial and axial load, e.g. conical magnets
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons

Definitions

  • the present invention relates to a uniaxial eccentric screw pump which is capable of transferring various fluids, such as gases, liquids, and powder, and in which a rotor and a stator separately rotate.
  • the driven magnet 7 and the stator 3 rotate in the same direction as the driving magnet 8 according to the rotation of the driving magnet 8 .
  • an inner surface forming the inner hole 3 a of the stator 3 presses an outer surface of the rotor 2 in the direction of rotation of the stator 3 , and this causes the rotor 2 to rotate in the same direction as the stator 3 .
  • spaces 10 formed in the stator 3 move from a suction port 6 a side to a discharge port 6 b side. Therefore, for example, a liquid can be suctioned from the suction port 6 a , and the suctioned liquid can be discharged from the discharge port 6 b.
  • Patent Document 1 Japanese Laid-Open Patent Application Publication SHO 63-302189
  • the conventional uniaxial eccentric screw pump 1 shown in FIG. 12 is configured such that the stator 3 is rotated in the predetermined direction by the electric motor, the inner surface forming the inner hole 3 a of the stator 3 presses the outer surface of the rotor 2 in the direction of rotation of the stator 3 , and this causes the rotor 2 to rotate in the same direction as the stator 3 , such that the inner surface forming the inner hole 3 a of the stator 3 and the outer surface of the rotor 2 inevitably contact each other. As a result, these contact portions wear away.
  • the present invention was made to solve the above problems, and an object of the present invention is to provide a uniaxial eccentric screw pump capable of transferring and filling fluids while realizing high flow rate accuracy, low pulsation, and long life.
  • the stator has a double thread internal screw type inner hole, a cross-sectional shape of the inner hole is elliptical, a cross-sectional shape of the rotor is circular, a ratio of a pitch of the rotor to a pitch of the inner hole is 1 to 2, and a ratio of a rotating speed of the rotor to a rotating speed of the stator is 2 to 1.
  • the rotor and the stator can be rotated in the same direction about their respective central axes.
  • a shaft sealing structure (such as a sealing member) for sealing the rotor driving shaft from the rotor becomes unnecessary. With this, it is possible to realize cost reduction, easy maintenance, and improvement of the durability performance of the uniaxial eccentric screw pump. In addition, it is possible to simplify disassembling, assembling, and cleaning operations.
  • the uniaxial eccentric screw pump according to the invention recited in claim 7 is configured such that the rotor driving portion causes the rotor to rotate and the stator driving portion causes the stator to rotate with the rotor and the stator not contacting each other.
  • the uniaxial eccentric screw pump according to the invention recited in claim 8 is configured such that: the stator has a double thread internal screw type inner hole or a triple thread internal screw type inner hole, and a cross-sectional shape of the inner hole is an elliptical shape or a substantially triangle shape each of whose three corners is a circular-arc shape; the rotor is a single thread external screw type or a double thread external screw type, and a cross-sectional shape of the rotor is a circular shape or a substantially oval shape; a ratio of a pitch of the rotor to a pitch of the inner hole is 1 to 2 or 2 to 3; and a ratio of a rotating speed of the rotor to a rotating speed of the stator is 2 to 1 or 3 to 2.
  • the stator is made of engineering plastic, and the rotor is made of a metal, the change in size due to the temperature change can be comparatively suppressed as compared to the rotator and stator which are made of rubber. With this, it is possible to suppress the deterioration of the flow rate accuracy due to the temperature change.
  • one or both of the rotor and the stator are rotatably supported by the magnetic noncontact bearings capable of receiving both the radial load and the thrust load. Therefore, as compared to the case of using the bearings capable of receiving the radial load and the bearings capable of receiving the thrust load, it is possible to simplify the configuration and comparatively reduce the volume of the uniaxial eccentric screw pump.
  • FIG. 7 show a magnetic pole type power transmission structure included in the uniaxial eccentric screw pump according to Embodiment 2 of the present invention.
  • FIG. 7( a ) is a diagram showing a driving magnetic pole portion
  • FIG. 7( b ) is a diagram showing a driven magnetic pole portion.
  • the stator 13 is formed to have a substantially short cylindrical shape having a double thread internal screw type inner hole 13 a for example.
  • a longitudinal cross-sectional shape of the inner hole 13 a is elliptical.
  • the stator 13 is made of engineering plastic, such as Teflon (trademark), polyacetal, or cast nylon.
  • the stator 13 is hermetically attached to an inside of a pump casing 14 .
  • the pump casing 14 includes an end stud 15 , a first casing 16 , and a second casing 17 which are arranged in this order from a right tip end side.
  • Embodiment 3 shown in FIG. 8 Differences between Embodiment 3 shown in FIG. 8 and Embodiment 2 shown in FIG. 6 are as follows.
  • Embodiment 2 shown in FIG. 6 is configured such that the rotor driving portion 27 causes the driving magnetic pole portion 49 to rotate to cause the driven magnetic pole portion 50 and the rotor 12 to rotate in the same direction as the driving magnetic pole portion 49 .
  • Embodiment 3 shown in FIG. 6 is configured such that the rotor driving portion 27 causes the driving magnetic pole portion 49 to rotate to cause the driven magnetic pole portion 50 and the rotor 12 to rotate in the same direction as the driving magnetic pole portion 49 .
  • the driven magnetic pole portion 50 and the rotor 12 can be directly rotated by the rotating magnetic field generated by the driving magnetic pole portion 69 . Therefore, it is possible to reduce transfer loss of the rotational force and comparatively reduce the volume of the uniaxial eccentric screw pump 67 .
  • the uniaxial eccentric screw pump 72 of Embodiment 4 is the same as the uniaxial eccentric screw pump 11 of Embodiment 1 shown in FIG. 1 , so that same reference numbers are used for the same components, and explanations thereof are omitted. With this, it is possible to omit the contact type bearings 18 and the seal portions 20 for sealing the bearings 18 . Further, it is possible to realize low noise and low vibration, and cause the stator 13 to smoothly rotate.
  • Embodiment 6 shown in FIG. 11 A difference between Embodiment 6 shown in FIG. 11 and Embodiment 3 shown in FIG. 8 is as follows.
  • Embodiment 3 shown in FIG. 8 is configured such that the rotor 12 and the stator 13 are rotatably supported by the first to fourth magnetically-levitated bearings 40 , 41 , 42 , and 43 and the first to fourth magnetic noncontact thrust bearings 44 , 45 , 46 , and 47 .
  • Embodiment 6 shown in FIG. 11 is configured such that the driving magnetic pole portion 69 having the annular shape is provided outside the outer peripheral surface of the driven magnetic pole portion 50 to be spaced apart from the driven magnetic pole portion 50 . With this, an axial length of the uniaxial eccentric screw pump 88 can be shortened.
  • the uniaxial eccentric screw pump 88 of Embodiment 6 shown in FIG. 11 is the same as the uniaxial eccentric screw pump 67 of Embodiment 3 shown in FIG. 8 , so that same reference numbers are used for the same components, and explanations thereof are omitted.
  • the stator 13 is made of engineering plastic, such as Teflon (trademark).
  • the stator 13 may be made of synthetic rubber, a metal, or the like.
  • the rotor 12 is made of a metal, such as stainless steel, but may be made of engineering plastic, such as Teflon (trademark).
  • the rotor 12 and the stator 13 are formed to rotate such that the inner surface forming the inner hole 13 a of the stator and the outer surface of the rotor 12 do not contact each other.
  • the inner hole 13 a of the stator and the rotor 12 may be formed to rotate such that the rotor 12 and both parallel surfaces 35 of the inner hole 13 a of the stator contact each other by an appropriate pressure. Even with this, it is possible to prevent the rotor 12 and the stator 13 from significantly wearing away and prevent different sizes of wearing from being generated on respective surfaces. Therefore, the fluid can be transferred and filled while realizing high flow rate accuracy, low pulsation, and long life.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US12/519,964 2006-12-20 2007-11-07 Uniaxial Eccentric Screw Pump Abandoned US20100092317A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2006343187 2006-12-20
JP2006-343187 2006-12-20
JP2007-235008 2007-09-11
JP2007235008A JP2008175199A (ja) 2006-12-20 2007-09-11 一軸偏心ねじポンプ
PCT/JP2007/071621 WO2008075507A1 (ja) 2006-12-20 2007-11-07 一軸偏心ねじポンプ

Publications (1)

Publication Number Publication Date
US20100092317A1 true US20100092317A1 (en) 2010-04-15

Family

ID=39536140

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/519,964 Abandoned US20100092317A1 (en) 2006-12-20 2007-11-07 Uniaxial Eccentric Screw Pump

Country Status (5)

Country Link
US (1) US20100092317A1 (enExample)
EP (1) EP2113667B1 (enExample)
JP (1) JP2008175199A (enExample)
AU (2) AU2007335618B2 (enExample)
WO (1) WO2008075507A1 (enExample)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130293050A1 (en) * 2012-05-04 2013-11-07 Chung Yuan Christian University Hybrid type magnet bearing system
WO2014099783A1 (en) 2012-12-19 2014-06-26 Schlumberger Canada Limited Motor control system
US9011122B2 (en) 2010-08-25 2015-04-21 Furukawa Industrial Machinery Systems Co., Ltd. Stator seal structure in uniaxial screw pump
CN105121853A (zh) * 2013-03-07 2015-12-02 威乐欧洲股份公司 具有过压保护的偏心螺杆泵
US9334691B2 (en) 2010-11-19 2016-05-10 Smith International, Inc. Apparatus and method for controlling or limiting rotor orbit in moving cavity motors and pumps
US9482223B2 (en) 2010-11-19 2016-11-01 Smith International, Inc. Apparatus and method for controlling or limiting rotor orbit in moving cavity motors and pumps
US9695638B2 (en) 2011-11-18 2017-07-04 Smith International, Inc. Positive displacement motor with radially constrained rotor catch
US20180097411A1 (en) * 2015-04-13 2018-04-05 Wobben Properties Gmbh Wind energy installation and pole stack for a synchronous generator of a wind energy installation and synchronous generator
DE102017210770A1 (de) * 2017-06-27 2018-12-27 Continental Automotive Gmbh Schraubenspindelpumpe, Kraftstoffförderaggregat und Kraftstofffördereinheit
CN110292319A (zh) * 2018-03-22 2019-10-01 佛山市顺德区美的电热电器制造有限公司 面包机
US11225964B2 (en) * 2017-06-28 2022-01-18 Atlas Copco Airpower, Naamloze Vennootschap Cylindrical symmetric volumetric machine
DE102020215571A1 (de) 2020-12-09 2022-06-09 Audi Aktiengesellschaft Pumpenvorrichtung für ein hydraulisches System eines Kraftfahrzeugs, hydraulisches System
US11384758B2 (en) * 2017-09-21 2022-07-12 Atlas Copco Airpower, Naamloze Vennootschap Cylindrical symmetric volumetric machine with an inlet ventilator
US11384762B2 (en) * 2017-09-21 2022-07-12 Atlas Copco Airpower, Naamloze Vennootschap Cylindrical symmetric volumetric machine
CN116044754A (zh) * 2021-02-24 2023-05-02 西安交通大学 一种椭圆形内啮合双螺杆压缩机转子及其设计方法
WO2023076176A1 (en) * 2021-10-25 2023-05-04 Graco Minnesota Inc. Progressive cavity pump with pump radially within the electric motor
CN116221318A (zh) * 2023-02-03 2023-06-06 上海惯容减震器有限公司 一种螺杆泵式消能惯容减震器及其应用方法
US20240384809A1 (en) * 2023-05-15 2024-11-21 Ckd Corporation Valve unit
US20250154950A1 (en) * 2022-01-18 2025-05-15 Heishin Ltd. Uniaxial eccentric screw pump
US20250154952A1 (en) * 2022-01-18 2025-05-15 Heishin Ltd. Uniaxial eccentric screw pump

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DE102008039973A1 (de) * 2008-08-27 2010-03-04 Wmf Württembergische Metallwarenfabrik Ag Exzenterschneckenpumpe
JP5283012B2 (ja) * 2008-10-31 2013-09-04 兵神装備株式会社 交換機能付きノズル、交換機能付きノズル装置及びそれを備える塗布装置
JP5356867B2 (ja) * 2009-03-09 2013-12-04 古河産機システムズ株式会社 一軸偏心ねじポンプ
JP5356868B2 (ja) * 2009-03-09 2013-12-04 古河産機システムズ株式会社 一軸偏心ねじポンプ
JP2014020258A (ja) * 2012-07-17 2014-02-03 Furukawa Industrial Machinery Systems Co Ltd 一軸偏心ねじポンプ
CA2898910A1 (en) 2012-12-19 2014-06-26 Schlumberger Canada Limited Progressive cavity based control system
JP6352604B2 (ja) 2013-08-20 2018-07-04 ヘイシンテクノベルク株式会社 回転容積型ポンプ用摺動部材、及び回転容積型ポンプ運転状態検知システム
WO2015124918A1 (en) 2014-02-18 2015-08-27 Vert Rotors Uk Limited Rotary positive-displacement machine
JP6421370B2 (ja) * 2014-08-26 2018-11-14 兵神装備株式会社 流量計及びポンプ装置
JP6585382B2 (ja) * 2015-05-27 2019-10-02 古河産機システムズ株式会社 ねじポンプ
JP6941550B2 (ja) * 2017-12-13 2021-09-29 古河機械金属株式会社 ねじポンプ用アウタロータ駆動装置およびこれを備えるねじポンプ
GB201811402D0 (en) * 2018-07-12 2018-08-29 Alconbury Weston Ltd Liquid process assembly
EP4127473B1 (en) * 2020-03-31 2025-03-26 Graco Minnesota Inc. Pump with high torque drive
JP7199128B1 (ja) * 2022-01-18 2023-01-05 兵神装備株式会社 一軸偏心ねじポンプ

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JPH1137155A (ja) * 1997-07-18 1999-02-09 Ishikawajima Harima Heavy Ind Co Ltd 磁気軸受およびその制御系
US6361292B1 (en) * 2000-04-12 2002-03-26 Sheldon S. L. Chang Linear flow blood pump
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US20050169779A1 (en) * 2004-01-30 2005-08-04 Christian Bratu Progressing cavity pump
JP2005315188A (ja) * 2004-04-30 2005-11-10 Heishin Engineering & Equipment Co Ltd マグネットカップリング型ポンプ
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Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9011122B2 (en) 2010-08-25 2015-04-21 Furukawa Industrial Machinery Systems Co., Ltd. Stator seal structure in uniaxial screw pump
US9482223B2 (en) 2010-11-19 2016-11-01 Smith International, Inc. Apparatus and method for controlling or limiting rotor orbit in moving cavity motors and pumps
US10612542B2 (en) 2010-11-19 2020-04-07 Smith International, Inc. Apparatus and method for controlling or limiting rotor orbit in moving cavity motors and pumps
US9334691B2 (en) 2010-11-19 2016-05-10 Smith International, Inc. Apparatus and method for controlling or limiting rotor orbit in moving cavity motors and pumps
US9695638B2 (en) 2011-11-18 2017-07-04 Smith International, Inc. Positive displacement motor with radially constrained rotor catch
US20130293050A1 (en) * 2012-05-04 2013-11-07 Chung Yuan Christian University Hybrid type magnet bearing system
US9181979B2 (en) * 2012-05-04 2015-11-10 Chung Yuan Christian University Hybrid type magnet bearing system
CN104937208A (zh) * 2012-12-19 2015-09-23 普拉德研究及开发股份有限公司 马达控制系统
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AU2011200664A1 (en) 2011-03-10
AU2011200664B2 (en) 2012-08-16
WO2008075507A1 (ja) 2008-06-26
EP2113667A4 (en) 2012-06-13
EP2113667B1 (en) 2013-10-16
AU2007335618A1 (en) 2008-06-26
EP2113667A1 (en) 2009-11-04
JP2008175199A (ja) 2008-07-31
AU2007335618B2 (en) 2011-04-21

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