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WO1992006301A1 - Pompe centrifuge et moteur integres - Google Patents

Pompe centrifuge et moteur integres Download PDF

Info

Publication number
WO1992006301A1
WO1992006301A1 PCT/US1991/007122 US9107122W WO9206301A1 WO 1992006301 A1 WO1992006301 A1 WO 1992006301A1 US 9107122 W US9107122 W US 9107122W WO 9206301 A1 WO9206301 A1 WO 9206301A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
centrifugal pump
shroud
flow
shrouds
Prior art date
Application number
PCT/US1991/007122
Other languages
English (en)
Inventor
Paul Cooper
Lee J. Bulson
Original Assignee
Ingersoll-Rand Company
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 Ingersoll-Rand Company filed Critical Ingersoll-Rand Company
Priority to AU89075/91A priority Critical patent/AU651399B2/en
Priority to CA002092438A priority patent/CA2092438C/fr
Priority to EP91920060A priority patent/EP0551435B1/fr
Priority to DE69105211T priority patent/DE69105211T2/de
Priority to KR1019930701042A priority patent/KR0171871B1/ko
Publication of WO1992006301A1 publication Critical patent/WO1992006301A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/048—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/064—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0646—Units comprising pumps and their driving means the pump being electrically driven the hollow pump or motor shaft being the conduit for the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/186—Shaftless rotors

Definitions

  • This invention relates generally to electrically driven fluid pumps, and more particularly to electrically driven centrifugal pumps which require no shaft seals.
  • Centrifugal fluid pumps are well known in the hydraulic and pneumatic fields. They commonly consist of a motor to drive a shaft on which a fluid impeller is mounted. Generally, the fluid inlet port, or suction port, feeds fluid to the center, or hub, of the impeller. A number of impeller vanes generally project outward from the hub in spiral paths and are supported between shrouds which, together with the vanes, define pumping channels. The rotor is encased in a housing which channels the working fluid from the inlet port to the hub, or inducer, where it is inducted into the pumping channels between the vanes and shrouds.
  • the centrifugal action of the impeller drives the working fluid outward to a diffuser at the periphery o*" the impeller disk where it enters a scroll shaped volute and, from there, is channelled to the discharge port of the pump.
  • the motor shaft which supports the impeller, requires bearings which are sometimes lubricated by the working fluid, but, in many cases, they require separate lubrication due to incompatibility of the working fluid. In all cases, seals are required to prevent leakage of the working fluid around the impeller shaft where it enters the pump housing. After some time in service, the bearings may deteriorate to the point where they permit some radial displacement of the rotating shaft. This causes accelerated wear and deterioration of the shaft seal and results in leakage of the working fluid from the pump housing.
  • an impeller disk which also functions as a rotor for a brushless DC motor in a centrifugal fluid pump, comprising a hub section; at least one disk shaped shroud containing permanent magnets; a plurality of impeller blades projecting outward from the hub and fixed to a face of the shroud to define fluid pumping channels; and means for supplying fluid to the pumping channels.
  • the pump including the impeller disk exhibits a novel construction in that the hub section includes inducer means for inducing fluid flow from one or more inlets to the pumping channels through openings in stator coils and the impeller disks.
  • the impeller may be axially hydrodynamically balanced by providing rings for partially closing the gaps between the stator coils and the impeller so that a pressure is established in the gaps.
  • FIG. 1 is a schematic sectional elevation view illustrating one embodiment of a centrifugal pump according to the present invention
  • Fig. 2 is a schematic sectional elevation view of another embodiment of the pump of the present invention
  • Fig. 3 is a fragmentary view along line 3-3 of the pump embodied in Fig. 1.
  • DETAILED DESCRIPTION Fig. 1 is a schematic cross sectional view of one embodiment of the pump of the present invention, which is seen to be laterally symmetrical about the vertical center plane represented by the centerline of Fig. 1.
  • the housing 10 has an inlet port 11 and a discharge port 12 which are connected by means of inducer assembly 18, impeller shrouds 15, rotating vaneless diffuser 24, and volute 13.
  • the pump fluid enters at the inlet port 11; divides and passes into the two sides of the inducer assembly 18; passes between the two impeller shrouds 15 through pumping channels 55 (shown in Fig. 3) which are defined by the spaces between neighboring impeller blades 21 and the impeller shrouds 15, between which the impeller blades 21 are disposed; passes through the rotating vaneless diffuser 24; then passes through the volute 13 and into discharge port 12. Between diffuser 24 and volute 13 a small amount of the high pressure fluid feeds back through axial thrust balance passages 45.
  • These narrow passages provide the gap necessary for rotation of the rotor shrouds 15 between the stators 14 and, by admission of the feedback fluid, provide a hydrodynamic balance to counteract any axial thrusts of the rotor 15 so that it remains centered between stators 14.
  • Axial thrust balancing rings 16 are provided in the balance passage 45 either on the surface of the stator can 17 or on a projection of housing 10. By narrowing the axial gap between the impeller shrouds 15 and ⁇ tator cans 17 or housing 10, these rings cause an increase of fluid pressure in the balance passage 45 which enhances che axial thrust balance performance.
  • axial thrust balancing rings 16 The alternative provided for placement of the axial thrust balancing rings 16 is required because, in some cases, stators 14 will not be canned or encapsulated. In such cases, it is necessary to place the axial thrust balancing rings 16 on projections of housing 10.
  • Each half of housing 10 has a toroidal recess 33 in which a stator 14 is secured.
  • recirculation passages 20 are provided to assure smooth inducer action at off-design flow rates.
  • the rotor assembly which includes inducer assembly 18, shrouds 15, impeller blades 21, and rotating diffuser 24 is supported on journals provided on the outside of the tubular axial extensions of shrouds 15 in radial magnetic bearings 35 and auxiliary bearings 40.
  • the rotor is supported by the radial magnetic bearings 35 which have a large enough clearance to provide non-contact bearing support to the rotor.
  • auxiliary bearings 40 are provided for the ensuing emergency rundown of the rotor only, and they have a smaller clearance than do magnetic bearings 35.
  • Impeller shrouds 15 each contain a peripheral array of permanent magnets required for a rotor in a brushless DC motor when used in conjunction with stators 14 containing the windings and electrical connections required for operation as a motor. Because impeller shrouds 15 contain permanent magnets, and because shrouds 15 are supported in radial magnetic bearings 35 and auxiliary bearings 40, there is no need for any shaft to penetrate the housing 10 and, thus, no need for rotary shaft seals which can cause wear of the shaft and will eventually leak.
  • Fig. 2 illustrates another embodiment of the pump of the present invention.
  • the housing 10 is composed of several sections, and it has two inlets 11. Otherwise, in all other respects, the pumps are functionally identical. For this reason, numbering of the various components has been retained consistent with that used in Fig. 1.
  • Fig. 3 shows a fragmentary schematic sectional view of the rotor and housing along line 3-3 of Fig. 1. Vanes 21 are attached to shroud 15. Inducer assembly 18 feeds fluid to the impeller blades which pump it radially outward through pumping channels 55 defined by lades 21 and shrouds 15. Diffuser 24 is defined by that space between the two shrouds 15 radially outside that which is occupied by blades 21. Pressurized fluid from diffuser 24 is carried away through volute 13.
  • the particular design parameters for a given pumping application are determined by pressure and volume requirements, space constraints, working fluid properties, and desired orientation of inlet and discharge ports. These are the considerations that determine the diameter of the impeller shrouds 15, the spacing between the shrouds and consequently the width of the impeller blades 21, the size of diffuser 24 if needed, the size of inducer assembly 18, and the size and shape of the pump housing 10 and recirculation passages 20 which are provided to assure smooth inducer action at off-design flow rates.
  • Stators 14 and impeller shrouds 15 are matched according to pumping power requirements. Stators 14 may or may not be encapsulated in cans 17, depending upon whether the working fluid is compatible with the stators.
  • This invention provides an integrated centrifugal pump and motor having the advantages of compactness, the ability to operate electronically at variable speeds, a shaftless rotor which requires no seals, non-contact radial bearing supports during operation, and hydrodynamic axial thrust balance for the rotor. These advantages are obtained when pumping either compressible or incompressible fluids.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Centrifugal Separators (AREA)

Abstract

Pompe centrifuge et moteur intégrés caractérisés par un disque-hélice contenant des aimants permanents et faisant office de rotor pour un moteur à courant continu sans balai. Le rotor est supporté par des supports radiaux sans contact et il est équilibré hydrodynamiquement contre les éventuelles poussées axiales de manière qu'il n'y a aucun contact entre les éléments rotatifs et fixes pendant le fonctionnement. Comme le disque-hélice constitue également le rotor du moteur on n'a pas besoin d'arbre, au sens commun, lequel pénètrerait dans le carter et par conséquent nécessiterait des joints. La pompe obtenue est compacte et peut être commandée électroniquement à des vitesses variables.
PCT/US1991/007122 1990-10-04 1991-09-27 Pompe centrifuge et moteur integres WO1992006301A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
AU89075/91A AU651399B2 (en) 1990-10-04 1991-09-27 Integrated centrifugal pump and motor
CA002092438A CA2092438C (fr) 1990-10-04 1991-09-27 Ensemble moteur et pompe centrifuge
EP91920060A EP0551435B1 (fr) 1990-10-04 1991-09-27 Pompe centrifuge et moteur integres
DE69105211T DE69105211T2 (de) 1990-10-04 1991-09-27 Kreiselpumpe mit integriertem motor.
KR1019930701042A KR0171871B1 (ko) 1990-10-04 1991-09-27 일체형 원심 펌프 및 모터

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US59365590A 1990-10-04 1990-10-04
US593,655 1990-10-04

Publications (1)

Publication Number Publication Date
WO1992006301A1 true WO1992006301A1 (fr) 1992-04-16

Family

ID=24375592

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1991/007122 WO1992006301A1 (fr) 1990-10-04 1991-09-27 Pompe centrifuge et moteur integres

Country Status (9)

Country Link
EP (1) EP0551435B1 (fr)
JP (1) JP2546943B2 (fr)
KR (1) KR0171871B1 (fr)
CN (1) CN1022504C (fr)
AU (1) AU651399B2 (fr)
CA (1) CA2092438C (fr)
DE (1) DE69105211T2 (fr)
WO (1) WO1992006301A1 (fr)
ZA (1) ZA917488B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996041082A1 (fr) * 1995-06-07 1996-12-19 HER MAJESTY IN RIGHT OF CANADA represented by THE MINISTER OF NATURAL RESOURCES CANADA Pompe a faible debit
RU2129669C1 (ru) * 1998-06-24 1999-04-27 Общество с ограниченной ответственностью "Фирма АГРОИНЖСТРОЙ" Бессальниковый электронасос с вентильным двигателем постоянного тока
DE19846737A1 (de) * 1998-10-12 2000-04-20 Voit Stefan Elektrisch betreibbares Pumpelement zum Einsatz in einem Kühlsystem sowie Wärmetauscher eines Kühlsystems
US6234772B1 (en) * 1999-04-28 2001-05-22 Kriton Medical, Inc. Rotary blood pump
RU2202053C2 (ru) * 2000-08-15 2003-04-10 Федеральное государственное унитарное предприятие "Исследовательский центр им. М.В.Келдыша" Центробежный насос
RU2472277C1 (ru) * 2011-08-10 2013-01-10 Павел Николаевич Манташьян Магнитный насос
CN118572958A (zh) * 2024-08-05 2024-08-30 凯利达科技股份有限公司 一种无轴磁力泵

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101255868B (zh) * 2007-12-10 2010-11-24 兰州理工大学 电机内嵌叶片泵
US8905729B2 (en) * 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with electro-magnet coupling inside the impeller
CN112682315A (zh) * 2020-12-17 2021-04-20 武汉船用电力推进装置研究所（中国船舶重工集团公司第七一二研究所） 一种双向轴流泵
CN112879313B (zh) * 2021-01-22 2022-07-01 东北石油大学 一种机泵一体化的潜油离心泵

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR591315A (fr) * 1924-03-06 1925-07-02 Rateau Sa Dispositif d'équilibrage des pompes et ventilateurs centrifuges et machines analogues
US1586978A (en) * 1921-02-03 1926-06-01 Worthington Pump & Mach Corp Centrifugal pump
GB582036A (en) * 1944-07-07 1946-11-01 Maldwyn Lewis Thomas Improved combined pump and electric motor unit
US2700343A (en) * 1950-05-11 1955-01-25 Jr Albert R Pezzillo Motor pump unit
US3347168A (en) * 1966-02-16 1967-10-17 Westinghouse Electric Corp Motor pump unit
DE3905278A1 (de) * 1988-02-26 1989-09-07 Gen Electric Durch einen elektronisch kommutierten motor angetriebene einrichtung
EP0378251A2 (fr) * 1981-03-18 1990-07-18 Günther Walter Otto Bramm Appareil de pompage à impulseur magnétiquement suspendu et entraîné

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6284694U (fr) * 1985-11-14 1987-05-29
JPH0433435Y2 (fr) * 1986-05-23 1992-08-11
JPH0776560B2 (ja) * 1987-09-14 1995-08-16 テルモ株式会社 血液移送用ポンプ
JPH0786356B2 (ja) * 1988-04-22 1995-09-20 日機装株式会社 吸収式冷凍機用キャンドモータポンプ
JP2729637B2 (ja) * 1988-10-04 1998-03-18 京セラ株式会社 スクリュー遠心ポンプ
JPH07117060B2 (ja) * 1989-03-22 1995-12-18 芳雄 矢野 流体移送装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1586978A (en) * 1921-02-03 1926-06-01 Worthington Pump & Mach Corp Centrifugal pump
FR591315A (fr) * 1924-03-06 1925-07-02 Rateau Sa Dispositif d'équilibrage des pompes et ventilateurs centrifuges et machines analogues
GB582036A (en) * 1944-07-07 1946-11-01 Maldwyn Lewis Thomas Improved combined pump and electric motor unit
US2700343A (en) * 1950-05-11 1955-01-25 Jr Albert R Pezzillo Motor pump unit
US3347168A (en) * 1966-02-16 1967-10-17 Westinghouse Electric Corp Motor pump unit
EP0378251A2 (fr) * 1981-03-18 1990-07-18 Günther Walter Otto Bramm Appareil de pompage à impulseur magnétiquement suspendu et entraîné
DE3905278A1 (de) * 1988-02-26 1989-09-07 Gen Electric Durch einen elektronisch kommutierten motor angetriebene einrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN ,vol. 13, no. 133 (M-809)(3481) 4 April 1989;& JP,A,63 302 198 ( NIKKISO ) 9 December 1988 see abstract *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996041082A1 (fr) * 1995-06-07 1996-12-19 HER MAJESTY IN RIGHT OF CANADA represented by THE MINISTER OF NATURAL RESOURCES CANADA Pompe a faible debit
US5769069A (en) * 1995-06-07 1998-06-23 Her Majesty The Queen In Right Of Canada, As Represented By The Minister Of Natural Resources Low flow-rate pump
RU2129669C1 (ru) * 1998-06-24 1999-04-27 Общество с ограниченной ответственностью "Фирма АГРОИНЖСТРОЙ" Бессальниковый электронасос с вентильным двигателем постоянного тока
DE19846737A1 (de) * 1998-10-12 2000-04-20 Voit Stefan Elektrisch betreibbares Pumpelement zum Einsatz in einem Kühlsystem sowie Wärmetauscher eines Kühlsystems
US6234772B1 (en) * 1999-04-28 2001-05-22 Kriton Medical, Inc. Rotary blood pump
RU2202053C2 (ru) * 2000-08-15 2003-04-10 Федеральное государственное унитарное предприятие "Исследовательский центр им. М.В.Келдыша" Центробежный насос
RU2472277C1 (ru) * 2011-08-10 2013-01-10 Павел Николаевич Манташьян Магнитный насос
CN118572958A (zh) * 2024-08-05 2024-08-30 凯利达科技股份有限公司 一种无轴磁力泵

Also Published As

Publication number Publication date
AU651399B2 (en) 1994-07-21
CA2092438C (fr) 2002-05-07
AU8907591A (en) 1992-04-28
EP0551435B1 (fr) 1994-11-17
KR0171871B1 (ko) 1999-03-20
CN1061836A (zh) 1992-06-10
DE69105211D1 (de) 1994-12-22
DE69105211T2 (de) 1995-06-01
ZA917488B (en) 1993-03-31
CA2092438A1 (fr) 1992-04-05
JP2546943B2 (ja) 1996-10-23
JPH06502470A (ja) 1994-03-17
CN1022504C (zh) 1993-10-20
EP0551435A1 (fr) 1993-07-21
KR930702619A (ko) 1993-09-09

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