EP0237868A2 - Pompe centrifuge à roue radiale ou axiale - Google Patents

Pompe centrifuge à roue radiale ou axiale Download PDF

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Publication number
EP0237868A2
EP0237868A2 EP87103057A EP87103057A EP0237868A2 EP 0237868 A2 EP0237868 A2 EP 0237868A2 EP 87103057 A EP87103057 A EP 87103057A EP 87103057 A EP87103057 A EP 87103057A EP 0237868 A2 EP0237868 A2 EP 0237868A2
Authority
EP
European Patent Office
Prior art keywords
impeller
pump
centrifugal pump
auxiliary
pump according
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
EP87103057A
Other languages
German (de)
English (en)
Other versions
EP0237868A3 (en
EP0237868B1 (fr
Inventor
Ernst Hauenstein
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Individual
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Individual
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 Individual filed Critical Individual
Priority to AT87103057T priority Critical patent/ATE60411T1/de
Publication of EP0237868A2 publication Critical patent/EP0237868A2/fr
Publication of EP0237868A3 publication Critical patent/EP0237868A3/de
Application granted granted Critical
Publication of EP0237868B1 publication Critical patent/EP0237868B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/404—Transmission of power through magnetic drive coupling
    • F05B2260/4041—Transmission of power through magnetic drive coupling the driven magnets encircling the driver magnets

Definitions

  • the present invention relates to a radial centrifugal pump, the working side of which is completely tightly separated from the drive side by a canned pot, in which, in addition, the pump impeller, which is mounted on a shaft between two axial end stops, is driven via a magnetic coupling acting through the wall of the canned pot and is in operation the impeller act axial thrust, caused by different pressure ratios on the impeller front and impeller rear, means being provided to compensate for these thrust forces.
  • Centrifugal pumps of this type are generally known. Their field of application is very wide, but due to the lack of seals, it is mainly in the field of chemistry, where particularly toxic or otherwise aggressive liquids have to be pumped.
  • centrifugal pumps in the form of so-called canned motor pumps or magnetic coupling pumps was the collection and balancing of the hydraulic forces inside the pump, in particular the thrust forces acting on the pump wheel.
  • the previously known solutions were unsatisfactory in the sense that complex constructions were required, which were also associated with relatively high energy losses (friction losses, efficiency reductions). This is all the more regrettable, since today's materials have made it possible to build the actual drive system more compactly and thus to keep the outer dimensions small.
  • the purpose of the present invention was to find in radial or axial centrifugal pumps of the type described at the outset a structurally simple solution for compensating for the axial thrust acting on the impeller, which further simplifies the actual pump construction and helps to reduce the internal forces that previously occurred that in particular the canned tube can be made with a further reduced wall thickness, which in turn can improve the overall efficiency.
  • the solution to this problem is characterized according to the invention in that the actual pump impeller, on its front side, i.e. on the side facing the suction, the delivery channels are provided, an auxiliary delivery wheel is assigned, which serves to reduce the pressure in the room or the rooms on the rear of the impeller.
  • the spaces on the rear of the impeller usually consist of a so-called hub space and an inner and outer drive space.
  • the latter two spaces are separated from one another by the flange of the carrier of one magnetic coupling part, which flange-like protrudes from the rear of the impeller.
  • control means preferably in the form of control slots or channels, are preferably provided on the pump housing, specifically in relation to the periphery of the delivery channels of the auxiliary delivery wheel, so that the medium conveyed by the auxiliary delivery wheel from the space behind the impeller as a function of the to promote the pressure conditions prevailing on the front or rear of the impeller into the pressure chamber of the pump.
  • the auxiliary conveyor wheel is preferably arranged or formed on the rear side of the actual pump impeller, for example directly on the rear wall of the pump impeller.
  • the conveying channels of the auxiliary conveying wheel are preferably designed such that they communicate with one or more of the spaces on the rear of the impeller. For example, a number of separate conveying channels of the auxiliary conveying wheel can be assigned to each of the spaces to be relieved. Depending on the magnitude of the thrust forces that arise in each case, the output of the delivery channels of the auxiliary feed wheel is more or less covered by the control means, caused by an oscillating axial displacement of the pump impeller, which ensures permanent automatic thrust compensation.
  • thrust compensation enables impellers with open or closed blading to be used as desired.
  • the bearing journal or the support shaft for the impeller can e.g. be integrated into the end face of the containment shell, or, in the case of larger embodiments, be supported in a suitable manner in the intake manifold.
  • pumps of any desired type can be built without complex control channels.
  • the rooms on the rear of the impeller can also be rinsed with cleaning fluid with little effort.
  • only a supply line for cleaning fluid into the rear hub space is required, from which certain delivery channels of the auxiliary feed wheel lead the rinsing fluid into the outer drive space.
  • the flushing liquid could also be supplied directly to the outer drive compartment.
  • the construction according to the invention is particularly suitable for pumps in which the driven part is designed as an external rotor, since on the one hand modern materials allow the construction of rotors with a low mass and on the other hand practically no friction losses occur. Nevertheless, the inevitable gaps can be made very narrow, since the risk of clogging is greatly reduced in the construction according to the invention.
  • Fig. L of the drawing shows purely schematically a radial centrifugal pump with magnetic coupling in section, wherein in the lower half of the picture a variant of the upper half of the picture is shown both with respect to the canned pot and the impeller. However, the variants have no influence on the basic structure of the pump.
  • the pump essentially consists of a housing 1 with intake port 2, a bearing pin 3 arranged in the example shown in the intake port 2 (which in the lower variant is also formed in one piece with the canned pot bottom) for a pump impeller 4 and one for the working side (pump side) completely sealed from the drive side (motor side) separating canned pot 5. Also shown is internal magnetic rotor 6 of a drive motor, not shown, the housing of which is flanged to the pump housing 1.
  • the bearing journal 3 for the pump impeller 4 is seated in a hub cover 3 ⁇ , which is supported and fastened in the intake flange 2 via supports 7, 8.
  • the medium to be conveyed reaches the pressure chamber 8 via the suction port 2 and the pump impeller 4 (in the example shown a closed impeller) and from there into the pressure line (not shown).
  • the impeller 4 with closed blades 4 ⁇ is overhung on the bearing journal 3, it being able to move freely between the stops 9 and 10 under the axial thrust forces that occur. As will be shown, the impeller does not come to rest against the stops 9, 10, which essentially serve to position the wheel.
  • This ring flange l2 divides the pump-side drive space l3, which is located on the rear side of the impeller 4, into an outer and an inner space A or B. Also on the impeller rear side is a so-called hub space C.
  • the core of the present invention now lies in this pressure or thrust compensation:
  • the pressure acting on the impeller from rooms A, B and C is greater than the pressure on the suction or front side of the impeller 4, so that the impeller would be pressed in the suction direction without special precautions. However, this should be avoided.
  • auxiliary conveyor wheel 4 which usually consists of one piece with the actual pump impeller 4, the pressure on the back of the impeller is now reduced and the axial movement of the impeller 4 in the direction of the intake is thereby stopped. So that there is no opposite movement of the impeller 4, i.e. a shift in the direction of the drive side, the delivery rate of the auxiliary conveyor wheel 4 ⁇ is controlled:
  • one or more bores 17 are preferably provided between the pressure space 8 of the pump and the drive space A.
  • the auxiliary conveyor wheel 4 ⁇ can be designed such that from the different rooms A, B and C inlet openings 18, l9 and 20, respectively, to the individual delivery channels l6 of the auxiliary conveyor wheel 4 ⁇ are provided, with a different design that for each room A, B and C a number of separate delivery channels (e.g. 2l for room C in the lower variant) are provided.
  • a mixed construction is also conceivable.
  • a rinsing liquid can be conveyed into the space C via a line 22 and a bore 23 in the journal 3 in order to from there to be promoted via the delivery channels 2l of the auxiliary feed wheel 4 ⁇ not in the pressure chamber 8 of the pump, but in room A (and from here in room B). Excellent cleaning of the pump can thus be carried out in a simple manner.
  • a rinsing or cleaning liquid could, however, also be introduced directly into space A, for example via an inlet 24.
  • FIGS. 2 and 3 show purely schematically how the control of the delivery rate of the auxiliary feed wheel 4 ⁇ via control slots on the housing, relative to the feed channels of the auxiliary feed wheel.
  • the delivery channels are covered and the pressure in room A will increase
  • Fig. 3 shows the situation with delivery channels open via the control slots, in which the pressure in room A decreases.
  • Fig. 4 finally shows a purely schematic plan view of the rear of the impeller, i.e. on the auxiliary feed wheel, with different inlet openings in the feed channels.
EP87103057A 1986-03-21 1987-03-04 Pompe centrifuge à roue radiale ou axiale Expired - Lifetime EP0237868B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87103057T ATE60411T1 (de) 1986-03-21 1987-03-04 Radial- oder axialkreiselpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1160/86A CH672820A5 (fr) 1986-03-21 1986-03-21
CH1160/86 1986-03-21

Publications (3)

Publication Number Publication Date
EP0237868A2 true EP0237868A2 (fr) 1987-09-23
EP0237868A3 EP0237868A3 (en) 1988-01-20
EP0237868B1 EP0237868B1 (fr) 1991-01-23

Family

ID=4203879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87103057A Expired - Lifetime EP0237868B1 (fr) 1986-03-21 1987-03-04 Pompe centrifuge à roue radiale ou axiale

Country Status (7)

Country Link
US (1) US4793777A (fr)
EP (1) EP0237868B1 (fr)
JP (1) JP2535004B2 (fr)
AT (1) ATE60411T1 (fr)
CH (1) CH672820A5 (fr)
DE (1) DE3767517D1 (fr)
ES (1) ES2020520B3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4812108A (en) * 1986-09-25 1989-03-14 Seikow Chemical Engineering & Machinery Ltd. Magnet pump
WO1996032592A1 (fr) * 1995-04-14 1996-10-17 Ceramiques & Composites S.A. Pompe centrifuge a entrainement magnetique
EP0982499A1 (fr) * 1998-08-21 2000-03-01 CP Pumpen AG Pompe centrifuge à entrainement magnétique
DE202016105312U1 (de) * 2016-09-23 2018-01-09 Speck Pumpen Verkaufsgesellschaft Gmbh Förderpumpe

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2519466Y2 (ja) * 1990-10-12 1996-12-04 株式会社帝国電機製作所 ガスシール型モータポンプ
FR2698667B1 (fr) * 1992-11-30 1995-02-17 Europ Propulsion Pompe centrifuge à rouet ouvert.
FR2715442B1 (fr) * 1994-01-26 1996-03-01 Lorraine Carbone Pompe centrifuge à entraînement magnétique.
US6135728A (en) * 1998-10-29 2000-10-24 Innovative Mag-Drive, L.L.C. Centrifugal pump having an axial thrust balancing system
US6234748B1 (en) 1998-10-29 2001-05-22 Innovative Mag-Drive, L.L.C. Wear ring assembly for a centrifugal pump
US6293772B1 (en) 1998-10-29 2001-09-25 Innovative Mag-Drive, Llc Containment member for a magnetic-drive centrifugal pump
US6123507A (en) * 1998-11-30 2000-09-26 Smith & Loveless, Inc. Single port impeller
EP1340917B2 (fr) * 2001-06-05 2011-08-31 Iwaki Co., Ltd. Pompe a entrainement magnetique
US7101158B2 (en) 2003-12-30 2006-09-05 Wanner Engineering, Inc. Hydraulic balancing magnetically driven centrifugal pump
JP4959424B2 (ja) * 2007-05-31 2012-06-20 勇 青谷 ポンプ装置
US8506259B2 (en) 2009-12-23 2013-08-13 Solar Turbines Inc. Fluid compression system
US8905729B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with electro-magnet coupling inside the impeller
US8905728B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with permanent magnet coupling inside the impeller
US9488184B2 (en) 2012-05-02 2016-11-08 King Abdulaziz City For Science And Technology Method and system of increasing wear resistance of a part of a rotating mechanism exposed to fluid flow therethrough
DE102013007849A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung
DE102014006568A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung und Verfahren zum Herstellen eines Spalttopfes der Pumpenanordnung
US9771938B2 (en) * 2014-03-11 2017-09-26 Peopleflo Manufacturing, Inc. Rotary device having a radial magnetic coupling
JP6671048B2 (ja) * 2015-11-12 2020-03-25 パナソニックＩｐマネジメント株式会社 ポンプ
CN108496010B (zh) * 2015-12-07 2021-04-02 流体处理有限责任公司 用于抵消多级泵中产生的轴向推力的对置式叶轮耐磨环底切
US10746196B2 (en) * 2017-04-09 2020-08-18 Technology Commercialization Corp. Methods and devices for reducing circumferential pressure imbalances in an impeller side cavity of rotary machines

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT242520B (de) * 1963-04-09 1965-09-27 Philip Pensabene Elektrisch angetriebene Pumpe
AT262774B (de) * 1963-12-14 1968-06-25 Richard Halm Flüssigkeitspumpe
US3881840A (en) * 1973-09-05 1975-05-06 Neratoom Centrifugal pump for processing liquids containing abrasive constituents, more particularly, a sand pump or a waste-water pumper
DE2620502A1 (de) * 1975-05-12 1976-11-25 Siebec Filtres Magnetlaeuferpumpe
EP0163126A1 (fr) * 1984-05-02 1985-12-04 Pompe Ing. Calella S.p.A. Dispositif de pompage électrique
EP0171515A1 (fr) * 1984-07-16 1986-02-19 CP Pumpen AG Pompe centrifuge avec chapeau tubulaire d'isolation de l'entrefer

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2209109A (en) * 1935-11-30 1940-07-23 Firm A W Mackensen Centrifugal pump with axial movement of the shaft
US2361521A (en) * 1943-11-01 1944-10-31 W S Darley & Company Centrifugal pump
US2942555A (en) * 1957-04-15 1960-06-28 Rinaldo F Pezzillo Combination pump and motor
US3589827A (en) * 1969-08-12 1971-06-29 Sergei Stepanovich Gerasimenko Centrifugal leakproof fluid pump
JPS5055902A (fr) * 1973-09-20 1975-05-16
JPS527002A (en) * 1975-07-07 1977-01-19 Mitsubishi Heavy Ind Ltd Method of removing thrust of impeller in high pressure multistage pump
GB2152584B (en) * 1983-06-08 1987-02-25 Sundstrand Corp Centrifugal pump
ATE32931T1 (de) * 1984-07-16 1988-03-15 Cp Pumpen Ag Kreiselpumpe mit einem spaltrohrtopf.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT242520B (de) * 1963-04-09 1965-09-27 Philip Pensabene Elektrisch angetriebene Pumpe
AT262774B (de) * 1963-12-14 1968-06-25 Richard Halm Flüssigkeitspumpe
US3881840A (en) * 1973-09-05 1975-05-06 Neratoom Centrifugal pump for processing liquids containing abrasive constituents, more particularly, a sand pump or a waste-water pumper
DE2620502A1 (de) * 1975-05-12 1976-11-25 Siebec Filtres Magnetlaeuferpumpe
EP0163126A1 (fr) * 1984-05-02 1985-12-04 Pompe Ing. Calella S.p.A. Dispositif de pompage électrique
EP0171515A1 (fr) * 1984-07-16 1986-02-19 CP Pumpen AG Pompe centrifuge avec chapeau tubulaire d'isolation de l'entrefer

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
KSB-Kreiselpumpenlexikon, 02/1980 *
SOVIET INVENTIONS ILLUSTRATED, Sektion P,Q, Woche 8343, 7 Dezember 1983 DERWENT PUBLICATIONS LTD. London, Q5 * SU 981 690 (A) (BYKO/) * *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4812108A (en) * 1986-09-25 1989-03-14 Seikow Chemical Engineering & Machinery Ltd. Magnet pump
WO1996032592A1 (fr) * 1995-04-14 1996-10-17 Ceramiques & Composites S.A. Pompe centrifuge a entrainement magnetique
FR2733010A1 (fr) * 1995-04-14 1996-10-18 Ceramiques Et Composites Sa Pompe centrifuge a entrainement magnetique
EP0982499A1 (fr) * 1998-08-21 2000-03-01 CP Pumpen AG Pompe centrifuge à entrainement magnétique
DE202016105312U1 (de) * 2016-09-23 2018-01-09 Speck Pumpen Verkaufsgesellschaft Gmbh Förderpumpe

Also Published As

Publication number Publication date
DE3767517D1 (de) 1991-02-28
EP0237868A3 (en) 1988-01-20
US4793777A (en) 1988-12-27
CH672820A5 (fr) 1989-12-29
ES2020520B3 (es) 1991-08-16
ATE60411T1 (de) 1991-02-15
JP2535004B2 (ja) 1996-09-18
JPS62233493A (ja) 1987-10-13
EP0237868B1 (fr) 1991-01-23

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