EP1347178A1 - Pompe centrifuge facile à nettoyer - Google Patents

Pompe centrifuge facile à nettoyer Download PDF

Info

Publication number: EP1347178A1
Authority: EP; European Patent Office
Prior art keywords: rotor; pump; centrifugal pump; pump according; impeller
Prior art date: 2002-03-21
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

EP03005190A

Other languages

German (de)

English (en)

Other versions

EP1347178B1 (fr

Inventor

Heinz Rust

Friedemann Seibert

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.)

Hilge GmbH and Co KG

Original Assignee

Philipp Hilge 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.)

2002-03-21

Filing date

2003-03-08

Publication date

2003-09-24

2003-03-08 Application filed by Philipp Hilge GmbH filed Critical Philipp Hilge GmbH

2003-09-24 Publication of EP1347178A1 publication Critical patent/EP1347178A1/fr

2005-05-11 Application granted granted Critical

2005-05-11 Publication of EP1347178B1 publication Critical patent/EP1347178B1/fr

2023-03-08 Anticipated expiration legal-status Critical

Status 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
- 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
- F04D13/0606—Canned motor pumps
- F04D13/0633—Details of the bearings
- 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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
- F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

the present invention relates to a centrifugal pump with a pump housing, which one Comprises pump chamber, which has a suction area and a discharge area, with an impeller, which is rotatably mounted within the pump chamber around an impeller axis, and with a Wheel drive.
centrifugal pump which are very easy to clean and which e.g. by briefly pumping a flushing medium a pump medium previously present in the pump can be completely removed in order to Avoid contamination of media that are pumped later, and the rinsing process should also be avoided quick and easy and without disassembly and without using excessive amounts of Detergent should be done.
the present invention is based on the object To create a centrifugal pump with the features mentioned above, which is even easier and is easier to clean and which is therefore particularly suitable for sterile applications or in general for applications in which a simplified flushing and cleaning of a pump is desired is.
the impeller drive Pump consists of at least one reluctance motor, the electrically contactless rotor in the volume of the pump chamber acted upon by the pump medium, and its stator is arranged on or in a housing section of the pump surrounding the rotor.
Such a reluctance motor has been used conventionally for centrifugal pumps Drives the advantage that the rotor does not have to have permanent magnets or any contains electrical windings that require a power supply.
the rotors also contain no permanent magnets.
the drive rotor has no mechanical or electrical connection to other drive elements no seals are required for corresponding transitions.
the rotor can be connected directly to the driven impeller and both parts together can be arranged in the pump room so that easy cleaning and rinsing of these parts is easily possible.
the rotor is independent of the magnetic driving forces has a magnetic bearing.
Such storage ensures that the rotor in Operation of the pump does not come into contact with the pump housing, so without appropriate Friction even higher speeds are possible.
the invention would also be straightforward one or more plain bearings open on both sides can be realized, which are easy to flush and to are clean, since such bearings do not need to have a sealing function.
Magnetic storage is only possible or at least considerably facilitated by the fact that the rotor of the reluctance motor contains no permanent magnets for the drive, but only soft magnetic material.
the rotor is also coupled directly to the impeller, so that none at all Gear elements are present in which parts of the pump medium could get caught.
the rotor is a ring, which with a corresponding Drive shaft is connected, with spaces between radial projections of the Ring are either filled with non-magnetic material or the entire ring is enveloped is so that the gaps are covered.
the rotors of reluctance motors typically have radial projections in the manner of the teeth of a gear, which at different times by magnetic induction from a each closest pole shoe are tightened, according to the desired speed of the rotor a quick switchover between several poles of the stator takes place.
the surface should be as smooth as possible received, the design is an essentially smooth ring with filled interdental spaces or a continuous wrapping is preferred.
support cams provided, which in the case of a Rotor standstill lie on the corresponding housing surfaces and also in the case of a Contact with the housing during the rotation take over the function of sliding elements.
these support cams are encircling in a ring Web, and preferably on the outer cylindrical surface of the annular rotor and if necessary also on one or both axial end faces of the rotor.
the material of these cams or webs is chosen so that it has the lowest possible sliding friction with the inner surface of the pump chamber housing.
One embodiment is particularly preferred the invention, in which two reluctance motors are provided for the drive, one rotor each axially in front of an impeller or a group of impellers connected in series, and a rotor behind the impeller or the group of impellers connected in series is arranged.
the rotors are expediently located in the vicinity of the suction area and the discharge area of the pump.
the Pump is designed as an axial pump, that is, as a pump in which both the suction area or suction nozzle of the pump as well as the discharge area or discharge nozzle (discharge nozzle) the pump coaxial to the common axis of the rotor or the rotors and the impeller or the impellers are arranged.
an embodiment of the invention is preferred in which a plurality of impellers are connected in series Rotate the impeller cells.
the stator of the drive according to the invention is expediently located outside the pump chamber arranged, a four-pole winding for driving the rotor is preferred.
a two- or multi-pole winding for the radial magnetic bearing of the rotor be provided.
Additional windings can be provided for the axial magnetic bearing of the rotor become.
These windings are expediently in the rotor or rotor ring directly surrounding wall area of the pump housing arranged. For this e.g. special Recesses can be provided in the wall of the pump housing.
the radial play of the rotor is at most 1 up to 2 mm and the axial play maximum 0.5 to 1 mm. It should be borne in mind that due to the expediently rigid and rotationally fixed connection of the rotor or the rotor hub to the drive shaft the impellers each radial and axial movement of the rotor in the same way the or the impellers is transmitted so that the impellers in their impeller cells, that is compared to the partitions provided in the pump room, which separate the individual pump cells or define impeller cells, must have a corresponding radial and axial play. Out for this reason it is of course preferred for a high efficiency of the pump if that radial and axial play is kept as small as possible, but without running the risk that it frequent or even regular contact of the rotor with the surrounding wall areas of the pump housing comes.
the windings for the magnetic bearing should of course be independent of the stator windings the reluctance motor can be switched, so that the magnetic bearing both slow running as well as when the rotor is stopped.
any seals that are between individual components of the pump housing or e.g. also between a hub of the rotor and the corresponding drive shaft for the impellers should, if possible, be open to the pump room and easily accessible, i.e. neither in front of the gaskets between the gaskets and surrounding wall areas narrow, narrow seal gaps remain, into which the pump medium penetrate and which would then be difficult to clean.
the seals to the pump room should be largely open and the seal receptacles on the inside walls of the pumps be designed so that the transition from the sealing surface to the adjacent housing surface always relatively abrupt and at an angle of more than 30 °, so that on this Way narrow and narrow sealing gaps can be avoided.
the rotor is advantageously as a spoke wheel with a hub and an annular rim as well typically three to a maximum of six spokes formed, which hub and rim or rim ring connect with each other, the actual rotor being made of soft magnetic material with tooth-like radial projections exists on the ring or rim area of such Spoked wheel limited.
the spokes should have a cross section that allows the passage of the Pump medium as little as possible, because the spokes in the suction area and / or in Discharge area of the pump medium.
the single figure shows an axial longitudinal section through a preferred embodiment of the invention Centrifugal pump.
the centrifugal pump designated overall by 10, consists of a multi-part pump housing, which consists in detail of a suction cover 1, a pressure cover 2, a first motor housing 3, a second motor housing 3 'and pump cell housings 13 is formed. Especially on the motor housing sections 3 and 3 'additional cooling fins can 25 may be provided.
the individual housing sections are sealed by sealing rings 6 and 7, respectively connected with each other.
the pump housing described above thus defines a pump chamber 20, which is a suction area 26 and a discharge area or pressure area 27, the actual pumping effect is generated by three series-connected impeller cells, which are separated by partitions 36 or 35 and housing sections 13 are defined.
the intake port 16 and the pressure port 17 are arranged coaxially to the common axis 18 of the impellers 4 and the rotors 5.
the first Impeller cell has an inlet opening 29 which surrounds the drive shaft 19 in a ring shape, butting it Pump medium radially outwards, from where it is conducted via guide plates 21 into the next impeller cell which also has a central, annular inlet opening.
the pump medium After passing through a third impeller cell, the pump medium arrives as shown Arrows into the discharge or pressure area 27 and from there through the pressure port 17 outside or in a pressure line. As you can see, the pump medium flows through both in Suction area 26 and in the pressure area 27 the spoke wheels of the two rotors 5 and 5 '.
the spokes 14 of the spoke wheels have a circular shape Cross-section, but you might as well have an elongated or oval or flat cross-section have and be propeller-like against the axis 18.
the rotors 5 are only very here represented schematically.
the flat, recessed bars 23, 24 represent soft magnetic Elements or recesses between them.
the in the surrounding pump housing 3 Shown flat, bar-shaped elements 12, 22 represent the space for stator windings or for magnetic bearing windings.
the radially outer peripheral surface of a rotor 5 is a slightly protruding, rotating Web 9 formed, which could also be divided into two or more narrower webs and which serves as an emergency camp, in the event that there is a contact of the rotor 5 with the inner wall of the surrounding housing 3 comes.
a similar web 9 is also on the axial outside of the rotors 5 and 5 'are provided, which also lie opposite corresponding inner surfaces of the pump housing, however, under normal operating conditions in a small but essentially constant distance on the order of 0.5 mm to these surfaces.
the radial play of the webs or cams 9 on the rotors 5 and 5 ' is a maximum of 1 to 2 mm.
the impellers or impeller blades 4, which are fixed, also have a corresponding radial play are mounted on a shaft 19, which in turn is rigidly and rigidly connected to the hub 15 of the rotor 5 is.
the rotor 5 and the impellers 4 therefore rotate about a common axis 18
Pump cells are formed by partitions 35, 36, which in between one of the impeller blades Include 4 swept volumes.
the medium is through the impeller blades 4th radially outwards into the pressure area 39 of the impeller cell in question and is from there via baffles 21 again the next annular suction opening of a next impeller cell fed, etc., until the pump medium finally from the last impeller cell into the pressure chamber 27 is ejected.
Both the pump medium entering the intake area 20 through the intake port 16 and also the pump medium emerging in the pressure region 27 and the corresponding pressure connection 17 must pass between the spokes 14 of the rotors 5 and 5 ', respectively.
the cross-section of the spokes is shown here as a circular cross-section, but this can Cross-section also be oval or oblong-flat and are generally designed so that it flows through Pump medium opposes as little resistance as possible or the pump flow still supported.
Each rotor 5, 5 'expediently has only three or four corresponding spokes.
These seals 8 are, as is the case with the seals 6 and 7 recognizes sealing rings with a significant part of their peripheral surface to the inside The pumping chamber should be exposed and thus be well washed over by the pumping medium.
the pump is designed so that it consists of as many identical parts as possible.
the suction cover 1 and the pressure cover 2 identical components, which are only mirror images are arranged to each other.
the pump housing sections 3, 3 ' which are also the stator area of the reluctance motors are identical and are only mirror images of each other arranged. The same also applies to the rotors 5 including the associated spokes 14 and Hubs 22.
the individual pump cell housings or pressure covers 13 are different Pump cells are of identical design, that is to say they each have a cylindrical housing section 13 and a radially inwardly extending partition 35 on the suction cover the next following impeller cell. There are corresponding ones on the pressure side of each of the impeller cells Baffles 21 provided on the partition 35. As you can see, are shown in the Embodiment two identical impeller cells with corresponding identical housing sections 13 arranged one behind the other. A third cell only consists of an impeller 4.
the housing sections 3, 3 ' which form the stators for the reluctance motors, also have still cooling fins 25 on.
the axial arrangement of the suction port 16 and the pressure port 17 leads to the impellers do not experience an effective load in a radial direction, so that it becomes easier for the rotors 5, 5 'to be magnetically supported in the radial direction.
the axial magnetic bearing is independent of the radial bearing.

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)
Cyclones (AREA)

EP03005190A 2002-03-21 2003-03-08 Pompe centrifuge facile à nettoyer Expired - Lifetime EP1347178B1 (fr)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
DE10212693		2002-03-21
DE10212693A DE10212693A1 (de)	2002-03-21	2002-03-21	Leicht zu reinigende Kreiselpumpe

Publications (2)

Publication Number	Publication Date
EP1347178A1 true EP1347178A1 (fr)	2003-09-24
EP1347178B1 EP1347178B1 (fr)	2005-05-11

Family

ID=27771483

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP03005190A Expired - Lifetime EP1347178B1 (fr)	2002-03-21	2003-03-08	Pompe centrifuge facile à nettoyer

Country Status (4)

Country	Link
EP (1)	EP1347178B1 (fr)
AT (1)	ATE295479T1 (fr)
DE (2)	DE10212693A1 (fr)
DK (1)	DK1347178T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2009137318A1 (fr) *	2008-05-06	2009-11-12	Fmc Technologies, Inc.	Pompe à paliers magnétiques
DE102008038787A1 (de) *	2008-08-13	2010-02-18	Siemens Aktiengesellschaft	Fluidenergiemaschine
US8696331B2 (en)	2008-05-06	2014-04-15	Fmc Technologies, Inc.	Pump with magnetic bearings

Citations (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO1996031934A1 (fr) *	1995-04-03	1996-10-10	Sulzer Electronics Ag	Machine rotative avec systeme electromagnetique d'entrainement en rotation
EP0856666A1 (fr) *	1997-01-31	1998-08-05	Ebara Corporation	Pompe à liquide et procédé de régulation d'une telle pompe
US5939813A (en) *	1995-08-24	1999-08-17	Sulzer Electronics Ag	Gap tube motor
US6053705A (en) *	1996-09-10	2000-04-25	Sulzer Electronics Ag	Rotary pump and process to operate it
EP1114648A2 (fr) *	1996-06-26	2001-07-11	University Of Pittsburgh	Pompe à fluide

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE3715216A1 (de) *	1987-05-07	1988-11-17	Doll Robert	Tauchpumpe, insbesondere fuer tiefsiedende fluessigkeiten
US5112200A (en) *	1990-05-29	1992-05-12	Nu-Tech Industries, Inc.	Hydrodynamically suspended rotor axial flow blood pump
AU9068798A (en) *	1997-07-26	1999-02-16	Allweiler Ag	Mounting for a turbo-machine rotor and its use
DE29907332U1 (de) *	1999-04-20	1999-09-02	Mediport Kardiotechnik Gmbh	Vorrichtung zur schonenden Förderung von ein- oder mehrphasigen Fluiden
JP2001207988A (ja) *	2000-01-26	2001-08-03	Nipro Corp	磁気駆動型軸流ポンプ

2002
- 2002-03-21 DE DE10212693A patent/DE10212693A1/de not_active Ceased
2003
- 2003-03-08 DK DK03005190T patent/DK1347178T3/da active
- 2003-03-08 DE DE50300523T patent/DE50300523D1/de not_active Expired - Lifetime
- 2003-03-08 EP EP03005190A patent/EP1347178B1/fr not_active Expired - Lifetime
- 2003-03-08 AT AT03005190T patent/ATE295479T1/de not_active IP Right Cessation

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO1996031934A1 (fr) *	1995-04-03	1996-10-10	Sulzer Electronics Ag	Machine rotative avec systeme electromagnetique d'entrainement en rotation
US5939813A (en) *	1995-08-24	1999-08-17	Sulzer Electronics Ag	Gap tube motor
EP1114648A2 (fr) *	1996-06-26	2001-07-11	University Of Pittsburgh	Pompe à fluide
US6053705A (en) *	1996-09-10	2000-04-25	Sulzer Electronics Ag	Rotary pump and process to operate it
EP0856666A1 (fr) *	1997-01-31	1998-08-05	Ebara Corporation	Pompe à liquide et procédé de régulation d'une telle pompe

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2009137318A1 (fr) *	2008-05-06	2009-11-12	Fmc Technologies, Inc.	Pompe à paliers magnétiques
AU2009244607B2 (en) *	2008-05-06	2013-10-17	Fmc Technologies, Inc.	Pump with magnetic bearings
US8696331B2 (en)	2008-05-06	2014-04-15	Fmc Technologies, Inc.	Pump with magnetic bearings
US8777596B2 (en)	2008-05-06	2014-07-15	Fmc Technologies, Inc.	Flushing system
US9601964B2 (en)	2008-05-06	2017-03-21	Fmc Technologies, Inc.	In-line flow mixer
DE102008038787A1 (de) *	2008-08-13	2010-02-18	Siemens Aktiengesellschaft	Fluidenergiemaschine

Also Published As

Publication number	Publication date
ATE295479T1 (de)	2005-05-15
DE10212693A1 (de)	2003-10-02
EP1347178B1 (fr)	2005-05-11
DK1347178T3 (da)	2005-06-06
DE50300523D1 (de)	2005-06-16

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