EP0359136A1 - Pompe centrifuge sans joint, nettoyable - Google Patents

Pompe centrifuge sans joint, nettoyable Download PDF

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Publication number
EP0359136A1
EP0359136A1 EP89116582A EP89116582A EP0359136A1 EP 0359136 A1 EP0359136 A1 EP 0359136A1 EP 89116582 A EP89116582 A EP 89116582A EP 89116582 A EP89116582 A EP 89116582A EP 0359136 A1 EP0359136 A1 EP 0359136A1
Authority
EP
European Patent Office
Prior art keywords
impeller
centrifugal pump
cleanable
pump according
glandless
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.)
Withdrawn
Application number
EP89116582A
Other languages
German (de)
English (en)
Inventor
Wilfried Dr.-Ing. Lehmann
Rainer Dipl.-Ing. Landowski
Peter Dipl.-Ing. Mette
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.)
Otto Tuchenhagen GmbH and Co KG
Sihi GmbH and Co KG
Original Assignee
Otto Tuchenhagen GmbH and Co KG
Sihi GmbH and Co KG
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 Otto Tuchenhagen GmbH and Co KG, Sihi GmbH and Co KG filed Critical Otto Tuchenhagen GmbH and Co KG
Publication of EP0359136A1 publication Critical patent/EP0359136A1/fr
Withdrawn legal-status Critical Current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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • 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
    • 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 invention relates to a cleanable glandless centrifugal pump according to the preamble of claim 1.
  • Centrifugal pumps of the type identified in the introduction are used where the requirement for increased occupational and operational safety as well as greatest environmental friendliness is a priority.
  • Magnetically acting, synchronously transmitting rotary couplings use the attraction and repulsion forces between magnets in two coupling halves. They are used for the contactless transmission of torques, whereby, unlike the hysteresis and eddy current clutches, a slip between the two coupling halves cannot occur.
  • Permanent magnetic synchronous clutches which, in connection with glandless centrifugal pumps, are preferably designed as so-called central rotary couplings. They require a partition, the so-called can. This has the task of separating the space for the fluid to be pumped from the atmosphere.
  • the inner magnetic rotor which is also equipped with permanent magnets, is arranged within this containment shell. This in turn is mounted in a bearing flange and medium-lubricated plain bearings and transfers the torque given off by the motor to the impeller without slippage.
  • a housing forms the end of this completely sealed unit.
  • a shaft passage from the room for the fluid to be pumped is not available and therefore is only a static seal between the housing and the containment shell is required.
  • the inner magnetic rotor is attached to the impeller at an axial distance from it by a connecting part.
  • the connecting part also serves to mount the impeller and the inner magnet rotor within the housing.
  • the containment shell encloses the inner magnet rotor and parts of the bearing arrangement. The lubrication of the slide bearing for mounting the impeller in connection with the inner magnet rotor is usually carried out via the fluid to be pumped.
  • the known design of the containment shell has a cavity which is connected to the impeller housing via the bearing gap of the slide bearing. Due to the mode of operation of the hydrodynamically operating plain bearing, the fluid to be conveyed reaches the free spaces of the containment shell via the bearing gap. A complete exchange of the fluid located in the sometimes very intricate dead spaces of the containment shell over the bearing gap of the slide bearing is excluded.
  • centrifugal pumps are therefore completely unsuitable for the reasons mentioned above if the delivery of the fluid has to take place under hygienic or sterile or bacteriologically perfect conditions. Such requirements are placed in particular in the food and beverage industry, in pharmacy or in the sterile field of various fields of application.
  • Centrifugal pumps that meet the aforementioned requirements must be automatically cleanable in the flow.
  • CIP cleanability CIP: cleaning in place
  • the facilities to be cleaned must allow an automatic supply of cleaning liquid and cleaning of the product or product residues in all areas on the spot .
  • CIP cleaning in place
  • a glandless centrifugal pump has already been proposed (GM 19 82 247), in which a partition designed as a containment shell penetrates the impeller concentrically, serves as a cantilevered bearing journal and forms a bearing ring gap with it.
  • This known solution does not disclose any information as to how a defined flow can be ensured in the critical areas, in particular in the bearing ring gap and in the dead space between the impeller hub that is not exposed to the flow and the rear housing wall.
  • the proposed design and sealing of the partition wall gives the glandless centrifugal pump a particularly simple and easy-to-clean design.
  • Conventional centrifugal pumps are usually designed so that the hydraulic efficiency is as high as possible. This is achieved, among other things, by dimensioning the liquid-loaded gaps between stationary and moving components as closely as possible.
  • this dimensioning rule there is a deviation from this dimensioning rule insofar as all the gaps located in areas that are critical in terms of cleaning technology, in particular the bearing gap, are subjected to a flow ensuring adequate cleaning.
  • an advantageous embodiment of the centrifugal pump according to the invention provides that the bearing ring gap is connected on both sides to a hub-side annular space, the latter in each case via Column with a defined passage cross-section is connected to the space of the impeller blades.
  • centrifugal pump provides a hub-side annular space separated by the impeller into two partial spaces, one of which has a first opening with a defined passage cross-section with the area of the suction port and the other in the same way via a second opening with the Area of the pressure port is connected.
  • the pressure difference formed between the suction and pressure ports results in a particularly pronounced, defined gap flow oriented in the radial and axial direction between stationary and moving components within the housing of the conveying device.
  • the arrangement of the bearing ring gap and its connection on both sides to the hub-side annular space ensures that, in particular during cleaning, the cleaning fluid to be conveyed flows through the bearing ring gap in sufficient quantity, since its two ends are connected to areas which are due to the pressure distribution in the housing of the impeller have different pressure levels.
  • the bearing ring gap In order to clean the critical area of the centrifugal pump, the bearing ring gap, particularly intensively, another advantageous embodiment of the centrifugal pump provides that measures are provided in the bearing ring gap and / or at its inlet which increase the kinetic energy of the gap flow in the bearing ring gap.
  • centrifugal pump provides that a bearing bush arranged in the impeller in the region of the bearing ring gap is in turn designed as an impeller. As a result, the gap flow in this area is forced by an additional increase in its kinetic energy.
  • centrifugal pump In order to intensify the cleaning of the bearing ring gap by the formation of flow turbulence during the cleaning run, another embodiment of the centrifugal pump according to the invention provides that the boundary surface of the partition wall and / or the bearing bush facing the bearing ring gap are provided with axial or helical grooves or elevations or is.
  • the arrangement of the impeller-side half of the rotary coupling in a recess in a hub of the impeller ensures a compact arrangement while avoiding dead spaces in this area.
  • the hermetically sealed chamber of the impeller-side half of the rotary coupling in the recess of the hub of the impeller ensures a particularly easy-to-clean arrangement, which moreover promotes the conveyance of the fluid under hygienic or sterile conditions or bacteriologically perfect conditions guaranteed.
  • a compact and easy-to-clean arrangement of the impeller-side half of the rotary coupling is achieved in that the latter is hermetically sealed by the hub and a cover part on the one hand and a bearing bush enclosing the partition wall on the other hand.
  • a further embodiment of the centrifugal pump according to the invention provides that the bearing bush is provided on both sides with a thrust surface which limits its axial displaceability in the housing.
  • the contact surface is designed in such a way that when it is in contact with the housing there is still sufficient liquid passage between the contact surface and the housing.
  • the impeller is provided on both sides towards the housing with a contact surface which has the same properties with regard to its liquid permeability as the contact surfaces on the bearing bush.
  • the centrifugal pump In order to ensure wear resistance and hardness, chemical resistance and good temperature properties and, furthermore, to keep power losses due to eddy current formation when cutting the partition wall small with the magnetic field lines of the central rotary coupling, another development of the centrifugal pump according to the invention provides that the partition wall and bearing bush are made of a wear-resistant, chemically resistant, high electrical resistance material, preferably a ceramic.
  • Figure 1 shows, representative of other centrifugal pumps, a meridian section through a so-called self-priming side channel pump.
  • the present invention can also be used without restriction on so-called normal-suction centrifugal pumps or also on rotating positive displacement pumps.
  • the self-priming side channel pump allows both the conveyance of gaseous and liquid fluids, and a reversal of the conveying direction is also possible by changing the direction of rotation.
  • the housing 1 of the centrifugal pump which consists of a motor-side housing part 1b and a housing cover 1a, there is an open parallel-walled rotor with radially directed blades, hereinafter referred to as impeller 5, as the characteristic component.
  • the housing cover 1a has a suction and a pressure port 1c or 1d, which are connected to a side channel 1e.
  • the housing 1 is on its engine side Housing part 1b in connection with the housing cover 1a and connecting means 18 connected to a lantern housing 3, the latter being centered and fastened to a flange of a motor 2 via connecting means 17.
  • a pot-shaped hub 5a is formed on the impeller 5, a recess 5b receiving the impeller-side half of the central rotary coupling 8, 9.
  • Part 8 is a multiplicity of rotationally symmetrically arranged “permanent magnets”, while part 9 represents a soft iron covering that enhances the magnetic effect.
  • the parts 8 and 9 of the impeller-side half of the central rotary coupling are hermetically sealed by the hub 5a and a cover part 10 welded to it on the one hand and a bearing bush 11 on the other hand.
  • a bore formed on the inside of the bearing bush 11 is penetrated concentrically by a partition 6, which is tubular, the latter being accommodated on both sides in the housing parts 1a and 1b in a statically sealing manner via seals 15.
  • the tubular partition 6 serves the hub 5a of the impeller 5 in connection with the bearing bush 11 as a journal.
  • Bearing bush 11 and partition 6 form a bearing ring gap 13.
  • the latter is connected on both sides to an annular space 19 which surrounds the hub 5 a of the impeller 5. Since the impeller 5 is arranged with a lateral play, which is ensured under all operating conditions, in relation to the adjacent housing parts 1a and 1b in the housing 1 of the centrifugal pump; there is a connection between the hub-side annular space 19 and the space of the impeller blades through column 20, which result from the aforementioned game.
  • the partition 6 and the bearing bush 11 are preferably made of a wear-resistant, chemically resistant, high electrical resistance material. Ceramic materials, especially silicon carbides, have proven to be advantageous.
  • the boundary surface of the partition 6 and / or the bearing bush 11 facing the bearing ring gap 13 are or are provided with axial or helical grooves or elevations 14, as a result of which the cleaning action within the bearing ring gap 13 can be intensified.
  • a motor shaft 4 is guided through the motor-side housing part 1b and extends through the tubular partition 6.
  • the motor shaft 4 carries on its circumference in the area of the hub 5a of the impeller 5 another half of the central rotary coupling 7, 12, part 7 being permanent magnets distributed rotationally symmetrically over the circumference, while part 12 represents a soft iron ring which increases the magnetic effect .
  • a flywheel 21 is provided on the motor shaft 4 in the area of the lantern housing 3. While seals 15 seal the partition 6 from the housing parts 1a and 1b to the shaft-side part of the central rotary coupling 7, 12, a housing seal 16 ensures that the housing parts 1a and 1b are sealed from their external environment.
  • the half of the central rotary coupling 7, 12 assigned to it transmits a torque to the half of the central rotary coupling 8, 9 on the impeller side.
  • the two coupling halves 8, 9 and 7, 12 rotate against each other so far that the required torque acts between them.
  • the speed of the motor shaft 4 is transferred to the impeller 5 synchronously. Due to effective pressure differences in the housing 1 of the centrifugal pump, the latter fills with the fluid to be delivered, so that the hub-side annular space 19 and the bearing ring gap 13 connected to it are also acted upon with the fluid to be delivered.
  • the cleaning of the hub-side annular space 19 is unproblematic since a liquid exchange between the latter and the space of the impeller blading is readily provided via the gaps 20, the cleaning of the surfaces delimiting the hub-side annular space 19 by the hub 5a of the impeller rotating in this area 5 is supported extraordinarily intensively.
  • the bearing bush 11 is in turn designed in this area as an impeller. There are several ways to do this. On the one hand, the blades can extend over the entire axial length of the bearing bush 11, on the other hand, the bearing bush is bladed either only at the entry of the bearing ring gap 13 or at its outlet or on both sides.
  • thrust faces 23 which are provided on both sides of the impeller 5 towards the housing parts 1a and 1b, respectively.
  • the radial position of these contact surfaces 23 can be located within the radial extension of the impeller 5, preferably completely inside or outside.
  • the impeller side half of the central rotary coupling 8.9 is hermetically chambered within the recess 5b of the hub 5a, the cover part 10 being welded to the hub 5a and the bearing bush 11, which delimits the chamber for the central rotary coupling 8.9 radially inwardly, with absolutely no leakage the cover part 10 and the hub 5a is cast.
  • Figure 2 shows a meridian section through a further embodiment of the centrifugal pump according to the invention.
  • the pressure port 1d is formed on the motor-side housing part 1b.
  • the hub-side annular space 19, into which the bearing ring gap 13 ends with its two ends, is separated by the impeller 5 into two partial spaces, of which the one arranged to the left of the impeller 5 has a first opening 20 * with a defined passage cross-section with the The area of the suction nozzle 1c and the other is connected in the same way via a second opening 20 ** to the area of the pressure nozzle 1d.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP89116582A 1988-09-13 1989-09-08 Pompe centrifuge sans joint, nettoyable Withdrawn EP0359136A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19883831068 DE3831068A1 (de) 1988-09-13 1988-09-13 Verfahren zur reinigung einer stoffbuchslosen, rotierend arbeitenden foerdereinrichtung fuer fluide

Publications (1)

Publication Number Publication Date
EP0359136A1 true EP0359136A1 (fr) 1990-03-21

Family

ID=6362831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89116582A Withdrawn EP0359136A1 (fr) 1988-09-13 1989-09-08 Pompe centrifuge sans joint, nettoyable

Country Status (3)

Country Link
EP (1) EP0359136A1 (fr)
DE (1) DE3831068A1 (fr)
WO (1) WO1990002880A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29716109U1 (de) * 1997-09-08 1999-01-14 Speck Pumpenfabrik Walter Spec Spalttopfpumpe
CN105179259A (zh) * 2015-07-07 2015-12-23 君禾泵业股份有限公司 带有清洁装置的高效潜水泵及其清洁方法

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4131628A1 (de) * 1991-09-23 1993-03-25 Klein Schanzlin & Becker Ag Taumelscheibenpumpe
FR2733010B1 (fr) * 1995-04-14 1997-07-04 Ceramiques Et Composites Sa Pompe centrifuge a entrainement magnetique
DE19608602A1 (de) * 1996-03-06 1997-09-11 Peter Dipl Ing Mette Stopfbuchslose Strömungsmaschine mit einem Laufrad radialer Bauart
DE10200579B4 (de) * 2002-01-09 2013-06-06 Hilge Gmbh & Co. Kg Selbstansaugende Kreiselpumpe
DE102006053096A1 (de) * 2006-11-10 2008-05-15 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Fluidikeinrichtung und Verfahren zu deren Betrieb

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2002896A1 (fr) * 1968-02-29 1969-10-31 Bignert Folke
JPS5891393A (ja) * 1981-11-26 1983-05-31 Nishigaki Pump Seizo Kk マグネツト駆動ポンプ
EP0184703A1 (fr) * 1984-11-22 1986-06-18 Fuji Photo Film Co., Ltd. Système de pompage magnétique multiple
GB2181184A (en) * 1985-10-09 1987-04-15 Ngk Insulators Ltd Magnetic-drive centrifugal pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1982247U (de) * 1967-05-09 1968-03-28 Gerhard Obermann Kreiselpumpe, ruehrwerk od. dgl. geraet mit fluessigkeitsdurchfluss ohne wellendurchfuehrungsdichtung.
US3420184A (en) * 1967-05-17 1969-01-07 Julius L Englesberg Pump employing magnetic drive
FR2082896A5 (fr) * 1970-03-31 1971-12-10 Inst Francais Du Petrole
GB1496035A (en) * 1974-07-18 1977-12-21 Iwaki Co Ltd Magnetically driven centrifugal pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2002896A1 (fr) * 1968-02-29 1969-10-31 Bignert Folke
JPS5891393A (ja) * 1981-11-26 1983-05-31 Nishigaki Pump Seizo Kk マグネツト駆動ポンプ
EP0184703A1 (fr) * 1984-11-22 1986-06-18 Fuji Photo Film Co., Ltd. Système de pompage magnétique multiple
GB2181184A (en) * 1985-10-09 1987-04-15 Ngk Insulators Ltd Magnetic-drive centrifugal pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Vol. 7, No. 189 (M-237)(1334) 18 August 1983; & JP,A,58 091 393 (NISHIGAKI PONPU SEIZOU) 31 Mai 1983, das ganze Dokument. *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29716109U1 (de) * 1997-09-08 1999-01-14 Speck Pumpenfabrik Walter Spec Spalttopfpumpe
CN105179259A (zh) * 2015-07-07 2015-12-23 君禾泵业股份有限公司 带有清洁装置的高效潜水泵及其清洁方法
CN105179259B (zh) * 2015-07-07 2017-08-22 君禾泵业股份有限公司 带有清洁装置的高效潜水泵及其清洁方法

Also Published As

Publication number Publication date
WO1990002880A1 (fr) 1990-03-22
DE3831068A1 (de) 1990-03-22

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