WO1990002880A1 - Pompe centrifuge nettoyable sans presse-etoupe - Google Patents

Pompe centrifuge nettoyable sans presse-etoupe Download PDF

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Publication number
WO1990002880A1
WO1990002880A1 PCT/EP1989/001044 EP8901044W WO9002880A1 WO 1990002880 A1 WO1990002880 A1 WO 1990002880A1 EP 8901044 W EP8901044 W EP 8901044W WO 9002880 A1 WO9002880 A1 WO 9002880A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
centrifugal pump
cleanable
pump according
glandless
Prior art date
Application number
PCT/EP1989/001044
Other languages
German (de)
English (en)
Inventor
Peter Mette
Wilfried Lehmann
Rainer Landowski
Original Assignee
Otto Tuchenhagen Gmbh & Co Kg
Sihi Gmbh & 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 & Co Kg, Sihi Gmbh & Co Kg filed Critical Otto Tuchenhagen Gmbh & Co Kg
Publication of WO1990002880A1 publication Critical patent/WO1990002880A1/fr

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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 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 rotating couplings use the attraction and repulsion forces between magnets in two coupling halves. They serve 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 are known, 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 magnet rotor which is also equipped with permanent magnets, is arranged within this containment shell. This, in turn, is supported 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 magnet rotor is fastened to the impeller at an axial distance from it via a connecting part.
  • the connecting part also serves to support 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 the bearing of the impeller in connection with the inner magnet rotor is usually carried out via the pump to be pumped
  • the well-known design of the containment shell has a cavity which with the over the bearing gap of the plain bearing
  • Impeller housing is connected. Due to the
  • the known centrifugal pumps are from the aforementioned
  • CIP cleaning in place
  • the glandless centrifugal pump has a particularly simple and easy-to-clean design.
  • centrifugal pumps are usually designed so that the hydraulic efficiency is as high as possible. This is achieved, among other things, by making the liquid-loaded gaps between stationary and moving components as small as possible.
  • the centrifugal pump according to the invention 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. Due to the mechanism of action of the pump, there is a pressure difference in the fluid between the suction and pressure ports within the pump housing, which pressure difference is used to flow through the column in question in a defined radial and axial direction. A deterioration of the associated with this gap flow
  • 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.
  • a further advantageous embodiment of the centrifugal pump according to the invention provides a hub-side annular space separated by the impeller into two subspaces, one of which has a first opening with a defined passage cross-section with the area of the suction nozzle and the other in the same way via a second opening with the Area of the pressure nozzle is connected. This results as a result of the formed between the suction and discharge nozzle
  • Pressure difference is a particularly pronounced, defined, in the radial and axial direction between stationary and moving components oriented gap flow within the housing of the conveyor.
  • 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 for measures to be taken in the bearing ring gap and / or at its entry
  • centrifugal pump provides that a bearing bush arranged in the impeller in
  • another embodiment of the centrifugal pump according to the invention provides that the bearing ring gap facing
  • Boundary surface of the partition wall and / or the bearing blocks are or are provided with axial or helical grooves or elevations.
  • Invention provides is for a compact arrangement
  • 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 also promotes the conveyance of the fluid under hygienic or sterile conditions or bacteriologically perfect conditions guaranteed.
  • Centrifugal pump according to the invention 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.
  • Embodiment of the centrifugal pump according to the invention that the bearing bush is provided on both sides with a thrust surface limiting its axial displacement 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.
  • Centrifugal pump regardless of Conveying task between the suction and pressure ports required pressure difference, in each application, to provide a minimum pressure difference to ensure the gap flow.
  • An embodiment of the invention is shown in the drawing and will be described in more detail below.
  • FIG. 2 shows a meridian section through another embodiment of the centrifugal pump according to the invention with a
  • FIG. 1 shows, representative of other centrifugal pumps, a meridian section through a so-called self-priming side channel pump. It should be particularly emphasized at this point that 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, a reversal of the conveying direction being 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 le.
  • 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 half of the central rotary coupling 8, 9 on the impeller side.
  • Part 8 is a multiplicity of rotationally symmetrically arranged “permanent magnets”, while part 9 has a 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
  • Bearing ring gap 13 The latter is on both sides with one
  • Housing 1 of the centrifugal pump is arranged by
  • Bearing bushing 11 preferably consist of a wear-resistant, chemically resistant, high electrical one
  • Resistant 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 effect within the
  • Bearing ring gap 13 can intensify.
  • a motor shaft 4 is passed 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 arranged symmetrically distributed over the circumference, while part 12 is a soft iron ring which reinforces the magnetic effect represents.
  • a flywheel 21 is provided on the motor shaft 4 in the area of the lantern housing 3. While seals 15, the partition 6 opposite the housing parts 1a and 1b to the shaft-side part of the central rotary coupling 7, 12
  • a housing seal 16 ensures a sealing of the housing parts 1a and 1b from their external environment.
  • Annulus 19 on both sides of the impeller 5 results in a Flow through the bearing ring gap 13, so that in it on the one hand the fluid flow required for the hydrodynamic lubrication effect and on the other the cleaning flow required for its cleaning with cleaning agent is ensured.
  • 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.
  • contact surfaces 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 vary within the radial extension of the impeller 5,
  • the impeller-side half of the central rotary coupling 6, 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 inward, with an absolutely tight seal 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.
  • Partial spaces are separated, of which the one arranged to the left of the impeller 5 has a defined opening via a first opening 20 *
  • Passage cross section is connected to the area of the suction port 1c and the other in the same way via a second opening 20 to the area of the pressure port 1d.
  • Partial space of the hub-side annular space 19 From here, the fluid penetrates into the entire circumference of the bearing ring gap 13, flows through it, into the partial space of the hub-side located to the left of the impeller 5

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Une pompe centrifuge nettoyable sans presse-étoupe, notamment une pompe regénérative, comporte au moins un rotor (5) entraîné au moyen d'un accouplement tournant magnétique à transmission synchrone logé à l'intérieur de ce dernier. Les deux moitiés de l'accouplement sont mutuellement séparées par une cloison (6) qui délimite l'espace pour le fluide à refouler à l'encontre de la pression atmosphérique et qui est reliée solidairement et hermétiquement avec le carter de pompe (1). Une moitié de l'accouplement tournant (7, 12) est montée dans ou sur le rotor (5), et la cloison (6) traversant concentriquement ce dernier, lui sert de tourillon et, conjointement avec lui, forme un passage annulaire de portée (13). La cloison (6) est tubulaire et scellée de manière statique des deux côtés du rotor (5) dans le carter de la pompe centrifuge (1; 1a, 1b). Le passage annulaire de portée (13) est relié, directement ou indirectement, avec une région de la tubulure d'aspiration (1c) et avec une région de la tubulure de refoulement (1d).
PCT/EP1989/001044 1988-09-13 1989-09-08 Pompe centrifuge nettoyable sans presse-etoupe WO1990002880A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3831068.6 1988-09-13
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
WO1990002880A1 true WO1990002880A1 (fr) 1990-03-22

Family

ID=6362831

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1989/001044 WO1990002880A1 (fr) 1988-09-13 1989-09-08 Pompe centrifuge nettoyable sans presse-etoupe

Country Status (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996032592A1 (fr) * 1995-04-14 1996-10-17 Ceramiques & Composites S.A. Pompe centrifuge a entrainement magnetique

Families Citing this family (6)

* 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
DE19608602A1 (de) * 1996-03-06 1997-09-11 Peter Dipl Ing Mette Stopfbuchslose Strömungsmaschine mit einem Laufrad radialer Bauart
DE29716109U1 (de) * 1997-09-08 1999-01-14 Speck Pumpenfabrik Walter Spec Spalttopfpumpe
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
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2082896A5 (fr) * 1970-03-31 1971-12-10 Inst Francais Du Petrole
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
SE331922B (fr) * 1968-02-29 1971-01-18 F Bignert
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
FR2082896A5 (fr) * 1970-03-31 1971-12-10 Inst Francais Du Petrole
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 May 1983. *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Also Published As

Publication number Publication date
DE3831068A1 (de) 1990-03-22
EP0359136A1 (fr) 1990-03-21

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