EP1225342A1 - Impellersystem for pumps - Google Patents

Impellersystem for pumps Download PDF

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Publication number
EP1225342A1
EP1225342A1 EP02000423A EP02000423A EP1225342A1 EP 1225342 A1 EP1225342 A1 EP 1225342A1 EP 02000423 A EP02000423 A EP 02000423A EP 02000423 A EP02000423 A EP 02000423A EP 1225342 A1 EP1225342 A1 EP 1225342A1
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EP
European Patent Office
Prior art keywords
impeller
drive shaft
compensation unit
nut
impeller system
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
EP02000423A
Other languages
German (de)
French (fr)
Other versions
EP1225342B1 (en
Inventor
Klaus Engels
Roland Fach
Stefan Leuchtenberger
Fritz Volz
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.)
Venator Germany GmbH
Original Assignee
Sachtleben Chemie GmbH
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Filing date
Publication date
Application filed by Sachtleben Chemie GmbH filed Critical Sachtleben Chemie GmbH
Publication of EP1225342A1 publication Critical patent/EP1225342A1/en
Application granted granted Critical
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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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • F04D7/065—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals for liquid metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/95—Preventing corrosion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • F05D2300/432—PTFE [PolyTetraFluorEthylene]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/60—Properties or characteristics given to material by treatment or manufacturing
    • F05D2300/615—Filler

Definitions

  • the invention relates to an impeller system for pumps with a in a housing arranged drive shaft with an impeller for conveying liquid media connected is.
  • Circulation pumps are e.g. B. in the chemical industry to promote and / or Circulation of sometimes aggressive media used. So z. B. in one Thin acid recovery plant according to EP 0 476 744 B1 70% sulfuric acid circulated at a temperature of 120 ° C.
  • the invention is based on the object of an impeller system for pumps to improve the preamble of claim 1 so that operational safety and availability is increased and the maintenance costs of the pumps are reduced are.
  • this object is achieved in that the impeller consists of one ceramic material and that the impeller on a compensation unit postponed to absorb the thermal expansion.
  • Ceramic impellers are extremely unaffected by aggressive (corrosive and abrasive) media such.
  • B. sulfuric acid, making their lifespan essential is longer than with impellers made of metallic materials.
  • the invention proposes that the impeller on a compensation unit is postponed to absorb the thermal expansion. hereby the different thermal expansion is absorbed so that it is too no dangerous tensions can arise.
  • the compensation unit is a sleeve with an outer Kammprofile. The impeller is then slid onto this sleeve.
  • the Compensation unit is expedient for a better hold on a socket, such as B. applied a gunmetal bushing.
  • the compensation unit is made of Teflon (PTFE).
  • the comb profile of the compensation unit is preferably perpendicular to the longitudinal axis the drive shaft inclined so that the individual combs fold can.
  • Teflon is advantageously used strength-increasing fillers added.
  • These fillers can z. B. consist of one or more of the following substances: graphite, Talc, chalk, titanium dioxide, silicon carbide, glass particles. Glass particles have become proven to be particularly efficient.
  • the drive shaft is preferably a one-piece hollow shaft.
  • the impeller is in preferred embodiment via an axially the impeller and the drive shaft protruding expansion screw via an impeller nut at the front end the impeller and a lock nut on the drive end of the drive shaft non-positively connected to the drive shaft.
  • the impeller nut advantageously covers the front end of the impeller almost completely.
  • Each between the impeller nut and the impeller and the impeller and The drive shaft is a flat gasket for transmitting the torque and sealing, preferably arranged an elastomer flat seal.
  • Fig. 1 shows more schematically the essential elements of a circulation pump according to the prior art for aggressive media, such.
  • the reference number 17 denotes a pump housing in which an impeller 18 is arranged for circulating the medium.
  • Impeller 18 is pushed directly onto the drive shaft 6 and with a Impeller nut 5 attached.
  • Impeller 18 and drive shaft 6 are made of a metallic Made of material.
  • Fig. 2 shows an impeller system according to the invention as a cross section through the front end of the drive shaft 6 and Fig. 3 by the drive end the drive shaft 6 in the pump housing 17th
  • a one-piece hollow bore shaft 6b runs through the entire pump. On her a shaft sleeve 6a is attached. Shaft 6b and shaft sleeve 6a are in this Registration is often referred to as drive shaft 6 for the sake of simplicity.
  • Impeller 18 At the front end of the drive shaft 6, an impeller 18 is attached.
  • This Impeller 18 according to the invention consists of a ceramic material.
  • Expansion screw 4 which has an impeller nut at its front end 5 and at its drive end (see Fig. 3) has a lock nut 3.
  • the impeller nut 5 covers the front End of the impeller 18 almost completely.
  • the impeller nut 5 is via a threaded adapter 1 and an anti-rotation device 9 attached to the expansion screw 4.
  • an anti-rotation device 9 attached to the expansion screw 4.
  • the reference numeral 11 is the Denoted longitudinal axis of the drive shaft 6.
  • This Compensation unit 2 consists of a sleeve made of Teflon (PTFE) with a outer comb profile 10.
  • the compensation unit 2 is held by a Gunmetal bushing 12, onto which the compensation unit 2 is pushed.
  • the Comb profile 10 of the compensation unit 2 is perpendicular to the longitudinal axis 11 of the Drive shaft 6 slightly inclined, d. H. for the radial expansion of the impeller 18.
  • This comb profile 10 absorbs thermal expansion.
  • the impeller 18 with the gunmetal bushing 12 is on the expansion screw 4 pushed and the expansion screw 4 into the drive shaft 6 or the shaft 6b is plugged in until the impeller 18 with the compensation unit 2 is arranged between the impeller nut 5 and the drive shaft 6. Subsequently the expansion screw 4 at the drive end of the drive shaft 6 via the lock nut 3 z. B. anchored using a torque wrench.
  • This impeller system according to the invention has been in operation for many years proven to be extremely reliable and low-maintenance.

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

Abstract

The rotor wheel system comprises a ceramic rotor wheel connected to a drive shaft (6) mounted in a housing (17). The wheel is pushed onto a compensation unit (2) such as a sleeve with external toothed profile (10) to take up the thermal expansion. The compensation unit can be made from teflon mixed with strengthening fillers such as graphite, titanium dioxide.

Description

Die Erfindung betrifft ein Laufradsystem für Pumpen mit einer in einem Gehäuse angeordneten Antriebswelle, die mit einem Laufrad zum Fördern flüssiger Medien verbunden ist.The invention relates to an impeller system for pumps with a in a housing arranged drive shaft with an impeller for conveying liquid media connected is.

Umwälzpumpen werden z. B. in der chemischen Industrie zum Fördern und/oder Umwälzen von zum Teil aggressiven Medien verwendet. So wird z. B. in einer Dünnsäure-Rückgewinnungsanlage nach der EP 0 476 744 B1 70%ige Schwefelsäure mit einer Temperatur von 120°C umgewälzt.Circulation pumps are e.g. B. in the chemical industry to promote and / or Circulation of sometimes aggressive media used. So z. B. in one Thin acid recovery plant according to EP 0 476 744 B1 70% sulfuric acid circulated at a temperature of 120 ° C.

Derartige aggressive Medien bewirken, dass die Laufräder einer sehr starken Belastung unterliegen und nur eine beschränkte Laufzeit haben. Danach müssen diese Laufräder ausgetauscht werden. Hierzu muss die Pumpe abgestellt werden. Bei einem kontinuierlichen Produktionsprozess muss die zu reparierende Pumpe durch eine funktionierende ersetzt werden. Dies alles bedingt hohe Kosten.Such aggressive media cause the impellers to be very strong Subject to load and have a limited term. After that have to these wheels are replaced. To do this, the pump must be switched off. In a continuous production process, the one to be repaired Pump to be replaced by a working one. All of this entails high costs.

Der Erfindung liegt die Aufgabe zu Grunde, ein Laufradsystem für Pumpen nach dem Oberbegriff des Anspruchs 1 so zu verbessern, dass die Betriebssicherheit und -verfügbarkeit erhöht ist und die Instandhaltungskosten der Pumpen reduziert sind.The invention is based on the object of an impeller system for pumps to improve the preamble of claim 1 so that operational safety and availability is increased and the maintenance costs of the pumps are reduced are.

Erfindungsgemäß wird diese Aufgabe dadurch gelöst, dass das Laufrad aus einem keramischen Werkstoff besteht und dass das Laufrad auf einer Kompensationseinheit zur Aufnahme der Wärmedehnung aufgeschoben ist. According to the invention, this object is achieved in that the impeller consists of one ceramic material and that the impeller on a compensation unit postponed to absorb the thermal expansion.

Keramische Laufräder sind extrem unanfällig gegenüber aggressiven (korrosiv und abrasiv) Medien, wie z. B. Schwefelsäure, so dass ihre Lebensdauer wesentlich länger ist als bei Laufrädern aus metallischen Werkstoffen.Ceramic impellers are extremely unaffected by aggressive (corrosive and abrasive) media such. B. sulfuric acid, making their lifespan essential is longer than with impellers made of metallic materials.

Nachteilig ist jedoch, dass der Wärmeausdehnungskoeffizient von keramischen Laufrädern völlig verschieden von dem der metallischen Antriebswelle ist.The disadvantage, however, is that the coefficient of thermal expansion of ceramic Impellers is completely different from that of the metallic drive shaft.

Aus diesem Grund schlägt die Erfindung vor, dass das Laufrad auf einer Kompensationseinheit zur Aufnahme der Wärmeausdehnung aufgeschoben ist. Hierdurch wird die unterschiedliche Wärmeausdehnung aufgefangen, so dass es zu keinen gefährlichen Spannungen kommen kann.For this reason, the invention proposes that the impeller on a compensation unit is postponed to absorb the thermal expansion. hereby the different thermal expansion is absorbed so that it is too no dangerous tensions can arise.

In bevorzugter Ausführungsform ist die Kompensationseinheit eine Hülse mit äußerem Kammprofil. Auf dieser Hülse ist dann das Laufrad aufgeschoben. Die Kompensationseinheit ist zweckmäßigerweise zum besseren Halt auf eine Buchse, wie z. B. einer Rotgussbuchse aufgebracht.In a preferred embodiment, the compensation unit is a sleeve with an outer Kammprofile. The impeller is then slid onto this sleeve. The Compensation unit is expedient for a better hold on a socket, such as B. applied a gunmetal bushing.

Erfindungsgemäß ist die Kompensationseinheit aus Teflon (PTFE) hergestellt.According to the invention, the compensation unit is made of Teflon (PTFE).

Bevorzugt ist das Kammprofil der Kompensationseinheit senkrecht zur Längsachse der Antriebswelle geneigt, so dass sich die einzelnen Kämme umlegen können.The comb profile of the compensation unit is preferably perpendicular to the longitudinal axis the drive shaft inclined so that the individual combs fold can.

Zur Erhöhung der Lebenszeit der Kompensationseinheit werden dem Teflon vorteilhafterweise festigkeitserhöhende Füllstoffe zugemischt. Diese Füllstoffe können z. B. aus einem oder mehreren der nachfolgenden Stoffe bestehen: Graphit, Talkum, Kreide, Titandioxid, Siliziumkarbid, Glaspartikel. Glaspartikel haben sich als besonders effizient erwiesen. To increase the lifetime of the compensation unit, the Teflon is advantageously used strength-increasing fillers added. These fillers can z. B. consist of one or more of the following substances: graphite, Talc, chalk, titanium dioxide, silicon carbide, glass particles. Glass particles have become proven to be particularly efficient.

Die Antriebswelle ist bevorzugt eine einstückige hohle Welle. Das Laufrad ist in bevorzugter Ausführungsform über eine das Laufrad und die Antriebswelle axial durchragende Dehnschraube über eine Laufradmutter am stirnseiteigen Ende des Laufrades und einer Kontermutter am antriebsseitigen Ende der Antriebswelle mit der Antriebswelle kraftschlüssig verbunden.The drive shaft is preferably a one-piece hollow shaft. The impeller is in preferred embodiment via an axially the impeller and the drive shaft protruding expansion screw via an impeller nut at the front end the impeller and a lock nut on the drive end of the drive shaft non-positively connected to the drive shaft.

Vorteilhafterweise deckt die Laufradmutter das stirnseitige Ende des Laufrades nahezu vollständig ab.The impeller nut advantageously covers the front end of the impeller almost completely.

Jeweils zwischen der Laufradmutter und dem Laufrad und dem Laufrad und der Antriebswelle ist zur Übertragung des Drehmoments und Abdichtung eine Flachdichtung, bevorzugt eine Elastomerflachdichtung angeordnet.Each between the impeller nut and the impeller and the impeller and The drive shaft is a flat gasket for transmitting the torque and sealing, preferably arranged an elastomer flat seal.

Folgende Vorteile hat das erfindungsgemäße Laufradsystem:

  • sehr hohe chemische Beständigkeit
  • hohe Abrasionsfestigkeit
  • bei hohen Temperaturen einsetzbar
  • einsetzbar bei hohen Antriebsleistungen
  • kraftschlüssige Verbindung des Laufrades mit der Antriebswelle.
The impeller system according to the invention has the following advantages:
  • very high chemical resistance
  • high abrasion resistance
  • Can be used at high temperatures
  • can be used with high drive power
  • positive connection of the impeller with the drive shaft.

Weitere Merkmale der Erfindung ergeben sich aus den Figuren, die nachfolgend beschrieben sind. Es zeigt:

Fig. 1
eine Pumpe nach dem Stand der Technik im Querschnitt,
Fig.2
ein erfindungsgemäßes Laufradsystem als Querschnitt durch das stirnseitige Ende und
Fig. 3
durch das antriebsseitige Ende der Antriebswelle.
Further features of the invention emerge from the figures, which are described below. It shows:
Fig. 1
a pump according to the prior art in cross section,
Fig.2
an inventive impeller system as a cross section through the front end and
Fig. 3
through the drive end of the drive shaft.

Fig. 1 zeigt mehr schematisch die wesentlichen Elemente einer Umwälzpumpe nach dem Stand der Technik für aggressive Fördermedien, wie z. B. Schwefelsäure.Fig. 1 shows more schematically the essential elements of a circulation pump according to the prior art for aggressive media, such. B. sulfuric acid.

Mit dem Bezugszeichen 17 ist ein Pumpengehäuse bezeichnet in dem ein Laufrad 18 zum Umwälzen des Fördermediums angeordnet ist.The reference number 17 denotes a pump housing in which an impeller 18 is arranged for circulating the medium.

Das Laufrad 18 ist direkt auf die Antriebswelle 6 aufgeschoben und mit einer Laufradmutter 5 befestigt. Laufrad 18 und Antriebswelle 6 sind aus einem metallischen Werkstoff gefertigt.The impeller 18 is pushed directly onto the drive shaft 6 and with a Impeller nut 5 attached. Impeller 18 and drive shaft 6 are made of a metallic Made of material.

Fig. 2 zeigt ein erfindungsgemäßes Laufradsystem als Querschnitt durch das stirnseitige Ende der Antriebswelle 6 und Fig. 3 durch das antriebsseitige Ende der Antriebswelle 6 in dem Pumpengehäuse 17.Fig. 2 shows an impeller system according to the invention as a cross section through the front end of the drive shaft 6 and Fig. 3 by the drive end the drive shaft 6 in the pump housing 17th

Eine einstückige hohlgebohrte Welle 6b durchzieht die gesamte Pumpe. Auf ihr ist eine Wellenhülse 6a aufgesetzt. Welle 6b und Wellenhülse 6a sind in dieser Anmeldung der Einfachheit halber oft als Antriebswelle 6 bezeichnet.A one-piece hollow bore shaft 6b runs through the entire pump. On her a shaft sleeve 6a is attached. Shaft 6b and shaft sleeve 6a are in this Registration is often referred to as drive shaft 6 for the sake of simplicity.

Am stirnseitigen Ende der Antriebswelle 6 ist ein Laufrad 18 befestigt. Dieses Laufrad 18 besteht erfindungsgemäß aus einem keramischen Werkstoff. Zur Befestigung des Laufrades 18 ist in der Antriebswelle 6 (bzw. der Welle 6b) eine Dehnschraube 4 eingelassen, die an ihrem stirnseitigen Ende eine Laufradmutter 5 und an ihrem antriebsseitigen Ende (siehe Fig. 3) eine Kontermutter 3 aufweist. Zwischen der Laufradmutter 5 und der Antriebswelle 6 bzw. der Wellenhülse 6a ist das Laufrad 18 eingeklemmt. Die Laufradmutter 5 deckt dabei das stirnseitige Ende des Laufrades 18 nahezu vollständig ab.At the front end of the drive shaft 6, an impeller 18 is attached. This Impeller 18 according to the invention consists of a ceramic material. For fixing of the impeller 18 is in the drive shaft 6 (or the shaft 6b) Expansion screw 4, which has an impeller nut at its front end 5 and at its drive end (see Fig. 3) has a lock nut 3. Between the impeller nut 5 and the drive shaft 6 or the shaft sleeve 6a the impeller 18 is jammed. The impeller nut 5 covers the front End of the impeller 18 almost completely.

Zur Übertragung des Drehmoments und Abdichtung ist zwischen der Laufradmutter 5 und dem Laufrad 18 und zwischen der Antriebswelle 6 bzw. der Wellenhülse 6a und dem Laufrad 18 jeweils eine Flachdichtung 7, bevorzugt eine Elastomerflachdichtung angeordnet.To transfer the torque and seal is between the impeller nut 5 and the impeller 18 and between the drive shaft 6 and the shaft sleeve 6a and the impeller 18 each have a flat seal 7, preferably an elastomer flat seal arranged.

Die Laufradmutter 5 ist über einen Gewindeadapter 1 und einer Verdrehsicherung 9 auf der Dehnschraube 4 befestigt. Mit dem Bezugszeichen 11 ist die Längsachse der Antriebswelle 6 bezeichnet.The impeller nut 5 is via a threaded adapter 1 and an anti-rotation device 9 attached to the expansion screw 4. With the reference numeral 11 is the Denoted longitudinal axis of the drive shaft 6.

Ein wesentliches Element der Erfindung ist, dass das Laufrad 18 auf einer Kompensationseinheit 2 zur Aufnahme der Wärmedehnung aufgeschoben ist. Diese Kompensationseinheit 2 besteht aus einer Hülse aus Teflon (PTFE) mit einem äußeren Kammprofil 10. Gehalten wird die Kompensationseinheit 2 von einer Rotgussbuchse 12, auf die die Kompensatinseinheit 2 aufgeschoben ist. Das Kammprofil 10 der Kompensationseinheit 2 ist senkrecht zur Längsachse 11 der Antriebswelle 6 leicht geneigt, d. h. zur radialen Ausdehnung des Laufrades 18.An essential element of the invention is that the impeller 18 on a compensation unit 2 is pushed on to absorb the thermal expansion. This Compensation unit 2 consists of a sleeve made of Teflon (PTFE) with a outer comb profile 10. The compensation unit 2 is held by a Gunmetal bushing 12, onto which the compensation unit 2 is pushed. The Comb profile 10 of the compensation unit 2 is perpendicular to the longitudinal axis 11 of the Drive shaft 6 slightly inclined, d. H. for the radial expansion of the impeller 18.

Dieses Kammprofil 10 fängt Wärmedehnungen auf.This comb profile 10 absorbs thermal expansion.

Bei der Montage der Pumpe wird das Laufrad 18 mit der Rotgussbuchse 12 auf die Dehnschraube 4 geschoben und die Dehnschraube 4 in die Antriebswelle 6 bzw. die Welle 6b gesteckt bis das Laufrad 18 mit der Kompensationseinheit 2 zwischen der Laufradmutter 5 und der Antriebswelle 6 angeordnet ist. Anschließend wird am antriebsseitigen Ende der Antriebswelle 6 die Dehnschraube 4 über die Kontermutter 3 z. B. über einen Drehmomentschlüssel verankert. When installing the pump, the impeller 18 with the gunmetal bushing 12 is on the expansion screw 4 pushed and the expansion screw 4 into the drive shaft 6 or the shaft 6b is plugged in until the impeller 18 with the compensation unit 2 is arranged between the impeller nut 5 and the drive shaft 6. Subsequently the expansion screw 4 at the drive end of the drive shaft 6 via the lock nut 3 z. B. anchored using a torque wrench.

Dieses erfindungsgemäße Laufradsystem hat sich im längjährigen Betrieb als äußerst betriebssicher und wartungsarm erwiesen.This impeller system according to the invention has been in operation for many years proven to be extremely reliable and low-maintenance.

Claims (11)

Laufradsystem für Pumpen mit einer in einem Gehäuse (17) angeordneten Antriebswelle (6), die mit einem Laufrad (18) zum Fördern flüssiger Medien verbunden ist, dadurch gekennzeichnet, dass das Laufrad (18) aus einem keramischen Werkstoff besteht und dass das Laufrad (18) auf einer Kompensationseinheit (2) zur Aufnahme der Wärmedehnung aufgeschoben ist.Impeller system for pumps with a drive shaft (6) arranged in a housing (17), which is connected to an impeller (18) for conveying liquid media, characterized in that the impeller (18) consists of a ceramic material and that the impeller ( 18) is pushed onto a compensation unit (2) for absorbing the thermal expansion. Laufradsystem nach Anspruch 1, dadurch gekennzeichnet, dass die Kompensationseinheit (2) eine Hülse mit äußerem Kammprofil (10) ist.Impeller system according to claim 1, characterized in that the compensation unit (2) is a sleeve with an outer comb profile (10). Laufradsystem nach Anspruch 2, dadurch gekennzeichnet, dass das Kammprofil (10) senkrecht zur Längsachse (11) der Antriebswelle (6) eine Neigung aufweist.Impeller system according to claim 2, characterized in that the comb profile (10) has an inclination perpendicular to the longitudinal axis (11) of the drive shaft (6). Laufradsystem nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Kompensationseinheit (2) aus Teflon hergestellt ist.Impeller system according to one of claims 1 to 3, characterized in that the compensation unit (2) is made of Teflon. Laufradsystem nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Kompensationseinheit (2) auf eine Buchse, insbesondere Rotgussbuchse (12) aufgebracht ist.Impeller system according to one of claims 1 to 4, characterized in that the compensation unit (2) is applied to a bushing, in particular gunmetal bushing (12). Laufradsystem nach Anspruch 4, dadurch gekennzeichnet, dass dem Teflon der Kompensationseinheit (2) festigkeitserhöhende Füllstoffe zugemischt sind.Impeller system according to claim 4, characterized in that the Teflon of the compensation unit (2) strength-increasing fillers are mixed. Laufradsystem nach Anspruch 6, dadurch gekennzeichnet, dass die Füllstoffe aus einem oder mehreren der nachfolgenden Stoffe bestehen: Graphit, Talkum, Kreide, Titandioxid, Siliziumkarbid, Glaspartikel. Impeller system according to claim 6, characterized in that the fillers consist of one or more of the following substances: graphite, talc, chalk, titanium dioxide, silicon carbide, glass particles. Laufradsystem nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Antriebswelle (6) eine einstückige hohle Welle (6b) ist.Impeller system according to one of claims 1 to 7, characterized in that the drive shaft (6) is a one-piece hollow shaft (6b). Laufradsystem nach einem der Ansrüche 1 bis 8, dadurch gekennzeichnet, dass das Laufrad (18) über eine das Laufrad (18) und die Antriebswelle (6) axial durchragende Dehnschraube (4) über eine Laufradmutter (5) am stirnseitigen Ende des Laufrades (18) und einer Kontermutter (3) am antriebsseitigen Ende der Antriebswelle (6) mit der Antriebswelle (6) kraftschlüssig verbunden ist.Impeller system according to one of Claims 1 to 8, characterized in that the impeller (18) via an expansion screw (4) axially projecting through the impeller (18) and the drive shaft (6) via an impeller nut (5) at the front end of the impeller (18 ) and a lock nut (3) on the drive end of the drive shaft (6) with the drive shaft (6) is non-positively connected. Laufradsystem nach Anspruch 9, dadurch gekennzeichnet, dass die Laufradmutter (5) das stirnseitige Ende des Laufrades (18) nahezu vollständig abdeckt.Impeller system according to claim 9, characterized in that the impeller nut (5) almost completely covers the front end of the impeller (18). Laufradsystem nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass jeweils zwischen der Laufradmutter (5) und dem Laufrad (18) und dem Laufrad (18) und der Antriebswelle (6) bzw. der Wellenhülse (6a) zur Übertragung des Drehmomentes und Abdichtung eine Flachdichtung (7), bevorzugt Elastomerflachdichtung angeordnet ist.Impeller system according to claim 9 or 10, characterized in that between the impeller nut (5) and the impeller (18) and the impeller (18) and the drive shaft (6) or the shaft sleeve (6a) for transmitting the torque and sealing one Flat gasket (7), preferably elastomer flat gasket is arranged.
EP02000423A 2001-01-18 2002-01-08 Impellersystem for pumps Expired - Lifetime EP1225342B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10102104 2001-01-18
DE10102104A DE10102104A1 (en) 2001-01-18 2001-01-18 Impeller system for pumps

Publications (2)

Publication Number Publication Date
EP1225342A1 true EP1225342A1 (en) 2002-07-24
EP1225342B1 EP1225342B1 (en) 2010-05-05

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Family Applications (1)

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EP02000423A Expired - Lifetime EP1225342B1 (en) 2001-01-18 2002-01-08 Impellersystem for pumps

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EP (1) EP1225342B1 (en)
AT (1) ATE467052T1 (en)
DE (2) DE10102104A1 (en)
ES (1) ES2345762T3 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2433589A (en) * 1939-05-25 1947-12-30 Nash Engineering Co Pump
US3255702A (en) 1964-02-27 1966-06-14 Molten Metal Systems Inc Hot liquid metal pumps
US5249869A (en) * 1991-05-21 1993-10-05 Sundstrand Corporation Preloaded assembly with thermal compensation
EP0476744B1 (en) 1990-09-20 1995-04-05 METALLGESELLSCHAFT Aktiengesellschaft Process for the concentration of diluted acid in a three-stage vacuum evaporator system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3738081A1 (en) * 1987-11-10 1989-05-18 Rheinhuette Vorm Ludwig Beck G CONNECTION FOR MATERIALS OF DIFFERENT HEAT EXPANSION
DE4336687C2 (en) * 1992-10-27 2001-12-06 Piller Industrieventilatoren G Rotor unit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2433589A (en) * 1939-05-25 1947-12-30 Nash Engineering Co Pump
US3255702A (en) 1964-02-27 1966-06-14 Molten Metal Systems Inc Hot liquid metal pumps
EP0476744B1 (en) 1990-09-20 1995-04-05 METALLGESELLSCHAFT Aktiengesellschaft Process for the concentration of diluted acid in a three-stage vacuum evaporator system
US5249869A (en) * 1991-05-21 1993-10-05 Sundstrand Corporation Preloaded assembly with thermal compensation

Also Published As

Publication number Publication date
EP1225342B1 (en) 2010-05-05
ES2345762T3 (en) 2010-10-01
ATE467052T1 (en) 2010-05-15
DE10102104A1 (en) 2002-07-25
DE50214406D1 (en) 2010-06-17

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