EP1625304A1 - Multistage centrifugal pump - Google Patents

Multistage centrifugal pump

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Publication number
EP1625304A1
EP1625304A1 EP04731592A EP04731592A EP1625304A1 EP 1625304 A1 EP1625304 A1 EP 1625304A1 EP 04731592 A EP04731592 A EP 04731592A EP 04731592 A EP04731592 A EP 04731592A EP 1625304 A1 EP1625304 A1 EP 1625304A1
Authority
EP
European Patent Office
Prior art keywords
pump
bearing
centrifugal pump
stage
centrifugal
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
EP04731592A
Other languages
German (de)
French (fr)
Other versions
EP1625304B1 (en
Inventor
Jörg Urban
Wolfgang Kochanowski
Bernhard Brecht
Stephan Scharpf
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KSB AG
Original Assignee
KSB AG
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Publication date
Application filed by KSB AG filed Critical KSB AG
Publication of EP1625304A1 publication Critical patent/EP1625304A1/en
Application granted granted Critical
Publication of EP1625304B1 publication Critical patent/EP1625304B1/en
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Anticipated expiration legal-status Critical

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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
    • F04D29/043—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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • 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
    • F04D29/047—Bearings hydrostatic; hydrodynamic

Definitions

  • the invention relates to a multi-stage centrifugal pump in which each pump stage comprises a housing consisting of one or more parts and an impeller disposed therein, the pump stages being arranged between inlet and outlet end pieces for connection to fluid-carrying systems and held therewith by connecting means. All impellers are arranged on a pump shaft supported in at least two pump bearings, a pump shaft end is provided with a receptacle for a connection means of a drive, and external support means are arranged for attaching the centrifugal pump to an installation location in the region of the end pieces.
  • centrifugal pumps constructed as link pumps are designed to convey a fluid to a high pressure level. They are designed as separate devices, the pump shaft with the interposition of a coupling element with a drive machine, such as an electric motor or a turbine, are connected. Centrifugal pump and drive machine are mounted together on a base plate or on a foundation. They are often used as multi-stage feed pumps in power plants or other facilities where a high pressure is required. As a result of the multi-stage construction and the arrangement of the pump stages between the end pieces can easily be adapted to different operating conditions during their manufacture by the number and type of pump stages is varied. For this purpose, the connecting means and the pump shaft are tuned to the corresponding overall length of the centrifugal pump and a base plate or a pump foundation is to be formed according to the overall length.
  • centrifugal pumps are known from DE 22 04 995 A1, DE 26 14 163 B1 and KSB-Kumblelpumpenlexikon, 3rd updated edition, page 185.
  • the pump shafts are arranged outside and at a distance from the end pieces of the centrifugal pump.
  • the distance between the pump bearings increases a necessary space for the shaft seals to be mounted, with which a liquid outlet is prevented from the housing of the centrifugal pump.
  • a consequent large bearing distance between the shaft bearings is disadvantageous because unfavorable vibrations of the rotating component can result.
  • the inclusion of pipeline forces, which are passed through the end pieces in the centrifugal pump negatively affects the balance of power of the centrifugal pump.
  • centrifugal pumps For attachment of such centrifugal pumps at the respective site serve external support means which are provided on the end pieces or between the end pieces of the centrifugal pump.
  • An unfavorably chosen location of these outer support means which are generally designed as feet, ridges or struts, may adversely affect the vibration performance of the rotating components with respect to a built-in centrifugal pump.
  • the invention is based on the problem of optimizing the vibration behavior of the rotating system in a multi-stage centrifugal pump and to allow operation at higher speeds.
  • the solution to this problem provides, a bearing distance L ⁇ _ between facing bearing faces of two pump bearings with the greatest distance from each other, smaller or equal to the product of a minimum devisnbauhohe LM multiplied by the reduced by the value 1 number of pump stages.
  • a particularly rigid design of the rotating part, also called rotor, a centrifugal pump is achieved.
  • a bearing end face of pump bearings in the form of sliding bearings is arranged at the point at which a sliding bearing gap has its beginning or its inlet opening.
  • the shaft bearing is located in the immediate vicinity of the highly loaded wheels.
  • the decisive for the bearing distance minimum istnbauhohe L is determined by a projected onto the pump shaft, measured in the axial direction minimum center distance between two downstream impeller outlet widths. Likewise, it could also be used a distance between the impeller entrances of downstream wheels.
  • Embodiments provide that a pressure-side pump bearing is arranged in a manner known per se in the direction of the pump shaft projection of the pressure nozzle cross-section.
  • a pressure-side pump bearing can be arranged in a last pump stage, or a pressure-side pump bearing is arranged between or in pump stages, which are preceded by a last pump stage in the flow direction.
  • the shortening of the bearing distance serve the measures that a suction-side pump bearing is arranged in a first pump stage and that a suction-side pump bearing is disposed between or in subsequent pump stages, which follow a first pump stage.
  • outer pump bearing those bearings are considered, which are closest to the respective pressure or suction end of the pump shaft and between which all or part of the wheels are arranged by the pump stages on the pump shaft.
  • a pump stage is formed by an impeller with the surrounding, consisting of one or more flow-guiding parts housing.
  • Special additional components such as inducer, compensation devices, auxiliary wheels or seals do not constitute pump stages in this context.
  • a rigid pump design results when a distance between bearing centers of two outer pump bearings LL is equal to or smaller than a distance to be measured in the shaft direction LA between the support means. Since the support means are arranged in the region of the end pieces, this results in an overall improved vibration behavior. For this results in a particularly large-scale arrangement of the support means, whereby the attachment of the centrifugal pump is particularly stable at its later site. Acting on the centrifugal pump Pipe forces are thus conducted safely and without negative effects on the rotating pump part in a foundation.
  • the connecting means are arranged on the end pieces, whereby the cohesion of the main parts of the centrifugal pump is ensured.
  • suction-side bearing of the pump shaft is always arranged within the pump housing, compared to a bearing arrangement in which the pump bearings are arranged outside the pressurized housing, an additional shaft seal is saved and there is an improvement in operational safety.
  • the shortened bearing clearance improves overall the vibration behavior of the rotating component.
  • a pressure-side bearing is arranged in the outlet end piece. This measure also improves the power flow between a pipe to be connected to the centrifugal pump and a foundation at the installation site. A possible rectilinear force flow exerts no negative effect on the vibration behavior of the rotating part.
  • the inlet and / or outlet end pieces are designed as separate components and are force-transmitting to pump stage parts. Likewise, the inlet and / or outlet end pieces may be integral parts of pump stage parts.
  • a minimum bearing distance LLmin to be measured between mutually facing bearing faces is determined by a number of pump stages reduced by a value of 2 to 5 multiplied by a minimum tier height.
  • Fig. 1 shows a section through a centrifugal pump
  • Fig. 2 is a suction side bearing assembly.
  • a five-stage centrifugal pump is shown, the wheels 1 rotate in the housings 2 each stage and which are mounted together on a pump shaft 3.
  • the pump stages are arranged between an inlet end piece 4 and an outlet end piece 6 and have pump stage parts 2.1 - 2.5, which are designed to be pressure-bearing and accommodate further flow-leading internals.
  • the pump stage parts 2.1 - 2.4 are designed as equal parts.
  • the inlet end piece 4 is formed in two parts in the lower half of the embodiment, wherein the separate, annular component 4 rests on the pump stage part 2.6 of the first stage to transmit power.
  • This pump stage part 2.6 simultaneously contains the suction opening 5 of the centrifugal pump and performs the function of a housing cover.
  • the pump stage part 2.6 of the first stage is an integral part of the inlet end piece 4 and thus forms a component.
  • the pump stage 2.5 is made longer than the preceding pump stage parts 2.1 - 2.4 of the other pump stages. It contains a larger collecting space, from which a discharge nozzle 7 discharges, by means of which a conveyed fluid is passed into a pipeline system to be connected.
  • the outlet end piece 6 is executed in the lower half of the drawing as a separate, annular component and shown in the upper half of the drawing as an integral part of the housing 2.5. It also forms the abutment for external connection means 8, with which all pump parts are held together.
  • connecting means 8 tie rods are here shown, which are passed through corresponding openings of the end pieces 4, 6 and ensure the cohesion of the centrifugal pump by means of screw elements.
  • support means 9, 10 are arranged, which allow attachment of the centrifugal pump at its future installation.
  • the distance LA between the support means 9, 10 is greater than the distance LL between the bearings 11, 12 of the pump shaft 3. A to be connected to a drive shaft end
  • This fifth pump stage has a collar 14 which, starting from the drive-side end of the pump stage part 2.5, projects on a smaller diameter into the pump stage part 2.5 and thus forms the receptacle for the bearing 11. In addition, there is enough free space in this collar o 14 to arrange an axial thrust balancing device 15 therein.
  • the bearing 11 is approximately in the middle of the pressure port 7, whereby a good flow of forces with respect to male pipe forces or derived 5 vibration forces is possible.
  • suction side bearing 12 of the pump shaft 3 is arranged in this embodiment between the first and second pump stage and is supported here within the housing 2.1 of the first stage.
  • the bearings 11 and 12 are formed as medium-lubricated bearings and are lubricated by the pumped liquid.
  • the bearings can be designed as plain bearings and / or as rolling bearings. Their selection depends on the fluid to be delivered and the bearing load that occurs.
  • the medium-lubricated bearings eliminate service intervals for otherwise used bearing lubrication.
  • Suction opening 5 and the discharge nozzle 7 act on the centrifugal pump, taken in terms of the vibration behavior in an optimal manner. Due to the very short bearing distance LL of the rotating part of the multi-stage centrifugal pump results in an extremely high vibration resistance of the rotating system, where is significantly improved by the reliability of such a centrifugal pump.
  • end pieces 4, 6 as separate components has the additional advantage that they can be made of a different material. If due to a fluid to be conveyed liquid wetted components must consist of high quality stainless steel, then in cost-reducing manner, the parts of the end pieces, with which the connecting means 8 are connected to transmit power, made of a cheaper material.
  • Fig. 2 shows the use of an inlet star, which is located within the suction opening 5. It has a bearing pin 17 which cooperates with the suction-side pump bearing 12.
  • the pump bearing 12 is in this case installed in the form of a sleeve within a bore 18 of the suction side shaft end 18 here. By appropriate further, not shown lubrication holes, a liquid circulation is ensured by the pump bearing 12.

Abstract

A multistage centrifugal pump in which each stage includes a one-piece or multi-piece housing and an impeller disposed therein. The pump stages are arranged between an inlet end member and an outlet end member and retained therebetween by connectors so as to be connected to a flow-guiding system. All impellers are positioned on a single pump shaft that is supported by at least two pump bearings. One end of the pump shaft is provided with a device for receiving a connector of a drive unit, and outer support members are disposed at mounting points adjacent the end members in order to mount the centrifugal pump in its installation location. The pump shaft ( 3 ) is supported by two two pump bearings ( 11, 12 ), with the maximum distance (L<SUB>L</SUB>) between confronting sides of the two pump bearings ( 11, 12 ) being less than or equal to a minimum structural stage height (L<SUB>M</SUB>) multiplied by the number of pump stages ( 2.1 - 2.5 ) minus 1.

Description

Beschreibung description
Mehrstufige KreiselpumpeMulti-stage centrifugal pump
Die Erfindung betrifft eine Kreiselpumpe mehrstufiger Bauart, bei der jede Pumpenstufe ein aus einem oder mehreren Teilen bestehendes Gehäuse und ein darin angeordnetes Laufrad aufweist, für einen Anschluss an strömungsführende Systeme die Pumpenstufen zwischen Einlass- und Auslass-Endstücken angeordnet und dazwischen mit Verbindungsmitteln gehalten sind, auf einer in mindestens zwei Pum- penlagern abgestützten Pumpenwelle alle Laufräder angeordnet sind, ein Pumpen- wellenende mit einer Aufnahme für ein Verbindungsmittel eines Antriebes versehen ist und zur Befestigung der Kreiselpumpe an einem Aufstellort im Bereich der Endstücke äußere Auflagemittel angeordnet sind.The invention relates to a multi-stage centrifugal pump in which each pump stage comprises a housing consisting of one or more parts and an impeller disposed therein, the pump stages being arranged between inlet and outlet end pieces for connection to fluid-carrying systems and held therewith by connecting means. All impellers are arranged on a pump shaft supported in at least two pump bearings, a pump shaft end is provided with a receptacle for a connection means of a drive, and external support means are arranged for attaching the centrifugal pump to an installation location in the region of the end pieces.
Derartige als Gliederpumpen ausgebildete Kreiselpumpen sind dazu ausgelegt, ein Fluid auf ein hohes Druckniveau zu fördern. Sie sind als eigenständige Geräte ausgebildet, deren Pumpenwelle unter Zwischenschaltung eines Kupplungselementes mit einer Antriebsmaschine, beispielsweise eines Elektromotors oder eine Turbine, verbunden sind. Kreiselpumpe und Antriebsmaschine werden zusammen auf einer Grundplatte oder auf einem Fundament montiert. Sie finden häufig Anwendung als mehrstufige Speisepumpen in Kraftwerksanlagen oder sonstigen Einrichtungen, bei denen ein hoher Druck gefordert ist. Infolge des mehrstufigen Aufbaues und der Anordnung der Pumpenstufen zwischen den Endstücken kann bei deren Herstellung in einfacherWeise eine Anpassung an unterschiedliche Betriebsbedingungen erfolgen, indem die Anzahl und die Bauart der Pumpenstufen variiert wird. Dazu sind die Verbindungsmittel und die Pumpenwelle auf die entsprechende Gesamtlänge der Kreiselpumpe abzustimmen und eine Grundplatte oder ein Pumpenfundament ist entsprechend der Baulänge auszubilden.Such centrifugal pumps constructed as link pumps are designed to convey a fluid to a high pressure level. They are designed as separate devices, the pump shaft with the interposition of a coupling element with a drive machine, such as an electric motor or a turbine, are connected. Centrifugal pump and drive machine are mounted together on a base plate or on a foundation. They are often used as multi-stage feed pumps in power plants or other facilities where a high pressure is required. As a result of the multi-stage construction and the arrangement of the pump stages between the end pieces can easily be adapted to different operating conditions during their manufacture by the number and type of pump stages is varied. For this purpose, the connecting means and the pump shaft are tuned to the corresponding overall length of the centrifugal pump and a base plate or a pump foundation is to be formed according to the overall length.
Solche gattungsgemäßen Bauarten von Kreiselpumpen sind durch die DE 22 04 995 A1 , die DE 26 14 163 B1 und durch das KSB-Kreiselpumpenlexikon, 3. aktualisierte Auflage, Seite 185, bekannt. Bei diesen mehrstufigen Gliederpumpen sind die jewei- ligen Pumpenlager der Pumpenwellen außerhalb und mit Abstand zu den Endstük- ken der Kreiselpumpe angeordnet. Den Abstand zwischen den Pumpenlagern vergrößert ein notwendiger Raum für die anzubringenden Wellenabdichtungen, mit denen ein Flüssigkeitsaustritt aus dem Gehäuse der Kreiselpumpe verhindert wird. Aus schwingungstechnischer Sicht ist ein dadurch bedingter großer Lagerabstand zwischen den Wellenlagern nachteilig, da daraus ungünstige Schwingungen des rotierenden Bauteiles resultieren können. Und die Aufnahme von Rohrleitungskräften, die über die Endstücke in die Kreiselpumpe geleitet werden, beeinflußt die Kräfteverhältnisse der Kreiselpumpe negativ.Such generic types of centrifugal pumps are known from DE 22 04 995 A1, DE 26 14 163 B1 and KSB-Kreiselpumpenlexikon, 3rd updated edition, page 185. With these multi-stage segment pumps, the respective The pump shafts are arranged outside and at a distance from the end pieces of the centrifugal pump. The distance between the pump bearings increases a necessary space for the shaft seals to be mounted, with which a liquid outlet is prevented from the housing of the centrifugal pump. From a vibration point of view, a consequent large bearing distance between the shaft bearings is disadvantageous because unfavorable vibrations of the rotating component can result. And the inclusion of pipeline forces, which are passed through the end pieces in the centrifugal pump, negatively affects the balance of power of the centrifugal pump.
Zur Befestigung solcher Kreiselpumpen am jeweiligen Einsatzort dienen äußere Auflagemittel, die an den Endstücken oder auch zwischen den Endstücken der Kreiselpumpe vorgesehen sind. Eine ungünstig gewählte Lage dieser äußeren Auflagemittel, die allgemein als Füße, Leisten oder Streben gestaltet sind, kann in Bezug auf eine eingebaute Kreiselpumpe nachteilige Auswirkungen auf das Schwingungsverhalten der rotierenden Bauteile ausüben.For attachment of such centrifugal pumps at the respective site serve external support means which are provided on the end pieces or between the end pieces of the centrifugal pump. An unfavorably chosen location of these outer support means, which are generally designed as feet, ridges or struts, may adversely affect the vibration performance of the rotating components with respect to a built-in centrifugal pump.
Der Erfindung liegt das Problem zugrunde, bei einer mehrstufigen Kreiselpumpe das Schwingungsverhalten des rotierenden Systems zu optimieren und einen Betrieb mit höheren Drehzahlen zu ermöglichen. Die Lösung dieses Problems sieht vor, ein Lagerabstand Lι_ zwischen einander zugewandten Lagerstirnseiten von zwei Pumpenlagern mit größtem Abstand zueinander, kleiner oder gleich ist dem Produkt aus einer minimalen Stufenbauhohe LM multipliziert mit der um den Wert 1 reduzierten Anzahl der Pumpenstufen.The invention is based on the problem of optimizing the vibration behavior of the rotating system in a multi-stage centrifugal pump and to allow operation at higher speeds. The solution to this problem provides, a bearing distance Lι_ between facing bearing faces of two pump bearings with the greatest distance from each other, smaller or equal to the product of a minimum Stufenbauhohe LM multiplied by the reduced by the value 1 number of pump stages.
Mit dieser Lösung wird eine besonders steife Ausbildung des rotierenden Teiles, auch Rotor genannt, einer Kreiselpumpe erreicht. Dabei ist eine Lagerstirnseite von Pumpenlagern in Form von Gleitlagern an derjenigen Stelle angeordnet, an der ein Gleitlagerspalt seinen Anfang oder seine Einströmöffnung hat. Bei Wälzlagern ist es die den kleinsten Abstand gewährleistende Stirnfläche eines Lagerringes. Durch den äußerst kurzen Abstand zwischen den Pumpenlagern ergibt sich eine besonders stabilisierende Ausbildung des gesamten rotierenden Systems. Und die Wellenlagerung ist in unmittelbarer Nähe der hochbelasteten Laufräder angeordnet. Die für den Lagerabstand maßgebende minimale Stufenbauhohe L wird ermittelt durch einen auf die Pumpenwelle projizierten, in axialer Richtung gemessenen minimalen Mittenabstand zwischen zwei einander nachgeschalteten Laufradaustrittsbreiten. Ebenso könnte dazu auch ein Abstand zwischen den Laufradeintritten von einander nachgeschalteten Laufrädern verwendet werden.With this solution, a particularly rigid design of the rotating part, also called rotor, a centrifugal pump is achieved. In this case, a bearing end face of pump bearings in the form of sliding bearings is arranged at the point at which a sliding bearing gap has its beginning or its inlet opening. For rolling bearings, it is the smallest distance guaranteeing face of a bearing ring. The extremely short distance between the pump bearings results in a particularly stabilizing design of the entire rotating system. And the shaft bearing is located in the immediate vicinity of the highly loaded wheels. The decisive for the bearing distance minimum Stufenbauhohe L is determined by a projected onto the pump shaft, measured in the axial direction minimum center distance between two downstream impeller outlet widths. Likewise, it could also be used a distance between the impeller entrances of downstream wheels.
Ausgestaltungen sehen vor, dass ein druckseitiges Pumpenlager in an sich bekannter Weise in der auf die Pumpenwelle gerichteten Projektion des Druckstutzenquerschnittes angeordnet ist. Ebenso kann ein druckseitiges Pumpenlager in einer letzten Pumpenstufe angeordnet, oder ein druckseitiges Pumpenlager ist zwischen oder in Pumpenstufen angeordnet, die einer letzten Pumpenstufe in Strömungsrichtung vorangestellt sind. Mittels dieser Maßnahme ergibt sich, insbesondere bei Kreiselpumpen mit einer zweistelligen Anzahl von Pumpenstufen, eine wesentlich steifere Anordnung eines aus Welle und Laufrädern bestehenden Rotors.Embodiments provide that a pressure-side pump bearing is arranged in a manner known per se in the direction of the pump shaft projection of the pressure nozzle cross-section. Likewise, a pressure-side pump bearing can be arranged in a last pump stage, or a pressure-side pump bearing is arranged between or in pump stages, which are preceded by a last pump stage in the flow direction. By means of this measure results, in particular in centrifugal pumps with a two-digit number of pump stages, a much stiffer arrangement of a shaft and impellers existing rotor.
Ebenfalls der Verkürzung des Lagerabstandes dienen die Maßnahmen, dass ein saugseitiges Pumpenlager in einer ersten Pumpenstufe angeordnet ist und dass ein saugseitiges Pumpenlager zwischen oder in nachfolgenden Pumpenstufen angeordnet ist, die auf eine erste Pumpenstufe nachfolgen.Also, the shortening of the bearing distance serve the measures that a suction-side pump bearing is arranged in a first pump stage and that a suction-side pump bearing is disposed between or in subsequent pump stages, which follow a first pump stage.
Als äußere Pumpenlager werden diejenigen Lager angesehen, die dem jeweiligen druck- oder saugseitigen Ende der Pumpenwelle am nächsten liegen und zwischen denen auf der Pumpenwelle alle oder ein Teil der Laufräder von den Pumpenstufen angeordnet sind. Und eine Pumpenstufe wird gebildet von einem Laufrad mit dem umgebenden, aus einem oder mehreren strömungsführenden Teilen bestehenden Gehäuse. Spezielle Zusatzbauteile, wie Inducer, Ausgleichseinrichtungen, Hilfslauf- räder oder Dichtungen stellen in diesem Zusammenhang keine Pumpenstufen dar.As outer pump bearing those bearings are considered, which are closest to the respective pressure or suction end of the pump shaft and between which all or part of the wheels are arranged by the pump stages on the pump shaft. And a pump stage is formed by an impeller with the surrounding, consisting of one or more flow-guiding parts housing. Special additional components such as inducer, compensation devices, auxiliary wheels or seals do not constitute pump stages in this context.
Eine steife Pumpenbauweise ergibt sich, wenn ein Abstand zwischen Lagermitten von zwei äußeren Pumpenlagern LL gleich oder kleiner ist als ein in Wellenrichtung zu messender Abstand LA zwischen den Auflagemitteln. Da die Auflagemittel im Bereich der Endstücke angeordnet sind, ergibt sich somit ein insgesamt verbessertes Schwingungsverhalten. Denn es ergibt sich somit eine besonders großflächige Anordnung der Auflagemittel, wodurch die Befestigung der Kreiselpumpe an ihrem späteren Aufstellungsort besonders stabil ist. Auf die Kreiselpumpe einwirkende Rohrleitungskräfte werden somit sicher und ohne negative Auswirkungen auf den rotierenden Pumpenteil in ein Fundament geleitet.A rigid pump design results when a distance between bearing centers of two outer pump bearings LL is equal to or smaller than a distance to be measured in the shaft direction LA between the support means. Since the support means are arranged in the region of the end pieces, this results in an overall improved vibration behavior. For this results in a particularly large-scale arrangement of the support means, whereby the attachment of the centrifugal pump is particularly stable at its later site. Acting on the centrifugal pump Pipe forces are thus conducted safely and without negative effects on the rotating pump part in a foundation.
In an sich bekannter Art sind die Verbindungsmittel an den Endstücken angeordnet, wodurch der Zusammenhalt der Hauptteile der Kreiselpumpe gewährleistet ist.In a manner known per se, the connecting means are arranged on the end pieces, whereby the cohesion of the main parts of the centrifugal pump is ensured.
Da das saugseitige Lager der Pumpenwelle immer innerhalb des Pumpengehäuses angeordnet ist, wird gegenüber einer Lageranordnung, bei der die Pumpenlager außerhalb des druckführenden Gehäuses angeordnet sind, eine zusätzliche Wellenab- dichtung eingespart und es ergibt sich eine Verbesserung der Betriebssicherheit. Der verkürzte Lagerabstand verbessert insgesamt das Schwingungsverhalten des rotierenden Bauteiles.Since the suction-side bearing of the pump shaft is always arranged within the pump housing, compared to a bearing arrangement in which the pump bearings are arranged outside the pressurized housing, an additional shaft seal is saved and there is an improvement in operational safety. The shortened bearing clearance improves overall the vibration behavior of the rotating component.
Nach einer anderen Ausgestaltung ist ein druckseitiges Lager in dem Auslass- Endstück angeordnet. Auch diese Maßnahme verbessert den Kraftfluss zwischen einer an die Kreiselpumpe anzuschließenden Rohrleitung und einem Fundament am Aufstellungsort. Ein dadurch möglicher geradliniger Kraftfluss übt keine negative Wirkung mehr auf das Schwingungsverhalten des rotierenden Teiles aus.According to another embodiment, a pressure-side bearing is arranged in the outlet end piece. This measure also improves the power flow between a pipe to be connected to the centrifugal pump and a foundation at the installation site. A possible rectilinear force flow exerts no negative effect on the vibration behavior of the rotating part.
Die Anordnung einer Wellenabdichtung im Bereich zwischen einem Wellenende und dem nächstgelegenen Pumpenlager hat sich ebenfalls als vorteilhaft erwiesen, da aus der steiferen Wellenlagerung geringere Dichtungsbelastungen resultieren.The arrangement of a shaft seal in the region between a shaft end and the nearest pump bearing has also proved to be advantageous, as resulting from the stiffer shaft bearing lower sealing loads.
Die Einlass- und/oder Auslass-Endstücke sind als separate Bauteile ausgebildet und liegen kräfteübertragend an Pumpenstufenteilen an. Ebenso können die Einlassund/oder Auslass-Endstücke integrale Bestandteile von Pumpenstufenteilen sein.The inlet and / or outlet end pieces are designed as separate components and are force-transmitting to pump stage parts. Likewise, the inlet and / or outlet end pieces may be integral parts of pump stage parts.
Bei einer großen Anzahl von Pumpenstufen, beispielsweise bei Verwendung von mehr als zehn Pumpenstufen, hat es sich als vorteilhaft erwiesen, wenn ein zwischen einander zugekehrten Lagerstirnseiten zu messender minimaler Lagerabstand LLmin sich ermittelt aus einer um einen Wert 2 bis 5 reduzierten Anzahl von Pumpenstufen multipliziert mit einer minimalen Stufenbauhohe.With a large number of pump stages, for example when using more than ten pump stages, it has proved to be advantageous if a minimum bearing distance LLmin to be measured between mutually facing bearing faces is determined by a number of pump stages reduced by a value of 2 to 5 multiplied by a minimum tier height.
Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im folgenden näher beschrieben. Es zeigen die Fig. 1 einen Schnitt durch eine Kreiselpumpe und dieEmbodiments of the invention are illustrated in the drawings and will be described in more detail below. It show the Fig. 1 shows a section through a centrifugal pump and the
Fig. 2 eine saugseitige Lageranordnung.Fig. 2 is a suction side bearing assembly.
Im Ausführungsbeispiel der Fig. 1 ist eine fünfstufige Kreiselpumpe dargestellt, deren Laufräder 1 in den Gehäusen 2 jeder Stufe rotieren und die gemeinsam auf einer Pumpenwelle 3 befestigt sind. Die Pumpenstufen sind zwischen einem Einlass- Endstück 4 und einem Auslass-Endstück 6 angeordnet und verfügen über Pumpen- stufenteile 2.1 - 2.5, die drucktragend ausgebildet sind und weitere strömungsführende Einbauten aufnehmen. In dem Beispiel sind die Pumpenstufenteile 2.1 - 2.4 als Gleichteile konstruiert. Das Einlass-Endstück 4 ist in der unteren Hälfte des Ausführungsbeispieles zweiteilig ausgebildet, wobei dessen separates, ringförmiges Bauteil 4 am Pumpenstufenteil 2.6 der ersten Stufe kräfteübertragend anliegt. Dieses Pumpenstufenteil 2.6 beinhaltet gleichzeitig die Saugöffnung 5 der Kreiselpumpe und übt die Funktion eines Gehäusedeckels aus. In der oberen Hälfte des Ausführungsbeispiels ist das Pumpenstufenteil 2.6 der ersten Stufe integraler Bestandteil des Einlass-Endstückes 4 und bildet damit ein Bauteil.In the embodiment of FIG. 1, a five-stage centrifugal pump is shown, the wheels 1 rotate in the housings 2 each stage and which are mounted together on a pump shaft 3. The pump stages are arranged between an inlet end piece 4 and an outlet end piece 6 and have pump stage parts 2.1 - 2.5, which are designed to be pressure-bearing and accommodate further flow-leading internals. In the example, the pump stage parts 2.1 - 2.4 are designed as equal parts. The inlet end piece 4 is formed in two parts in the lower half of the embodiment, wherein the separate, annular component 4 rests on the pump stage part 2.6 of the first stage to transmit power. This pump stage part 2.6 simultaneously contains the suction opening 5 of the centrifugal pump and performs the function of a housing cover. In the upper half of the embodiment, the pump stage part 2.6 of the first stage is an integral part of the inlet end piece 4 and thus forms a component.
Analog verhält es sich mit dem Auslass-Endstück 6. Es ist in der oberen Zeichnungshälfte mehrteilig aufgebaut und darin integrierter Bestandteil ist die Pumpenstufe 2.5 von der letzten, hier fünften Pumpenstufe. Das Pumpenstufenteil 2.5 ist länger ausgeführt als die vorangestellten Pumpenstufenteile 2.1 - 2.4 der anderen Pumpenstufen. Es enthält einen größeren Sammelraum, aus dem heraus ein Druckstutzen 7 ausmündet, mit dessen Hilfe ein gefördertes Fluid in ein anzuschließendes Rohrleitungssystem geleitet wird.It is analogous to the outlet end piece 6. It is constructed in several parts in the upper half of the drawing and integrated part is the pump stage 2.5 of the last, here fifth pump stage. The pump stage part 2.5 is made longer than the preceding pump stage parts 2.1 - 2.4 of the other pump stages. It contains a larger collecting space, from which a discharge nozzle 7 discharges, by means of which a conveyed fluid is passed into a pipeline system to be connected.
Das Auslass-Endstück 6 ist in der unteren Zeichnungshälfte als separates, ringförmiges Bauteil ausgeführt und in der oberen Zeichnungshälfte als integraler Bestandteil des Gehäuses 2.5 dargestellt. Es bildet gleichzeitig das Widerlager für äußere Verbindungsmittel 8, mit denen alle Pumpenteile zusammengehalten werden. Als Verbindungsmittel 8 sind hier Zuganker gezeigt, die durch entsprechende Öffnungen der Endstücke 4, 6 hindurchgeführt sind und mit Hilfe von Schraubelementen den Zusammenhalt der Kreiselpumpe gewährleisten. An den Endstücken 4 und 6 sind Auflagemittel 9, 10 angeordnet, die eine Befestigung der Kreiselpumpe an ihrem künftigen Aufstellort ermöglichen. Der Abstand LA zwischen den Auflagemitteln 9, 10 ist größer als der Abstand LL zwischen den Lagern 11 , 12 der Pumpenwelle 3. Ein mit einem Antrieb zu verbindendes WellenendeThe outlet end piece 6 is executed in the lower half of the drawing as a separate, annular component and shown in the upper half of the drawing as an integral part of the housing 2.5. It also forms the abutment for external connection means 8, with which all pump parts are held together. As connecting means 8 tie rods are here shown, which are passed through corresponding openings of the end pieces 4, 6 and ensure the cohesion of the centrifugal pump by means of screw elements. At the end pieces 4 and 6 support means 9, 10 are arranged, which allow attachment of the centrifugal pump at its future installation. The distance LA between the support means 9, 10 is greater than the distance LL between the bearings 11, 12 of the pump shaft 3. A to be connected to a drive shaft end
5 13 befindet sich in der Nähe des druckseitigen Lagers 11 , welches im Gehäuse 2.5 der hier letzten oder 5. Pumpenstufe angeordnet ist. Diese 5. Pumpenstufe verfügt über einen Bund 14, welcher, ausgehend von dem antriebsseitigem Ende des Pum- penstufenteiles 2.5, auf kleinerem Durchmesser in das Pumpenstufenteil 2.5 hineinragt und somit die Aufnahme für das Lager 11 bildet. Zusätzlich ist in diesem Bund o 14 genügend Freiraum, um darin eine Axialschubausgleichseinrichtung 15 anzuordnen.5 13 is located in the vicinity of the pressure-side bearing 11, which is arranged in the housing 2.5 of the last or fifth pump stage here. This fifth pump stage has a collar 14 which, starting from the drive-side end of the pump stage part 2.5, projects on a smaller diameter into the pump stage part 2.5 and thus forms the receptacle for the bearing 11. In addition, there is enough free space in this collar o 14 to arrange an axial thrust balancing device 15 therein.
Das Lager 11 liegt ungefähr in der Mitte des Druckstutzens 7, wodurch ein guter Kräfteverlauf hinsichtlich aufzunehmender Rohrleitungskräfte bzw. abzuleitender 5 Schwingungskräfte möglich ist.The bearing 11 is approximately in the middle of the pressure port 7, whereby a good flow of forces with respect to male pipe forces or derived 5 vibration forces is possible.
Das andere, saugseitige Lager 12 der Pumpenwelle 3 ist in diesem Ausführungsbeispiel zwischen der ersten und zweiten Pumpenstufe angeordnet und ist hier innerhalb des Gehäuses 2.1 der ersten Stufe abgestützt. oThe other, suction side bearing 12 of the pump shaft 3 is arranged in this embodiment between the first and second pump stage and is supported here within the housing 2.1 of the first stage. O
Zwischen dem Lager 11 und dem Wellenende 13 ist eine Wellenabdichtung 16 angeordnet. Die Lager 11 und 12 sind als mediumgeschmierte Lager ausgebildet und werden von der geförderten Flüssigkeit geschmiert. Die Lager können als Gleitlager und/oder als Wälzlager ausgebildet sein. Deren Auswahl ist abhängig von dem zu 5 fördernden Fluid und der auftretenden Lagerbelastung. Mit Hilfe der mediumge- schmierten Lager entfallen die Serviceintervalle für ansonsten verwendete Lagerschmierungen.Between the bearing 11 and the shaft end 13, a shaft seal 16 is arranged. The bearings 11 and 12 are formed as medium-lubricated bearings and are lubricated by the pumped liquid. The bearings can be designed as plain bearings and / or as rolling bearings. Their selection depends on the fluid to be delivered and the bearing load that occurs. The medium-lubricated bearings eliminate service intervals for otherwise used bearing lubrication.
Infolge der Anordnung der Lager 11 , 12 zwischen den kräfteübertragenden Auflage- 0 mittein 9, 10 der Kreiselpumpe werden Rohrleitungskräfte, die im Bereich derAs a result of the arrangement of the bearings 11, 12 between the force-transmitting Auflage- 0 mittein 9, 10 of the centrifugal pump are pipeline forces in the field of
Saugöffnung 5 und des Druckstutzen 7 auf die Kreiselpumpe einwirken, im Hinblick auf das Schwingungsverhalten in optimaler Weise aufgenommen. Durch den sehr kurzen Lagerabstand LL des rotierenden Teils der mehrstufigen Kreiselpumpe ergibt sich eine außerordentlich hohe Schwingungsfestigkeit des rotierenden Systems, wo- durch die Betriebssicherheit einer derartigen Kreiselpumpe in entscheidender Weise verbessert wird.Suction opening 5 and the discharge nozzle 7 act on the centrifugal pump, taken in terms of the vibration behavior in an optimal manner. Due to the very short bearing distance LL of the rotating part of the multi-stage centrifugal pump results in an extremely high vibration resistance of the rotating system, where is significantly improved by the reliability of such a centrifugal pump.
Weiter ergibt der kurze Lagerabstand LL zwischen den Pumpenlagern 11 , 12 eine sehr kurz bauende mehrstufige Kreiselpumpe, bei der die Schwingungen der Pumpenwelle und deren kritische Drehzahl entscheidend positiv beeinflußt wird. Dies hat eine verbesserte Biegelinie der Pumpenwelle zur Folge, wodurch als zusätzlicher Vorteil die Spaltabmessungen zwischen den rotierenden und stillstehenden Pumpenteilen verringert werden können. Dies führt zu einer Wirkungsgradsteigerung, da somit Spaltstromverluste wesentlich reduziert werden, ohne dabei die Betriebssicherheit zu beeinträchtigen. Die kürzere Bauweise hat insgesamt eine Kostenreduktion zur Folge, da sich insgesamt der Materialeinsatz und die Betriebskosten reduzieren.Next results in the short bearing distance LL between the pump bearings 11, 12 a very short-built multi-stage centrifugal pump, in which the vibrations of the pump shaft and its critical speed is decisively positively influenced. This results in an improved bending line of the pump shaft, whereby as an added advantage, the gap dimensions between the rotating and stationary pump parts can be reduced. This leads to an increase in efficiency, since thus gap current losses are significantly reduced without compromising the reliability. Overall, the shorter design results in a cost reduction, since overall material usage and operating costs are reduced.
Die Ausbildung der Endstücke 4, 6 als separate Bauteile hat den zusätzlichen Vorteil, dass diese aus einem anderen Material hergestellt werden können. Wenn aufgrund eines zu fördernden Fluids die flüssigkeitsberührten Bauteile aus hochwertigen Edelstahlen bestehen müssen, dann können in kostenreduzierender Weise die Teile der Endstücke, mit denen die Verbindungsmittel 8 kräfteübertragend verbunden sind, aus einem preiswerteren Material bestehen.The formation of the end pieces 4, 6 as separate components has the additional advantage that they can be made of a different material. If due to a fluid to be conveyed liquid wetted components must consist of high quality stainless steel, then in cost-reducing manner, the parts of the end pieces, with which the connecting means 8 are connected to transmit power, made of a cheaper material.
Die Fig. 2 zeigt die Verwendung eines Einlaufsternes, der innerhalb der Saugöffnung 5 befindlich ist. Er verfügt über einen Lagerzapfen 17, der mit dem saugseitigen Pumpenlager 12 zusammenwirkt. Das Pumpenlager 12 ist hierbei in Form einer Büchse innerhalb einer Bohrung 18 des hier saugseitigen Wellenendes 18 eingebaut. Durch entsprechende weitere, nicht dargestellte Schmierbohrungen, wird eine Flüssigkeitszirkulation durch das Pumpenlager 12 gewährleistet. Fig. 2 shows the use of an inlet star, which is located within the suction opening 5. It has a bearing pin 17 which cooperates with the suction-side pump bearing 12. The pump bearing 12 is in this case installed in the form of a sleeve within a bore 18 of the suction side shaft end 18 here. By appropriate further, not shown lubrication holes, a liquid circulation is ensured by the pump bearing 12.

Claims

Patentansprüche Claims
1. Kreiselpumpe mehrstufiger Bauart, bei der jede Pumpenstufe ein aus einem oder mehreren Teilen bestehendes Gehäuse und ein darin angeordnetes Laufrad aufweist, für einen Anschluss an strömungsführende Systeme die Pumpenstufen zwischen Einlass- und Auslass-Endstücken angeordnet und dazwischen mit Verbindungsmitteln gehalten sind, auf einer in mindestens zwei Pumpenlagern abgestützten Pumpenwelle alle Lauf räder angeordnet sind, ein Pumpen- wellenende mit einer Aufnahme für ein Verbindungsmittel eines Antriebes versehen ist und zur Befestigung der Kreiselpumpe an einem Aufstellort im Bereich der Endstücke äußere Auflagemittel angeordnet sind, dadurch gekennzeichnet, dass ein Lagerabstand (LL) zwischen einander zugewandten Lagerstirnseiten von zwei Pumpenlagern (11 , 12) mit größtem Abstand zueinander, klei- ner oder gleich ist dem Produkt aus einer minimalen Stufenbauhohe (L ) multipliziert mit der um den Wert 1 reduzierten Anzahl der Pumpenstufen (2.1 - 2.5).1.Centrifugal pump of multi-stage design, in which each pump stage has a housing consisting of one or more parts and an impeller arranged therein, for connection to flow-conducting systems, the pump stages are arranged between inlet and outlet end pieces and are held in between with connecting means, on one All impellers are arranged in at least two pump bearings supported pump shafts, one pump shaft end is provided with a receptacle for a connecting means of a drive, and external support means are arranged in the area of the end pieces for fastening the centrifugal pump, characterized in that a bearing distance ( LL) between mutually facing bearing faces of two pump bearings (11, 12) with the greatest distance from each other, smaller or equal is the product of a minimum step height (L) multiplied by the number of pump steps reduced by 1 (2.1 - 2.5) .
2. Kreiselpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass ein auf die Pumpenwelle (3) projizierter, in axialer Richtung gemessener minimaler Mitten- abstand zwischen zwei einander nachgeschalteten Laufradaustrittsbreiten die minimale Stufenbauhohe (LM) ergibt.2. Centrifugal pump according to claim 1, characterized in that a projected onto the pump shaft (3), measured in the axial direction, the minimum center distance between two successive impeller outlet widths results in the minimum step height (LM).
3. Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein druckseitiges Pumpenlager (11 ) in an sich bekannter Weise in der auf die Pum- penwelle (3) gerichteten Projektion des Druckstutzenquerschnittes angeordnet ist.3. Centrifugal pump according to claim 1 or 2, characterized in that a pressure-side pump bearing (11) is arranged in a manner known per se in the projection of the pressure nozzle cross section directed towards the pump shaft (3).
4. Kreiselpumpe nach Anspruch 3, dadurch gekennzeichnet, dass ein druckseitiges Pumpenlager (11) in einer letzten Pumpenstufe (2.5) angeordnet ist.4. Centrifugal pump according to claim 3, characterized in that a pressure-side pump bearing (11) is arranged in a last pump stage (2.5).
5. Kreiselpumpe nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass ein druckseitiges Pumpenlager (11) zwischen oder in Pumpenstufen angeordnet ist, die einer letzten Pumpenstufe (2.5) in Strömungsrichtung vorangestellt sind. 5. Centrifugal pump according to claim 3 or 4, characterized in that a pressure-side pump bearing (11) is arranged between or in pump stages which precede a last pump stage (2.5) in the flow direction.
6. Kreiselpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass ein saugseitiges Pumpeniager (12) in einer ersten Pumpenstufe (2.1 ) angeordnet ist.6. Centrifugal pump according to one of claims 1 to 5, characterized in that a suction-side pump bearing (12) is arranged in a first pump stage (2.1).
7. Kreiselpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass ein saugseitiges Pumpenlager (12) zwischen oder in nachfolgenden Pumpenstufen angeordnet ist, die auf eine erste Pumpenstufe (2.1) nachfolgen.7. Centrifugal pump according to one of claims 1 to 5, characterized in that a suction-side pump bearing (12) is arranged between or in subsequent pump stages, which follow a first pump stage (2.1).
8. Kreiselpumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der Lagerabstand (LL) zwischen den zwei mit größtem Anstand zueinander angeordneten Pumpenlagern (11 , 12) kleiner oder gleich ist als ein in Wellenrichtung zu messender Abstand (LA) zwischen den Auflagemitteln (9, 10),8. Centrifugal pump according to one of claims 1 to 7, characterized in that the bearing distance (LL) between the two pump bearings (11, 12) arranged at the greatest distance from one another is smaller or equal than a distance (LA) to be measured in the shaft direction between the Support means (9, 10),
9. Kreiselpumpe nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Auflagemittel (9, 10) im Bereich der Endstücke (4, 6) angeordnet sind.9. Centrifugal pump according to one of claims 1 to 8, characterized in that the support means (9, 10) are arranged in the region of the end pieces (4, 6).
10. Kreiselpumpe einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Verbindungsmittel (8) an den Endstücken (4, 6) angeordnet sind.10. Centrifugal pump according to one of claims 1 to 9, characterized in that the connecting means (8) on the end pieces (4, 6) are arranged.
11. Kreiselpumpe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass das druckseitige Pumpenlager (11) in dem Auslass-Endstück (6) angeordnet ist.11. Centrifugal pump according to one of claims 1 to 10, characterized in that the pressure-side pump bearing (11) is arranged in the outlet end piece (6).
12. Kreiselpumpe nach einem der Ansprüche 1 bis 11 , dadurch gekennzeichnet, dass eine Wellenabdichtung (16) im Bereich zwischen einem Wellenende (13) und dem nächstgelegenen Pumpenlager (11 , 12) angeordnet ist.12. Centrifugal pump according to one of claims 1 to 11, characterized in that a shaft seal (16) is arranged in the region between a shaft end (13) and the nearest pump bearing (11, 12).
13. Kreiselpumpe nach einem der Ansprüche 1 bis 11 , dadurch gekennzeichnet, dass die Einlass- und/oder Auslass-Endstücke (4, 6) als separate Bauteile aus- gebildet sind und kräfteübertragend an Pumpenstufenteilen (2.5, 2.6) anliegen.13. Centrifugal pump according to one of claims 1 to 11, characterized in that the inlet and / or outlet end pieces (4, 6) are designed as separate components and bear force-transmitting against pump stage parts (2.5, 2.6).
14. Kreiselpumpe nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Einlass- und/oder Auslass-Endstücke (4, 6) integrale Bestandteile von Pumpenstufenteilen (2.5, 2.6) sind. 14. Centrifugal pump according to one of claims 1 to 13, characterized in that the inlet and / or outlet end pieces (4, 6) are integral components of pump stage parts (2.5, 2.6).
5. Kreiselpumpe nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass ein zwischen einander zugekehrten Lagerstirnseiten zu messender minimaler Lagerabstand (LLmin) ist gleich einer um einen Wert 2 bis 5 reduzierten Anzahl von Pumpenstufen multipliziert mit einer minimalen Stufenbauhohe. 5. Centrifugal pump according to one of claims 1 to 13, characterized in that a minimum bearing distance (L Lm i n ) to be measured between facing end faces of the bearings is equal to a number of pump stages reduced by a value 2 to 5 multiplied by a minimum stage height.
EP04731592A 2003-05-17 2004-05-07 Multistage centrifugal pump Active EP1625304B1 (en)

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DE10322382A DE10322382A1 (en) 2003-05-17 2003-05-17 Multi-stage centrifugal pump
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EP1625304B1 (en) 2006-09-13
US20060127232A1 (en) 2006-06-15
WO2004109117A1 (en) 2004-12-16
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DE10322382A1 (en) 2004-12-02
DE502004001498D1 (en) 2006-10-26

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