EP1546563B1 - Support bearing for a vertical centrifugal pump - Google Patents

Support bearing for a vertical centrifugal pump Download PDF

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Publication number
EP1546563B1
EP1546563B1 EP03807788.9A EP03807788A EP1546563B1 EP 1546563 B1 EP1546563 B1 EP 1546563B1 EP 03807788 A EP03807788 A EP 03807788A EP 1546563 B1 EP1546563 B1 EP 1546563B1
Authority
EP
European Patent Office
Prior art keywords
centrifugal pump
support bearing
bearing
housing
medium
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.)
Expired - Fee Related
Application number
EP03807788.9A
Other languages
German (de)
French (fr)
Other versions
EP1546563A1 (en
Inventor
Wolfgang Scharffenberger
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.)
KSB SE and Co KGaA
Original Assignee
KSB SE and Co KGaA
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
Priority to DE10245957 priority Critical
Priority to DE10245957A priority patent/DE10245957A1/en
Application filed by KSB SE and Co KGaA filed Critical KSB SE and Co KGaA
Priority to PCT/EP2003/008919 priority patent/WO2004033918A1/en
Publication of EP1546563A1 publication Critical patent/EP1546563A1/en
Application granted granted Critical
Publication of EP1546563B1 publication Critical patent/EP1546563B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/04Shafts or bearings, or assemblies thereof
    • F04D29/041Axial thrust balancing
    • F04D29/0413Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/06Lubrication
    • F04D29/061Lubrication especially adapted for liquid pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/08Sealings
    • F04D29/10Shaft sealings
    • F04D29/106Shaft sealings especially adapted for liquid pumps

Description

  • Gegenstand der Erfindung ist eine vertikal angeordnete Kreiselpumpe mit einem oberhalb von ihr vorgesehenen Traglager, das die durch die Kreiselpumpe ausgeübten Axial- und Radialkräfte aufnimmt und das durch ein über das Traglager geleitetes Medium geschmiert und gegebenenfalls gekühlt wird, wobei die Kreiselpumpe über eine Welle angetrieben wird, die durch ein das Traglager umgebendes Gehäuse und in ein zum Förderbereich der Kreiselpumpe gehörendes Gehäuse oder Gehäuseteil geführt ist, und wobei eine Wellenabdichtung vorgesehen ist, die den das Fördermedium enthaltenden Bereich von der Umgebung trennt.The invention relates to a vertically arranged centrifugal pump with a support bearing provided above it, which absorbs the axial and radial forces exerted by the centrifugal pump and which is lubricated by an over the support bearing medium and optionally cooled, the centrifugal pump is driven by a shaft which is guided by a housing surrounding the support bearing and in a housing or housing part belonging to the conveying region of the centrifugal pump, and wherein a shaft seal is provided which separates the area containing the conveying medium from the environment.
  • Pumpen der hier angesprochenen Art besitzen eine oder mehrere Stufen, die meist in einem Topf angeordnet sind. Die Pumpen werden beispielsweise als Kondensatpumpen eingesetzt. Das Traglager einer solchen Pumpe ist vor allem einer axialen Belastung ausgesetzt, hat aber auch radiale Kräfte aufzunehmen. Bisher war es üblich, das Traglager oberhalb des strömungsführenden Gehäuses der Kreiselpumpe in einem von diesem getrennten Gehäuse anzuordnen. Das Traglager wurde entweder durch ein im Gehäuse gespeichertes Fett oder Öl geschmiert oder es wurde von einem gesondert bereitgestellten Medium, beispielsweise Öl, geschmiert und unter Umständen auch gekühlt. So wurde dieses unter Druck zu setzende Medium über jeweils eine Rohrleitung dem Traglager zu- und von diesem abgeführt. Da die Antriebswelle der Kreiselpumpe über das Gehäuse des Traglagers und in das zum Förderbereich der Kreiselpumpe gehörende Gehäuse geführt wurde, waren hier drei verschiedene Wellenabdichtungen notwendig.Pumps of the type discussed here have one or more stages, which are usually arranged in a pot. The pumps are used, for example, as condensate pumps. The support bearing of such a pump is mainly exposed to an axial load, but also has to absorb radial forces. So far, it has been customary to arrange the support bearing above the flow-guiding housing of the centrifugal pump in a separate housing from this. The support bearing was either lubricated by a stored in the housing grease or oil or it was lubricated by a separately provided medium, such as oil, and possibly also cooled. Thus, this under pressure medium to be added via one pipe to the support bearing and discharged from this. Since the drive shaft of the centrifugal pump was passed over the housing of the support bearing and in the belonging to the delivery area of the centrifugal pump housing, here three different shaft seals were necessary.
  • Die US-A-5 413 459 offenbart eine in explosionsgefährdete Umgebung betriebene vertikale Pumpenanordnung mit einem Magnetkupplungsantrieb. Eine Wellenabdichtung ist bei dieser Pumpe nicht vorhanden. Vom Pumpendruckstutzen wird über eine externe Rohrleitung und eine darin integrierte aufwendige Schmier- und Kühlmitteleinrichtung ein Teil der Förderflüssigkeit entnommen und als ein Schmier- und Kühlmittelstrom von außen in die Magnetkupplung eingespeist. Ein daraus abfließender Schmiermittelstrom dient zur Kühlung eines axialen Traglagers.The US-A-5 413 459 discloses a vertical pump assembly operated in an explosive environment with a magnetic drive. A shaft seal is not available for this pump. From the pump discharge nozzle, a part of the delivery liquid is removed via an external pipeline and a complex lubricant and coolant device integrated therein and fed as a lubricant and coolant flow from the outside into the magnetic coupling. A flowing out of this lubricant flow is used for cooling an axial support bearing.
  • Vor allem der bei der geschilderten Ausführung zu treibende Aufwand für die Bereitstellung sowie Zu- und Abführung eines gesonderten Schmier- und Kühlmittels für das Traglager, aber auch der Aufwand für die verschiedenen Wellenabdichtungen ließen den Wunsch entstehen, eine Ausführung zu schaffen, die diesen Aufwand entscheidend verringert. Die der Erfindung zugrundeliegende Aufgabe basiert auf diesem Wunsch.Above all, in the described embodiment to be driven effort for the provision and supply and discharge of a separate lubricant and coolant for the support bearing, but also the cost of the various shaft seals gave rise to the desire to create a design that makes this effort crucial reduced. The object underlying the invention is based on this desire.
  • Die somit gestellte Aufgabe wird ausgehend von einer Kreiselpumpe der eingangs zitierten Art erfindungsgemäß dadurch gelöst, dass das das Traglager umgebende Gehäuse über den von dem Radiallager gebildeten Spalt mit dem Druckbereich der Kreiselpumpe verbunden ist und das der Schmierung dienende Medium über diesen Spalt dem Traglager zugeführt wird, während der Abführung des Mediums eine das Gehäuse mit dem Einlaufbereich der Kreiselpumpe verbindende Rohrleitung dient, und wobei eine Wellenabdichtung auf der vom Förderbereich der Kreiselpumpe abgewandten Seite des Traglagers angeordnet ist.The object thus posed is achieved on the basis of a centrifugal pump of the type cited in the present invention that the housing surrounding the support bearing is connected via the gap formed by the radial bearing with the pressure range of the centrifugal pump and the medium serving for lubrication is fed through this gap to the support bearing , During the discharge of the medium, a pipe connecting the housing with the inlet region of the centrifugal pump, and wherein a shaft seal is arranged on the side facing away from the conveying region of the centrifugal pump side of the support bearing.
  • Die erfindungsgemäße Lösung erfordert kein Fremdmedium für die Schmierung und Kühlung des Traglagers. Dies bedeutet eine erhebliche Einsparung und die Beseitigung einer möglichen Störquelle. Der unmittelbare Anschluss des Traglagergehäuses an das strömungsführende Gehäuse erlaubt eine Verringerung der Baulänge.The solution according to the invention requires no foreign medium for the lubrication and cooling of the support bearing. This means a considerable saving and the elimination of a possible source of interference. The direct connection of the support bearing housing to the flow-guiding housing allows a reduction in the overall length.
  • Es wird als zweckmäßigste Lösung angesehen, wenn das Axiallager und das Radiallager durch Gleitlager gebildet werden. Dies eröffnet im übrigen die Möglichkeit, das das Traglager umgebende Gehäuse über den von dem Radiallager gebildeten Spalt mit dem Förderbereich der Kreiselpumpe zu verbinden, um das der Schmierung dienende Medium über diesen Spalt dem Traglager zuzuführen. Hieraus ergibt sich der Vorzug, dass anstelle der bisher notwendigen drei Wellenabdichtungen nur noch eine erforderlich ist.It is considered to be the most convenient solution when the thrust bearing and the radial bearing are formed by plain bearings. This, moreover, opens up the possibility of connecting the housing surrounding the supporting bearing via the gap formed by the radial bearing to the conveying region of the centrifugal pump, in order to supply the lubricant used for the medium via this gap to the supporting bearing. This results in the advantage that instead of the previously required three shaft seals only one is required.
  • Anhand eines Ausführungsbeispiels wird die Erfindung näher erläutert. Es zeigt
  • Fig. 1
    einen Teil eines Kondensat- und Speisewasserkreislaufs, der mit einer Kreiselpumpe der gattungsgemäßen Art ausgestattet ist;
    Fig. 2
    eine mit einem Traglager der vorbekannten Bauart ausgestattete Kreiselpumpe;
    Fig. 3
    den oberen Bereich einer erfindungsgemäß gestalteten Kreiselpumpe.
    Reference to an embodiment of the invention will be explained in more detail. It shows
    Fig. 1
    a part of a condensate and feed water circuit, which is equipped with a centrifugal pump of the generic type;
    Fig. 2
    a centrifugal pump equipped with a support bearing of the prior art type;
    Fig. 3
    the upper portion of an inventive designed centrifugal pump.
  • Die in der Fig. 1 dargestellte Anlage ist mit einer Kreiselpumpe 1 ausgestattet, die durch einen Elektromotor 2 angetrieben wird. Die Kreiselpumpe 1 besitzt fünf Stufen. Das von ihr zu fördernde, von einem Kondensator 3 über eine Leitung 4 kommende Medium wird über einen in einem Ein-/Auslaufgehäuse 5 angeordneten Einlauf 6 in einen Topf 7 geführt, von wo es über einen Pumpeneinlaß 8 angesaugt wird. Die Kreiselpumpe 1 fördert das Medium in ein Druckrohr 9 und von dort aus über einen Auslaß 10 und eine Leitung 11 zu einem Speisewasserbehälter 12.The in the Fig. 1 shown system is equipped with a centrifugal pump 1, which is driven by an electric motor 2. The centrifugal pump 1 has five stages. The medium to be delivered by it, coming from a condenser 3 via a line 4 medium is passed through a arranged in an inlet / outlet housing 5 inlet 6 in a pot 7, from where it is sucked in via a pump inlet 8. The centrifugal pump 1 conveys the medium into a pressure pipe 9 and from there via an outlet 10 and a line 11 to a feedwater tank 12th
  • Die Kreiselpumpe 1 ist über eine Antriebswelle 13 mit dem Elektromotor 2 verbunden. Die Antriebswelle 13, die die Laufräder der Kreiselpumpe 1 trägt, wird von einem Traglager 14 aufgenommen.The centrifugal pump 1 is connected via a drive shaft 13 to the electric motor 2. The drive shaft 13, which carries the impellers of the centrifugal pump 1 is received by a support bearing 14.
  • Die in der Fig. 2 dargestellte Ausführung besitzt ein Traglager 15, das als ein vor allem axiale, aber auch radiale Kräfte aufnehmendes Wälzlager ausgelegt ist. Das Traglager 15 ist in einem Gehäuse 16 angeordnet. Über einen Anschluß 17 wird das Traglager 15 mit einem Schmier- und Kühlmedium versorgt. Über einen Anschluß 18 wird das Schmier- und Kühlmedium wieder abgeführt. Um einen Austritt des Mediums in die Umgebung zu verhindern, sind Wellendichtungen 19 und 20 am Gehäuse 16 vorgesehen. Das Ein-/Auslaufgehäuse 5 ist durch eine Wellendichtung 21 abgedichtet.The in the Fig. 2 embodiment shown has a support bearing 15 which is designed as a mainly axial, but also radial forces receiving rolling bearing. The support bearing 15 is arranged in a housing 16. Via a connection 17, the support bearing 15 is supplied with a lubricating and cooling medium. About a terminal 18, the lubricating and cooling medium is discharged again. To prevent leakage of the medium into the environment, shaft seals 19 and 20 are provided on the housing 16. The inlet / outlet housing 5 is sealed by a shaft seal 21.
  • Die Fig. 3 zeigt eine erfindungsgemäße Ausführung. Hier wird das Traglager aus zwei Gleitlagern gebildet: einem Axiallager 22 und einem Radiallager 23. Das Traglager ist von einem Gehäuse 24 umgeben, das unmittelbar auf das Ein-/Auslaufgehäuse 25 aufgesetzt ist. Über den Spalt, der zwischen der Lagerschale 26 und der Buchse 27 des Radiallagers 23 gebildet wird, gelangt Fördermedium aus dem Auslaufbereich 28 in das Innere des Gehäuses 24. Somit schmiert das Fördermedium sowohl das Radiallager 23 als auch das Axiallager 22. Der Abführung des Mediums aus dem Gehäuse 24 dient eine im Bereich des Einlaufs 29 mündende Rohrleitung 30. Das Gehäuse 24 wird somit ständig von dem Medium durchströmt und somit werden auch das Axiallager 22 und das Radiallager 23 unausgesetzt gekühlt. Ein externes Schmier- und Kühlmedium, eine externe Druckquelle und eine externe Kühlung für das Medium werden also eingespart.The Fig. 3 shows an embodiment of the invention. Here, the support bearing is formed of two plain bearings: a thrust bearing 22 and a radial bearing 23. The support bearing is surrounded by a housing 24 which is placed directly on the inlet / outlet housing 25. Via the gap which is formed between the bearing shell 26 and the bushing 27 of the radial bearing 23, conveying medium passes from the outlet region 28 into the interior of the housing 24. Thus, the conveying medium lubricates both the radial bearing 23 and the axial bearing 22. The discharge of the medium from the housing 24 is used in the region of the inlet 29 opening pipe 30. The housing 24 is thus constantly flowed through by the medium and thus also the thrust bearing 22 and the radial bearing 23 are continuously cooled. An external lubrication and cooling medium, an external pressure source and an external cooling for the medium are thus saved.
  • Die in der Fig. 3 dargestellte erfindungsgemäße Ausführung benötigt im Gegensatz zu der vorbekannten Ausführung der Fig. 2 nur eine Wellenabdichtung 31 am Austritt der Antriebswelle 13 in die Umgebung. Hieraus ergibt sich eine weitere Einsparung. Schließlich bleibt noch erwähnen, daß die erfindungsgemäße Ausführung eine kürzere Erstreckung besitzt als die vorbekannte Gestaltung.The in the Fig. 3 illustrated embodiment of the invention requires in contrast to the prior art embodiment of Fig. 2 only one shaft seal 31 at the outlet of the drive shaft 13 in the environment. This results in a further saving. Finally, it should be mentioned that the embodiment according to the invention has a shorter extension than the previously known design.

Claims (1)

  1. Vertically arranged centrifugal pump with a support bearing which is provided above it and is subdivided into an axial bearing (22) and a radial bearing (23) and which is lubricated and, if appropriate, cooled by the conveying medium of the centrifugal pump, the conveying medium being supplied to the support bearing (22, 23) via a connection running to the delivery region (28) of the centrifugal pump and being discharged from there, furthermore the housing (24) which surrounds the axial bearing (22) and the radial bearing (23) directly adjoining the housing (25) belonging to the conveying region of the centrifugal pump, and that region of the centrifugal pump which contains conveying medium being closed off in a leaktight manner with respect to the surroundings, characterized in that the housing (24) surrounding the support bearing (22, 23) is connected to the delivery region (28) of the centrifugal pump via the gap formed by the radial bearing (23), and the medium serving for lubrication is supplied to the support bearing (22, 23) via this gap, while a pipeline (30) connecting the housing (24) to the inflow region (29) of the centrifugal pump serves for the discharge of the medium, a shaft seal (31) being arranged on the side of the support bearing (22, 23) which faces away from the conveying region of the centrifugal pump.
EP03807788.9A 2002-10-02 2003-08-12 Support bearing for a vertical centrifugal pump Expired - Fee Related EP1546563B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE10245957 2002-10-02
DE10245957A DE10245957A1 (en) 2002-10-02 2002-10-02 Thrust bearing for a vertical rotary pump has a combined thrust and radial bearing cooled and lubricated by the pumped liquid
PCT/EP2003/008919 WO2004033918A1 (en) 2002-10-02 2003-08-12 Support bearing for a vertical centrifugal pump

Publications (2)

Publication Number Publication Date
EP1546563A1 EP1546563A1 (en) 2005-06-29
EP1546563B1 true EP1546563B1 (en) 2013-10-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03807788.9A Expired - Fee Related EP1546563B1 (en) 2002-10-02 2003-08-12 Support bearing for a vertical centrifugal pump

Country Status (4)

Country Link
US (1) US7318707B2 (en)
EP (1) EP1546563B1 (en)
DE (1) DE10245957A1 (en)
WO (1) WO2004033918A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101691871B (en) * 2008-08-29 2011-03-16 浙江水泵总厂有限公司 Improvement on axial thrust balancing device of vertical multistage barrel pump
US8398361B2 (en) 2008-09-10 2013-03-19 Pentair Pump Group, Inc. High-efficiency, multi-stage centrifugal pump and method of assembly
CN103016388B (en) * 2012-12-29 2015-05-13 山东星源矿山设备集团有限公司 Thrust bearing for high-power high-voltage dry motor
EP3199815B1 (en) * 2016-01-26 2020-07-15 Grundfos Holding A/S Centrifugal pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1279471B (en) * 1962-11-12 1968-10-03 Halbergerhuette Gmbh Longitudinal bearing for a circulating centrifugal pump with overhung impeller
US3220352A (en) * 1962-12-03 1965-11-30 Atkinson Guy F Co Pump lubrication system
US3171355A (en) * 1963-03-14 1965-03-02 Dresser Ind Well pump
US3482522A (en) * 1968-01-15 1969-12-09 Baker Mfg Co Pitless booster pump unit
US4234290A (en) * 1978-11-30 1980-11-18 Binks Manufacturing Company Turbine pump
US5413459A (en) * 1991-10-01 1995-05-09 Crane Co. Verticle turbine pump
US5961301A (en) * 1997-07-31 1999-10-05 Ansimag Incorporated Magnetic-drive assembly for a multistage centrifugal pump

Also Published As

Publication number Publication date
EP1546563A1 (en) 2005-06-29
WO2004033918A1 (en) 2004-04-22
US20050232794A1 (en) 2005-10-20
DE10245957A1 (en) 2004-04-15
US7318707B2 (en) 2008-01-15

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