EP0535365A1 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
EP0535365A1
EP0535365A1 EP92114535A EP92114535A EP0535365A1 EP 0535365 A1 EP0535365 A1 EP 0535365A1 EP 92114535 A EP92114535 A EP 92114535A EP 92114535 A EP92114535 A EP 92114535A EP 0535365 A1 EP0535365 A1 EP 0535365A1
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EP
European Patent Office
Prior art keywords
housing
centrifugal pump
pump
fan wheel
shaft
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Granted
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EP92114535A
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German (de)
French (fr)
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EP0535365B1 (en
Inventor
Hauke Dipl.-Ing. Kuhrt
Hermann Dipl.-Ing. Müller
Wilfried Dr.-Ing. Lehmann
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Sihi GmbH and Co KG
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Sihi GmbH and Co KG
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Publication of EP0535365A1 publication Critical patent/EP0535365A1/en
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    • 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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5893—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps heat insulation or conduction

Definitions

  • the invention relates to a centrifugal pump, in particular for conveying hot media, with a pump housing, a shaft emerging from the pump housing, a shaft seal, the housing of which is connected to the pump housing, with a fan wheel fastened to the shaft and with a region of the fan wheel and perforated fender covering axially adjoining areas on both sides.
  • the lifespan of the shaft seal depends on the temperature. In addition to design features that inhibit the heat flow from the pump to the seal, it is therefore known to cool the seal housing by means of an air flow that is generated by a fan arranged on the shaft. This is surrounded by a mudguard that is broken through to allow heat and air exchange. For example, it can contain longitudinal slots (FR-A 22 20 723). Because the seal usually, at least after a certain amount of wear, leakage fluid passes through, there is a risk that the leakage fluid reaches the fan wheel and is thrown off by it with a considerable range. This could be countered by using a particularly high-quality seal, which is then also particularly complex. Or you can provide a case drain chamber after the mechanical seal, which is provided with a special drain (DE-A 26 30 513); this is expensive.
  • the invention solves this problem in a simpler manner by providing that the mudguard is designed to be unbroken in the area of the axial extent of the fan wheel. If medium is sprayed outside, it is caught by the unbroken part of the fender.
  • the function of the fan wheel is not affected because the inflow to and from the fan wheel is mainly influenced by the conditions on one or the other axial side of the fan wheel. In any case, this applies if, according to the invention, the ratio of the outer diameter of the fan wheel to the fender diameter is less than 0.8, preferably also less than 0.6.
  • the proportion of the open area of the fender in its perforated areas should be at least 60%. At least, this applies when the fender pumps and connects more or less closely to the housing parts on the drive side.
  • the shaft is expediently surrounded by an elongated cooling housing between the pump housing and the seal housing at a short distance. It has been shown that its known effect can be increased if a throttle is arranged between the interior of the seal housing and the adjoining interior of the cooling housing.
  • thermal insulation is arranged between a wall delimiting the pump interior on the drive side and a wall that closes off the pump housing on the drive side and carries the seal housing (directly or indirectly via the cooling housing).
  • This thermal insulation can be formed by a cavity, which is preferably filled with air or with the medium to be pumped.
  • a relatively large blade angle of the fan wheel has proven to be expedient, namely an angle on the outer diameter of the fan wheel between the blades and the circumferential direction between 20 and 40 degrees.
  • the pump housing 1, which receives the pump impeller 2, is closed on the drive side by a cover 3, which comprises a wall 5 delimiting the pump interior 4 and a wall 6 on the drive side which is spaced therefrom, including an intermediate space 7.
  • the wall parts 5 and 6 form a seat for a bearing bush 8 which receives the pump shaft 9.
  • the wall 6 of the pump housing cover 3 is integrally connected to the elongated cooling housing 10, which the shaft 9 surrounds at a short distance and carries at its end the seal housing 11, which contains suitable sealant 12, for example shaft seals.
  • the bearing bush 8 prevents the free circulation of the medium from the pump interior 4 to the cooling housing 10.
  • a throttle 13 prevents the circulation of the medium enclosed in the cooling housing 10 to the interior of the seal housing 11. Both reduce the heat transfer.
  • the bearing bush 8 which bridges the gap between the walls 5 and 6, consists of poorly heat-conducting material (for example coal or ceramic) and / or has a small cross-section, insofar as it consists of good heat-conducting material, to thereby reduce the heat transfer from the wall 5 to the cooling housing 10.
  • the shaft 9 merges into a coupling sleeve 14 which is mounted in a bearing housing 16 by means of a roller bearing 15 which, together with a flange 17, is supported by means of ribs 18 by a flange 19 which is connected to the pump housing cover 3 is.
  • the fan wheel 20 which is designed as an axial fan, sits on the shaft 9 between the seal housing 11 and the coupling sleeve 14. As shown at 21, its wings are twisted at their outer circumference by an unusually strong angle with respect to the circumferential direction, which is between 20 and 40 degrees.
  • a cylindrical mudguard 24 supported by the ribs 18, which connects to the flanges 17 and 19 without or with only a small distance and preferably extends over the full circumference, but at least over the top and side regions thereof. As shown at 22, the entire surface is perforated with the exception of the region 23, which corresponds to the axial extent of the fan wheel 20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)

Abstract

Centrifugal pump, especially for pumping hot media. In order to cool the sealing casing (11) and a cooling casing section (10) disposed between the sealing casing (11) and the pump casing, there is disposed on the shaft (9) a fan impeller (20) which is surrounded by a perforated guard plate (24). It is provided, according to the invention, that the guard plate (24), in the region (23) of the axial extent of the fan impeller (20), is continuous and that it is perforated only in the regions axially in front of and behind the fan impeller (20). The external diameter of the fan impeller (20) is considerably smaller than that of the guard plate (24). Between the interior of the sealing casing (11) and the adjoining interior of the cooling casing or the pump casing (1), a restrictor (13) is provided.

Description

Die Erfindung betrifft eine Kreiselpumpe, insbesondere zur Förderung heißer Medien, mit einem Pumpengehäuse, einer aus dem Pumpengehäuse austretenden Welle, einer Wellenabdichtung, deren Gehäuse mit dem Pumpengehäuse verbunden ist, mit einem auf der Welle befestigten Lüfterrad und mit einem den Bereich des Lüfterrads und die daran beiderseits axial anschließenden Bereiche abdeckenden, durchbrochenen Schutzblech.The invention relates to a centrifugal pump, in particular for conveying hot media, with a pump housing, a shaft emerging from the pump housing, a shaft seal, the housing of which is connected to the pump housing, with a fan wheel fastened to the shaft and with a region of the fan wheel and perforated fender covering axially adjoining areas on both sides.

Die Lebensdauer der Wellendichtung ist temperaturabhängig. Neben konstruktiven Merkmalen, die den Wärmestrom von der Pumpe zur Dichtung hemmen, ist des deshalb bekannt, das Dichtungsgehäuse mittels eines Luftstroms zu kühlen, der von einem auf der Welle angeordneten Lüfter erzeugt wird. Dieser wird von einem Schutzblech umgeben, das zur Ermöglichung von Wärme- und Luftaustausch durchbrochen ist. Beispielsweise kann es Längsschlitze enthalten (FR-A 22 20 723). Da die Dichtung in der Regel, zumindest nach einem gewissen Verschleiß, Leckflüssigkeit durchläßt, besteht die Gefahr, daß die Leckflüssigkeit zum Lüfterrad gelangt und von diesem mit beträchtlicher Reichweite abgeschleudert wird. Dem könnte man dadurch begegnen, daß man eine besonders hochwertige Dichtung verwendet, die dann aber auch besonders aufwendig ist. Oder man kann im Anschluß an die Gleitringdichtung einen Leckflüssigkeitsaufnahmeraum vorsehen, der mit einem besonderen Abfluß versehen ist (DE-A 26 30 513); dies ist aufwendig.The lifespan of the shaft seal depends on the temperature. In addition to design features that inhibit the heat flow from the pump to the seal, it is therefore known to cool the seal housing by means of an air flow that is generated by a fan arranged on the shaft. This is surrounded by a mudguard that is broken through to allow heat and air exchange. For example, it can contain longitudinal slots (FR-A 22 20 723). Because the seal usually, at least after a certain amount of wear, leakage fluid passes through, there is a risk that the leakage fluid reaches the fan wheel and is thrown off by it with a considerable range. This could be countered by using a particularly high-quality seal, which is then also particularly complex. Or you can provide a case drain chamber after the mechanical seal, which is provided with a special drain (DE-A 26 30 513); this is expensive.

Die Erfindung löst dieses Problem auf einfachere Weise, indem sie vorsieht, daß das Schutzblech im Bereich der axialen Erstreckung des Lüfterrads undurchbrochen ausgeführt ist. Falls Medium nach außen abgespritzt wird, wird es von dem undurchbrochen ausgeführten Teil des Schutzblechs aufgefangen.The invention solves this problem in a simpler manner by providing that the mudguard is designed to be unbroken in the area of the axial extent of the fan wheel. If medium is sprayed outside, it is caught by the unbroken part of the fender.

Die Funktion des Lüfterrades wird dadurch nicht beeinträchtigt, weil der Zustrom zum und Abstrom vom Lüfterrad hauptsächlich von den Verhältnissen auf der einen bzw. anderen axialen Seite des Lüfterrades beeinflußt wird. Jedenfalls gilt dies dann, wenn erfindungsgemäß das Verhältnis des Außendurchmessers des Lüfterrades zu dem Schutzblechdurchmesser kleiner als 0,8, vorzugsweise auch kleiner als 0,6 ist.The function of the fan wheel is not affected because the inflow to and from the fan wheel is mainly influenced by the conditions on one or the other axial side of the fan wheel. In any case, this applies if, according to the invention, the ratio of the outer diameter of the fan wheel to the fender diameter is less than 0.8, preferably also less than 0.6.

Wenn bei einer bekannten Konstruktion (US-PS 4 632 643) der Lüfter eines Motors zur Erzeugung des Kühlluftstroms benutzt wird, so ist dieser von dem geschlossenen Motorgehäuse umgeben, so daß vom Lüfter abspritzende Leckflüssigkeit nicht fortgeschleudert werden kann. Sie wird dann aber im Motorgehäuse festgehalten, was noch schädlicher ist. Das erfindungsgemäß behandelte Problem wurde bei der bekannten Konstruktion offenbar nicht bedacht.If, in a known construction (US Pat. No. 4,632,643), the fan of a motor is used to generate the cooling air flow, then this is surrounded by the closed motor housing, so that leakage liquid spraying off the fan cannot be thrown away. But it is then held in the motor housing, which is even more harmful. The problem treated according to the invention was apparently not considered in the known construction.

Um einen hinreichenden Wärme- und Luftaustausch zu ermöglichen, sollte der Anteil der offenen Fläche des Schutzblechs an dessen durchbrochenen Bereichen mindestens 60 % betragen. Mindestens gilt dies dann, wenn das Schutzblech pumpen- und antriebsseitig an dort befindliche Gehäuseteile mehr oder weniger eng anschließt.In order to enable adequate heat and air exchange, the proportion of the open area of the fender in its perforated areas should be at least 60%. At least, this applies when the fender pumps and connects more or less closely to the housing parts on the drive side.

Um den Wärmetransport vom Pumpengehäuse zu dem Dichtungsgehäuse zu hemmen, ist die Welle zweckmäßigerweise zwischen dem Pumpengehäuse und dem Dichtungsgehäuse in geringem Abstand von einem langgestreckten Kühlgehäuse umgeben. Es hat sich gezeigt, daß dessen an sich bekannte Wirkung gesteigert werden kann, wenn zwischen dem Innenraum des Dichtungsgehäuses und dem sich anschließenden Innenraum des Kühlgehäuses eine Drossel angeordnet ist.In order to inhibit the heat transfer from the pump housing to the seal housing, the shaft is expediently surrounded by an elongated cooling housing between the pump housing and the seal housing at a short distance. It has been shown that its known effect can be increased if a throttle is arranged between the interior of the seal housing and the adjoining interior of the cooling housing.

Erfindungsgemäß kann vorgesehen sein, daß zwischen einer den Pumpeninnenraum antriebsseitig begrenzenden Wand und einer das Pumpengehäuse antriebsseitig abschließenden Wand, die (unmittelbar oder mittelbar über das Kühlgehäuse) das Dichtungsgehäuse trägt, eine Wärmedämmung angeordnet ist. Diese Wärmedämmung kann von einem Hohlraum gebildet sein, der vorzugsweise von Luft oder auch von zu pumpendem Medium gefüllt ist.According to the invention it can be provided that thermal insulation is arranged between a wall delimiting the pump interior on the drive side and a wall that closes off the pump housing on the drive side and carries the seal housing (directly or indirectly via the cooling housing). This thermal insulation can be formed by a cavity, which is preferably filled with air or with the medium to be pumped.

Ferner hat sich ein verhältnismäßig großer Flügelwinkel des Lüfterrads als zweckmäßig erwiesen, nämlich ein Winkel am Außendurchmesser des Lüfterrads zwischen den Flügeln und der Umfangsrichtung zwischen 20 und 40 Grad.Furthermore, a relatively large blade angle of the fan wheel has proven to be expedient, namely an angle on the outer diameter of the fan wheel between the blades and the circumferential direction between 20 and 40 degrees.

Die Erfindung wird im folgenden näher unter Bezugnahme auf die Zeichnung erläutert, die ein vorteilhaftes Ausführungsbeispiel in einem Längsschnitt veranschaulicht.The invention is explained in more detail below with reference to the drawing, which illustrates an advantageous embodiment in a longitudinal section.

Das Pumpengehäuse 1, das das Pumpenlaufrad 2 aufnimmt, wird antriebsseitig von einem Deckel 3 geschlossen, der eine den Pumpeninnenraum 4 begrenzende Wand 5 und eine davon Abstand aufweisende, antriebsseitige Wand 6 unter Einschluß eines Zwischenraums 7 umfaßt. Die Wandteile 5 und 6 bilden einen Sitz für eine Lagerbuchse 8, die die Pumpenwelle 9 aufnimmt. An die Wand 6 des Pumpengehäusedeckels 3 schließt sich einstückig das langgestreckte Kühlgehäuse 10 an, das die Welle 9 mit geringem Abstand umgibt und an seinem Ende das Dichtungsgehäuse 11 trägt, das geeignete Dichtungsmittel 12, beispielsweise Wellendichtringe, enthält. Die Lagerbuchse 8 verhindert die freie Zirkulation des Mediums aus dem Pumpeninnenraum 4 zum Kühlgehäuse 10. Eine Drossel 13 verhindert die Zirkulation des im Kühlgehäuse 10 eingeschlossenen Mediums zum Innenraum des Dichtungsgehäuses 11. Beides vermindert den Wärmetransport. Darüber hinaus kann vorgesehen sein, daß die Lagerbuchse 8, die den Zwischenraum zwischen den Wänden 5 und 6 überbrückt, aus schlecht wärmeleitendem Material (beispielsweise Kohle oder Keramik) besteht und/oder geringen Querschnitt hat, soweit sie aus gut wärmeleitendem Material besteht, um dadurch den Wärmetransport von der Wand 5 zum Kühlgehäuse 10 herabzusetzen.The pump housing 1, which receives the pump impeller 2, is closed on the drive side by a cover 3, which comprises a wall 5 delimiting the pump interior 4 and a wall 6 on the drive side which is spaced therefrom, including an intermediate space 7. The wall parts 5 and 6 form a seat for a bearing bush 8 which receives the pump shaft 9. The wall 6 of the pump housing cover 3 is integrally connected to the elongated cooling housing 10, which the shaft 9 surrounds at a short distance and carries at its end the seal housing 11, which contains suitable sealant 12, for example shaft seals. The bearing bush 8 prevents the free circulation of the medium from the pump interior 4 to the cooling housing 10. A throttle 13 prevents the circulation of the medium enclosed in the cooling housing 10 to the interior of the seal housing 11. Both reduce the heat transfer. In addition, it can be provided that the bearing bush 8, which bridges the gap between the walls 5 and 6, consists of poorly heat-conducting material (for example coal or ceramic) and / or has a small cross-section, insofar as it consists of good heat-conducting material, to thereby reduce the heat transfer from the wall 5 to the cooling housing 10.

Jenseits des Dichtungsgehäuses 11 geht die Welle 9 in eine Kupplungsmuffe 14 über, die mittels eines Wälzlagers 15 in einem Lagergehäuse 16 gelagert ist, das, zusammen mit einem Flansch 17, mittels Rippen 18 von einem Flansch 19 getragen wird, der an dem Pumpengehäusedeckel 3 angeschlossen ist.Beyond the seal housing 11, the shaft 9 merges into a coupling sleeve 14 which is mounted in a bearing housing 16 by means of a roller bearing 15 which, together with a flange 17, is supported by means of ribs 18 by a flange 19 which is connected to the pump housing cover 3 is.

Zwischen Dichtungsgehäuse 11 und Kupplungsmuffe 14 sitzt auf der Welle 9 das Lüfterrad 20, das als Axiallüfter ausgeführt ist. Seine Flügel sind, wie bei 21 gezeigt, an ihrem Außenumfang um einen ungewöhnlich starken Winkel gegenüber der Umfangsrichtung verdreht, der zwischen 20 und 40 Grad liegt.The fan wheel 20, which is designed as an axial fan, sits on the shaft 9 between the seal housing 11 and the coupling sleeve 14. As shown at 21, its wings are twisted at their outer circumference by an unusually strong angle with respect to the circumferential direction, which is between 20 and 40 degrees.

Zwischen den Flanschen 17 und 19 ist ein von den Rippen 18 gestütztes, zylindrisches Schutzblech 24 vorgesehen, das ohne oder mit nur geringem Abstand an die Flanschen 17 und 19 anschließt und sich vorzugsweise über den vollen Umfang erstreckt, zumindest aber über dessen Oberseite und Seitenbereiche. Es ist, wie bei 22 gezeigt, ganzflächig gelocht mit Ausnahme des Bereichs 23, der der axialen Erstreckung des Lüfterrads 20 entspricht.Provided between the flanges 17 and 19 is a cylindrical mudguard 24 supported by the ribs 18, which connects to the flanges 17 and 19 without or with only a small distance and preferably extends over the full circumference, but at least over the top and side regions thereof. As shown at 22, the entire surface is perforated with the exception of the region 23, which corresponds to the axial extent of the fan wheel 20.

Die Zu- und Abströmung ist im Bereich des Luftrads durch das Lagergehäuse 16 und die Kupplungsmuffe 14 auf der einen Seite und das Dichtungsgehäuse 11 auf der anderen Seite gestört. Auch das Vorhandensein des Schutzblechs wirkt sich aus, obwohl zwischen der Wand 6 und dem Flansch 19 zusätzlich zu den Löchern des Schutzblechs 24 Abströmquerschnitte 25 vorhanden sind. Es hat sich gezeigt, daß unter diesen Verhältnissen die besten Ergebnisse erzielt werden, wenn der Außendurchmesser DL des Lüfterrads das 0,8fache, vorzugsweise das 0,6fache, des Durchmessers DS des Schutzblechs nicht übersteigt.The inflow and outflow is disturbed in the area of the air wheel by the bearing housing 16 and the coupling sleeve 14 on one side and the seal housing 11 on the other side. The presence of the mudguard also has an effect, although in addition to the holes in the mudguard 24 there are outflow cross sections 25 between the wall 6 and the flange 19. It has been found that the best results are achieved under these conditions if the outer diameter DL of the fan wheel does not exceed 0.8 times, preferably 0.6 times, the diameter DS of the mudguard.

Claims (8)

Kreiselpumpe, insbesondere zur Förderung heißer Medien, mit einem Pumpengehäuse (1), einer aus dem Pumpengehäuse austretenden Welle (9), einer Wellenabdichtung (12), deren Gehäuse (11) mit dem Pumpengehäuse (1) verbunden ist, mit einem auf der Welle (9) befestigten Lüfterrad (20) und mit einem dem Bereich des Lüfterrads und die daran beiderseits axial anschließenden Bereiche abdeckenden, durchbrochenen Schutzblech (24), dadurch gekennzeichnet, daß das Schutzblech (24) im Bereich (23) der axialen Erstreckung des Lüfterrades (20) undurchbrochen ausgeführt ist.Centrifugal pump, in particular for conveying hot media, with a pump housing (1), a shaft (9) emerging from the pump housing, a shaft seal (12), the housing (11) of which is connected to the pump housing (1), with one on the shaft (9) attached fan wheel (20) and with a perforated protective plate (24) covering the region of the fan wheel and the regions axially adjoining it on both sides, characterized in that the protective plate (24) in the region (23) of the axial extension of the fan wheel ( 20) is continuous. Kreiselpumpe nach Anspruch 1, dadurch gekennzeichnet, daß das Schutzblech (24) einerseits an das Pumpengehäuse (1) oder einen damit verbundenen Flansch (19) und andererseits an ein Motor- oder Lagergehäuse (16) oder einen damit verbundenen Flansch (17) anschließt.Centrifugal pump according to claim 1, characterized in that the protective plate (24) connects on the one hand to the pump housing (1) or a flange (19) connected to it and on the other hand to a motor or bearing housing (16) or a flange (17) connected to it. Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Verhältnis des Außendurchmessers DL des Lüfterrads zu dem Durchmesser DS des Schutzblechs kleiner als 0,8, vorzugsweise kleiner als 0,6 ist.Centrifugal pump according to claim 1 or 2, characterized in that the ratio of the outer diameter DL of the fan wheel to the diameter DS of the fender is less than 0.8, preferably less than 0.6. Kreiselpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Anteil der offenen Fläche des Schutzblechs in dessen durchbrochenen Bereichen mindestens 60% beträgt.Centrifugal pump according to one of claims 1 to 3, characterized in that the proportion of the open area of the fender in its perforated areas is at least 60%. Kreiselpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß zwischen dem Pumpengehäuse (1) und dem Dichtungsgehäuse (11) ein die Welle (9) mit geringem Abstand umgebendes, langgestrecktes Kühlgehäuse (10) angeordnet ist.Centrifugal pump according to one of claims 1 to 4, characterized in that an elongated cooling housing (10) surrounding the shaft (9) at a short distance is arranged between the pump housing (1) and the sealing housing (11). Kreiselpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß zwischen dem Innenraum des Dichtungsgehäuses (11) und dem sich anschließenden Innenraum des Pumpengehäuses bzw. des Kühlgehäuses (10) eine Drossel (13) angeordnet ist.Centrifugal pump according to one of claims 1 to 3, characterized in that a throttle (13) is arranged between the interior of the seal housing (11) and the adjoining interior of the pump housing or the cooling housing (10). Kreiselpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß zwischen einer den Pumpeninnenraum (4) antriebsseitig begrenzenden Wand (5) und einer das Pumpengehäuse antriebsseitig abschließenden Wand (6), die das Dichtungsgehäuse (11) trägt, eine Wärmedämmung (7) angeordnet ist.Centrifugal pump according to one of claims 1 to 6, characterized in that between a wall (5) delimiting the pump interior (4) on the drive side and a wall (6) which closes off the pump housing and carries the seal housing (11), thermal insulation (7) is arranged. Kreiselpumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Flügel (21) des Lüfterrads (20) an ihrem Außendurchmesser einen Winkel zwischen 20 und 40 Grad mit der Umfangsrichtung einschließen.Centrifugal pump according to one of claims 1 to 7, characterized in that the blades (21) of the fan wheel (20) form an angle between 20 and 40 degrees with the circumferential direction on their outer diameter.
EP92114535A 1991-09-09 1992-08-26 Centrifugal pump Expired - Lifetime EP0535365B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9111161U 1991-09-09
DE9111161U DE9111161U1 (en) 1991-09-09 1991-09-09 Centrifugal pump

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EP0535365A1 true EP0535365A1 (en) 1993-04-07
EP0535365B1 EP0535365B1 (en) 1995-10-25

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EP (1) EP0535365B1 (en)
AT (1) ATE129547T1 (en)
DE (2) DE9111161U1 (en)
DK (1) DK0535365T3 (en)
ES (1) ES2079757T3 (en)
GR (1) GR3018394T3 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996027740A1 (en) * 1995-03-06 1996-09-12 Sterling Fluid Systems (Germany) Gmbh Pump for conveying hot media
CN103644137A (en) * 2013-12-04 2014-03-19 江苏大学 Hot water circulating pump suspension body with outer wall provided with cooling water jacket

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10013152A1 (en) * 2000-03-17 2001-09-20 Ksb Ag Seal housing
CN103267020A (en) * 2013-04-24 2013-08-28 欧技工业设备（江苏）有限公司 High-temperature molten salt pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2220723A1 (en) * 1973-03-08 1974-10-04 Borg Warner
DE2630513A1 (en) * 1976-07-07 1978-01-12 Allweiler Ag Heat transfer oil pump - has cooling section with outlying shaft seal in housing cooled by surrounding axially guided air flow from fan
US4632643A (en) * 1985-02-14 1986-12-30 Nielsen Axel L Sump pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2220723A1 (en) * 1973-03-08 1974-10-04 Borg Warner
DE2630513A1 (en) * 1976-07-07 1978-01-12 Allweiler Ag Heat transfer oil pump - has cooling section with outlying shaft seal in housing cooled by surrounding axially guided air flow from fan
US4632643A (en) * 1985-02-14 1986-12-30 Nielsen Axel L Sump pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996027740A1 (en) * 1995-03-06 1996-09-12 Sterling Fluid Systems (Germany) Gmbh Pump for conveying hot media
AU700101B2 (en) * 1995-03-06 1998-12-24 Sterling Fluid Systems (Germany) Gmbh Pump for delivering hot media
US5911565A (en) * 1995-03-06 1999-06-15 Sterling Fluid Systems (Germany) Gmbh Pump for conveying hot media
CN103644137A (en) * 2013-12-04 2014-03-19 江苏大学 Hot water circulating pump suspension body with outer wall provided with cooling water jacket

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EP0535365B1 (en) 1995-10-25
DK0535365T3 (en) 1996-02-12
ES2079757T3 (en) 1996-01-16
ATE129547T1 (en) 1995-11-15
DE59204123D1 (en) 1995-11-30
DE9111161U1 (en) 1993-01-14
GR3018394T3 (en) 1996-03-31

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