EP0744551A1 - Centrifugal pump for conveying hot media - Google Patents
Centrifugal pump for conveying hot media Download PDFInfo
- Publication number
- EP0744551A1 EP0744551A1 EP96106606A EP96106606A EP0744551A1 EP 0744551 A1 EP0744551 A1 EP 0744551A1 EP 96106606 A EP96106606 A EP 96106606A EP 96106606 A EP96106606 A EP 96106606A EP 0744551 A1 EP0744551 A1 EP 0744551A1
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- EP
- European Patent Office
- Prior art keywords
- sealing
- pump
- mechanical seal
- medium
- compensation device
- 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.)
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Classifications
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/106—Shaft sealings especially adapted for liquid pumps
- F04D29/108—Shaft sealings especially adapted for liquid pumps the sealing fluid being other than the working liquid or being the working liquid treated
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/12—Shaft sealings using sealing-rings
- F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
- F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
Definitions
- the invention relates to a seal arrangement for a centrifugal pump for conveying hot media, consisting of at least one mechanical seal arranged in the area of a shaft bushing, a cooling circuit for cooling the mechanical seal, a partial flow of the conveying medium being usable as a cooling medium of the mechanical seal.
- a multi-stage pump construction which is equipped with external bearing housings.
- the bearing housings are preceded by mechanical seals located inside the pump that are exposed to the medium to be pumped.
- the mechanical seals are preceded by throttling sections, which are used to reduce the pressure.
- Return lines are arranged downstream in the direction of flow, with which the conveyed medium is returned to the suction nozzle.
- a shaft seal for centrifugal pumps is known, which is arranged in the area of the shaft end and at the housing outlet.
- the shaft seal consists of a hydrodynamic mechanical seal arranged on the atmosphere side and a further seal arranged on the pump side, with a seal located between the two seals Sealing chamber a circular flow is used for cooling and the removal of dirt particles.
- the pump-side seal is designed as a hydrodynamic mechanical seal, which is bridged by a bypass arranged in the sealing chamber and connecting it to the inside of the pump, which serves for targeted leakage. With the help of this measure, an external cooling device is to be saved and the life of the seal is to be improved.
- the sealing chamber itself is acted upon by the pressure medium of the centrifugal pump with the pumped medium in order to ensure the pressure necessary for the mechanical seal to function.
- This pressure is discharged into the interior of the pump via the second mechanical seal with the help of a targeted leak.
- the second mechanical seal thus acts as a throttle for reducing pressure.
- their use increases the manufacturing costs of the entire pump unit.
- the invention has for its object to realize a safe and inexpensive cooling of a mechanical seal for centrifugal pumps with an operation up to 160 ° C medium temperature.
- This object is achieved with the features of claim 1.
- a cooling air flow generated by the drive motor can be used in addition to others.
- the medium circulating in the cooling circuit is separated from the rest of the medium by the sealing element, so that mixing between these areas is prevented in normal operation.
- the pressure equalization caused between the sealing space and the pump interior relieves the sealing element located in between in the simplest way.
- the pump interior includes all spaces that are arranged in front of the mechanical seal space.
- the sealing element can be designed as a simple, touching sealing ring. Its material properties are selected so that it is resistant to the prevailing temperatures.
- the pressure equalization with the help of a simple pressure relief bore does not require any special manufacturing measures. A sealing lip of the sealing element is therefore not exposed to any stress, so that special treatment of a pump shaft or a shaft protection sleeve located thereon is unnecessary.
- the promotional effect within the cooling circuit the mechanical seal itself or auxiliary devices connected to it are generated. The cooling circuit removes the heat that is transferred from the pump material to the cooling medium during operation.
- thermosiphon circuit is formed within the cooling circuit, which ensures sufficient cooling of the mechanical seal even when a centrifugal pump is in the ready state in the ready state.
- the sealing ring which is to a certain extent upstream of the mechanical seal, prevents heat exchange with the hot pumping medium in the simplest way in normal operation.
- a hot medium is only fed into the cooling medium if the pressure inside the cooling circuit should drop due to a seal leak. Only in such cases is lost cooling medium replaced by hot, flowing medium.
- a pressure housing 1 with the last impeller 2 located therein is shown.
- This impeller 2 is followed by an axial thrust compensation device 3, from which a return line 4 leads to the suction port of the centrifugal pump, not shown here.
- the axial thrust compensation device can also be dispensed with if the structural design of the pump provides compensation in a different way, e.g. B. by opposing arrangement.
- the axial thrust compensation device is followed by a sealing element 5, which separates the space 6 containing the axial thrust compensation device 3 from an actual seal space 8 containing a mechanical seal 7.
- the seal chamber 8 has a drain line 9 through which heated medium flows outwards, one - not here shown - cooler passes and is introduced as a cooled medium through the line 10 in the region of an opening 11 in the seal chamber 8 of the seal housing 12.
- the contacting sealing element (5) designed here as a sealing ring rests on the rotating part of the pump, in the exemplary embodiment shown on a shaft protection sleeve (14) which is pushed over a pump shaft (22).
- the sealing element or the sealing ring (5) can also bear directly on a pump shaft (22) or another rotating pump part. It effectively prevents an exchange between the hot medium and the lower temperature cooling medium. At most, in situations in which cooling medium has to be replaced by medium through leakage in the area of the mechanical seal, there is an inflow of medium.
- the pumped medium flows from the area of the last impeller (2) through a bearing gap (13) to the - if applicable - axial thrust compensation device (3). From their space (6) the hot medium flows in front of the sealing ring (5) via the gaps (15, 16, 17) into a collecting space (18), from where it is low through a return line (4) to the suction nozzle or a point Pressure of the centrifugal pump is supplied.
- a pressure compensation device (19) is arranged between the collecting space (18) for the conveyed medium and the sealing space (8).
- This is designed as a simple through hole and, as shown, can also penetrate the sealing element (5) in a recess (20).
- a non-contact sealing element for example in the form of a labyrinth seal, would be unsuitable, since its sealing effect is insufficient and excessive heat transfer would take place due to the hot pumping medium flowing through.
- the sealing housing is therefore heated exclusively by heat transfer to the metallic parts.
- the circled sealing element in Fig. 1 is shown in Fig. 2 in an enlarged view.
- the shape of the pressure compensation device selected here has the additional advantage that it simultaneously forms an anti-rotation device for the sealing element.
- the embodiment of a pressure compensation device (19) selected here consists of a tubular component which penetrates the wall surface of the collecting space (18). It extends with part of its length into a recess (20) in the sealing element (5), which is thus held in its position to prevent rotation. With a U-shaped design, the recess (20) allows the sealing element (5) to be simply pushed into the installation position during installation.
- the pressure compensation device (19) can be designed in a simple form as a dowel pin. When arranged at a location other than the one shown, the axial overall length increases slightly, but the system as such is still functional.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft eine Dichtungsanordnung für eine Kreiselpumpe zur Förderung heißer Medien, bestehend aus mindestens einer im Bereich einer Wellendurchführung angeordneten Gleitringdichtung, einem Kühlkreislauf zur Kühlung der Gleitringdichtung, wobei ein Teilstrom des Fördermediums als Kühlmedium der Gleitringdichtung verwendbar ist.The invention relates to a seal arrangement for a centrifugal pump for conveying hot media, consisting of at least one mechanical seal arranged in the area of a shaft bushing, a cooling circuit for cooling the mechanical seal, a partial flow of the conveying medium being usable as a cooling medium of the mechanical seal.
Durch die DE-A- 27 37 294 ist eine Pumpenkonstruktion mehrstufiger Bauart bekannt, die mit außenliegenden Lagergehäusen ausgestattet ist. Den Lagergehäusen vorangestellt sind innerhalb der Pumpe befindliche Gleitringdichtungen, die dem Fördermedium ausgesetzt sind. Den Gleitringdichtungen wiederum sind Drosselstrecken vorangestellt, mit deren Hilfe ein Druckabbau bezweckt wird. In Strömungsrichtung nachgeordnet sind Rückführleitungen, mit denen Fördermedium zum Saugstutzen zurückgeführt wird.From DE-A-27 37 294 a multi-stage pump construction is known, which is equipped with external bearing housings. The bearing housings are preceded by mechanical seals located inside the pump that are exposed to the medium to be pumped. In turn, the mechanical seals are preceded by throttling sections, which are used to reduce the pressure. Return lines are arranged downstream in the direction of flow, with which the conveyed medium is returned to the suction nozzle.
Eine andere Lösung ist durch die DE-A- 26 45 755 bekannt, die eine Kreiselpumpe zur Förderung giftiger Medien zum Gegenstand hat. Darin sind zwei Dichtungen gezeigt, wobei die erste nach Art einer Packung unmittelbar hinter einem Laufrad angeordnet ist und der Packungsdichtung eine Gleitringdichtung nachgeordnet ist. Um den Austritt giftiger Medien zu verhindern, wird in den Gleitringdichtungsraum von außen ein Medium mit höherem Druck eingespeist. Damit wird sichergestellt, daß bei eventuellen Undichtigkeiten das eingespeiste Medium in die Pumpe einströmt und nicht umgekehrt.Another solution is known from DE-A-26 45 755, which has a centrifugal pump to promote toxic media. Two seals are shown therein, the first being arranged in the manner of a packing directly behind an impeller and a mechanical seal being arranged downstream of the packing seal. In order to prevent toxic media from escaping, a medium with higher pressure is fed into the mechanical seal area from the outside. This ensures that in the event of any leaks, the medium fed into the pump flows into the pump and not vice versa.
Durch die DE-A- 38 04 183 ist eine Wellendichtung für Kreiselpumpen bekannt, die im Bereich des Wellenendes und am Gehäuseausgang angeordnet ist. Die Wellendichtung besteht aus einer atmosphärenseitig angeordneten hydrodynamischen Gleitringdichtung und einer weiteren pumpenseitig angeordneten Dichtung, wobei in eine zwischen den beiden Dichtungen befindliche Dichtungskammer ein der Kühlung und der Abführung von Schmutzteilchen dienender Zirkularstrom eingeleitet wird. Die pumpenseitige Dichtung ist als hydrodynamische Gleitringdichtung ausgebildet, die durch einen in der Dichtungskammer angeordneten, diese mit dem Pumpeninnern verbindenden, der gezielten Leckage dienenden Bypass überbrückt ist. Mit Hilfe dieser Maßnahme soll eine externe Kühleinrichtung eingespart werden und eine Lebensdauerverbesserung der Dichtung erreicht werden. Der Dichtungsraum selbst wird vom Druckstutzen der Kreiselpumpe mit Fördermedium beaufschlagt, um damit einen für die Funktion der Gleitringdichtung notwendigen Druck sicherzustellen. Dieser Druck wird über die zweite Gleitringdichtung mit Hilfe einer gezielten Leckage in das Pumpeninnere abgeleitet. Die zweite Gleitringdichtung wirkt damit gewissermaßen als Drossel zum Druckabbau. Durch deren Einsatz erhöht sich jedoch die Fertigungskosten des gesamten Pumpenaggregates.From DE-A-38 04 183 a shaft seal for centrifugal pumps is known, which is arranged in the area of the shaft end and at the housing outlet. The shaft seal consists of a hydrodynamic mechanical seal arranged on the atmosphere side and a further seal arranged on the pump side, with a seal located between the two seals Sealing chamber a circular flow is used for cooling and the removal of dirt particles. The pump-side seal is designed as a hydrodynamic mechanical seal, which is bridged by a bypass arranged in the sealing chamber and connecting it to the inside of the pump, which serves for targeted leakage. With the help of this measure, an external cooling device is to be saved and the life of the seal is to be improved. The sealing chamber itself is acted upon by the pressure medium of the centrifugal pump with the pumped medium in order to ensure the pressure necessary for the mechanical seal to function. This pressure is discharged into the interior of the pump via the second mechanical seal with the help of a targeted leak. The second mechanical seal thus acts as a throttle for reducing pressure. However, their use increases the manufacturing costs of the entire pump unit.
Der Erfindung liegt die Aufgabe zugrunde, für Kreiselpumpen mit einem Betrieb bis 160 °C Mediumtemperatur eine sichere und wenig aufwendige Kühlung einer Gleitringdichtung zu verwirklichen. Die Lösung dieser Aufgabe erfolgt mit den Merkmalen des Anspruches 1. Zur Kühlung des im Bereich der Gleitringdichtung zirkulierenden Kühlmediums kann neben anderen auch ein vom Antriebsmotor erzeugter Kühlluftstrom benutzt werden. Das im Kühlkreislauf zirkulierende Fördermedium wird durch das Dichtungselement vom übrigen Fördermedium getrennt, so daß im Normalbetrieb eine Vermischung zwischen diesen Bereichen unterbunden wird. Der bewirkte Druckausgleich zwischen dem Dichtungsraum und dem Pumpeninnenraum entlastet in einfachster Weise das dazwischen befindliche Dichtungselement. Der Pumpeninnenraum umfaßt alle Räume, die vor dem Gleitringdichtungsraum angeordnet sind.The invention has for its object to realize a safe and inexpensive cooling of a mechanical seal for centrifugal pumps with an operation up to 160 ° C medium temperature. This object is achieved with the features of
Das Dichtungselement kann nach einer weiteren vorteilhaften Ausgestaltung der Erfindung als einfacher, berührend wirkender Dichtungsring ausgebildet sein. Dessen Materialeigenschaften sind so gewählt, daß er gegenüber den vorherrschenden Temperaturen beständig ist. Der Druckausgleich mit Hilfe einer einfachen Druckentlastungsbohrung erfordert keine besonderen fertigungstechnischen Maßnahmen. Eine Dichtlippe des Dichtungselementes ist damit keiner Belastung ausgesetzt, so daß eine besondere Behandlung einer Pumpenwelle bzw. einer darauf befindlichen Wellenschutzhülse entbehrlich ist. Die Förderwirkung innerhalb des Kühlkreislaufes wird durch die Gleitringdichtung selbst oder damit verbundene Hilfseinrichtungen erzeugt. Der Kühlkreislauf transportiert diejenige Wärme ab, die während des Betriebes vom Werkstoff der Pumpe auf das Kühlmedium übertragen wird. Im übrigen bildet sich innerhalb des Kühlkreislaufes ein Thermosyphonkreislauf aus, der auch bei einer im warmen Zustand in Bereitschaftsstellung befindlichen Kreiselpumpe für eine ausreichende Kühlung der Gleitringdichtung sorgt. Der Dichtungsring, welcher gewissermaßen der Gleitringdichtung vorgeschaltet ist, unterbindet im Normalbetrieb in einfachster Weise einen Wärmeaustausch mit dem heißen Fördermedium. Eine Zufuhr von heißen Fördermedium in das Kühlmedium findet nur dann statt, wenn durch eine Dichtungsleckage der Druck innerhalb des Kühlkreislaufes absinken sollte. Nur in solchen Fällen wird verlorenes Kühlmedium durch nachströmendes heißes Fördermedium ersetzt. Ausgestaltungen der Erfindung sind in den Unteransprüchen beschrieben und werden in der Figurenbeschreibung näher erläutert.According to a further advantageous embodiment of the invention, the sealing element can be designed as a simple, touching sealing ring. Its material properties are selected so that it is resistant to the prevailing temperatures. The pressure equalization with the help of a simple pressure relief bore does not require any special manufacturing measures. A sealing lip of the sealing element is therefore not exposed to any stress, so that special treatment of a pump shaft or a shaft protection sleeve located thereon is unnecessary. The promotional effect Within the cooling circuit, the mechanical seal itself or auxiliary devices connected to it are generated. The cooling circuit removes the heat that is transferred from the pump material to the cooling medium during operation. In addition, a thermosiphon circuit is formed within the cooling circuit, which ensures sufficient cooling of the mechanical seal even when a centrifugal pump is in the ready state in the ready state. The sealing ring, which is to a certain extent upstream of the mechanical seal, prevents heat exchange with the hot pumping medium in the simplest way in normal operation. A hot medium is only fed into the cooling medium if the pressure inside the cooling circuit should drop due to a seal leak. Only in such cases is lost cooling medium replaced by hot, flowing medium. Embodiments of the invention are described in the subclaims and are explained in more detail in the description of the figures.
Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird im folgenden näher beschrieben. Es zeigen hierbei die
- Fig. 1
- das druckseitige Ende einer mehrstufigen Kreiselpumpe und die
- Fig. 2
- einen vergrößerten Ausschnitt im Bereich des Dichtungsringes.
- Fig. 1
- the pressure side end of a multi-stage centrifugal pump and the
- Fig. 2
- an enlarged section in the area of the sealing ring.
In der Fig. 1 ist von einer mehrstufigen Kreiselpumpe als Ausschnitt ein Druckgehäuse 1 mit darin befindlichen letzten Laufrad 2 gezeigt. Diesem Laufrad 2 ist eine Axialschubausgleichseinrichtung 3 nachgeordnet, von der aus eine Rückführleitung 4 zum - hier nicht dargestellten - Saugstutzen der Kreiselpumpe führt. Auf die Axialschubausgleichseinrichtung kann auch verzichtet werden, wenn der konstruktive Aufbau der Pumpe auf andere Art für einen Ausgleich sorgt, z. B. durch gegenläufige Anordnung. Hier ist der Axialschubausgleichseinrichtung ein Dichtungselement 5 nachgeordnet, welches den die Axialschubausgleichseinrichtung 3 enthaltenden Raum 6 von einem eigentlichen, eine Gleitringdichtung 7 enthaltenen Dichtungsraum 8 trennt. Der Dichtungsraum 8 verfügt über eine Abflußleitung 9, durch die erwärmtes Medium nach außen strömt, einen - hier nicht dargestellten - Kühler passiert und als abgekühltes Medium durch die Leitung 10 im Bereich einer Öffnung 11 in den Dichtungsraum 8 des Dichtungsgehäuse 12 eingeführt wird.In Fig. 1 of a multi-stage centrifugal pump as a section, a
Das hier als Dichtungsring ausgebildete berührende Dichtungselement (5) liegt am rotierenden Teil der Pumpe an, im gezeigten Ausführungsbeispiel an einer Wellenschutzhülse (14), die über eine Pumpenwelle (22) geschoben ist. Das Dichtungselement bzw. der Dichtungsring (5) kann auch direkt auf einer Pumpenwelle (22) oder einem anderen rotierenden Pumpenteil dichtend anliegen. Er verhindert in wirkungsvoller Weise, daß ein Austausch zwischen dem heißen Fördermedium und dem eine geringere Temperatur aufweisenden Kühlmedium stattfindet. Allenfalls in den Situationen, in denen durch Leckage im Bereich der Gleitringdichtung Kühlmedium durch Fördermedium ersetzt werden muß, erfolgt ein Zustrom von Fördermedium.The contacting sealing element (5) designed here as a sealing ring rests on the rotating part of the pump, in the exemplary embodiment shown on a shaft protection sleeve (14) which is pushed over a pump shaft (22). The sealing element or the sealing ring (5) can also bear directly on a pump shaft (22) or another rotating pump part. It effectively prevents an exchange between the hot medium and the lower temperature cooling medium. At most, in situations in which cooling medium has to be replaced by medium through leakage in the area of the mechanical seal, there is an inflow of medium.
Das Fördermedium strömt aus dem Bereich des letzten Laufrades (2) durch einen Lagerspalt (13) zur - gegebenenfalls angeordneten - Axialschubausgleichseinrichtung (3). Aus deren Raum (6) fließt das heiße Fördermedium vor dem Dichtungsring (5) über die Spalte (15, 16, 17) in einen Sammelraum (18), von wo aus es durch eine Rückführleitung (4) dem Saugstutzen bzw. einer Stelle niedrigen Druckes der Kreiselpumpe zugeführt wird.The pumped medium flows from the area of the last impeller (2) through a bearing gap (13) to the - if applicable - axial thrust compensation device (3). From their space (6) the hot medium flows in front of the sealing ring (5) via the gaps (15, 16, 17) into a collecting space (18), from where it is low through a return line (4) to the suction nozzle or a point Pressure of the centrifugal pump is supplied.
Bei dem hier gewählten Ausführungsbeispiel ist eine Druckausgleichseinrichtung (19) zwischen dem Sammelraum (18) für das Fördermedium und dem Dichtungsraum (8) angeordnet. Diese ist hier als einfache Durchgangsbohrung ausgebildet und kann, wie gezeigt, auch das Dichtungselement (5) in einer Aussparung (20) durchdringen. Somit herrscht am berührend wirkenden Dichtungselement (5) Druckausgleich, wodurch eine Dichtungslippe (21) erheblich geringer belastet ist. Ein berührungslos wirkendes Dichtungselement, beispielsweise in Form einer Labyrinthdichtung, wäre ungeeignet, da dessen Dichwirkung nicht ausreicht und eine zu große Wärmeübertragung durch hindurchströmendes heißes Fördermedium erfolgen würde. Die Aufheizung des Dichtungsgehäuses erfolgt also ausschließlich durch Wärmeübertragung an den metallischen Teilen. Findet für das Dichtungsgehäuse (12) zusätzlich ein Werkstoff mit geringem Wärmeübertragungskoffizienten Verwendung, z. B. ein austenitischer Stahl, ein keramischer Werkstoff oder andere isolierende Werkstoffe, dann kann die Verwendung findende Gleitringdichtung problemlos bei 160 °C Fördermediumtemperatur oder höher eingesetzt werden.In the exemplary embodiment selected here, a pressure compensation device (19) is arranged between the collecting space (18) for the conveyed medium and the sealing space (8). This is designed as a simple through hole and, as shown, can also penetrate the sealing element (5) in a recess (20). Thus there is pressure equalization on the contacting sealing element (5), whereby a sealing lip (21) is loaded considerably less. A non-contact sealing element, for example in the form of a labyrinth seal, would be unsuitable, since its sealing effect is insufficient and excessive heat transfer would take place due to the hot pumping medium flowing through. The sealing housing is therefore heated exclusively by heat transfer to the metallic parts. Finds for the seal housing (12) in addition a material with low heat transfer coefficient use, for. B. an austenitic steel, a ceramic material or other insulating materials, then the mechanical seal used can be used without any problems at a fluid temperature of 160 ° C or higher.
Das in Fig. 1 eingekreiste Dichtungselement ist in Fig. 2 in vergrößerter Darstellung gezeigt. Die hier gewählte Form der Druckausgleichseinrichtung hat den zusätzlichen Vorteil, daß sie gleichzeitig eine Verdrehsicherung für das Dichtungselement bildet. Die hier gewählte Ausführungsform einer Druckausgleichseinrichtung (19) besteht aus einem die Wandfläche des Sammelraumes (18) durchdringenden rohrförmigen Bauteil. Es erstreckt sich mit einem Teil seiner Länge in eine Aussparung (20) des Dichtelementes (5) hinein, welches somit in seiner Position verdrehsichernd gehalten ist. Die Aussparung (20) erlaubt bei U-förmiger Gestaltung während des Einbaues ein einfaches Einschieben des Dichtungselementes (5) in die Einbaulage. Bei einer kreisförmigen Gestaltung der Aussparung (20) müßte zwar erst das Dichtungselement (5) und danach die Druckausgleichseinrichtung (19) montiert werden, aber damit würde sich gleichzeitig eine Lagesicherung für das Dichtungselement ergeben. Die Druckausgleichseinrichtung (19) kann in einer einfachen Form als Spannstift ausgebildet sein. Bei einer Anordnung an einer anderen als der gezeigten Stelle vergrößert sich die axiale Baulänge zwar geringfügig, das System als solches ist aber unverändert funktionsfähig.The circled sealing element in Fig. 1 is shown in Fig. 2 in an enlarged view. The shape of the pressure compensation device selected here has the additional advantage that it simultaneously forms an anti-rotation device for the sealing element. The embodiment of a pressure compensation device (19) selected here consists of a tubular component which penetrates the wall surface of the collecting space (18). It extends with part of its length into a recess (20) in the sealing element (5), which is thus held in its position to prevent rotation. With a U-shaped design, the recess (20) allows the sealing element (5) to be simply pushed into the installation position during installation. With a circular design of the recess (20), the sealing element (5) and then the pressure compensation device (19) would have to be installed, but this would also result in securing the position of the sealing element. The pressure compensation device (19) can be designed in a simple form as a dowel pin. When arranged at a location other than the one shown, the axial overall length increases slightly, but the system as such is still functional.
In denjenigen Betriebssituationen, bei denen aus Verschleißgründen im Dichtungsspalt der Gleitringdichtung (7) ein Verlust an Kühlmedium entsteht, ergibt sich im Kühlkreislauf ein Druckabfall. Nun kann durch die Druckausgleichseinrichtung heißes Fördermedium kurzfristig in den Kühlkreislauf nachströmen, um diesen wieder aufzufüllen. Die Abflußleitung (9) aus dem Dichtungsraum (8) ist unmittelbar neben der Druckausgleichseinrichtung (19) angeordnet. Damit ist sichergestellt, daß zuströmendes heißes Medium nicht auf den Dichtungsspalt der Gleitringdichtung trifft und diesen schädigt. Vielmehr wird es vom zirkulierenden Kühlmediumstrom mitgerissen und fließt erst einem Kühler zu, um danach dem Dichtungsraum (8) zuzuströmen.In those operating situations in which there is a loss of cooling medium in the sealing gap of the mechanical seal (7) for reasons of wear, there is a pressure drop in the cooling circuit. Now hot medium can flow briefly into the cooling circuit through the pressure compensation device in order to refill it. The drain line (9) from the sealing chamber (8) is arranged directly next to the pressure compensation device (19). This ensures that inflowing hot medium does not hit the sealing gap of the mechanical seal and damage it. Rather, it is carried away by the circulating coolant flow and only flows to a cooler in order to then flow to the seal chamber (8).
Claims (6)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19518564A DE19518564A1 (en) | 1995-05-20 | 1995-05-20 | Centrifugal pump for conveying hot media |
| DE19518564 | 1995-05-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0744551A1 true EP0744551A1 (en) | 1996-11-27 |
| EP0744551B1 EP0744551B1 (en) | 2000-07-05 |
Family
ID=7762434
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP96106606A Expired - Lifetime EP0744551B1 (en) | 1995-05-20 | 1996-04-26 | Centrifugal pump for conveying hot media |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5795129A (en) |
| EP (1) | EP0744551B1 (en) |
| AT (1) | ATE194412T1 (en) |
| DE (2) | DE19518564A1 (en) |
| DK (1) | DK0744551T3 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE29704389U1 (en) * | 1997-03-11 | 1997-05-07 | Feodor Burgmann Dichtungswerke GmbH & Co, 82515 Wolfratshausen | Leakage return arrangement in a sealing device |
| EP1087144B1 (en) * | 1999-09-23 | 2005-11-30 | Cryomec AG | Tandem mechanical seal for cryogenic pumps |
| DE502006004968D1 (en) * | 2006-01-12 | 2009-11-12 | Sulzer Pumpen Ag | Turbomachine for a fluid with a radial sealing gap |
| US8398361B2 (en) | 2008-09-10 | 2013-03-19 | Pentair Pump Group, Inc. | High-efficiency, multi-stage centrifugal pump and method of assembly |
| DE102009023907A1 (en) * | 2009-06-04 | 2010-12-09 | Ksb Aktiengesellschaft | Sealing system for centrifugal pumps |
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|---|---|---|---|---|
| US3090320A (en) * | 1960-12-07 | 1963-05-21 | Durametallic Corp | Seals for stuffing boxes and the like permitting flushing thereof |
| FR2188727A5 (en) * | 1972-06-09 | 1974-01-18 | Burgmann Dichtungswerk Feodor | |
| US3999882A (en) * | 1975-03-17 | 1976-12-28 | Dresser Industries, Inc. | Flushing and cooling system for shaft seals and pumps |
| FR2388148A1 (en) * | 1977-04-22 | 1978-11-17 | Dresser Ind | PERFECTED SWEEPING AND COOLING CIRCUIT FOR PUMPS |
| JPS59119099A (en) * | 1982-12-24 | 1984-07-10 | Hitachi Ltd | Shaft sealing apparatus of rotary pump for high- temperature high-pressure fluid |
| DE8601166U1 (en) * | 1986-01-18 | 1986-02-27 | Sihi Gmbh & Co Kg, 2210 Itzehoe | Pump for pumping hot water |
| EP0588259A1 (en) * | 1992-09-14 | 1994-03-23 | KSB Aktiengesellschaft | Recycling of the axial thrust compensation water |
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| US3825270A (en) * | 1972-05-09 | 1974-07-23 | Standun | Wiper seal for apparatus such as metallic can body formers |
| US4053163A (en) * | 1974-12-26 | 1977-10-11 | George Vegella | Seal construction |
| DE2630513C2 (en) * | 1976-07-07 | 1985-11-28 | Allweiler Ag, 7760 Radolfzell | Cooling device for a pump unit |
| US4121839A (en) * | 1976-08-18 | 1978-10-24 | Mitsui Toatsu Chemicals, Inc. | Sealing system for use in composite multi-stage pump |
| DE2645755A1 (en) * | 1976-10-09 | 1978-04-13 | Klein Schanzlin & Becker Ag | SHAFT SEAL |
| DE2925244C2 (en) * | 1979-06-22 | 1982-09-30 | Howaldtswerke-Deutsche Werft Ag Hamburg Und Kiel, 2300 Kiel | Sealing arrangement for stern tube systems |
| DE3324468A1 (en) * | 1983-07-07 | 1985-01-17 | Krull, Gerhard, 4803 Steinhagen | Sealed rolling contact bearing, especially for water pumps in motor vehicles |
| DE3342297A1 (en) * | 1983-11-23 | 1985-06-05 | Howaldtswerke-Deutsche Werft Ag Hamburg Und Kiel, 2300 Kiel | DEVICE FOR SEALING AN OIL LUBRICATED BEARING IN GREATER WATER DEPTH |
| DE3804183C2 (en) * | 1988-02-11 | 1994-11-24 | Klein Schanzlin & Becker Ag | Shaft seal for centrifugal pumps |
| GB8901656D0 (en) * | 1989-01-26 | 1989-03-15 | Flexibox Ltd | Shaft seal |
| US5180297A (en) * | 1991-03-22 | 1993-01-19 | The Gorman-Rupp Company | Fluid transfer pump with shaft seal structure |
| DE9318143U1 (en) * | 1993-11-26 | 1994-01-27 | ABEL GmbH & Co Handels- und Verwaltungsgesellschaft, 21514 Büchen | Sealed shaft exit from a pump housing |
-
1995
- 1995-05-20 DE DE19518564A patent/DE19518564A1/en not_active Withdrawn
-
1996
- 1996-04-26 EP EP96106606A patent/EP0744551B1/en not_active Expired - Lifetime
- 1996-04-26 AT AT96106606T patent/ATE194412T1/en not_active IP Right Cessation
- 1996-04-26 DK DK96106606T patent/DK0744551T3/en active
- 1996-04-26 DE DE59605536T patent/DE59605536D1/en not_active Expired - Lifetime
- 1996-05-20 US US08/650,527 patent/US5795129A/en not_active Expired - Lifetime
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| US3090320A (en) * | 1960-12-07 | 1963-05-21 | Durametallic Corp | Seals for stuffing boxes and the like permitting flushing thereof |
| FR2188727A5 (en) * | 1972-06-09 | 1974-01-18 | Burgmann Dichtungswerk Feodor | |
| US3999882A (en) * | 1975-03-17 | 1976-12-28 | Dresser Industries, Inc. | Flushing and cooling system for shaft seals and pumps |
| FR2388148A1 (en) * | 1977-04-22 | 1978-11-17 | Dresser Ind | PERFECTED SWEEPING AND COOLING CIRCUIT FOR PUMPS |
| JPS59119099A (en) * | 1982-12-24 | 1984-07-10 | Hitachi Ltd | Shaft sealing apparatus of rotary pump for high- temperature high-pressure fluid |
| DE8601166U1 (en) * | 1986-01-18 | 1986-02-27 | Sihi Gmbh & Co Kg, 2210 Itzehoe | Pump for pumping hot water |
| EP0588259A1 (en) * | 1992-09-14 | 1994-03-23 | KSB Aktiengesellschaft | Recycling of the axial thrust compensation water |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP0744551B1 (en) | 2000-07-05 |
| DK0744551T3 (en) | 2000-11-06 |
| ATE194412T1 (en) | 2000-07-15 |
| US5795129A (en) | 1998-08-18 |
| DE59605536D1 (en) | 2000-08-10 |
| DE19518564A1 (en) | 1996-11-21 |
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