EP1343972A1 - Method for operating a motor pump - Google Patents

Method for operating a motor pump

Info

Publication number
EP1343972A1
EP1343972A1 EP01991838A EP01991838A EP1343972A1 EP 1343972 A1 EP1343972 A1 EP 1343972A1 EP 01991838 A EP01991838 A EP 01991838A EP 01991838 A EP01991838 A EP 01991838A EP 1343972 A1 EP1343972 A1 EP 1343972A1
Authority
EP
European Patent Office
Prior art keywords
rotor
pump unit
liquid
unit according
bearing
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
EP01991838A
Other languages
German (de)
French (fr)
Other versions
EP1343972B1 (en
Inventor
Jorgen Christensen
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.)
Grundfos AS
Original Assignee
Grundfos AS
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
Application filed by Grundfos AS filed Critical Grundfos AS
Publication of EP1343972A1 publication Critical patent/EP1343972A1/en
Application granted granted Critical
Publication of EP1343972B1 publication Critical patent/EP1343972B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0633—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0626—Details of the can
    • 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
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/602—Drainage
    • F05D2260/6022—Drainage of leakage having past a seal

Definitions

  • the invention relates to a method for operating a pump assembly according to the features specified in the preamble of claim 1 and a pump assembly according to the features specified in the preamble of claim 3.
  • Centrifugal pump units of small and medium power are usually designed as wet rotors. H. they have a can which seals the rotor space from the stator space, in particular against the ingress of pumped liquid.
  • the delivery liquid located in the rotor space also serves in particular to lubricate the bearings that support the rotor shaft.
  • the pumps of this type have proven their worth since they do not require a seal to the area of the moving parts, and the rotor space can therefore be connected to the pump space by lines.
  • the efficiency of the dry runner is fundamentally superior to that of the wet runner, since the distance between the rotor and Stator can be reduced and the magnetic field between these components is not weakened by the can, but the additional effort for seals and the associated maintenance in long-term operation is so great that, at least for small and medium sizes, almost exclusively wet-running motors are used. In addition, permanent lubrication of the bearing must be ensured.
  • the object of the present invention is to create a method for operating a pump unit, with which the pump can be operated at higher speeds.
  • a generic pump unit should be designed in such a way that it can be driven at high speeds without the above-described s ys t e m b e d i n g t e n N a c h t e i l e d e r b e i d e S S ys t e m e
  • the basic idea of the present invention is to operate a wet-running motor in such a way that it does
  • Wet running motor can be formed, but in operation has the properties of a dry runner, in particular without running the liquid usually located in the rotor space in wet running motors. This allows the design advantages of the wet running motor, which has no complex seals between the pump and
  • the invention therefore provides that the liquid in the rotor space is at least partially removed before, during and / or after the engine is run up to an operating speed.
  • the liquid located between the rotor and the canned tube is preferably evaporated by the action of heat. It is in this area that the removal of the liquid is particularly important, since the highest relative speeds between the rotor and the can also make it the highest
  • the device-like structure for operating a pump unit in the manner described above can be achieved in a structurally particularly simple and therefore cost-effective manner in that the rotor space is sealed in a pressure-limited manner with respect to the delivery liquid.
  • a pressure-limited seal is sufficient to keep the rotor space largely free of liquid during operation.
  • the design certainly provides that the rotor space is filled with liquid before the motor starts.
  • the liquid is either activated by a valve provided for this purpose or by a pressure that is only S ⁇ me seal or other suitable means removed from the rotor space in that the liquid evaporates due to heating and thus the volume is increased.
  • the pump construction can advantageously be provided as in a wet-running motor, so that in particular the liquid-lubricated plain bearings, which are favorable for high speeds, can be used.
  • the invention provides that the bearings supporting the rotor are arranged outside the rotor space.
  • at least one bearing carrying the rotor preferably that which is more distant from the pump impeller, is arranged within the can, since then a liquid supply can take place via the central shaft bore and thus also an extensive axial pressure compensation on the shaft.
  • both shaft ends are led out of the rotor space, an impeller then being provided on one shaft end and the liquid to be removed from the rotor space being drained off near the shaft end facing away from the impeller. If, then, as described above, there is pressure equalization via a shaft bore or another line connection, the liquid can be removed from the
  • Rotor chamber take place almost without pressure and need not be against the Delivery pressure of the pump.
  • a line connection through the shaft that is to say when this end of the shaft is acted upon by the pressure on the suction side of the pump, such removal is particularly easy.
  • Mechanical seals are preferably used as pressure-limited sealing means, the pressure limitation being set by selecting a corresponding spring with which the sliding rings are kept in contact.
  • the mechanical seal is arranged in each case between the rotor and the adjacent bearing, the bearing receptacle for the bearing removed from the impeller being seated within the can.
  • the bearing receptacle is expediently sealed off from the can by means of an outer seal and against the fixed part of the mechanical seal by means of an inner seal.
  • the bearing holder or the mechanical seal is in contact with the end face of the rotor with play, or that a separate displacement component is provided between the bearing holder and the rotor, which allows the free, during operation
  • This displacer component is expediently made of heat-insulating material, preferably plastic, in order to prevent the heat generated in the rotor chamber from being deliberately dissipated at the end for the evaporation of the liquid located there or that condensate is formed in this area. That's why it is expedient to also manufacture the bearing receptacles from a heat-insulating material.
  • the canned tube In order to achieve the fastest and most complete evaporation of the liquid in the rotor space, it can be advantageous to design the canned tube to be heatable at least in a partial area.
  • the heat can be generated by friction in the area between the rotor and the can, so that the liquid heats up automatically when the engine is started up and is thus evaporated.
  • a canned heater can be provided, either by electrical resistance heating or inductively, in particular by the magnetic field formed between the rotor and stator during operation.
  • a permanent magnet motor is particularly advantageously used as the motor.
  • Fig. 1 is a longitudinal section through a centrifugal pump assembly according to the invention.
  • Fig. 2 shows the detail II in Figure 1 in an enlarged view.
  • the pump unit shown in the figures has a housing 1 with a round cross section, on the lower end of which a suction-side inlet 2 and on the upper end of which a pressure-side outlet 3 is formed.
  • the liquid to be pumped is sucked in at the inlet 2, from there it reaches a suction mouth 4 of a centrifugal wheel 5 of the pump, from which it goes radially outward into an annular channel 6 to the outlet 3.
  • the channel 6 is delimited on its outside by the housing 1, on its inside by a motor housing 7 which is fixed within the housing 1.
  • the electrical supply to the unit takes place via an electrical connection 8 passing laterally out of the motor housing 7, through the channel 6 and out of the housing 1.
  • the motor housing 7 accommodates a stator 9 which is delimited on its inside by a can 10.
  • a rotor 1 1 which is seated on a shaft 12 which is mounted near its ends in slide bearings 13, 14 which are seated in bearing seats 15, 16 which are located within the
  • the can 10 radially delimits a rotor space 17, which is spatially and pressure-limited in relation to the rest of the can space by mechanical seals 18, 19.
  • the shaft 12 which is mounted within the slide bearings 13 and 14, carries the impeller 5 at the lower end and, moreover, the rotor 11. It has a central through hole 20, which a
  • both the upper bearing 13 are supplied with delivery fluid via the bore 20 and the lower bearing 14.
  • the delivery pressure of the pump is present at the lower bearing 14, whereas the suction-side pressure is present at the upper bearing 13.
  • the rotor chamber 17 is only sealed via mechanical seals 18 and 19 from the canned chamber which is filled with liquid during operation.
  • the structure of such a mechanical seal is shown in FIG. 2 using the upper mechanical seal 18.
  • the mechanical seal 18 consists of a stationary slide ring 21, which is incorporated within the component forming the bearing receptacle 15, is radially sealed by means of an O-ring 22, and is mounted displaceably in the axial direction of the shaft 12.
  • This stationary slide ring 21 is pressurized by a helical spring 23 surrounding the shaft 12.
  • the coil spring 23 is also arranged within the component forming the bearing seat 15.
  • This annular space formed between the shaft 12 and the component forming the bearing receptacle 15 is connected via a channel 24 to the space delimited by the motor housing 7 in the region of the upper bearing 13, which is in line connection with the bore 20.
  • a rotating slide ring 25 abuts the stationary slide ring 21 on the end face, it sits within a shaft shoulder and rotates with the shaft 12.
  • the mechanical seal 18 thus formed seals the rotor space 17 from the rest of the canned space, a corresponding seal is provided on the other side of the rotor 11.
  • the rotor space 17 can be completely or partially filled with delivery liquid.
  • the liquid in the rotor chamber 17 is heated. Until the liquid evaporates and the pressure inside the rotor space 17 rises rapidly. If the limit pressure formed by the mechanical seal 18 and exceeded by the pressure force of the spring 23 is exceeded, the stationary seal ring lifts off the rotating seal ring 25, ie moves upwards in the illustration according to FIG. 1, whereby the rotor space 17 with the the space surrounding the bearing 13 via the duct 24 is connected. Due to the pressure formed in the rotor 17, the rotor is automatically emptied via the mechanical seal 18 until finally there is no liquid but only steam in the rotor space. Then the motor works like a dry-running motor. The operating speed of such an engine can be, for example, between 40,000 and 100,000 revolutions per minute. The process described above is repeated each time the motor is started, provided that the rotor space 17 is again filled with liquid.
  • a rotating first displacement body 26 is provided on the front side of the rotor 11, which is arranged on the front side of the rotor, as well as a second fixed displacement body 27, which is sealed by an O-ring 28 abuts on the can 10.
  • the displacers 26 and 27 are formed from heat-insulating plastic and have two main functions. On the one hand, they should largely fill the space remaining in the rotor space 17 between the rotor 11 and the component forming the bearing receptacle 15 in order to reduce the free volume of the
  • these bodies 26 and 27 represent insulation bodies which isolate the rotor space 17, which is hot during operation, from the adjacent storage space, in order to avoid the formation of condensate in this area and thus increased friction.
  • the design and arrangement of the mechanical seal 19 arranged on the other side of the rotor 11 corresponds functionally to that described with reference to the structure of the mechanical seal 18. Displacement bodies 26 and 27 are also provided there. Due to the design, the removal of the liquid from the rotor space 17 can in principle be carried out via one or both of the Mechanical seals 18 and 19 are made. However, this is preferably done via the upper mechanical seal 18, since only the suction-side pressure is present there via the bore 12, whereas the pressure-side pressure is present at the other mechanical seal 19, which pressure has to be overcome when the liquid is removed from the rotor space.
  • the liquid in the rotor space is automatically heated and evaporated as soon as corresponding speed ranges are reached.
  • an additional electrical or other type of heating can also be provided, in particular the canned tube can be heated in the area outside the rotor 12, that is to say where the displacement bodies 26 and 27 are arranged. Can also be used instead of a mechanical seal
  • Pressure relief valve can be provided at a suitable location in the rotor space, for example in the can, in order to remove the liquid.
  • the motor shown in the exemplary embodiment is a direct current motor, but alternating current or heavy current motors can also be used.

Abstract

The invention relates to a method for operating a pump unit provided with a centrifugal pump which is driven by an electric motor and which comprises a rotor (11) extending inside a collimator (10). The rotor chamber (17) is separated in a fluid-tight manner with respect to the stator (9). When said motor is actuated, to achieve an operational running speed, liquid which is situated in the rotor chamber (17) is evaporated as a result of the friction heat as the speed rises and is subsequently removed in order to enable the motor to function in a dry running mode.

Description

Verfahren zum Betreiben eines Pumpenaggregats Method for operating a pump set
Die Erfindung betrifft ein Verfahren zum Betreiben eines Pumpenaggregats gemäß den im Oberbegriff des Anspruchs 1 angegebenen Merkmalen sowie ein Pumpenaggregat gemäß den im Ober- begriff des Anspruchs 3 angegebenen Merkmalen.The invention relates to a method for operating a pump assembly according to the features specified in the preamble of claim 1 and a pump assembly according to the features specified in the preamble of claim 3.
Kreiselpumpenaggregate kleiner und mittlerer Leistung wie sie heute zum Stand der Technik zählen, sind üblicherweise als Nassläufer ausgebildet, d. h. sie weisen ein Spaltrohr auf, das den Rotorraum gegenüber dem Statorraum abdichtet, insbesondere gegen Eindringen von Förderflüssigkeit. Die im Rotorraum befindliche Förderflüssigkeit dient insbesondere auch zur Schmierung der die Rotorwelle tragenden Lager. Die Pumpen dieser Bauart haben sich bestens bewährt, da sie keine Dichtung zu dem Bereich der beweglichen Teile benötigt, der Rotorraum also mit dem Pumpenraum leitungsverbunden sein kann.Centrifugal pump units of small and medium power, as they are part of the state of the art today, are usually designed as wet rotors. H. they have a can which seals the rotor space from the stator space, in particular against the ingress of pumped liquid. The delivery liquid located in the rotor space also serves in particular to lubricate the bearings that support the rotor shaft. The pumps of this type have proven their worth since they do not require a seal to the area of the moving parts, and the rotor space can therefore be connected to the pump space by lines.
Andererseits zählt es zum Stand der Technik Trockenläufer einzusetzen, d. h. die das Pumpenlaufrad tragende Welle gegenüber dem Motor abzudichten. Um hier zuverlässig und über lange Zeit den Rotorraum gegenüber der Förderflüssigkeit abzudichten, sind aufwändige Dichtungskonstruktionen erforderlich, die teuer und häufig verschleißanfällig sind.On the other hand, it is part of the prior art to use dry rotors, i. H. to seal the shaft supporting the pump impeller from the motor. In order to reliably seal the rotor space from the liquid to be conveyed over a long period of time, complex sealing constructions are required, which are expensive and often susceptible to wear.
Zwar ist der Trockenläufer vom Wirkungsgrad dem Nassläufer grundsätzlich überlegen, da der Abstand zwischen Rotor und Stator verringert werden kann und das magnetische Feld zwischen diesen Bauteilen nicht durch das Spaltrohr abgeschwächt wird, doch ist der Mehraufwand für Dichtungen und die damit im Langzeitbetrieb auch einhergehende Wartung so groß, dass zumindest bei kleinen und mittleren Baugrößen nahezu ausschließlich Nasslaufmotoren eingesetzt werden. Im Übrigen ist für die Dauerschmierung des Lagers Sorge zu tragen.The efficiency of the dry runner is fundamentally superior to that of the wet runner, since the distance between the rotor and Stator can be reduced and the magnetic field between these components is not weakened by the can, but the additional effort for seals and the associated maintenance in long-term operation is so great that, at least for small and medium sizes, almost exclusively wet-running motors are used. In addition, permanent lubrication of the bearing must be ensured.
Um die hydraulische Leistung solcher Kreiselpumpen und deren Wirkungsgrad zu steigern, ist es bekannt, dem Aggregat einen miniaturisierten Frequenzumrichter zuzuordnen, welcher dem Elektromotor vorgeschaltet ist und eine praktisch beliebig hohe Drehzahl des Motors unabhängig von der Netzfrequenz- und Spannung ermöglicht. Mit zunehmender Drehzahl allerdings macht sich die Flüssigkeitsreibung zwischen Rotor und Spaltrohr negativ bemerkbar, so dass eine Drehzahlerhöhung über bestimmte Grenzen hinaus bei dieser Bauart derzeit nicht sinnvoll ist.In order to increase the hydraulic performance of such centrifugal pumps and their efficiency, it is known to assign a miniaturized frequency converter to the unit, which is connected upstream of the electric motor and enables a practically arbitrary high speed of the motor regardless of the mains frequency and voltage. With increasing speed, however, the fluid friction between the rotor and the canned tube has a negative impact, so that increasing the speed beyond certain limits is currently not sensible with this type of construction.
Vor diesem Stand der Technik liegt der vorliegenden Erfindung die Aufgabe zugrunde, ein Verfahren zum Betreiben eines Pumpenaggregats zu schaffen, mit dem ein Betrieb der Pumpe bei höheren Drehzahlen möglich ist. Darüber hinaus soll ein gattungsgemäßes Pumpenaggregat so ausgebildet werden, dass es mit hohen Drehzahlen antreibbar ist, ohne die Eingangs geschilderten s ys t e m b e d i n g t e n N a c h t e i l e d e r b e i d e n S ys t e m eIn view of this prior art, the object of the present invention is to create a method for operating a pump unit, with which the pump can be operated at higher speeds. In addition, a generic pump unit should be designed in such a way that it can be driven at high speeds without the above-described s ys t e m b e d i n g t e n N a c h t e i l e d e r b e i d e S S ys t e m e
(Nassläufer/Trockenläufer) aufzuweisen.(Wet runner / dry runner).
Der verfahrensmäßige Teil dieser Aufgabe wird durch die in Anspruch 1 angegebenen Merkmale, der vorrichtungsmäßige Teil durch die in Anspruch 3 angegebenen Merkmale gelöst. Vorteil- hafte Ausgestaltungen der Erfindung sind in den Unteransprüchen, der nachfolgenden Beschreibung und der Zeichnung angegeben.The procedural part of this object is achieved by the features specified in claim 1, the device-related part by the features specified in claim 3. Advantage- adhesive embodiments of the invention are specified in the subclaims, the following description and the drawing.
Grundgedanke der vorliegenden Erfindung ist es, einen Nasslauf- motor so zu betreiben, dass dieser von der Bauart her zwar alsThe basic idea of the present invention is to operate a wet-running motor in such a way that it does
Nasslaufmotor ausgebildet sein kann, im Betrieb jedoch die Eigenschaften eines Trockenläufers aufweist, insbesondere ohne die bei Nasslaufmotoren üblicherweise im Rotorraum befindliche Flüssigkeit läuft. Hierdurch können die konstruktiven Vorteile des Nasslauf- motors, der keine aufwändigen Dichtungen zwischen Pumpe undWet running motor can be formed, but in operation has the properties of a dry runner, in particular without running the liquid usually located in the rotor space in wet running motors. This allows the design advantages of the wet running motor, which has no complex seals between the pump and
Motor benötigt, beibehalten werden, ohne auf die insbesondere bei hohen Drehzahlen vorteilhaften Eigenschaften eines Trockenläufers verzichten zu müssen. Die Erfindung sieht also vor, dass vor, während und/oder nach dem Hochfahren des Motors auf eine Betriebsdrehzahl die im Rotorraum befindliche Flüssigkeit zumindest teilweise entfernt wird. Vorzugsweise wird dabei die zwischen Rotor und Spaltrohr befindliche Flüssigkeit durch Wärmeeinwirkung verdampft. Denn gerade in diesem Bereich ist das Entfernen der Flüssigkeit besonders wichtig, da hier aufgrund der hohen Relativ- geschwindigkeiten zwischen Rotor und Spaltrohr auch die höchsteMotor needed to be maintained without having to forego the properties of a dry rotor, which are particularly advantageous at high speeds. The invention therefore provides that the liquid in the rotor space is at least partially removed before, during and / or after the engine is run up to an operating speed. The liquid located between the rotor and the canned tube is preferably evaporated by the action of heat. It is in this area that the removal of the liquid is particularly important, since the highest relative speeds between the rotor and the can also make it the highest
Reibleistung entsteht.Friction power arises.
Für den vorrichtungsmäßigen Aufbau zum Betrieb eines Pumpenaggregats in der vorbeschriebenen Weise sind zahlreiche kon- struktive Varianten möglich. Konstruktiv besonders einfach und damit kostengünstig kann dies dadurch erreicht werden, dass der Rotorraum gegenüber der Förderflüssigkeit druckbegrenzt abgedichtet ist. Eine solche druckbegrenzte Abdichtung reicht aus, um den Rotorraum während des Betriebs weitgehend flüssigkeitsfrei zu halten. Die Konstruktion sieht dabei durchaus vor, dass der Rotorraum vor Beginn des Motoranlaufs flüssigkeitsgefüllt ist. Die Flüssigkeit wird jedoch entweder durch ein gesondert dafür vorgesehenes Ventil, durch eine nur bis zu einem bestimmten Druck wirk- sαme Dichtung oder andere geeignete Mittel aus dem Rotorraum dadurch entfernt, dass aufgrund einer Erwärmung die Flüssigkeit verdampft und damit das Volumen vergrößert wird. Hierdurch steigt der Druck an, bis die Druckbegrenzug des Rotorraums über- schritten wird und die dort befindliche Flüssigkeit, sei es in gasförmiger oder flüssiger Form, entweicht. Gleichzeitig führt der dann dort herrschende Dampfdruck dazu, dass keine weitere Förderflüssigkeit in den Rotorraum eindringt. Im Übrigen kann die Pumpenkonstruktion in vorteilhafter Weise wie bei einem Nasslaufmotor vorgesehen sein, so dass insbesondere die für hohe Drehzahlen günstigen flüssigkeitsgeschmierten Gleitlager eingesetzt werden können.Numerous design variants are possible for the device-like structure for operating a pump unit in the manner described above. This can be achieved in a structurally particularly simple and therefore cost-effective manner in that the rotor space is sealed in a pressure-limited manner with respect to the delivery liquid. Such a pressure-limited seal is sufficient to keep the rotor space largely free of liquid during operation. The design certainly provides that the rotor space is filled with liquid before the motor starts. However, the liquid is either activated by a valve provided for this purpose or by a pressure that is only Sαme seal or other suitable means removed from the rotor space in that the liquid evaporates due to heating and thus the volume is increased. As a result, the pressure rises until the pressure limit of the rotor space is exceeded and the liquid there, whether in gaseous or liquid form, escapes. At the same time, the vapor pressure then prevailing there means that no further delivery liquid penetrates into the rotor space. In addition, the pump construction can advantageously be provided as in a wet-running motor, so that in particular the liquid-lubricated plain bearings, which are favorable for high speeds, can be used.
Um die Versorgung der Lager mit Flüssigkeit auch dann sicher- stellen zu können, wenn der Rotorraum bei Betriebsdrehzahl desIn order to be able to ensure that the bearings are supplied with liquid even when the rotor chamber is at the operating speed of the
Motors weitgehend flüssigkeitsfrei ist, sieht die Erfindung vor, die den Rotor tragenden Lager ausserhalb des Rotorraums anzuordnen. Dabei wird jedoch mindestens ein den Rotor tragendes Lager, vorzugsweise das dem Pumpenlaufrad entferntere innerhalb des Spaltrohrs angeordnet, da dann eine Flüssigkeitsversorgung über die zentrale Wellenbohrung und somit auch ein weitgehender axialer Druckausgleich an der Welle stattfinden kann.Motor is largely liquid-free, the invention provides that the bearings supporting the rotor are arranged outside the rotor space. In this case, however, at least one bearing carrying the rotor, preferably that which is more distant from the pump impeller, is arranged within the can, since then a liquid supply can take place via the central shaft bore and thus also an extensive axial pressure compensation on the shaft.
Es ist günstig, wenn beide Wellenenden aus dem Rotorraum he- rausgeführt sind, wobei dann an einem Wellenende ein Laufrad vorgesehen ist und die aus dem Rotorraum abzuführende Flüssigkeit nahe dem dem Laufrad abgewandten Wellenende abgeführt wird. Wenn dann nämlich, wie vorstehend geschildert, ein Druckausgleich über eine Wellenbohrung oder eine andere Lei- tungsverbindung besteht, kann die Abfuhr der Flüssigkeit aus demIt is expedient if both shaft ends are led out of the rotor space, an impeller then being provided on one shaft end and the liquid to be removed from the rotor space being drained off near the shaft end facing away from the impeller. If, then, as described above, there is pressure equalization via a shaft bore or another line connection, the liquid can be removed from the
Rotorraum nahezu drucklos erfolgen und muss nicht gegen den Förderdruck der Pumpe erfolgen. Bei einer Leitungsverbindung durch die Welle, wenn also dieses'Wellenende mit dem Druck der Saugseite der Pumpe beaufschlagt ist, ist eine solche Abfuhr besonders leicht möglich.Rotor chamber take place almost without pressure and need not be against the Delivery pressure of the pump. In the case of a line connection through the shaft, that is to say when this end of the shaft is acted upon by the pressure on the suction side of the pump, such removal is particularly easy.
Als druckbegrenzt abdichtende Mittel werden vorzugsweise Gleitringdichtungen eingesetzt, wobei die Einstellung der Druckbegrenzung durch Wahl einer entsprechenden Feder erfolgt, mit der die Gleitringe in Kontakt gehalten werden.Mechanical seals are preferably used as pressure-limited sealing means, the pressure limitation being set by selecting a corresponding spring with which the sliding rings are kept in contact.
Zweckmäßig ist es, wenn die Gleitringdichtung jeweils zwischen Rotor und dem benachbarten Lager angeordnet ist, wobei die Lageraufnahme für das vom Laufrad entfernte Lager innerhalb des Spaltrohrs sitzt. Dabei wird die Lageraufnahme zweckmäßiger- weise mittels einer äusseren Dichtung gegenüber dem Spaltrohr und mittels einer inneren Dichtung gegenüber dem feststehenden Teil der Gleitringdichtung abgedichtet.It is expedient if the mechanical seal is arranged in each case between the rotor and the adjacent bearing, the bearing receptacle for the bearing removed from the impeller being seated within the can. The bearing receptacle is expediently sealed off from the can by means of an outer seal and against the fixed part of the mechanical seal by means of an inner seal.
Um die Flüssigkeit aus dem Rotorraum möglichst vollständig entfer- nen zu können, ist es zweckmäßig, dass entweder die Lageraufnahme oder die Gleitringdichtung mit Spiel stirnseitig an dem Rotor anliegen oder ein gesondertes Verdrängungsbauteil zwischen Lageraufnahme und Rotor vorgesehen ist, das das freie, im Betrieb durch Flüssigkeit ausfüllbare Volumen zwischen der Stirnsei- te des Rotors und der Lageraufnahme verringert. Dieses Verdrängerbauteil wird zweckmäßigerweise aus wärmeisolierendem Werkstoff, vorzugsweise Kunststoff, hergestellt, um zu verhindern, dass die im Rotorraum bewusst erzeugte Wärme zum Verdampfen der dort befindlichen Flüssigkeit stirnseitig abgeführt wird oder dass in diesem Bereich Kondensat entsteht. Aus diesem Grunde ist es zweckmäßig, auch die Lageraufnahmen aus einem wärmeisolierenden Werkstoff zu fertigen.In order to be able to remove the liquid from the rotor space as completely as possible, it is expedient that either the bearing holder or the mechanical seal is in contact with the end face of the rotor with play, or that a separate displacement component is provided between the bearing holder and the rotor, which allows the free, during operation The volume of liquid that can be filled between the face of the rotor and the bearing mount is reduced. This displacer component is expediently made of heat-insulating material, preferably plastic, in order to prevent the heat generated in the rotor chamber from being deliberately dissipated at the end for the evaporation of the liquid located there or that condensate is formed in this area. That's why it is expedient to also manufacture the bearing receptacles from a heat-insulating material.
Um eine möglichst schnelle und volständige Verdampfung der im Rotorraum befindlichen Flüssigkeit zu erzielen, kann es vorteilhaft sein, das Spaltrohr zumindest in einem Teilbereich beheizbar auszugestalten. Grundsätzlich kann die Wärmeerzeugung durch Reibung im Bereich zwischen Rotor und Spaltrohr erfolgen, so dass sich die Flüssigkeit am Hochfahren des Motors selbsttätig erhitzt und somit verdampft wird. Es kann jedoch auch ergänzend oder zum Verdampfen vor dem Anlaufen des Motors eine Spaltrohrheitzung vorgesehen sein, sei es durch eine elektrische Widerstandsheizung oder auch induktiv, insbesondere durch das zwischen Rotor und Stator im Betrieb gebildete Magnetfeld. Besonders vorteilhaft wird als Motor ein Permanentmagnetmotor eingesetzt.In order to achieve the fastest and most complete evaporation of the liquid in the rotor space, it can be advantageous to design the canned tube to be heatable at least in a partial area. In principle, the heat can be generated by friction in the area between the rotor and the can, so that the liquid heats up automatically when the engine is started up and is thus evaporated. However, in addition or for evaporation, a canned heater can be provided, either by electrical resistance heating or inductively, in particular by the magnetic field formed between the rotor and stator during operation. A permanent magnet motor is particularly advantageously used as the motor.
Die Erfindung ist nachfolgend anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher erläutert. Es zeigen:The invention is explained below with reference to an embodiment shown in the drawing. Show it:
Fig. 1 ein Längsschnitt durch ein Kreiselpumpenaggregat nach der Erfindung undFig. 1 is a longitudinal section through a centrifugal pump assembly according to the invention and
Fig. 2 die Einzelheit II in Figur 1 in vergrößerter Darstellung.Fig. 2 shows the detail II in Figure 1 in an enlarged view.
Das in den Figuren dargestellte Pumpenaggregat weist ein Gehäuse 1 runden Querschnitts auf, an dessen unterer Stirnseite ein saugseitiger Einlass 2 und an dessen oberer Stirnseite ein druckseitiger Auslass 3 gebildet ist. Die zu fördernde Flüssigkeit wird am Einlass 2 angesaugt, gelangt von dort in einen Saugmund 4 eines Kreiselrades 5 der Pumpe, von dem aus es radial nach außen in einen ringförmigen Kanal 6 zum Auslass 3 gelangt. Der Kanal 6 wird an seiner Außenseite durch das Gehäuse 1 begrenzt, auf seiner Innenseite durch ein Motorgehäuse 7, das innerhalb des Gehäuses 1 festgelegt ist. Die elektrische Versorgung des Aggregats erfolgt über einen seitlich aus dem Motorgehäuse 7, den Kanal 6 durchsetzenden und aus dem Gehäuse 1 herausgeführten elektrischen Anschluss 8. Das Motorgehäuse 7 nimmt einen Stator 9 auf, der an seiner Innenseite durch ein Spaltrohr 10 begrenzt ist. Innerhalb des Spaltrohrs 10 läuft ein Rotor 1 1 , der auf einer Welle 12 sitzt, die nahe ihren Enden in Gleitlagern 13, 14 gelagert ist, die in Lageraufnahmen 15, 16 sitzen, die innerhalb desThe pump unit shown in the figures has a housing 1 with a round cross section, on the lower end of which a suction-side inlet 2 and on the upper end of which a pressure-side outlet 3 is formed. The liquid to be pumped is sucked in at the inlet 2, from there it reaches a suction mouth 4 of a centrifugal wheel 5 of the pump, from which it goes radially outward into an annular channel 6 to the outlet 3. The channel 6 is delimited on its outside by the housing 1, on its inside by a motor housing 7 which is fixed within the housing 1. The electrical supply to the unit takes place via an electrical connection 8 passing laterally out of the motor housing 7, through the channel 6 and out of the housing 1. The motor housing 7 accommodates a stator 9 which is delimited on its inside by a can 10. Within the canned tube 10 runs a rotor 1 1, which is seated on a shaft 12 which is mounted near its ends in slide bearings 13, 14 which are seated in bearing seats 15, 16 which are located within the
Spaltrohrs 10 und somit innerhalb des Motorgehäuses 7 festgelegt sind.Canned tube 10 and thus within the motor housing 7 are fixed.
Das Spaltrohr 10 begrenzt radial einen Rotorraum 1 7, der stirnseitig durch Gleitringdichtungen 18, 19 räumlich und druckbegrenzt gegenüber dem übrigen Spaltrohrraum wird.The can 10 radially delimits a rotor space 17, which is spatially and pressure-limited in relation to the rest of the can space by mechanical seals 18, 19.
Die Welle 12, die innerhalb der Gleitlager 13 und 14 gelagert ist, trägt am unteren Ende das Laufrad 5 und im Übrigen den Rotor 1 1 . Sie weist eine zentrale Durchgangsbohrung 20 auf, welche eineThe shaft 12, which is mounted within the slide bearings 13 and 14, carries the impeller 5 at the lower end and, moreover, the rotor 11. It has a central through hole 20, which a
Leitungsverbindung zwischen dem Saugmund 4 und dem in Figur 1 oberen Ende des Motorgehäuses 7 bildet. Da die Welle 12 wie bei Nasslaufmotoren üblich, nicht gegenüber dem Pumpenraum abgedichtet ist, werden sowohl das obere Lager 13 über die Boh- rung 20 als auch das untere Lager 14 mit Förderflüssigkeit versorgt.Forms a line connection between the suction mouth 4 and the upper end of the motor housing 7 in FIG. 1. Since the shaft 12, as is usual with wet-running motors, is not sealed off from the pump chamber, both the upper bearing 13 are supplied with delivery fluid via the bore 20 and the lower bearing 14.
Dabei steht am unteren Lager 14 der Förderdruck der Pumpe an, wohingegen am oberen Lager 13 der saugseitige Druck anliegt. Der Rotorraum 17 ist lediglich über Gleitringdichtungen 18 und 19 gegenüber dem im Betrieb flüssigkeitsgefüllten Spaltrohrraum abgedichtet. Der Aufbau einer solchen Gleitringdichtung ist anhand der oberen Gleitringdichtung 18 in Figur 2 dargestellt. Die Gleitringdichtung 18 besteht aus einem stationären Gleitring 21 , der innerhalb des die Lageraufnahme 15 bildenden Bauteils eingegliedert, mittels eines O-Rings 22 gegenüber diesem radial abgedichtet und in Achsrichtung der Welle 12 verschiebbar gela- gert ist. Dieser stationäre Gleitring 21 wird von einer die Welle 12 umgebenden Schraubenfeder 23 druckkraftbeaufschlagt. Die Schraubenfeder 23 ist ebenfalls innerhalb des die Lageraufnahme 15 bildenden Bauteils angeordnet. Dieser zwischen Welle 12 und dem die Lageraufnahme 15 bildenden Bauteil gebildete Ringraum ist über einen Kanal 24 mit dem durch das Motorgehäuse 7 abgegrenzten Raum im Bereich des oberen Lagers 13 verbunden, der mit der Bohrung 20 in Leitungsverbindung steht.The delivery pressure of the pump is present at the lower bearing 14, whereas the suction-side pressure is present at the upper bearing 13. The rotor chamber 17 is only sealed via mechanical seals 18 and 19 from the canned chamber which is filled with liquid during operation. The structure of such a mechanical seal is shown in FIG. 2 using the upper mechanical seal 18. The mechanical seal 18 consists of a stationary slide ring 21, which is incorporated within the component forming the bearing receptacle 15, is radially sealed by means of an O-ring 22, and is mounted displaceably in the axial direction of the shaft 12. This stationary slide ring 21 is pressurized by a helical spring 23 surrounding the shaft 12. The coil spring 23 is also arranged within the component forming the bearing seat 15. This annular space formed between the shaft 12 and the component forming the bearing receptacle 15 is connected via a channel 24 to the space delimited by the motor housing 7 in the region of the upper bearing 13, which is in line connection with the bore 20.
Ein rotierender Gleitring 25 liegt stirnseitig an dem stationären Gleitring 21 an, er sitzt innerhalb eines Wellenabsatzes und rotiert mit der Welle 12.A rotating slide ring 25 abuts the stationary slide ring 21 on the end face, it sits within a shaft shoulder and rotates with the shaft 12.
Die so gebildete Gleitringdichtung 18 dichtet den Rotorraum 17 zum übrigen Spaltrohrraum ab, eine entsprechende Abdichtung ist auf der anderen Seite des Rotors 1 1 vorgesehen.The mechanical seal 18 thus formed seals the rotor space 17 from the rest of the canned space, a corresponding seal is provided on the other side of the rotor 11.
Beim Anlauf der Pumpe kann der Rotorraum 1 7 ganz oder teilweise mit Förderflüssigkeit gefüllt sein. Sobald die Motordrehzahl ansteigt, wird die im Rotorraum 1 7 befindliche Flüssigkeit erwärmt. Solange bis schließlich die Flüssigkeit verdampft und der Druck innerhalb des Rotorraums 17 rapide ansteigt. Wenn der durch die Gleitringdichtung 18 gebildetet und über die Druckkraft der Feder 23 festgelegte Grenzdruck überschritten ist, hebt der stationäre Gleitring vom rotierenden Gleitring 25 ab, bewegt sich also in der Dar- Stellung gemäß Figur 1 nach oben, wodurch der Rotorraum 1 7 mit dem das Lager 13 umgebenden Raum über den Kanal 24 leitungs- verbunden wird. Durch den im Rotorrαum 17 gebildeten Druck wird der Rotorrαum selbsttätig über die Gleitringdichtung 18 entleert, bis schließlich keine Flüssigkeit, sondern nur noch Dampf im Rotorraum befindlich ist. Dann arbeitet der Motor quasi wie ein Trockenlaufmotor. Die Betriebsdrehzahl eines solchen Motors kann beispielsweise zwischen 40.000 und 100.000 Umdrehungen pro Minute liegen. Der vorbeschriebene Vorgang wiederholt sich bei jedem Anlauf des Motors, sofern der Rotorraum 1 7 wieder flüssigkeitsgefüllt ist.When the pump starts up, the rotor space 17 can be completely or partially filled with delivery liquid. As soon as the engine speed increases, the liquid in the rotor chamber 17 is heated. Until the liquid evaporates and the pressure inside the rotor space 17 rises rapidly. If the limit pressure formed by the mechanical seal 18 and exceeded by the pressure force of the spring 23 is exceeded, the stationary seal ring lifts off the rotating seal ring 25, ie moves upwards in the illustration according to FIG. 1, whereby the rotor space 17 with the the space surrounding the bearing 13 via the duct 24 is connected. Due to the pressure formed in the rotor 17, the rotor is automatically emptied via the mechanical seal 18 until finally there is no liquid but only steam in the rotor space. Then the motor works like a dry-running motor. The operating speed of such an engine can be, for example, between 40,000 and 100,000 revolutions per minute. The process described above is repeated each time the motor is started, provided that the rotor space 17 is again filled with liquid.
Um eine möglichst vollständige Entfernung der Flüssigkeit aus dem Rotorraum 1 7 zu gewährleisten, sind stirnseitig des Rotors 1 1 ein mitlaufender erster Verdrängungskörper 26 vorgesehen, der stirnseitig des Rotors angeordnet ist, sowie ein zweiter feststehender Verdrängungskörper 27, der über einen O-Ring 28 dicht am Spaltrohr 10 anliegt. Die Verdrängungskörper 26 und 27 sind aus wärmeisolierendem Kunststoff gebildet und haben im Wesentlichen zwei Aufgaben. Sie sollen zum einen den im Rotorraum 1 7 zwischen Rotor 1 1 und dem die Lageraufnahme 15 bildenden Bauteil ver- bleibenden Raum weitgehend ausfüllen, um das freie Volumen desIn order to ensure as complete a removal of the liquid as possible from the rotor chamber 17, a rotating first displacement body 26 is provided on the front side of the rotor 11, which is arranged on the front side of the rotor, as well as a second fixed displacement body 27, which is sealed by an O-ring 28 abuts on the can 10. The displacers 26 and 27 are formed from heat-insulating plastic and have two main functions. On the one hand, they should largely fill the space remaining in the rotor space 17 between the rotor 11 and the component forming the bearing receptacle 15 in order to reduce the free volume of the
Rotorraums 1 7 und damit die mögliche Flüssigkeitsaufnahme desselben zu minimieren. Zum anderen stellen diese Körper 26 und 27 Isolationskörper dar, welche den im Betrieb heissen Rotorraum 1 7 von den benachbarten Lagerraum isolieren, um somit eine Kon- densatbildung in diesem Bereich und damit eine erhöhte Reibung zu vermeiden. Die Ausbildung und Anordnung der auf der anderen Seite des Rotors 1 1 angeordneten Gleitringdichtung 19 enspricht funktioneil der anhand des der Gleitringdichtung 18 beschriebenen Aufbaus. Auch dort sind Verdrängungskörper 26 und 27 vor- gesehen. Konstruktionsbedingt kann das Entfernen der Flüssigkeit aus dem Rotorraum 1 7 grundsätzlich über eine oder beide der Gleitringdichtungen 18 und 19 erfolgen. Bevorzugt wird dies jedoch über die obere Gleitringdichtung 18 erfolgen, da dort über die Bohrung 12 nur der saugseitige Druck anliegt, wohingegen an der anderen Gleitringdichtung 19 der druckseitige Druck anliegt, der beim Entfernen der Flüssigkeit aus dem Rotorraum überwunden werden muss.To minimize rotor space 1 7 and thus the possible liquid absorption of the same. On the other hand, these bodies 26 and 27 represent insulation bodies which isolate the rotor space 17, which is hot during operation, from the adjacent storage space, in order to avoid the formation of condensate in this area and thus increased friction. The design and arrangement of the mechanical seal 19 arranged on the other side of the rotor 11 corresponds functionally to that described with reference to the structure of the mechanical seal 18. Displacement bodies 26 and 27 are also provided there. Due to the design, the removal of the liquid from the rotor space 17 can in principle be carried out via one or both of the Mechanical seals 18 and 19 are made. However, this is preferably done via the upper mechanical seal 18, since only the suction-side pressure is present there via the bore 12, whereas the pressure-side pressure is present at the other mechanical seal 19, which pressure has to be overcome when the liquid is removed from the rotor space.
Bei dem vorstehend beschriebenen Ausführungsbeispiel erfolgt die Erwärung und Verdampfung der im Rotorraum befindlichen Flüssig- keit selbsttätig, sobald entsprechende Drehzahlbereiche erreicht werden. Es kann jedoch gemäß der Erfindung auch eine zusätzliche elektrische oder anderwertige Heizung vorgesehen sein, so kann insbsondere das Spaltrohr im Bereich ausserhalb des Rotors 12, also dort, wo die Verdrängungskörper 26 und 27 angordnet sind, beheizt sein. Auch kann anstelle der Gleitringdichtung einIn the exemplary embodiment described above, the liquid in the rotor space is automatically heated and evaporated as soon as corresponding speed ranges are reached. However, according to the invention, an additional electrical or other type of heating can also be provided, in particular the canned tube can be heated in the area outside the rotor 12, that is to say where the displacement bodies 26 and 27 are arranged. Can also be used instead of a mechanical seal
Überdruckventil an geeigneter stelle im Rotorraum, beispielsweise im Spaltrohr vorgesehen sein, um die Flüssigkeit zu entfernen. Der im Ausführungsbeispiel dargestellte Motor ist ein Gleichstrommotor, es können jedoch auch Wechsel- bzw. Starkstrommotoren einge- setzt werden. Pressure relief valve can be provided at a suitable location in the rotor space, for example in the can, in order to remove the liquid. The motor shown in the exemplary embodiment is a direct current motor, but alternating current or heavy current motors can also be used.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
Gehäusecasing
Einlassinlet
Auslassoutlet
Saugmundsaugmund
Kreiselradimpeller
Kanalchannel
Motorgehäuse elektrischer AnschlussMotor housing electrical connection
Statorstator
Spaltrohrcanned
Rotorrotor
Wellewave
Lager obenBearing upstairs
Lager untenCamp below
Lageraufnahme obenStock upstairs
Lageraufnahme untenInventory below
Rotorraumrotor chamber
Gleitringdichtung obenMechanical seal on top
Gleitringdichtung untenMechanical seal below
Bohrung in der Welle stationärer GleitringBore in the shaft of the stationary slide ring
O-RingO-ring
Schraubenfedercoil spring
Kanal rotierender GleitringChannel rotating slide ring
Verdrängungskörperdisplacer
Verdrängungskörperdisplacer
O-Ring O-ring

Claims

A N S P R U C H E EXPECTATIONS
1 . Verfahren zum Betreiben eines Pumpenaggregats mit einer Kreiselpumpe und mit einem diese antreibenden Elektromotor, dessen Rotor (1 1 ) in einem Spaltrohr (10) läuft, das den Rotorraum (1 7) gegenüber dem Stator (9) fluiddicht trennt, dadurch gekennzeichnet, dass vor, während und/oder nach dem Hochfahren des Motors auf eine Betriebsdrehzahl die im Rotorraum (1 7) befindliche Flüssigkeit zumindest teilweise entfernt wird.1 . Method for operating a pump assembly with a centrifugal pump and with an electric motor driving it, the rotor (1 1) of which runs in a can (10) which separates the rotor space (1 7) from the stator (9) in a fluid-tight manner, characterized in that before , during and / or after the engine is ramped up to an operating speed, the liquid in the rotor space (17) is at least partially removed.
2. Verfahren nach Anspruch 1 , dadurch gekennzeichnet, dass die zwischen Rotor ( 1 1 ) und Spaltrohr (10) befindliche Flüssigkeit durch Wärmeeinwirkung verdampft wird.2. The method according to claim 1, characterized in that the liquid located between the rotor (1 1) and the can (10) is evaporated by the action of heat.
3. Pumpenaggregat, insbesondere zum Betreiben nach einem3. Pump unit, in particular for operation after a
Verfahren gemäß Anspruch 1 oder 2, mit einer Kreiselpumpe und mit einem diese antreibenden Elektromotor, dessen Rotor ( 1 1 ) in einem Spaltrohr ( 10) läuft, das den Rotorraum( 17) gegenüber dem Stator (9) fluiddicht trennt, dadurch gekennzeichnet, dass Mittel (18, 19, 23) vorgesehen sind, die den Rotorraum (1 7) gegenüber der Förderflüssigkeit druckbegrenzt abdichten.Method according to claim 1 or 2, with a centrifugal pump and with an electric motor driving it, the rotor (1 1) of which runs in a can (10) which separates the rotor chamber (17) from the stator (9) in a fluid-tight manner, characterized in that Means (18, 19, 23) are provided which seal the rotor space (1 7) against the conveying liquid in a pressure-limited manner.
4. Pumpenaggregat nach Anspruch 3, dadurch gekennzeich- net, dass die den Rotor ( 1 1 ) tragenden Lager (13, 14) aus- serhalb des Rotorraums (1 7) angeordnet sind. 4. Pump unit according to claim 3, characterized in that the bearings (13, 14) carrying the rotor (1 1) are arranged outside the rotor space (1 7).
5. Pumpenαggregαt nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens ein den Rotor (11) tragendendes Lager (13, 14) innerhalb des Spaltrohrs (10) angeordnet ist.5. Pumpenαggregαt according to any one of the preceding claims, characterized in that at least one bearing (13, 14) supporting the rotor (11) is arranged within the can (10).
6. Pumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass beide Wellenenden aus dem Rotorraum (17) herausgeführt sind, dass an einem Wellenende ein Laufrad (5) vorgesehen ist und dass die zu ent- fernende Flüssigkeit nahe dem dem Laufrad6. Pump unit according to one of the preceding claims, characterized in that both shaft ends are led out of the rotor chamber (17), that an impeller (5) is provided at one shaft end and that the liquid to be removed is close to the impeller
(5)abgewandten Wellenende abgeführt wird.(5) facing away from the shaft end.
7. Pumpenaggregat nach Anspruch 1, dadurch gekennzeichnet, dass die den Rotorraum (17) gegenüber der Förder- flüssigkeit druckbegrenzt abdichtenden Mittel durch mindestens eine Gleitringdichtung (18, 19) gebildet sind.7. Pump unit according to claim 1, characterized in that the means sealing the rotor space (17) with respect to the delivery liquid and pressure-limited are formed by at least one mechanical seal (18, 19).
8. Tauchpumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein die Welle (12) des Rotors (11) aufnehmendes Lager (13, 14) in einer Lageraufnahme (15, 16) sitzt, welche in das Spaltrohr (10) eingegliedert ist, und dass die Gleitringdichtung (18, 19) zwischen dem Rotor (11) und einer Lageraufnahme (15, 16) angeordnet ist.8. Submersible pump unit according to one of the preceding claims, characterized in that a shaft (12) of the rotor (11) accommodating bearing (13, 14) is seated in a bearing seat (15, 16) which is incorporated in the can (10) , and that the mechanical seal (18, 19) between the rotor (11) and a bearing holder (15, 16) is arranged.
9. Tauchpumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Lageraufnahme (15, 16) mittels einer äußeren Dichtung (28) gegenüber dem Spaltrohr (10) und mittels einer inneren Dichtung(22) gegenüber dem feststehenden Teil (21) der9. Submersible pump unit according to one of the preceding claims, characterized in that the bearing receptacle (15, 16) by means of an outer seal (28) relative to the can (10) and by means of an inner seal (22) relative to the fixed part (21)
Gleitringdichtung (18, 19) abgedichtet ist. Mechanical seal (18, 19) is sealed.
10. Tαuchpumpenαggregαt nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Lageraufnahme ( 15, 16) oder die Gleitringdichtung ( 18, 19) mit Spiel stirnseitig an dem Rotor ( 1 1 ) anliegt oder ein gesondertes Verdrängungsbauteil (26, 27) zwischen Lageraufnahme (15,10. Tαuchpumpenαggregαt according to one of the preceding claims, characterized in that the bearing holder (15, 16) or the mechanical seal (18, 19) rests with play on the end face of the rotor (1 1) or a separate displacement component (26, 27) between the bearing holder (15,
1 6) und Rotor ( 1 1 ) vorgesehen ist, welches das freie, im Betrieb durch Flüssigkeit ausfüllbare Volumen zwischen Ro- tor( l 1 ) und Lageraufnahme ( 15, 1 6) verringert.1 6) and rotor (1 1) is provided, which reduces the free volume that can be filled with liquid during operation between the rotor (l 1) and the bearing holder (15, 1 6).
1 1 . Tauchpumpenaggregat nach einem der vorhergehenden1 1. Submersible pump unit according to one of the preceding
Ansprüche, dadurch gekennzeichnet, dass die Dichtungen (22, 28) zwischen Lageraufnahme ( 15, 1 6) und Spaltrohr(I O) sowie zwischen Lageraufnahme ( 15, 1 6) und dem feststehenden Teil (21 ) der Gleitringdichtung ( 18, 19) durch 0-Ringe(22, 28) gebildet sind.Claims, characterized in that the seals (22, 28) between the bearing seat (15, 1 6) and the can (IO) and between the bearing seat (15, 1 6) and the fixed part (21) of the mechanical seal (18, 19) 0-rings (22, 28) are formed.
12. Tauchpumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Lageraufnahme ( 15, 16) und/oder das Verdrängungsbauteil (26, 27) aus einem wärmeisolierenden Werkstoff besteht.12. Submersible pump unit according to one of the preceding claims, characterized in that the bearing holder (15, 16) and / or the displacement component (26, 27) consists of a heat-insulating material.
13. Tauchpumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Spaltrohr(l O) zumindest in einem Teilbereich beheizbar ist.13. Submersible pump unit according to one of the preceding claims, characterized in that the can (l O) can be heated at least in a partial area.
14. Tauchpumpenaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Spaltrohr(l O) elektrisch beheizbar ist.14. Submersible pump unit according to one of the preceding claims, characterized in that the can (l O) is electrically heated.
15. Tauchpumpenaggregat nach einem der vorhergehenden15. Submersible pump unit according to one of the preceding
Ansprüche, dadurch gekennzeichnet, dass das Spaltrohr(I O) induktiv beheizbar ist, insbesondere durch das zwischen Rotor ( 1 1 ) und Stator (9) im Betrieb gebildete Magnetfeld. Claims, characterized in that the can (IO) can be heated inductively, in particular by the magnetic field formed between the rotor (1 1) and the stator (9) during operation.
6. Tαuchpumpenαggregαt nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Motor ein Permanentmagnetmotor ist. 6. Tαuchpumpenαggregαt according to one of the preceding claims, characterized in that the motor is a permanent magnet motor.
EP01991838A 2000-12-22 2001-12-13 Method for operating a motor pump Expired - Lifetime EP1343972B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10064717A DE10064717A1 (en) 2000-12-22 2000-12-22 Method for operating a pump set
DE10064717 2000-12-22
PCT/EP2001/014656 WO2002052156A1 (en) 2000-12-22 2001-12-13 Method for operating a motor pump

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EP1343972A1 true EP1343972A1 (en) 2003-09-17
EP1343972B1 EP1343972B1 (en) 2009-01-14

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EP01991838A Expired - Lifetime EP1343972B1 (en) 2000-12-22 2001-12-13 Method for operating a motor pump

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US (1) US7264450B2 (en)
EP (1) EP1343972B1 (en)
JP (1) JP4195291B2 (en)
CN (1) CN1238638C (en)
AT (1) ATE421041T1 (en)
DE (2) DE10064717A1 (en)
WO (1) WO2002052156A1 (en)

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Publication number Publication date
ATE421041T1 (en) 2009-01-15
US7264450B2 (en) 2007-09-04
US20040052645A1 (en) 2004-03-18
JP2004516422A (en) 2004-06-03
CN1238638C (en) 2006-01-25
EP1343972B1 (en) 2009-01-14
JP4195291B2 (en) 2008-12-10
CN1481478A (en) 2004-03-10
DE10064717A1 (en) 2002-07-11
DE50114665D1 (en) 2009-03-05
WO2002052156A1 (en) 2002-07-04

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