EP0078345A1 - Centrifugal pump with axial thrust compensation driven by an air-gap sleeve motor - Google Patents

Centrifugal pump with axial thrust compensation driven by an air-gap sleeve motor Download PDF

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Publication number
EP0078345A1
EP0078345A1 EP81109474A EP81109474A EP0078345A1 EP 0078345 A1 EP0078345 A1 EP 0078345A1 EP 81109474 A EP81109474 A EP 81109474A EP 81109474 A EP81109474 A EP 81109474A EP 0078345 A1 EP0078345 A1 EP 0078345A1
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EP
European Patent Office
Prior art keywords
pump
gap
chamber
high pressure
centrifugal pump
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.)
Withdrawn
Application number
EP81109474A
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German (de)
French (fr)
Inventor
Volker Stapelfeldt
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.)
BRAN and LUEBBE
SPX Flow Technology Germany GmbH
Original Assignee
BRAN and LUEBBE
Bran und Luebbe GmbH
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Application filed by BRAN and LUEBBE, Bran und Luebbe GmbH filed Critical BRAN and LUEBBE
Priority to EP81109474A priority Critical patent/EP0078345A1/en
Publication of EP0078345A1 publication Critical patent/EP0078345A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D13/0613—Special connection between the rotor compartments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a canned motor centrifugal pump with axial thrust compensation, with a casing that accommodates the canned pipe and encloses at least one pump impeller, a rotatable and axially displaceably mounted rotor shaft that supports the rotor and one or more pump impellers, at least one in the housing from the high pressure side of the pump to the canned interior of the partial flow duct for passing a partial material flow that is used for heat dissipation and lubrication through the rotor gap and to the slide bearings, one formed between the pump impeller and an intermediate wall of the housing and communicating with the bearing gap of the pump-mounted sliding bearing and an annular gap between the pump impeller and the intermediate wall of the housing Compensation chamber, arranged in the rear wall of the pump impeller facing this, the low pressure side of which connects the compensation chamber with through-openings and, if appropriate, the flow cross-section for the material to be conveyed om with axial displacements of the rotor shaft itself active counteracting changing throttle devices
  • the axial thrust compensation is also greatly influenced by the size of the partial flow and the changes in the conveyed material forming the partial flow during operation.
  • changes in the composition and / or the temperature of the conveyed material forming the partial flow often lead to strong changes in viscosity, which lead to undesirable axial displacements of the rotor shaft in the conventional designs.
  • the setting of the central axial position of the rotor shaft on the test bench is carried out by correspondingly setting the cross-sectional dimensions of the through openings in the pump impeller.
  • the size of these passage openings can not be changed during operation.
  • Another difficulty is that the test benches for such centrifugal pumps are usually always with and for cost reasons the same pumped medium and not operated with the pumped material for which the respective centrifugal pump is to be used later in operation.
  • the resulting viscosity differences between the test medium and the medium to be pumped in practice also result in deviations in the axial position of the rotor shaft.
  • the centrifugal pump of the type mentioned is characterized in accordance with the invention in that the high-pressure chamber. is connected to the equalization chamber by an inlet channel with a larger flow cross-section relative to the bearing gap of the pump-mounted slide bearing and to the annular gap between the pump impeller and the intermediate wall of the housing, and the inlet channel has a flow control device, which is also adjustable during operation, for regulating the pressure in the equalizing chamber.
  • the centrifugal pump can be quickly and easily adapted to changes in the composition and / or the physical data (temperature, viscosity, etc.) of the material to be conveyed and any undesirable axial load on the bearings can be avoided, which increases operational reliability and the service life.
  • centrifugal pump It is particularly advantageous to detect the axial position of the rotor shaft by means of a corresponding position indicator and to provide an adjustment device for the flow control device that is automatically actuated by the signals thereof. In this way, the axial position of the rotor shaft can be kept optimally without operating effort.
  • the canned motor centrifugal pump 1 shown in the figures has a casing 2 enclosing the canned motor and the pump impeller 19, which contains the canned pipe 6 tightly installed therein and the stator 7 of the canned motor surrounding it.
  • a rotor shaft 13 which supports the rotor 14 of the canned motor, is rotatably and axially displaceably limited in a sliding bearing 9 near the pump and a sliding bearing 11 remote from the pump.
  • the plain bearing 9 close to the pump is arranged in an intermediate wall 5 of the housing.
  • the hollow rotor shaft 13 provided with a continuous return channel 17 is connected to the pump impeller 19 in a rotationally fixed manner.
  • the pump impeller 19 When the pump impeller 19 is set into rapid rotation by the current flowing in the winding of the stator 7 via the rotor 14 seated on the rotor shaft 13, the pump impeller 19 sucks the conveyed material out of the low-pressure space 3, which by centrifugal force into the pump impeller 19 surrounding high pressure chamber 4 is promoted and flows out of it.
  • the high pressure chamber 4 is of low pressure room 3 separated by an annular gap 29.
  • a partial flow duct 16 leads through the housing intermediate wall 5 to the canned interior 8.
  • the partial material flow flowing through the partial flow duct 16 flows through the rotor gap 15 between the outer surface of the rotor 14 and the canned pipe 6 and also becomes the bearing gap 10 near the pump Plain bearing 9 and the bearing gap 12 of the pump-remote sliding bearing 11 supplied.
  • the main quantity of the partial flow is discharged via a throttle gap 28 formed between the end of the rotor shaft 13 remote from the pump and a collar of the housing which surrounds it at a short distance, the cross section of which is larger or smaller depending on the axial position of the rotor shaft 13. After passing the throttle gap 28, the partial flow flows back through the return duct 17 in the rotor shaft 13 to the low-pressure chamber 3.
  • a compensation chamber 18 is provided which communicates on the one hand with the bearing gap 10 of the sliding bearing 9 close to the pump and on the other hand is separated from the high-pressure chamber 4 by an axial annular gap 21 and an adjoining radial annular gap.
  • the compensation chamber 18 is also connected to the low-pressure side by through openings 20 arranged in the rear wall of the pump impeller 19.
  • an inlet channel 22 is also provided in the intermediate wall 5 of the housing, which in the illustrated embodiment starts from the canned interior 8 and leads to the compensation chamber 18.
  • a flow control device 23 is provided in the inlet channel 22, which in the embodiment shown in FIG. 2 can be adjusted by an actuating device 25 to be actuated from the outside in order to regulate the flow rate through the inlet channel 22.
  • the actuating device 25 is actuated by the signals of a position indicator device 24 which detects the axial position of the rotor shaft 13 and which is arranged on a tube which projects from the housing 2 in a pressure-tight manner and in which there is an extension of the rotor shaft 13 can move axially.
  • a partial flow branched off from the high-pressure space via the partial flow channel 16 is introduced into the can interior.
  • the partial atom is passed on the one hand through the rotor gap 15 and to the bearing gaps 10 and 12 of the slide bearings in order to dissipate the heat generated there on the one hand and to have a lubricating effect on the other.
  • the partial flow flowing away from the pump at the end of the rotor shaft 13 through the throttle gap 28 and the return duct 17 generates a liquid pressure acting on the rotor shaft 13 in the direction of the low-pressure chamber 3.
  • the part of the conveyed material emerging through the bearing gap 10 of the sliding bearing 9 near the pump reaches the equalizing chamber 18 and from there via the passage openings 20 back into the pump impeller 19.
  • a partial flow which can be regulated via the flow control device 23 flows from the canned space interior 8 via the inlet channel 22 to the compensation chamber 18. Since the flow cross section of the inlet channel 22 is larger than the flow cross section of the bearing gap 10 of the slide bearing 9 near the pump and of the annular gap 21, the pressure in the compensation chamber 18 and thus on the surfaces of the pump impeller 19 lying in the compensation chamber 18 Exerted pushing force can be adjusted appropriately by actuating the flow control device 23 without the size of the partial flow flowing through the rotor gap 15 being significantly changed thereby. When the flow control device 23 is closed, the compensation chamber 18 only receives the quantity of conveyed material passing through the bearing gap 10 of the sliding bearing 9 near the pump and the annular gap 21.
  • the compensation chamber 18 flows to conveyed goods according to the sum of the flow cross-sections of the inlet channel 22, the bearing gap 10 of the pump-bearing slide bearing 9 and the annular gap 21.
  • the pressure in the compensation chamber 18 can be varied within wide limits, whereby the axial position of the rotor shaft 13 can be changed in the desired manner and can be optimally adapted to the operating conditions.
  • centrifugal pump explained above on the basis of a preferred exemplary embodiment can be modified appropriately by the person skilled in the art in various ways depending on the requirements of the individual case, as long as the supply of conveyed material, which can also be regulated externally during operation, to a compensating chamber influencing the axial position of the rotor shaft without a substantial change in the is achieved by the partial flow flowing through the rotor gap.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The pump has a subflow channel leading from the high pressure side to the interior of the air-gap sleeve, and a balancing chamber, which is formed between the pump impeller and a casing partition and communicates, on the one hand, with the bearing gap of the sliding bearing near the pump and, on the other hand, with the low pressure side via passage openings, and which is additionally connected to the high pressure side via an inlet channel which has a flow-regulating device that can be adjusted in operation. <IMAGE>

Description

Die Erfindung betrifft eine Spaltrohrmotor-Kreiselpumpe mit Axialschubausgleich, mit einem das Spaltrohr aufnehmenden, mindestens ein Pumpenlaufrad umschließenden Gehäuse, einer darin in Gleitlagern drehbar und begrenzt axial verschiebbar gelagerten, den Rotor und ein oder mehrere Pumpenlaufräder tragenden Rotorwelle, mindestens einem im Gehäuse von der Hochdruckseite der Pumpe zum Spaltrohr-Innenraum führenden Teilstromkanal zum Hindurchleiten eines zur Wärmeabführung und Schmierung dienenden Fördergut-Teilstromes durch den Rotorspalt und zu den Gleitlagern, einer zwischen dem Pumpenlaufrad und einer Gehäusezwischenwand gebildeten, mit dem Lagerspalt des pumpennahen Gleitlagers und einem Ringspalt zwischen Pumpenlaufrad und Gehäusezwischenwand kommunizierenden Ausgleichskammer, in der dieser zugewandten Rückwand des Pumpenlaufrades angeordneten, dessen Niederdruckseite mit der Ausgleichskammer verbindenden Durchlaßöffnungen sowie ggf. den Durchflußquerschnitt für den Fördergut-Teilstrom bei Axialverschiebungen der Rotorwelle selbsttätig gegensteuernd verändernden Drosselvorrichtungen.The invention relates to a canned motor centrifugal pump with axial thrust compensation, with a casing that accommodates the canned pipe and encloses at least one pump impeller, a rotatable and axially displaceably mounted rotor shaft that supports the rotor and one or more pump impellers, at least one in the housing from the high pressure side of the pump to the canned interior of the partial flow duct for passing a partial material flow that is used for heat dissipation and lubrication through the rotor gap and to the slide bearings, one formed between the pump impeller and an intermediate wall of the housing and communicating with the bearing gap of the pump-mounted sliding bearing and an annular gap between the pump impeller and the intermediate wall of the housing Compensation chamber, arranged in the rear wall of the pump impeller facing this, the low pressure side of which connects the compensation chamber with through-openings and, if appropriate, the flow cross-section for the material to be conveyed om with axial displacements of the rotor shaft itself active counteracting changing throttle devices.

Bei den aus der DE-AS 12 57 581 bekannten Spaltrohrmotor-Kreiselpumpen dieser Artefolgt der Axialschubausgleich dadurch, daß beide Seiten des Spaltrohr-Innenraumes jeweils über die mit Nuten versehenen Spalte der Gleitlager und an diese angrenzende radiale Ringspalte mit Räumen niedrigeren Druckes verbunden sind, wobei je nach der axialen Stellung der Rotorwelle der Durchflußquerschnitt des einen oder des anderen radialen Ringspalts verändert und durch die dabei erzeugte Druckdifferenz eine Rückstellung der Rotorwelle bewirkt wird. Da der durch den Rotorspalt geleitete Teilstrom jedoch auch der Abführung der vom Motor und von den Gleitlagern erzeugten Wärme dienen soll, ist jede durch eine zum Axialschubausgleich erfolgende Drosselung des Teilstroms für die Wärmeabführung von Nachteil. Darüber hinaus wird auch der Axialschubausgleich durch die Größe des Teilstroms sowie die im Betrieb auftretenden Veränderungen des den Teilstrom bildenden Förderguts stark beeinflußt. So treten beispielsweise mit Veränderungen in der Zusammensetzung und/oder der Temperatur des den Teilstrom bildenden Förderguts vielfach starke Viskositätsveränderungen ein, die bei den herkömmlichen Konstruktionen zu unerwünschten Axialverschiebungen der Rotorwelle führen.In the canned motor centrifugal pumps of this type e known from DE-AS 12 57 581, the axial thrust compensation follows in that both sides of the canned interior are each connected to spaces of lower pressure via the grooved column of the slide bearings and adjacent radial annular gaps , depending on the axial position of the rotor shaft, the flow cross-section of one or the other radial annular gap is changed and a reset of the rotor shaft is brought about by the pressure difference generated in the process. However, since the partial flow conducted through the rotor gap is also intended to dissipate the heat generated by the motor and the plain bearings, any throttling of the partial flow which is used to compensate for axial thrust is disadvantageous for heat dissipation. In addition, the axial thrust compensation is also greatly influenced by the size of the partial flow and the changes in the conveyed material forming the partial flow during operation. For example, changes in the composition and / or the temperature of the conveyed material forming the partial flow often lead to strong changes in viscosity, which lead to undesirable axial displacements of the rotor shaft in the conventional designs.

Bei Kreiselpumpen der hier betrachteten Art erfolgt die Einstellung der mittleren axialen Stellung der Rotorwelle auf dem Prüfstand durch entsprechende Einstellung der Querschnittsabmessungen der Durchlaßöffnungen im Pumpenlaufrad. Die Größe dieser Durchlaßöffnungen kann aber während des Betriebs nicht verändert werden. Eine weitere Schwierigkeit besteht darin, daß die Prüfstände für derartige Kreiselpumpen normalerweise aus Kostengründen stets mit ein und demselben Fördermedium und nicht mit dem Fördergut betrieben werden, für das die jeweilige Kreiselpumpe später im Betrieb eingesetzt werden soll. Die dadurch bedingten Viskositätsunterschiede zwischen dem Prüfmedium und dem im Praxisbetrieb zu fördernden Medium ergeben ebenfalls Abweichungen in der axialen Stellung der Rotorwelle.In centrifugal pumps of the type considered here, the setting of the central axial position of the rotor shaft on the test bench is carried out by correspondingly setting the cross-sectional dimensions of the through openings in the pump impeller. The size of these passage openings can not be changed during operation. Another difficulty is that the test benches for such centrifugal pumps are usually always with and for cost reasons the same pumped medium and not operated with the pumped material for which the respective centrifugal pump is to be used later in operation. The resulting viscosity differences between the test medium and the medium to be pumped in practice also result in deviations in the axial position of the rotor shaft.

Aufgabe der Erfindung ist es nun, eine Kreiselpumpe der eingangs genannten Art zu schaffen, die mit einfachen Mitteln eine von der Größe des durch den Spaltrohr-Innenraum geführten Teilstrom unabhängige, auch bei laufendem Betrieb durchführbare Regelung des Axialschubausgleichs gestattet.It is an object of the invention to provide a centrifugal pump of the type mentioned at the outset which, with simple means, permits regulation of the axial thrust compensation which is independent of the size of the partial flow passed through the interior of the canned tube and which can also be carried out during operation.

Zur Lösung dieser Aufgabe ist die Kreiselpumpe der eingangs genannten Art erfindungsgemäß dadurch gekennzeichnet, daß der Hochdruckraum . mit der Ausgleichskammer durch einen Einlaßkanal mit relativ zum Lagerspalt des pumpennahen Gleitlagers und zum Ringspalt zwischen dem Pumpenlaufrad und der Gehäusezwischenwand größerem Strömungsquerschnitt verbunden ist und der Einlaßkanal eine auch im Betrieb verstellbare Durchfluß-Regelvorrichtung zur Regelung des Druckes in der Ausgleichskammer aufweist.To solve this problem, the centrifugal pump of the type mentioned is characterized in accordance with the invention in that the high-pressure chamber. is connected to the equalization chamber by an inlet channel with a larger flow cross-section relative to the bearing gap of the pump-mounted slide bearing and to the annular gap between the pump impeller and the intermediate wall of the housing, and the inlet channel has a flow control device, which is also adjustable during operation, for regulating the pressure in the equalizing chamber.

Auf diese Weise wird mit geringem Aufwand eine auch bei laufender Kreiselpumpe einfache Verstellbarkeit der axialen Stellung der Rotorwelle ermöglicht. Dadurch kann die Kreiselpumpe rasch und einfach sowohl Veränderungen in der Zusammensetzung und/oder den physikalischen Daten (Temperatur, Viskosität, etc.) des Förderguts angepaßt und jede unerwünschte Axialbelastung der Lager vermieden werden, was die Betriebssicherheit und die Lebensdauer erhöht.In this way, the axial position of the rotor shaft can be adjusted easily with little effort, even when the centrifugal pump is running. As a result, the centrifugal pump can be quickly and easily adapted to changes in the composition and / or the physical data (temperature, viscosity, etc.) of the material to be conveyed and any undesirable axial load on the bearings can be avoided, which increases operational reliability and the service life.

Vorteilhafte weitere Ausgestaltungen der Kreiselpumpe sind in den Unteransprüchen beschrieben. Besonders vorteilhaft ist, die axiale Stellung der Rotorwelle durch eine entsprechende Stellungs-Anzeigevorrichtung zu erfassen und eine durch deren Signale automatisch betätigte Verstellvorrichtung für die Durchfluß-Regelvorrichtung vorzusehen. Auf diese Weise kann die axiale Stellung der Rotorwelle ohne Bedienungsaufwand optimal gehalten werden.Advantageous further developments of the centrifugal pump are described in the subclaims. It is particularly advantageous to detect the axial position of the rotor shaft by means of a corresponding position indicator and to provide an adjustment device for the flow control device that is automatically actuated by the signals thereof. In this way, the axial position of the rotor shaft can be kept optimally without operating effort.

Im folgenden wird eine bevorzugte Ausführungsform der erfindungsgemäßen Kreiselpumpe unter Bezugnahme auf die beigefügten Zeichnungen weiter erläutert. Es zeigen:

  • Fig. 1 einen schematischen Längsschnitt durch eine erfindungsgemäße Kreiselpumpe und
  • Fig.·2 einen vergrößerten Längsschnitt durch einen Teil der Kreiselpumpe gemäß Fig. 1.
In the following a preferred embodiment of the centrifugal pump according to the invention is further explained with reference to the accompanying drawings. Show it:
  • Fig. 1 shows a schematic longitudinal section through a centrifugal pump according to the invention and
  • 2 shows an enlarged longitudinal section through part of the centrifugal pump according to FIG. 1.

Die in den Figuren dargestellte Spaltrohrmotor-Kreiselpumpe 1 besitzt ein den Spaltrohrmotor und das Pumpenlaufrad 19 umschließendes Gehäuse 2, welches das darin dicht eingebaute Spaltrohr 6 und den dieses umgebenden Stator 7 des Spaltrohrmotors enthält. Im Inneren des Gehäuses 2 ist eine den Rotor 14 des Spaltrohrmotors tragende Rotorwelle 13 in einem pumpennahen Gleitlager 9 und einem pumpenfernen Gleitlager 11 drehbar und begrenzt axial verschiebbar gelagert. Das pumpennahe Gleitlager 9 ist in einer Gehäusezwischenwand 5 angeordnet. Die mit einem durchgehenden Rückführkanal 17 versehene hohle Rotorwelle 13 ist mit dem Pumpenlaufrad 19 drehfest verbunden. Wenn das Pumpenlaufrad 19 über den auf der Rotorwelle 13 sitzenden Rotor 14 von dem in der Vicklung des Stators 7 fließenden Strom in schnelle Umdrehung versetzt wird, saugt das Pumpenlaufrad 19 aus dem Niederdruckraum 3 das Fördergut an, das durch Einwirkung der Zentrifugalkraft in den das Pumpenlaufrad 19 umgebenden Hochdruckraum 4 gefördert wird und aus diesem abströmt. Der Hochdruckraum 4 ist vom Niederdruckraum 3 durch einen Ringspalt 29 getrennt.The canned motor centrifugal pump 1 shown in the figures has a casing 2 enclosing the canned motor and the pump impeller 19, which contains the canned pipe 6 tightly installed therein and the stator 7 of the canned motor surrounding it. In the interior of the housing 2, a rotor shaft 13, which supports the rotor 14 of the canned motor, is rotatably and axially displaceably limited in a sliding bearing 9 near the pump and a sliding bearing 11 remote from the pump. The plain bearing 9 close to the pump is arranged in an intermediate wall 5 of the housing. The hollow rotor shaft 13 provided with a continuous return channel 17 is connected to the pump impeller 19 in a rotationally fixed manner. When the pump impeller 19 is set into rapid rotation by the current flowing in the winding of the stator 7 via the rotor 14 seated on the rotor shaft 13, the pump impeller 19 sucks the conveyed material out of the low-pressure space 3, which by centrifugal force into the pump impeller 19 surrounding high pressure chamber 4 is promoted and flows out of it. The high pressure chamber 4 is of low pressure room 3 separated by an annular gap 29.

Vom Hochdruckraum 4 führt ein Teilstromkanal 16 durch die Gehäusezwischenwand 5 zum Spaltrohr-Innenraum 8. Der durch den Teilstromkanal 16 zuströmende Fördergut-Teilstrom fließt durch den Rotorspalt 15 zwischen der Außenfläche des Rotors 14 und dem Spaltrohr 6 hindurch und wird außerdem dem Lagerspalt 10 des pumpennahen Gleitlagers 9 und dem Lagerspalt 12 des pumpenfernen Gleitlagers 11 zugeführt. Die Abführung der Hauptmenge des Teilstroms erfolgt über einen zwischen dem pumpenfernen Ende der Rotorwelle 13 und einem diese in geringem Abstand umschließenden Kragen des Gehäuses gebildeten Drosselspalt 28, dessen Querschnitt je nach der axialen Stellung der Rotorwelle 13 größer oder kleiner ist. Nach dem Passieren des Drosselspalts 28 strömt der Teilstrom durch den Rückführkanal 17 in der Rotorwelle 13 zum Niederdruckraum 3 zurück.From the high-pressure chamber 4, a partial flow duct 16 leads through the housing intermediate wall 5 to the canned interior 8. The partial material flow flowing through the partial flow duct 16 flows through the rotor gap 15 between the outer surface of the rotor 14 and the canned pipe 6 and also becomes the bearing gap 10 near the pump Plain bearing 9 and the bearing gap 12 of the pump-remote sliding bearing 11 supplied. The main quantity of the partial flow is discharged via a throttle gap 28 formed between the end of the rotor shaft 13 remote from the pump and a collar of the housing which surrounds it at a short distance, the cross section of which is larger or smaller depending on the axial position of the rotor shaft 13. After passing the throttle gap 28, the partial flow flows back through the return duct 17 in the rotor shaft 13 to the low-pressure chamber 3.

Zwischen der Gehäusezwischenwand 5 und der dieser zugewandten Rückseite des Pumpenlaufrades 19 ist eine Ausgleichskammer 18 vorgesehen, die einerseits mit dem Lagerspalt 10 des pumpennahen Gleitlagers 9 kommuniziert und andererseits vom Hochdruckraum 4 durch einen axialen Ringspalt 21 und einen daran anschließenden radialen Ringspalt getrennt ist. Die Ausgleichskammer 18 ist ferner durch in der Rückwand des Pumpenlaufrades 19 angeordnete Durchlaßöffnungen 20 mit der Niederdruckseite verbunden.Between the housing intermediate wall 5 and the back of the pump impeller 19 facing this, a compensation chamber 18 is provided which communicates on the one hand with the bearing gap 10 of the sliding bearing 9 close to the pump and on the other hand is separated from the high-pressure chamber 4 by an axial annular gap 21 and an adjoining radial annular gap. The compensation chamber 18 is also connected to the low-pressure side by through openings 20 arranged in the rear wall of the pump impeller 19.

Erfindungsgemäß ist ferner in der Gehäusezwischenwand 5 ein Einlaßkanal 22 vorgesehen, der bei der dargestellten Ausführungsform vom Spaltrohr-Innenraum 8 ausgeht und zur Ausgleichskammer 18 führt. Im Einlaßkanal 22 ist eine Durchfluß-Regelvorrichtung 23 vorgesehen, die bei der in Fig. 2 dargestellten Ausführungsform durch eine von außen zu betätigende Stellvorrichtung 25 verstellt werden kann, um die Durchflußmenge durch den Einlaßkanal 22 zu regulieren.According to the invention, an inlet channel 22 is also provided in the intermediate wall 5 of the housing, which in the illustrated embodiment starts from the canned interior 8 and leads to the compensation chamber 18. A flow control device 23 is provided in the inlet channel 22, which in the embodiment shown in FIG. 2 can be adjusted by an actuating device 25 to be actuated from the outside in order to regulate the flow rate through the inlet channel 22.

Bei der in Fig. 1 dargestellten Ausführungsform wird die Stellvorrichtung 25 durch die Signale einer die axiale Stellung der Rotorwelle 13 erfassenden Stellungs-Anzeigevorrichtung 24 betätigt, die auf einem aus dem Gehäuse 2 druckdicht herausragenden Rohr angeordnet ist, in welchem sich ein Fortsatz der Rotorwelle 13 axial verschieben kann.In the embodiment shown in FIG. 1, the actuating device 25 is actuated by the signals of a position indicator device 24 which detects the axial position of the rotor shaft 13 and which is arranged on a tube which projects from the housing 2 in a pressure-tight manner and in which there is an extension of the rotor shaft 13 can move axially.

Im Betrieb wird ein aus dem Hochdruckraum über den Teilstromkanal 16 abgezweigter Teilstrom in den Spaltrohr-Innenraum eingeführt. Der Teilatrom wird einerseits durch den Rotorspalt 15 und zu den Lagerspalten 10 und 12 der Gleitlager geleitet, um einerseits die dort erzeugte Wärme abzuführen und andererseits schmierend zu wirken. Der am pumpenfernen Ende der Rotorwelle 13 durch den Drosselspalt 28 und den Rückführkanal 17 abströmende Teilstrom erzeugt einen die Rotorwelle 13 in Richtung zum Niederdruckraum 3 beaufschlagenden Flüssigkeitsdruck. Die durch den Lagerspalt 10 des pumpennahen Gleitlagers 9 austretende Teilmenge des Förderguts gelangt in die Ausgleichskammer 18 und von dieser über die Durchlaßöffnungen 20 zurück ins Pumpenlaufrad 19. Daneben strömt aber ein über die Durchfluß-Regelvorrichtung 23 regulierbarer Teilstrom vom Spaltrohr-Innenraum 8 über den Einlaßkanal 22 zur Ausgleichskammer 18. Da der Strömungsquerschnitt des Einlaßkanals 22 größer ist, als der Strömungsquerschnitt des Lagerspalts 10 des pumpennahen Gleitlagers 9 und des Ringspalts 21, kann der Druck in der Ausgleichskammer 18 und damit die auf die in der Ausgleichskammer 18 liegenden Flächen des Pumpenlaufrades 19 ausgeübte Schubkraft durch Betätigung der Durchfluß-Regelvorrichtung 23 zweckentsprechend eingestellt werden, ohne daß dadurch die Größe des durch den Rotorepalt 15 fließenden Teilstromes wesentlich verändert wird. Wenn die Durchfluß-Regelvorrichtung 23 geschlossen ist, fließt der Ausgleichskammer 18 nur die durch den Lagerspalt 10 des pumpennahen Gleitlagers 9 und den Ringspalt 21 hindurchtretende Fördergutmenge zu. Wenn die Durchfluß-Regelvorrichtung 23 vollständig geöffnet ist, strömt der Ausgleichskammer 18 Fördergut zu entsprechend der Summe der Strömungsquerschnitte des Einlaßkanals 22, des Lagerspalts 10 des pumpennahen Gleitlagers 9 und des Ringspaltes 21. Durch entsprechende Betätigung der Durchfluß-Regelvorrichtung 23 kann der Druck in der Ausgleichskammer 18 innerhalb weiter Grenzen variiert werden, wodurch die axiale Stellung der Rotorwelle 13 jeweils in der gewünschten Weise verändert und den Betriebsbedingungen optimal angepaßt werden kann.In operation, a partial flow branched off from the high-pressure space via the partial flow channel 16 is introduced into the can interior. The partial atom is passed on the one hand through the rotor gap 15 and to the bearing gaps 10 and 12 of the slide bearings in order to dissipate the heat generated there on the one hand and to have a lubricating effect on the other. The partial flow flowing away from the pump at the end of the rotor shaft 13 through the throttle gap 28 and the return duct 17 generates a liquid pressure acting on the rotor shaft 13 in the direction of the low-pressure chamber 3. The part of the conveyed material emerging through the bearing gap 10 of the sliding bearing 9 near the pump reaches the equalizing chamber 18 and from there via the passage openings 20 back into the pump impeller 19. In addition, however, a partial flow which can be regulated via the flow control device 23 flows from the canned space interior 8 via the inlet channel 22 to the compensation chamber 18. Since the flow cross section of the inlet channel 22 is larger than the flow cross section of the bearing gap 10 of the slide bearing 9 near the pump and of the annular gap 21, the pressure in the compensation chamber 18 and thus on the surfaces of the pump impeller 19 lying in the compensation chamber 18 Exerted pushing force can be adjusted appropriately by actuating the flow control device 23 without the size of the partial flow flowing through the rotor gap 15 being significantly changed thereby. When the flow control device 23 is closed, the compensation chamber 18 only receives the quantity of conveyed material passing through the bearing gap 10 of the sliding bearing 9 near the pump and the annular gap 21. If the flow control device 23 is completely open, the compensation chamber 18 flows to conveyed goods according to the sum of the flow cross-sections of the inlet channel 22, the bearing gap 10 of the pump-bearing slide bearing 9 and the annular gap 21. By appropriate actuation of the flow control device 23, the pressure in the compensation chamber 18 can be varied within wide limits, whereby the axial position of the rotor shaft 13 can be changed in the desired manner and can be optimally adapted to the operating conditions.

Die vorstehend an Hand eines bevorzugten Ausführungsbeispiels erläuterte Kreiselpumpe kann vom Fachmann je nach den Anforderungen des Einzelfalles in verschiedener Weise zweckentsprechend abgewandelt werden, solange dabei die auch im Betrieb von außen regelbare Zuführung von Fördergut zu einer die axiale Stellung der Rotorwelle beeinflussenden Ausgleichskammer ohne wesentliche Veränderung des durch den Rotorspalt fließenden Teilstromes erzielt wird.The centrifugal pump explained above on the basis of a preferred exemplary embodiment can be modified appropriately by the person skilled in the art in various ways depending on the requirements of the individual case, as long as the supply of conveyed material, which can also be regulated externally during operation, to a compensating chamber influencing the axial position of the rotor shaft without a substantial change in the is achieved by the partial flow flowing through the rotor gap.

Claims (5)

1) Spaltrohrmotor-Kreiselpumpe mit Axialschubausgleich, mit einem das Spaltrohr aufnehmenden, mindestens ein Pumpenlaufrad umschließenden Gehäuse, einer darin in Gleitlagern drehbar und begrenzt axial verschiebbar gelagerten, den Rotor und ein oder mehrere Pumpenlaufräder tragenden Rotorwelle, mindestens einem im Gehäuse von der Hochdruckseite der Pumpe zum Spaltrohr-Innenraum führenden Teilstromkanal zum Hindurchleiten eines zur Wärmeabführung und Schmierung dienenden Fördergut-Teilstromes durch den Rotorspalt und zu den Gleitlagern, einer zwischen dem Pumpenlaufrad und einer Gehäusezwischenwand gebildeten, mit dem Lagerspalt des pumpennahen Gleitlagers und einem Ringspalt zwischen Pumpenlaufrad und Gehäusezwischenwand kommunizierenden Ausgleichskammer, in der dieser zugewandten Rückwand des Pumpenlaufrades angeordneten, dessen Niederdruckseite mit der Ausgleichskammer verbindenden Durchlaßöffnungen sowie ggf.den Durchflußquerschnitt für den Fördergut-Teilstrom bei Axialverschiebungen der Rotorwelle selbsttätig gegensteuernd verändernden Vorrichtungen, dadurch gekennzeichnet, daß: a) der Hoohdruckraum (4) mit der Ausgleichskammer (18) durch einen Einlaßkanal (22) mit relativ zum Lagerspalt (10) des pumpennahen Gleitlagers (9) und zum Ringspalt (21) zwischen dem Pumpenlaufrad (20) und der Gehäusezwischenwand (5) größerem Strömungsquerschnitt verbunden ist und b) der Einlaßkanal (22) eine auch im Betrieb verstellbare Durchfluß-Regelvorrichtung (23) zur Regelung des Druckes in der Ausgleichskammer (18) aufweist. 1) canned motor centrifugal pump with axial thrust compensation, with a casing that accommodates the canned pipe and encloses at least one pump impeller, a rotatable and axially displaceable rotor shaft that supports the rotor and one or more pump impellers, at least one in the housing from the high pressure side of the pump partial flow duct leading to the inner space of the canned pipe for passing a partial material flow for heat dissipation and lubrication through the rotor gap and to the slide bearings, a compensation chamber formed between the pump impeller and an intermediate wall of the housing and communicating with the bearing gap of the slide bearing near the pump and an annular gap between the pump impeller and intermediate wall of the housing, arranged in this rear wall of the pump impeller, the low-pressure side of which connects the compensation chamber to the through-openings and, if appropriate, the flow cross-section for the partial flow of material to be conveyed in the event of axial displacements the rotor shaft automatically countermeasures changing devices, characterized in that: a) the high pressure chamber (4) with the compensation chamber (18) through an inlet channel (22) with relative to the bearing gap (10) of the pump-close sliding bearing (9) and to the annular gap (21) between the pump impeller (20) and the intermediate wall (5) larger flow cross-section is connected and b) the inlet channel (22) has a flow control device (23), which is also adjustable during operation, for regulating the pressure in the compensation chamber (18). 2) Kreiselpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Ausgleichskammer (18) mit dem Hochdruckraum (4) über einen axialen Ringspalt (21) und mindestens einen an diesen anschließenden radialen Ringspalt kommuniziert.2) Centrifugal pump according to claim 1, characterized in that the compensation chamber (18) communicates with the high pressure chamber (4) via an axial annular gap (21) and at least one radial annular gap adjoining this. 3) Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Einlaßkanal (22) hochdruckseitig vom Teilstromkanal (16) oder dem Spaltrohr-Innenraum (8) abzweigt.3) Centrifugal pump according to claim 1 or 2, characterized in that the inlet duct (22) branches off from the partial flow duct ( 16 ) or the canned interior (8) on the high-pressure side. 4) Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Einlaßkanal (22) hochdruckseitig zwischen dem die Ausgleichskammer (18) vom Hochdruckraum (4) trennenden Ringspalt (21) und dem den Hochdruckraum (4) vom Niederdruckraum (3) trennenden Ringspalt (29) mündet.4) Centrifugal pump according to claim 1 or 2, characterized in that the inlet channel (22) on the high pressure side between the separating chamber (18) from the high pressure chamber (4) separating the annular gap (21) and the high pressure chamber (4) from the low pressure chamber (3) separating the annular gap (29) opens. 5) Kreiselpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß eine durch Signale einer die axiale Stellung der Rotorwelle (13) erfassenden Stellungs-Anzeigevorrichtung (24) betätigte Stellvorrichtung für die Durchfluß-Regelvorrichtung (23) vorgesehen ist.5) Centrifugal pump according to one of claims 1 to 4, characterized in that a position indicator device (24) actuated by signals of an axial position of the rotor shaft (13) detecting the setting device for the flow control device (23) is provided.
EP81109474A 1981-10-31 1981-10-31 Centrifugal pump with axial thrust compensation driven by an air-gap sleeve motor Withdrawn EP0078345A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP81109474A EP0078345A1 (en) 1981-10-31 1981-10-31 Centrifugal pump with axial thrust compensation driven by an air-gap sleeve motor

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Application Number Priority Date Filing Date Title
EP81109474A EP0078345A1 (en) 1981-10-31 1981-10-31 Centrifugal pump with axial thrust compensation driven by an air-gap sleeve motor

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2583466A1 (en) * 1985-06-14 1986-12-19 Licentia Gmbh Feed pump
WO2002012728A1 (en) * 2000-08-03 2002-02-14 Ksb Aktiengesellschaft Axial thrust compensation device
EP1378667A2 (en) * 2002-07-04 2004-01-07 HERMETIC-PUMPEN GmbH Pumping system
DE102006011613A1 (en) * 2006-03-14 2007-09-20 Ksb Aktiengesellschaft Centrifugal pump with axial thrust balancing device
US8337142B2 (en) 2006-08-30 2012-12-25 Schlumberger Technology Corporation System and method for reducing thrust acting on submersible pumping components
CN101761489B (en) * 2008-12-26 2013-01-23 张志勇 Submerged pump
EP3042440A1 (en) * 2013-09-03 2016-07-13 Nuovo Pignone S.r.l. Fan-cooled electrical machine with axial thrust compensation
CN111810411A (en) * 2020-08-10 2020-10-23 大连海密梯克泵业有限公司 Multistage shielding pump with balance disc structure
US10890189B2 (en) 2016-06-01 2021-01-12 Schlumberger Technology Corporation Submersible pumping system having thrust pad flow bypass
CN113137396A (en) * 2020-01-17 2021-07-20 格兰富控股联合股份公司 Pump bearing retainer
CN113757158A (en) * 2021-08-18 2021-12-07 合肥新沪屏蔽泵有限公司 Balance drum structure for multistage shield pump
CN114922825A (en) * 2022-06-15 2022-08-19 杭州大路实业有限公司 Centrifugal pump structure driven by disc type motor
CN115596684A (en) * 2022-12-01 2023-01-13 中国核动力研究设计院（Cn） Compressor, supercritical carbon dioxide circulation system and compressor pressure control method

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2583466A1 (en) * 1985-06-14 1986-12-19 Licentia Gmbh Feed pump
WO2002012728A1 (en) * 2000-08-03 2002-02-14 Ksb Aktiengesellschaft Axial thrust compensation device
EP1378667A2 (en) * 2002-07-04 2004-01-07 HERMETIC-PUMPEN GmbH Pumping system
DE10230025A1 (en) * 2002-07-04 2004-02-12 Hermetic-Pumpen Gmbh pumping
EP1378667A3 (en) * 2002-07-04 2005-01-12 HERMETIC-PUMPEN GmbH Pumping system
DE102006011613A1 (en) * 2006-03-14 2007-09-20 Ksb Aktiengesellschaft Centrifugal pump with axial thrust balancing device
US8337142B2 (en) 2006-08-30 2012-12-25 Schlumberger Technology Corporation System and method for reducing thrust acting on submersible pumping components
CN101761489B (en) * 2008-12-26 2013-01-23 张志勇 Submerged pump
EP3042440A1 (en) * 2013-09-03 2016-07-13 Nuovo Pignone S.r.l. Fan-cooled electrical machine with axial thrust compensation
EP3042440B1 (en) * 2013-09-03 2022-12-21 Nuovo Pignone Tecnologie - S.r.l. Fan-cooled electrical machine with axial thrust compensation
US10890189B2 (en) 2016-06-01 2021-01-12 Schlumberger Technology Corporation Submersible pumping system having thrust pad flow bypass
CN113137396A (en) * 2020-01-17 2021-07-20 格兰富控股联合股份公司 Pump bearing retainer
EP3851677A1 (en) * 2020-01-17 2021-07-21 Grundfos Holding A/S Pump bearing retainer
US20210222699A1 (en) * 2020-01-17 2021-07-22 Grundfos Holding A/S Pump bearing retainer
CN113137396B (en) * 2020-01-17 2023-06-06 格兰富控股联合股份公司 Pump bearing retainer
CN111810411A (en) * 2020-08-10 2020-10-23 大连海密梯克泵业有限公司 Multistage shielding pump with balance disc structure
CN113757158A (en) * 2021-08-18 2021-12-07 合肥新沪屏蔽泵有限公司 Balance drum structure for multistage shield pump
CN113757158B (en) * 2021-08-18 2023-12-05 合肥新沪屏蔽泵有限公司 Balance drum structure for multistage shielding pump
CN114922825A (en) * 2022-06-15 2022-08-19 杭州大路实业有限公司 Centrifugal pump structure driven by disc type motor
CN115596684A (en) * 2022-12-01 2023-01-13 中国核动力研究设计院（Cn） Compressor, supercritical carbon dioxide circulation system and compressor pressure control method

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