EP1378667A2 - Pumpstand - Google Patents
Pumpstand Download PDFInfo
- Publication number
- EP1378667A2 EP1378667A2 EP03010971A EP03010971A EP1378667A2 EP 1378667 A2 EP1378667 A2 EP 1378667A2 EP 03010971 A EP03010971 A EP 03010971A EP 03010971 A EP03010971 A EP 03010971A EP 1378667 A2 EP1378667 A2 EP 1378667A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pumping station
- station according
- drive shaft
- impeller
- 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- Withdrawn
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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
- 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 pumping station with a single or multi-stage centrifugal pump, at least one pump impeller overhung on a drive shaft of a pump drive is, a for axial thrust compensation on the drive shaft Compensating device is provided.
- the pump and the drive motor integrated into one unit.
- the pump part can both in single and multi-stage construction become.
- the impeller or the impellers are included arranged flying on a common drive shaft.
- Multi-stage pumps in particular, can sometimes be considerable Develop axial thrust forces using conventional thrust bearing collars can no longer be mastered.
- a canned motor pump has therefore already been created, those on the side facing away from the wheelset and located in the motor housing Shaft end of the drive shaft a relief device for axial thrust compensation.
- the relief device has a relief disk connected to the drive shaft in a rotationally fixed manner on. A radial front edge area of this relief disk forms a transverse to the longitudinal direction of the Drive shaft-oriented compensation channel, one of which is axial Oriented peripheral walls upstream limited throttle is.
- the pre-throttle forms a rigid liquid throttle
- Through the pre-throttle and the compensation channel becomes a liquid sub-flow of the pumped liquid from the pressure side to the suction side of this known centrifugal pump guided.
- Another partial flow of the flow is branched off as a cooling stream and on the inner peripheral wall of the Canned pot past through a longitudinal bore of the hollow drilled Drive shaft led back to the suction side of the pump.
- the inventive solution to this problem consists in the Pumping station of the type mentioned in particular in that the compensation device between the at least one pump impeller and the pump drive is arranged.
- the compensation device not on the side of the Pump drive arranged - rather the compensation device between the at least one pump impeller and the Pump drive placed.
- This arrangement of the compensation device can be long and especially external return lines be avoided for the relief current and a separate guidance of the relief flow from the engine cooling flow favored. Since the compensation device in particular in the Placed near the pump impellers and thus in the area in which the axial thrust mainly arises, becomes an independent design of pump and pump drive or even a modular structure of the invention Pump stand favors.
- Compensating device is arranged on the drive shaft and / or directly to the at least one impeller or the impeller set borders. It is useful if the compensation device in a separate from the pump drive or separable pump housing is arranged.
- a preferred embodiment according to the invention provides that the balancing device as a hydraulic relief device is designed and that the compensation device especially one depending on the axial wave position forms variable relief device.
- the compensation device can be designed expediently in this way be that this has an equalization channel, on the one hand from a radial surface one with the drive shaft in Wavelength direction immovably connected relief body and on the other hand bounded by a wall section fixed to the housing is and that through the equalization channel a particular Partial flow from the pressure side to the suction side of the pump of the flow is guided.
- a pre-throttle is connected upstream of the compensation channel.
- the pre-choke by a in the longitudinal direction of the Drive shaft oriented and flowed through by the partial flow Throttle channel is formed, and that the throttle channel is preferred on the one hand through the peripheral wall of the relief body and on the other hand by a the peripheral wall of the relief body encompassing wall section limited.
- a particularly compact and space-saving embodiment according to The invention provides that the relief body on the pressure side on the pump impeller of the last pump stage in the conveying direction the centrifugal pump is held.
- An external return line can be avoided, for example when the partial flow coming from the relief device via a return duct to the suction side of the centrifugal pump or one of their front, preferably in the conveying direction Pump stages is performed and if the return channel between the pump impeller hub of at least one pump stage and the drive shaft is provided.
- centrifugal pump is designed as a canned motor pump.
- Fig. 1 is a pumping station 1 with a canned motor centrifugal pump 2 shown, in particular as a liquid pump serves.
- the centrifugal pump 2 on the one hand and the pump drive 3 with the electric drive motor on the other hand integrated into one unit.
- the centrifugal pump 2, which is also designed in one stage can be multi-stage here and has one Impeller set with three pump impellers 4, 5, 6. These pump impellers 4, 5, 6 are adjacent to each other on a common one Drive shaft 7 overhung.
- centrifugal pump 2 and the pump drive 3 are in separate, Housing parts releasably connected together. there is the rotor 8 held in a rotationally fixed manner on the drive shaft 7 of the pump drive 2 encompassed by the outer stator 9 and hermetically sealed by a canned pot 10.
- a motor cooling flow is provided for cooling the pump drive 3, its flow guidance here by a dashed line Line M is indicated.
- This engine cooling flow M is called a partial flow of the flow from the pressure side of the pump impeller set from the inside of the canned pot 10 over to the shaft end facing away from the wheelset Drive shaft 7 guided to from there through the hollow drilled drive shaft 7 through to the suction side of the centrifugal pump 2 or to be redirected between two wheels.
- the canned motor pump 2 shown here has compensation of those generated in particular by the pump impellers 4, 5, 6 Axial thrust on a compensating device 11.
- This balancer 11 is between the pump impeller and the pump drive 3 in the detachably connected to the pump drive 3 Pump housing part arranged.
- the compensation device 11 is here as a hydraulic relief device designed by also one, here partial stream E des indicated by a dash-dotted line Flow from the suction side to the pressure side of the canned motor pump 2 is performed.
- the compensating device 11 has an annular circumference Relief body 12, which is approximately L-shaped in cross section is designed and an axial portion 13 and has a radial portion 14.
- This relief body 12 is on the back on the pressure side of the last one in the conveying direction Pump impeller 6 provided.
- the compensation device 11 has a radial here oriented compensation channel 15 on the one hand by a Radial surface 16 on the relief body 12 and on the other hand by a wall section 7 fixed to the housing is limited.
- This Compensation channel 15 forms a flexible throttle, one of the axial shaft position variable relief against the axial thrust causes.
- a rigid pre-throttle 18 is connected upstream of the equalization channel 15, which by a in the longitudinal direction of the shaft of the drive shaft 7 oriented throttle channel through which the partial flow E flows is formed.
- This throttle channel is an axial Circumferential wall 19 of the relief body 12 on the one hand and through a circumferential wall 19 of the relief body 12 Wall section 20 limited.
- the partial flow E coming from the compensating device 11 becomes through a return duct to the suction side of the centrifugal pump 2 or one of their pumping stages, which are preferably at the front in the conveying direction guided. While it can be seen in Fig. 1 that this Return channel between the pump impeller hub of the pump impellers 5, 6 and the drive shaft 7 is provided in FIG. 2 clearly shows that this is assigned to the partial stream E. Return channel through three, over the shaft circumference of the drive shaft 7 distributed longitudinal grooves 21 in the drive shaft 7 and / or in the impeller hubs of the pump impellers 4, 5, 6 can be formed. In Fig. 1 it can be seen that the Compensation device 11 behind the last in the conveying direction Pump impeller 6 is arranged.
- the one for axial thrust compensation required relief flow E is behind the flow branched off in the conveying direction last pump impeller 6, by the pre-throttle 18 the variable throttle gap of the compensation device 11 fed where one of the axial shaft position dependent tax gap is formed. From there the Relief current E via an inlet cross bore 22 in the return channel formed by the grooves 21 between Impeller hubs and drive shaft 7 and another Outlet transverse bore 23, for example, behind that in the conveying direction first, suction-side pump impeller 4 out.
- the for Return of the relief current E required return channel is by at least one, preferably several Longitudinal grooves 21 in the impeller hubs of the pump impellers 5, 6 formed, wherein the grooves 21 are arranged so that they in aligned in the axial direction. Through cross holes in the impeller hubs the return point can be anywhere between two pump impellers.
- the return channel formed by grooves 21 of the pump impellers for the relief current E is easy to manufacture and builds extremely compact. This makes it possible to have a compact space-saving compensation device 11 for a multi-stage To create canned motor pump.
- Return channel of the relief current 11 are omitted outer bypass lines and any necessary welded connections.
- Separate discharge current E and Motor cooling flow M has the advantage that both partial flows are decoupled are, i.e. do not influence each other. Moreover can the return of both partial streams at different points in the pump section if this is due to thermal reasons or due to the axial forces actually occurring should be. The latter is important for funding of boiling liquids, where with evaporation of the funding must be expected.
- the axial play of the drive shaft 7 in the direction of the centrifugal pump 2 is limited by the gap width "zero" on the Control gap of the relief device 11, - in the Centrifugal pump 2 opposite direction through the gap width "Zero" on the axial bearing band of the pump-side bearing.
- the axial shaft play of the drive shaft 7 can be very adjust exactly. In the event that the wave play through the Axial bearing collars on the pump or motor side Bearing is determined, this is only with larger tolerances possible because the tolerances of all seals and Components between the axial bearing on the pump and motor side on add up.
- the compensation device 11 in the pump part of the here shown Pumping station 1 is particularly compact Design. Since the led through the compensation device 11 Relief current E through a through longitudinal grooves 21 formed in the impeller hubs and by the drive shaft 7 limited return channel can be returned separately external bypass lines are dispensed with. The axial play the drive shaft 7 is independent of component and sealing tolerances. Since the motor cooling current M is independent of the relief current E is guided through the hollow drilled drive shaft 7, can the engine cooling regardless of the balancing device 11 can be designed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
- Fig. 1
- eine mehrstufige Spaltrohrmotorpumpe in einem Längsschnitt, und
- Fig. 2
- die Spaltrohrmotorpumpe aus Fig. 1 in einem TeilQuerschnitt durch ihre Antriebswelle im Bereich eines Pumpenlaufrades.
Claims (11)
- Pumpstand (1) mit einer ein- oder mehrstufigen Kreiselpumpe (2), deren zumindest eines Pumpenlaufrad (4, 5, 6) auf einer Antriebswelle (7) eines Pumpenantriebs (3) fliegend gelagert ist, wobei zum Axialschubausgleich an der Antriebswelle (7) eine Ausgleichsvorrichtung (11) vorgesehen ist, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) zwischen dem zumindest einen Pumpenlaufrad (6) und dem Pumpenantrieb (3) angeordnet ist.
- Pumpstand nach Anspruch 1, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) auf der Antriebswelle (7) angeordnet ist und/oder an das zumindest eine Laufrad (6) oder den Laufradsatz (4, 5, 6) unmittelbar angrenzt.
- Pumpstand nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) in einem vom Pumpenantrieb (3) getrennten oder trennbaren Pumpengehäuse angeordnet ist.
- Pumpstand nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) als hydraulische Entlastungsvorrichtung ausgestaltet ist.
- Pumpstand nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) eine in Abhängigkeit vom axialen Wellenstand variable Entlastungsvorrichtung bildet.
- Pumpstand nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Ausgleichsvorrichtung (11) einen quer zur Wellen-Längsachse orientierten Ausgleichskanal (15) hat, der einerseits von einer Radialfläche (16) eines mit der Antriebswelle (7) in Wellen-Längsrichtung unverrückbar verbundenen Entlastungskörpers (12) und andererseits von einem gehäusefesten Wandungsabschnitt (17) begrenzt ist und dass durch den Ausgleichskanal (15) ein insbesondere von der Druckseite zur Saugseite der Pumpe (2) geführter Teilstrom (E) des Förderstroms geführt ist.
- Pumpstand nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass dem Ausgleichskanal (15) eine Vordrossel vorgeschaltet ist.
- Pumpstand nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Vordrossel durch einen in Wellen-Längsrichtung der Antriebswelle (7) orientierten und vom Teilstrom (E) durchströmten Drosselkanal gebildet ist und dass der Drosselkanal vorzugsweise einerseits durch die Umfangswandung (19) des Entlastungskörpers (12) umgreifenden Wandungsabschnitt (20) begrenzt ist.
- Pumpstand nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Entlastungskörper (12) druckseitig an dem Pumpenlaufrad (6) der in Förderrichtung letzten Pumpstufe der Kreiselpumpe (2) gehalten ist.
- Pumpstand nach einem der Ansprüche 1 bis 9, dadurch kennzeichnet, dass der von der Ausgleichsvorrichtung (11) kommende Teilstrom (E) über einen Rückführungskanal zur Saugseite der Kreiselpumpe (2) oder einer ihrer in Förderrichtung vorzugsweise forderen Pumpstufen (4, 5) geführt ist und dass der Rückführungskanal zwischen der Pumpenlaufradnabe zumindest einer Pumpstufe (4, 5, 6) und der Antriebswelle (7) vorgesehen ist.
- Pumpstand nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die Kreiselpumpe (2) als Spaltrohrmotorpumpe ausgestaltet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10230025 | 2002-07-04 | ||
DE10230025A DE10230025A1 (de) | 2002-07-04 | 2002-07-04 | Pumpstand |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1378667A2 true EP1378667A2 (de) | 2004-01-07 |
EP1378667A3 EP1378667A3 (de) | 2005-01-12 |
Family
ID=29719456
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03010971A Withdrawn EP1378667A3 (de) | 2002-07-04 | 2003-05-16 | Pumpstand |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1378667A3 (de) |
DE (1) | DE10230025A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3936726A1 (de) * | 2020-07-07 | 2022-01-12 | Sulzer Management AG | Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102840142B (zh) * | 2012-09-26 | 2015-08-12 | 上海创科泵业制造有限公司 | 一种电机上置的多级屏蔽泵 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3031973A (en) * | 1959-11-30 | 1962-05-01 | Kramer Herman | Centrifugal pump with canned motor |
US3220350A (en) * | 1964-09-03 | 1965-11-30 | Crane Co | Motor driven pump |
EP0078345A1 (de) * | 1981-10-31 | 1983-05-11 | Bran & Lübbe GmbH | Spaltrohrmotor-Kreiselpumpe mit Axialschubausgleich |
DE3232473A1 (de) * | 1982-09-01 | 1984-03-01 | Reinecker Heyko Dipl Ing Fh | Kreiselpumpe mit spaltrohr-magnetkupplung |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4938641B1 (de) * | 1970-08-06 | 1974-10-19 | ||
DE3520360C2 (de) * | 1985-06-07 | 1994-03-31 | Hermetic Pumpen Gmbh | Pumpenaggregat mit einer mehrstufigen Pumpe |
-
2002
- 2002-07-04 DE DE10230025A patent/DE10230025A1/de not_active Withdrawn
-
2003
- 2003-05-16 EP EP03010971A patent/EP1378667A3/de not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3031973A (en) * | 1959-11-30 | 1962-05-01 | Kramer Herman | Centrifugal pump with canned motor |
US3220350A (en) * | 1964-09-03 | 1965-11-30 | Crane Co | Motor driven pump |
EP0078345A1 (de) * | 1981-10-31 | 1983-05-11 | Bran & Lübbe GmbH | Spaltrohrmotor-Kreiselpumpe mit Axialschubausgleich |
DE3232473A1 (de) * | 1982-09-01 | 1984-03-01 | Reinecker Heyko Dipl Ing Fh | Kreiselpumpe mit spaltrohr-magnetkupplung |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3936726A1 (de) * | 2020-07-07 | 2022-01-12 | Sulzer Management AG | Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens |
Also Published As
Publication number | Publication date |
---|---|
DE10230025A1 (de) | 2004-02-12 |
EP1378667A3 (de) | 2005-01-12 |
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RIC1 | Information provided on ipc code assigned before grant |
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18W | Application withdrawn |
Effective date: 20060118 |