EP3295034B1 - Centrifugal pump with sliding rotor - Google Patents
Centrifugal pump with sliding rotor Download PDFInfo
- Publication number
- EP3295034B1 EP3295034B1 EP16733866.4A EP16733866A EP3295034B1 EP 3295034 B1 EP3295034 B1 EP 3295034B1 EP 16733866 A EP16733866 A EP 16733866A EP 3295034 B1 EP3295034 B1 EP 3295034B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- main body
- centrifugal pump
- cover body
- blades
- 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.)
- Active
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 7
- 238000007789 sealing Methods 0.000 claims description 2
- 238000002485 combustion reaction Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 239000002826 coolant Substances 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 238000001816 cooling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
- F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
-
- 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
- F04D29/042—Axially shiftable rotors
Definitions
- the invention relates to a centrifugal pump, in particular a water pump, which is designed as a radial pump or a semi-axial pump, with an impeller rotatably arranged in a housing about an axis and connected to a drive shaft, which impeller has an impeller main body with impeller blades and an impeller cover disk, with the impeller outlet width being adjusted of the impeller, the main impeller body and the impeller cover body are axially displaceable relative to one another via an adjustment device, the main impeller body being arranged axially displaceably on the drive shaft or the impeller cover body, and the adjustment device being operatively connected to the main impeller body, the impeller cover body being groove-shaped on the front side facing the main impeller body Has pockets for receiving the impeller blades.
- Centrifugal pumps which can be regulated by adjusting the impeller outlet width are known.
- the regulation of the impeller outlet width has, in comparison with a throttle regulation via split ring slide, as it is for example from the EP 1 657 446 A2 is known, the advantage of lower losses and a higher degree of efficiency, since no energy is destroyed, but only the energy required in each case is transferred to the fluid.
- the impeller blades are connected to an impeller support disk on the drive and pressure side.
- the adjustment of the impeller outlet width between an idle position and a pumping position takes place by means of a suction-side control disk which has slots corresponding to the impeller blades and rotates with the impeller support disk.
- the U.S. 4,798,517 A discloses a pump with an impeller carrying impeller blades, the outlet width of which can be varied by a suction-side control disc, the control disc having slots corresponding to the impeller blades in order to be pushed over the impeller blades.
- a similar centrifugal pump with variable geometry is also from the U.S. 5,169,286 A or the U.S. 4,828,455 A known.
- the disadvantage is that relatively high flow losses occur in operating areas of the pump in which the unneeded impeller blade outlet width protrudes through the slots of the control disk into the water space, which worsens the efficiency of the pump in these operating areas.
- Another disadvantage is that this concept is only suitable for two-dimensional blade contours, but not for three-dimensional, i.e. spatially curved, impeller blade shapes, such as those from the AT 506 342 B1 , the DE 100 50 108 A or the JP S59-165895 A are known. With three-dimensionally curved impeller blades, the pump efficiency of centrifugal pumps can be significantly improved.
- the delivery rate change is carried out by an axially displaceable control disk arranged on the drive and pressure side.
- Conveyor blades are arranged on the drive shaft in an area facing away from the drive side and delimit pump conveying spaces with an axial conveying wall.
- the pump chambers are axially delimited on the side opposite the axial conveying wall by the end face of the control disk.
- the U.S. 6,074,167 A discloses a variable geometry centrifugal pump wherein the impeller has an inner disc and an outer ring between which two-dimensional, spiral-shaped impeller blades are arranged. Between the inner disk and the outer ring there is an axially displaceable control disk which has spiral-shaped slots for the impeller blades. By axially moving the control disk between the inner disk and the outer ring of the impeller by means of an actuator, the impeller blade length can be switched between short impeller blades for low delivery rates and long impeller blades for high delivery rates.
- the pamphlet DE 102 47 424 A1 describes a radial pump with a pump impeller, which can be moved axially out of the suction channel into a passive area by a thermocouple.
- the passive area is formed by a cover disk which is provided on the open flanks of the impeller blades and which seals the suction channel against the flow direction towards the housing.
- the impeller blades protrude through the cover disk, which leads to increased flow losses. Only a two-dimensional blade shape is possible.
- the DE 10 2014 217 489 A1 discloses a similar water pump with a radial impeller, which has an axially movable impeller part with rotor blades and an axially fixed impeller part.
- the axially fixed impeller part has openings whose shape corresponds to the rotor blades. The blades can thus be pushed into the openings to adjust the flow.
- only two-dimensional blades are possible.
- the DE 1 703 139 A shows a similar radial centrifugal pump.
- the DE 10 2011 005 476 A1 discloses a controllable cooling pump for the cooling circuit of an internal combustion engine with a blade wheel rotatably mounted about an axis of rotation, which has a pressure-side rear wall carrying blades, wherein the blades protrude into a blade space.
- the impeller has a cover part on the suction side and is connected to a driven hollow shaft, a push rod being guided in the hollow shaft in an axially displaceable manner.
- a guide body is arranged between the cover part and the paddle wheel and is connected to the push rod and can be axially displaced by means of this to regulate the coolant flow.
- the blades are three-dimensionally curved and the guide body can be rotated about the axis of rotation relative to the blade wheel. However, especially in the important suction area, no three-dimensional impeller blade geometry is possible. Comparatively high adjusting forces are necessary to adjust the guide body.
- the invention is therefore based on the object of ensuring active and reliable regulation with very low drive power over the entire speed and temperature range in centrifugal pumps - in particular with spatially curved impeller blade geometry.
- the three-dimensional curvature of the impeller blades within the diameter of the suction mouth enables the centrifugal pump to be particularly efficient.
- the main impeller body is to be understood here as that first part of the multi-part impeller which carries the impeller blades, that is to say to which the impeller blades are fixedly and immovably connected. That second part of the impeller which closes off the blade channels on the end face remote from the main impeller body is referred to here as the impeller cover body.
- the impeller cover body can deviate from a purely cylindrical disc shape.
- the front side of the impeller cover body facing the main impeller body can have a, for example, concavely curved surface which is designed in accordance with the optimal flow conditions in the blade channels.
- Operationally connected means that the adjustment device is physically connected to its function for adjusting the main impeller body with the main impeller body.
- this connection can be of a mechanical, hydraulic, pneumatic or electromagnetic type.
- the impeller cover body is preferably rigidly connected to the pump shaft, that is to say non-rotatably and non-displaceably.
- the impeller cover body is thus drive-connected to the drive shaft so that it cannot be displaced and rotated.
- the pockets on the rear side of the impeller cover body facing away from the main impeller body are closed.
- the depth of the pockets of the impeller cover body is dimensioned in such a way that the pockets can accommodate the impeller blades completely or predominantly - except for a defined minimum impeller outlet width when the main impeller body is axially displaced.
- the impeller cover body is arranged on the side of the main impeller body facing away from the suction side, and the main impeller body on the suction side - and not the impeller cover body - is adjusted, flow losses can be avoided. There are no axially protruding parts on the suction side, which could possibly have a negative effect on the efficiency.
- the impeller blades can dip into pockets of the impeller cover body.
- the pockets can also be three-dimensionally curved in accordance with the three-dimensional impeller blade shape.
- the main impeller body should be designed to be pivotable about the axis of rotation by at least a defined angular range relative to the impeller cover body in order to enable the impeller blades to be displaced into and out of the pockets.
- the angular range is defined by the pitch of the three-dimensionally curved impeller blades. In the event of an axial adjustment of the main impeller body, it is rotated in accordance with the pitch of the impeller blades relative to the angular position of the impeller cover body.
- the main impeller body Apart from this slight relative rotational movement when the main impeller body is displaced, the main impeller body is drive-connected to the impeller cover body and is therefore driven by the latter, that is to say rotated about the axis of rotation.
- This drive connection is most easily made directly through the form fit between the impeller blades and the pockets acting in the direction of rotation.
- the axial position of the main impeller body can be fixed by the adjusting device in every adjustment position.
- the main impeller body is arranged on the side of the impeller facing away from the drive side.
- the impeller cover body is advantageously arranged on the drive side of the impeller facing away from the suction mouth.
- the impeller main body is sealed on the side facing away from the impeller cover body from the housing via at least one labyrinth seal. It is particularly advantageous if a labyrinth seal is arranged between the main impeller body and the housing of the pump both in the area of the suction mouth of the impeller and near the exit from the impeller.
- the labyrinth seal consists in a known manner of intermeshing elements of the impeller main body and the housing, in the simplest case of an annular projection of one part which engages in a correspondingly shaped and dimensioned annular groove of the other part.
- the main body of the impeller can be adjusted in the most varied of ways, mechanically, electromagnetically, pneumatically, hydraulically or thermally.
- Mechanical adjustments can be implemented, for example, by screw gears or thrust gears.
- the adjusting device can have a threaded spindle that can be rotated via an actuator and a spindle nut, wherein the threaded spindle is rotatably mounted within the drive shaft designed as a hollow shaft and the spindle nut is in contact with the main impeller body, and the spindle nut and the Impeller main body in the axial direction immovable, preferably rotatable relative to one another, are connected to one another.
- the adjusting device can have a thrust gear with a push rod which can be displaced via an actuator and which is connected to a push sleeve, the push rod being mounted axially displaceably within the drive shaft designed as a hollow shaft and the push sleeve being connected to the main impeller body , and wherein the thrust sleeve and the impeller main body are connected to one another in an axially immovable manner, preferably rotatable relative to one another.
- the electromagnetic actuator has at least one electromagnet fixed to the housing and at least one, preferably ring-shaped permanent magnet, which is permanently connected to the main impeller body, the at least one permanent magnet preferably in the area of one of the main impeller body and the housing sealing labyrinth seal is arranged.
- FIGS. 1 to 7 each show a centrifugal pump 1 with a two-part housing 2 in which a multi-part impeller 3 is arranged.
- the impeller 3 consists of an impeller main body 4 and an impeller cover body 5, wherein a plurality of three-dimensionally curved impeller blades 6 are fixedly connected to the impeller main body 4, for example made in one piece with it.
- the impeller cover body 5 is non-rotatably and also non-displaceably connected to a drive shaft 7 which is rotatably supported around the axis 8 by means of shaft bearings 9 in the housing 2.
- the drive shaft is driven, for example, by means of a belt pulley 7a via a traction means (not shown).
- the main impeller body 4 is mounted on the impeller cover body 5 in an axially displaceable manner. A direct connection between the drive shaft 7 and the main impeller body 4 is not provided in the examples.
- the main impeller body 4 is arranged on the suction side 10 of the centrifugal pump 1 and forms the suction mouth 11.
- the impeller cover body 5 is arranged on the drive side 12 and has a front side 13 facing the impeller main body 4, which, together with the impeller blades 6 and the inner side 14 of the impeller main body 4, spans closed blade channels 15.
- the impeller cover body 5 has groove-like pockets 16 on the front side 13 which are shaped in accordance with the three-dimensional curvature of the impeller blades 6.
- the pockets 16 are designed to be closed towards the rear side 17 of the impeller cover body 5 facing away from the impeller main body 4 and are designed such that the impeller blades 6 can at least predominantly be pushed in.
- the impeller blades 6 and the pockets 16 form a form fit in the direction of rotation, so that the main impeller body 4 is driven by the impeller cover body 5 via this form fit, while the impeller cover body 5 is driven directly by the drive shaft 7.
- the housing 2 of the centrifugal pump forms an outlet spiral 2a.
- the impeller main body 4 on the suction side is mounted so as to be axially displaceable in the hub 5 a of the impeller cover body 5.
- the impeller blades 6 of the impeller main body 4 can dip into the pockets 16, whereby the impeller blade outlet width b can be adjusted between a minimum value and a maximum value by moving the impeller main body 4.
- a smooth sliding of the impeller main body 4 on the impeller cover body 5 can be achieved if the impeller material is modified with lubricants.
- the pockets 16 in the impeller deck 5 can be covered with a cover 5b forming the rear side 17 of the impeller cover body 5 in order to avoid pressure-side flow losses.
- labyrinth seals 20, 21 are arranged between the impeller main body 4 and the housing 2, with the in the FIGS. 1 to 3
- An inner first labyrinth seal 20 in the area of the suction mouth 11 and an outer second labyrinth seal 21 in the area of the outer diameter 4b of the main impeller body 4 facing the pressure side 18 is provided in the embodiment variants shown.
- the first and second labyrinth seals 20, 21 are combined and arranged directly adjacent.
- Each labyrinth seal 20, 21 consists of intermeshing elements 20a, 20b; 21a, 21b of the impeller main body 4 and the housing 2, for example from an annular projection 20a, 21a of one part, for example of the impeller main body 4, which engages in a corresponding annular groove 20b, 21b of the other part, for example of the housing 2.
- the cylindrical projections 20a, 21a together with the corresponding annular grooves 20b, 21b of the housing 2 form the labyrinth seals 20, 21.
- the impeller main body 4 is adjusted via an adjusting device 22 in the axial direction along the axis 8 of the drive shaft 7 - in the case of the FIGS. 1 to 5 Variants shown against the force of a return force formed by a return spring 23 - shifted.
- the adjustment of the main impeller body 4 can take place in the most varied of ways mechanically, electromagnetically, pneumatically, hydraulically or thermally.
- Fig. 1 and Fig. 2 is a mechanical adjustment
- Fig. 3 an electromagnetic adjustment is provided.
- Fig. 1 shows a first embodiment of the invention, wherein the adjusting device 22 has a helical gear 24 with a threaded spindle 26 rotatable via an actuator 25 and a spindle nut 27, the threaded spindle 26 and the spindle nut 27 being designed as a high-helix thread drive.
- the threaded spindle 26 is rotatably supported within the drive shaft 7, which is designed as a hollow shaft, via slide bearings 19 and is axially secured.
- a seal 19a is arranged between the threaded spindle 26 and the drive shaft 7.
- the spindle nut 27 is connected to the impeller main body 4, the spindle nut 27 and the impeller main body 4 being connected to one another so as to be immovable in the axial direction and rotatable relative to one another.
- the threaded spindle 26 can be rotated clockwise or counterclockwise via the actuator 25.
- the spindle nut 27 In uncontrolled operation, for example in the event of failure of the actuator 25, the spindle nut 27 is moved by the return spring 23, which is mounted in the impeller cover body 5 and designed as a compression spring, the hub 4a of the impeller main body 4 and an axial bearing 28 against a stop 29 on the threaded spindle 26, whereby failsafe sets the maximum impeller blade outlet width b max .
- the spindle nut 27 is moved, depending on the required function, via the actuator 25 and the threaded spindle 26 against the axial bearing 28, the hub 4a of the main impeller body 4 and the return spring 23, thus setting the desired impeller blade outlet width b.
- the actuator 25 can be formed, for example, by a stepping motor 30 and a spur gear drive 31.
- Fig. 2 shows a second embodiment variant according to the invention, wherein the adjusting device 22 has a thrust gear 32 with a push rod 33 and a push sleeve 34.
- the push rod 33 is slidably mounted in the hollow drive shaft 7 by means of slide bearings 19 and is sealed by at least one seal 19a.
- the push rod 33 protrudes centrally through the bearing 35 of the actuator 25, a stop 29, which can be secured against rotation, being firmly connected to the push rod 33 at the first end 33a of the push rod 33.
- the push rod 33 can be moved via the actuator 25 in the direction of the pulley 7a.
- the push sleeve 34 is firmly connected to the push rod 33.
- the push rod 33 In uncontrolled operation, for example if the actuator 25 fails, the push rod 33 is moved in the direction of the suction side by the return spring 23 mounted in the impeller cover body 5, the hub 4a of the main impeller body 4 and the axial bearing 28 until the stop 29 on the bearing 35 of the actuator 25 pending, whereby the maximum impeller blade outlet width b max is set in a fail-safe manner.
- the push rod 33 depending on the required function, is moved via the actuator 25 in the direction of the pulley 7a and thus deflected via the push sleeve 34, the axial bearing 28 and the hub 4a of the impeller main body 4 against the return spring 23, which is designed as a compression spring, and thus the desired impeller blade outlet width b set.
- the actuator 25 can for example be a pneumatic, hydraulic or electrical lifting element.
- Fig. 3 shows a third embodiment variant according to the invention, the adjusting device 22 having an electromagnetic actuator 25.
- the adjustment device 22 has at least one permanent magnet 36 firmly connected to the main impeller body 4 and an electromagnet 37 firmly connected to the housing 2.
- the permanent magnets 36 and corresponding electromagnets 37 can be in the area of the outer labyrinth seal 21 be arranged.
- the main impeller body 4 In uncontrolled operation, for example if the actuator 25 fails, the main impeller body 4 is moved in the direction of the suction side 10 by the return spring 23 mounted in the impeller cover body 5, for example designed as a compression spring, and the hub 4a of the main impeller body 4 until the hub 4a of the main impeller body 4 is moved
- the stop 29 arranged on the drive shaft 7 is present, the maximum impeller blade outlet width b max being set fail-safe.
- the impeller main body 4 is moved against the return spring 23 in the direction of the drive side 12 by a corresponding energization of the electromagnet 37, thus setting the desired impeller blade outlet width b.
- the fourth embodiment variant shown has the adjusting device 22 as in FIG Fig. 1 a helical gear 24 with a threaded spindle 26, which can be rotated via an actuator 25, and a spindle nut 27.
- the threaded spindle 26 is rotatably supported within the drive shaft 7, which is designed as a hollow shaft, via slide bearings 19 and is axially secured.
- a seal 19a is arranged between the threaded spindle 26 and the drive shaft 7.
- the spindle nut 27 is connected to the impeller main body 4, the spindle nut 27 and the impeller main body 4 being connected to one another so as to be immovable in the axial direction and rotatable relative to one another.
- the threaded spindle 26 can be rotated clockwise or counterclockwise via the actuator 25.
- the spindle nut 27 In uncontrolled operation, for example in the event of failure of the actuator 25, the spindle nut 27 is moved by the return spring 23, which is mounted in the impeller cover body 5 and designed as a compression spring, into the position shown in FIG Fig. 4 End position shown with maximum impeller blade outlet width b max moved.
- the spindle nut 27 is moved against the return spring 23 via the actuator 25 and the threaded spindle 26, depending on the required function, and the desired impeller blade outlet width b is thus set.
- the actuator 25 can be formed, for example, by a stepping motor 30 and a spur gear drive 31.
- FIGS. 6 and 7 show a fifth embodiment variant according to the invention, the adjusting device 22 having a push gear 38 with a push rod 33 and a push sleeve 34.
- the push rod 33 is slidably mounted in the hollow drive shaft 7 by means of slide bearings 19 and is sealed by at least one seal 19a.
- the push rod 33 is connected at a first end 33a via a linkage 38 to the actuator 25 and can be moved via this in the direction of the belt pulley 7a.
- the push sleeve 34 is firmly connected to the push rod 33.
- the push rod 33 is moved, depending on the required function, via the actuator 25 in the direction of the belt pulley 7a and thus deflected via the thrust sleeve 34, the axial bearing 28 and the hub 4a of the impeller main body 4 and thus the desired impeller blade outlet width b is set.
- the actuator 25 can for example be a pneumatic, hydraulic or electrical lifting element.
- FIG. 13 shows an impeller main body 4 of the impeller 3 of FIGS FIGS. 6 and 7
- the centrifugal pump shown here 1 The main impeller body 4 contains a plurality of three-dimensionally curved impeller blades 6, wherein in the exemplary embodiment each rotor blade 6 has a first section 6a and a second section 6b essentially axially adjoining it.
- the first section 6a is essentially two-dimensional, that is to say in a normal plane ⁇ on the axis 8 of the drive shaft 7 or push rod 33, curved and designed such that it can dip into the groove-shaped pockets 16 of the impeller cover body 5.
- the impeller blades 6 are curved three-dimensionally. This second section 6b also remains in FIG Fig. 7 second end position shown outside the pockets 16.
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Description
Die Erfindung betrifft eine Kreiselpumpe, insbesondere Wasserpumpe, welche als Radialpumpe oder Halbaxialpumpe ausgebildet ist, mit einem in einem Gehäuse um eine Achse drehbar angeordneten und mit einer Antriebswelle verbundenen Laufrad, welches Laufrad einen Laufradschaufeln aufweisenden Laufradhauptkörper und eine Laufraddeckscheibe aufweist, wobei zur Verstellung der Laufradaustrittsbreite des Laufrades der Laufradhauptkörper und der Laufraddeckkörper relativ zueinander über eine Verstelleinrichtung axial verschiebbar sind, wobei der Laufradhauptkörper axial verschiebbar auf der Antriebswelle oder dem Laufraddeckkörper angeordnet ist, und wobei die Verstelleinrichtung mit dem Laufradhauptkörper wirkverbunden ist, wobei der Laufraddeckkörper auf der dem Laufradhauptkörper zugewandten Frontseite nutförmige Taschen zur Aufnahme der Laufradschaufeln aufweist.The invention relates to a centrifugal pump, in particular a water pump, which is designed as a radial pump or a semi-axial pump, with an impeller rotatably arranged in a housing about an axis and connected to a drive shaft, which impeller has an impeller main body with impeller blades and an impeller cover disk, with the impeller outlet width being adjusted of the impeller, the main impeller body and the impeller cover body are axially displaceable relative to one another via an adjustment device, the main impeller body being arranged axially displaceably on the drive shaft or the impeller cover body, and the adjustment device being operatively connected to the main impeller body, the impeller cover body being groove-shaped on the front side facing the main impeller body Has pockets for receiving the impeller blades.
Insbesondere bei als Kühlmittelpumpen von Brennkraftmaschinen zum Antrieb von Fahrzeugen ergibt sich die Forderung nach geringem minimalen Kühlmittelstrom in der Warmlaufphase der Brennkraftmaschine und einer bedarfsgerechten Regelung entsprechend dem Betrieb der Brennkraftmaschine.In particular, when used as coolant pumps for internal combustion engines to drive vehicles, there is a requirement for a low minimum coolant flow in the warm-up phase of the internal combustion engine and demand-based regulation corresponding to the operation of the internal combustion engine.
Kreiselpumpen, welche durch Laufradaustrittsbreitenverstellung geregelt werden können, sind bekannt. Die Regelung der Laufradaustrittsbreite hat im Vergleich mit einer Drosselregelung über Spaltringschieber, wie sie beispielsweise aus der
Bei der
Die
Nachteilig ist, dass in Betriebsbereichen der Pumpe, bei denen die nicht benötigte Laufradschaufelaustrittsbreite durch die Schlitze der Steuerscheibe hindurch in den Wasserraum ragt, relativ hohe Strömungsverluste entstehen, wodurch der Wirkungsgrad der Pumpe in diesen Betriebsbereichen verschlechtert wird. Ein weiterer Nachteil ist, dass dieses Konzept sich nur für zweidimensionale Schaufelkonturen, aber nicht für dreidimensional, also räumlich gekrümmte Laufradschaufelformen, wie sie beispielsweise aus der
Eine weitere Zentrifugalpumpe mit variabler Geometrie, wobei die Laufradschaufelaustrittsbreite durch eine Steuerscheibe verändert wird, welche über die Laufradschaufeln des axial unverschiebbaren Laufrades geschoben wird, ist aus der
Bei der in der
Die
Die Druckschrift
Die
Die
Aus der
Ferner ist aus der
Der Erfindung liegt somit die Aufgabe zugrunde, bei Kreiselpumpen - insbesondere mit räumlich gekrümmter Laufradschaufelgeometrie - über den gesamten Drehzahl- und Temperaturbereich eine aktive und zuverlässige Regelung mit sehr geringer Antriebsleistung zu gewährleisten.The invention is therefore based on the object of ensuring active and reliable regulation with very low drive power over the entire speed and temperature range in centrifugal pumps - in particular with spatially curved impeller blade geometry.
Erfindungsgemäß erfolgt dies dadurch, dass die Laufradschaufeln - zumindest im Bereich des Saugmundes - dreidimensional gekrümmt sind.According to the invention, this takes place in that the impeller blades - at least in the area of the suction mouth - are three-dimensionally curved.
Die dreidimensionale Krümmung der Laufradschaufeln innerhalb des Durchmessers des Saugmundes ermöglicht besonders gute Wirkungsgrade der Kreiselpumpe.The three-dimensional curvature of the impeller blades within the diameter of the suction mouth enables the centrifugal pump to be particularly efficient.
Unter Laufradhauptkörper ist hier jener erste Teil des mehrteiligen Laufrades zu verstehen, welcher die Laufradschaufeln trägt, also mit welchem die Laufradschaufeln fest und unbeweglich verbunden sind. Jener zweite Teil des Laufrades, welcher die Schaufelkanäle an der dem Laufradhauptkörper abgewandten Stirnseite abschließt, wird hier als Laufraddeckkörper bezeichnet. Der Laufraddecckörper kann dabei von einer rein zylindrischen Scheibenform abweichen. Insbesondere kann die dem Laufradhauptkörper zugewandte Frontseite der des Laufraddeckkörpers eine beispielsweise konkav gekrümmte Fläche aufweisen, welche entsprechend den optimalen Strömungsbedingungen in den Schaufelkanälen gestaltet ist.The main impeller body is to be understood here as that first part of the multi-part impeller which carries the impeller blades, that is to say to which the impeller blades are fixedly and immovably connected. That second part of the impeller which closes off the blade channels on the end face remote from the main impeller body is referred to here as the impeller cover body. The impeller cover body can deviate from a purely cylindrical disc shape. In particular, the front side of the impeller cover body facing the main impeller body can have a, for example, concavely curved surface which is designed in accordance with the optimal flow conditions in the blade channels.
Wirkverbunden heißt, dass die Verstelleinrichtung physikalisch ihrer Funktion zur Verstellung des Laufradhauptkörpers mit dem Laufradhauptkörper in Verbindung steht. Je nach Ausbildung der Verstelleinrichtung kann diese Verbindung mechanischer, hydraulischer, pneumatischer oder elektromagnetischer Art sein.Operationally connected means that the adjustment device is physically connected to its function for adjusting the main impeller body with the main impeller body. Depending on the design of the adjusting device, this connection can be of a mechanical, hydraulic, pneumatic or electromagnetic type.
Durch die erfindungsgemäße Ausbildung des Laufrades ergibt sich zu Folge der Druckverteilung am Laufrad ein signifikant geringerer Achsschub im Vergleich zu herkömmlichen Laufradbauformen und damit geringere Verstellkräfte. Vorzugsweise ist der Laufraddeckkörper starr, also drehfest und verschiebefest, mit der Pumpenwelle verbunden. Der Laufraddeckkörper ist somit unverschiebbar und unverdrehbar mit der Antriebswelle antriebsverbunden.Due to the design of the impeller according to the invention, the pressure distribution on the impeller results in a significantly lower axial thrust compared to conventional impeller designs and thus lower adjustment forces. The impeller cover body is preferably rigidly connected to the pump shaft, that is to say non-rotatably and non-displaceably. The impeller cover body is thus drive-connected to the drive shaft so that it cannot be displaced and rotated.
Besonders vorteilhaft ist es, wenn die Taschen auf der dem Laufradhauptkörper abgewandten Rückseite des Laufraddeckkörpers geschlossen sind. Die Tiefe der Taschen des Laufraddeckkörpers ist dabei so dimensioniert, dass die Taschen bei axialer Verschiebung des Laufradhauptkörpers die Laufradschaufeln vollständig oder - bis auf eine definierte minimale Laufradaustrittsbreite - überwiegend aufnehmen können.It is particularly advantageous if the pockets on the rear side of the impeller cover body facing away from the main impeller body are closed. The depth of the pockets of the impeller cover body is dimensioned in such a way that the pockets can accommodate the impeller blades completely or predominantly - except for a defined minimum impeller outlet width when the main impeller body is axially displaced.
Dadurch, dass der Laufraddeckkörper auf der der Saugseite abgewandten Seite des Laufradhauptkörpers angeordnet ist, und der saugseitige Laufradhauptkörper - und nicht der Laufraddeckkörper - verstellt wird, können Strömungsverluste vermieden werden. Saugseitig gibt es keine axial vorspringenden Teile, welche sich eventuell nachteilig auf den Wirkungsgrad auswirken könnten. Die Laufradschaufeln können in Taschen des Laufraddeckkörpers eintauchen.Because the impeller cover body is arranged on the side of the main impeller body facing away from the suction side, and the main impeller body on the suction side - and not the impeller cover body - is adjusted, flow losses can be avoided. There are no axially protruding parts on the suction side, which could possibly have a negative effect on the efficiency. The impeller blades can dip into pockets of the impeller cover body.
Geht die räumliche Krümmung der Laufradschaufeln über den Durchmesser des Saugmundes hinaus, so können auch die Taschen entsprechend der dreidimensionalen Laufradschaufelform dreidimensional gekrümmt sein. In diesem Falle sollte der Laufradhauptkörper relativ zum Laufraddeckkörper um die Drehachse um zumindest einen definierten Winkelbereich schwenkbar ausgebildet sein, um ein Verschieben der Laufradschaufeln in die und aus den Taschen zu ermöglichen. Dabei wird der Winkelbereich durch die Steigung der dreidimensional gekrümmten Laufradschaufeln definiert. Bei einer axialen Verstellung des Laufradhauptkörpers wird dieser also entsprechend der Steigung der Laufradschaufeln relativ zum Winkellage des Laufraddeckkörpers verdreht.If the spatial curvature of the impeller blades goes beyond the diameter of the suction mouth, then the pockets can also be three-dimensionally curved in accordance with the three-dimensional impeller blade shape. In this case, the main impeller body should be designed to be pivotable about the axis of rotation by at least a defined angular range relative to the impeller cover body in order to enable the impeller blades to be displaced into and out of the pockets. The angular range is defined by the pitch of the three-dimensionally curved impeller blades. In the event of an axial adjustment of the main impeller body, it is rotated in accordance with the pitch of the impeller blades relative to the angular position of the impeller cover body.
Abgesehen von dieser geringfügigen Relativverdrehbewegung bei Verschiebung des Laufradhauptkörpers ist der Laufradhauptkörper mit dem Laufraddeckkörper antriebsverbunden und wird also von diesem angetrieben, also um die Drehachse gedreht. Diese Antriebsverbindung erfolgt am einfachsten direkt durch den in Drehrichtung wirkenden Formschluss zwischen den Laufradschaufeln und den Taschen. Um ein selbständiges Verstellen der Laufradaustrittsbreite zu Folge der Drehbewegung des Laufrades zu vermeiden, ist es günstig, wenn die axiale Position des Laufradhauptkörpers durch die Verstelleinrichtung in jeder Verstelllage fixierbar ist.Apart from this slight relative rotational movement when the main impeller body is displaced, the main impeller body is drive-connected to the impeller cover body and is therefore driven by the latter, that is to say rotated about the axis of rotation. This drive connection is most easily made directly through the form fit between the impeller blades and the pockets acting in the direction of rotation. In order to avoid an independent adjustment of the impeller outlet width as a result of the rotational movement of the impeller, it is advantageous if the axial position of the main impeller body can be fixed by the adjusting device in every adjustment position.
Besonders geringe Verstellkräfte für die Laufradaustrittsbreitenverstellung werden benötigt, wenn der axial verschiebbare Laufradhauptkörper den Saugmund der Kreiselpumpe ausbildet. Insbesondere bei dreidimensional gekrümmten Laufradschaufeln mit geschlossenen Schaufelkanälen haben Berechnungen und Versuche ergeben, dass die Laufradaustrittsbreitenverstellung durch Verschiebung des Laufradhauptkörpers besondere Vorteile im Vergleich zu einer aus dem Stand der Technik bekannten Verschiebung einer Steuerscheibe bringt, da wesentlich geringere Verstellkräfte nötig sind. Der Grund dafür ist, dass sich die beidseits auf den Laufradhauptkörper wirkenden Druckkräfte bei saugseitiger Anordnung des Laufradhauptkörpers zumindest annähernd aufheben, sodass die auf den Laufradhauptkörper wirkende resultierende Axialkraft sehr klein oder sogar annähernd Null ist.Particularly low adjustment forces for the impeller outlet width adjustment are required if the axially displaceable main impeller body has the suction mouth the centrifugal pump forms. In the case of three-dimensionally curved impeller blades with closed blade channels in particular, calculations and tests have shown that adjusting the impeller outlet width by shifting the main impeller body has particular advantages compared to shifting a control disk known from the prior art, since significantly lower adjustment forces are required. The reason for this is that the pressure forces acting on both sides of the main impeller body at least approximately cancel each other out when the main impeller body is arranged on the suction side, so that the resulting axial force acting on the main impeller body is very small or even approximately zero.
In einer bevorzugten Ausführungsform ist vorgesehen, dass der Laufradhauptkörper auf der der Antriebsseite abgewandten Seite des Laufrades angeordnet ist. Der Laufraddeckkörper ist dabei günstigerweise auf der dem Saugmund abgewandten Antriebsseite des Laufrades angeordnet.In a preferred embodiment it is provided that the main impeller body is arranged on the side of the impeller facing away from the drive side. The impeller cover body is advantageously arranged on the drive side of the impeller facing away from the suction mouth.
Um in jeder Verschiebestellung des Laufradhauptkörpers druck- und Strömungsverluste so klein wie möglich zu halten, ist es besonders vorteilhaft, wenn der Laufradhauptkörper auf der dem Laufraddeckkörper abgewandten Seite gegenüber dem Gehäuse über zumindest eine Labyrinthdichtung abgedichtet ist. Besonders vorteilhaft ist es dabei, wenn sowohl im Bereich des Saugmundes des Laufrades, als auch nahe dem Austritt aus dem Laufrad jeweils eine Labyrinthdichtung zwischen dem Laufradhauptkörper und dem Gehäuse der Pumpe angeordnet ist. Die Labyrinthdichtung besteht in bekannter Weise aus sich verkämmenden Elementen des Laufradhauptkörpers und des Gehäuses, im einfachsten Fall aus einem ringförmigen Vorsprung des einen Teils, der in eine entsprechende geformte und dimensionierte Ringnut des anderen Teils eingreift.In order to keep pressure and flow losses as small as possible in every shifting position of the impeller main body, it is particularly advantageous if the impeller main body is sealed on the side facing away from the impeller cover body from the housing via at least one labyrinth seal. It is particularly advantageous if a labyrinth seal is arranged between the main impeller body and the housing of the pump both in the area of the suction mouth of the impeller and near the exit from the impeller. The labyrinth seal consists in a known manner of intermeshing elements of the impeller main body and the housing, in the simplest case of an annular projection of one part which engages in a correspondingly shaped and dimensioned annular groove of the other part.
Die Verstellung des Laufradhauptkörpers kann auf verschiedenste Weise mechanisch, elektromagnetisch, pneumatisch, hydraulisch oder thermisch erfolgen.The main body of the impeller can be adjusted in the most varied of ways, mechanically, electromagnetically, pneumatically, hydraulically or thermally.
Mechanische Verstellungen können beispielsweise durch Schraubgetriebe oder Schubgetriebe realisiert werden.Mechanical adjustments can be implemented, for example, by screw gears or thrust gears.
Bei einer ersten erfindungsgemäßen Ausführungsvariante mit einem Schraubgetriebe kann die Verstelleinrichtung eine über einen Aktuator verdrehbare Gewindespindel und eine Spindelmutter aufweisen, wobei die Gewindespindel innerhalb der als Hohlwelle ausgebildeten Antriebswelle drehbar gelagert ist und die Spindelmutter mit dem Laufradhauptkörper in Kontakt steht, und wobei die Spindelmutter und der Laufradhauptkörper in axialer Richtung unverschiebbar, vorzugsweise relativ zueinander drehbar, miteinander verbunden sind.In a first embodiment variant according to the invention with a helical gear, the adjusting device can have a threaded spindle that can be rotated via an actuator and a spindle nut, wherein the threaded spindle is rotatably mounted within the drive shaft designed as a hollow shaft and the spindle nut is in contact with the main impeller body, and the spindle nut and the Impeller main body in the axial direction immovable, preferably rotatable relative to one another, are connected to one another.
Bei einer zweiten erfindungsgemäßen Ausführungsvariante mit einem Schubgetriebe kann die Verstelleinrichtung ein Schubgetriebe mit einer über einen Aktuator verschiebbaren Schubstange aufweisen, welche mit einer Schubmuffe verbunden ist, wobei die Schubstange innerhalb der als Hohlwelle ausgebildeten Antriebswelle axial verschiebbar gelagert ist und die Schubmuffe mit dem Laufradhauptkörper verbunden ist, und wobei die Schubmuffe und der Laufradhauptkörper in axialer Richtung unverschiebbar, vorzugsweise relativ zueinander drehbar, miteinander verbunden sind.In a second embodiment variant according to the invention with a thrust gear, the adjusting device can have a thrust gear with a push rod which can be displaced via an actuator and which is connected to a push sleeve, the push rod being mounted axially displaceably within the drive shaft designed as a hollow shaft and the push sleeve being connected to the main impeller body , and wherein the thrust sleeve and the impeller main body are connected to one another in an axially immovable manner, preferably rotatable relative to one another.
In einer dritten erfindungsgemäßen Ausführungsvariante mit einem elektromagnetischen Aktuator ist vorgesehen, dass der elektromagnetische Aktuator zumindest einen gehäusefesten Elektromagneten und zumindest einen vorzugsweise ringförmigen Permanentmagneten aufweist, welcher fest mit dem Laufradhauptkörper verbunden ist, wobei vorzugsweise der zumindest einen Permanentmagneten im Bereich einer den Laufradhauptkörper und das Gehäuse abdichtenden Labyrinthdichtung angeordnet ist.In a third embodiment variant according to the invention with an electromagnetic actuator it is provided that the electromagnetic actuator has at least one electromagnet fixed to the housing and at least one, preferably ring-shaped permanent magnet, which is permanently connected to the main impeller body, the at least one permanent magnet preferably in the area of one of the main impeller body and the housing sealing labyrinth seal is arranged.
Die Erfindung wird im Folgenden anhand der nichteinschränkenden Ausführungsbeispiele näher erläutert. Es zeigen:
- Fig. 1
- eine erfindungsgemäße Kreiselpumpe in einer ersten Ausführungsvariante in einem Längsschnitt;
- Fig. 2
- eine erfindungsgemäße Kreiselpumpe in einer zweiten Ausführungsvariante in einem Längsschnitt;
- Fig. 3
- eine erfindungsgemäße Kreiselpumpe in einer dritten Ausführungsvariante in einem Längsschnitt;
- Fig. 4
- eine erfindungsgemäße Kreiselpumpe in einer vierten Ausführungsvariante in einem Längsschnitt in einer ersten Endstellung;
- Fig. 5
- diese Kreiselpumpe in einer zweiten Endstellung in einem Längsschnitt;
- Fig. 6
- eine erfindungsgemäße Kreiselpumpe in einer fünften Ausführungsvariante in einem Längsschnitt in einer ersten Endstellung;
- Fig. 7
- diese Kreiselpumpe in einer zweiten Endstellung in einem Längsschnitt; und
- Fig. 8
- ein Laufrad der in
Fig. 6 und Fig. 7 dargestellten Kreiselpumpe in einer Schrägansicht.
- Fig. 1
- a centrifugal pump according to the invention in a first embodiment variant in a longitudinal section;
- Fig. 2
- a centrifugal pump according to the invention in a second variant in a longitudinal section;
- Fig. 3
- a centrifugal pump according to the invention in a third variant in a longitudinal section;
- Fig. 4
- a centrifugal pump according to the invention in a fourth variant in a longitudinal section in a first end position;
- Fig. 5
- this centrifugal pump in a second end position in a longitudinal section;
- Fig. 6
- a centrifugal pump according to the invention in a fifth variant in a longitudinal section in a first end position;
- Fig. 7
- this centrifugal pump in a second end position in a longitudinal section; and
- Fig. 8
- an impeller of the in
FIGS. 6 and 7 centrifugal pump shown in an oblique view.
Funktionsgleiche Teile sind in den Ausführungsbeispielen mit gleichen Bezugszeichen versehen.Parts with the same function are provided with the same reference symbols in the exemplary embodiments.
Die
Der Laufradhauptkörper 4 ist jeweils axial verschiebbar am Laufraddeckkörper 5 gelagert. Eine direkte Verbindung zwischen der Antriebswelle 7 und Laufradhauptkörper 4 ist in den Beispielen nicht vorgesehen. Der Laufradhauptkörper4 ist auf der Saugseite 10 der Kreiselpumpe 1 angeordnet und bildet den Saugmund 11 aus. Der Laufraddeckkörper 5 ist auf der Antriebsseite 12 angeordnet und weist eine dem Laufradhauptkörper 4 zugewandte Frontseite 13 auf, welche zusammen mit den Laufradschaufeln 6 und der Innenseite 14 des Laufradhauptkörpers 4 geschlossene Schaufelkanäle 15 aufspannt. Der Laufraddeckkörper 5 weist auf der Frontseite 13 nutartige Taschen 16 auf, welche entsprechend der dreidimensionalen Krümmung der Laufradschaufeln 6 geformt sind. Die Taschen 16 sind zur dem Laufradhauptkörper 4 abgewandten Rückseite 17 des Laufraddeckkörpers 5 hin geschlossen ausgeführt und so gestaltet, dass die Laufradschaufeln 6 zumindest überwiegend eingeschoben werden können.The
Die Laufradschaufeln 6 und die Taschen 16 bilden in Drehrichtung einen Formschluss, sodass der Laufradhauptkörper 4 über diesen Formschluss durch den Laufraddeckkörper 5 angetrieben wird, während der Laufraddeckkörper 5 direkt durch die Antriebswelle 7 angetrieben wird.The
Im Bereich der Druckseite 18 bildet das Gehäuse 2 der Kreiselpumpe eine Austrittsspirale 2a aus.In the area of the
Der saugseitige Laufradhauptkörper 4, ist in der Nabe 5a des Laufraddeckkörpers 5 axial verschiebbar gelagert. Die Laufradschaufeln 6 des Laufradhauptkörpers 4 können in die Taschen 16 eintauchen, wodurch die Laufradschaufelaustrittsbreite b zwischen einem Minimalwert und einem Maximalwert durch Verschieben des Laufradhauptkörpers 4 eingestellt werden kann. Ein ruckfreies Gleiten des Laufradhauptkörpers 4 am Laufraddeckkörper 5 kann erreicht werden, wenn der Laufradwerkstoff mit Schmiermitteln modifiziert ist. Die Taschen 16 im Laufraddeckkörper 5 können mit einer die Rückseite 17 des Laufraddeckkörpers 5 bildenden Abdeckung 5b abgedeckt sein, um druckseitige Strömungsverluste zu vermeiden.The impeller
Um in jeder Stellung des Laufradhauptkörpers 4 Strömungsverluste durch Kurzschlussströmungen zwischen Druckseite 18 und Saugseite 10 zu vermeiden, sind zwischen dem Laufradhauptkörper 4 und dem Gehäuse 2 Labyrinthdichtungen 20, 21 angeordnet, wobei bei den in den
Der Laufradhauptkörper 4 wird über eine Verstelleinrichtung 22 in axialer Richtung entlang der Achse 8 der Antriebswelle 7 - bei den in den
Die Verstellung des Laufradhauptkörpers 4 kann auf verschiedenste Weise mechanisch, elektromagnetisch, pneumatisch, hydraulisch oder thermisch erfolgen. In den
Die Gewindespindel 26 kann über den Aktuator 25 im oder gegen den Uhrzeigersinn gedreht werden. Die Spindelmutter 27 wird im ungeregelten Betrieb, beispielsweise bei Ausfall des Aktuators 25, von der im Laufraddeckkörper 5 gelagerten, als Druckfeder ausgebildeten Rückstellfeder 23, der Nabe 4a des Laufradhauptkörpers 4 und einem Axiallager 28 gegen einen Anschlag 29 auf der Gewindespindel 26 bewegt, wodurch sich ausfallssicher die maximale Laufradschaufelaustrittsbreite bmax einstellt. Im geregelten Betrieb wird die Spindelmutter 27, je nach geforderter Funktion, über den Aktuator 25 und die Gewindespindel 26 gegen das Axiallager 28, die Nabe 4a des Laufradhauptkörpers 4 und die Rückstellfeder 23 bewegt und damit die gewünschte Laufradschaufelaustrittsbreite b eingestellt. Der Aktuator 25 kann beispielsweise durch einen Schrittmotor 30 und einen Stirnradantrieb 31 gebildet sein.The threaded
Bei der in den
Die Gewindespindel 26 kann über den Aktuator 25 im oder gegen den Uhrzeigersinn gedreht werden. Die Spindelmutter 27 wird im ungeregelten Betrieb, beispielsweise bei Ausfall des Aktuators 25, von der im Laufraddeckkörper 5 gelagerten, als Druckfeder ausgebildeten Rückstellfeder 23 in die in
Die
In jeder der Ausführungsvarianten kann über den gesamten Drehzahl-, und Temperaturbereich eine aktive und zuverlässige Regelung der Kreiselpumpe 1 mit sehr geringer Antriebsleistung erzielt werden.In each of the design variants, an active and reliable regulation of the
Claims (14)
- Centrifugal pump (1), in particular a water pump, which is designed as a radial pump or mixed flow pump, comprising an impeller (3) which is arranged in a housing (2) so as to be rotatable about an axis (8) and is connected to a drive shaft (7), which impeller (3) comprises an impeller main body (4) having impeller blades (6) and an impeller cover body (5), wherein, for adjustment of the impeller outlet width (b) of the impeller (3), the impeller main body (4) and the impeller cover body (5) are axially displaceable relative to one another via an adjusting device (22), wherein the impeller main body (4) is arranged in an axially displaceable manner on the drive shaft (7) or the impeller cover body (5), and wherein the adjusting device (22) is operatively connected to the impeller main body (4), wherein the impeller cover body (5) has groove-shaped pockets (16) on the front side (13) facing the impeller main body (4) for accommodating the impeller blades (6), characterised in that the impeller blades (6) are curved three-dimensionally - at least in the region of the suction mouth (11).
- Centrifugal pump (1) according to claim 1, characterised in that the impeller cover body (5) is rigidly connected to the drive shaft (7).
- Centrifugal pump (1) according to claim 1 or 2, characterised in that the pockets (16) on the rear side (17) of the impeller cover body (5) facing away from the impeller main body (4) are formed in a closed manner.
- Centrifugal pump (1) according to claim 3, characterised in that the pockets (16) are also curved three-dimensionally according to the three-dimensional shape of the impeller blades.
- Centrifugal pump (1) according to claim 4, characterised in that the impeller main body (4) is arranged relative to the impeller cover body (5) so as to be pivotable about the axis (8) through at least a defined angular range.
- Centrifugal pump (1) according to one of claims 1 to 5, characterised in that the impeller main body (4) is drive-connected to the impeller cover body (5) and driven thereby.
- Centrifugal pump (1) according to one of claims 1 to 6, characterised in that the impeller main body (4) forms the suction mouth (11) of the centrifugal pump (1).
- Centrifugal pump (1) according to one of claims 1 to 7, characterised in that the impeller cover body (5) is arranged on the drive side (12) of the impeller (3) facing away from the suction mouth (11).
- Centrifugal pump (1) according to one of claims 1 to 8, characterised in that closed blade channels (15) are formed between the impeller main body (4) and the impeller cover body (5).
- Centrifugal pump (1) according to one of claims 1 to 9, characterised in that the impeller main body (4) is sealed off from the housing (2) on the side facing away from the impeller cover body (5) by means of at least one labyrinth seal (20, 21).
- Centrifugal pump (1) according to one of claims 1 to 10, characterised in that the adjusting device (22) comprises a screw gear (24) with a threaded spindle (26) rotatable via an actuator (25) and a spindle nut (27), wherein the threaded spindle (26) is rotatably mounted within the drive shaft (7) formed as a hollow shaft and the spindle nut (27) is connected to the impeller main body (4), and wherein the spindle nut (27) and the impeller main body (4) are connected to each other so as to be non-displaceable in the axial direction, preferably rotatable relative to each other.
- Centrifugal pump (1) according to one of claims 1 to 10, characterised in that the adjusting device (22) has a thrust gear (32) with a push rod (33) displaceable via an actuator (25), which push rod (33) is connected to a push sleeve (34), wherein the push rod (33) is mounted in an axially displaceable manner within the drive shaft (7) formed as a hollow shaft and the push sleeve (34) is connected to the impeller main body (4), and wherein the push sleeve (34) and the impeller main body (4) are connected to one another so as to be non-displaceable in the axial direction, preferably rotatable relative to one another.
- Centrifugal pump (1) according to one of claims 1 to 12, characterised in that the adjusting device (22) comprises an electromagnetic actuator (25).
- Centrifugal pump (1) according to claim 13, characterised in that the electromagnetic actuator (25) comprises at least one electromagnet (37) fixed to the housing and at least one preferably annular permanent magnet (36) which is fixedly connected to the impeller main body (4), wherein preferably the at least one permanent magnet (36) is arranged in the region of a labyrinth seal (20, 21) sealing the impeller main body (4) and the housing (2).
Applications Claiming Priority (2)
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ATA50398/2015A AT517163B1 (en) | 2015-05-13 | 2015-05-13 | ROTARY PUMP |
PCT/AT2016/050129 WO2016179619A1 (en) | 2015-05-13 | 2016-05-06 | Centrifugal pump with sliding rotor |
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EP3295034A1 EP3295034A1 (en) | 2018-03-21 |
EP3295034B1 true EP3295034B1 (en) | 2021-01-20 |
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EP16733866.4A Active EP3295034B1 (en) | 2015-05-13 | 2016-05-06 | Centrifugal pump with sliding rotor |
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EP (1) | EP3295034B1 (en) |
AT (1) | AT517163B1 (en) |
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US7789049B2 (en) | 2008-07-14 | 2010-09-07 | Honda Motor Co., Ltd. | Variable capacity water pump via electromagnetic control |
EP2299120B1 (en) * | 2009-09-14 | 2017-04-19 | Pierburg Pump Technology GmbH | Mechanical coolant pump for cooling an internal combustion engine |
DE102010005936A1 (en) * | 2010-01-26 | 2011-07-28 | LICOS Trucktec GmbH, 88677 | Device for a pump and water pump |
DE102011005476A1 (en) * | 2011-03-14 | 2012-09-20 | Schaeffler Technologies AG & Co. KG | Adjustable coolant pump for cooling circuit of internal combustion engine, has impeller which protrudes into suction chamber blades which is curved in three dimensions, and guide rotatable about rotation axis in relative to impeller |
DE102012200752A1 (en) * | 2012-01-19 | 2013-07-25 | Schaeffler Technologies AG & Co. KG | Controllable coolant pump for cooling circuit of water-cooled combustion engine, has vane wheel connected with cover disk by wings, where radial height of pressure edge of wings is changed from guide plate and edge to relief surface |
DE102014217489A1 (en) * | 2013-09-10 | 2015-03-12 | Schaeffler Technologies Gmbh & Co. Kg | Axial, by a shaft extending actuator assembly |
-
2015
- 2015-05-13 AT ATA50398/2015A patent/AT517163B1/en not_active IP Right Cessation
-
2016
- 2016-05-06 EP EP16733866.4A patent/EP3295034B1/en active Active
- 2016-05-06 WO PCT/AT2016/050129 patent/WO2016179619A1/en unknown
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
AT517163B1 (en) | 2019-08-15 |
EP3295034A1 (en) | 2018-03-21 |
WO2016179619A1 (en) | 2016-11-17 |
AT517163A1 (en) | 2016-11-15 |
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