EP2818725B1 - Pompe centrifuge avec roue à aubes déplaçable axialement et obturable - Google Patents

Pompe centrifuge avec roue à aubes déplaçable axialement et obturable Download PDF

Info

Publication number
EP2818725B1
EP2818725B1 EP13174142.3A EP13174142A EP2818725B1 EP 2818725 B1 EP2818725 B1 EP 2818725B1 EP 13174142 A EP13174142 A EP 13174142A EP 2818725 B1 EP2818725 B1 EP 2818725B1
Authority
EP
European Patent Office
Prior art keywords
impeller
functional position
centrifugal pump
flow path
closed
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
Application number
EP13174142.3A
Other languages
German (de)
English (en)
Other versions
EP2818725A1 (fr
Inventor
Thomas Blad
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to EP13174142.3A priority Critical patent/EP2818725B1/fr
Priority to PCT/EP2014/063370 priority patent/WO2014207030A1/fr
Priority to CN201480036938.7A priority patent/CN105339672B/zh
Priority to US14/392,246 priority patent/US10539142B2/en
Publication of EP2818725A1 publication Critical patent/EP2818725A1/fr
Application granted granted Critical
Publication of EP2818725B1 publication Critical patent/EP2818725B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04D29/042—Axially shiftable rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • 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
    • F04D13/064—Details of the magnetic circuit
    • 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
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/62—Electrical actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the invention relates to a centrifugal pump unit and an impeller for such a centrifugal pump unit.
  • centrifugal pump units which have an axially displaceable shaft, whereby the impeller can be brought into two axial positions, wherein in a first position, the flow path closed by the impeller and in a second position, the flow path through the impeller is opened.
  • Such an arrangement is for example off DE 101 15 989 A1 known.
  • the impeller In the first position, in which the flow path is closed by the impeller, the impeller is held by spring force, while it is drawn when energized by the drive motor by a resulting axial magnetic force against the spring force in the second position.
  • the drive motor In order to open the impeller and the pump, it is necessary that the drive motor has a special configuration which generates a magnetic axial force for moving the impeller when energized.
  • DE 21 07 000 discloses a centrifugal pump with an axially displaceable impeller to selectively bring the impeller into fluid communication with two different inputs.
  • the impeller is designed so that it is moved during operation of the pump unit by the hydraulic pressure in one of the possible switching positions and can be moved via an electromagnetic coil in the motor either against this hydraulic force in a second switching position.
  • U1 discloses a pump having an electric drive motor in which the impeller is axially movable to be selectively moved to a closed or opened position.
  • the impeller can be moved by a magnetic force or a hydraulic force in the closed position and open automatically during operation of the pump unit by an opposite hydraulic pressure.
  • the impeller can be held by an axial centering of the rotor in the stator during operation in an open position and moved in the de-energized state by an additional spring or an additional magnet in a closed switching position.
  • EP 2 228 891 A2 discloses an electric motor for actuating a valve with a pump impeller, which simultaneously forms a movable valve member.
  • the pump impeller can be moved by normal to the operation of the pump impeller opposite direction of rotation via a thread in a closed switching position.
  • DE 25 10 787 A1 discloses a pump unit with an impeller, which can be selectively moved to a closed or open switching position.
  • the impeller is axially movable together with the rotor of the drive motor.
  • the rotor has a conical configuration, so that it is moved by the prevailing magnetic forces in operation in an axial position, which moves the impeller in its open position. The provision is made via a spring.
  • DE 10 2010 062 752 A1 discloses another pump unit with an axially movable impeller, which is movable between an open and a closed switching position. For movement, an additional hydraulic system is provided.
  • centrifugal pump unit which allows a displacement of the impeller between a first and a second functional position without additional components and makes it possible to keep the impeller without hydraulic pressure in one of the functional positions.
  • the centrifugal pump unit according to the invention has an electric drive motor, which is preferably designed as a permanent magnet rotor.
  • the drive motor is preferably a canned motor, i. H. a wet running engine.
  • the drive motor drives at least one impeller.
  • the impeller can be connected via a shaft to the rotor of the drive motor.
  • the impeller is also directly connected to a shaftless rotor or integrally formed with at least a part of the rotor.
  • the impeller is movable in the axial direction between at least two functional positions. In this case, the movement of the impeller preferably takes place together with the shaft or the rotor of the electric drive motor.
  • a flow path through the impeller is substantially closed, so that the impeller can assume a valve function in this functional position and can substantially block a flow path through the centrifugal pump assembly.
  • the shut-off essentially means that a small residual pass can remain and may even be desirable, as set forth below.
  • the flow path through the impeller and thus through the centrifugal pump unit is open and the centrifugal pump unit can promote the drive of the electric drive motor by rotation of the at least one impeller, a fluid, in particular a liquid.
  • the impeller is held in a first functional position by a magnetic force, in particular a permanent magnetic force. From the first to the second functional position, the impeller can then according to the invention be moved by a hydraulic force and held in the second position by a hydraulic force.
  • This hydraulic force is a hydraulic force generated by a fluid delivered by the impeller.
  • the impeller generates, when it is driven by the drive motor, the output pressure, which in turn acts on the impeller and / or coupled to the impeller for power transmission component that acts on the impeller, a hydraulic force, it in the second Function position holds.
  • the impeller in a very simple manner by driving the drive motor, ie by commissioning the drive motor, the impeller can be moved axially to open the flow passage.
  • the impeller is held in the first operative position by a permanent magnetic force acting between a permanent magnet rotor connected to the impeller and the surrounding stator of the drive motor. So can be dispensed with additional components for generating a permanent magnetic force. In addition, these Kratterzeugungssch are substantially free of wear, so that a high reliability of the pump unit according to the invention is ensured.
  • the impeller is held in the first functional position by a permanent magnetic force, which results from an axial displacement of the permanent magnet rotor relative to the stator of the drive motor. A permanent magnet rotor tends in the axial direction to center in the iron circle of the stator in the axial direction.
  • this permanent-magnet restoring force is used to hold the impeller in the first functional position and to move it, if necessary, from the second functional position into the first functional position, when the hydraulic force which drives the impeller in the second functional position holds, falls away.
  • the centrifugal pump unit is designed so that the hydraulic force which holds the impeller in the second functional position is greater than the permanent magnetic force which holds the impeller in the first functional position.
  • the flow path through the impeller is closed in the first functional position and opened in the second functional position.
  • the impeller in the first functional position, the impeller is preferably located closer to the stator than in the second functional position.
  • the impeller is preferably moved further to the suction side than in the first functional position.
  • a reverse configuration is possible.
  • a closure element is preferably present, which in the functional position in which the flow path is closed by the impeller, at least a large part, preferably more than 90%, closes an outlet opening or inlet opening of the impeller.
  • the closing element thus achieves the closing of the flow path, it being possible, as described above, that in the flow path, a residual opening remains, which allows a flow when starting the impeller in the closed or locked functional position to ensure a pressure build-up on the output side of the impeller in this functional position to the desired hydraulic force for moving the impeller in the create second functional position.
  • Such residual opening is preferably less than 10% of the total flow path, more preferably less than 5% or 2% of the total flow path.
  • the centrifugal pump unit is designed such that the closure element in that functional position in which the flow path is substantially closed by the impeller, the inlet opening or the outlet largely, but only so far closes that when starting the impeller, a pressure build-up on the output side of the impeller is possible.
  • the residual opening of the impeller is preferably as small as possible, but as large as necessary to set pressure in the closed state.
  • the impeller is preferably movable between the first and the second functional position relative to the closure element.
  • the closure element is preferably stationary and the impeller, as described, axially displaceable.
  • the closure element may preferably surround the impeller circumferentially and the impeller immerses with its outer wall in the inner circumference of the closure element.
  • the impeller may have an axial-side or radial-side inlet opening and the closure element may substantially cover the inlet opening in a functional position in order to close the closure the flow path through the impeller, wherein, as described above, a certain residual opening, preferably less than 10% or 5%, more preferably less than 2% may remain.
  • the closure element is preferably aligned so that it extends transversely to the longitudinal or rotational axis of the impeller and the end face closes the inlet opening.
  • the closure element is preferably designed as an annular wall which can cover the outer circumference of the impeller.
  • the impeller may have a radial outlet opening and cover the closure element in a functional position, the outlet opening.
  • the centrifugal pump unit is designed so that the flow path is effected by the impeller by closing the radial or peripheral outlet opening.
  • the closure element is preferably designed as an annular wall, which in a functional position, d. H. the functional position, in which the flow path is substantially closed, surrounding the outlet opening circumferentially.
  • a residual opening may remain in the manner described above.
  • the centrifugal pump assembly is designed such that in the functional position in which the flow path is closed by the impeller, the impeller rests with a peripheral edge bounding the outlet opening at an end edge of the annular wall.
  • the flow path between the first peripheral edge, which preferably faces the other functional position, and the annular wall are preferably substantially sealed tight.
  • more preferred may be between a second peripheral edge opposite this first peripheral edge and the annular wall in that functional position in which the flow path through the impeller is substantially closed, a flow passage remains which is open to an axial end face of the impeller. This is preferably a pressure-side axial end face on the outside of the impeller.
  • this axial end face is preferably located in a space enclosed by the annular wall, which, when the impeller rests with its first end edge, which limits the outlet opening, on the annular wall, is completely closed to a pressure channel. In this way the flow path to the outside is completely interrupted. However, there remains a flow path from the outlet side of the impeller to a pressure-side end face, so that upon rotation of the impeller in this area can build up a pressure which acts on the end face of the impeller and thus generates a hydraulic force which the impeller from this functional position in the other functional position, if necessary, shifts against an acting permanent magnetic force or spring force.
  • a special impeller for a centrifugal pump unit is advantageous for the invention.
  • This impeller may find particular use in a centrifugal pump unit, as described above, but could also be used independently in another centrifugal pump unit.
  • the impeller has at least one outlet opening and an inlet opening.
  • An essential feature is that the inlet opening is not located on the axial side but in a peripheral portion of the impeller, ie, is open to the outer circumference and the radial side.
  • Such an impeller allows the valve function described above, but could not only be used to close the flow path, but also, for example, by axial displacement between two possible Change or switch flow paths or cause a mixing function.
  • this impeller has a closed suction-side axial end face, on which the peripheral portion adjoins the inlet opening.
  • the fluid to be delivered flows essentially not in the axial direction but substantially in the radial direction through the inlet opening into the impeller.
  • the closed axial end side on the suction side of the impeller can simultaneously take over the function of a control disk by different hydraulic pressures acting on both sides of this end face, d. H. once on the inside of the impeller and once on the opposite outside of the impeller. These hydraulic forces can be used for axial positioning or displacement of the impeller, depending on which side of the impeller, a larger force acts.
  • the closed axial end face may be formed in one piece or in one piece with the other parts of the impeller.
  • this closed side in the form of a separate disc, which is fixed directly on a shaft of the rotor, as well as the impeller.
  • a disk can be arranged axially spaced from the impeller, so that a gap remains between the disk and the suction-side axial end of the impeller, which forms the annular radial-side inlet opening.
  • the inlet opening is formed as a extending over the entire circumference of the impeller annular opening.
  • webs may optionally be formed in the opening in the axial direction, which the Circumferential edges bounding the opening connect together to stabilize the structure of the impeller.
  • a closed axial end face of the impeller may be connected to the remaining parts of the impeller via the shaft or a connecting element in the interior of the impeller to ensure a connection across the annular opening.
  • the described opening preferably has a surface which corresponds to 50 to 150% of the cross-sectional area in the interior of the impeller in this area, this cross-sectional area extending transversely to the longitudinal or rotational axis of the impeller.
  • the opening of the impeller is preferably chosen so large that no high flow velocities occur in this area.
  • the impeller has on its suction side an elongated cylindrical portion of constant cross section, which preferably has an outer surface which corresponds to a size of 50 to 150% of an inner cross section (transverse to the longitudinal axis of the impeller) in the interior of this section.
  • this cylindrical portion the above-described annular or radially opened opening, which forms the inlet opening of the impeller, are located.
  • the cylindrical portion of the impeller permits axial movement of the impeller in a pump set as described above, wherein the entry portion in each position of the impeller can be sealed sufficiently outwardly to surround the pressure and suction sides of the impeller in each To separate position from each other.
  • the pump unit according to the first embodiment in FIGS. 1 and 2 has an electric drive motor 2, which has a stator 4 and a rotor 6 rotatable about the longitudinal axis X therein.
  • the drive motor is designed as a wet-running motor and has a gap tube 7 between the stator 4 and the rotor 6. This can be formed completely closed and separates rotor space and stator space.
  • the rotor is designed as a permanent magnet rotor 6 and rotatably connected to a along the longitudinal axis X extending shaft 8, which is preferably made of ceramic and machined over its entire length to storage quality.
  • the shaft in turn is non-rotatably connected to an impeller 10, which is preferably formed of plastic.
  • the rotor 6 is arranged axially movable together with the shaft 8 and the impeller 10 in its bearings 12, so that the impeller in a Fig. 1 shown first axial functional position and an in Fig. 2 shown axially spaced second functional position can take.
  • the impeller is closer to the stator 4 in the first functional position than in the second functional position.
  • the impeller 10 has on its axial end face an inlet opening 14 in the form of a suction mouth.
  • a fluid to be conveyed in particular a liquid to be conveyed in the axial direction X in the Inflow impeller 10.
  • the flow is then accelerated radially outwards by the centrifugal forces prevailing during rotation of the impeller and can emerge from the impeller 10 through a peripheral outlet opening located at the axial end facing away from the inlet opening 14.
  • the outlet opening 16 is formed as an annular opening in the peripheral region of the impeller adjacent to a pressure-side axial end face 18 of the impeller.
  • the outlet opening 16 is closed by a closure element in the form of a ring wall 20.
  • the annular wall 20 extends starting from a wall bounding the pump chamber, in this case a bearing carrier 22 in a direction away from the stator 4.
  • the annular wall 20 has such an axial length that it completely covers the axial extent of the outlet opening 16 in the first functional position and comes into contact with a first peripheral edge 24 which limits the outlet opening 16 on one axial side.
  • the first peripheral edge 24 is the suction side of the impeller 10 facing the peripheral edge which limits the outlet opening 16.
  • the annular gap 28 forms a flow passage from the interior of the impeller through the outlet opening 16 to the pressure-side end face 18 of the impeller 10. This flow path is open even when the annular wall 20 abuts the first peripheral edge 24 and so the flow path through the impeller to the outside in a pressure channel 30 closes.
  • the outlet opening 16 is displaced in the axial direction outside of the annular wall 20, ie the peripheral edge 24 has been disengaged from the end edge of the annular wall 20 and the annular wall 20 substantially no longer overlaps the annular outlet opening 16, so that during rotation of the impeller 10 funded fluid from the outlet opening 16 can escape into the pressure channel 30.
  • acts on the pressure-side end face 18 of the impeller 10 further, the hydraulic force F H due to the pressure in the pressure channel 30. This hydraulic force F H keeps the impeller 10 in the in Fig. 2 shown second functional position.
  • the rotor 6 In the first functional position is, as in Fig. 1 shown, the rotor 6 centered with respect to the surrounding stator 4 in the axial direction X, that is, the axial center S of the stator and the axial center R of the rotor are substantially one above the other. If the rotor, as in Fig. 2 shown, the dimension a is shifted relative to the stator 4, to bring the impeller 10 in the second functional position shown, thereby shifts the axial center R of the rotor 6 relative to the axial center S of the stator 4 also by the dimension a, as in Fig. 2 shown. This results in a magnetic restoring force F M. This is because the rotor 6 is a permanent magnet rotor to a permanent magnetic force.
  • the magnetic restoring force F M endeavors to restore the rotor 6 in the in Fig. 1 to move shown axially centered position. Ie. the magnetic restoring force F M counteracts the hydraulic force F H. As long as the hydraulic force F H is greater than this magnetic restoring force F M , the impeller 10 remains in the in Fig. 2 shown second functional position. By appropriate dimensioning of the drive motor and the impeller 10, this can be ensured. In addition, the drive motor 2 can be controlled so that always a sufficient pressure in the pressure channel 30 is ensured in order to keep the impeller 10 in operation in the second functional position shown.
  • the output side of the impeller in the pressure channel 30 again set a pressure which counteracts the magnetic restoring force F M and the impeller 10 in its second functional position or in a functional position between the first and the second Function position holds.
  • the pump unit has no electronic quantity limitation and, for example, is not externally controllable in order to reduce the flow rate in certain operating conditions.
  • Fig. 3 and 4 show a second embodiment of the invention.
  • the drive motor 2 is identical to the in Fig. 1 and 2 formedorgansbespiel, so reference is made to the relevant description. Also, this drive motor 2 is designed so that by moving the rotor 6 relative to the stator 4 by the dimension a, the axial center of the rotor 6 from the axial center S of the stator 4 is out of control, so that a magnetic restoring force F M results as previously described in the first embodiment.
  • the second embodiment differs from the first embodiment in that of the impeller 10 ', which is connected to the shaft 8, not the outlet opening 16' but the inlet opening 14 'is closed in the first functional position.
  • the outlet opening 16 ' remains in fluid communication with the pressure channel 30 in both functional positions.
  • the connection between the suction channel 32 'and the inlet opening 14' is substantially closed.
  • the inlet opening 14 ' is formed in this impeller 10' according to the invention as a peripheral or radial inlet opening 14 '.
  • the inlet opening 14 ' forms a circumferential annular opening through which fluid in the radial direction in the interior of the impeller 10' can occur.
  • the suction-side end face 34 of the impeller 10 ' is formed closed.
  • the suction-side end face 34 is formed by a disk-shaped wall, which at the same time has the function of a control disk can take over, since on the two sides of the suction-side end face 34, that is, both the interior of the impeller facing surface and the outwardly directed surface, a hydraulic pressure can act.
  • the inlet opening 14 ' In the first functional position, the inlet opening 14 'is located so that it faces an annular wall 36 in the pump chamber or pump housing.
  • the annular wall 38 is formed concentrically to the longitudinal axis X and surrounds the annular inlet opening 14 'so that it is substantially completely covered.
  • the inner diameter of the wall 36 is slightly larger than the outer diameter of the opening 14 'adjacent circumferential surfaces, so that between the wall 16' and the inlet opening 14 'bounding peripheral edge an annular gap 38 remains.
  • This forms a residual opening when the flow path through the impeller 10 'is substantially closed in the first functional position.
  • this residual opening represents less than 2% of the area of the inlet opening 14 ', so that only a very small flow passage remains.
  • the flow passage through the gap 38 is dimensioned so that here just as much fluid or liquid in the first functional position according to Fig. 3 can flow through that when starting the impeller 10 'can build up a pressure in the pressure channel 30.
  • a pressure leads to a hydraulic axial force F H , which acts on the pressure-side cover plate or front side 18 'from the outside to the impeller 10', so that this in the direction A from the first functional position in the in Fig. 4 shown second functional position is moved.
  • the inlet opening 14 ' is opposite the suction channel 32, so that the suction channel 32' through the inlet opening 14 'with the interior of the impeller 10' is in fluid communication and the impeller 10 'promotes fluid or fluid in rotation in the usual way ,
  • the hydraulic axial force F H continues to act on the pressure-side cover disk or end face 18 ', so that when there is sufficient Pressure in the pressure channel 30, the impeller 10 'is held in this second functional position against the magnetic restoring force F M.
  • the drive motor 2 is controlled so that always a sufficient output-side pressure in the pressure channel 30 is ensured.

Landscapes

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

Claims (9)

  1. Groupe motopompe centrifuge avec un moteur d'entraînement électrique (2) et au moins une roue à aubes (10; 10') qui est déplaçable en direction axiale (X) entre au moins deux positions de fonctionnement, dans une première position de fonctionnement, un trajet de flux passant par la roue à aubes (10 ; 10') étant sensiblement obturé et, dans une deuxième position de fonctionnement, le trajet de flux passant par la roue à aubes (10; 10') étant ouvert, la roue à aubes (10; 10') étant maintenue dans la première position de fonctionnement par une force magnétique permanente (FM) qui agit entre un rotor à aimant permanent (6) attaché à la roue à aubes (10, 10') et déplaçable axialement en union avec celle-ci et le stator entourant (4) du moteur d'entraînement (2) et résulte d'un écart axial (a) du rotor à aimant permanent (6) par rapport au stator (4) du moteur d'entraînement (2), et étant maintenue dans la deuxième position de fonctionnement par une force hydraulique (FH) engendrée par le fluide transporté par la roue à aubes, laquelle force est supérieure à la force magnétique permanente (FM).
  2. Groupe motopompe centrifuge selon la revendication précédente, caractérisé en ce qu'il y a un élément d'obturation (20 ; 36) qui, dans la position de fonctionnement dans laquelle le trajet de flux passant par la roue à aubes (10') est obturé, obture une ouverture de sortie (16) ou une ouverture d'entrée (14') de la roue à aubes (10 ; 10') au moins dans la plus grande partie, de préférence à plus de 90 %.
  3. Groupe motopompe centrifuge selon la revendication 2, caractérisé en ce que, dans la position de fonctionnement dans laquelle le trajet de flux passant par la roue à aubes (10 ; 10') est obturé, l'élément d'obturation (20; 36) obture l'ouverture d'entrée (14') ou l'ouverture de sortie (16) dans la plus grande partie, mais seulement autant que, lors de la mise en rotation de la roue à aubes (10 ; 10'), une pression puisse être engendrée du côté de la sortie de la roue à aubes (10 ; 10').
  4. Groupe motopompe centrifuge selon la revendication 2 ou 3, caractérisé en ce que la roue à aubes (10 ; 10') est déplaçable, entre la première et la deuxième positions de fonctionnement, par rapport à l'élément d'obturation (20 ; 36).
  5. Groupe motopompe centrifuge selon l'une des revendications 2 à 4, caractérisé en ce que la roue à aubes (10') comprend une ouverture d'entrée (14') du côté axial ou du côté radial et en ce que l'élément d'obturation (36) recouvre l'ouverture d'entrée dans une position de fonctionnement.
  6. Groupe motopompe centrifuge selon l'une des revendications 2 à 5, caractérisé en ce que la roue à aubes (10) comprend une ouverture de sortie (16) du côté radial et en ce que l'élément d'obturation (26) recouvre l'ouverture de sortie (16) dans une position de fonctionnement.
  7. Groupe motopompe centrifuge selon la revendication 6, caractérisé en ce que l'élément d'obturation (20) est configuré comme une paroi annulaire qui, dans une position de fonctionnement, entoure l'ouverture de sortie (16) sur son pourtour.
  8. Groupe motopompe centrifuge selon la revendication 7, caractérisé en ce que, dans la position de fonctionnement dans laquelle le trajet de flux passant par la roue à aubes (10) est obturé, la roue à aubes (10) est en appui, par un premier bord périphérique (24) délimitant l'ouverture de sortie (16), sur un bord frontal de la paroi annulaire (20).
  9. Groupe motopompe centrifuge selon la revendication 8, caractérisé en ce que, dans la position de fonctionnement dans laquelle le trajet de flux passant par la roue à aubes (10) est obturé, un passage de flux (28), qui est ouvert vers un côté frontal axial (18) de la roue à aubes (10), reste entre un deuxième bord périphérique (26) en regard du premier bord périphérique (24) et la paroi annulaire (20).
EP13174142.3A 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement et obturable Active EP2818725B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13174142.3A EP2818725B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement et obturable
PCT/EP2014/063370 WO2014207030A1 (fr) 2013-06-27 2014-06-25 Pompe centrifuge dont le rotor peut être déplacé axialement et peut être fermé
CN201480036938.7A CN105339672B (zh) 2013-06-27 2014-06-25 具有轴向可移动、可封闭的叶轮的离心泵
US14/392,246 US10539142B2 (en) 2013-06-27 2014-06-25 Rotary pump with axially displaceable, closeable rotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13174142.3A EP2818725B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement et obturable

Publications (2)

Publication Number Publication Date
EP2818725A1 EP2818725A1 (fr) 2014-12-31
EP2818725B1 true EP2818725B1 (fr) 2017-09-13

Family

ID=48745734

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13174142.3A Active EP2818725B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement et obturable

Country Status (4)

Country Link
US (1) US10539142B2 (fr)
EP (1) EP2818725B1 (fr)
CN (1) CN105339672B (fr)
WO (1) WO2014207030A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3076020B1 (fr) 2015-03-31 2020-12-30 Magna Powertrain FPC Limited Partnership Pompe à eau électrique à écoulement variable régulé à ressort
ES2904473T3 (es) * 2017-08-23 2022-04-05 Sulzer Management Ag Dispositivo de rodamiento de eje con dispositivo de elevación
CN110094339B (zh) * 2018-10-24 2020-06-26 浙江朗庆智能科技有限公司 离心式的尿素泵
CN111102205B (zh) * 2020-01-08 2020-11-20 福州城建设计硏究院有限公司 一种基于地下污水的防卡涩的自吸式排污泵
DE102021207404A1 (de) * 2021-07-13 2023-01-19 Robert Bosch Gesellschaft mit beschränkter Haftung Pumpenvorrichtung, insbesondere Magnetkupplungspumpenvorrichtung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2265806A (en) * 1939-05-15 1941-12-09 Goldschmied Livio Pump
US3329095A (en) * 1965-11-16 1967-07-04 Henning G Bartels Booster pump
DE2107000A1 (de) * 1971-02-13 1972-08-24 Loewe Pumpenfabrik Gmbh Kreiselpumpe, insbes. Heizungsumwälzpumpe
DE2510787A1 (de) * 1975-03-08 1976-09-16 Vaillant Joh Kg Pumpe
DE9319309U1 (de) * 1993-12-16 1995-08-03 Licentia Gmbh Pumpe mit einem elektrischen Antriebsmotor
DE19523661A1 (de) * 1995-06-29 1997-01-02 Mayer Helmut Turborotor
DE19845864A1 (de) * 1998-10-05 2000-04-06 Wilo Gmbh Spaltrohrmotor
DE10115989A1 (de) 2000-04-04 2001-12-13 Bernhard Stadler Radial-Strömungsmaschine, insbesondere Umwälzpumpe
CN201148979Y (zh) * 2007-12-17 2008-11-12 杭州大路实业有限公司 轴向力自平衡型磁力传动多级离心泵
DE102009011946A1 (de) * 2009-03-10 2010-09-16 Wilo Se Elektromotor zum Betätigen eines Ventils
DE102010062752A1 (de) * 2010-12-09 2012-06-14 Mahle International Gmbh Pumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US10539142B2 (en) 2020-01-21
WO2014207030A1 (fr) 2014-12-31
EP2818725A1 (fr) 2014-12-31
US20160273542A1 (en) 2016-09-22
CN105339672A (zh) 2016-02-17
CN105339672B (zh) 2018-05-15

Similar Documents

Publication Publication Date Title
EP0568909B1 (fr) Obturateur à disque rotatif pour turbine à gaz
EP2818725B1 (fr) Pompe centrifuge avec roue à aubes déplaçable axialement et obturable
EP2798224B2 (fr) Groupe de pompe
WO2008119404A1 (fr) Dispositif de transport de fluides
EP3540233A1 (fr) Groupe pompe centrifuge avec valve rotative
EP2284414B1 (fr) Embrayage à friction de liquide
EP1725775A1 (fr) Ensemble comprenant un moteur a induit exterieur a commutation electronique
EP2818726B1 (fr) Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents
WO2008058779A1 (fr) Dispositif de régulation pour un moteur à combustion interne
EP3376037B1 (fr) Groupe pompe centrifuge
EP3267042B1 (fr) Groupe motopompe
EP3657021A1 (fr) Pompe à vide
WO2018167043A1 (fr) Groupe motopompe
EP2228891B1 (fr) Moteur électrique destiné à actionner une soupape
EP2378127B1 (fr) Composant de guidage d'écoulement doté d'une pompe et d'une robinetterie
WO2017076649A1 (fr) Pompe à liquide de refroidissement pour un moteur à combustion interne
DE10115989A1 (de) Radial-Strömungsmaschine, insbesondere Umwälzpumpe
EP2002123A1 (fr) Pompe a fluide
DE102005057771B4 (de) Kältemittelverdichter
EP2786021B1 (fr) Motopompe de compteur hydraulique
DE102017223576A1 (de) Kühlmittelpumpe zum Fördern eines Kühlmittels
DE102020116770B4 (de) Vakuumpumpe mit integriertem miniaturventil
EP3907406B1 (fr) Pompe à vide
DE102017216696B4 (de) Flüssigkeitsreibungskupplung
WO2020126223A1 (fr) Compresseur à canal latéral conçu pour un système de pile à combustible pour transporter et/ou comprimer un milieu gazeux

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130627

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

R17P Request for examination filed (corrected)

Effective date: 20150622

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20170322

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 928441

Country of ref document: AT

Kind code of ref document: T

Effective date: 20171015

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013008323

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170913

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171213

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171214

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171213

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180113

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013008323

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

26N No opposition filed

Effective date: 20180614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180627

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180627

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 928441

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170913

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170913

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20220623

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20220621

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502013008323

Country of ref document: DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20220630

Year of fee payment: 10

Ref country code: DE

Payment date: 20220624

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502013008323

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20230627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240103

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230627