EP2818725A1 - Pompe centrifuge avec roue à aubes déplaçable axialement et obturable - Google Patents

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

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Publication number
EP2818725A1
EP2818725A1 EP13174142.3A EP13174142A EP2818725A1 EP 2818725 A1 EP2818725 A1 EP 2818725A1 EP 13174142 A EP13174142 A EP 13174142A EP 2818725 A1 EP2818725 A1 EP 2818725A1
Authority
EP
European Patent Office
Prior art keywords
impeller
functional position
centrifugal pump
pump assembly
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13174142.3A
Other languages
German (de)
English (en)
Other versions
EP2818725B1 (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 US14/392,246 priority patent/US10539142B2/en
Priority to PCT/EP2014/063370 priority patent/WO2014207030A1/fr
Priority to CN201480036938.7A priority patent/CN105339672B/zh
Publication of EP2818725A1 publication Critical patent/EP2818725A1/fr
Application granted granted Critical
Publication of EP2818725B1 publication Critical patent/EP2818725B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/042—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.
  • 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 or a spring 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, on the output side a 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, which 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 functional position by a permanent magnetic force, which in particular acts 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 force generating means 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 according to the invention to hold the impeller in the first functional position and optionally from the second functional position to move to the first functional position, when the hydraulic force that holds the impeller in the second functional position, eliminated.
  • 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. This then causes the hydraulic axial force is eliminated when switching off the drive motor and the impeller is moved by the permanent magnetic force back into the first functional position. If the drive motor is turned on, the impeller generates a pressure on the output side and the said hydraulic axial force is built up, which is greater than the permanent-magnet restoring force, so that the impeller is then moved from the first functional position into the second functional position.
  • the flow path is closed by the impeller in the first functional position and opened in the second functional position.
  • a reverse embodiment is possible in which the flow path is closed by the impeller in the second functional position and opened in the first functional position.
  • the impeller in the first functional position, is preferably located closer to the stator than in the second functional position. In the second functional position, the impeller is preferably moved further to the suction side than in the first functional position. Again, however, 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.
  • the invention is also an impeller for a centrifugal pump unit beyond.
  • 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 of the invention is that the inlet opening is not located on the axial side but in a peripheral portion of the impeller, that is, 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 according to the invention has a closed suction-side axial end face, on which the peripheral section 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.
  • Such 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.
  • an impeller according to the invention can be created, which has an opening which is open to the outer circumference.
  • 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 assembly as described above, wherein the entrance 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-conducting connection 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 ' is such 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 peripheral 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.
  • the first functional position is that in which the flow path through the impeller is closed.
  • the impeller and the drive motor can also be easily designed so that the second functional position is the one in which the flow path is closed. This could be achieved by an offset between the stator and rotor in the reverse direction and by the use of a pressure-relieved impeller, in which the pressure-side end face of the impeller is subjected to the suction-side pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP13174142.3A 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement et obturable Not-in-force 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
US14/392,246 US10539142B2 (en) 2013-06-27 2014-06-25 Rotary pump with axially displaceable, closeable rotor
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

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

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13174142.3A Not-in-force 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)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3076020A1 (fr) * 2015-03-31 2016-10-05 Magna Powertrain Inc. Pompe à eau électrique à écoulement variable régulé à ressort
CN109424578A (zh) * 2017-08-23 2019-03-05 苏尔寿管理有限公司 具有提升装置的轴支承装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

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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
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EP3076020A1 (fr) * 2015-03-31 2016-10-05 Magna Powertrain Inc. Pompe à eau électrique à écoulement variable régulé à ressort
US10760577B2 (en) 2015-03-31 2020-09-01 Magna Powertrain Fpc Limited Partnership Spring regulated variable flow electric water pump
CN109424578A (zh) * 2017-08-23 2019-03-05 苏尔寿管理有限公司 具有提升装置的轴支承装置

Also Published As

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EP2818725B1 (fr) 2017-09-13
CN105339672A (zh) 2016-02-17
CN105339672B (zh) 2018-05-15
WO2014207030A1 (fr) 2014-12-31
US10539142B2 (en) 2020-01-21
US20160273542A1 (en) 2016-09-22

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