EP2818726A1 - Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents - Google Patents

Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents Download PDF

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Publication number
EP2818726A1
EP2818726A1 EP13174144.9A EP13174144A EP2818726A1 EP 2818726 A1 EP2818726 A1 EP 2818726A1 EP 13174144 A EP13174144 A EP 13174144A EP 2818726 A1 EP2818726 A1 EP 2818726A1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump unit
pressure
force
designed
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
EP13174144.9A
Other languages
German (de)
English (en)
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EP2818726B1 (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 EP13174144.9A priority Critical patent/EP2818726B1/fr
Priority to PCT/EP2014/063371 priority patent/WO2014207031A1/fr
Priority to US14/392,325 priority patent/US10539143B2/en
Priority to CN201480047257.0A priority patent/CN105492776B/zh
Publication of EP2818726A1 publication Critical patent/EP2818726A1/fr
Application granted granted Critical
Publication of EP2818726B1 publication Critical patent/EP2818726B1/fr
Active 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
    • 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
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0207—Pumps

Definitions

  • the invention relates to a pump unit with the features specified in the preamble of claim 1.
  • a centrifugal pump assembly in which a rotor shaft is axially displaceable together with the impeller, so that the impeller can be moved to a position in which its peripheral outlet openings are closed. In this way, the pump unit can take over a valve function and block a flow passage.
  • a pump unit with two wheels which are driven by a common shaft. These wheels can be moved by axial movement of the shaft in each case between two Austrittskandlen in the axial direction, so that the wheels depending on the axial position of the shaft either water from a primary circuit in a secondary circuit and back or only separately promote in the primary circuit and the secondary circuit.
  • a hydraulically or pneumatically actuated arranged outside the pump unit lifting device is provided for axial displacement of the shaft while a hydraulically or pneumatically actuated arranged outside the pump unit lifting device is provided.
  • Such has the disadvantage that the shaft must be led out of the interior of the pump housing, so that a sealed passage must be provided.
  • the pump unit according to the invention has an electric drive motor, in particular a wet-running electric drive motor, d. H. a canned motor in which the stator is separated from the rotor space by a split tube.
  • the pump unit is designed as a centrifugal pump unit and has at least one impeller, which is driven in rotation by the electric drive motor.
  • the impeller can be connected via a shaft to the rotor of the electric drive motor.
  • rotor and shaft form an integrated component and that the impeller is connected to this component.
  • the impeller may be integrally formed with the rotor and / or the shaft.
  • the impeller is arranged so that it can be moved in the axial direction between at least two positions, ie operating positions in which it can be rotationally driven by the drive motor.
  • the pump unit is designed so that in a first of these two positions, the impeller is arranged so that it is located in a first flow path through the pump unit and promotes fluid during rotation through this first flow path.
  • the second position or operating position is a position in which the Impeller in a second flow path, which runs through the pump unit, is located and during rotation, ie during operation of the pump unit, promotes fluid through this second flow path.
  • the impeller by axially moving the impeller along its rotational or longitudinal axis, it is possible to move the impeller between two operating positions, ie, said first position and said second position, to selectively provide fluid through a first or second flow path depending on the position in which the impeller is located. It is also conceivable that the impeller can assume one or more intermediate positions between said first and second positions in which it promotes fluid proportionally through both of the at least two flow paths.
  • the intended axial movement of the impeller is preferably chosen so large that in each position of the impeller, the cross-sectional area of the inlet opening of the impeller is so large that a certain maximum flow rate is not exceeded.
  • the pump unit is designed so that the inlet opening into the impeller, in particular a radial-side inlet opening in the impeller, as described below, has a surface which has in the range of 50 to 150% of the inner cross-sectional area of the impeller on the suction side. This inner cross-sectional area extends transversely to the longitudinal or rotational axis of the impeller.
  • the pump unit is designed in such a way that, at least in one direction of movement of the impeller, this movement takes place by means of a hydraulic force which itself is caused by the fluid conveyed by the impeller.
  • the pump unit is designed so that the pressure of the fluid conveyed by the impeller acts on a suitable surface such that an axial direction, ie parallel to the axis of rotation of the Impeller directed hydraulic force is generated, which is used to move the impeller axially in this direction.
  • the use of the hydraulic force to move the impeller has the advantage that can be dispensed with external actuators and the force required to move rather by the pump unit, that can be generated by the rotating impeller itself.
  • the entire rotor may be tightly encapsulated inside the can.
  • the pump unit is preferably designed so that the impeller in operation, d. H. when rotationally driven by the drive motor, by at least one hydraulic force generated by the conveyed fluid in at least one of the positions, i. H. in the first or second position.
  • the fluid pressure generated by the impeller can act on a corresponding connected to the impeller or coupled to the power transmission pressure surface, so that a force is exerted on the pressure surface, which presses the impeller in the desired position or holds in this position.
  • the force is preferably directed parallel to the axis of rotation of the impeller. Ie. said pressure surface preferably has an orientation transverse to this axis of rotation or at least one component directed transversely to the axis of rotation.
  • the pump unit is designed so that the impeller in operation by an interaction of at least one of the funded fluid generated hydraulic force, a spring force and / or an axially acting magnetic force in at least one of the positions, ie said first or second position, held is, wherein the magnetic force further preferably acts on a rotor connected to the impeller of the drive motor.
  • the impeller is held by the magnetic force in one of the two said positions, wherein in this state, the magnetic force is greater than an acting in the opposite direction of the impeller hydraulic force.
  • a spring force generated by a spring element act on the impeller so that it is held in one of the positions.
  • the impeller In the second position then acts on the impeller, a hydraulic force, for example in a manner described in the above-oriented pressure surface, which is greater than the magnetic force and / or the spring force, so that the impeller against the magnetic force and / or the spring force in the second position is held.
  • the impeller may be selectively held in the first or second position by interaction of a magnetic force and / or a spring force and a hydraulic force, wherein in one of the positions the hydraulic force and in the other position the magnetic force or spring force is greater.
  • one of the forces In order to achieve a switching between the positions, one of the forces must be correspondingly increased and / or the other force must be reduced accordingly.
  • the hydraulic force is preferably generated by the impeller itself during its rotation, this force will not act at standstill of the pump unit, so that in this state then preferably only a magnetic force and / or a spring force acts on the impeller.
  • the impeller can be moved in the idle state by the magnetic force and / or the spring force in a predetermined one of the two positions, so that the impeller is always in a defined one of the two possible positions at rest of the pump unit. Ie. When starting, the pump set always starts from a defined position.
  • the pump unit can also be designed such that by the energization of the drive motor, an axially acting magnetic force is generated, which can be generated for example by interaction between the rotor and the stator of the drive motor.
  • a magnetic force can also move the impeller from a rest position, which represents a first position, in the axial direction to a second position. In the first position, the impeller can then be held, for example, by a magnetic force and / or a spring force.
  • magnetic axial force can optionally be supported with a suitable embodiment of the pump unit by the above-described hydraulic axial force which is generated by the impeller itself.
  • the impeller is preferably connected to a rotor of the electric drive motor and at least one magnetic force, in particular the magnetic force described above, which acts on the impeller in the axial direction, preferably results from a magnetic interaction between the rotor and a surrounding stator, in particular one axial offset between rotor and stator.
  • a magnetic interaction between the rotor and a surrounding stator in particular one axial offset between rotor and stator.
  • the rotor is formed as a permanent magnet rotor and located in a stator having iron elements and coils, the rotor tends to magnetically center in the axial direction inside the iron part of the stator. If the rotor is moved out of this centered position in the axial direction, this results in an axial magnetic restoring force acting against this movement.
  • the pump unit can be designed so that when operating the pump the impeller in the axial direction, a pressure of the pumped fluid at least in certain operating states acts such that a hydraulic force is generated on the impeller, which moves the impeller with the rotor in the axial direction against the resulting magnetic restoring force from the centered position in the stator.
  • a pressure of the pumped fluid at least in certain operating states acts such that a hydraulic force is generated on the impeller, which moves the impeller with the rotor in the axial direction against the resulting magnetic restoring force from the centered position in the stator.
  • a magnetic actuating and / or holding force which acts on the rotor and thus the impeller in the axial direction can be generated without additional magnetic elements or other holding or actuating elements would be required in the pump unit.
  • a spring force generated by a spring element can be used to hold the impeller in a desired position.
  • the pump unit could also be designed so that a spring force and a magnetic force in the manner described above hold the impeller in one of the positions.
  • the pump unit is designed so that the impeller is arranged in its first position such that it promotes in a first outlet channel and the impeller is arranged in its second position such that it conveys into a second outlet channel.
  • the impeller when moved between the first and second positions, is moved between the two said exit edges, preferably remaining in communication with one and the same inlet channel in both positions. Ie.
  • the switching between two flow paths takes place in that the output, in which promotes the impeller, is changed by axial movement of the impeller.
  • the impeller is arranged in its first position such that it is connected at its suction side with a first inlet channel, and the impeller is arranged in its second position such that it is connected at its suction side with a second inlet channel.
  • the impeller remains in both positions in fluid-conducting connection with the same outlet channel. Ie. the impeller conveys into the same outlet passage in both positions but sucks in the first position through a different entrance passage than in the second position. In this way, in this embodiment, a switching between the two flow paths is achieved in that the impeller is brought into fluid communication with two different inlet channels.
  • both embodiments can be combined with each other, d. H. upon movement of the impeller both the connection to the inlet channel and the connection to the outlet channel can be changed. For example, it is possible to switch the subsidy between two separate circuits.
  • the pump unit is designed such that the hydraulic force can be generated by a specific operating mode of the drive motor, in particular by a speed change.
  • a specific operating mode of the drive motor for example, by increasing the speed of the output side pressure of the fluid can be increased so that the pressure acting on the above-mentioned pressure surface increased so much that a counteracting force, in particular the magnetic force described above, is overcome and then the impeller in another Position is shifted in the axial direction.
  • a counteracting force in particular the magnetic force described above
  • the impeller moves axially.
  • a valve could be opened by speed and pressure increase, whereby a pressure surface is acted upon by the hydraulic pressure.
  • the pump unit may be designed such that the hydraulic force, by which the impeller is axially displaced, is generated by different degrees of acceleration of the drive motor.
  • Different strong accelerations of the drive motor can lead to different pressure build-up in the subsequent to the pump unit line systems, so that on the impeller itself or with the impeller, for example via the rotor shaft connected or force-transmitting coupled pressure surfaces, different pressures can act.
  • two opposing pressure surfaces, for. B. on opposite axial sides of the impeller may be provided, which are both acted upon by the impeller generated by the fluid pressure, but via a subsequent conduit system.
  • the impeller can be moved by the higher hydraulic force in the appropriate direction.
  • appropriate design of the pump unit can then be prevented that on the other side of the displacement counteracting force is generated. This can be done, for example, by closing a flow path or by counteracting an interaction or assistance by a magnetic force as described above.
  • the pump unit is designed as a bistable system, in which the impeller in operation by the acting hydraulic and / or magnetic forces and / or spring forces, in particular by those as described above, each held stable in its first and second positions becomes. This means that once the impeller has reached one of the two positions during operation, it remains in this position during operation. To move to the other position is either an external force to apply or to change the operating state of the pump unit so that a switching force is generated, which shifts the impeller in the respective other position.
  • the pump unit can be designed so that it can cause a movement of the impeller from one to the other position only when starting, ie when accelerating the drive motor from a standstill.
  • the pump unit may be configured so that the idle wheel is held in one of the positions by a magnetic force and / or a spring force.
  • the pump unit can be designed so that due to the flow resistance of the subsequent piping systems or hydraulic components, a pressure acting on a pressure surface, which is used to generate power in the axial direction, pressure builds up at different rates. Now if there are two opposite pressure surfaces and both with the same hydraulic Force are applied, there is no force which acts in the axial direction of the impeller and this could move, for example, against a magnetic force or spring force.
  • the impeller is located in its first position axially closer to the stator of the drive motor than in its second position. Ie. it is moved from its first position in the axial direction away from the stator to the second position.
  • the pump unit is configured so that in the first position of the impeller acting in the direction of the first position hydraulic force on a suction side axial end side of the impeller or a pressure element or a pressure surface, which is coupled to transmit force to the impeller acts. Ie. the hydraulic force in the first position causes the impeller to be pushed to the first position. The fluid pressure acts on the said axial end face of the impeller or a pressure element.
  • the pump unit may preferably be designed such that in the first position of the impeller acts in the direction of the first position magnetic force and / or spring force on the impeller.
  • This may, for example, be a magnetic force which, as described above, consists of an axial offset between Rotor and stator results, ie when the rotor with the impeller is moved out of this position, creates a magnetic restoring force between the rotor and stator, which pushes or pulls the rotor in the first position.
  • a spring element for generating a spring force could be present.
  • Such a magnetic force and / or spring force can serve, in particular, to hold the impeller in the first position when the pump unit is stationary, so that the impeller always starts from the first position.
  • the pump unit is designed such that at least in the second position of the impeller acting in the direction of the second position hydraulic force on a pressure side axial end side of the impeller or a second position facing away from a pressure element or one of the second position facing away pressure surface acts, which is coupled with the impeller force-transmitting.
  • This hydraulic force can then be used to hold in operation the impeller in the second position, in particular against a magnetic force and / or spring force, as described above.
  • the pump unit is designed such that in the second position of the impeller, a suction-side axial end face of the impeller or the end face of a coupled to the impeller pressure element is depressurized.
  • the axial end face of the impeller on the suction side is pressure-relieved, in particular, when the low output pressure of the fluid flowing back into the circuit to the pump unit is present here.
  • the pressure reduction or pressure loss can occur, for example, in a downstream of the pump unit downstream piping system.
  • the line systems connected to the flow paths have different throttle properties, so that when starting the Impeller of the pressure build-up in these systems runs at different speeds, so that the axial displacement of the impeller can be achieved by different strong accelerations.
  • At least one connecting channel may be present in the pump unit, which connects a downstream of the impeller pressure range or pressure channel with a side facing away from the pressure area of the impeller or a coupled to the impeller for power transmission pressure element to a hydraulic pressure from the output side of the impeller to transmit to the side facing away from the printing area of the impeller or the pressure element.
  • a hydraulic force can be generated, which presses the impeller in one of the positions, in particular the first position, or holds in this.
  • a control element for example a switchable valve or a throttle point, be arranged to control the flow through the connecting channel.
  • the pressure build-up on the connected side of the impeller or the pressure element can be prevented or delayed to prevent the axial displacement of the impeller and, for example, to move the impeller to the second position by pressing on the opposite side of the impeller or the pressure element is first built up a higher pressure.
  • a receiving space in which a closed suction-side axial end face of the impeller or a pressure element coupled to the impeller, such as a control disk, enters at least one position of the impeller and which is designed such that it preferably via a Throttle is acted upon by a hydraulic pressure generated by the impeller for generating a hydraulic force.
  • the throttle point can be formed by a gap between a peripheral wall of the receiving space and the outer periphery of the axial end face of the impeller or the pressure element.
  • a damping effect on entry of the end face or of the pressure element into the receiving space can be achieved via this gap or throttle point.
  • the invention is in addition to the pump unit described above, a heating system with such a pump unit.
  • the pump unit acts in the heating system, which in the sense of this invention, an air conditioner is to be understood as heating circulation pump unit to circulate the heat carrier in the heating system, in particular water.
  • the heating system according to the invention has at least two system parts, of which a first part of the system is connected to the first flow path of the pump unit and the second part of the system to the second flow path of the pump unit.
  • the system parts may be heat exchangers and piping systems, which in each case form a circuit with the flow paths of the pump unit. Ie.
  • the first flow path of the pump unit lies in a fluid circuit through the first part of the plant and the second flow path of the pump unit is in a fluid circuit through the second part of the system, so that the impeller in its first position promotes fluid through the first part of the system and in its second position fluid through the second part of the system.
  • the impeller in its first position promotes fluid through the first part of the system and in its second position fluid through the second part of the system.
  • the two parts of the system are at least two consumers or at least two heat sources.
  • two consumers can be two different heating circuits of a heating system which heat different parts of the building.
  • a different heat sources for example, a conventional, heated with fossil fuels boiler and a solar thermal system can serve.
  • the two flow paths through the pump unit are then each connected to one of the heat sources or a consumer via corresponding piping systems, so that the heating medium or fluid, especially water is conveyed through these equipment parts, depending on whether the impeller in the first or the second position located.
  • the first part of the plant is a space heating circuit and the second part of the plant is a heat exchanger for domestic water heating.
  • a heat generator in the form of a fossil-heated boiler is usually provided, which has a primary heat exchanger in which a heating medium, in particular water, is heated. This is then optionally by the radiator in the rooms to be heated, ie by a space heating circuit, or by a heat exchanger for Warming of service water.
  • a circulation pump is usually provided and the switching between the space heating circuit and the heat exchanger for domestic water heating is effected by a 3/2-way valve.
  • the circulation pump is replaced by a pump unit, as described above, can be dispensed with in such a system on the 3/2-way valve, since the switching between domestic water heating and space heating can then be done by axial displacement of the impeller in the pump unit.
  • the impeller conveys through the first flow path in the pump unit and thus through a connected first part of the installation, namely the space heating circuit.
  • the impeller When the impeller is in its second position, it promotes the heating medium through the second flow path and thus through the connected to this heat exchanger for domestic water heating.
  • the construction of a heating system can be significantly simplified as can be dispensed with an additional valve and the switching between the heating circuits ideally can be done solely by targeted control of the drive motor of the pump unit, for example by changing the speed or change the acceleration when starting.
  • the heating system is configured such that at a branch point between the first and second abutment part prevailing hydraulic pressure in at least one of the positions of the impeller causes a hydraulic force that holds the impeller in this position.
  • the plant is preferably designed so that this hydraulic pressure is transmitted through that part of the plant through which no flow takes place in this position of the impeller.
  • the unused plant part can be used as a control line for controlling or holding pressurization of the impeller.
  • the prevailing at the branch point Pressure used to hold the impeller in one of its positions or move it to the desired position.
  • the invention further relates to a boiler for a heating system, as described above.
  • the boiler preferably has a pump unit as described above. Further, it has a primary heat exchanger in which the heating fluid is heated, for example by a burner for fossil fuels, preferably gas. Furthermore, it is provided with a secondary heat exchanger for domestic water heating and at least one connection for a space heating circuit. This connection for the space heating circuit has at least one connection for the trace and a connection for the return of the space heating circuit.
  • the secondary heat exchanger and the connection for the space heating circuit, d. H. in particular its trace, are connected via a branch point with the primary heat exchanger. Ie.
  • the boiler is designed so that at the branch point prevailing hydraulic pressure in at least one of the positions of the impeller of the pump unit in this causes a hydraulic force which holds the impeller in this position.
  • the hydraulic pressure at the branch point is used to control or hold the impeller in a desired position.
  • 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. essential to the invention Feature 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, to change or switch by axial displacement between two possible flow paths or to 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 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, ie 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.
  • the opening optionally webs may be formed in the axial direction, which interconnect the peripheral edges which define the opening, in order 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, the inlet portion or inlet opening being sufficiently sealed to the outside in each position of the impeller can be used to separate the pressure and the suction side of the impeller in each position from each other.
  • FIGS. 1 and 2 schematically a pump unit 2 is shown, which is integrated in a heating system 4, for example, a compact heating system.
  • the heating system 4 has a first part of the plant, which is formed by a space heating circuit 6.
  • a second system part or heating circuit is formed by a heat exchanger 8 for heating domestic water.
  • the first heating circuit through the space heating circuit 6 and the heating circuit through the heat exchanger 8 branch at a branch point 10 which is located downstream of a primary heat exchanger 12.
  • the primary heat exchanger 12 may be arranged for example in a gas or oil boiler and is used to heat the heating medium, in particular water, in the heating system 4, which downstream then through the heat exchanger 8 for the domestic water heating, which forms a secondary heat exchanger 8, and / or the space heating circuit 6 flows.
  • the fluid which forms the heating medium promoted by the pump unit 2 through the primary heat exchanger 12 and the heating circuits.
  • the pump unit 2 is a centrifugal pump unit, which has an electric drive motor 14, which via a shaft 16 drives a rotationally fixed on this and fixed in the axial direction impeller 18.
  • the shaft 16 is preferably made of ceramic and processed over its entire length in bearing quality.
  • the impeller is preferably made of plastic.
  • the drive motor 14 is designed as a wet-running electric motor, which has a can 20, which fluid-tightly separates the stator 22 from the rotor space in which the rotor 24 is arranged.
  • the rotor 24 is preferably designed as a permanent magnet rotor and also fixed axially fixed and rotationally fixed to the shaft 16. Possibly.
  • the rotor 24 could be integrally formed with the shaft 16.
  • the stator 22, which is shown here only schematically, can usually be formed from an iron part with stator coils arranged therein.
  • the shaft 16 is axially displaceable with the rotor 24 and the impeller 18 in the axial direction X in their bearings 26. Thereby, the impeller 18 is between a first position, which in Fig. 1 is shown, and a second position, which in Fig. 2 shown is movable. In his first position, which in Fig. 1 is shown, the impeller 18 is located closer to the stator 22 than in its second position, which in Fig. 2 is shown.
  • the impeller 18 has in a known manner radially outwardly directed outlet openings 28, which are open to a surrounding outlet channel 30 out.
  • the outlet channel 30 is in this example with the Entrance side of the primary heat exchanger 12 connected. Ie. the fluid exiting from the impeller 18 is conveyed through the outlet channel 30 to the primary heat exchanger 12.
  • the suction port 32 is optionally in fluid communication with a first inlet channel 34 or a second inlet channel 36. Ie. in the first in Fig. 1 shown position of the impeller 18 sucks this via its suction port 32 fluid from the first inlet channel 34 at.
  • This first inlet channel 34 connects downstream to the space heating circuit 6 and thus forms part of a first flow path for the heating medium through this space heating circuit 6.
  • Axially spaced from the suction port 32 is attached to the shaft 16, a pressure element in the form of a control disk 38.
  • This is so of the suction port 32 in the axial direction spaced, that between the control disk 38 and the peripheral edge of the suction mouth 32, a circumferential gap 39 is formed, which in the first position, the first inlet channel 34 and in the second position of the impeller opposite the second inlet channel 36.
  • the control disc 38 closes with a peripheral wall 37, the second inlet channel 36, so that in this position substantially no fluid from the second inlet channel 36 can flow into the suction port 32 and so in the first in Fig. 1 shown position substantially no fluid or heating medium is conveyed through the secondary heat exchanger 8.
  • a peripheral wall of the impeller 16 closes the first inlet channel 34, so that the impeller 32 substantially no fluid from the first inlet channel 34 sucks and thus substantially no fluid or heating medium is conveyed through the space heating circuit 6.
  • the peripheral wall of the impeller 18 and the control disk 38 thus simultaneously have the function of valve elements.
  • the axial displacement of the shaft 16 is achieved with the impeller 18 without additional actuators alone by the operation of the electric drive motor 14.
  • the impeller 18 in the in Fig. 1 shown first position ie in his case closest to this Stator 22 located position.
  • this is achieved by magnetic restoring forces M in the electric drive motor 14, which act in the axial direction X.
  • the rotor 24 is centered relative to the stator 22 in the axial direction, ie, the axial center S of the stator is congruent with the axial center R of the rotor.
  • a hydraulic force F 2 acts on a pressure-side pressure disk 44 of the impeller 18 during operation of the pump assembly.
  • the size of the control writing 38 in relation to the surface of the rear cover plate 44 and the design of the drive motor 14 can be achieved between the hydraulic forces F 1 and F 2 and the magnetic restoring force M, such an interaction that the magnetic restoring force M and hydraulic axial force F 1 are greater than the hydraulic force F 2 .
  • a seal 52 may be arranged, which prevents the pressure-side cover plate 44 is acted upon by the pressure prevailing in the outlet passage 30 p 1 .
  • substantially eliminates the previously described hydraulic force F 2 so that the impeller 18 by the hydraulic force F 1 in the in FIGS. 1 and 3 shown first position can be held.
  • This can be additionally supported by the magnetic restoring force M.
  • the space in the interior of the seal 52 could also be provided with a lower pressure from inside the impeller 18 via an optional, in Fig. 3 dashed line aperture 54 in the pressure-side cover plate 44 are acted upon.
  • a plurality of apertures 54 could also be provided.
  • the axial displacement of the impeller also takes place in the Fig. 3 Example shown in the foregoing and explained below manner.
  • the control disk 38 is arranged so that it dips in the direction away from the drive motor 14 with axial displacement of the rotor 24 with the impeller 18 in a receiving space 43.
  • the receiving space 43 has in a plane transverse to the longitudinal or rotational axis X has a circular cross-section whose inner diameter is slightly larger than the outer diameter of the control disk 38.
  • the receiving space 43 is cup-shaped and open only on its side facing the impeller 18 side. In the in Fig. 1 shown first position of the impeller 18, the control disk 38 is just outside the receiving space 43, so that the first side 40 of the control disk 38, which faces away from the impeller, extends substantially in a plane with the peripheral edge at the axial end of the receiving space 43.
  • annular gap 45 is formed between this peripheral edge and the control disk 38.
  • This forms a throttle for the fluid in the second inlet channel 36, so that in the receiving space 43, a slower pressure build-up than in the inlet channel 36 takes place.
  • a state is reached at fast start, in which at the first first side facing away from the impeller 18 of the control disk 38 initially substantially no pressure, while at the opposite the impeller 18 and the suction mouth 32 facing the second side 42 of the control disk 38 itself builds up a pressure which causes a force F 3 in the axial direction, which is greater than the described magnetic restoring force M and thus the rotor 18 from the in Fig. 1 shown first position in the in Fig. 2 moved shown second position.
  • connection channel 46 opens at the peripheral wall of the receiving space 23 in a region which in the second Position of the peripheral wall 37 of the control disk 38 is covered and thus closed. Via the connecting channel 46, a rapid build-up of pressure in the receiving space 43 is achieved during slow starting of the drive motor 14, so that there quickly a hydraulic force F 1 is built up, which supports the magnetic force M to hold the impeller 18 in the first position shown. In order to achieve that to move the impeller 18 in the in Fig.
  • a hydraulic force F 3 can be constructed, which acts on the second, the impeller side facing the control disk 38, 46 is disposed in the connecting channel 46, a control element 48 for controlling the flow through the connecting channel 46, which as a simple throttle or can be designed as a switchable valve.
  • the connecting channel 46 is particularly advantageous when the hydraulic resistance in the heating part before the consumer, ie in particular in the primary heat exchanger 12, is very large.
  • the consumers form the space heating circuit 6 and the secondary heat exchanger 8. If the hydraulic resistance in this heating part is very large, the pressure p 2 at the branch point 10 becomes too low to exert a suitable hydraulic force F 1 on the impeller.
  • control element 48 is designed as a switchable valve, then the connecting channel 46 can be closed, so that no hydraulic pressure F 1 can build up in the receiving space 43 and initially a hydraulic force F 3 builds up over the first inlet channel 34 second side 42 of the control disk 38 acts. This hydraulic force F 3 then leads to the axial displacement of the impeller 18 from the in Fig. 1 shown position in the Fig. 2 shown position, in which case additionally the control disk 38 with its peripheral wall 37 closes the connecting channel 36. If the control 48 is designed as a throttle, it can be ensured by a suitable design of the throttle, that at a fast start of the drive motor from the in Fig.
  • control disk 38 may be an integral part of the impeller 18.
  • an impeller 18 is provided which has a closed suction-side axial end face. This is formed by the control disk 38.
  • the impeller then has a circumferential suction or inlet opening, which is formed by the gap 39.
  • the gap 39 preferably has a surface which is 50 to 150% of the cross-sectional area in the interior of the impeller 18 in the region of the gap 39. This inner cross-sectional area extends transversely to the longitudinal axis X. In this way, a sufficiently large flow cross-section is ensured in the region of the gap 39.
  • impeller 18 in the region of the gap 39 has a cylindrical extension of constant cross section, which allows the axial displacement of the gap 39 between the inlet channels 34 and 36.
  • the control disk 38 may be connected to the remaining parts of the impeller 18 via suitable webs or connecting elements in the interior or else, as shown here, by the shaft 16.
  • the described magnetic restoring force M could also be assisted or replaced by a spring force. So could for example, in the receiving space 43, a compression spring are arranged which exerts a compressive force generated in the axial direction X on the axial end face of the shaft 16, which the shaft 16 with the rotor 24 and the impeller 18 in the in FIGS. 1 and 3 shown first position presses.
  • control disk 38 could be designed as a fixed, ie not together with the shaft 16 rotating component and the shaft could only come with its front side on the control disk 38 slidably to the plant. Thus, the control disk 38 could still exert a directed in the direction of the hydraulic force F 1 axial force on the shaft. By appropriate positive engagement, the control disk 38 could also transmit a hydraulic force F 3 in the axial direction of the shaft 16, without having to rotate together with this.
  • the impeller 18 could possibly take intermediate positions, whereby a mixing function could be realized. So could such a pump unit, for example, as a mixer, for. B. for a floor heating circuit, act. Then, for example, the first inlet channel 34 would be connected to the heating water inlet, while the second inlet channel 36 would be connected to the return from the underfloor heating circuit and the outlet channel 30 would be connected to the inlet side of the underfloor heating circuit.
  • such a pump unit instead of optionally two different heating circuits to operate as parts of a heating system, could also be used so that it optionally fluid from two different heat sources or heat generators, such as a fossil-fired boiler and a solar thermal Facility promotes.
  • two different heat sources instead of the space heating circuit 6 and the secondary heat exchanger 8, for example, two different heat sources could be connected to the pump unit 2.
EP13174144.9A 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents Active EP2818726B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13174144.9A EP2818726B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents
PCT/EP2014/063371 WO2014207031A1 (fr) 2013-06-27 2014-06-25 Pompe centrifuge à rotor pouvant être déplacé axialement pour permettre un refoulement sur différents trajets d'écoulement
US14/392,325 US10539143B2 (en) 2013-06-27 2014-06-25 Centrifugal pump having axially moveable impeller wheel for conveying different flow paths
CN201480047257.0A CN105492776B (zh) 2013-06-27 2014-06-25 用于供应不同流动路径并具有可轴向移动的叶轮的离心泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13174144.9A EP2818726B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents

Publications (2)

Publication Number Publication Date
EP2818726A1 true EP2818726A1 (fr) 2014-12-31
EP2818726B1 EP2818726B1 (fr) 2017-08-23

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EP13174144.9A Active EP2818726B1 (fr) 2013-06-27 2013-06-27 Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents

Country Status (4)

Country Link
US (1) US10539143B2 (fr)
EP (1) EP2818726B1 (fr)
CN (1) CN105492776B (fr)
WO (1) WO2014207031A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10487837B2 (en) * 2015-01-22 2019-11-26 Litens Automotive Partnership Multi-stage impeller assembly for pump
DE102015100929A1 (de) * 2015-01-22 2016-08-11 Ari-Armaturen Albert Richter Gmbh & Co Kg Stellventil
CN105952684B (zh) * 2016-06-17 2018-08-21 四川五洲仁信科技有限公司 新能源汽车电子水泵、控制系统及方法
EP3376038B1 (fr) * 2017-03-14 2021-07-28 Grundfos Holding A/S Groupe motopompe
EP3376049A1 (fr) * 2017-03-14 2018-09-19 Grundfos Holding A/S Groupe motopompe
EP3376037B1 (fr) * 2017-03-14 2021-01-27 Grundfos Holding A/S Groupe pompe centrifuge
US20230136689A1 (en) * 2020-03-20 2023-05-04 Jui-Cheng Chang Pump with variable suction/discharge amount and drive device composed of the pump and driving method thereof
CN112502998B (zh) * 2020-12-01 2022-08-05 石家庄栾兴泵业有限公司 一种低噪节能的双壳渣浆泵

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US2265806A (en) * 1939-05-15 1941-12-09 Goldschmied Livio Pump
DE1528798A1 (de) * 1961-06-14 1969-09-18 Regulator Ag Mit einem Verteilerventil baulich vereinigte Pumpe
DE2107000A1 (de) * 1971-02-13 1972-08-24 Loewe Pumpenfabrik Gmbh Kreiselpumpe, insbes. Heizungsumwälzpumpe
DE3002210A1 (de) 1980-01-22 1981-07-30 Herbert 7853 Steinen Hüttlin Pumpe oder geblaese, insbesondere fuer heizungs- und klimaanlagen
DE19523661A1 (de) * 1995-06-29 1997-01-02 Mayer Helmut Turborotor
DE10006396A1 (de) * 1999-05-06 2000-11-09 Eberspaecher J Gmbh & Co Heizsystem, insbesondere für Kraftfahrzeuge
DE10115989A1 (de) 2000-04-04 2001-12-13 Bernhard Stadler Radial-Strömungsmaschine, insbesondere Umwälzpumpe
JP2006214348A (ja) * 2005-02-03 2006-08-17 Toyota Motor Corp ポンプ装置、冷却システムおよび燃料電池システム
EP2228891A2 (fr) * 2009-03-10 2010-09-15 Wilo Se Moteur électrique destiné à actionner une soupape

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US2660366A (en) * 1950-05-03 1953-11-24 Klein Harold Compressor surge inhibitor
US3723019A (en) * 1971-05-21 1973-03-27 Worthington Corp Means to overcome low flow problems of inducers in centrifugal pumps
DE4020120A1 (de) * 1990-06-25 1991-01-31 Klaus Prof Dr Ing Affeld Medizinische vorrichtung zur erzeugung eines alternierenden volumenstroms fuer den antrieb von implantierbaren blutpumpen
WO2000068032A1 (fr) * 1999-05-06 2000-11-16 J. Eberspächer Gmbh & Co. Systeme de chauffage, notamment pour vehicules automobiles

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Publication number Priority date Publication date Assignee Title
US2265806A (en) * 1939-05-15 1941-12-09 Goldschmied Livio Pump
DE1528798A1 (de) * 1961-06-14 1969-09-18 Regulator Ag Mit einem Verteilerventil baulich vereinigte Pumpe
DE2107000A1 (de) * 1971-02-13 1972-08-24 Loewe Pumpenfabrik Gmbh Kreiselpumpe, insbes. Heizungsumwälzpumpe
DE3002210A1 (de) 1980-01-22 1981-07-30 Herbert 7853 Steinen Hüttlin Pumpe oder geblaese, insbesondere fuer heizungs- und klimaanlagen
DE19523661A1 (de) * 1995-06-29 1997-01-02 Mayer Helmut Turborotor
DE10006396A1 (de) * 1999-05-06 2000-11-09 Eberspaecher J Gmbh & Co Heizsystem, insbesondere für Kraftfahrzeuge
DE10115989A1 (de) 2000-04-04 2001-12-13 Bernhard Stadler Radial-Strömungsmaschine, insbesondere Umwälzpumpe
JP2006214348A (ja) * 2005-02-03 2006-08-17 Toyota Motor Corp ポンプ装置、冷却システムおよび燃料電池システム
EP2228891A2 (fr) * 2009-03-10 2010-09-15 Wilo Se Moteur électrique destiné à actionner une soupape

Also Published As

Publication number Publication date
CN105492776A (zh) 2016-04-13
US10539143B2 (en) 2020-01-21
EP2818726B1 (fr) 2017-08-23
CN105492776B (zh) 2018-01-19
US20160273543A1 (en) 2016-09-22
WO2014207031A1 (fr) 2014-12-31

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