EP3376049A1 - Groupe motopompe - Google Patents

Groupe motopompe Download PDF

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Publication number
EP3376049A1
EP3376049A1 EP17160830.0A EP17160830A EP3376049A1 EP 3376049 A1 EP3376049 A1 EP 3376049A1 EP 17160830 A EP17160830 A EP 17160830A EP 3376049 A1 EP3376049 A1 EP 3376049A1
Authority
EP
European Patent Office
Prior art keywords
valve element
impeller
centrifugal pump
pressure
suction
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.)
Pending
Application number
EP17160830.0A
Other languages
German (de)
English (en)
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 EP17160830.0A priority Critical patent/EP3376049A1/fr
Priority to CN201880018499.5A priority patent/CN110418898B/zh
Priority to PCT/EP2018/056207 priority patent/WO2018167043A1/fr
Priority to US16/492,795 priority patent/US11333151B2/en
Publication of EP3376049A1 publication Critical patent/EP3376049A1/fr
Pending legal-status Critical Current

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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction 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
    • 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
    • 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
    • F04D29/4273—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps suction eyes
    • 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
    • F04D29/4293—Details of fluid inlet or outlet
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/48—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps
    • F04D29/486—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible 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
    • F24D3/00—Hot-water central heating systems
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/105—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system pumps combined with multiple way valves

Definitions

  • the invention relates to a centrifugal pump unit with an electric drive motor and a valve element arranged in the pump unit, which is movable between at least two switching positions.
  • centrifugal pump units which at the same time include a valve device, which makes it possible to switch between two flow paths through which promotes the centrifugal pump unit.
  • valve devices which switch depending on the direction of rotation of the centrifugal pump assembly.
  • DE 9013992 U1 Such a centrifugal pump unit is known, which has a switching device, with the aid of which it is possible to switch between two inputs of the centrifugal pump assembly.
  • the centrifugal pump unit disclosed therein has a relatively complicated mechanism, which has an inflow element located on the pressure side, which is flowed by the output-side flow generated by the centrifugal pump unit and can be moved into two different positions depending on the flow direction.
  • a valve element is switched on the suction side of the pump unit between the two inputs.
  • the centrifugal pump assembly has an electric drive motor and at least one impeller, which is driven in rotation by this electric drive motor.
  • a rotor of the electric drive motor is connected to the impeller, for example via a shaft.
  • the impeller is arranged in a pump housing surrounding the impeller, which preferably limits the fluid-filled space to be conveyed outwards.
  • the pump housing has at least two connections, in particular two suction-side inputs and a pressure-side outlet. This means that the impeller preferably sucks a liquid from at least one of the two inlets and delivers it to the pressure-side outlet.
  • a movable valve element is arranged, which is movable between at least two switching positions, in which the flow paths through the two ports, in particular the two inputs are opened differently.
  • a pure switching can be provided, wherein in one of the two switching positions a first connection or input is opened and a second connection or input is closed, while in the second switching position the first connection or input is closed and the second connection or Input is open.
  • one or more switch positions provided are in which not one of the terminals or inputs is completely closed, but only the degree of opening of the two terminals or inputs to each other is changed so that, for example, in a first switching position, the first port or input is opened further than in a second switching position.
  • a mixing ratio of the flows through the first and second inputs between the two switching positions could be changed by movement of the valve element, ie the valve element acting as an adjustable mixing valve.
  • the valve element is designed and arranged in the pump housing such that it is located in the pump housing between the suction and pressure sides of the centrifugal pump assembly and separates them from one another.
  • the valve element is preferably arranged so that it separates a connected to a suction side of the impeller suction chamber, in which preferably open the two inputs, from one with the pressure side of the impeller and preferably with a connection as an outlet in communication pressure chamber. This means that the valve element adjoins both the suction chamber and the pressure chamber.
  • the valve element preferably has a suction chamber facing side, which comes into contact with the liquid in the suction chamber, and a pressure chamber facing side, which comes into contact with the liquid in the pressure chamber and is acted upon by the pressure in the pressure chamber. Due to the fact that the valve element adjoins both the pressure side and the suction side, on the one hand it becomes possible to utilize pressure differences between both sides for moving the valve element. On the other hand, further forces acting in the pressure space and / or in the suction space, in particular flow forces of the flowing liquid, can be used to actuate the valve element. In particular, it is possible to use forces prevailing in the pressure chamber and thus to perform a switching function on the suction side.
  • the valve element according to the invention is mechanically and / or hydraulically coupled to at least one movement between the at least two switching positions with the drive motor.
  • This coupling is favored by the arrangement of the valve element between the pressure and suction chamber.
  • the valve element on the one hand in the suction chamber with the two inputs interact to change the flow paths through these two inputs in the at least two switching positions.
  • the valve element is directly facing the pressure chamber or has a delimiting to the pressure chamber side on which the mechanical and / or hydraulic coupling can act to move the valve element. In this way, complicated mechanisms for coupling a flow chamber located in the pressure chamber with a located on the suction side valve element can be avoided. Rather, it is possible to apply the valve element directly in the pressure chamber with force to move it between the switching positions.
  • the valve element preferably has force application elements or force application surfaces facing the pressure chamber, against which the mechanical and / or hydraulic coupling acts.
  • the hydraulic coupling between drive motor and valve element can be carried out particularly preferably via the liquid in the pressure chamber.
  • the fluid is set in motion, for example, by the impeller itself and transmits the movement to the valve element. This can be done for example by prevailing between the valve element and the fluid frictional forces.
  • a friction prevailing in the pressure chamber of the fluid flowing there can be used on the walls delimiting the pressure chamber in order to move the valve element.
  • the valve element can be moved on its side facing the pressure chamber on the friction occurring there by a fluid flow. That's the way the movement works the valve element can be caused by otherwise loss-related energy loss.
  • the valve element between the at least two switching positions is rotatable. This allows a particularly simple motion coupling, since a rotational movement is generated anyway by the drive motor. For example, a flow rotating in the pressure chamber can act on the valve element and move it in rotation.
  • the axis of rotation about which the valve element is rotatable expediently extends parallel to the axis of rotation of the impeller and more preferably in alignment with the axis of rotation of the impeller, d. H. preferably substantially in extension of the axis of rotation of the impeller.
  • This ensures that the impeller or the rotor of the drive motor and the valve element rotate about the same axis.
  • a very simple hydraulic and / or mechanical coupling between the valve element and the drive motor or impeller is possible.
  • There are preferably no transmission elements required, d. H. on gears, levers or the like can be dispensed with.
  • the valve element is rotatably mounted in its center and rotatably mounted in particular in the pump housing independently of the impeller.
  • the valve element is furthermore preferably designed so that it is in contact with the pump housing in at least one position only via the central bearing and possibly required restoring elements (eg return springs) and, moreover, can rotate freely about this central bearing.
  • the central bearing is preferably designed such that the radius (outer radius) of the bearing surfaces is preferably less than a third, more preferably less than a quarter of the radius of the outer circumference of the valve element. This will be a very easy one Rotatability of the valve element by forces which attack attack outside of storage, since these forces act on a comparatively long lever on the storage.
  • a particularly smooth bearing of the valve element allows this can be moved by comparatively small forces between the at least two switching positions. This favors, for example, a hydraulic coupling between the drive motor and the valve element.
  • the valve element is rotatably mounted in the interior of the pump housing in a space filled with a fluid to be delivered or a fluid to be delivered.
  • the storage is "wet” so that the storage can be lubricated by the liquid itself.
  • the bearing can be sealed inside the pump housing by seals against the surrounding liquid.
  • such a seal may for example be designed so that it is not hermetically sealed, but lets through a certain small amount of liquid, which can then serve, for example, the lubrication of the bearing. In this case, however, impurities can be retained by the seal and it can thus be prevented that impurities enter the storage.
  • a sealing gap in the seal is preferably dimensioned so that the liquid to be delivered, for. As water, can pass through the sealing gap, but impurities such as particles are retained.
  • the storage may preferably be prelubricated, in particular also be permanently lubricated. That is, in the storage may be previously introduced a lubricant, which is then optionally diluted in the course of operation by the liquid inside the pump housing and / or replaced.
  • the valve element is designed and arranged such that it is movable along a first movement path between the at least two switching positions and is additionally movable in a second, second movement path extending at an angle to the first movement path.
  • the first movement path is preferably a rotary movement about an axis of rotation, as described above.
  • the second movement path is preferably a movement path which runs linearly, in particular along the axis of rotation or parallel to the axis of rotation of the valve element.
  • the valve element is preferably movable between a first position, in which it is objected to by at least one contact surface, and a second position, in which it is in contact with this contact surface.
  • the valve element In the first position, the valve element is preferably freely rotatable about a bearing in the manner described above. In the second position, it preferably comes with the contact surface, which may be formed in particular on the pump housing to the plant. By this system, preferably, the further rotational movement can be prevented and / or a seal can be realized.
  • At least one damping means can be provided, which is connected to the valve element or cooperates and is designed such that a movement of the valve element along the second movement path is damped or delayed.
  • the damping can act on a movement from the first position to the second position and / or during a movement from the second position to the first position.
  • an effect is at least in the movement from the second position to the first position. This ensures that a disengagement is delayed from the at least one contact surface and so the valve element longer in a fixed non-rotatable Position is held.
  • the second movement path of the valve element preferably runs parallel to or along the axis of rotation of the impeller, which, as described above, is further preferably aligned with the axis of rotation of the valve element.
  • the valve element can be acted upon by a restoring element, for example a restoring spring, with a restoring force which acts along the second movement path and preferably in the direction of the first position.
  • the restoring element endeavors to move the valve element back into an initial position, wherein the initial position is preferably the first position, in which, more preferably, the valve element is freely rotatable. It can thus be achieved that, when the drive motor is switched off, the valve element, after the forces and moments generated by the impeller have subsided, is returned to the first position by the return element.
  • the valve element has a pressure surface facing the pressure chamber, to which the pressure prevailing in the pressure chamber pressure acts such that the valve element along the second Movement path is subjected to a compressive force, which preferably acts in the direction of the second position.
  • the pressure force thus preferably counteracts a restoring force.
  • the described at least one contact surface is at least one sealing surface.
  • This may in particular be a sealing surface, which is situated in such a way that the pressure region is sealed against the suction region by abutment of the valve element on the sealing surface.
  • at least one sealing surface may be provided and located in such a way that one of the connections and in particular one of the inlets opposite the suction space is sealed by contact of the valve element with this sealing surface.
  • valve element is only in the second position in sealing contact with the sealing surfaces or, it is achieved that in the first position, the sealing surfaces can disengage and thus reduces the ruling on the valve element friction forces in the first position be so that it is slightly movable between its at least two switch positions in the first position.
  • the at least one contact surface extends angled to the second path of movement, d. H. a force prevailing in the direction of the movement path can lead to a pressure force on the contact surface.
  • a force prevailing in the direction of the movement path can lead to a pressure force on the contact surface.
  • the valve element is mechanically and / or hydraulically coupled to the drive motor for its movement.
  • the valve element can be moved by the drive motor between the at least two switching positions, wherein more preferably, depending on the direction of rotation of the drive motor, the valve element is moved into one of the two switching positions.
  • a stop can be provided in each of the switching positions, which prevents further movement of the valve element in the same direction.
  • a first embodiment can be taken depending on the desired switching position of the valve element of the drive motor only in the desired direction of rotation in operation, depending on the design of the impeller optionally different efficiencies for the two directions of rotation can be achieved.
  • the movement of the valve element in the second direction of movement can, for. B. can be achieved that the valve element is first moved by the drive motor in a first switching position by the drive motor is rotated in the direction of this switching position. As a result of the pressure building up in the pressure chamber, the valve element is preferably moved to its second position.
  • a force generating means which exerts a force on the at least one valve element in the direction of one of the at least two switching positions, the force preferably being a spring force, a magnetic force and / or gravity.
  • a force generating means can be dispensed with the direction of rotation of the drive motor.
  • the valve element can be moved in one of the two switching positions by the drive motor and then when switching off the drive motor by the force generating means back to the other switching position, which represents a starting position, are moved.
  • the drive motor can be configured such that it can be put into operation in this starting position so quickly that a pressure builds up in the pressure space, which pressure is applied to the valve element along the second movement path presses the contact surface before the valve element can be moved by a building up in the pressure chamber flow in its second switching position.
  • the drive motor is correspondingly slowly put into operation, the flow can first build up, which moves the valve element into the second switching position before the pressure is sufficiently great to press the valve element against the contact surface along the second movement path. This can be achieved by suitable control of the drive motor via a control device activating the drive motor.
  • the valve element is preferably configured such that it can be moved by a fluid flow running in the pressure space in the direction of rotation of the impeller and / or that the valve element is coupled to move with the impeller or a shaft driving the impeller via a coupling is, which is preferably pressure and / or speed and / or rotational direction dependent solvable.
  • the drive via the fluid flow rotating in the pressure chamber can preferably take place in such a way that this fluid flow acts by frictional forces on a surface of the valve element facing the pressure chamber.
  • this surface of the valve element can be provided with drivers, in particular with blades.
  • Such blades can more preferably simultaneously serve as a guide to deflect the radially outgoing from the impeller flow in a desired direction.
  • the impeller is freely rotatable, its flow can also act on the suction side and cause a rotation of the valve element.
  • the inputs on the suction side or in the suction chamber can be placed so that they direct the flow in the suction chamber so that they support a rotation or movement of the valve element in a desired direction.
  • the valve element can according to a particular embodiment also on the suction side facing surface with corresponding driving elements or blades are provided, on which a flow in the suction chamber can act to move the valve element.
  • the pressure chamber facing surface of the valve element is preferably designed so large that an outer diameter of this surface of the valve element is at least two to five times as large as the diameter of the suction mouth of the impeller.
  • the pressure chamber facing surface of the valve element thus surrounds the suction mouth preferably annular.
  • the at least one valve element is designed and arranged such that in the pressure chamber, a flow generated by the impeller acts on the valve element to move between the at least two switching positions and the suction chamber is configured such that the prevailing flow there is no force exerts on the valve element in the direction of movement between the switching positions. That is, according to this embodiment, the valve element is formed on its side facing the suction chamber as smooth as possible and without force application surfaces on which the flow could act. This configuration prevents the flow or the liquid in the suction chamber from braking or preventing the movement of the valve element between the switching positions.
  • a mechanical coupling may be provided by a suitable coupling.
  • the coupling can act positively and / or positively.
  • the coupling is preferably designed so that it can be mechanically disengaged. This can be done for example by the movement of the valve element along the second movement path, as described above. So would a pressure-dependent releasable coupling created.
  • a speed-dependent releasable design could be realized, for example, by forming a lubricating film between the coupling surfaces at sufficiently high speed, which cancels the friction clutch. Such a design would overcome the friction between the clutch surfaces in the manner of a plain bearing at a sufficiently high speed.
  • a direction-dependent acting clutch could for example be realized by correspondingly shaped driver, which occur only in one direction of rotation in positive engagement and slide along in the opposite direction of rotation to each other.
  • This could be an embodiment in the manner of a pawl or ratchet.
  • the valve element would always moved only in one direction of rotation of the drive motor in a desired switching position. After reaching the switching position of the drive motor could then be taken in the opposite direction of rotation in operation to start the delivery operation of the centrifugal pump assembly. In this opposite direction of rotation, the clutch then disengages and the valve element can thus remain in the previously assumed switching position.
  • the valve element has an opening, via which the suction chamber communicates with a suction mouth of the impeller.
  • the suction orifice of the impeller may preferably be in contact or in engagement with the valve element in the peripheral region of the opening in order to achieve a seal with respect to the pressure space delimited by the valve element.
  • the suction mouth of the impeller may for example be surrounded by a collar which engages in the opening of the valve element.
  • the opening of the valve element could be surrounded by a collar, which overlaps with a collar on the impeller surrounding the suction mouth. So can a seal between the valve element and Suction mouth can be achieved.
  • the part of the valve element which surrounds the opening can face the pressure space or limit the pressure space in which the impeller rotates.
  • the opposite surface of the valve element faces the suction chamber, so that the valve element suction and pressure chamber in the vicinity of the suction mouth of the impeller separates from each other.
  • the drive motor is controlled via a control device such that it can be driven in two directions of rotation and / or is preferably adjustable in its rotational speed.
  • the control device can for this purpose have a speed controller and in particular a frequency converter for rotating direction and / or speed setting.
  • the change in the rotational speed is preferably possible in such a way that the acceleration during startup and deceleration of the drive motor can be varied in order to realize different acceleration characteristics.
  • the control device is designed in such a way that it can accelerate and / or decelerate the drive motor to different degrees by, for example, selecting corresponding ramps for acceleration and / or deceleration.
  • the centrifugal pump unit according to the invention is preferably a circulating pump unit, in particular a circulating pump unit, as used in heating and / or air conditioning systems for circulating a heat carrier.
  • a circulating pump unit is preferably designed for the promotion of water as a heat transfer medium.
  • the electric drive motor is preferably a wet-running electric drive motor, ie a canned motor in which a split tube or split pot separates the stator from the rotor, so that the rotor rotates in the liquid to be conveyed.
  • centrifugal pump assembly according to the invention described in the following description relate to applications in heating and / or air conditioning systems, in which of the centrifugal pump unit, a liquid heat carrier, in particular water, is circulated.
  • the centrifugal pump unit according to the first embodiment of the invention has a motor housing 2, in which an electric drive motor is arranged.
  • This has in known manner a stator 4 and a rotor 6, which is arranged on a rotor shaft 8.
  • the rotor 6 rotates in a rotor space, which is separated from the stator space in which the stator 4 is arranged by a split tube or a split pot 10. That is, it is a wet-running electric drive motor.
  • the motor housing 2 is connected to a pump housing 12, in which a rotatably connected to the rotor shaft 8 impeller 14 rotates.
  • an electronics housing 16 is arranged, which is a control electronics or control device for controlling the electrical Drive motor in the pump housing 2 includes.
  • the electronics housing 16 could also be arranged in a corresponding manner on another side of the stator housing 2.
  • a movable valve element 18 is arranged in the pump housing 12.
  • This valve element 18 is rotatably mounted on an axis 20 in the interior of the pump housing 12, in such a way that the axis of rotation of the valve element 18 is aligned with the axis of rotation X of the impeller 14.
  • the axis 20 is rotatably fixed to the bottom of the pump housing 12.
  • the valve element 18 is not only rotatable about the axis 20, but by a certain amount in the longitudinal direction X movable. In one direction, this linear mobility is limited by the pump housing 12, against which the valve element 18 abuts with its outer circumference. In the opposite direction, the mobility is limited by the nut 22, with which the valve element 18 is mounted on the axle 20. It should be understood that instead of the nut 22, another axial attachment of the valve member 18 to the axle 20 could be selected.
  • the valve element 18 separates in the pump housing 12 a suction chamber 24 from a pressure chamber 26.
  • the pressure chamber 26 rotates the impeller 14.
  • the pressure chamber 26 is connected to the pressure connection or discharge nozzle 27 of the centrifugal pump assembly, which forms the outlet of the centrifugal pump assembly.
  • In the suction chamber 24 open two suction-side inputs 28 and 30, of which the input 28 is connected to a first suction port 32 and the input 30 to a second suction port 34 of the pump housing 12.
  • the valve element 18 is disc-shaped and at the same time performs the function of a conventional deflector plate, which separates the suction chamber 24 from the pressure chamber 26.
  • the valve element 18 has a central suction opening 36, which has a protruding having circumferential collar which is in engagement with the suction mouth 38 of the impeller 14 and is substantially in close contact with the suction mouth 38. Facing the impeller 14, the valve member 18 is formed substantially smooth.
  • the valve element On the side facing away from the impeller 14, the valve element has two annular sealing surfaces 40, which are located in this embodiment on closed tubular nozzle.
  • the two annular sealing surfaces 40 are arranged at two diametrically opposite positions on the sealing element 18 with respect to the axis of rotation X, so that they can in the peripheral region of the inputs 28 and 30 at the bottom of the pump housing 12 in tight contact with each other to close the inputs 28 and 30.
  • support members 42 are arranged, which can also come to rest on the peripheral portion of the inputs 28, 30, but are spaced apart so that they do not close the inputs 28, 30 then.
  • the inputs 28 and 30 are not on a diameter line with respect to the axis of rotation X, but on a radially offset straight line, so that upon rotation of the valve element 18 about the rotation axis X in a first switching position, the input 38 is closed by a sealing surface 40, while the support elements 42nd lie at the entrance 30 and open it. In a second switching position, the input 30 is closed by a sealing surface 40, while the support elements 42 abut in the peripheral region of the input 28 and open it.
  • the first switching position in which the input 38 is closed and the input 30 is opened, is in Fig. 5 shown.
  • the second switching position, in which the input 30 is closed and the input 28 is open is in Fig. 6 shown. This means, by a rotation of the valve element by 90 ° about the axis of rotation X can be switched between the two switching positions.
  • the two switching positions are limited by a stop element 44 which abuts alternately on two stops 46 in the pump housing 12.
  • a spring 48 pushes the valve member 18 in a disengaged position in which the outer periphery of the valve member 18 is not close to the pump housing 12 and the sealing surfaces 40 not tight in the peripheral region of the inputs Abut 28 and 30, so that the valve element 18 can rotate about the axis 20.
  • the drive motor is rotated by the control device 17 in the electronics housing 16, so that the impeller 14 rotates, a circulating flow is generated in the pressure chamber 26, which rotates the valve element 18 in its direction of rotation via friction.
  • the control device 17 is designed so that it can selectively drive the drive motor in two directions of rotation.
  • valve element 18 about the rotational axis X depending on the direction of rotation of the impeller 14 on the offset from the impeller 14 in rotation flow can also be moved in two directions, since the flow in the peripheral region of the impeller 14 always runs in the direction of rotation.
  • the valve element 18 can be rotated between the two limited by the stops 46 switching positions.
  • the support elements 42 come to rest, so that this input remains open and a flow path from this input 28, 30 to the suction port 36 and from there into the interior the impeller 14 is given.
  • a frictional engagement between the valve element 18 and the pump housing 12 is simultaneously created. This frictional engagement ensures that the valve element 18 is held in the achieved switching position. This makes it possible to temporarily take the drive motor out of operation again and to put it back into operation in the opposite direction of rotation, without the valve element 18 being rotated.
  • the described centrifugal pump assembly according to the first embodiment of the invention can be used, for example, in a heating system as shown in FIG Fig. 7 is shown.
  • a heating system is commonly used in homes or homes and is used to heat the building and to provide heated service water.
  • the heating system has a heat source 52, for example in the form of a gas boiler.
  • a heating circuit 54 is present, which leads, for example, by different radiators of a building.
  • a secondary heat exchanger 56 is provided, via which service water can be heated.
  • a switching valve is required, which selectively directs the heat transfer stream through the heating circuit 54 or secondary heat exchanger 56.
  • this valve function by the valve element 18, which is integrated into the centrifugal pump unit 1, taken over.
  • the control is carried out by the control device 17 in the electronics housing 16.
  • the heat source 52 is connected.
  • a flow path 58 is connected, while to the suction port 34, a flow path 60 is connected through the heating circuit 54.
  • the second embodiment according to Fig. 8 to 10 differs from the first embodiment in the construction of the valve element 18 '.
  • the valve element 18 ' separates the pressure chamber 26 from a suction chamber 24 of the pump housing 12.
  • the valve element 18 has a central suction opening 36', in which the suction port 38 of the impeller 14 sealingly engages.
  • the valve element 18 ' Opposite the suction opening 36, the valve element 18 'has an opening 62 which, depending on the switching position of the valve element 18', can optionally be brought to coincide with one of the inputs 28, 30.
  • the inputs 28 ', 30' in this embodiment differ in their shape from the inputs 28, 30 according to the previous embodiment.
  • the valve element 18 ' has a central projection 64, which engages in a central hole 60 in the bottom of the pump housing 12 and is rotatably mounted there about the axis of rotation X. At the same time, the projection 64 in the hole 66 also allows axial movement along the axis of rotation X, which is limited in one direction by the bottom of the pump housing 12 and in the other direction by the impeller 14. On its outer circumference, the valve element 18 'has a pin 68 which engages in a semicircular groove 70 at the bottom of the pump housing 12.
  • the ends of the groove 70 serve as abutment surfaces for the pin 68 in the two possible switching positions of the valve element 18 ', wherein in a first switching position, the opening 62 via the input 28' and in a second switching position the opening 62 on the input 30 'and the other input through the bottom of the valve element 18 'is closed.
  • the rotational movement of the valve element 18 'between the two switching positions also takes place in this embodiment by the flow caused in the pressure chamber 26 by the impeller 14.
  • projections 72 directed in the pressure space 26.
  • the third embodiment according to Fig. 11 to 13 shows a further possible embodiment of the valve element 18 ".
  • This embodiment differs from the preceding embodiments in the construction of the valve element 18".
  • This is designed as a valve drum.
  • the pump housing 12 substantially corresponds to the structure according to Fig. 1 to 6
  • the arrangement of the inputs 28 and 30 corresponds to the arrangement described with reference to the first embodiment.
  • the valve drum of the valve element 18 " consists of a cup-shaped lower part, which is closed by a cover 78.
  • the cover 78 faces the pressure chamber 26 and has the central suction opening 36, which engages with its axially directed collar in the suction port 38 of the impeller 14.
  • the bottom of the lower part 36 an inlet opening 80, which is brought depending on the switching position with one of the inputs 28, 30, while the respective other input 28, 30 is closed by the bottom of the lower part 26.
  • the valve element 18 is rotatably mounted on an axis 20 which is fixed in the bottom of the pump housing 12, wherein the axis of rotation, which is defined by the axis 20, the axis of rotation X of the impeller 14 corresponds. Also in this embodiment, the valve element 18 "along the axis 20 to a certain extent axially displaceable, whereby also a spring 48 is provided, which in the rest position the valve element 18" in his in Fig. 13 shown released position presses. This axial position is limited in this embodiment by the nut 22.
  • valve element 18 " In the released position, the valve element 18 ", as described above, by the flow, which is caused by the impeller 14, rotatable, that is, there is a hydraulic coupling between the impeller 14 and valve element 18" made. In the adjacent position, which in Fig. 12 is shown, depending on the switching position to one of the inputs 28, 30 sealed. On the other hand, there is also a seal between the suction chamber 24 and the pressure chamber 26 by the contact of the valve element 18 "on the abutment shoulder 50th
  • the bearing of the valve element 18 "on the axis 20 is further encapsulated by two sleeves 82 and 84, so that these areas are protected from contamination by the pumped fluid and can optionally be pre-lubricated. to the easy rotation of the valve element 18 "through the to ensure flow caused by the impeller 14. It should be understood that even with the other embodiments described herein, the storage could be suitably encapsulated.
  • Fig. 14 and 15 show a fourth embodiment in which the structure of the pump housing 12 corresponds to the structure of the pump housing 12 according to the first and the third embodiment.
  • the rotational movement of the valve element 18c by the suction-side flow that is, the entering into the suction port 38 of the impeller 14, supported flow.
  • the valve element 18c is formed substantially drum-shaped and has a pressure chamber 26 facing the cover 28 with the central suction opening 36, which with the suction mouth 38, as described above, is engaged.
  • the lower part shown here 76b has two inlet openings 80, which can be brought to cover depending on the switching position with one of the inputs 28, 30, wherein the respective other input 28, 30 is sealed by the bottom of the lower part 46b, as in the preceding Embodiment has been described.
  • a guide wheel 86 is arranged with blades, in which the flow from the inlet openings 80 enters radially and axially to the central suction opening 36 exits.
  • a torque is also generated about the axis 20, through which the valve element 18c can be moved between the switching positions. This essentially works as described above.
  • a spring 48 may also be provided to move the valve element 18c to a released position. Since the shape of the blades of the stator 86 always generates a torque in the same direction, regardless of which direction the impeller 14 rotates, in this embodiment, the return movement by a weight 88. Im Operation, the centrifugal pump unit is always in the installation position, which in Fig. 15 is shown, in which the rotation axis X extends horizontally. When the centrifugal pump assembly is turned off, the valve member 18c always rotates about the axis 20 so that the weight 88 is below.
  • valve element 18c By the torque generated by the stator 86, the valve element 18c can be rotated against this restoring force generated by the weight 88, whereby by rapid commissioning of the drive motor in the pressure chamber 26 so quickly a pressure can be built up that the valve element 18c in its adjacent position occurs, as described above, in which it is non-positively rotatably held on the pump housing 12 without being moved out of its rest position. It should be understood that a provision of the valve member by gravity or other restoring force regardless of the drive could also be used in the other embodiments described herein.
  • the fifth embodiment according to Fig. 16 to 18 differs from the preceding embodiments again in the construction of the valve element.
  • the valve element 18d is conical.
  • the valve element 18d has a conical cup-shaped lower part 76d, which is closed by a cover 78d, wherein in the lid 78d in turn a central suction opening 36 is formed, which in the manner described above with the suction port 38 of the impeller 14 is engaged.
  • entrance ports 90 which can be selectively made to overlap by rotating the valve element 18d having entrances connected to the suction ports 32 and 34 to a flow path through the inside of the valve element 18d to the suction port 36 produce.
  • valve element 18d has a pin-shaped projection 64, which engages in a recess at the bottom of the pump housing 12 and there rotatably supports the valve element 18d about the axis of rotation X.
  • a released position as in Fig. 18 is shown, and an adjacent position, as in Fig. 17 shown is possible.
  • the lower part 76d of the valve element 18d is substantially not abutted on the pump housing 12, so that it is rotatable by the flow in the pressure chamber 26, as described in the embodiments described above.
  • a reciprocating movement of the valve element 18d can be achieved, wherein the rotational movement of the valve element 18d can also be limited here by stops, not shown.
  • the adjacent position according to Fig. 17 on the one hand there is a tight contact of the valve element 18d, on the other hand it is frictionally held, so that in turn, as long as the pressure in the pressure chamber 26 is sufficiently large, even with a change of direction of the impeller 14 is not moved between the switching positions.
  • the sixth embodiment according to Fig. 19 to 22nd is similar to the embodiment 2 according to Fig. 8 to 10 ,
  • the pump housing 12 essentially corresponds to the structure shown and described there.
  • the motor housing 2 with the electronics housing 16 and the can 10 correspond to the structure according to the second embodiment.
  • the valve element 18e has a very similar structure to the construction of the valve element 18 '. It lacks only the projections 72 and the pin 74.
  • the opening 62 is designed in the same way.
  • the suction port 36e substantially corresponds to the structure of the suction port 36 '.
  • the valve member 18e is rotatably supported on a hollow shaft which enters the hole 66 in the bottom of the Pump housing 12 is inserted.
  • the spring 48 is disposed inside the hollow axle 94.
  • valve element 18e is additionally movable axially along the axis of rotation X, which is the axis of rotation of the impeller 14 and of the valve element 18e.
  • Fig. 21 shows the first switching position, in which the opening 62 opposite the input 28 '
  • Fig. 22 shows the second switching position in which the opening 62 opposite the second input 30 '.
  • valve element 18e again via the impeller 14, but here a mechanical coupling is provided, which is realized in that the impeller 14 comes frictionally with its surrounding the suction mouth 38 area on the circumference of the suction port 36e to rest.
  • the valve element 18e is rotated with the impeller 14 until the pin 68 reaches a stop.
  • the clutch disengages due to slip.
  • the valve element 18e is then moved axially, as described above, into its abutting position, the clutch being disengaged from the impeller 14 occurs, so that the impeller 14 can then rotate substantially frictionless.
  • the seventh embodiment according to Fig. 23 and 24 differs from the sixth embodiment described above in that on the valve element 18f extending into the pressure chamber 26 into a tongue 96 is arranged, which serves in the pressure chamber 26 as an additional valve element.
  • the pump housing 12 has an additional pressure port 98, which opens separately to the pressure port 27 into the pressure chamber 26.
  • the tongue 96 can, depending on the switching position of the valve element 18f, release the pressure port 27 or the pressure port 28 and cover the respective other pressure port.
  • a pressure-side switching on the pressure side of the impeller 14 is provided.
  • a mixing function can be realized simultaneously via the inputs 28 'and 30' in that the opening 92 is positioned such that it covers these two inputs 28 ', 30' in a first switching position, so that liquid from both inputs 28 ', 30' passes through the opening 62 and further through the suction mouth 38 flows.
  • the opening 62 covers only the input 28 ', while the input 30' is closed in the manner described above from the bottom of the valve element 18f.
  • the pressure port 27 is closed and the pressure port 98 released.
  • the movement of the valve element 18f can be realized in the manner described above via the impeller 14 and a mechanical coupling, which disengages by axial displacement of the valve element 18f at sufficiently high pressure in the pressure chamber 26.
  • the valve element 18f is mounted on the rotor shaft 8.
  • the eighth embodiment according to Fig. 25 to 28 differs from the sixth embodiment in the design of the mechanical Coupling between the rotor shaft 8 and the valve element 18g.
  • the valve element 18 g is mounted directly on the rotor shaft 8, which is formed extended and extends into the hole 66 in the bottom of the pump housing 12.
  • two ring segments 100 with slide bearing properties, in particular of ceramic, are arranged inside the valve element 18g.
  • the ring segments 100 are held together by a clamping ring 102 and pressed against the rotor shaft 8.
  • the two ring segments 100 in this example essentially form a 2/3 ring.
  • valve element 18g engages with a projection 104 on its inner circumference, so that the two ring segments 100 are arranged in a rotationally fixed manner in the interior of the valve element 18g.
  • a passage 106 which effects the valve function, remains in the valve element 18g.
  • the passage 106 may in a first switching position, which in Fig. 27 is shown, the input 30 'opposite and in a second switching position, which in Fig. 28 is shown, the input 28 'opposite.
  • the other entrance is closed in each case.
  • the valve element 18g according to the above-described embodiments of the pressure prevailing in the pressure chamber 26 pressure in the axial direction in abutment against the inputs 28 'and 30' surrounding the bottom of the pump housing 2.
  • the rotor shaft 8 is at the start non-positively on the inner circumference of the ring segments 10 and rotates these and thus the valve element 18g with.
  • stops in the pump housing 12 may be formed in the manner described above. If the valve element 18g reaches one of these stops, the pump shaft 8 slips inside the ring segments 100. With Increasing speed of the rotor shaft 8 may also form a lubricant film in the manner of a sliding bearing between the outer circumference of the rotor shaft 8 and the inner surfaces of the ring segments 100, so that the rotor shaft 8 can then rotate substantially frictionless in the interior of the ring segments 100.
  • valve element 18g for adjusting the valve element 18g between its two switching positions of the drive motor is preferably moved by the control device 17 at a lower speed than the speed at which the impeller 14 is rotated during operation.
  • the drive motor can be driven in the manner described above in two directions of rotation, in turn, after reaching the desired switching position in the manner described above can be achieved by rapid speed increase, that the valve element 18g due to the Pressure in the pressure chamber 26 and its system at the bottom of the pump housing 12 remains in the previously reached switching position.
  • a mechanical coupling between the drive motor and the valve element is also provided, wherein in these embodiments, the drive motor of the control device 17 in two different operating modes or operating modes can be controlled.
  • a first mode which corresponds to the normal operation of the circulating pump unit
  • the drive motor rotates in a conventional manner with a desired, in particular adjustable by the control device 17, speed.
  • the second operating mode the drive motor is activated in open-loop mode, so that the rotor can be rotated incrementally in individual angular steps which are smaller than 360 °.
  • the drive motor in the manner of a stepping motor can be moved in individual steps, which is used in these embodiments, the valve element targeted in small angular increments to move to a defined position, as described below.
  • a mixing valve as it can be used for example for temperature adjustment for underfloor heating.
  • the motor housing 2 with the electronics housing 16 corresponds to the embodiment described above.
  • the pump housing 12 is constructed substantially the same as the pump housing according to the first embodiment Fig. 1 to 6 , only the outer configuration is different.
  • the valve element 18h is also drum-shaped in this ninth embodiment and consists of a cup-shaped lower part 76h, which is closed on its side facing the impeller 14 by a cover 78h. In the central region of the lid 78h, a suction opening 36 is formed.
  • the valve element 18 h is rotatably mounted on an axis 20, which is arranged in the bottom of the pump housing 12. In this case, the axis of rotation of the valve element 18h, as in the examples described above, corresponds to the axis of rotation X of the rotor shaft 8h.
  • valve element 18h is also axially displaceable along the axis X and by a spring 48 in the in Fig. 33 shown rest position, in which the valve element 18h is in a released position in which the lower part 76h is not applied to the bottom of the pump housing 12, so that the valve element 18h is substantially freely rotatable about the axis 20.
  • the front end of the rotor shaft 8 h which is designed as a coupling 108.
  • the clutch 108 engages with a counter-coupling 110, which is non-rotatably arranged on the valve element 18h in engagement.
  • the coupling 108 has tapered coupling surfaces, which essentially describe a sawtooth profile along a circumferential line in such a way that torque transmission takes place only in one direction of rotation from the coupling 108 to the counter-coupling 110 is possible, namely in the direction of rotation A in Fig. 31 , In the opposite direction of rotation B, however, the clutch slips through, resulting in an axial movement of the valve element 18h.
  • the direction of rotation B is the direction of rotation in which the pump unit is driven in normal operation.
  • the direction of rotation A is used for targeted adjustment of the valve element 18h. That is, here is a direction of rotation dependent coupling is formed.
  • the mating coupling 110 of the clutch 108 by the pressure in the pressure chamber 26 disengaged. If the pressure in the pressure chamber 26 increases, a pressure force which opposes and exceeds the spring force of the spring 48 acts on the cover 78h, so that the valve element 18h is pressed into the abutting position, which in FIG Fig. 32 is shown.
  • the lower part 76h is located on the bottom side of the pump housing 12, so that on the one hand the valve element 18h is frictionally held and on the other hand a tight contact is achieved, which seals the pressure and the suction side in the manner described below against each other.
  • the pump housing 12 has two suction ports 32 and 34, of which the suction port 32 opens at an inlet 28h and the suction port 34 at an inlet 30h in the bottom of the pump housing 12 in its interior, that is, the suction chamber 24 inside.
  • the lower part 76h of the valve element 18h has in its bottom an arcuate opening 112 which extends substantially through 90 °.
  • Fig. 34 shows a first switching position in which the opening 112 covers only the input 30h, so that a flow path is given only from the suction port 34 to the suction port 36 and thus to the suction port 38 of the impeller 14.
  • the second input 28 h is sealed by the voltage applied in its peripheral region bottom of the valve element 18 h.
  • FIG. 36 shows the second switching position in which the opening 112 covers only the input 28h, while the entrance is closed 30h. In this switching position, only one flow path from the suction port 32 to the suction mouth 38 is opened.
  • Fig. 35 now shows an intermediate position in which the opening 112 covers both inputs 28h and 30h, the input 30h is only partially released.
  • a mixing ratio between the flows from the inputs 28h and 30h can be changed.
  • the valve element 18h can also be adjusted in small steps in order to change the mixing ratio.
  • the centrifugal pump assembly with the integrated valve, as described above, characterized by the dashed line 1.
  • the hydraulic circuit has a heat source 114 in the form of, for example, a gas boiler, whose outlet opens into, for example, the suction port 34 of the pump housing 12.
  • a floor heating circuit 116 connects to the pressure connection 27 of the centrifugal pump assembly 1, the return of which is connected both to the inlet of the heat source 114 and to the suction connection 32 of the centrifugal pump unit.
  • a further heating circuit 120 can be supplied with a heat carrier, which has the output-side temperature of the heat source 114.
  • the floor heating circuit 116 can be regulated in its flow temperature in such a way that cold water from the return to the hot water on the output side of the heat source 114 is mixed, by changing the opening ratios of the inputs 28h and 30h in the manner described above, the mixing ratio Rotation of the valve element 18h can be changed.
  • the tenth embodiment according to FIGS. 38 to 47 shows a centrifugal pump unit, which in addition to the above-described mixer functionality still has a switching functionality for additional supply of a secondary heat exchanger for domestic water heating.
  • valve element 18i has, in addition to the opening 112, a passage 122 which extends from an opening 124 in the lid 78i to an opening in the bottom of the base 76i and thus connects the two axial ends of the valve element 18i. Further, in the valve element 18i is still an only to the bottom, that is, to the bottom of the lower part 76i and thus open to the suction chamber 24 toward arcuate bridging opening 126 is formed, which is closed to the pressure chamber 26 through the lid 78i.
  • the pump housing 12 has, in addition to the pressure port 27 and the two previously described suction ports 34 and 32, a further port 128.
  • the port 128 opens into an inlet 130 in the bottom of Umisselzpumpenaggregates 12 in addition to the inputs 28h and 30h in the suction chamber 24 into it.
  • FIGS. 43 to 46 the various switching positions are explained, in which case the lid 78i of the valve element 18i is shown partially opened to illustrate the position of the underlying openings.
  • Fig. 43 shows a first switching position, in which the opening 112 facing the input 30h, so that a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is made. In the switching position according to Fig.
  • the opening 112 is above the inlet 130, so that a flow connection from the port 128 to the suction port 36 and via this into the suction mouth 38 of the impeller 14 is created.
  • the opening 112 is located above the entrance 30h, so that in turn a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is given.
  • a partial overlap of the opening 124 and the through-hole 122 with the input 28h takes place, so that a connection between the pressure chamber 26 and the suction port 32 is made, which acts as a pressure port.
  • the bypass opening 126 concurrently covers the input 130 and a portion of the input 28h, thus also providing a connection from the terminal 128 via the input 130, the bypass opening 126 and the input 28h to the terminal 32.
  • Fig. 46 shows a fourth switching position in which the passageway 122 completely covers the entrance 28h, so that the connection 32 is connected via the through-passage 122 and the opening 124 to the pressure space 26. At the same time, the bridging opening 126 only covers the entrance 130. The opening 112 also covers the entrance 30h.
  • the heating system in turn has a primary heat exchanger or a heat source 114, which may be, for example, a gas boiler.
  • a first heating circuit 120 On the output side of the flow path is in a first heating circuit 120, which may be formed for example by conventional radiators or radiators.
  • a flow path branches off to a secondary heat exchanger 56 for heating service water.
  • the heating system further includes a floor heating circuit 116.
  • the connection 32 of the pump housing 12 is connected to the flow of the underfloor heating circuit 116.
  • the impeller 14 promotes liquid from the suction port 34 via the pressure port 27 through the heat source 140 and the heating circuit 120 and back to the suction port 34.
  • the valve element 18i in the second switching position which in Fig. 44 is shown, the plant is switched to domestic water operation, in this state, the pump assembly or the impeller 14 promotes liquid from the port 128, which serves as a suction port, through the pressure port 27, via the heat source 114 through the secondary heat exchanger 56 and back to the terminal 128.
  • the valve element 18i in the third switching position which in Fig. 45 is shown, the underfloor heating circuit 116 is additionally supplied.
  • the water flows into the suction mouth 38 of the impeller 14 and is conveyed via the pressure connection 27 via the heat source 114 in the manner described by the first heating circuit 120.
  • the liquid emerges on the output side of the impeller 14 from the pressure chamber 26 into the opening 124 and through the through-passage 122 and thus flows to the connection 32 and via this into the underfloor heating circuit 116.
  • Fig. 45 The switch position shown flows simultaneously via the bridging opening 126 liquid via the terminal 128 and the input 130 into the terminal 32. That is, here water flows through the heat source 114 through the secondary heat exchanger 26 and the terminal 128 to the terminal 32. Since in this heating operation on Secondary heat exchanger 56 substantially no heat removed is, the port 32 hot water in addition to the cold water, which flows from the pressure chamber 26 via the passage 122 to the terminal 32, mixed. By varying the degree of opening via the valve position 18i, the amount of hot water mixed in at port 32 can be varied.
  • Fig. 46 shows a switching position in which the admixture is turned off and the terminal 32 is exclusively in communication with the pressure chamber 26 directly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP17160830.0A 2017-03-14 2017-03-14 Groupe motopompe Pending EP3376049A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17160830.0A EP3376049A1 (fr) 2017-03-14 2017-03-14 Groupe motopompe
CN201880018499.5A CN110418898B (zh) 2017-03-14 2018-03-13 泵机组
PCT/EP2018/056207 WO2018167043A1 (fr) 2017-03-14 2018-03-13 Groupe motopompe
US16/492,795 US11333151B2 (en) 2017-03-14 2018-03-13 Pump assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17160830.0A EP3376049A1 (fr) 2017-03-14 2017-03-14 Groupe motopompe

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EP (1) EP3376049A1 (fr)
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WO (1) WO2018167043A1 (fr)

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EP3904689A1 (fr) 2020-04-28 2021-11-03 Grundfos Holding A/S Ensemble pompe centrifuge
EP3904738A1 (fr) 2020-04-28 2021-11-03 Grundfos Holding A/S Dispositif de soupape hydraulique et ensemble e pompe centrifuge comprenant un tel dispositif de soupape hydraulique
CN115337695A (zh) * 2022-08-30 2022-11-15 奇力士（武汉）智慧水务科技有限公司 一种用于变频器水冷循环的过滤装置

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EP3929445A1 (fr) * 2020-06-22 2021-12-29 Grundfos Holding A/S Dispositif de pompe centrifuge
US12012915B2 (en) 2021-02-09 2024-06-18 Honda Motor Co., Ltd. Pump cover attachment system

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WO2016102269A1 (fr) * 2014-12-22 2016-06-30 Grundfos Holding A/S Système hydraulique
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DE19809123B4 (de) * 1998-03-04 2005-12-01 Daimlerchrysler Ag Wasserpumpe für den Kühlkreislauf einer Brennkraftmaschine
ATE456748T1 (de) * 2007-10-29 2010-02-15 Grundfos Management As Pumpenaggregat
EP2818726B1 (fr) * 2013-06-27 2017-08-23 Grundfos Holding A/S Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents

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DE9013992U1 (de) 1990-10-08 1991-10-24 Grundfos International A/S, Bjerringbro Motorpumpenaggregat für Kreislaufsysteme mit zwei parallelen Kreisläufen
US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system
US20160258340A1 (en) * 2013-11-16 2016-09-08 Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg Electromotive coolant pump
WO2016102269A1 (fr) * 2014-12-22 2016-06-30 Grundfos Holding A/S Système hydraulique

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3904689A1 (fr) 2020-04-28 2021-11-03 Grundfos Holding A/S Ensemble pompe centrifuge
EP3904738A1 (fr) 2020-04-28 2021-11-03 Grundfos Holding A/S Dispositif de soupape hydraulique et ensemble e pompe centrifuge comprenant un tel dispositif de soupape hydraulique
WO2021219539A1 (fr) 2020-04-28 2021-11-04 Grundfos Holding A/S Ensemble soupape hydraulique et ensemble pompe centrifuge doté d'un tel ensemble soupape hydraulique
WO2021219540A1 (fr) 2020-04-28 2021-11-04 Grundfos Holding A/S Ensemble de pompes centrifuges
US20230167826A1 (en) * 2020-04-28 2023-06-01 Grundfos Holding A/S Centrifugal pump assembly
CN115337695A (zh) * 2022-08-30 2022-11-15 奇力士（武汉）智慧水务科技有限公司 一种用于变频器水冷循环的过滤装置
CN115337695B (zh) * 2022-08-30 2023-08-22 奇力士（武汉）智慧水务科技有限公司 一种用于变频器水冷循环的过滤装置

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CN110418898B (zh) 2022-04-01
WO2018167043A1 (fr) 2018-09-20
US20200056614A1 (en) 2020-02-20
US11333151B2 (en) 2022-05-17

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