EP3267042B1 - Groupe motopompe - Google Patents

Groupe motopompe Download PDF

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Publication number
EP3267042B1
EP3267042B1 EP16178585.2A EP16178585A EP3267042B1 EP 3267042 B1 EP3267042 B1 EP 3267042B1 EP 16178585 A EP16178585 A EP 16178585A EP 3267042 B1 EP3267042 B1 EP 3267042B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve element
impeller
pump assembly
assembly according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16178585.2A
Other languages
German (de)
English (en)
Other versions
EP3267042A1 (fr
Inventor
Olav Jensen
Ole Hansen
Bent Døssing
Robert Greve
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 EP16178585.2A priority Critical patent/EP3267042B1/fr
Priority to CN201710555549.0A priority patent/CN107588202B/zh
Priority to US15/645,036 priority patent/US10514038B2/en
Publication of EP3267042A1 publication Critical patent/EP3267042A1/fr
Application granted granted Critical
Publication of EP3267042B1 publication Critical patent/EP3267042B1/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
    • 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
    • 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
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2283—Rotors specially for centrifugal pumps with special measures for reverse pumping action
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/911—Pump having reversible runner rotation and separate outlets for opposing directions of rotation

Definitions

  • the invention relates to a pump unit with the features specified in the preamble of claim 1.
  • a valve for a dual pump of a window cleaning system of a motor vehicle in which a valve body is arranged on each of two membrane elements arranged at a distance from one another, so that incorrect delivery to a washing nozzle not to be supplied with washing liquid is avoided.
  • a plunger transmits the movement of one valve body to the other.
  • the DE 34 42 907 A1 describes an aggregate for conveying liquid with one that can be operated in both directions of rotation Synchronous motor, whereby a guide element changes depending on the direction of rotation so that the flow losses through the outflow opening are reduced in each case.
  • the DE 197 45 737 A1 relates to a pump for supplying hot water, a pivotable valve element being pivoted by the water flow depending on the direction of rotation of a pump impeller. In such configurations, water hammer in the system, which lead to undesirable noises, is problematic.
  • the pump unit has a pump housing in which an impeller is rotatably arranged.
  • the impeller rotates in the interior of the pump housing.
  • the impeller is connected in a known manner to a suction connection or suction nozzle.
  • the pump unit also has an electric drive motor, the rotor of which is rotatably connected to the impeller in such a way that the electric drive motor rotates the impeller.
  • the drive motor or its stator housing is preferably connected to the pump housing in a known manner.
  • the drive motor is designed so that it can be selectively driven in two directions of rotation.
  • a suitable control device can be provided which controls the drive motor in such a way that it rotates in a desired direction of rotation.
  • the control device preferably controls the energization of the stator coils of the drive motor.
  • the control device can in particular include a frequency converter, via which the rotational speed of the drive motor can preferably be regulated in addition to the direction of rotation.
  • the impeller also rotates optionally in two desired opposite directions of rotation.
  • a valve arrangement is also arranged in the pump housing, which switches an outlet-side flow path, that is to say the flow path downstream of the impeller, between two outlets formed in the pump housing.
  • the valve arrangement is preferably designed such that it can be moved between two switch positions by the flow caused by the impeller, the flow in the peripheral region of the impeller also being directed in different directions depending on the direction of rotation of the impeller. Due to the different flow directions, a valve element of the valve arrangement can be specifically moved between several switching positions.
  • the valve arrangement has two valve elements, a first movable valve element being arranged at a first of the two outputs and a second movable valve element being arranged at a second of the two outputs.
  • the first valve element thus serves to close the first outlet, while the second valve element serves to close the second outlet.
  • the valve elements are arranged or designed such that they are in their closed position in a rest position, that is to say when the impeller is stationary. In the rest position, this means that the first valve element at least partially closes the first outlet and the second valve element at least partially closes the second outlet.
  • a partial closing of the outputs is to be understood to mean that the cross-section of the output in the closed position is reduced compared to the open position, preferably by more than half, more preferably by more than two thirds. As stated below, a certain flow passage preferably remains even in the closed position.
  • valve elements are arranged and designed such that the first valve element can be moved into an open position by a flow caused by the impeller in its first direction of rotation, while the second valve element can be moved by one of the Impeller in the second direction of rotation flow is movable into an open position. If the flow moves the first valve element into its open position, the second valve element simultaneously remains in its closed position. Conversely, the first valve element remains in its closed position when the second valve element is moved into its open position by the flow which occurs when the impeller rotates in the second direction of rotation.
  • the configuration according to the invention has the advantage over the known rotational direction-dependent switching devices that the outputs are essentially closed in the rest position. This has the effect that when the pump assembly is started up, a flow is initially generated essentially only in the interior of the pump housing in order to move one of the valve elements into its open position depending on the direction of rotation. Because there is essentially no flow through the outputs, water hammer when switching over when the pump set is started up is minimized or avoided. This means that when the pump unit is started up, a flow is first generated inside the pump unit, the hydraulic energy of which is used to move one of the valve elements.
  • valve element When the pump unit is started up, a valve element always opens, i.e. one of the valve elements is moved into its open position depending on the direction of rotation.
  • the pump set is switched off, i.e. the impeller comes to a standstill, the valve element moves back into its closed position.
  • the drive motor is then driven in the opposite direction of rotation, so that the impeller inside the pump housing generates a flow in the opposite direction, which opens the other valve element and so the flow through the other outlet from the pump housing to the outside.
  • the design according to the invention enables a very smooth and quiet switching between the two flow paths, which are defined by the two outputs, by the targeted control of the drive motor, that is to say in particular not only by the choice of the direction of rotation, but also of the course of the acceleration.
  • the first and the second valve element are preferably movable independently of one another. It allows the first valve element to remain in its closed position while the second valve element is moving to its open position and vice versa.
  • first and the second valve element are preferably each designed as a flap which can be pivoted about a pivot axis between the open position and the closed position.
  • the flap preferably comes to rest with a surface sealing against a valve seat surrounding an associated outlet.
  • the valve elements are preferably arranged in such a way that their pivot axis is located at one longitudinal end, this longitudinal end preferably being the longitudinal end which is the most distant from the impeller.
  • the pivot axis or pivot axes of the flaps preferably extend parallel to the axis of rotation of the impeller, the flaps extending essentially radially to the impeller.
  • valve elements further preferably have a sealing area or a sealing surface which can come into sealing contact with a corresponding valve seat which surrounds the associated outlet.
  • valve elements preferably have one Attack surface or an attack area on which the flow generated by the impeller acts to move the valve element.
  • the engagement region is preferably formed by an axial end region of the flap spaced apart from the pivot axis.
  • the attack area preferably extends into an annular space of the pump housing surrounding the impeller, so that the flow generated in this annulus by the impeller can act directly on the attack area.
  • the first and the second valve element can be pivoted about the same pivot axis.
  • this can be a pivot axis, which preferably extends parallel to the axis of rotation of the impeller.
  • the valve elements are preferably designed in the manner described above, the flaps being articulated at one end on the pivot axis and the opposite free end of the flaps in each case forming an attack surface or an attack region for the flow.
  • the sealing area or the sealing surface is preferably between the engagement area and the pivot axis.
  • the pivot axis is preferably arranged at the end of the flap which is the most distant from the impeller.
  • valve elements are further preferably designed and arranged such that they are in contact with one another when one of the valve elements is in its open position. That means preferably that the valve element moving into the open position pivots until it comes to rest on the other valve element, which remains in its closed position.
  • This configuration has the advantage that the released flow path to the opened outlet is maximized and that the opened valve element additionally presses the valve element in its closed position into its closed position and / or can perform an additional sealing function, as will be described below.
  • the valve elements each have an opening which enables a flow passage into the associated outlet, even in the closed position of this valve element.
  • These openings in the valve elements are preferably dimensioned such that the outlets in the closed positions of the valve elements are essentially closed, that is to say largely as described above, but a small flow passage remains.
  • the opening essentially ensures that there is pressure equalization between both sides of the valve element. This pressure compensation ensures that when the impeller starts up, the valve element is not pressed against the valve seat by the pressure generated in the pump housing. This reduces the holding force to be overcome by the flow, so that the valve element can be moved more easily from the closed to the open position. This supports a silent, smooth switching of the valve device by moving one of the valve elements.
  • the opening in the first valve element and the opening in the second valve element are preferably arranged such that the opening in the first valve element is closed by the second valve element and the opening in the second valve element is closed by the first valve element when the two valve elements are connected to one another are in annex. That is, that itself in its open position, the valve element closes, that it comes to rest on the other valve element, which is in its closed position, at the same time the opening in that valve element, which is in its closed position. Only by opening one of the valve elements is the other valve element and thus the associated outlet completely closed. In this state, the pressure generated by the pump unit then acts on the two valve elements, so that these valve elements are pressed against each other and the valve element, which is in its closed position, against the associated valve seat.
  • the first and second valve elements are further preferably acted upon by at least one restoring element such that they are each held in their closed position when the impeller is at a standstill, the first and second valve elements preferably being provided by a common restoring element, in particular one arranged between the valve elements Spring are energized.
  • the reset element or elements thus ensure that after the pump unit is switched off and the impeller comes to a standstill, the valve elements are moved back into their rest position, that is to say their closed position.
  • the spring element can be special preferably be designed as a torsion spring which rotates about a common axis of rotation or pivoting of the two valve elements and with its free legs is in engagement or contact with one of the valve elements. This enables a particularly simple construction and simple assembly, since the torsion spring can be pushed together with the two valve elements onto a common pivot or rotation axis.
  • the valve elements can be elastic or rigid. If the valve elements are elastic, in the simplest case they can be designed as tabs or flaps made of a rubber or elastomer material. If the valve elements are elastic, the elastic restoring forces which are generated when the valve element is deformed can form the described restoring element. Such valve elements can be moved from the closed to the open position by deformation. If the valve elements are rigid, they preferably rotate about fixed swivel or rotation axes, in particular about a common swivel or rotation axis. The rigid valve elements are essentially rigid, but can additionally have elastic regions or sections, which can particularly preferably be integrally connected to the rigid sections. The rigid valve elements can e.g. additionally be provided with elastic sealing surfaces or elastic sections.
  • An elastic seal is preferably arranged in each case on the valve elements and / or valve seats opposite them. This ensures reliable sealing of the outlet when the valve element is in its closed position.
  • an elastic seal can be provided between the two valve elements if they have openings in the manner described above.
  • Such an additional sealing element ensures a seal in the Area of the opening of the valve element which is in its closed position when the second valve element comes into contact with it.
  • the opening in the valve element on the side of the valve element which faces the second valve element can be surrounded by an elastic seal.
  • a sealing surface can be formed on the valve elements in a region which covers the opening of the other valve element when the two valve elements come into contact with one another.
  • the pump housing has a receiving opening located between the two outlets, which is open to the interior of the pump housing and into which the two valve elements are inserted from the outside of the pump housing, the two valve elements preferably being in one in the Receiving opening used valve insert are stored.
  • the receiving opening is sealed off from the outside by a cover, this cover preferably being part of the valve insert. This simplifies assembly, since the valve elements can be inserted into the pump housing from the outside. Furthermore, the valve elements are easily accessible for maintenance purposes without having to disassemble the other parts of the pump assembly.
  • the receiving opening is preferably shaped such that it has no undercuts when viewed from the outside.
  • the pump housing with the receiving opening can easily be produced as a casting, in particular as an injection molded part made of plastic, a core which defines the receiving opening being able to be pulled outward from the pump housing. At this point, a lost core can be dispensed with.
  • the two outputs of the pump housing described are preferably located in the receiving opening or branch from the Opening. This means that the flow starts from the interior of the pump housing, in which the impeller rotates, first into the receiving opening and then from there into one of the two exits, depending on which valve element is in its open position.
  • the two outputs each have a valve seat facing the interior of the pump housing or located in the flow path from the interior, against which the associated valve element comes into contact with its sealing surface in its closed position, at least around the respective output partially closed.
  • the valve seats of the two outputs are preferably opposite one another, the valve seats particularly preferably extending essentially parallel to one another. If the valve seats are located in the receiving opening, the valve seats preferably extend essentially parallel to the longitudinal direction of the receiving opening on two opposite side walls of the receiving opening.
  • An essentially parallel arrangement of the valve seats means that slight draft angles, which are required to remove a core from the receiving opening after casting, are still regarded in this sense as a parallel arrangement.
  • valve seats enables that valve element which moves into its open position to move to the second valve element which is in a closed position and can come into contact with this valve element, as described above , This applies in particular if the valve elements perform a pivoting movement from the closed to the open position.
  • the pivot axes preferably extend parallel to the surfaces spanned by the valve seats. If the swivel axis is common, this is preferred also located in a plane which is located between the surfaces spanned by the valve seats.
  • valve elements further preferably each have a sealing surface provided for contact with a valve seat, which extends at an angle to a radius with respect to the pivot axis of the respective valve element.
  • Valve elements of this type preferably have a substantially triangular shape in a plane normal to the pivot axis, one side of the sealing element, which forms the sealing surface, and a second side of the valve element, which is provided for abutment against the second valve element, preferably in a pointed shape Extend angles to each other.
  • the pivot or rotation axis is preferably on or in the surface which is provided for contact with the second valve element.
  • the angled arrangement of the sealing surface makes it possible for the valve seats to be located in planes extending parallel to one another in spite of the provided pivoting movement with a common pivot axis.
  • the pump assembly is particularly preferably designed as a circulation pump assembly and more preferably as a heating circulation pump assembly.
  • it can be a heating circulation pump unit which is used in a gas boiler.
  • a gas boiler with a pump unit as described above and below, is not part of the invention.
  • the pump unit can be part of a hydraulic block, which forms an integrated unit for a compact heating system and in particular for a gas boiler.
  • the drive motor is preferably a wet-running drive motor, that is to say a drive motor in which the rotor and stator pass a can or a can are separated from each other.
  • the drive motor particularly preferably has a permanent magnet rotor.
  • the drive motor can further preferably have a frequency converter for speed regulation.
  • the impeller and the interior of the pump housing can be dimensioned such that an annular free space remains in the interior of the pump housing in the peripheral region of the impeller.
  • This annular free space is preferably of a size in which the radius of the inner circumference of the pump housing is at least 1.4 times and preferably at least 2 times as large as the radius of the impeller in at least one circumferential section in the circumferential region of the impeller.
  • the radius of the inner circumference of the pump housing is particularly preferably appropriately dimensioned over the entire circumference.
  • the radius of the inner circumference of the pump housing is further preferably at least 2 or 3 times as large as the radius of the impeller in at least one circumferential section.
  • valve elements are preferably arranged or dimensioned such that a free space remains between the valve element and the outer circumference of the impeller in each position, so that the circulating flow is not prevented by the valve element.
  • the pump unit 1 shown in the figures is designed as a circulation pump unit with a wet-running electric drive motor.
  • the pump unit 1 has a pump housing 2, which can be designed as a cast component made of metal or plastic.
  • the pump housing 2 has a suction connection 4 and two pressure ports 6 and 8.
  • Attached to the pump housing 2 is a motor or stator housing 10, in which the electric drive motor is arranged.
  • an electronics housing 12 is arranged, in which a control or regulating device for controlling the electric drive motor is arranged.
  • an impeller 14 is arranged in the interior of the pump housing 2 and is connected in a rotationally fixed manner to the rotor 16 of the electric drive motor.
  • the rotor 16 is rotatably held in a bearing 18 which is fixed to a bearing plate 20 in the pump housing 2.
  • the stator of the electric drive motor is arranged, on the inner periphery of which there is a containment shell 21 which separates the rotor space in which the rotor 16 is arranged from the stator, so that the rotor space can be filled with liquid. It is therefore a wet-running drive motor.
  • a receiving opening 22 extends radially outward.
  • the receiving opening 22 forms part of an outlet-side flow path through which the flow accelerated by the impeller 14 exits the pump housing 2.
  • the pressure ports 6 and 8 branch off at a first outlet 24 and a second outlet 26, which are located in the interior of the receiving opening 22 (see Fig. 7 ).
  • a valve insert 28 is inserted from the outside into the receiving opening 22 and has a closure plate 30 which closes the receiving opening 22 to the outside.
  • the closure plate 30 also serves as a carrier and holds a rotation or pivot axis 32, on which a first valve element 34 and a second valve element 36 are pivotally mounted.
  • a torsion spring 38 is arranged on the swivel axis 32, which forms a reset element and presses the first valve element 34 and the second valve element 36 apart in the assembled state.
  • the two valve elements 34 and 36 are identical and are only rotated by 180 ° to one another.
  • Fig. 3 shows the valve insert 28 in the assembled state before insertion into the receiving opening 22 of the pump housing 2.
  • the first and the second valve elements 34, 36 are rotated through 180 ° to one another, arranged away from one another on the pivot axis 32, so that their outer surfaces 40 facing away from one another are sealing surfaces form, which come to close the exits 24 and 26 on their outer circumference, which each forms a valve seat, come to rest.
  • elastic sealing elements can be arranged on the outer circumference of the outputs 24, 26 or on the sealing surfaces 40.
  • the flap-shaped valve elements 34 and 36 are designed such that in each case an opening 42 is formed in the sealing surface 40, which opening 42 extends transversely to the sealing surface 40 through the valve element 34, 36.
  • the opening 42 is arranged eccentrically in the valve element 34, 36 as seen in the direction of the pivot axis 32.
  • the opening 42 is arranged in one half as viewed in the sealing surface 40 in the direction of the pivot axis 32. Since the two identically designed valve elements 34 and 36 are arranged rotated by 180 ° with respect to one another, the opening 42 in the first valve element 34 is offset from the opening 42 in the second valve element 36 Fig. 4
  • the opening 42 in the first valve element 34 lies in the upper half, while the opening 42 in the second valve element 36 lies in the lower half. This means that when the two valve elements 34 and 36 come into contact with one another, the openings 42 in the two valve elements 34 and 36 do not align with one another.
  • valve elements 34 and 36 on their side facing away from the sealing surface 40 have an engagement element 44 in addition to the opening 42, which corresponds in shape to the opening 42 on the same side.
  • the engaging element 44 of the first valve element 34 thus engages in the opening 42 of the second valve element 36 when the two valve elements come into contact with one another while overcoming the spring force of the torsion spring 38.
  • the opening 42 of the second valve element 36 is closed by the first valve element 34 and its engagement element 44.
  • the engagement element 44 can be designed elastically in the form of a seal.
  • the engagement element 44 of the second valve element 36 engages in the opening 42 of the first valve element 34 to close it.
  • the first and the second outlet 24 and 26 lie opposite one another in the receiving opening 22, the valve seats formed by the edge of the outlet 24 and 26 being located in mutually parallel planes.
  • the first valve element 34 and the second valve element 36 are actuated by the torsion spring 38, which acts as a restoring element acts, pressed into its rest position, which represents a closed position in which the first valve element 34 covers the first outlet 24 and the second valve element 36 covers the second outlet 26.
  • the first outlet and the second outlet are essentially closed by the first valve element 34 and the second valve element 36, ie closed except for the flow passage through the openings 42.
  • Fig. 5 . 6 As in the Fig. 5 . 6 .
  • valve elements 34 and 36 are so long in a direction transverse to the pivot axis 32 that their ends 46 spaced apart from the pivot axis 32 extend into the interior 15 and thus into an annular space surrounding the impeller 14.
  • the surfaces adjoining the ends 46 in the extension of the sealing surfaces 40 of the valve elements 34, 36 form engagement surfaces on which the flow rotating in the interior 15 acts when the impeller 14 rotates.
  • the control device arranged in the electronics housing 12 is designed such that it can specifically control the electric drive motor in two different directions of rotation A and B. This can be done, for example, via a frequency converter, which specifically energizes the coils in the stator.
  • the valve device in the valve insert 28 is designed such that, depending on the direction of rotation A, B, it directs the flow into the first outlet 24 and thus to the first pressure port 6 or to the second outlet 26 and thus to the second pressure port 8.
  • the heating circuit of a heating system for a building can be connected to the first pressure connection 6, while a heat exchanger for heating service water connects to the second pressure connection 8.
  • the control device 12 When the pump unit is started up, the control device 12 thus initially specifies the direction of rotation in order to specify in which of the two outputs 24 or 26 the delivery should take place. If now the first output 24 with the subsequent Pressure port 6 is to be used, the pump unit is set in motion so that the impeller rotates in the first direction of rotation A. In the in Fig. 5 and 7 Except in the rest position shown, the exits 24 and 26 are essentially closed except for the flow passages through the openings 42. The openings 42 bring about a pressure equalization between the two sides of the valve elements 34 and 36, so that the valve elements 34 and 36 are not pressed against the outlets 24 and 26 by the pressure which forms in the interior 15 when the pump unit is started up.
  • valve elements 34 and 36 are essentially held in their position only by the torsion spring 38.
  • the impeller rotates in the direction A
  • a rotating flow is generated in the interior 15 of the pump housing 2 in the peripheral region of the impeller.
  • the flow also rotates in the direction of rotation A and thus acts on the contact surface of the first valve element 34.
  • the flow thus generates a force on the first valve element 34 which counteracts the spring force of the torsion spring 38 and thus the first valve element 34 from the closed position in FIG moves its open position, in which the valve element 34 abuts the second valve element 36.
  • the first valve element 34 closes the opening 42 in the second valve element 36.
  • the second outlet 26, at which the second valve element 36 remains in contact, is now completely closed.
  • the first outlet 24 is completely open, so that the flow flows through this outlet 24 into the pressure port 6.
  • the pressure prevailing in the interior 15 now acts on the sealing surface 40 of the first valve element 34, which, via the contact with the second valve element 36, presses it into an additional sealing contact with the valve seat, which surrounds the second outlet 26.
  • This state, in which the first valve element 34 is open and thus a flow path through the first outlet 24 to the pressure port 6, is shown in FIGS Figure 6A and 8A shown.
  • the impeller 14 comes to a standstill and the flow and the pressure in the interior 15 disappear.
  • the first valve element 34 is then brought back into its rest position by the torsion spring 38, in which it essentially closes the first outlet 24.
  • the pump unit is operated in the opposite direction of rotation B, the second valve element 36 will accordingly move into an open position in which it comes into contact with the first valve element 34 and thus the opening 42 in the first valve element 34 and thus the first outlet 24 completely closes.
  • the second outlet 26 is opened and the flow can flow through this outlet into the second pressure port 8. This state, in which the second valve element 36 is in its open position, is in the Figure 6B and 8B shown.
  • the control device in the electronics housing 12 can also adapt the acceleration of the drive motor so that just enough pressure and flow are initially built up during start-up to move one of the valve elements 34, 36 into the desired open position move and only then the motor is accelerated so that the desired final pressure or flow is built up.
  • the interior 15 of the pump housing 2 is dimensioned such that it has a considerably larger diameter than the outer diameter of the impeller 14.
  • a free annular space 47 remains in the peripheral region of the impeller 14, in which a rotating flow in the periphery of the impeller 14 can form, which then acts on the contact surfaces of the valve elements 34 and 36 depending on the direction of rotation, in order to be able to move them into the open position.
  • the valve elements 34 and 36 are dimensioned such that their free ends 46 are spaced from the outer circumference of the impeller 34 in any angular position during the pivoting movement about the pivot axis 32, so that the valve elements 34 and 36 do not collide with the impeller 14.
  • the distance between the ends 46 and the outer circumference of the impeller 14 is further preferably selected such that there is always a free space through which the annular or rotating flow can run in the circumferential region of the impeller 14.
  • the annular space 47 leads to an overall improved efficiency, in particular if the impeller 14 has curved blades.
  • the receiving opening 22 is formed such that no undercuts are formed in a direction radial to the axis of rotation X of the drive motor.
  • the receiving opening 22 can be formed by a core, which can be pulled outwards in the radial direction after the pump housing 2 has been cast. This enables the receiving space 22 to be easily manufactured.
  • valve elements 34 and 36 are articulated on the pivot axis so that the The pivot axis 32 is arranged in relation to the axis of rotation x of the impeller at the radially outer end of the valve elements 34, 36, that is to say the pivot axis 32 is at a maximum distance from the impeller or the axis of rotation x in the radial direction.
  • the pivot axis 32 'could also be located at the radially inner end of the valve elements 34' and 36 '.
  • the circulation pump unit according to the invention is preferably used in a heating system, in particular in a gas boiler, which are not part of the invention.
  • a heating system with a gas heater 48 is shown schematically in Fig. 11 shown.
  • the gas heater 48 comprises a burner 50 with a primary heat exchanger 52, via which the water in the heating circuit is heated.
  • the water is pumped through the heating circuit via the pump unit 1.
  • Via the control device 12 of the pump unit 1 its direction of rotation is specified in the manner described above, as a result of which the valve arrangement formed by the valve elements 34, 36 is switched over.
  • the valve arrangement serves to switch the flow path between a heating circuit 54, which runs through a building, and a secondary heat exchanger 55, which is used to heat industrial water.
  • the heating circuit 54 runs through one or more radiators 56, wherein In the sense of this description, circles of an underfloor heating system can also be regarded as radiators.
  • the flow either through the secondary heat exchanger 55 or the heating circuit 54.
  • the system is preferably designed so that the direction of rotation in which the Heating water is directed through the heating circuit 54, which is the direction of rotation for which the curvature of the impeller blades is optimized.
  • the primary heat exchanger 52 with the burner 50, the pump unit 1 and the secondary heat exchanger 55 preferably form components of the gas boiler 48 and the pump unit 1 and the secondary heat exchanger 55 are preferably integrated into a hydraulic assembly, that is to say a hydraulic block.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (14)

  1. Groupe motopompe comprenant un carter de pompe (2), une turbine montée rotative dans le carter de pompe (2), un moteur d'entraînement électrique relié à la turbine (14) pour l'entraîner, le moteur étant adapté pour pouvoir lui-même être entraîné sélectivement dans deux sens de rotation (A, B), ainsi qu'un agencement de valves (28) disposé dans le carter de pompe (2), qui est configuré de façon qu'il commute un trajet de flux en aval de la turbine, en fonction du sens de rotation (A, B) de la turbine (14), entre deux sorties (24, 26) formées dans le carter de pompe, l'agencement de valves comprenant un premier élément de valve (34) mobile disposé à une première (24) des deux sorties et un deuxième élément de valve (36) mobile disposé à une deuxième (26) des deux sorties,
    les éléments de valve (34, 36) étant, chacun, dans une position de repos, dans une position dans laquelle le premier élément de valve (34) obture au moins partiellement la première sortie (24) et le deuxième élément de valve (36) obture au moins partiellement la deuxième sortie (26), et
    le premier élément de valve (34) étant adapté pour pouvoir être mis dans une position ouverte par un courant engendré par la turbine (14) tournant dans son premier sens de rotation (A) et le deuxième élément de valve (36) étant adapté pour pouvoir être mis dans une position ouverte par un courant engendré par la turbine (14) tournant dans son deuxième sens de rotation (B), caractérisé en ce que les éléments de valve (34, 36) comprennent chacun une ouverture (42) qui permet un passage de flux vers la sortie correspondante (24, 26) même en position fermée de cet élément de valve (34, 36).
  2. Groupe motopompe selon la revendication 1, caractérisé en ce que le premier et le deuxième élément de valve (34, 36) sont mobiles indépendamment l'un de l'autre.
  3. Groupe motopompe selon la revendication 1 ou 2, caractérisé en ce que le premier et le deuxième élément de valve (34, 36) sont formés, chacun, comme un clapet adapté pour pouvoir pivoter sur un axe de pivotement (32) entre la position ouverte et la position fermée.
  4. Groupe motopompe selon la revendication 3, caractérisé en ce que le premier et le deuxième élément de valve (34, 36) sont adaptés pour pouvoir pivoter sur le même axe de pivotement (32).
  5. Groupe motopompe selon l'une des revendications 1 à 4, caractérisé en ce que les éléments de valve (34, 36) sont disposés de telle façon que, lorsqu'un des éléments de valve (34, 36) se trouve dans sa position ouverte, ils sont en appui l'un sur l'autre.
  6. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que l'ouverture (42) dans le premier élément de valve (34) et l'ouverture (42) dans le deuxième élément de valve (36) sont disposées décalées l'une par rapport à l'autre de façon telle que l'ouverture (42) dans le premier élément de valve (34) est fermée par le deuxième élément de valve (36) et l'ouverture (42) dans le deuxième élément de valve (36) est fermée par le premier élément de valve (34) lorsque les deux éléments de valve (34, 36) sont en appui l'un sur l'autre.
  7. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le premier et le deuxième élément de valve (34, 36) sont soumis à une force par au moins un élément de rappel (38) de façon à ce qu'ils soient tenus, en position de repos de la turbine (14), respectivement dans leur position fermée, le premier et le deuxième élément de valve (34, 36) étant soumis à une force par un élément de rappel (38) commun, en particulier par un ressort (38) fixé entre les éléments de valve.
  8. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que les éléments de valve (34, 36) sont formés, chacun, de façon élastique ou, selon une alternative, de façon rigide.
  9. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce qu'un joint d'étanchéité élastique est fixé respectivement aux éléments de valve (34, 36) et/ou aux sièges de valves en regard de ceux-ci.
  10. Groupe motopompe selon l'une des revendications, caractérisé en ce que le carter de pompe (2) comprend, entre les deux sorties, une ouverture d'admission (22) qui s'ouvre sur l'intérieur (15) du carter de pompe (2) et dans lequel les deux éléments de valve (34, 36) sont insérés à partir du côté extérieur du carter de pompe (2), les deux éléments de valve (34, 36) étant logés de préférence dans un insert de valves (28) inséré dans l'ouverture d'admission (22).
  11. Groupe motopompe selon la revendication 10, caractérisé en ce que les deux sorties (24, 26) sont situées dans l'ouverture d'admission (22).
  12. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que les deux sorties (24, 26) comprennent des sièges de valve tournés vers l'intérieur (15) du carter de pompe (2) qui sont en regard l'un de l'autre, les sièges de valve étant orientés, de préférence, sensiblement parallèlement l'un par rapport à l'autre.
  13. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que les éléments de valve (34, 36) comprennent, chacun, une surface d'étanchéité (40) prévue pour un appui sur un siège de valve, qui s'étend sous un angle par rapport à un rayon partant de l'axe de pivotement (32) de l'élément de valve (34, 36) respectif.
  14. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce qu'il est formé comme groupe motopompe de recirculation, en particulier pour une utilisation dans une installation de chauffage et de préférence avec un moteur d'entrainement à fonctionnement humide.
EP16178585.2A 2016-07-08 2016-07-08 Groupe motopompe Active EP3267042B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP16178585.2A EP3267042B1 (fr) 2016-07-08 2016-07-08 Groupe motopompe
CN201710555549.0A CN107588202B (zh) 2016-07-08 2017-07-10 泵机组
US15/645,036 US10514038B2 (en) 2016-07-08 2017-07-10 Pump assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16178585.2A EP3267042B1 (fr) 2016-07-08 2016-07-08 Groupe motopompe

Publications (2)

Publication Number Publication Date
EP3267042A1 EP3267042A1 (fr) 2018-01-10
EP3267042B1 true EP3267042B1 (fr) 2020-01-15

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US (1) US10514038B2 (fr)
EP (1) EP3267042B1 (fr)
CN (1) CN107588202B (fr)

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Publication number Priority date Publication date Assignee Title
WO2019210973A1 (fr) * 2018-05-04 2019-11-07 Electrolux Appliances Aktiebolag Lave-linge et son procédé de fonctionnement
USD949926S1 (en) * 2020-02-13 2022-04-26 Michael Padgett Pump
USD979481S1 (en) 2020-02-13 2023-02-28 Michael Padgett Sea chest assembly
US11369101B1 (en) 2020-02-13 2022-06-28 Michael Padgett Water delivery to a live bait well
DE102022131010A1 (de) * 2022-11-23 2024-05-23 Miele & Cie. Kg Pumpvorrichtung, Haushaltsgerät mit Pumpvorrichtung und Verfahren zum Betreiben einer Pumpvorrichtung

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Also Published As

Publication number Publication date
CN107588202B (zh) 2020-04-21
EP3267042A1 (fr) 2018-01-10
US20180010609A1 (en) 2018-01-11
US10514038B2 (en) 2019-12-24
CN107588202A (zh) 2018-01-16

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