EP3267042A1 - Groupe motopompe - Google Patents

Groupe motopompe Download PDF

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Publication number
EP3267042A1
EP3267042A1 EP16178585.2A EP16178585A EP3267042A1 EP 3267042 A1 EP3267042 A1 EP 3267042A1 EP 16178585 A EP16178585 A EP 16178585A EP 3267042 A1 EP3267042 A1 EP 3267042A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve element
impeller
pump unit
unit 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.)
Granted
Application number
EP16178585.2A
Other languages
German (de)
English (en)
Other versions
EP3267042B1 (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.
  • 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 with a suction port or suction.
  • the pump unit also has an electric drive motor whose rotor is connected in such a rotationally fixed manner with the impeller that the electric drive motor can drive the impeller rotationally.
  • the drive motor or its stator housing is connected to the pump housing in a known manner.
  • the drive motor is designed so that it can be selectively driven selectively in two directions of rotation.
  • a suitable control device can be provided, which controls the drive motor so 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 may in particular include a frequency converter, via which, in addition to the direction of rotation, preferably also the rotational speed of the drive motor can be regulated.
  • the impeller also rotates selectively in two desired opposite directions of rotation.
  • a valve arrangement is further arranged, which can switch an outlet-side flow path, that is, the flow path downstream of the impeller between two outputs formed in the pump housing.
  • the valve assembly is preferably designed such that it can be moved by the flow caused by the impeller between two switching positions, wherein, depending on the direction of rotation of the impeller, the flow in the peripheral region of the impeller is also directed in different directions. Due to the different flow directions, a valve element of the valve arrangement can be selectively moved between several switching positions.
  • the valve arrangement has two valve elements, wherein a first movable valve element is arranged on a first of the two outlets and a second movable valve element is arranged on a second of the two outlets.
  • first valve element serves to close the first outlet
  • second valve element serves to close the second outlet.
  • the valve elements are arranged so that they are in a rest position, that is, when the impeller is stationary, in its closed position. That is, in the rest position, the first valve element at least partially closes off the first outlet, and the second valve element at least partially closes off the second outlet.
  • a partial closure of the outlets means that the outlet in the closed position is reduced in cross-section with respect to the open position, preferably reduced by more than half, more preferably by more than two-thirds. As explained below, preferably in the closed position, a certain flow passage remains.
  • valve elements are arranged and configured such that the first valve element is movable to an open position by a flow caused by the impeller in its first rotational direction, while the second valve element is moved by one of the Impeller in the second direction of rotation caused flow is movable to an open position.
  • the first valve element is moved to its open position by the flow
  • the second valve element remains in its closed position at the same time.
  • the first valve element remains in its closed position when the second valve member is moved to its open position by the flow which occurs upon rotation of the impeller in the second rotational direction.
  • the embodiment of the invention has the advantage over the known direction of rotation dependent switching devices that the outputs are substantially closed in the rest position. This causes that upon start-up of the pump assembly, a flow is initially generated substantially only in the interior of the pump housing to move depending on the direction of rotation of the valve elements in its open position. Due to the fact that substantially no flow takes place through the outputs, water hammer during switching when commissioning the pump unit are minimized or avoided. This means that during startup of the pump unit, a flow is initially generated in the interior of the pump unit, the hydraulic energy of which is used to move one of the valve elements.
  • valve element that is, one of the valve elements is moved depending on the direction of rotation in its open position.
  • the pump unit is turned off, that is, the impeller comes to a standstill, the valve element moves back to its closed position.
  • the drive motor is then driven in the reverse direction of rotation, so that the impeller generates a flow in the opposite direction in the interior of the pump housing, which opens the other valve element and so the flow through the other outlet from the pump housing leads to the outside.
  • the inventive design allows by the targeted control of the drive motor, that is, in particular, not only by the choice of the direction of rotation, but also the acceleration curve, a very gentle and quiet switching between the two flow paths, which are defined by the two outputs.
  • the first and the second valve element are independently movable. It allows the first valve member to remain in its closed position while the second valve member is moving to its open position and vice versa.
  • first and the second valve element are each preferably designed as a flap pivotable about a pivot axis between the open position and the closed position.
  • the flap preferably comes with a surface sealingly against a valve seat surrounding an associated outlet to the plant.
  • the valve elements are arranged so that their pivot axis is located at a longitudinal end, said longitudinal end is preferably the one longitudinal end which is furthest from the impeller.
  • the pivot axis or pivot axes of the flaps further preferably extend parallel to the axis of rotation of the impeller, wherein the flaps extend substantially radially to the impeller.
  • valve elements 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 An attack surface or an attack area on which the flow generated by the impeller acts to move the valve element.
  • the engagement portion is preferably formed by an axial end portion of the flap spaced from the pivot axis.
  • the engagement region preferably extends into an annular space of the pump housing surrounding the impeller, so that the flow generated by the impeller in this annular space can act directly on the engagement area.
  • the first and the second valve element are pivotable about the same pivot axis.
  • This may, as described above, be a pivot axis, which preferably extends parallel to the axis of rotation of the impeller.
  • the valve elements in the manner described above are flap-shaped, wherein the flaps are articulated at one end to the pivot axis and the opposite free end of the flaps each forms an attack surface or an attack area for the flow.
  • the sealing region or the sealing surface is preferably located between the engagement region and the pivot axis.
  • the pivot axis is preferably arranged at the end of the flap, which is the furthest from the impeller.
  • valve elements are configured and arranged so that, when one of the valve elements is in its open position, they are in contact with each other. That is, preferably, the valve element which moves into the open position pivots until it comes into abutment against the other valve element which lingers in its closed position.
  • This embodiment has the advantage that the released flow path is maximized to the open outlet and that open valve element additionally presses the valve element located in its closed position into its closed position and / or can take on an additional sealing function, as will be described below.
  • the valve elements each have an opening which allows a flow passage into the associated outlet even in a closed position of this valve element. That is, the opening extends from that side of the valve element, which faces the interior of the pump housing, that is, the impeller, into the outlet.
  • These openings in the valve elements are preferably dimensioned so that the outputs in the closed positions of the valve elements substantially, that is, as described above, are largely closed, but a small flow passage remains.
  • the opening essentially ensures that a pressure equalization between both sides of the valve element is given. This pressure compensation ensures that when starting the impeller, the valve element is not pressed by the pressure generated in the pump housing against the valve seat. As a result, the holding force to be overcome by the flow is reduced, so that the valve element can be moved more easily from the closed to the open position. This assists a silent soft switching of the valve means by movement of one of the valve elements.
  • the opening in the first valve element and the opening in the second valve element are arranged offset from one another such that the opening in the first valve element by the second valve element and the opening in the second valve element are closed by the first valve element, when the two valve elements together are in plant. That is, the valve element located in its open position closes thereby, 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, the other valve element and thus the associated output is completely closed. In this state, then the pressure generated by the pump unit acts on the two valve elements, so that these valve elements against each other and the valve element, which is in its closed position, is pressed against the associated valve seat.
  • the first and the second valve element are subjected to force by at least one return element so that they are each held in its closed position at standstill of the impeller, wherein preferably the first and the second valve element by a common return element, in particular by an arranged between the valve elements Spring, are subjected to force.
  • the or the return elements thus ensure that after switching off the pump unit, when the impeller comes to a standstill, the valve elements are moved back to their rest position, that is, their closed position.
  • the spring element can be particularly Preferably be designed as a torsion spring, which rotates about a common rotational or pivot axis of the two valve elements and with their free legs in each case with one of the valve elements into engagement or conditioning. This allows a particularly simple structure and easy installation, since the torsion spring can be pushed together with the two valve elements on a common pivot or rotation axis.
  • the valve elements may be elastic or rigid. If the valve elements are elastic, they can be formed in the simplest case as tabs or flaps made of a rubber or elastomeric material. If the valve elements are designed to be elastic, the elastic restoring forces that are generated when the valve element is deformed can form the described restoring element. Such valve elements can be moved by deformation from the closed to the open position. If the valve elements are rigid, they preferably rotate about fixed pivot or rotation axes, in particular about a common pivot or rotation axis.
  • the rigid valve elements are substantially rigid, but may additionally have elastic regions or sections, which may particularly preferably be connected in a materially bonded manner to the rigid sections. The rigid valve elements may e.g. be additionally provided with elastic sealing surfaces or elastic sections.
  • an elastic seal is arranged in each case on the valve elements and / or these opposite valve seats. This provides a reliable seal of the outlet when the valve member is in its closed position.
  • an elastic seal between the two valve elements may be provided when they have openings in the manner described above.
  • Such an additional sealing element provides a seal in the Area of the opening of that valve element, which is in its closed position, when the second valve element comes to rest on this.
  • the opening in the valve element on the side of the valve element, which faces the second valve element be surrounded by an elastic seal.
  • a sealing surface may be formed there 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 each other.
  • the pump housing has a receiving opening located between the two outputs, which is open to the interior of the pump housing and in which the two valve elements are inserted from the outside of the pump housing, wherein the two valve elements preferably in one in the Receiving opening inserted valve insert are stored.
  • the receiving opening is sealed to the outside by a lid, this cover is preferably part of the valve core.
  • the pump housing with the receiving opening can be easily manufactured as a casting, in particular as an injection molded part made of plastic, wherein a core, which defines the receiving opening, can be pulled out of the pump housing.
  • a lost core can be dispensed with at this point.
  • the described two outputs of the pump housing are preferably located in the receiving opening or branches of the Receiving opening. That is, the flow, starting from the interior of the pump housing, in which the impeller rotates, first enters the receiving opening and then from there into one of the two outlets, depending on which valve element is in its open position.
  • the two outputs each have a the interior of the pump housing facing or in the flow path of the interior valve seat on which the associated valve element comes with a sealing surface in its closed position to the plant to the respective output at least partially closed.
  • the valve seats of the two exits are preferably opposite one another, wherein the valve seats particularly preferably extend substantially parallel to one another.
  • the valve seats When the valve seats are located in the receiving opening, the valve seats preferably extend substantially parallel to the longitudinal direction of the receiving opening on two opposite side walls of the receiving opening.
  • a substantially 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 considered in this sense as a parallel arrangement.
  • valve seats allow that valve element which moves into its open position to move towards the second valve element, which is in a closed position, and can come into abutment with this valve element as described above , This is especially true when 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. In a common pivot axis, this is preferably Located in a plane which is located between the surfaces formed by the valve seats.
  • valve elements further preferably each have a sealing surface provided for engagement with a valve seat, which extends at an angle to a radius with respect to the pivot axis of the respective valve element.
  • Such valve elements preferably have a substantially triangular shape in a plane normal to the pivot axis, wherein one side of the sealing element, which forms the sealing surface and a second side of the valve element, which is provided for bearing against the second valve element, preferably in an acute Extend angle to each other.
  • the pivot or rotation axis is preferably on or in the surface which is provided for engagement with the second valve element.
  • the angled arrangement of the sealing surface makes it possible, despite the intended pivoting movement in a common pivot axis, the valve seats may be located in mutually parallel planes.
  • the pump unit is designed as Umisselzpumpenaggregat and more preferably as Bankungsum stiilzpumpenaggregat.
  • it may be a Schuungsumicalzpumpenaggregat, which is used in a gas boiler.
  • the pump unit may 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, a drive motor in which rotor and stator a split tube or a split pot are separated from each other.
  • the drive motor has a permanent magnet rotor.
  • the drive motor may have a frequency converter for speed control.
  • the impeller and the interior of the pump housing can be dimensioned such that in the peripheral region of the impeller in the interior of the pump housing remains an annular space.
  • This annular clearance preferably has a size at 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, at least in a circumferential section in the peripheral region of the impeller.
  • the radius of the inner circumference of the pump housing over the entire circumference is dimensioned accordingly. More preferably, the radius of the inner circumference of the pump housing in at least one peripheral portion at least 2 or 3 times as large as the radius of the impeller.
  • valve elements are preferably arranged or dimensioned so that in each position, a clearance between the valve element and the outer periphery of the impeller remains, so that the circulating flow is not prevented by the valve element.
  • the pump unit 1 shown in the figures is designed as a circulating pump unit with a wet-running electric drive motor.
  • the pump unit 1 has a pump housing 2, which may be formed as a cast component of metal or plastic.
  • the pump housing 2 has a suction port 4 and two discharge 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 disposed inside the pump housing 2, which is rotatably connected to the rotor 16 of the electric drive motor.
  • the rotor 16 is rotatably supported 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 circumference of a split pot 21 is located, which separates the rotor space, in which the rotor 16 is disposed from the stator, so that the rotor space can be filled with liquid. It is thus a wet-running drive motor.
  • a receiving opening 22 extends radially outwards.
  • the receiving opening 22 forms part of an outlet-side flow path through which the flow accelerated by the impeller 14 emerges from the pump housing 2.
  • valve insert 28 Inserted from the outside into the receiving opening 22 is a valve insert 28, which has a closure plate 30 which closes the receiving opening 22 to the outside.
  • the closure plate 30 serves as a carrier and holds a pivot axis 32, to which a first valve element 34 and a second valve element 36 are pivotally mounted.
  • a torsion spring 38 is also arranged, which forms a return element and in the mounted state, the first valve element 34 and the second valve member 36 presses apart.
  • the two valve elements 34 and 36 are identical and arranged only rotated by 180 ° to each other.
  • Fig. 3 shows the valve core 28 in the assembled state prior to insertion into the receiving opening 22 of the pump housing 2.
  • the first and second valve elements 34, 36 are rotated 180 ° to each other, facing away from each other on the pivot axis 32, so that their outer surfaces facing away from each other 40 sealing surfaces form, which come to close the outputs 24 and 26 on the outer circumference, which each forms a valve seat, sealingly to the plant.
  • elastic sealing elements can be arranged on the outer circumference of the exits 24, 26 or on the sealing surfaces 40.
  • the flap-shaped valve elements 34 and 36 are formed so that in each case an opening 42 is formed in the sealing surface 40, which is located extends transversely to the sealing surface 40 through the valve member 34, 36 therethrough.
  • the opening 42 is seen in the direction of the pivot axis 32 eccentrically in the valve element 34, 36 is arranged.
  • the opening 42 is arranged in one half in the sealing surface 40 in the direction of the pivot axis 32 seen. Since the two identically formed valve elements 34 and 36 are arranged rotated through 180 ° to each other, thus the opening 42 in the first valve element 34 is offset from the opening 42 in the second valve element 36th In Fig. 4 the opening 42 in the first valve element 34 is in the upper half, while the opening 42 in the second valve element 36 is located in the lower half. This causes that when the two valve elements 34 and 36 come into contact with each other, the openings 42 in the two valve elements 34 and 36 are not aligned.
  • the valve elements 34 and 36 have, on their side facing away from the sealing surface 40, rather than the opening 42, an engagement element 44, which corresponds to its shape to the opening 42 on the same side.
  • the engagement element 44 of the first valve element 34 engages in the opening 42 of the second valve element 36 when the two valve elements come to rest against each other by 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 member 44 may be formed 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 the closure thereof.
  • Fig. 7 are the first and the second output 24 and 26 in the receiving opening 22 opposite to each other, wherein the valve seats formed by the edge of the outputs 24 and 26 are located in mutually parallel planes.
  • the first valve element 34 and the second valve element 36 by the torsion spring 38, which serves as a return element Pressed in its rest position, which represents a closed position in which the first valve element 34, the first output 24 and the second valve element 36, the second output 26 overlaps.
  • the first output and the second output are substantially 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 are the first and the second output 24 and 26 in the receiving opening 22 opposite to each other, wherein the valve seats formed by the edge of the outputs 24 and 26 are located in mutually parallel planes.
  • valve elements 34 and 36 are formed in a direction transverse to the pivot axis 32 so long that their pivot axis 32 spaced ends 46 extend into the interior 15 and thus into an annular space surrounding the impeller 14.
  • the adjoining the ends 46 surfaces in extension of the sealing surfaces 40 of the valve elements 34, 36 form engagement surfaces on which the rotating in the interior 15 flow upon rotation of the impeller 14 acts.
  • the arranged in the electronics housing 12 control device is designed so that it can drive the electric drive motor targeted in two different directions of rotation A and B. This can be done for example via a frequency converter, which energizes the coils in the stator targeted.
  • the valve device in the valve core 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 into the second outlet 26 and thus to the second pressure port 8.
  • the heating circuit of a heater for a building can be connected to the first pressure port 6, while a heat exchanger for heating service water connects to the second pressure port 8.
  • the direction of rotation is thus initially predetermined by the control device 12 in order to specify in which of the two outputs 24 or 26 is to be conveyed. 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 shown rest position, the outputs 24 and 26 are substantially closed except for the flow passages through the openings 42. The openings 42 effect a pressure equalization between both sides of the valve elements 34 and 36, so that the valve elements 34 and 36 are not pressed upon startup of the pump unit by the pressure forming in the interior 15 against the outputs 24 and 26.
  • valve members 34 and 36 are held in position substantially only by the torsion spring 38.
  • a rotating flow in the peripheral region of the impeller is generated in the interior 15 of the pump housing 2.
  • the flow also rotates in the direction of rotation A and thus acts on the engagement surface of the first valve element 34.
  • the flow thus generates on the first valve element 34 a force 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 member 34 abuts against the second valve element 36.
  • the first valve element 34 closes the opening 42 in the second valve element 36.
  • the second output 26, on which the second valve element 36 remains in abutment is now completely closed.
  • the first outlet 24 is fully open, so that the flow through this outlet 24 flows into the discharge nozzle 6.
  • the pressure prevailing in the interior 15 now acts on the sealing surface 40 of the first valve element 34, which via the abutment against the second valve element 36 presses this in additional sealing contact with the valve seat which surrounds the second outlet 26.
  • This state, in which the first valve element 34 is opened and thus a flow path through the first output 24 is opened to the discharge port 6, is in the Fig. 6A and 8A shown.
  • the control device in the electronics housing 12 can also adjust the acceleration of the drive motor so that when commissioning initially just as much pressure and flow are built to one of the valve elements 34, 36 in the desired open position move and then the engine is then accelerated so that the desired final pressure or flow is established.
  • valve elements 34 and 36 are dimensioned such that their free ends 46 are spaced apart at any angular position during pivotal movement about pivot axis 32 from the outer periphery of impeller 34 such that valve elements 34 and 36 do not collide with impeller 14.
  • the distance between the ends 46 and the outer periphery of the impeller 14 is selected so that there is always a free space through which the annular or rotating flow can extend in the peripheral region of the impeller 14.
  • the annular space 47 leads to an overall improved efficiency, especially when the impeller 14 has curved blades.
  • the receiving opening 22 is formed so 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 out after the casting of the pump housing 2 in the radial direction to the outside. This allows a simple production of the receiving space 22nd
  • valve elements 34 and 36 are hinged to the pivot axis, that the Pivot axis 32 relative to the axis of rotation x of the impeller at the radially outer end of the valve elements 34, 36 is arranged, that is, the pivot axis 32 is maximally spaced from the impeller or the axis of rotation x in the radial direction.
  • the pivot axis 32 'but could also be located at the radially inner end of the valve elements 34' and 36 '.
  • valve element 34 'and 36' may correspond to the embodiment described above.
  • openings 42 may also be provided.
  • the circulating pump unit according to the invention is preferably used in a heating system, in particular in a gas boiler, which are also the subject of the invention.
  • a heating system with a gas boiler 48 is shown schematically in FIG Fig. 11 shown.
  • the gas boiler 48 includes a burner 50 with a primary heat exchanger 52, via which the water is heated in the heating circuit.
  • the water is conveyed through the heating circuit.
  • the control device 12 of the pump unit 1 the direction of rotation is predetermined in the manner described above, whereby the valve arrangement formed by the valve elements 34, 36 valve arrangement is switched.
  • the valve arrangement serves to switch over the flow path between a heating circuit 54, which runs through a building, and a secondary heat exchanger 55, which serves for the heating of service water.
  • the heating circuit 54 passes through one or more radiators 56, wherein Within the meaning of this description, radiators are also considered to be circles of underfloor heating. Depending on the direction of rotation A, B, the flow either through the secondary heat exchanger 55 or the heating circuit 54.
  • the system is preferably designed so that the rotational direction 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. This ensures that the pump unit 1 works most of the operating time with the maximum efficiency, since the direction of rotation, at which the water is passed through the secondary heat exchanger 55, is usually used less frequently, since the operating times for hot water heating are usually lower as the operating hours for heating a building.
  • 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 preferably the pump unit 1 and the secondary heat exchanger 55 in a hydraulic _Bauillon, that is integrated 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)
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 true EP3267042A1 (fr) 2018-01-10
EP3267042B1 EP3267042B1 (fr) 2020-01-15

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ID=56403993

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

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USD979481S1 (en) 2020-02-13 2023-02-28 Michael Padgett Sea chest assembly
USD949926S1 (en) * 2020-02-13 2022-04-26 Michael Padgett Pump
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
US12085081B1 (en) * 2023-09-23 2024-09-10 Cooper-Standard Automotive Inc. Fluid pump and valve switch

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Also Published As

Publication number Publication date
US20180010609A1 (en) 2018-01-11
CN107588202A (zh) 2018-01-16
CN107588202B (zh) 2020-04-21
US10514038B2 (en) 2019-12-24
EP3267042B1 (fr) 2020-01-15

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