EP3267042B1 - Pump unit - Google Patents
Pump unit Download PDFInfo
- 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
Links
- 238000007789 sealing Methods 0.000 claims description 28
- 238000010438 heat treatment Methods 0.000 claims description 27
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 13
- 230000033001 locomotion Effects 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 229920001971 elastomer Polymers 0.000 description 2
- 239000008236 heating water Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000005406 washing Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 239000008235 industrial water Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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- 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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Description
Die Erfindung betrifft ein Pumpenaggregat mit den im Oberbegriff des Anspruchs 1 angegebenen Merkmalen.The invention relates to a pump unit with the features specified in the preamble of
In Heizungsanlagen, insbesondere Kompaktheizungsanlagen, stellt sich das Problem, den Heizwasser-Kreislauf zwischen zwei Strömungswegen umzuschalten, nämlich einmal durch einen Heizkreislauf im Gebäude und einmal durch einen Wärmetauscher zum Erwärmen von Brauchwasser. Dazu ist es bekannt, Pumpenaggregate mit integrierten Ventilelementen einzusetzen, welche in Abhängigkeit von der Drehrichtung des Laufrades des Pumpenaggregates zwischen zwei möglichen Strömungswegen umschalten. In der Regel ist hierzu ein bewegliches Ventilelement vorgesehen, welches von der Strömung um das Laufrad mitgenommen wird und je nach Strömungsrichtung gegen einen von zwei möglichen Ausgängen gedrückt wird, um diesen zu verschließen, so dass die Strömung durch den jeweils anderen Ausgang das Pumpenaggregat verlässt. Das heißt, das Ventilelement schließt die Ausgänge derart abwechselnd, dass immer ein Ausgang geschlossen und gleichzeitig der andere Ausgang geöffnet ist. Aus der
Im Hinblick auf diese Problematik ist es Aufgabe der Erfindung, ein Pumpenaggregat mit einem durch die Drehrichtung des Antriebsmotors umschaltbaren Ventilelement dahingehend zu verbessern, dass ein möglichst geräuschloses Schalten des Ventilelementes möglich ist.In view of these problems, it is an object of the invention to improve a pump unit with a valve element which can be switched over by the direction of rotation of the drive motor, so that the valve element can be switched as silently as possible.
Diese Aufgabe wird durch ein Pumpenaggregat mit den in Anspruch 1 angegebenen Merkmalen gelöst. Bevorzugte Ausführungsformen ergeben sich aus den Unteransprüchen, der nachfolgenden Beschreibung sowie den beigefügten Figuren.This object is achieved by a pump unit with the features specified in
Das erfindungsgemäße Pumpenaggregat weist ein Pumpengehäuse auf, in welchem ein Laufrad drehbar angeordnet ist. Das Laufrad rotiert dabei im Innenraum des Pumpengehäuses. Das Laufrad ist in bekannter Weise mit einem Sauganschluss bzw. Saugstutzen verbunden. Das Pumpenaggregat weist ferner einen elektrischen Antriebsmotor auf, dessen Rotor mit dem Laufrad derart drehfest verbunden ist, dass der elektrische Antriebsmotor das Laufrad drehend antreibt. Bevorzugt ist der Antriebsmotor bzw. dessen Statorgehäuse mit dem Pumpengehäuse in bekannter Weise verbunden.The pump unit according to the invention 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.
Der Antriebsmotor ist so ausgebildet, dass er gezielt wahlweise in zwei Drehrichtungen antreibbar ist. Dazu kann eine geeignete Steuereinrichtung vorgesehen sein, welche den Antriebsmotor so ansteuert, dass er in einer gewünschten Drehrichtung rotiert. Dazu steuert die Steuereinrichtung vorzugsweise die Bestromung der Statorspulen des Antriebsmotors. Die Steuereinrichtung kann insbesondere einen Frequenzumrichter beinhalten, über welchen neben der Drehrichtung vorzugsweise auch die Drehzahl des Antriebsmotors regelbar ist. Abhängig von der Drehrichtung des Antriebsmotors rotiert auch das Laufrad somit wahlweise in zwei gewünschten entgegengesetzten Drehrichtungen.The drive motor is designed so that it can be selectively driven in two directions of rotation. For this purpose, 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. For this purpose, 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. Depending on the direction of rotation of the drive motor, the impeller also rotates optionally in two desired opposite directions of rotation.
In dem Pumpengehäuse ist ferner eine Ventilanordnung angeordnet, welche einen austrittseitigen Strömungsweg, das heißt den Strömungsweg stromabwärts des Laufrades zwischen zwei in dem Pumpengehäuse ausgebildeten Ausgängen umschaltet. Bei Verwendung des Pumpenaggregates in einer Heizungsanlage kann beispielsweise einer der Ausgänge mit einem Heizkreislauf durch das Gebäude und der andere Ausgang mit einem Sekundärwärmetauscher zum Erwärmen des Brauchwassers versehen sein. Die Ventilanordnung ist vorzugsweise so ausgebildet, dass sie durch die von dem Laufrad verursachte Strömung zwischen zwei Schaltstellungen bewegbar ist, wobei je nach Drehrichtung des Laufrades die Strömung im Umfangsbereich des Laufrades ebenfalls in unterschiedlichen Richtungen gerichtet ist. Durch die unterschiedlichen Strömungsrichtungen kann ein Ventilelement der Ventilanordnung gezielt zwischen mehreren Schaltstellungen bewegt werden.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. When using the pump set in a heating system, for example, one of the exits with a heating circuit through the building and the other outlet can be provided with a secondary heat exchanger for heating the domestic water. 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.
Erfindungsgemäß weist die Ventilanordnung zwei Ventilelemente auf, wobei ein erstes bewegliches Ventilelement an einem ersten der beiden Ausgänge und ein zweites bewegliches Ventilelement an einem zweiten der zwei Ausgänge angeordnet ist. So dient das erste Ventilelement dazu, den ersten Ausgang zu verschließen, während das zweite Ventilelement dazu dient, den zweiten Ausgang zu verschließen. Die Ventilelemente sind so angeordnet bzw. ausgestaltet, dass sie sich in einer Ruhelage, das heißt wenn das Laufrad stillsteht, in ihrer geschlossenen Stellung befinden. Das heißt in der Ruhelage verschließt das erste Ventilelement den ersten Ausgang zumindest teilweise und das zweite Ventilelement den zweiten Ausgang zumindest teilweise. Unter einem teilweise Verschließen der Ausgänge ist im Sinne dieser Erfindung zu verstehen, dass der Ausgang in der geschlossenen Stellung in seinem Querschnitt gegenüber der geöffneten Stellung verkleinert ist, vorzugsweise um mehr als die Hälfte, weiter bevorzugt um mehr als zwei Drittel verkleinert ist. Wie unten dargelegt, verbleibt vorzugsweise auch in der geschlossenen Stellung ein gewisser Strömungsdurchgang.According to the invention, 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. For the purposes of this invention, 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.
Ferner sind die Ventilelemente so angeordnet und ausgestaltet, dass das erste Ventilelement durch eine von dem Laufrad in dessen erster Drehrichtung verursachten Strömung in eine geöffnete Stellung bewegbar ist, während das zweite Ventilelement durch eine von dem Laufrad in dessen zweiter Drehrichtung verursachten Strömung in eine geöffnete Stellung bewegbar ist. Wenn durch die Strömung das erste Ventilelement in seine geöffnete Stellung bewegt wird, verbleibt gleichzeitig das zweite Ventilelement in seiner geschlossenen Stellung. Umgekehrt verbleibt das erste Ventilelement in seiner geschlossenen Stellung, wenn das zweite Ventilelement durch die Strömung, welche bei Drehung des Laufrades in der zweiten Drehrichtung auftritt, in seine geöffnete Stellung bewegt wird.Furthermore, the 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.
Die erfindungsgemäße Ausgestaltung hat gegenüber den bekannten drehrichtungsabhängigen Schalteinrichtungen den Vorteil, dass die Ausgänge in der Ruhelage im Wesentlichen geschlossen sind. Dies bewirkt, dass bei Inbetriebnahme des Pumpenaggregates eine Strömung zunächst im Wesentlichen nur im Inneren des Pumpengehäuses erzeugt wird, um abhängig von der Drehrichtung eines der Ventilelemente in seine geöffnete Stellung zu bewegen. Dadurch, dass im Wesentlichen keine Strömung durch die Ausgänge erfolgt, werden Wasserschläge beim Umschalten bei Inbetriebnahme des Pumpenaggregates minimiert bzw. vermieden. Das bedeutet bei der Inbetriebnahme des Pumpenaggregates wird zunächst im Inneren des Pumpenaggregates eine Strömung erzeugt, deren hydraulische Energie zum Bewegen eines der Ventilelemente verwendet wird.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.
Bei der Inbetriebnahme des Pumpenaggregates öffnet stets ein Ventilelement, das heißt eines der Ventilelemente wird abhängig von der Drehrichtung in seine geöffnete Stellung bewegt. Wenn das Pumpenaggregat ausgeschaltet wird, das heißt das Laufrad zum Stillstand kommt, bewegt sich das Ventilelement wieder zurück in seine geschlossene Stellung. Zum Umschalten der Ventileinrichtung wird dann der Antriebsmotor in umgekehrter Drehrichtung angetrieben, so dass das Laufrad im Inneren des Pumpengehäuses eine Strömung in entgegengesetzter Richtung erzeugt, welche das andere Ventilelement öffnet und so die Strömung durch den anderen Ausgang aus dem Pumpengehäuse nach außen leitet.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. When the pump set is switched off, i.e. the impeller comes to a standstill, the valve element moves back into its closed position. To switch the valve device, 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.
Die erfindungsgemäße Ausgestaltung ermöglicht durch die gezielte Ansteuerung des Antriebsmotors, das heißt insbesondere nicht nur durch die Wahl der Drehrichtung, sondern auch des Beschleunigungsverlaufes, ein sehr sanftes und geräuscharmes Umschalten zwischen den beiden Strömungswegen, welche durch die zwei Ausgänge definiert werden.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.
Bevorzugt sind das erste und das zweite Ventilelement unabhängig voneinander bewegbar. Es ermöglicht, dass das erste Ventilelement in seiner geschlossenen Stellung verbleibt, während sich das zweite Ventilelement in seine geöffnete Stellung bewegt und umgekehrt.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.
Bevorzugt sind ferner das erste und das zweite Ventilelement jeweils als eine um eine Schwenkachse zwischen der geöffneten Stellung und der geschlossenen Stellung schwenkbare Klappe ausgebildet. Dabei kommt die Klappe vorzugsweise mit einer Oberfläche dichtend an einem einen zugehörigen Ausgang umgebenden Ventilsitz zur Anlage. Bevorzugt sind die Ventilelemente so angeordnet, dass ihre Schwenkachse an einem Längsende gelegen ist, wobei dieses Längsende vorzugsweise dasjenige Längsende ist, welches am weitesten vom Laufrad beabstandet ist. Die Schwenkachse bzw. Schwenkachsen der Klappen erstrecken sich weiter bevorzugt parallel zur Drehachse des Laufrades, wobei sich die Klappen im Wesentlichen radial zum Laufrad erstrecken.Furthermore, the 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.
Weiter bevorzugt weisen die Ventilelemente einen Dichtbereich bzw. eine Dichtfläche auf, welche mit einem korrespondierenden Ventilsitz, welcher den zugehörigen Ausgang umgibt, in dichtende Anlage treten kann. Zusätzlich weisen die Ventilelemente vorzugsweise eine Angriffsfläche bzw. einen Angriffsbereich auf, auf welche die von dem Laufrad erzeugte Strömung zur Bewegung des Ventilelementes wirkt. Wenn das Ventilelement, wie oben beschrieben, als Klappe ausgebildet ist, wird der Angriffsbereich vorzugsweise von einem von der Schwenkachse beabstandeten axialen Endbereich der Klappe gebildet. Der Angriffsbereich erstreckt sich vorzugsweise in einen das Laufrad umgebenden Ringraum des Pumpengehäuses hinein, so dass die in diesem Ringraum von dem Laufrad erzeugte Strömung direkt auf den Angriffsbereich wirken kann.The 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. In addition, the 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. If the valve element is designed as a flap, as described above, 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.
Gemäß einer weiter bevorzugten Ausführungsform sind das ersten und das zweite Ventilelement um dieselbe Schwenkachse schwenkbar. Dies kann, wie oben beschrieben, eine Schwenkachse sein, welche sich vorzugsweise parallel zur Drehachse des Laufrades erstreckt. Vorzugsweise sind dabei die Ventilelemente in der vorangehend beschriebenen Weise klappenförmig ausgebildet, wobei die Klappen mit einem Ende an der Schwenkachse angelenkt sind und das entgegengesetzte freie Ende der Klappen jeweils eine Angriffsfläche bzw. einen Angriffsbereich für die Strömung bildet. Der Dichtbereich bzw. die Dichtfläche liegt vorzugsweise zwischen dem Angriffsbereich und der Schwenkachse. Die Schwenkachse ist dabei bevorzugt an dem Ende der Klappe angeordnet, welches am weitesten von dem Laufrad beabstandet ist.According to a further preferred embodiment, the first and the second valve element can be pivoted about the same pivot axis. As described above, 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.
Weiter bevorzugt sind die Ventilelemente so ausgestaltet und angeordnet, dass sie, wenn sich eines der Ventilelemente in seiner geöffneten Stellung befindet, miteinander in Anlage sind. Das heißt bevorzugt verschwenkt das sich in die geöffnete Stellung bewegende Ventilelement so weit, bis es an dem anderen, in seiner geschlossenen Stellung verweilenden Ventilelement, zur Anlage kommt. Diese Ausgestaltung hat den Vorteil, dass der freigegebene Strömungsweg zu dem geöffneten Ausgang maximiert wird und dass geöffnete Ventilelement zusätzlich das in seiner geschlossenen Stellung befindliche Ventilelement in seine geschlossene Stellung drückt und/oder eine zusätzliche Abdichtfunktion übernehmen kann, wie sie unten beschrieben werden wird.The 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.
Erfindungsgemäß weisen die Ventilelemente jeweils eine Öffnung auf, welche einen Strömungsdurchgang in den zugehörigen Ausgang auch in einer geschlossenen Stellung dieses Ventilelementes ermöglicht. Das heißt die Öffnung erstreckt sich von derjenigen Seite des Ventilelementes, welche dem Innenraum des Pumpengehäuses, das heißt dem Laufrad, zugewandt ist, in den Ausgang hinein. Diese Öffnungen in den Ventilelementen sind bevorzugt so dimensioniert, dass die Ausgänge in den geschlossenen Stellungen der Ventilelemente im Wesentlichen, das heißt wie oben beschrieben, Großteils geschlossen werden, aber ein geringer Strömungsdurchgang verbleibt. Die Öffnung sorgt im Wesentlichen dafür, dass ein Druckausgleich zwischen beiden Seiten des Ventilelementes gegeben ist. Dieser Druckausgleich sorgt dafür, dass beim Anlaufen des Laufrades das Ventilelement nicht durch den im Pumpengehäuse erzeugten Druck gegen den Ventilsitz gedrückt wird. Dadurch wird die durch die Strömung zu überwindende Haltekraft verringert, so dass sich das Ventilelement leichter von der geschlossenen in die geöffnete Stellung bewegen lässt. Dies unterstützt ein geräuschloses sanftes Umschalten der Ventileinrichtung durch Bewegung eines der Ventilelemente.According to the invention, 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. This means that the opening extends from the side of the valve element which faces the interior of the pump housing, that is to say the impeller, into the outlet. 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.
Bevorzugt sind die Öffnung in dem ersten Ventilelement und die Öffnung in dem zweiten Ventilelement derart versetzt zueinander angeordnet, dass die Öffnung in dem ersten Ventilelement durch das zweite Ventilelement und die Öffnung in dem zweiten Ventilelement durch das erste Ventilelement verschlossen werden, wenn die beiden Ventilelemente miteinander in Anlage sind. Das heißt, das sich in seiner geöffneten Stellung befindliche Ventilelement verschließt dadurch, dass es an dem anderen Ventilelement, welches in seiner geschlossenen Stellung ist, zur Anlage kommt, gleichzeitig die Öffnung in demjenigen Ventilelement, welches sich in seiner geschlossenen Stellung befindet. Erst durch das Öffnen eines der Ventilelemente wird das andere Ventilelement und dadurch der zugehörige Ausgang vollständig verschlossen. In diesem Zustand wirkt dann der von dem Pumpenaggregat erzeugte Druck auf die beiden Ventilelemente, so dass diese Ventilelemente gegeneinander und das Ventilelement, welches sich in seiner geschlossenen Stellung befindet, gegen den zugehörigen Ventilsitz gedrückt wird. In diesem Zustand ist dann der zugehörige Ausgang von dem Ventilelement, welches sich in seiner geschlossenen Stellung befindet, vollständig geschlossen. Das heißt aufgrund der so angeordneten Öffnungen wird erreicht, dass in der Ruhestellung und beim Anfahren des Pumpenaggregates, wenn sich beide Ventilelemente in ihrer geschlossenen Stellung befinden, die Ventilelemente im Wesentlichen nicht von Druck beaufschlagt sind. Wenn jedoch eines der Ventilelemente in seiner geöffneten Stellung ist, wird das andere Ventilelement, welches sich in seiner geschlossenen Stellung befindet, von dem vom Laufrad erzeugten Druck beaufschlagt und in der geschlossenen Stellung gehalten.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. In this state, the associated outlet from the valve element, which is in its closed position, is then completely closed. That is to say, on account of the openings arranged in this way, it is achieved that in the rest position and when starting up the pump assembly, when both valve elements are in their closed position, the valve elements are essentially not pressurized. However, when one of the valve elements is in its open position, the other valve element, which is in its closed position, is acted upon by the pressure generated by the impeller and held in the closed position.
Weiter bevorzugt sind das erste und das zweite Ventilelement durch zumindest ein Rückstellelement derart kraftbeaufschlagt, dass sie bei Stillstand des Laufrades jeweils in ihrer geschlossenen Stellung gehalten werden, wobei vorzugsweise das erste und das zweite Ventilelement durch ein gemeinsames Rückstellelement, insbesondere durch eine zwischen dem Ventilelementen angeordnete Feder, kraftbeaufschlagt sind. Das oder die Rückstellelemente sorgen somit dafür, dass nach dem Abschalten des Pumpenaggregates, wenn das Laufrad zum Stillstand kommt, die Ventilelemente wieder in ihre Ruhelage, das heißt ihre geschlossene Stellung, zurückbewegt werden. Wenn ein gemeinsames Federelement vorhanden ist, so kann das Federelement besonders bevorzugt als Drehfeder ausgebildet sein, welche sich um eine gemeinsame Dreh- bzw. Schwenkachse der beiden Ventilelemente dreht und mit ihren freien Schenkeln jeweils mit einem der Ventilelemente in Eingriff bzw. Anlage ist. Dies ermöglicht einen besonders einfachen Aufbau und eine einfache Montage, da die Drehfeder gemeinsam mit den beiden Ventilelementen auf eine gemeinsame Schwenk- bzw. Drehachse aufgeschoben werden kann.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. If a common spring element is present, 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.
Die Ventilelemente können elastisch oder starr ausgebildet sein. Wenn die Ventilelemente elastisch ausgebildet sind, können sie im einfachsten Fall als Laschen bzw. Klappen aus einem Gummi- bzw. Elastomermaterial ausgebildet sein. Wenn die Ventilelemente elastisch ausgebildet sind, können die elastischen Rückstellkräfte, welche beim Verformen des Ventilelementes erzeugt werden, das beschriebene Rückstellelement bilden. Derartige Ventilelemente können durch Verformung von der geschlossenen in die geöffnete Stellung bewegt werden. Wenn die Ventilelemente starr ausgebildet sind, drehen sie sich vorzugsweise um feststehende Schwenk- bzw. Drehachsen, insbesondere um eine gemeinsame Schwenk- oder Drehachse. Die starren Ventilelemente sind im Wesentlichen starr ausgebildet, können aber zusätzlich elastische Bereiche bzw. Abschnitte haben, welche besonders bevorzugt stoffschlüssig mit den starren Abschnitten verbunden sein können. Die starren Ventilelemente können z.B. zusätzlich mit elastischen Dichtflächen bzw. elastischen Abschnitten versehen sein.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.
Vorzugsweise ist jeweils an den Ventilelementen und/oder diesen gegenüberliegenden Ventilsitzen eine elastische Dichtung angeordnet. Diese sorgt für eine zuverlässige Abdichtung des Ausganges, wenn das Ventilelement in seiner geschlossenen Stellung ist. Zusätzlich kann eine elastische Dichtung zwischen den beiden Ventilelementen vorgesehen sein, wenn diese in der oben beschriebenen Weise Öffnungen aufweisen. Ein solches zusätzliches Dichtelement sorgt für eine Abdichtung im Bereich der Öffnung desjenigen Ventilelementes, welches sich in seiner geschlossen Stellung befindet, wenn das zweite Ventilelement an diesem zur Anlage kommt. So kann die Öffnung in dem Ventilelement an der Seite des Ventilelementes, welche dem zweiten Ventilelement zugewandt ist, von einer elastischen Dichtung umgeben sein. Alternativ oder zusätzlich kann an den Ventilelementen eine Dichtfläche dort in einem Bereich ausgebildet sein, welcher die Öffnung des anderen Ventilelementes überdeckt, wenn die beiden Ventilelemente miteinander in Anlage treten.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. In addition, 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. Thus, 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. Alternatively or additionally, 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.
Gemäß einer besonderen Ausführungsform der Erfindung weist das Pumpengehäuse eine zwischen den beiden Ausgängen gelegene Aufnahmeöffnung auf, welche zum Innenraum des Pumpengehäuses hin geöffnet ist und in welche von der Außenseite des Pumpengehäuses her die beiden Ventilelemente eingesetzt sind, wobei die beiden Ventilelemente vorzugsweise in einem in die Aufnahmeöffnung eingesetzten Ventileinsatz gelagert sind. Die Aufnahmeöffnung ist nach außen hin durch eine Deckel dicht verschlossen, wobei dieser Deckel vorzugsweise Teil des Ventileinsatzes ist. Dadurch wird die Montage vereinfacht, da die Ventilelemente von außen in das Pumpengehäuse eingesetzt werden können. Ferner sind die Ventilelemente zu Wartungszwecken leicht zugänglich, ohne die übrigen Teile des Pumpenaggregates zerlegen zu müssen. Die Aufnahmeöffnung ist vorzugsweise so geformt, dass sie von außen her gesehen keine Hinterschneidungen aufweist. So lässt sich das Pumpengehäuse mit der Aufnahmeöffnung leicht als Gussteil, insbesondere als Spritzgussteil aus Kunststoff fertigen, wobei ein Kern, welcher die Aufnahmeöffnung definiert, nach außen aus dem Pumpengehäuse herausgezogen werden kann. So kann an dieser Stelle auf einen verlorenen Kern verzichtet werden.According to a particular embodiment of the invention, 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. Thus, 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.
Die beschriebenen beiden Ausgänge des Pumpengehäuses sind vorzugsweise in der Aufnahmeöffnung gelegen bzw. zweigen von der Aufnahmeöffnung ab. Das heißt die Strömung tritt ausgehend von dem Innenraum des Pumpengehäuses, in welchem das Laufrad rotiert, zunächst in die Aufnahmeöffnung ein und dann von dort in einen der beiden Ausgänge, je nachdem welches Ventilelement sich in seiner geöffneten Stellung befindet.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.
Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung weisen die beiden Ausgänge jeweils einen dem Innenraum des Pumpengehäuses zugewandten bzw. im Strömungsweg von dem Innenraum gelegenen Ventilsitz auf, an welchem das zugehörige Ventilelement mit einer Dichtfläche in seiner geschlossenen Stellung zur Anlage kommt, um den jeweiligen Ausgang zumindest teilweise zu verschließen. Die Ventilsitze der beiden Ausgänge liegen vorzugsweise einander gegenüber, wobei die Ventilsitze sich besonders bevorzugt im Wesentlichen parallel zueinander erstrecken. Wenn die Ventilsitze in der Aufnahmeöffnung gelegen sind, erstrecken sich die Ventilsitze bevorzugt im Wesentlichen parallel zur Längsrichtung der Aufnahmeöffnung an zwei einander gegenüberliegenden Seitenwänden der Aufnahmeöffnung. Eine im Wesentlichen parallele Anordnung der Ventilsitze bedeutet, dass leichte Entformungsschrägen, welche erforderlich sind, um einen Kern nach dem Gießen aus der Aufnahmeöffnung zu entnehmen, in diesem Sinne noch als parallele Anordnung angesehen werden. Die gegenüberliegende Anordnung der Ventilsitze ermöglicht es, dass sich dasjenige Ventilelement, welches sich in seine geöffnete Stellung bewegt, zu dem zweiten Ventilelement, welches sich in einer geschlossenen Stellung befindet, hin bewegen kann und mit diesem Ventilelement, wie oben beschrieben, in Anlage treten kann. Dies gilt insbesondere, wenn die Ventilelemente eine schwenkende Bewegung von der geschlossenen in die geöffnete Stellung vollziehen. Wenn die Ventilelemente derart schwenkbar angeordnet sind, erstrecken sich die Schwenkachsen bevorzugt parallel zu den von den Ventilsitzen aufgespannten Flächen. Bei einer gemeinsamen Schwenkachse ist diese vorzugsweise mit in einer Ebene gelegen, welche zwischen den von den Ventilsitzen aufgespannten Flächen gelegen ist.According to a further preferred embodiment of the invention, 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. The opposite arrangement of the 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. If the valve elements are arranged so as to be pivotable, 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.
Die Ventilelemente weisen weiter bevorzugt jeweils eine zur Anlage an einem Ventilsitz vorgesehene Dichtfläche auf, welche sich gewinkelt zu einem Radius bezüglich der Schwenkachse des jeweiligen Ventilelementes erstreckt. Derartige Ventilelemente weisen in einer Ebene normal zu der Schwenkachse vorzugsweise eine im Wesentlichen dreieckige Gestalt auf, wobei sich eine Seite des Dichtelementes, welche die Dichtfläche bildet und eine zweite Seite des Ventilelementes, welche zur Anlage an dem zweiten Ventilelement vorgesehen ist, vorzugsweise in einem spitzen Winkel zueinander erstrecken. Die Schwenk- oder Drehachse liegt dabei bevorzugt an oder in der Fläche, welche zur Anlage mit dem zweiten Ventilelement vorgesehen ist. Die gewinkelte Anordnung der Dichtfläche ermöglicht es, dass trotz der vorgesehenen schwenkenden Bewegung bei einer gemeinsamen Schwenkachse, die Ventilsitze in sich parallel zueinander erstreckenden Ebenen gelegen sein können.The 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.
Besonders bevorzugt ist das Pumpenaggregat als Umwälzpumpenaggregat und weiter bevorzugt als Heizungsumwälzpumpenaggregat ausgebildet. Insbesondere kann es sich um ein Heizungsumwälzpumpenaggregat handeln, welches in einer Gastherme eingesetzt ist. Allerdings ist eine Gastherme mit einem Pumpenaggregat, wie es vorangehend und nachfolgend beschrieben wird, nicht Teil der Erfindung. Dabei kann das Pumpenaggregat Teil eines hydraulischen Blockes sein, welcher eine integrierte Baueinheit für eine Kompaktheizungsanlage und insbesondere für eine Gastherme bildet.The pump assembly is particularly preferably designed as a circulation pump assembly and more preferably as a heating circulation pump assembly. In particular, it can be a heating circulation pump unit which is used in a gas boiler. However, 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.
Der Antriebsmotor ist vorzugsweise ein nasslaufender Antriebsmotor, das heißt ein Antriebsmotor, bei welchem Rotor und Stator durch ein Spaltrohr bzw. einen Spalttopf voneinander getrennt sind. Besonders bevorzugt weist der Antriebsmotor einen Permanentmagnetrotor auf. Weiter bevorzugt kann der Antriebsmotor einen Frequenzumrichter zur Drehzahlregulierung aufweisen.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.
Gemäß einem weiteren bevorzugten Ausführungsbeispiel, das nicht Teil der Erfindung ist, können das Laufrad und der Innenraum des Pumpengehäuses derart dimensioniert sein, dass im Umfangsbereich des Laufrades im Inneren des Pumpengehäuses ein ringförmiger Freiraum verbleibt. Dieser ringförmige Freiraum hat bevorzugt eine Größe, bei welcher der Radius des Innenumfanges des Pumpengehäuses zumindest in einem Umfangsabschnitt im Umfangsbereich des Laufrades zumindest 1,4 mal und vorzugsweise zumindest 2 mal so groß wie der Radius des Laufrades ist. Besonders bevorzugt ist der Radius des Innenumfanges des Pumpengehäuses über den gesamten Umfang entsprechend dimensioniert. Weiter bevorzugt ist der Radius des Innenumfanges des Pumpengehäuses in zumindest einem Umfangsabschnitt mindestens 2 oder 3 mal so groß wie der Radius des Laufrades. Durch diesen ringförmigen Freiraum, welcher das Laufrad umgibt, wird die Ausbildung einer umfänglich rotierenden Strömung begünstigt, welche abhängig von der Drehrichtung des Laufrades verläuft und so die Ventilelemente in die gewünschte Schaltstellung bewegen kann. Die Ventilelemente sind bevorzugt so angeordnet bzw. dimensioniert, dass in jeder Stellung ein Freiraum zwischen Ventilelement und Außenumfang des Laufrades verbleibt, so dass die zirkulierende Strömung nicht durch das Ventilelement unterbunden wird.According to a further preferred exemplary embodiment, which is not part of the invention, 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. This annular free space, which surrounds the impeller, favors the formation of a circumferentially rotating flow which is dependent on the direction of rotation of the impeller and can thus move the valve elements into the desired switching position. The 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.
Nachfolgend wird die Erfindung deren Schutzumfang ausschließlich durch die nachfolgenden Ansprüche bestimmt ist, beispielhaft anhand der beigefügten Figuren beschrieben. In diesen zeigt:
- Fig. 1
- eine perspektivische Gesamtansicht eines erfindungsgemäßen Pumpenaggregates,
- Fig. 2
- eine Explosionsansicht des Pumpenaggregates gemäß
Fig. 1 , - Fig. 3
- eine perspektivische Draufsicht auf das Pumpengehäuse mit herausgenommenem Ventileinsatz,
- Fig. 4
- die Anordnung der Ventilelemente in perspektivischer Ansicht,
- Fig. 5
- eine perspektivische Ansicht des offenen Pumpengehäuses, wobei sich die Ventilelemente in ihrer Ruhestellung befinden,
- Fig. 6A
- eine Ansicht gemäß
Fig. 5 , in welcher sich das erste der Ventilelemente in seiner geöffneten Stellung befindet, - Fig. 6B
- eine Ansicht gemäß
Fig. 5 , in welcher sich das zweite Ventilelement in seiner geöffneten Stellung befindet, - Fig. 7
- eine Schnittansicht des Pumpengehäuses, in welcher sich die Ventilelemente in ihrer Ruhestellung befinden,
- Fig. 8A
- eine Schnittansicht gemäß
Fig. 7 , wobei sich das erste der Ventilelemente in einer geöffneten Stellung befindet, - Fig. 8B
- eine Schnittansicht gemäß
Fig. 7 , wobei sich das zweite der Ventilelemente in einer geöffneten Stellung befindet, - Fig. 9
- schematisch eine Anordnung der Ventilelemente im Pumpengehäuse gemäß einer zweiten Ausführungsform der Erfindung, wobei sich die Ventilelemente in ihrer geschlossenen Stellung befinden,
- Fig. 10
- eine Ansicht gemäß
Fig. 9 , in welcher sich eines der Ventilelemente in einer geöffneten Stellung befindet, und - Fig. 11
- das Schaltbild einer Heizungsanlage mit einem erfindungsgemäßen Pumpenaggregat.
- Fig. 1
- an overall perspective view of a pump unit according to the invention,
- Fig. 2
- an exploded view of the pump unit according to
Fig. 1 . - Fig. 3
- 3 shows a perspective top view of the pump housing with the valve insert removed,
- Fig. 4
- the arrangement of the valve elements in a perspective view,
- Fig. 5
- a perspective view of the open pump housing, the valve elements being in their rest position,
- Figure 6A
- a view according to
Fig. 5 , in which the first of the valve elements is in its open position, - Figure 6B
- a view according to
Fig. 5 , in which the second valve element is in its open position, - Fig. 7
- 2 shows a sectional view of the pump housing in which the valve elements are in their rest position,
- Figure 8A
- a sectional view according to
Fig. 7 , the first of the valve elements being in an open position, - Figure 8B
- a sectional view according to
Fig. 7 , the second of the valve elements being in an open position, - Fig. 9
- schematically an arrangement of the valve elements in the pump housing according to a second embodiment of the invention, the valve elements being in their closed position,
- Fig. 10
- a view according to
Fig. 9 , in which one of the valve elements is in an open position, and - Fig. 11
- the circuit diagram of a heating system with a pump unit according to the invention.
Das in den Figuren gezeigte Pumpenaggregat 1 ist als ein Umwälzpumpenaggregat mit einem nasslaufenden elektrischen Antriebsmotor ausgebildet. Das Pumpenaggregat 1 weist ein Pumpengehäuse 2 auf, welches als Gussbauteil aus Metall oder Kunststoff ausgebildet sein kann. Das Pumpengehäuse 2 weist einen Sauganschluss 4 und zwei Druckstutzen 6 und 8 auf. An das Pumpengehäuse 2 angesetzt ist ein Motor- bzw. Statorgehäuse 10, in welchem der elektrische Antriebsmotor angeordnet ist. An dem den Pumpengehäuse 2 abgewandten Axialende des Statorgehäuses 10 ist ein Elektronikgehäuse 12 angeordnet, in welchem eine Steuer- bzw. Regeleinrichtung zur Steuerung des elektrischen Antriebsmotors angeordnet ist.The
Wie in der Explosionsansicht gemäß
Ausgehend von dem Innenraum 15 des Pumpengehäuses 2, in welchem das Laufrad 14 rotiert, erstreckt sich radial nach außen eine Aufnahmeöffnung 22. Die Aufnahmeöffnung 22 bildet Teil eines austrittsseitigen Strömungsweges, durch welchen die von dem Laufrad 14 beschleunigte Strömung aus dem Pumpengehäuse 2 austritt. So zweigen die Druckstutzen 6 und 8 an einem ersten Ausgang 24 und einem zweiten Ausgang 26, welche im Inneren der Aufnahmeöffnung 22 gelegen sind, ab (siehe
Von außen in die Aufnahmeöffnung 22 eingesetzt ist ein Ventileinsatz 28, welcher eine Verschlussplatte 30 aufweist, welche die Aufnahmeöffnung 22 nach außen verschließt. Die Verschlussplatte 30 dient gleichzeitig als Träger und hält eine Dreh- bzw. Schwenkachse 32, an welcher ein erstes Ventilelement 34 und ein zweites Ventilelement 36 schwenkbar gelagert sind. Auf der Schwenkachse 32 ist darüber hinaus eine Drehfeder 38 angeordnet, welche ein Rückstellelement bildet und im montierten Zustand das erste Ventilelement 34 und das zweite Ventilelement 36 auseinander drückt. Die beiden Ventilelemente 34 und 36 sind identisch ausgebildet und lediglich um 180° gedreht zueinander angeordnet.A
Wie in
Die in dem Elektronikgehäuse 12 angeordnete Steuereinrichtung ist so ausgebildet, dass sie den elektrischen Antriebsmotor gezielt in zwei unterschiedlichen Drehrichtungen A und B ansteuern kann. Dies kann beispielsweise über einen Frequenzumrichter geschehen, welcher die Spulen im Stator gezielt bestromt. Die Ventileinrichtung in dem Ventileinsatz 28 ist so ausgebildet, dass sie abhängig von der Drehrichtung A, B die Strömung in den ersten Ausgang 24 und damit zu dem ersten Druckstutzen 6 oder in den zweiten Ausgang 26 und damit zu dem zweiten Druckstutzen 8 lenkt. An den ersten Druckstutzen 6 kann sich beispielsweise der Heizkreis einer Heizung für ein Gebäude anschließen, während sich an den zweiten Druckstutzen 8 ein Wärmetauscher zum Erwärmen von Brauchwasser anschließt.The control device arranged in the
Bei Inbetriebnahme des Pumpenaggregates wird somit von der Steuereinrichtung 12 zunächst die Drehrichtung vorgegeben, um vorzugeben, in welchen der beiden Ausgänge 24 oder 26 gefördert werden soll. Wenn nun der erste Ausgang 24 mit dem sich anschließenden Druckstutzen 6 genutzt werden soll, wird das Pumpenaggregat so in Bewegung versetzt, dass sich das Laufrad in der ersten Drehrichtung A dreht. In der in
Wenn der Antriebsmotor von der Steuereinrichtung ausgestaltet wird, kommt das Laufrad 14 zum Stillstand und die Strömung sowie der Druck im Innenraum 15 verschwinden. Daraufhin wird das erste Ventilelement 34 durch die Drehfeder 38 wieder in seine Ruhelage gebracht, in welcher es den ersten Ausgang 24 im Wesentlichen verschließt. Wenn das Pumpenaggregat in der entgegengesetzten Drehrichtung B betrieben wird, wird sich entsprechend das zweite Ventilelement 36 in eine geöffnete Position bewegen, in welcher es an dem ersten Ventilelement 34 zur Anlage kommt und so die Öffnung 42 in dem ersten Ventilelement 34 und damit den ersten Ausgang 24 vollständig verschließt. Gleichzeitig wird der zweite Ausgang 26 geöffnet und die Strömung kann durch diesen Ausgang in den zweiten Druckstutzen 8 strömen. Dieser Zustand, in welchem das zweite Ventilelement 36 in seiner geöffneten Stellung ist, ist in den
Dadurch, dass die Ausgänge 24 und 26 in der Ruhelage von den Ventilelementen 34 und 36 im Wesentlichen verschlossen sind, wird erreicht, dass bei Inbetriebnahme des Pumpenaggregates sich zunächst lediglich ein Druck und eine Strömung im Innenraum 15 des Pumpengehäuses 2 aufbauen, welche dazu genutzt werden, eines der Ventilelemente 34, 36 in seine geöffnete Stellung zu bewegen. In den sich an den Druckstutzen 6 und 8 anschließenden Systemen wird in diesem Zustand zunächst im Wesentlichen keine Strömung und kein Druck aufgebaut, wodurch Wasserschläge beim Schalten der Ventilelemente 34 und 36 reduziert werden. Es kann somit ein sehr sanftes Umschalten erreicht werden. Dies wird auch durch den Druckausgleich über die Öffnungen 42 begünstigt, da so nur eine sehr geringe Umschaltkraft zum Bewegen der Ventilelemente 34 und 36 erforderlich ist. Die Steuereinrichtung im Elektronikgehäuse 12 kann darüber hinaus die Beschleunigung des Antriebsmotors so anpassen, dass bei Inbetriebnahme zunächst gerade so viel Druck und Strömung aufgebaut werden, um eines der Ventilelemente 34, 36 in die gewünschte geöffnete Stellung zu bewegen und erst im Anschluss der Motor dann so beschleunigt wird, dass der gewünschte Enddruck bzw. -durchfluss aufgebaut wird.The fact that the
Wie in den
Die Aufnahmeöffnung 22 ist so ausgebildet, dass in einer Richtung radial zur Drehachse X des Antriebsmotors keine Hinterschneidungen ausgebildet sind. So kann die Aufnahmeöffnung 22 durch einen Kern ausgebildet werden, welcher nach dem Gießen des Pumpengehäuses 2 in radialer Richtung nach außen herausgezogen werden kann. Dies ermöglicht eine einfache Fertigung des Aufnahmeraumes 22.The receiving
Bei dem zuvor beschriebenen Ausführungsbeispiel sind die Ventilelemente 34 und 36 an der Schwenkachse so angelenkt, dass die Schwenkachse 32 bezogen auf die Drehachse x des Laufrades am radial äußeren Ende der Ventilelemente 34, 36 angeordnet ist, das heißt die Schwenkachse 32 ist vom Laufrad bzw. der Drehachse x in radialer Richtung maximal beabstandet. Wie in
Wie oben beschrieben, wird das erfindungsgemäße Umwälzpumpenaggregat bevorzugt in einer Heizungsanlage eingesetzt, insbesondere in einer Gastherme, welche nicht Teil der Erfindung sind. Eine solche Heizungsanlage mit einer Gastherme 48 ist schematisch in
- 11
- Pumpenaggregatpump unit
- 22
- Pumpengehäusepump housing
- 44
- Sauganschluss/SaugstutzenSuction / suction
- 6, 86, 8
- Druckstutzenpressure port
- 1010
- Statorgehäusestator
- 1212
- Elektronikgehäuse mit SteuereinrichtungElectronics housing with control device
- 1414
- LaufradWheel
- 1515
- Innenrauminner space
- 1616
- Rotorrotor
- 1818
- Lagercamp
- 2020
- Lagerplattebearing plate
- 2121
- Spalttopf bzw. SpaltrohrCan or can
- 2222
- Aufnahmeöffnungreceiving opening
- 2424
- erster Ausgangfirst exit
- 2626
- zweiter Ausgangsecond exit
- 2828
- Ventileinsatzvalve core
- 3030
- Verschlussplatteclosing plate
- 32, 32'32, 32 '
- Schwenkachseswivel axis
- 34, 34'34, 34 '
- erstes Ventilelementfirst valve element
- 36, 36'36, 36 '
- zweites Ventilelementsecond valve element
- 3838
- Druckfedercompression spring
- 4040
- Dichtflächesealing surface
- 4242
- Öffnungopening
- 4444
- Eingriffselementengaging member
- 4646
- Enden der VentilelementeEnds of the valve elements
- 4747
- Ringraumannulus
- 4848
- Gasthermegas water heater
- 5050
- Brennerburner
- 5252
- PrimärwärmetauscherPrimary heat exchanger
- 5454
- Heizkreislaufheating circuit
- 5555
- SekundärwärmetauscherSecondary heat exchanger
- 5656
- Heizkörperradiator
- A, BA, B
- Drehrichtungendirections
- XX
- Drehachseaxis of rotation
Claims (14)
- A pump assembly with a pump casing (2), with an impeller which is rotatably arranged in the pump casing (2), with an electrical drive motor which is connected to the impeller (14) for the drive of this and which is selectively drivable in two rotation directions (A, B), as well as with a valve arrangement (28) which is arranged in the pump casing (2) and is designed in a manner such that it switches a flow path downstream of the impeller between two exits (24, 26) which are formed in the pump casing, in a manner depending on the rotation direction (A, B) of the impeller (14), wherein the valve arrangement comprises a first movable valve element (34) at a first of the two exits (24) and a second movable valve element (36) at a second of the two exits (26), wherein the valve elements (34, 36) in an idle position are each located in a closed position, in which the first valve element (34) at least partly closes the first exit (24), and the second valve element (36) at least partly closes the second exit (26), and wherein the first valve element (34) is movable into an opened position by way of a flow which caused by the impeller (14) in its first rotation direction (A), and the second valve element (36) is movable into an opened position by way of a flow which is caused by the impeller (14) in its second rotation direction (B), characterised in that the valve elements (34, 36) each comprise an opening (42) which permits a flow passage into the associated exit (24, 26) also in a closed position of this valve element (34, 36).
- A pump assembly according to claim 1, characterised in that the first and the second valve element (34, 36) are movable independently of one another.
- A pump assembly according to claim 1 or 2, characterised in that the first and the second valve element (34, 36) are each designed as a flap which is pivotable about a pivot axis (32) between the opened position and the closed position.
- A pump assembly according to claim 3, characterised in that the first and the second valve element (34, 36) are pivotable about the same pivot axis (32).
- A pump assembly according to one of the claims 1 to 4, characterised in that the valve elements (34, 36) are arranged in a manner such that they are in contact with one another when one of the valve elements (34, 36) is located in its opened position.
- A pump assembly according to one of the preceding claims, characterised in that the opening (42) in the first valve element (34) and the opening (42) in the second valve element (36) are arranged offset to one another in a manner such that the opening (42) in the first valve element (34) is closed by the second valve element (36) and the opening (42) in the second valve element (36) is closed by the first valve element (34), when the two valve elements (34, 36) are in contact with one another.
- A pump assembly according to one of the preceding claims, characterised in that the first and the second valve elements (34, 36) are subjected to force by way of at least one restoring element (38), in a manner such that given a standstill of the impeller (14), they are each held in their closed position, wherein preferably the first and the second valve element (34, 36) are subjected to force by a common restoring element (38), in particular by a spring (38) which is arranged between the valve elements.
- A pump assembly according to one of the preceding claims, characterised in that the valve elements (34, 36) are each designed elastically or alternatively rigidly.
- A pump assembly according to one of the preceding claims, characterised in that an elastic seal is arranged in each case on the valve elements (34, 36) and/or valve seats which lie opposite these.
- A pump assembly according to one of the preceding claims, characterised in that the pump casing (2) comprises a receiving opening (22) which is situated between the two exits (24, 26) and which is open to the interior (15) of the pump casing (2) and into which the two valve elements (34, 36) are inserted from the outer side of the pump casing (2), wherein the two valve elements (34, 36) are preferably mounted in a valve insert (28) which is inserted into the receiving opening (22).
- A pump assembly according to claim 10, characterised in that the two exits (24, 26) are situated in the receiving opening (22).
- A pump assembly according to one of the preceding claims, characterised in that the two exits (24, 26) comprise valve seats which face the interior (15) of the pump casing (2) and which lie opposite one another, wherein the valve seats are preferably aligned essentially parallel to one another.
- A pump assembly according to one of the preceding claims, characterised in that the valve elements (34, 36) each comprise a sealing surface (40) which is provided for contact on a valve seat and which extends angled to a radius with respect to the pivot axis (32) of the respective valve element (34, 36).
- A pump assembly according to one of the preceding claims, characterised in that it is designed as circulation pump assembly, in particular for use in a heating facility and preferably with a wetrunning drive motor.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP16178585.2A EP3267042B1 (en) | 2016-07-08 | 2016-07-08 | Pump unit |
CN201710555549.0A CN107588202B (en) | 2016-07-08 | 2017-07-10 | Pump assembly |
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 (en) | 2016-07-08 | 2016-07-08 | Pump unit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3267042A1 EP3267042A1 (en) | 2018-01-10 |
EP3267042B1 true EP3267042B1 (en) | 2020-01-15 |
Family
ID=56403993
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16178585.2A Active EP3267042B1 (en) | 2016-07-08 | 2016-07-08 | Pump unit |
Country Status (3)
Country | Link |
---|---|
US (1) | US10514038B2 (en) |
EP (1) | EP3267042B1 (en) |
CN (1) | CN107588202B (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
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AU2018421968A1 (en) * | 2018-05-04 | 2020-10-22 | Electrolux Appliances Aktiebolag | Laundry washing machine and method for operating the laundry washing machine |
US11369101B1 (en) | 2020-02-13 | 2022-06-28 | Michael Padgett | Water delivery to a live bait well |
USD979481S1 (en) | 2020-02-13 | 2023-02-28 | Michael Padgett | Sea chest assembly |
USD949926S1 (en) * | 2020-02-13 | 2022-04-26 | Michael Padgett | Pump |
DE102022131010A1 (en) * | 2022-11-23 | 2024-05-23 | Miele & Cie. Kg | Pumping device, household appliance with pumping device and method for operating a pumping device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3338297B2 (en) * | 1996-08-01 | 2002-10-28 | 象印マホービン株式会社 | Dishwasher pump |
Family Cites Families (15)
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US1680775A (en) * | 1926-06-09 | 1928-08-14 | Bbc Brown Boveri & Cie | Reversible blower apparatus |
US4000235A (en) * | 1975-05-13 | 1976-12-28 | National Forge Company | Method for molding particulate material into rods |
DE3442907A1 (en) * | 1984-11-24 | 1986-06-05 | Robert Bosch Gmbh, 7000 Stuttgart | Pump unit having an electric drive motor operable in either direction of rotation and designed as a synchronous motor |
US4846260A (en) * | 1986-12-31 | 1989-07-11 | Reliance Electric Company | Cooling system |
DE3708327A1 (en) * | 1987-03-14 | 1988-09-22 | Bosch Gmbh Robert | DEVICE FOR CONVEYING LIQUID ON TWO SPRAY NOZZLES DISC AREAS OF A MOTOR VEHICLE |
IT1210354B (en) * | 1987-03-17 | 1989-09-14 | Nuova Sme S P A | SELECTABLE DOUBLE DELIVERY PUMP |
AU9083391A (en) * | 1990-12-21 | 1992-07-22 | Transpar Iberica, S.A. | Double membrane anti-overflow device for electric pumps of windshield washers |
US5586862A (en) * | 1995-06-15 | 1996-12-24 | Danner; Michael | Centrifugal pump having a slidable gate |
JPH09188227A (en) * | 1996-01-12 | 1997-07-22 | Jidosha Denki Kogyo Co Ltd | Washer pump |
KR100220407B1 (en) * | 1996-10-28 | 1999-09-15 | 전주범 | Hot circulation pump having flow direction |
DE102007052490A1 (en) * | 2007-11-02 | 2009-05-07 | Continental Automotive Gmbh | Valve for dual pump of window wiping system of motor vehicle, has valve bodies located on membranes, which are moved independent of each other, where one of membranes is manufactured from elastic plastic |
EP2397777B1 (en) * | 2010-06-19 | 2016-08-03 | Grundfos Management A/S | Housing unit for a heating system |
CN103261762B (en) * | 2010-10-05 | 2015-12-02 | 株式会社利富高 | Dispensing valve and possess fluid feed system and the manufacture method thereof of this valve |
DE102013108426A1 (en) | 2013-08-05 | 2015-02-05 | Faurecia Emissions Control Technologies, Germany Gmbh | Valve assembly and exhaust system |
CN104344032B (en) * | 2014-11-13 | 2017-05-31 | 福建南方路面机械有限公司 | For the antifreezing check valve of liquid transmission pipeline |
-
2016
- 2016-07-08 EP EP16178585.2A patent/EP3267042B1/en active Active
-
2017
- 2017-07-10 CN CN201710555549.0A patent/CN107588202B/en active Active
- 2017-07-10 US US15/645,036 patent/US10514038B2/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3338297B2 (en) * | 1996-08-01 | 2002-10-28 | 象印マホービン株式会社 | Dishwasher pump |
Also Published As
Publication number | Publication date |
---|---|
EP3267042A1 (en) | 2018-01-10 |
CN107588202A (en) | 2018-01-16 |
CN107588202B (en) | 2020-04-21 |
US20180010609A1 (en) | 2018-01-11 |
US10514038B2 (en) | 2019-12-24 |
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