EP3596342B1 - Groupe pompe centrifuge - Google Patents

Groupe pompe centrifuge Download PDF

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Publication number
EP3596342B1
EP3596342B1 EP17745364.4A EP17745364A EP3596342B1 EP 3596342 B1 EP3596342 B1 EP 3596342B1 EP 17745364 A EP17745364 A EP 17745364A EP 3596342 B1 EP3596342 B1 EP 3596342B1
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EP
European Patent Office
Prior art keywords
valve
receiving space
valve element
centrifugal pump
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17745364.4A
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German (de)
English (en)
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EP3596342A1 (fr
Inventor
Thomas Blad
Peter Mønster
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
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Grundfos Holdings AS
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Publication of EP3596342A1 publication Critical patent/EP3596342A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—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
    • 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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine

Definitions

  • the invention relates to a centrifugal pump unit, in particular for use in a heating system.
  • centrifugal pump units are used as circulating pump units in order to circulate a liquid heat carrier, usually water, in the heating system.
  • mixers or mixing devices are integrated into many heating systems in order to be able to adjust the temperature of the heat transfer medium, in particular to be able to reduce it. This is particularly necessary for underfloor heating, which is operated with a lower flow temperature than that provided by a boiler.
  • Such a mixer and a circulating pump unit are therefore generally required for underfloor heating in order to circulate the heat transfer medium in the underfloor heating circuit.
  • DE 1 942 647 A discloses a circulating pump for heating systems with an integrated mixing device.
  • two suction nozzles open into a common mixing chamber, the mouths of the two suction nozzles in the mixing chamber being spaced apart from one another and lying opposite one another.
  • a valve element is arranged between the opposite openings of the suction nozzles, which valve element opens and closes the openings in opposite directions to one another in order to change the mixing ratio.
  • the mixing chamber is connected to the suction side of the impeller, i.e. the suction mouth of the impeller sucks the mixed liquid out of the mixing chamber.
  • CH 536 464 discloses a circulating pump for hot water central heating, which has a pump housing with an integrated has mixing device.
  • the suction side of the impeller is connected to a valve device via a suction channel, with this suction channel and two suction nozzles opening into a common valve chamber in which a rotatable valve element is arranged in order to open and close the flow paths of the two suction nozzles to the suction channel in opposite directions and thus setting the mixing ratio.
  • DE 2 337 60 A1 discloses a pump unit with two suction channels which open into a common mixing chamber in which a valve element can be moved linearly.
  • the common mixing space forms a suction space, which opens into the suction side of the impeller of the pump unit.
  • the centrifugal pump unit has an electric drive motor and at least one of these rotating driven impeller.
  • the electric drive motor is preferably designed as a wet-running electric drive motor, ie as a motor with a can or can between the stator and the rotor.
  • the drive motor can be electronically controlled, for example equipped with a frequency converter.
  • the impeller is arranged in a pump housing, in which a first suction channel is formed, which forms a first flow path from a first suction port to the suction side of the impeller.
  • the centrifugal pump unit according to the invention corresponds to a conventional centrifugal pump unit, as is used as a circulating pump unit for heating and air-conditioning systems.
  • the centrifugal pump unit according to the invention is also preferably provided and designed for this purpose.
  • the pump housing has a receiving space which intersects the first suction channel and is connected to a second suction connection piece.
  • a movable valve element is arranged inside this receiving space.
  • the valve element is connected to an actuator, via which it can be moved between at least two, preferably several, switching positions. Particularly preferably, the valve element can be moved steplessly between two end positions or end switch positions by the actuator.
  • the valve element and the actuator are designed such that a cross-sectional ratio between the first flow path, which extends from the first suction connection piece, and a second flow path, which extends from the second suction connection piece, can be changed by moving the valve element.
  • the valve element can be arranged in such a way that it changes the free flow cross section of the first flow path or the free flow cross section of the second flow path.
  • the valve element is particularly preferably arranged in such a way that it simultaneously blocks the free flow cross section of the first flow path and the second flow path is changed by increasing the flow cross section of one of the flow paths when it is displaced, while at the same time the free cross section of the other flow path is reduced.
  • the design of the receiving space in the pump housing allows the entire mixing device to be integrated into the pump housing.
  • the two flow paths from the first suction port and the second suction port lead directly to the suction side of the impeller through openings or seats of the valve element, so that the flow paths can be influenced by the valve element.
  • the mixing device is arranged directly on the suction side of the centrifugal pump unit or circulating pump unit, ie the at least one impeller.
  • a very compact and cost-effective structure is thus created.
  • assembly is simplified since a separate connection between a mixing device and the centrifugal pump assembly is no longer required during installation.
  • the actuator can preferably be designed electrically, thermally or hydraulically.
  • the actuator is particularly preferably an electric stepping motor, via which the valve element can be moved into a desired position.
  • a thermal actuator can directly detect the temperature in one of the flow paths and move the valve element depending on the temperature via an expansion element.
  • a hydraulic actuator can, for example, act as a function of pressure, so that the valve element is moved to a desired position as the pressure increases. In all types of drive, a return movement can also preferably be brought about by a restoring element, such as a restoring spring.
  • the actuator is a hydraulic actuator which has a pressure connection via which an output-side pressure of the impeller on the at least a valve element acts.
  • the hydraulic actuator is connected via the pressure connection to the pressure chamber or the flow path to the pressure port of the centrifugal pump unit, so that the pressure on the output side of the impeller can be used to displace or move the valve element.
  • a prestressing element is preferably provided, which exerts a prestressing force on the valve element.
  • the pretensioning element generates a pretensioning force which is directed in the opposite direction to a compressive force which is generated by the pressure on the output side.
  • the prestressing element and the valve element are arranged such that hydraulic pressure moves the valve element against the prestressing force, so that when the pressure decreases, the valve element is moved back into its initial position by the prestressing element acting as a restoring element.
  • the valve element preferably has a pressure surface or is coupled to a pressure element on which the hydraulic pressure acts, so that a pressure force is generated on the pressure element or the pressure surface, which is used to move the valve element.
  • the actuator can be a thermal actuator which is arranged in such a way that it moves the at least one valve element depending on a temperature in one of the two flow paths.
  • the valve element can be arranged such that it changes the flow cross section of the second flow path depending on the temperature of the heating medium in the first flow path, in particular reducing the free flow cross section of the second flow path as the temperature of the heating medium increases. If the second flow path is used to supply heated heat transfer medium, a small quantity of the heated heat transfer medium is thus fed in when the flow cross section is reduced. This can for example be required if the temperature of the heating medium in the floor heating circuit is sufficiently high.
  • the valve element is preferably arranged and effective in this cutting area.
  • the receiving space is delimited by a wall formed in one piece with at least one further part of the pump housing.
  • the receiving space is integrated directly into the pump unit and is preferably delimited or formed by a wall section of the pump housing.
  • the wall delimiting the receiving space and the entire pump housing are designed in one piece, preferably made of metal or plastic. This enables cost-effective production, for example as a cast component.
  • possible assembly steps are eliminated if the receiving space is designed directly and integrally in the pump housing, as is preferred according to the invention.
  • the receiving space has a tubular, in particular cylindrical and more preferably circular-cylindrical basic shape.
  • the longitudinal axis of the receiving space preferably extends transversely and more preferably perpendicularly to a plane in which the axis of rotation of the drive motor is located.
  • the tubular or, in particular, circular-cylindrical basic shape of the receiving space enables simple processing.
  • the basic shape preferably extends up to an opening of the receiving space, so that the entire interior can be machined through the opening and/or can be formed by a core that can be removed through the opening.
  • the arrangement of the longitudinal axis of the receiving space transverse to the axis of rotation of the drive motor enables a compact design of the centrifugal pump assembly with the integrated mixing device.
  • the first suction connection and a pressure connection formed on the pump housing are directed opposite one another in the direction of a common installation axis, ie arranged facing away from one another.
  • the receiving space has a tubular basic shape, in particular a circular-cylindrical basic shape, with the longitudinal axis of the receiving space extending transversely and in particular normal to a plane in which said installation axis is located.
  • the longitudinal axis of the receiving space particularly preferably extends transversely and more preferably perpendicularly to a plane which is spanned by the axis of rotation of the drive motor and the installation axis mentioned. This arrangement achieves a compact structure and easy assembly of the centrifugal pump unit.
  • a valve insert is inserted or pushed into the receiving space, inside which the at least one valve element is movably guided.
  • the valve insert preferably carries all the elements required for the valve function, preferably also the valve seats required, and serves to hold and guide the movable valve element.
  • the valve insert is particularly preferably pushed into the receiving space through an opening. This is preferably an opening at a longitudinal end of the receiving space, which has a tubular basic shape and in particular a circular-cylindrical basic shape.
  • one longitudinal end is preferably completely open, so that a large cross section is available for inserting the valve insert. This enables very easy assembly.
  • a valve insert is inserted into the receiving space, which interrupts the first suction channel in such a way that a first section of the first suction channel forms the first flow path and a second section of the first suction channel forms a flow path from the receiving space to the suction side of the impeller.
  • a second flow path preferably runs through the receiving space, which is connected to the first flow path in the region of the valve insert or opens into the first flow path. The part of the suction channel from the receiving space to the suction side of the impeller then forms a common flow path through which the mixed liquid flow is fed to the impeller.
  • the valve element can be moved in the direction of the longitudinal axis of the receiving space. In this way, a large range of movement or travel for the valve element is made available. Furthermore, it is also possible to guide the valve element on the inner wall of the receiving space or on a valve insert lying against the inner wall of the receiving space.
  • the first and/or the second flow path preferably end in a valve seat, with which the at least one valve element can be brought into contact. If the valve element can be brought into abutment against the valve seat, this enables the flow path to be closed completely. This is particularly preferred for the second flow path if this is used to supply heated heat transfer medium to a floor circuit. In this way, this flow path can be completely closed when no heated heat transfer medium is required. Furthermore the flow cross-section through the flow paths can be varied by spacing the valve element from the associated valve seat at different distances.
  • the first flow path opens into a valve seat and the second flow path opens into a second valve seat, and a flow path branches off to the suction side of the impeller between these two valve seats.
  • the valve element has two valve surfaces facing the valve seats, which are arranged such that when the valve element moves, one valve surface moves away from one of the valve seats and at the same time the other valve surface approaches the other valve seat. During the movement, one flow path is opened and the other flow path is closed at the same time.
  • the free flow cross section of the respective flow path is defined by the distance between the valve surface and the valve seat.
  • the two valve seats preferably face each other and the at least one valve element is located between the valve seats.
  • the valve surfaces of the valve element are preferably located on two axial ends of the valve element that face away from one another.
  • the at least one valve element is sleeve-shaped, with the second flow path running through the interior of the sleeve and the sleeve having an outlet opening in one wall, which is arranged opposite an inlet opening of a flow path to the suction side of the impeller in such a way that it can be brought to different extents to coincide with the inlet opening by moving the valve element.
  • the inlet opening can thus be further closed and/or opened set the free flow cross section in this flow path. If a wall of the valve element completely covers the inlet opening, the flow path is completely closed. In this configuration, the valve element is thus moved parallel to the valve seat, which surrounds the inlet opening or is formed by the edge of the inlet opening.
  • the valve element is designed and arranged in such a way that its outside closes a flow connection from the first flow path to the inlet opening to a different extent depending on the positioning of the valve element.
  • a functionality is thus achieved in which the first flow path runs along the outside of the valve element and is opened or closed by positioning the outside, while the second flow path runs through the inside of the valve element.
  • a valve surface acting in the direction of movement of the valve element is formed on the valve element, which in an end position of the valve element bears against a valve seat in such a way that the second flow path is closed.
  • an additional closure function is thus created.
  • an axially acting valve surface comes into sealing contact with the valve seat, while the flow rate is regulated by overlapping the inlet opening to different extents. This means that a complete seal does not have to be achieved during the parallel displacement of the wall of the valve element relative to the inlet opening, this is rather realized via a separate sealing surface with a separate valve seat. So can a slight Movability of the valve element to regulate the flow and yet a reliable seal can be realized in an end position.
  • the receiving space has a first opening at a first axial end. More preferably, the receiving space has a second opening at an opposite second axial end, in particular at an opposite second axial end in the direction of its longitudinal axis.
  • these openings can serve directly as a suction connection or can accommodate a suction connection piece forming the suction connection.
  • the openings allow the receiving space to be formed easily by means of removable cores. In addition, accessibility for machining or other processing of the inner surfaces of the receiving space is also ensured through the openings.
  • the components that form the valve element, in particular a valve insert can also be easily inserted or pushed into the receiving space through one of the openings or both of the openings.
  • one of the openings forms the second suction port or is connected to the second suction port.
  • a component that defines or supports the second suction port can be inserted into the opening.
  • the second suction port is then particularly preferably located at the axial end of the valve insert.
  • the receiving space has a second opening, this is preferably closed by a closure element. This means that this second opening is used for production and assembly and is no longer used in operation.
  • the actuator is arranged on the closure element and/or an actuating element of the actuator, which is connected to the valve element, extends through the closure element into the interior of the receiving space.
  • an opening of the receiving space can serve as a second suction nozzle and a closure element, which carries the actuator or has the passage for an actuating element of the actuator, is arranged in the other opening. This enables the required components to be arranged in a space-saving manner.
  • the actuating element connected to the valve element can also be designed as a pivotable lever which extends transversely to the direction of movement of the valve element and preferably extends outwards through a wall of the receiving space and/or a valve insert inserted into the receiving space.
  • a pivotable lever can be passed through an elastic sleeve or an elastic wall section, so that a very simple seal is possible.
  • an actuating element in the manner of a piston rod can also be guided through a linear passage into the interior of the receiving space. Spindle operation for the linear movement of the valve element could also be arranged.
  • FIG. 1 shows schematically a heating system in which the centrifugal pump unit according to the invention, as will be described below, can be used.
  • a heating system with such a centrifugal pump unit is also the subject of the invention.
  • the heating system described has at least one heating circuit 2 , which is shown here as a floor heating circuit 2 .
  • This heating circuit 2 is supplied with a liquid heat carrier or heating medium via a mixing device 4 .
  • the mixing device 4 is formed by a centrifugal pump unit, as will be described below.
  • the liquid heating medium is heated by a boiler 6.
  • the centrifugal pump unit could also be used in a corresponding manner in an air conditioning system for cooling.
  • the boiler 6 would be replaced by a cold source.
  • it is to be understood in the following description that such an air conditioning system is expressly included, even if the invention is described below by way of example only using the example of a heating system.
  • the boiler 6 can be, for example, a gas boiler or an oil boiler or another suitable heat source.
  • the centrifugal pump unit 10 or circulating pump unit 10, which contains the mixing device 4, conveys the liquid heating medium through the heating circuit 2, from which it is fed via a return line 12 to a mixing point 14 and via this back to the centrifugal pump unit 10.
  • a return 16 to the boiler 6 branches off from the return line 12 .
  • a flow line 18 also leads to the mixing point 14, a mixing valve 20 being arranged in the flow line 18, via which the flow of the heated heating medium which is fed to the mixing point 14 can be metered.
  • a mixing valve 21 is also arranged in the return line 12 , via which the flow from the return line 12 to the mixing point 14 can be regulated.
  • the two mixing valves 20 and 21 can be controlled in a coupled manner so that whenever one of the valves 20, 21 closes in order to reduce the flow, the other valve opens by a corresponding amount at the same time in order to increase the flow.
  • Both mixing valves 20, 21 can also be designed as a combined three-way valve, in which both the flow line 18 and the return line 12 are influenced via a valve element in order to change the mixing ratio of the heated heating medium, which is supplied via the flow line 18, with the to be able to set or change cold heat carrier, which is supplied via the return line 12, to the mixing point 14.
  • a centrifugal pump unit 10 is now provided, in which the entire mixing device 4, that is to say also the mixing valve 20 and the mixing point 14, are integrated.
  • a first embodiment of such a centrifugal pump unit is based on Figures 2 to 9 described.
  • the centrifugal pump unit has the same as usual circulating pump units for heating systems a drive motor, which is arranged in a stator or motor housing 22 .
  • a pump housing 24 is arranged on the motor housing 22 at an axial end in the direction of the axis of rotation X.
  • an electronics housing 26 is arranged at the opposite end, in which electronic control system 28 for controlling or regulating the drive motor is arranged.
  • the drive motor has a stator 30 and a rotor 32 in the usual way, which can preferably be designed as a permanent magnet rotor.
  • the drive motor is designed as a wet-running motor with a can 34 between the stator 30 and the rotor 32 .
  • the rotor 32 is connected via a rotor shaft 36 to an impeller 38 which is located in the pump housing 24 . In this way, the impeller 38 can be driven in rotation.
  • the pump housing 24 has a pressure connection 40 which branches off from a pressure chamber 42 surrounding the impeller 38 in the interior of the pump housing 24 . Furthermore, the pump housing 24, like known heating circulating pump units, has a first suction port 44. The pressure connection 40 and the first suction connection 44 are directed away from one another along a common installation axis Y. The pressure connection 40 and the suction connection 44 are also spaced apart by a distance which corresponds to the length of conventional or customary circulating pump units, so a conventional circulating pump unit can easily be replaced by the centrifugal pump unit according to the invention. Starting from the first suction nozzle 44, a first suction channel 46 extends to the suction side or to the suction mouth 48 of the impeller 38. The first suction channel 46 is designed in a form known from conventional heating circulating pumps.
  • the pump housing 24 also has a receiving space 50 intersecting the first suction channel 46 .
  • the wall delimiting the receiving space 50 is designed in one piece with the rest of the pump housing 24 as a cast component.
  • the receiving space 50 has a circular-cylindrical internal cross section, with its longitudinal axis Z extending normal to a plane spanned by the axis of rotation X and the installation axis Y described.
  • the receiving space 50 is tubular and has a first opening 52 and a second opening 54 at its opposite axial ends.
  • the first opening 52 and the second opening 54 each cover the entire longitudinal end of the receiving space 50, so that it is accessible over its entire internal cross section through the openings 52 and 54, which allows the assembly of components inside the receiving space 56 and also the machining of the inner surfaces of the receiving space 50 favored.
  • the receiving space 50 divides the first suction channel 46 into two sections 46a and 46b.
  • the first section 46a extends from the first suction port 44 to or into the receiving space 50 and the second section 46b extends from the receiving space 50 to the suction side or to the suction mouth 48 of the impeller 38.
  • a valve insert 56 is inserted or pushed through the first opening 52 into the receiving space 50 .
  • the valve insert 56 has a second intake port 58 at one longitudinal end.
  • the valve insert 56 is sealed off from the wall of the receiving space 50 on the circumference of the opening 52 .
  • the valve insert 56 interrupts the flow path through the first suction channel 46 with its section 60 inserted into the receiving space 50, so that it is divided into the aforementioned sections 46a and 46b.
  • the first section 46a of the suction channel 46 opens into an opening 62 in the wall of the section 60 of the valve insert 56 and thus into the interior of the hollow valve insert 56.
  • a valve element 64 is movably guided in the direction of the longitudinal axis Z of the receiving space 50 in the interior of the valve insert 56 .
  • the valve element 64 slides along the inner circumference of the valve insert 56, which is tubular, in the longitudinal direction Z.
  • the valve element 64 has radially directed projections 66 for guidance.
  • valve seats 68 and 70 which are spaced apart and face one another are formed in the interior of the valve insert 56 .
  • the valve seat 68 delimits the section of the interior of the valve insert 56 into which the opening 62 opens from the rest of the interior of the valve insert.
  • the second valve seat 70 is spaced close to the second suction port 58.
  • the two valve seats 68 and 70 are spaced from each other and face each other. Viewed in the direction of the longitudinal axis Z, the valve element 64 lies between the two valve seats 68 and 70.
  • the valve element 64 has a first valve surface 72 and a second valve surface 74 at its opposite axial ends.
  • the axial distance between the valve surfaces 72 and 74 facing away from each other in the direction of the longitudinal axis Z is smaller than the distance between the valve seats 68 and 70.
  • the valve element 64 can also be held in intermediate positions so that the between the valve seats 68, 70 and the flow paths formed by the valve surfaces 72, 74 can be opened to different extents.
  • an electric servomotor 76 is provided as the actuator in this exemplary embodiment, which can be designed in particular as a stepping motor and moves a pivotable lever 78, which extends through an opening in the valve insert 56 into the interior of the valve insert 56 and into the Valve element 64 engages.
  • the lever extends essentially transversely to the longitudinal axis Z of the receiving space through a peripheral wall of the valve insert 56.
  • the use of the pivotable lever 48 has the advantage that a good seal can be achieved via an elastic sealing collar at the opening of the valve insert 56.
  • drive units with the servomotor 76, the necessary gearing means and the lever 78 are already known from other applications, so that an existing component can be connected to the valve insert 56 as a drive unit.
  • the valve element 64 has such an axial length in the direction of the longitudinal axis Z that the recess 79 in the valve element 64, in which the lever 78 engages, is located in the valve insert 56 in a section which is located outside of the receiving space 50 is.
  • This extended configuration of the valve element 64 therefore has the advantage that the drive unit with the servomotor 76 can be arranged to the side of the motor housing 22 .
  • the fastening for the drive unit with the servomotor 46 which is designed here as a bayonet coupling 81, can be designed on the valve insert 56, which is preferably designed from plastic.
  • the corresponding receptacle or bayonet coupling 81 is simpler to form there than in the receptacle space 50, the wall of which together with the pump housing 24 is preferably designed as a cast metal part.
  • the servomotor 76 can be controlled by the control electronics 28 or by an external mixer control.
  • the second opening 54 of the receiving space 50 is closed by a closure element 80 .
  • the receiving space 50 is essentially symmetrical with respect to the installation axis Y.
  • the first suction port 44 is provided with the flow line 18 in the heating system 1 connected, while the second suction port 58 is connected to the return line 12.
  • the pressure port 40 is connected to the line that leads to the underfloor heating circuit 2 .
  • the valve seat 70 together with the valve surface 74 assumes the function of the mixing valve 21, while the valve surface 72 together with the valve seat 68 assumes the function of the mixing valve 20.
  • the mixing valves 20 and 21 are thus combined here to form a three-way valve.
  • the valve seat 70 could be removed or left out, so that only the functionality of the mixing valve 20 as a pure two-way valve would then remain.
  • valve element If the valve element is in the in 6 and 8th shown is the first valve position or end position, the sealing surface 72 is sealingly against the valve seat 68, so that the flow path through the first suction port 44 and the section 46a of the suction channel 46 to the receiving space 50 is closed.
  • valve surface 74 is at a maximum distance from the second valve seat 70, so that a second flow path, starting from the second suction connection 58 through the receiving space 50 to the second section 46b of the suction channel 46, is opened to the maximum. So promotes the impeller 38 during rotation, the heating medium through the heating circuit 2 via the return line 12 in a circle.
  • the valve element 64 In order to admix the heated heat carrier or heated heating medium, the valve element 64 is moved linearly along the longitudinal axis Z in the direction of a second switching or valve position. In this, the valve surface 72 moves away from the first valve seat 68, so that the first flow path is opened through the first section of the suction channel 46a and heating medium from the supply line 18 to the second section 46b of the suction channel 46 and via this to the impeller 38 can flow. In this intermediate position of the valve element 64, heating medium thus flows from the first suction connection 44 and from the second suction connection 58 to the impeller 38, so that the two heating medium flows are mixed.
  • valve element 64 When the valve element 64 is in its second end position, which is in 7 and 9 As shown, the second flow path via return line 12 is completely closed since valve surface 74 abuts valve seat 70 . Then the heating medium is conveyed into the underfloor heating circuit 2 only via the flow line 18 . In intermediate positions of the valve element 64 between the two switching positions, different mixtures of heated and cold heating medium can be achieved, with the mixing point 14 being located in the area of the branch of the section 46b of the first suction channel from the receiving space 50 .
  • the receiving space 50 is also configured identically to the first embodiment.
  • the opening 54 at the second axial end of the receiving space 50 is closed here by a closure element 80'.
  • a valve insert 56 ′ is inserted into the first opening 52 , the valve insert 56 ′ being sealed against the inner circumference of the receiving space 50 adjacent to the opening 52 .
  • the valve insert 56' could also be inserted through the second opening 54 into the receiving space 50, as was described with reference to the first exemplary embodiment.
  • a second suction nozzle 82 is arranged on the side of the valve insert 56'. This opens out via an opening 84 into the interior of the valve insert 56'.
  • a first valve seat 86 is arranged inside the valve insert 56 .
  • the valve seat 86 is located between an area 88 into which, as described with reference to the first exemplary embodiment, the first section 46a of the first suction channel 46 opens via the opening 62 in the section 60 of the valve insert 56', and the remaining interior of the valve insert 56'. from which the section 46b of the suction channel 46 branches off to the impeller 38.
  • a valve element 90 can come into contact with the valve seat 86 .
  • the valve element 90 is guided so as to be linearly movable in the direction of the longitudinal axis Z inside the valve insert 56'.
  • a return spring or a prestressing spring 92 rests against the closure element 60′, which presses against the valve element 90 with its opposite axial end and prestresses the valve element 90 in the direction of an open position in which it is lifted off the valve seat 86, or with a compressive force loaded.
  • the valve element 90 is energized by a thermostatic or expansion element 94 .
  • the interior of the thermostatic element 94 has a medium which expands as the temperature increases, so that the length of the thermostatic valve 94 in the direction of the longitudinal axis Z increases.
  • the thermostatic element 94 lies in a flow path from the opening 84 to the mouth of the second section 46b of the first suction channel, which leads to the suction mouth 48 of the impeller 38 (see FIG Embodiment according to Figures 2 to 9 ).
  • the thermostatic element 94 reacts to the temperature of the heating medium which is fed in through the return line 12 , provided that this is connected to the second suction port 82 . If the temperature of the heating medium from the return line 12 is sufficiently high, the thermostatic element 94 expands to such an extent that the valve element 90 is pressed against the force of the return spring 92 against the valve seat 86 and thus the first flow path, starting from the first suction connection 44 and the first Suction channel 46 is closed.
  • the thermostat element 94 contracts in the direction of the longitudinal axis Z, so that the return spring 92 moves the valve element 90 so that it is lifted from the valve seat 86 and the flow path through the first section 46a of the first suction channel 46 is released and heating medium from the flow line 18, which is connected to the first suction port 44, is admixed.
  • a purely temperature-controlled mixing valve is integrated into the receiving space 50 .
  • the temperature can be adjusted via the adjusting screw 96, by turning which the thermostatic element 94 can be displaced in the axial direction in the direction of the longitudinal axis Z.
  • a second valve seat 95 is disposed in the valve core 56' and faces the valve 86 but is spaced therefrom.
  • a second valve surface 97 interacts with the second valve seat 95 .
  • the second valve seat 95, together with the second valve surface 97 assumes the function of the mixing valve 21 in the return line 12, as described above, while the valve seat 86, together with a first valve surface 87 of the valve element 90, assumes the function of the mixing valve 20. That is, a three-way valve is also implemented in this exemplary embodiment, which combines the functionality of the two mixing valves 20 and 21 . So an interaction is achieved, ie when the flow path from the first suction port 44 to the impeller 38 is opened further, the flow path from the second suction port 82 to the impeller 38 is simultaneously reduced in cross-section and vice versa.
  • a mixing valve which is moved by a thermostatic element 94 as an actuator, can very easily be used as an alternative. can be integrated.
  • a third variant of the centrifugal pump unit is based on the Figures 14 to 18 described.
  • the drive motor with the pump housing 24 and the impeller 38 arranged therein is identical to the exemplary embodiments described in accordance with FIG Figures 2 to 13 educated.
  • the receiving space 50 on the pump housing 24 is also designed in an identical manner.
  • a valve insert 56" is inserted through the opening 52 of the receiving space 50.
  • this insert has a section 60 with the opening 62, which extends into the interior of the receiving space 50.
  • an additional bore is introduced in the pump housing 24, which forms a pressure channel 96.
  • the pressure channel 96 establishes a pressure connection between the pressure chamber 42 and the receiving chamber 50.
  • the valve insert 56" interrupts the first suction channel 46.
  • the first section 46a opens out on a first side of a valve seat 98 into the receiving space 50.
  • the second section 46b of the first suction channel branches off towards the impeller 38.
  • a valve element 100 is movably guided in the direction of the longitudinal axis Z inside the valve insert 56".
  • the valve element 100 can be connected to the valve seat 98 in Contact occur to close the flow passage through the valve seat 98.
  • a prestressing element in the form of a spring 102 is also provided in this exemplary embodiment, which in this example applies a prestressing force to the valve element 100 in the direction of the longitudinal axis Z, which presses the valve element 100 against the valve seat 98 .
  • the spring 102 rests with its longitudinal end facing away from the valve element 100 on an adjusting screw 104, via which the prestressing of the spring 102 can be preset or regulated.
  • a piston 105 which is connected to the valve element 100 extends through the valve seat 98 .
  • the piston 105 forms a pressure surface which is located in a pressure region 108 which is connected to the pressure chamber 42 in the interior of the pump housing 24 via the pressure channel 56 .
  • the fluid pressure generated on the outlet side of the impeller 38 thus acts on the end face of the piston 105.
  • An elastic bellows 106 seals off the pressure region 108 from the suction channels or the flow paths on the suction side.
  • the valve insert 56" has a second suction port 110 on the side, similar to the second suction port 82 in the second exemplary embodiment.
  • This second suction port 110 is connected to the return line 12 in the heating system.
  • the second suction port 110 opens into the interior of the valve insert via an opening 112 56".
  • the opening 112 is inside the valve insert 56" with the second section 46b of the first suction channel, which leads to the impeller 38. This creates a flow path from the second suction port 110 to the impeller 38.
  • the output-side pressure of the impeller 38 acts on the piston 105. This means that a compressive force is generated on the piston 105, which opposes the spring compressive force of the spring 102.
  • the piston 105 moves against the spring 102 and the valve element 100 is lifted from the valve seat 98.
  • the first flow path through the first suction channel 46 or the first section 46a of the first suction channel 46 and through the valve seat 98 to the second section 46b of the first suction channel and thus to the impeller 38 is released.
  • So heated heating medium from the flow line 18, which is connected to the first suction port 44, are admixed.
  • the mixing point 14 is in the region of the branch of the second section 46b of the first suction channel 46. This state is in 18 shown.
  • valve element 100 can be displaced further to the right until it comes to rest on a second valve seat 114 .
  • the flow path from the opening 112 to the second section 46b of the first suction channel is closed, so that only a flow connection from the first suction port 44 via the first suction channel 46 to the impeller 38 is released.
  • the valve element 100 can also be moved into one or more intermediate positions by appropriate pressure or speed adjustment, as a result of which the flow paths between the valve seat 114 and the valve element 100 and the valve seat 98 and the valve element 100 are opened to different extents.
  • a three-way valve is realized, which combines the functionalities of the valves 20 and 21 as described above.
  • the mixing ratio can be regulated solely as a function of pressure, with the pressure being dependent on the rotational speed of impeller 38 .
  • the mixing ratio can be changed by varying the speed of the drive motor.
  • a temperature pre-setting that is to say a pre-setting of a specific mixing ratio for a specific pressure, is possible via the adjusting screw 104, via which the prestressing of the spring 102 is adjusted.
  • a pressure-dependent actuator is thus provided, which can be integrated very easily into an identical pump housing 24 with the receiving space 50, as is also used in the first two exemplary embodiments. Only the additional bore for the pressure channel 96 has to be made in the pump housing 24 .
  • the valve insert 56" could be inserted into the opening 54 of the receiving space 50 instead of into the opening 52 in order to move the second suction connection 110 to the other side of the receiving space.
  • the pressure channel 96 would then only have to be on the opposite longitudinal end of the receiving space 50 or two pressure channels 96 would have to be provided, of which an unused one would be closed by the section 60 of the valve insert 56".
  • a fourth embodiment is in the Figures 19 to 23 shown.
  • This exemplary embodiment relates to a centrifugal pump unit with a higher output, which is correspondingly larger in size.
  • the design of the drive motor and the pump housing 24′ essentially corresponds to the design of the drive motor and the pump housing 24 according to the previous description, so that reference is also made to the previous description with regard to these components.
  • the drive motor is arranged inside a motor housing 22' and has a stator 30' and a rotor 32'.
  • the rotor 32' is connected via a rotor shaft 36' to an impeller 38' inside the pump housing 24' to drive the impeller 38' in rotation.
  • the drive motor is designed as a wet-running motor with a can 34' between the rotor 32' and the stator 30'.
  • An electronics housing 26' with control electronics 28' arranged therein is arranged at the axial end opposite the pump housing 24' in the direction of the axis of rotation.
  • the control electronics 28 ' is used to control the drive motor and optionally a drive of a mixing valve, such as it was previously described.
  • the pump housing 24' has, facing away from one another, a first suction connection 44' and a pressure connection 40', which is connected to the pressure chamber 42', which surrounds the impeller 38' on the output side.
  • a first suction channel 46' extends from the first suction connection 44' to the suction mouth of the impeller 38', the suction channel 46' also being cut through a receiving space 50' here, the receiving space 50' dividing the first suction channel 46' into a first section 46'a and a second section 46'b, as is also the case with the first three exemplary embodiments.
  • the structure of the pump housing 24' with the receiving space 50' corresponds to the structure of the pump housing 24 with the receiving space 50 according to the first three exemplary embodiments.
  • a second suction nozzle 116 is inserted into the receiving space 50' through its first opening 52'.
  • This arrangement has the advantage that the second suction port is fastened directly to the receiving space 50′, which is preferably made in one piece with the pump housing 24′ in cast metal.
  • a valve insert 120 is inserted into the receiving space 54' from the opposite axial end in the longitudinal direction Z through the second opening 54'.
  • the valve insert 20 is tubular and is connected to the suction nozzle 116 with its open end, which is arranged in the receiving space 50 ′.
  • a closure element 122 with an electric servomotor 124 is inserted into the opposite open end of the valve insert 120 .
  • the servomotor 124 can be controlled by the control electronics 28' or further external mixer control electronics.
  • the servomotor 124 moves an actuating element in the form of a drive rod 126 via a spindle drive, which extends through the closure element 122 in the direction of the longitudinal axis Z.
  • the drive rod 126 is moved linearly in the direction of the longitudinal axis Z by the servomotor 124 .
  • the drive rod 126 is connected to a sleeve or tubular valve element 128 and thus moves the valve element 128 inside the valve insert 120 in the direction of the longitudinal axis Z.
  • the valve element 128 is guided longitudinally movable inside the valve insert 120 .
  • the valve element 128 has a groove 130 into which a projection 132 on the inner circumference of the valve element 120 engages in order to prevent the valve element 128 from twisting.
  • valve element 128 The end of the valve element 128 which is connected to the drive rod 126 is closed, while the opposite end is open and engages the interior of the second suction port 116, with a flow path from the second suction port 116 into the interior of the valve element 128 given is.
  • the valve element 128 has an opening 134 in its outer peripheral surface.
  • the opening 134 in the wall of the sleeve-shaped valve element 128 forms an outlet opening which, with a corresponding axial positioning of the valve element 128 inside the valve insert 120, can be brought into alignment with an inlet opening 136 in a peripheral wall of the valve insert 120.
  • the inlet opening 136 forms the inlet opening of the second section 46'b of the suction channel 46, which leads to the suction mouth of the impeller 38'.
  • the inlet opening 136 coincides with the opening of the section 46'b of the suction channel 46.
  • the inlet opening 136 is adapted to the cross-sectional shape of the suction channel 46 in this area.
  • the closed longitudinal end of the sleeve-shaped valve element 128 slides with its outer circumference against the inner circumference of the valve insert 120.
  • the outlet opening 134 overlaps the inlet opening 136 to a different degree, so that the flow path through the interior of the valve element 128 to the impeller 38' is opened to different extents.
  • the return line 12 is connected.
  • the valve element 128 can come to rest axially with its radially projecting, closed axial end on a valve seat 118 inside the valve insert 120, so that this suction-side flow path is completely closed.
  • the first section 46'a of the suction channel 46 opens out via a further opening into the interior of the valve insert 120 in the area of the outer circumference of the valve element 128.
  • valve element 128 is moved in the direction of the closure element 122 and the opening 134 covers the inlet opening 136, the more the remaining flow path is closed past the outer circumference of the valve element 128 into the inlet opening 136, so that the first flow path on the suction side is further closed by the suction channel section 46'a.
  • the suction port 44' is in the 1 Heating system shown preferably connected to the flow line 18.
  • a valve is created here which acts both in the supply line 18 and in the return line 12, i.e. the more the flow path from the supply line 18 is opened, the more the flow path from the return line 12 is closed. That is to say, a three-way valve is also formed here, which combines the functionality of the valves 20 and 21 .
  • the tubular or sleeve-shaped design of the valve element 128 has the advantage that a maximum cross-section is realized through both flow paths, so that the hydraulic resistance is minimized.
  • the separation of the sealing function via the axial seal at the valve seat 118 from the flow control function via the orifice 134 also has the advantage of reducing the friction in the system, so that a smaller actuator motor is sufficient for movement.
  • the elliptical shape of the outlet opening 136 also has the advantage that with constant linear movement of the valve element 128 towards the end free flow cross section is reduced more, so that overall a favorable control behavior over the entire travel, in particular a linear control behavior can be realized.
  • the valve elements are moved linearly.
  • the linear movement has the advantage that a spindle motor can be used to drive it.
  • the spindle motor implements a gear in a very simple way, which at the same time converts the rotary movement into a linear movement and slows down the movement for good controllability.
  • the servomotor with the gear can be arranged in the dry area. Only a linear bushing or, in the case of the lever described, a sealing sleeve has to be provided in order to introduce the actuating element into the wet space.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (20)

  1. Groupe motopompe centrifuge destiné à être utilisé en tant que groupe motopompe de circulation pour des installations de chauffage et de climatisation, comprenant un carter de pompe (24; 24'), un moteur d'entraînement électrique ainsi qu'au moins une roue (38; 38') entraînée en rotation par celui-ci et disposée dans le carter de pompe (24; 24'), dans lequel est réalisé un canal d'aspiration (46; 46') qui forme un premier trajet d'écoulement depuis une première tubulure d'aspiration (44, 44') vers le côté aspiration de la roue (38; 38'),
    la première tubulure d'aspiration (44; 44') et une tubulure de refoulement (40; 40') formée au niveau du carter de pompe (24; 24') sont opposées l'une à l'autre dans la direction d'un axe de montage (Y) commun,
    caractérisé en ce que
    le carter de pompe (24; 24') comporte un espace de réception (50; 50') ayant une forme de base tubulaire, qui coupe le premier canal d'aspiration (46; 46') de façon à créer une région d'intersection entre le premier canal d'aspiration et l'espace de réception, où l'espace de réception (50; 50') est raccordé à une seconde tubulure d'aspiration (58; 82; 110; 116) et à l'intérieur duquel est agencé au moins un organe de soupape mobile (64; 90; 100; 128) qui est relié à un actionneur (76; 94; 105; 124) et conçu de telle sorte que le déplacement de l'organe de soupape (64; 90; 100; 128) peut faire varier un rapport de section transversale entre le premier trajet d'écoulement qui s'étend depuis la première tubulure d'aspiration (44; 44'), et un second trajet d'écoulement qui s'étend depuis la seconde tubulure d'aspiration (58; 82; 110; 116),
    en ce que le premier et le second trajet d'écoulement débouchent dans l'espace de réception (50; 50') et un segment (46b; 46'b) du premier canal d'aspiration (46; 46') forme un trajet d'écoulement depuis l'espace de réception (50; 50') vers le côté aspiration de la roue (38; 38'), au moins au nombre de une, et en ce que l'axe longitudinal (Z) de l'espace de réception (50; 50') s'étend transversalement et en particulier perpendiculairement à un plan dans lequel est situé l'axe de montage (Y).
  2. Groupe motopompe centrifuge selon la revendication 1, caractérisé en ce que l'actionneur est électrique, thermique ou hydraulique, et est en particulier un moteur électrique pas à pas (64; 128).
  3. Groupe motopompe centrifuge selon la revendication 2, caractérisé en ce que l'actionneur est un actionneur hydraulique (105) qui comporte une liaison de pression (96) via laquelle une pression côté sortie de la roue (38) agit sur l'organe de soupape (100), au moins au nombre de un, suite à quoi il est prévu, de préférence, un élément de précontrainte (102) qui génère une force de précontrainte exercée à l'opposé de la force de pression générée par la pression.
  4. Groupe motopompe centrifuge selon la revendication 2, caractérisé en ce que l'actionneur est un actionneur thermique (94) agencé de façon à déplacer l'organe de soupape (90), au moins au nombre de un, en fonction d'une température dans l'un des deux trajets d'écoulement.
  5. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'espace de réception (50, 50') est délimité par une paroi réalisée d'un seul tenant avec au moins une autre partie du carter de pompe (24; 24'), où, de préférence, la paroi délimitant l'espace de réception (50; 50') et l'ensemble du carter de pompe (24; 24') sont réalisés d'un seul tenant, de préférence en métal ou en matière plastique.
  6. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'espace de réception (50; 50') présente une forme de base tubulaire et son axe longitudinal (Z) s'étend transversalement, et en particulier perpendiculairement à un plan dans lequel est situé l'axe de rotation (X) du moteur d'entraînement.
  7. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce qu'est inséré dans l'espace de réception (50; 50') un insert de soupape (56; 56'; 56"; 120) à l'intérieur duquel l'élément de soupape (64; 90; 100; 128), au moins au nombre de un, est guidé de façon mobile, l'insert de soupape (56; 56'; 56"; 120) étant introduit de préférence à travers une ouverture pratiquée dans l'espace de réception (50; 50').
  8. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce qu'est inséré dans l'espace de réception (50; 50') un insert de soupape (56; 56'; 56"; 120) qui interrompt le premier canal d'aspiration (46; 46') de façon telle qu'un premier segment (46a; 46'a) du premier canal d'aspiration forme le premier trajet d'écoulement et un second segment (46b; 46'b) du premier canal d'aspiration forme un trajet d'écoulement depuis l'espace de réception (50; 50') vers le côté aspiration de la roue (38; 38').
  9. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'organe de soupape (64; 90; 100; 128), au moins au nombre de un, est mobile dans la direction de l'axe longitudinal (Z) de l'espace de réception (50; 50').
  10. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le premier et/ou le second trajet d'écoulement se terminent dans un siège de soupape (68; 70; 86; 98; 114) avec lequel l'organe de soupape (64; 90; 100; 128), au moins au nombre de un, peut être mis en contact.
  11. Groupe motopompe centrifuge selon la revendication 10, caractérisé en ce que le premier trajet d'écoulement et le second trajet d'écoulement débouchent respectivement dans un premier siège de soupape (68) et dans un second siège de soupape (70), et en ce qu'un trajet d'écoulement (46b) bifurque vers le côté aspiration de la roue (38) entre lesdits deux sièges de soupape (68, 70), dans lequel l'organe de soupape (64), au moins au nombre de un, présente deux surfaces de soupape orientées vers les sièges de soupape (68, 70), et qui sont agencées de façon telle que, lors d'un déplacement de l'organe de soupape (64), une surface de soupape s'éloigne de l'un des sièges de soupape (68, 70) et simultanément l'autre surface de soupape se rapproche de l'autre siège de soupape (68, 70).
  12. Groupe motopompe centrifuge selon la revendication 11, caractérisé en ce que les sièges de soupape (68, 70) se font face et l'organe de soupape (64), au moins au nombre de un, est situé entre les sièges de soupape (68, 70).
  13. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'organe de soupape (120), au moins au nombre de un, est en forme de manchon, en ce que le second trajet d'écoulement traverse l'intérieur du manchon et en ce que le manchon comporte, dans une paroi, un orifice de sortie (134) qui est disposé en regard d'un orifice d'entrée (136) d'un trajet d'écoulement vers le côté aspiration de la roue (38') de façon à pouvoir être amené plus ou moins en coïncidence avec l'orifice d'entrée (136) par le déplacement de l'organe de soupape (120).
  14. Groupe motopompe centrifuge selon la revendication 13, caractérisé en ce que l'organe de soupape (120) est conçu et agencé de façon à plus ou moins fermer, par sa face extérieure et en fonction du positionnement de l'organe de soupape (120), une liaison d'écoulement depuis le premier trajet d'écoulement jusqu'à l'orifice d'entrée (136).
  15. Groupe motopompe centrifuge selon la revendication 13 ou 14, caractérisé en ce qu'est formée au niveau de l'organe de soupape (120) une surface de soupape agissant dans la direction de déplacement (Z) de l'élément de soupape (120), laquelle, dans une position extrême de l'organe de soupape, repose sur un siège de soupape (118) de façon à fermer le second trajet d'écoulement.
  16. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'espace de réception (50; 50') présente, à une première extrémité axiale, une première ouverture (52; 52') et, de préférence à une seconde extrémité axiale opposée, une seconde ouverture (54; 54').
  17. Groupe motopompe centrifuge selon la revendication 16, caractérisé en ce que l'une des ouvertures (52; 52'; 54; 54') forme la seconde tubulure d'aspiration ou est reliée à la seconde tubulure d'aspiration, suite à quoi, de préférence, un insert de soupape, relié à la seconde tubulure d'aspiration, s'étend vers l'extérieur à partir de l'ouverture.
  18. Groupe motopompe centrifuge selon la revendication 16 ou 17, caractérisé en ce que l'une des ouvertures est fermée par un élément de fermeture (122).
  19. Groupe motopompe centrifuge selon la revendication 18, caractérisé en ce que l'actionneur (124) est disposé au niveau de l'élément de fermeture (122) et/ou en ce qu'un élément d'actionnement (136) de l'actionneur (124) relié à l'organe de soupape s'étend à travers l'élément de fermeture (122) et à l'intérieur de l'espace de réception.
  20. Groupe motopompe centrifuge selon l'une des revendications 1 à 17, caractérisé en ce qu'un élément d'actionnement relié à l'organe de soupape est conçu en tant que levier pivotant (78), qui s'étend transversalement à la direction de déplacement (Z) de l'organe de soupape (64) et s'étend vers l'extérieur de préférence par une paroi de l'espace de réception (50) et/ou d'un insert de soupape (56) inséré dans l'espace de réception (50). réception (50).
EP17745364.4A 2017-03-15 2017-08-03 Groupe pompe centrifuge Active EP3596342B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17161065.2A EP3376052B1 (fr) 2017-03-15 2017-03-15 Groupe pompe centrifuge
PCT/EP2017/069734 WO2018166639A1 (fr) 2017-03-15 2017-08-03 Ensemble pompe centrifuge

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Publication Number Publication Date
EP3596342A1 EP3596342A1 (fr) 2020-01-22
EP3596342B1 true EP3596342B1 (fr) 2022-01-12

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EP17161065.2A Active EP3376052B1 (fr) 2017-03-15 2017-03-15 Groupe pompe centrifuge
EP17745364.4A Active EP3596342B1 (fr) 2017-03-15 2017-08-03 Groupe pompe centrifuge

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US (1) US20210156396A1 (fr)
EP (2) EP3376052B1 (fr)
CN (1) CN110431312B (fr)
WO (1) WO2018166639A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH499018A (de) * 1968-09-03 1970-11-15 Troesch Hans A Dr Ing Umwälzpumpe für Heizungsanlagen
CH536464A (de) * 1971-01-26 1973-04-30 Rudolf Sonnek Ing Tech Buero Umwälzpumpe für Warmwasser-Zentralheizungsanlagen
CH555981A (de) * 1972-09-05 1974-11-15 Saurer Ag Adolph Anlage zum mischen und umwaelzen von waermetraegern.
DE19809123B4 (de) * 1998-03-04 2005-12-01 Daimlerchrysler Ag Wasserpumpe für den Kühlkreislauf einer Brennkraftmaschine
DE19943981A1 (de) * 1999-09-14 2001-03-15 Behr Thermot Tronik Gmbh & Co Ventil zum Regeln der Temperatur eines Verbrennungsmotors
US6499442B2 (en) * 2000-12-18 2002-12-31 Thomas J. Hollis Integral water pump/electronic engine temperature control valve
EP2172654B2 (fr) * 2008-10-01 2013-11-20 Grundfos Management A/S Agrégat de pompe centrifuge
WO2015070955A1 (fr) * 2013-11-16 2015-05-21 Brose Fahrzeugteile Gmbh & Co Kommanditgesellschaft, Würzburg Pompe à réfrigérant électromotrice
DE202014007453U1 (de) * 2014-06-07 2015-01-09 Günter Scholz Beimisch- und Umwälzpumpe, mit saugseitig eingebauten Zweiwegebeimischventil, zur Regelung der Vorlauftemperatur in einen Heizungs- oder Kühlwasserkreislauf

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Title
None *

Also Published As

Publication number Publication date
CN110431312B (zh) 2021-09-28
WO2018166639A1 (fr) 2018-09-20
CN110431312A (zh) 2019-11-08
EP3376052A1 (fr) 2018-09-19
EP3596342A1 (fr) 2020-01-22
US20210156396A1 (en) 2021-05-27
EP3376052B1 (fr) 2020-11-04

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