EP3376052B1 - Groupe pompe centrifuge - Google Patents

Groupe pompe centrifuge Download PDF

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Publication number
EP3376052B1
EP3376052B1 EP17161065.2A EP17161065A EP3376052B1 EP 3376052 B1 EP3376052 B1 EP 3376052B1 EP 17161065 A EP17161065 A EP 17161065A EP 3376052 B1 EP3376052 B1 EP 3376052B1
Authority
EP
European Patent Office
Prior art keywords
centrifugal pump
pump assembly
impeller
valve element
valve
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
EP17161065.2A
Other languages
German (de)
English (en)
Other versions
EP3376052A1 (fr
Inventor
Thomas Blad
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to EP17161065.2A priority Critical patent/EP3376052B1/fr
Priority to EP17745364.4A priority patent/EP3596342B1/fr
Priority to US16/494,003 priority patent/US20210156396A1/en
Priority to PCT/EP2017/069734 priority patent/WO2018166639A1/fr
Priority to CN201780088454.0A priority patent/CN110431312B/zh
Publication of EP3376052A1 publication Critical patent/EP3376052A1/fr
Application granted granted Critical
Publication of EP3376052B1 publication Critical patent/EP3376052B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—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 with an electric drive motor, at least one impeller driven in rotation by the drive motor, and two suction connections arranged on the suction side of the impeller.
  • Centrifugal pump units with integrated valve devices which make it possible to suck in or convey from two suction connections, the flow path between the two suction connections being able to be switched by the valve device.
  • the centrifugal pump assembly has an electric drive motor in a known manner, the electric drive motor preferably being a wet-running electric drive motor.
  • a wet-running electric drive motor has a can or a can which separates the stator space from the rotor space so that the rotor rotates in the liquid to be conveyed.
  • the rotor can, for example, be a permanent magnet rotor.
  • the drive motor preferably has a control device via which the speed of the drive motor can be changed.
  • the control device can further preferably have a frequency converter.
  • the centrifugal pump unit has two suction connections arranged on the suction side of the impeller, so that liquid can be fed to the impeller from both suction connections.
  • a valve element is arranged in at least one first flow path from a first of the two suction connections to the impeller.
  • the centrifugal pump assembly according to the invention also has a mechanical drive device which is used to move or adjust the valve element.
  • the mechanical drive device draws its energy solely from the conveyed fluid and does not require any electrical drive.
  • the mechanical drive device has a connection to a pressure chamber on the output side of the impeller and is designed in such a way that it exerts an actuating force on the valve element caused by changes in pressure and / or temperature. I.e.
  • the drive device moves the valve element purely mechanically as a function of pressure and / or temperature, this setting being based on the pressure or liquid temperature prevailing on the output side of the impeller via the connection described. This makes it very easy to adjust the valve element, take place in particular to mix two fluid flows from the two suction connections.
  • the impeller as well as the two suction connections and the above-described first flow path are preferably arranged with the valve element in a common housing, wherein this housing can be designed in one or more parts.
  • At least one basic structure of the housing which preferably comprises the majority of the housing walls, is preferably designed in one piece or in one piece, in particular as a cast component.
  • the valve device is integrated into the centrifugal pump unit.
  • a combined pump and valve housing is thus created, wherein this integrated housing for the valve can have a section which is referred to below as the valve housing.
  • a second flow path, which runs from the second suction connection to the impeller, is also preferably arranged in the interior of this housing.
  • valve device in the centrifugal pump unit can be configured in various ways. It is thus possible for a valve element to be arranged only in said first flow path from a first of the two suction connections to the impeller. Alternatively, it is possible that a valve element is arranged in each case both in the first flow path and in a second flow path from a second of the two suction connections to the impeller. It is also possible for a common valve element to be arranged in both flow paths or for the valve elements to be coupled to one another in the flow paths.
  • the valve elements are preferably arranged or coupled in such a way that when one flow path is closed, the other flow path is opened at the same time.
  • the drive device can have a pressure surface which is connected to the Valve element is connected to its movement.
  • the valve element can be moved by a pressure force on the pressure surface.
  • the pressure surface is arranged such that a pressure generated by the impeller acts on the pressure surface.
  • the valve element can be moved or switched as a function of the pressure, it being able to move, for example, by different degrees, in particular proportionally, to the pressure depending on the level of pressure.
  • Such a configuration enables the flow path from the first of the two suction connections to the impeller to be opened further, for example with increasing pressure, if the valve element is designed so that it continues to move with the aid of the pressure acting on the pressure surface is opened.
  • valve element when no pressure or a minimal pressure acts on the pressure surface, the valve element can be in a rest position in which the flow path is as closed as possible and preferably completely.
  • a reverse configuration would also be conceivable, according to which the flow path is opened as much as possible in the rest position and is increasingly closed by increasing the pressure, the flow path being able to be completely closed in a second end position.
  • the drive device preferably has an adjusting element that deforms as a function of temperature, in particular an expansion element.
  • an element deforms as a function of temperature, in particular it expands at higher temperatures. This change in shape is transmitted to the valve element through a mechanical connection so that it can be moved depending on the temperature.
  • a very simple regulation of a mixture temperature can be achieved in that the valve element is moved depending on the outlet temperature on the pressure side of the impeller.
  • the drive device is with the valve element preferably arranged so that the valve element is closed as the temperature rises, so that the admixture of warm liquid can be reduced.
  • the drive device preferably has an adjusting element that is movable in a cylinder, and the cylinder has a connection channel to a pressure chamber surrounding the impeller. Liquid reaches the cylinder via the connecting channel from the outlet side of the impeller, so that either the pressure or the temperature of the liquid can act on the adjusting element there.
  • the pressure surface can preferably be formed on a piston that is movable in a cylinder or on a deformable bellows. If the pressure in the cylinder increases, the piston is displaced in the cylinder or the bellows is deformed.
  • the valve element can be moved along with the movement of the piston or deformation of the bellows.
  • the malleable bellows has the advantage of being particularly robust. On such a bellows, in particular an end face can form the pressure surface and this end face can be connected to the valve element, for example via a piston rod.
  • the bellows has the advantage that it does not have to slide along an inner wall of the cylinder in order to achieve a seal, so that greater functional reliability can be guaranteed.
  • the pressure from the pressure chamber is applied to the cylinder via the connecting channel.
  • the valve element can be connected to the piston or the actuating element in the cylinder via a piston rod or in another suitable manner.
  • a spring acts on the valve element, which spring acts on the valve element with a spring force which is directed in the opposite direction to an actuating force which is generated by the drive device.
  • the force can for example be a compressive force which is generated by a pressure on a pressure surface. This means that the actuating force displaces the valve element against the spring force, and when the actuating force decreases, the spring preferably moves the valve element back into its rest or starting position.
  • the actuating force can be reduced, for example, by decreasing the pressure on the pressure surface or by reducing the temperature of the liquid on the outlet side of the impeller.
  • the spring acts as a return element.
  • a corresponding restoring force could, however, also be generated in a different way, for example by a weight on which the force of gravity acts, or, for example, also magnetically.
  • valve element is mounted so as to be linearly movable, and a movement axis along which the valve element is mounted so as to be movable extends preferably transversely and in particular normal to an axis of rotation of the impeller.
  • the direction of movement of the valve element running transversely to the axis of rotation of the impeller enables the centrifugal pump unit to be constructed in a compact manner.
  • the valve element is designed and arranged relative to a valve seat such that the valve element rests against the valve seat in a rest position and closes the flow path from the first suction connection to the impeller.
  • the valve element is displaced by the actuating force of the drive device in such a way that it is spaced apart from the valve seat and clears the flow path.
  • a valve seat is preferably located in each of the flow paths, which valve seat interacts with the valve element or the valve elements.
  • the valve element is preferably located in a flow path in the rest position on the valve seat, while in the other flow path the valve element is spaced as far as possible from the valve seat.
  • a flow path from the second suction connection to the impeller is present in the centrifugal pump unit.
  • no valve element is arranged in this second flow path.
  • the first flow path opens from the first suction connection downstream of the valve element into the second flow path from the second suction connection to the impeller. I.e. Both flow paths, starting from both suction connections, open out at the impeller or the suction mouth of the impeller, so that the impeller can suck in liquid from both flow paths.
  • the point at which the flow paths merge or merge into one another represents a mixing point at which the flows from the two flow paths mix.
  • a mixture can, as described above, be used to change the temperature by mixing a warm and a cold flow with one another.
  • the valve element can be used to change the mixing ratio and thus adjust the temperature.
  • valve element is arranged only in the described first flow path from the first suction connection to the impeller is particularly suitable for an injection circuit in which the liquid is supplied to the first suction connection under pressure.
  • the impeller described here can also be used for suction alone.
  • a valve element can also be used which acts in both flow paths, for example opens one flow path while at the same time closing the other flow path.
  • the electric drive motor preferably has a control device via which the speed of the drive motor can be changed.
  • the control device is preferably connected to a temperature sensor in the centrifugal pump assembly.
  • the temperature sensor is preferably arranged in such a way that it can detect the temperature of the liquid on the outlet side of the impeller. That is to say, the temperature sensor is preferably arranged in or in the vicinity of the pressure space which surrounds the impeller.
  • the control device is designed in such a way that it sets the speed of the drive motor as a function of a temperature detected by the temperature sensor. A temperature setpoint value can be specified for the control device and the control device regulates the speed so that this temperature value is kept constant.
  • the control device increases the speed of the drive motor, whereby the pressure on the output side of the impeller rises and, in the case of a pressure-dependent drive device, the valve element is displaced by the higher pressure, so that a mixing ratio of the flows through the flow paths can be changed, that a larger proportion of warm liquid is mixed in.
  • the speed of the drive motor is reduced accordingly, whereby the pressure drops and the valve element moves in the other direction.
  • the drive motor is preferably operated with a constant pressure control. It is possible to design the control device in such a way that its nominal temperature values can be specified, for example based on other recorded parameters. For example, the temperature setpoints can be increased depending on the outside temperature.
  • the embodiment described has the advantage that temperature regulation is possible without the need for an electrically or motor-driven drive element for the valve element. Rather, the temperature control is possible solely via the regulation or control of the drive motor. Yet it is there possible to change the temperature setpoint using electrical signals.
  • the valve element is arranged in a cylindrical valve housing, which preferably has openings at two mutually opposite axial ends which are closed by closure elements.
  • the openings allow the valve element to be introduced into the valve housing.
  • the openings make it possible to manufacture the valve housing simply as a cast component made of metal or plastic, in particular by injection molding, since cores can be removed through the openings.
  • the openings can then be closed by the aforementioned closure elements.
  • the closure elements are furthermore preferably releasable so that the valve housing can be opened for maintenance purposes.
  • the valve housing is inserted through at least one of the openings, an insert on which a valve seat cooperating with the valve element is formed. More preferably, the valve element and / or the drive device are also fastened or arranged on the insert, so that the entire valve device can preferably be inserted through one of the openings in the valve housing in the pre-assembled state. This simplifies the assembly.
  • the insert is preferably designed in such a way that it defines the valve seat in relation to the flow paths that open into the valve housing or branch off from the valve housing, positions it and seals it against these flow paths so that the valve seat with the valve element can fulfill its desired function, at least to specifically close or release a flow path.
  • the valve housing is arranged on an axial end face of the pump housing and, in particular, is designed in one piece with the pump housing, so that an integral housing is created.
  • the valve housing can be designed in one piece with the pump housing as a cast component made of metal or plastic.
  • the pump housing is advantageously unchanged in its interior, in particular in an area facing the impeller, so that this area can preferably be machined in the same way as corresponding pump housings without the valve housing.
  • the components arranged in the pump housing such as a deflector plate, which separates the suction chamber and pressure chamber, and in particular the impeller, can be designed identically to conventional pump assemblies without a valve housing.
  • the valve housing is preferably connected to the first suction connection via a first flow channel, to the second suction connection via a second flow channel and to a suction chamber in the interior of the pump housing adjoining the impeller.
  • the valve housing can take over the entire suction-side flow control and also contain a mixing point for mixing the flows from the first and second suction port, so that a mixed flow into the suction chamber and thus into the suction side through a connection between the valve housing and the suction chamber of the impeller can occur.
  • the first and the second flow channel are in and / or on the pump housing and the valve housing intersects the first and second flow channels.
  • the valve housing intersects the flow channels, this means that the basic shape of the valve housing intersects or penetrates the basic shapes of the flow channels, the flow channels, the pump housing and the valve housing preferably being manufactured in one piece as a cast component, in particular as an injection molded component made of plastic.
  • the valve housing particularly preferably has a cylindrical basic shape and more preferably a circular cylindrical basic shape and extends with its longitudinal axis normal to a plane spanned by the axis of rotation of the impeller and a radius of this axis of rotation.
  • the valve element preferably moves in the valve housing in the direction of its longitudinal axis, the valve housing simultaneously being able to form a cylinder for guiding an adjusting element or a piston with the pressure surface described above.
  • the closure elements which close the valve housing at the openings, engage in the openings and that the valve element and / or an adjusting element or piston are arranged and / or guided in the interior of at least one closure element.
  • the longitudinal axis of the valve housing which extends transversely to the axis of rotation of the impeller, also has the advantage that the valve housing can be arranged in a space-saving manner on an end or bottom side of a pump housing facing away from the drive motor and there at least one flow channel, which is normally in Pump housing is designed, can cut.
  • a longitudinal axis defined by the openings in the valve housing ie preferably a longitudinal axis which extends through the Extending center points of the openings, preferably extends transversely to an axis defined by the suction connection and a pressure connection of the centrifugal pump assembly.
  • the longitudinal axis of the valve housing can be the central or symmetry axis of this basic shape.
  • the axis of the valve housing which extends transversely to the connections of the centrifugal pump unit, is advantageous for the casting of the housing and also favors the compact design of the centrifugal pump unit, since the openings of the valve housing do not collide with connection flanges on the suction connection and the pressure connection and also with closure elements which the openings of the valve housing are relatively freely accessible so that they can be easily opened even when the centrifugal pump unit is installed, i.e. when the pressure connection and suction connection are connected to external pipelines, for example to remove the valve element components from the valve housing for maintenance purposes .
  • a first suction connection of the pump assembly extends, as described, preferably in alignment with the pressure connection, as is known from conventional centrifugal pump assemblies, in particular heating circulation pump assemblies.
  • the pressure connection and the suction connection are on one axis.
  • a second suction connection preferably extends transversely to a first suction connection, in particular a first suction connection, as described above.
  • the second suction connection can extend in particular in a direction which runs parallel to the axis of rotation of the impeller of the centrifugal pump assembly and further preferably in alignment with the axis of rotation.
  • the second suction connection can extend in the axial direction away from the rear side of the pump housing, ie the side of the pump housing facing away from the drive motor.
  • the centrifugal pump unit described is preferably a circulating pump unit and more preferably a heating circulating pump unit, i. H. around a circulating pump unit which is designed and intended to be used in a heating system.
  • the valve element can form a mixing valve by means of which a mixing ratio between a warm and a cold liquid flow can be set as a function of pressure or temperature.
  • a heat transfer medium conveyed in the circuit through a heating circuit with increasing pressure i.e. H. increasing speed of the drive motor
  • an increasing amount of heated heat transfer medium which has previously flowed through a heat source, such as a boiler
  • the speed of the drive motor is preferably increased with increasing heat demand, as described above.
  • the increased flow causes an increased pressure, so that the valve element, which is moved as a function of pressure, increases the temperature of the heat transfer medium by mixing in heated liquid.
  • the mixing ratio can also be changed as a function of the temperature using a drive device that reacts to temperature changes.
  • the drive device can be set to a fixed temperature value to be achieved and can be designed such that, when the temperature falls below this, it displaces the valve element in such a way that the associated flow path is opened further so that more heated heat transfer medium is mixed in.
  • the drive device can react in such a way that the valve element is moved more into a closed position, so that less heated heat transfer medium is added.
  • the centrifugal pump assembly has a stator or motor housing 2 with a pump housing 4 attached thereto axially in the direction of the longitudinal or rotational axis X.
  • An electric drive motor is arranged in the motor housing 2 and has a stator 6 with a rotor 7 arranged in the interior of a can 8. I.e. it is a wet-running electric drive motor.
  • the rotor drives an impeller 10, which rotates inside the pump housing 4.
  • an electronics housing 12 is attached to the motor housing 2, in which an electronic control device 14 is arranged which controls the drive motor.
  • the control device 14 is designed in particular for setting or regulating the speed of the drive motor, so that it can change the speed of the drive motor.
  • the control device further preferably has a frequency converter.
  • the control device can in particular have a temperature sensor arranged in the vicinity of the pressure chamber 16 or the can 8 in order to detect a temperature on the output side of the impeller 10.
  • the control device can be designed in such a way that its temperature setpoint values can be specified and it regulates the speed of the drive motor so that the setpoint values are reached.
  • a change in the speed changes the pressure on the outlet side, via which the pressure-dependent mixing device described below is operated.
  • the control device regulates the drive motor preferably according to a constant pressure curve, it being possible for this constant pressure, as described, to be changed as a function of temperature.
  • the impeller 10 is surrounded in the interior of the pump housing 4 by a pressure chamber 16 which opens into the pressure port or pressure connection 18 of the centrifugal pump assembly.
  • the impeller 10 faces a suction chamber 22 with its suction mouth 20.
  • the pump housing 4 also has two suction nozzles or suction connections 24 and 26.
  • a first suction connection 24 is designed and arranged in the pump housing 4 in a conventional manner. I.e. This suction connection 24 extends along a common axis with the pressure connection 18.
  • the second suction connection 26 extends in the direction of the axis of rotation X, about which the impeller 10 rotates, away from the axial end facing away from the electronics housing 12 and away from the pump housing 4. I.e. the suction port 26 extends essentially in alignment with the suction mouth 20 of the impeller 10.
  • a cylindrical valve housing 28 is formed integrally or in one piece with the pump housing 4.
  • the valve housing 28 is formed in one piece with the pump housing 4 in this exemplary embodiment as a cast component, in particular made of plastic or cast metal.
  • the valve housing 28 has a circular cylindrical basic shape with a longitudinal axis Y, which extends transversely to the axis of rotation X of the impeller 10 and in particular normal to a plane which is spanned by the axis of rotation X and an axis A, which is defined by the pressure connection 18 and the first Suction port 24 is defined.
  • the cylindrical valve housing 28 is located in the pump housing 4 in such a way that it intersects both a flow path from the first suction connection 24 to the suction chamber 22 and a flow path from the second suction connection 26 to the suction chamber 22.
  • there is a connecting channel 30 which extends from the pressure chamber 16 into the interior of the valve housing 28.
  • the connecting channel 29 can be introduced very simply as a bore from the inside of the pump housing 4 into the pump housing 4.
  • the valve housing 28 is designed to be open at both of its longitudinal ends, viewed in the direction of the longitudinal axis Y, and is closed at each longitudinal end by a closure element 30.
  • An insert 32 which defines a valve seat 34 in its interior, is inserted into the valve housing 28.
  • the valve seat 34 lies in a partition wall which is formed by the insert 32.
  • the tubular insert 32 On one side of the partition wall, the tubular insert 32 has an opening 36 which establishes a connection to the flow path from the second suction connection 26 to the suction chamber 22.
  • the insert 32 On the opposite side of the partition wall with the valve seat 34 in the direction of the longitudinal axis Y, the insert 32 has an opening 38 which establishes a connection to the flow path from the first suction connection 24 to the suction chamber 22, this flow path being through the opening in valve seat 34 and opening 36.
  • valve element 40 fastened to the insert 32 is also arranged, which is attached to the valve seat 34, as in FIG Figure 4 shown, sealing can come to the plant.
  • a compression spring 42 is arranged between the closure element 30 and the valve element 40, which presses the valve element into its closed position resting on the valve seat 34, which in Figure 4 is shown. In this position, the impeller 10 only sucks in liquid through the second suction connection 26 via the suction mouth 20 and the suction chamber 22 during rotation. The first suction connection 24 is closed in this state by the valve element 40, which rests against the valve seat 34.
  • a return is preferably connected to the suction connection 26, so that in this switch position the liquid heat transfer medium is circulated by the impeller 10 in the heating circuit without heated heat transfer medium being supplied from a heat source.
  • the connection for the heated heat transfer medium is preferably the suction connection 24.
  • the valve element 40 is connected to a piston 46 via a piston rod 44.
  • the piston 46 forms an actuator which is arranged in the area of the closure element 30.
  • the piston 46 is tightly connected to an axial end of the insert 32 via a bellows 48, so that the interior of the insert 32 is sealed off from the outside of the bellows 48 and the piston 46 via the bellows 48.
  • the latter forms a pressure surface 50 which extends normal to the longitudinal axis Y of the valve housing and the valve device.
  • the piston 46 can move along the longitudinal axis Y when there is pressure on the pressure surface 50, the valve element 40 being moved along with the piston rod 44 and being lifted off the valve seat 34, as in FIG Figure 5 is shown.
  • both suction-side flow paths are open and merge into one another in the area of suction space 22, so that a mixing area or mixing point is formed there, in which the flows from the two suction connections 24 and 26 mix.
  • the opening cross section changes through the valve seat 34 and thus the mixing ratio of the two flows.
  • the interior of the valve housing 28, in which the piston 46 is arranged is connected to the pressure chamber 16 via the connecting channel 29.
  • a pressure area 52 is thus formed on the outside of the bellows 48 and the pressure surface 50, in which essentially the same pressure as in the pressure chamber 16, ie on the output side of the impeller 10, prevails.
  • the piston 46 is displaced against the compression spring 42 by the pressure force generated on the pressure surface 50, so that the valve, which is formed by the valve element 40 and the valve seat 34, is opened further and the proportion of the flow through the suction port 24 is increased, ie preferably the proportion of heated heat transfer medium is increased.
  • the temperature of the heat transfer medium at the pressure connection 18 can be increased at the same time.
  • valve element 40 with the valve seat 34 acts only in the flow path from the first suction port 24 to the impeller 10.
  • Such an arrangement is particularly suitable for an injection circuit in which the liquid is supplied in the suction port 24 with a pre-pressure.
  • a valve arrangement into the valve housing 28, in which the valve is also in the second flow path from the second suction port 26 to the Impeller 20 acts.
  • a valve element can interact with two valve seats in such a way that one flow path is opened, while at the same time the other flow path is closed, preferably by the same amount. Due to the structural design, the valve element and valve seats can be adapted very easily to different applications.
  • the mixing device described here works depending on the pressure.
  • a valve which operates as a function of temperature can also be implemented in a very simple manner.
  • only another insert 32 has to be inserted into the valve housing 28, namely an insert which has an element that expands as a function of temperature, for example an expansion element.
  • the temperature in the pressure area 52 is essentially the same as on the outlet side of the impeller 10, so that the valve element 40 could also be moved here as a function of temperature, with an element that expands as a function of temperature being arranged in the area of the pressure area 52 instead of the piston 46 would and would be arranged such that the valve, which is formed by the valve element 40 and the valve seat 34, closes with increasing temperature in the pressure region 52.

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  • General Engineering & Computer Science (AREA)
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Claims (19)

  1. Groupe motopompe centrifuge comportant un moteur électrique d'entraînement (4, 6), au moins une roue mobile (10) entraînée en rotation par le moteur d'entraînement (4, 6), ainsi que deux raccords d'aspiration (24, 26) disposés côté aspiration de la roue mobile (10), dans lequel
    dans au moins un premier trajet d'écoulement, depuis un premier (24) des deux raccords d'aspiration vers la roue mobile (10) est agencé un élément de soupape (40), qui est pourvu d'un dispositif d'entraînement mécanique (46) qui présente une connexion (29) à une chambre de pression (16) côté sortie de la roue mobile (10) et est conçu de telle sorte qu'il exerce sur l'élément de soupape (40) une force de commande provoquée par des changements de pression et/ou de température, caractérisé en ce que l'élément de soupape (40) est agencé dans un boîtier de soupape cylindrique (28) qui présente des ouvertures au niveau de deux extrémités axiales opposées, un insert (32) étant inséré dans le boîtier de soupape (28) à travers l'une des ouvertures, au niveau duquel est formé au moins un siège de soupape (34) coopérant avec l'élément de soupape (40), au moins au nombre de un.
  2. Groupe motopompe centrifuge selon la revendication 1, caractérisé en ce que la roue mobile (10), les deux raccords d'aspiration (24, 26) et au moins le premier trajet d'écoulement ainsi que l'élément de soupape sont agencés dans un boîtier commun (4, 28).
  3. Groupe motopompe centrifuge selon la revendication 1 ou 2, caractérisé en ce qu'un élément de soupape (40) est agencé uniquement dans un premier trajet d'écoulement depuis un premier (24) des deux raccords d'aspiration vers la roue mobile (10), ou en ce qu'un élément de soupape respectif ou un élément de soupape commun est agencé dans le premier trajet d'écoulement et un second trajet d'écoulement depuis un second (26) des deux raccords d'aspiration vers la roue mobile (10).
  4. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le dispositif d'entraînement présente une surface de pression (50) qui est agencée de telle sorte que, via la connexion (29) à la chambre de pression (16), une pression générée par la roue mobile (10) agit sur la surface de pression (50).
  5. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le dispositif d'entraînement comporte un élément de réglage qui se déforme en fonction de la température, en particulier un élément expansible.
  6. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le dispositif d'entraînement comporte un élément de réglage (46) mobile dans un cylindre et en ce que le cylindre présente un canal de connexion (29) à une chambre de pression (16) entourant la roue mobile (10), suite à quoi de préférence la surface de pression (50) est formée au niveau d'un piston (46) mobile dans le cylindre ou au niveau d'un soufflet déformable (48).
  7. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce qu'un ressort (42) vient en prise au niveau d'au moins un élément de soupape (40), lequel ressort charge l'élément de soupape (40) d'une force de ressort qui est orientée à l'opposé d'une force de commande qui est générée par le dispositif d'entraînement.
  8. Groupe motopompe centrifuge, caractérisé en ce que l'élément de soupape (40), au moins au nombre de un, est logé pour se déplacer linéairement, et en ce qu'un axe de déplacement (Y) le long duquel l'élément de soupape (40) est mobile s'étend de préférence transversalement à un axe de rotation (X) de la roue mobile (10).
  9. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que l'élément de soupape (40) est agencé par rapport à au moins un siège de soupape (34) de telle sorte que l'élément de soupape (40) repose contre le siège de soupape (34) dans une position de repos et ferme le trajet d'écoulement depuis le premier raccordement d'aspiration (24) vers la roue mobile (10).
  10. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé par un trajet d'écoulement depuis le second raccord d'aspiration (26) vers la roue mobile (10), suite à quoi de préférence le trajet d'écoulement depuis le premier raccord d'aspiration (24) en aval de l'élément de soupape (40) débouche dans le trajet d'écoulement depuis le second raccord d'aspiration (26) vers la roue mobile (10).
  11. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le moteur électrique d'entraînement (4, 6) présente un dispositif de commande qui est relié à un capteur de température dans le groupe motopompe centrifuge et est conçu de telle sorte qu'il règle une vitesse de rotation du moteur d'entraînement (4, 6) en fonction d'une température détectée par le capteur de température.
  12. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que les ouvertures sont fermées par des éléments de fermeture (30).
  13. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le dispositif d'entraînement est agencé dans l'insert.
  14. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le boîtier de soupape (28) est agencé au niveau d'une face d'extrémité axiale d'un carter de pompe (4) et est en particulier formé d'une seule pièce avec le carter de pompe (4).
  15. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le boîtier de soupape (28) est en relation avec un premier canal d'écoulement vers le premier raccord d'aspiration (24), un second canal d'écoulement vers le second raccord d'aspiration (26), ainsi qu'une chambre d'aspiration (22) adjacente à la roue mobile (10) dans l'intérieur du carter de pompe (4).
  16. Groupe motopompe centrifuge selon la revendication 15, caractérisé en ce que le premier et le second canaux d'écoulement sont formés dans et/ou sur le carter de pompe (4) et en ce que le boîtier de soupape (28) coupe le premier et le second canaux d'écoulement.
  17. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce que le boîtier de soupape (28) présente une forme de base cylindrique et s'étend, avec son axe longitudinal (Y) perpendiculaire à un plan sous-tendu par l'axe de rotation (X) de la roue mobile et un rayon (A) par rapport à cet axe de rotation (X).
  18. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce qu'un axe longitudinal (Y) du boîtier de soupape (28) défini par les ouvertures s'étend transversalement à un axe (A) défini par un raccord d'aspiration (24) et un raccord de pression (18) du groupe motopompe centrifuge.
  19. Groupe motopompe centrifuge selon l'une des revendications précédentes, caractérisé en ce qu'un second raccord d'aspiration (26) s'étend transversalement à un premier raccord d'aspiration (24) et de préférence dans la direction d'un axe de rotation (X) du groupe motopompe centrifuge.
EP17161065.2A 2017-03-15 2017-03-15 Groupe pompe centrifuge Active EP3376052B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP17161065.2A EP3376052B1 (fr) 2017-03-15 2017-03-15 Groupe pompe centrifuge
EP17745364.4A EP3596342B1 (fr) 2017-03-15 2017-08-03 Groupe pompe centrifuge
US16/494,003 US20210156396A1 (en) 2017-03-15 2017-08-03 Centrifugal pump assembly
PCT/EP2017/069734 WO2018166639A1 (fr) 2017-03-15 2017-08-03 Ensemble pompe centrifuge
CN201780088454.0A CN110431312B (zh) 2017-03-15 2017-08-03 离心泵机组

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17161065.2A EP3376052B1 (fr) 2017-03-15 2017-03-15 Groupe pompe centrifuge

Publications (2)

Publication Number Publication Date
EP3376052A1 EP3376052A1 (fr) 2018-09-19
EP3376052B1 true EP3376052B1 (fr) 2020-11-04

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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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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)

Family Cites Families (9)

* 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
CN1365216A (zh) * 2000-12-18 2002-08-21 扎尔林克半导体V.N.股份有限公司 交换数据库高速缓冲存储器管理系统
PL2172654T5 (pl) * 2008-10-01 2014-04-30 Grundfos Management As Agregat z pompą wirową
CN105745450B (zh) * 2013-11-16 2017-10-24 博泽沃尔兹堡汽车零部件有限公司 电动冷却剂泵
DE102014008618A1 (de) * 2014-06-07 2015-12-17 Günter Scholz Beimisch- und Umwälzpumpe, mit saugseitig eingebautem Zweiwegebeimischventil, zur Regelung der Vorlauftemperatur in einen Heizungs- oder Kühlwasserkreislauf.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2018166639A1 (fr) 2018-09-20
EP3596342B1 (fr) 2022-01-12
US20210156396A1 (en) 2021-05-27
EP3596342A1 (fr) 2020-01-22
CN110431312B (zh) 2021-09-28
CN110431312A (zh) 2019-11-08
EP3376052A1 (fr) 2018-09-19

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