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EP3596342A1 - Ensemble pompe centrifuge - Google Patents

Ensemble pompe centrifuge

Info

Publication number
EP3596342A1
EP3596342A1 EP17745364.4A EP17745364A EP3596342A1 EP 3596342 A1 EP3596342 A1 EP 3596342A1 EP 17745364 A EP17745364 A EP 17745364A EP 3596342 A1 EP3596342 A1 EP 3596342A1
Authority
EP
European Patent Office
Prior art keywords
valve
receiving space
centrifugal pump
valve element
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.)
Granted
Application number
EP17745364.4A
Other languages
German (de)
English (en)
Other versions
EP3596342B1 (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
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
Publication of EP3596342A1 publication Critical patent/EP3596342A1/fr
Application granted granted Critical
Publication of EP3596342B1 publication Critical patent/EP3596342B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • 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 Umisselzpumpenaggregate in order to circulate a liquid heat transfer medium, usually water, in the heating system.
  • mixers or mixing devices are integrated into many heating systems in order to be able to adapt the temperature of the heat carrier, in particular to be able to reduce it. This is especially necessary for underfloor heating, which operates at a lower flow temperature than that provided by a boiler.
  • such a mixer and a circulating pump unit are required for underfloor heating in order to circulate the heat carrier in the underfloor heating circuit.
  • the centrifugal pump assembly has an electric drive motor and at least one of these rotating powered impeller on.
  • the electric drive motor is preferably designed as a wet-running electric drive motor, that is, as a motor with a split tube or split pot between the stator and the rotor.
  • the drive motor may 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 assembly according to the invention corresponds to a conventional centrifugal pump unit, as it is used as Umisselzpumpenaggregat for heating and air conditioning systems.
  • the centrifugal pump assembly according to the invention is preferably provided and designed for this purpose.
  • the pump housing has a receiving chamber which intersects the first suction channel and which is connected to a second suction nozzle.
  • a movable valve element is arranged inside this receiving space.
  • the valve element is connected to an actuator, via which it is movable between at least two, preferably a plurality of switching positions.
  • the valve element is infinitely movable between two end positions or end switch positions by the actuator.
  • the valve element and the actuator are designed so that by movement of the valve element, a cross-sectional relationship between the first flow path extending from the first suction port and a second flow path extending from the second suction port, is variable.
  • the valve element may be arranged such that it alters 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 arranged so that it at the same time the free flow cross-section of the first flow path. ges and the second flow path changed by increasing the flow cross-section of one of the flow paths in its displacement, while reducing the free cross-section of the other flow path is reduced. Due to the design of the receiving space in the pump housing, the entire mixing device can 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 assembly or circulating pump unit, that is, the at least one impeller. This creates a very compact and cost-effective construction. In addition, assembly is simplified, since a separate connection between a mixing device and the centrifugal pump unit is no longer required during installation.
  • the actuator may preferably be formed electrically, thermally or hydraulically.
  • the actuator is an electric stepping motor, via which the valve element can be moved to a desired position.
  • a thermal actuator can directly detect the temperature in one of the flow paths and displace the valve element in a temperature-dependent manner via an expansion element.
  • a hydraulic actuator for example, act pressure-dependent, so that the valve element is displaced with increasing pressure in a desired position.
  • a return movement can be effected in all types of drives, moreover, preferably by a return element, such as a return spring.
  • the actuator is a hydraulic actuator, which has a pressure connection, via which an output-side pressure of the impeller to the at least ⁇ a valve element acts. That is, the hydraulic actuator is connected via the pressure connection to the pressure chamber or the flow path to the discharge nozzle of the centrifugal pump assembly, so that the pressure on the output side of the impeller can be used to relocate or move the valve element.
  • a biasing element is provided, which exerts a biasing force on the valve element. At this time, the biasing member generates a biasing force that is oppositely directed to a pressing force generated by the output-side pressure.
  • the prestressing element and the valve element are arranged such that a hydraulic pressure moves the valve element counter to the pretensioning force so that, as the pressure decreases, the valve element is moved back into its starting position by the pretensioning 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 displace the valve element.
  • the actuator may be a thermal actuator, which is arranged so that it moves the at least one valve element in response to a temperature in one of the two flow paths.
  • the valve element may be arranged so 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 decreases with increasing temperature of the heating medium, the free flow cross-section of the second flow path.
  • the second flow path is used to supply heated heat carrier, a small amount of the heated heat carrier is thus supplied when reducing the flow cross-section. This can be be necessary if the temperature of the heating medium in the circuit of a floor heating is sufficiently high.
  • the first and second flow paths preferably open into the receiving space and a portion of the first suction channel forms a flow path from the receiving space to the suction side of the at least one impeller. That is, the receiving space intersects the first suction channel, so that there is a sectional area or a Schnitf- area between the first suction channel and the receiving space.
  • the valve element is preferably arranged and effective.
  • the receiving space is bounded by a wall formed integrally with at least one further part of the pump housing. That is, the receiving space is integrated directly into the pump unit and is preferably limited or formed by a wall portion of the pump housing. Particularly preferably, the wall bounding the receiving space and the entire pump housing are integrally formed, preferably made of metal or plastic. This allows a cost-effective production, for example as a cast component. In addition, eliminates possible assembly steps when the receiving space is formed directly integrally in the pump housing, as it 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 normally 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 allows for easy processing.
  • the basic form 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 removable through the opening core.
  • the arrangement of the longitudinal axis of the receiving space transversely to the axis of rotation of the drive motor allows a compact design of the centrifugal pump assembly with the integrated mixing device.
  • the first suction nozzle and a discharge nozzle formed on the pump housing are directed in the opposite direction to one another in the direction of a common installation axis, that is to say arranged away from one another.
  • the receiving space has, as described, preferably a tubular basic shape, in particular circular cylindrical basic shape, wherein the longitudinal axis of the receiving space preferably transversely and in particular extends normal to a plane in which said installation axis is located.
  • the longitudinal axis of the receiving space extends transversely and further preferably normal to a plane which is spanned by the axis of rotation of the drive motor and said mounting axis.
  • a valve insert is inserted or inserted 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 required valve seats and serves to hold and guide the movable valve element.
  • the valve insert is inserted through an opening in the receiving space. 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. In this basic form, a longitudinal end is preferably completely open, so that a large cross section is available for inserting the valve core. This allows a very simple installation.
  • a valve insert is inserted into the receiving space, which interrupts the first suction channel such that a first portion of the first suction channel forms the first flow path and a second portion of the first suction channel forms a flow path from the receiving space to the suction side of the impeller forms.
  • a second flow path which is connected to the first flow path or opens into the first flow path in the area of the valve insert, preferably extends through the receiving space. 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 supplied to the impeller.
  • the valve element is movable in the direction of the longitudinal axis of the receiving space. Thus, a large range of movement or travel for the valve element is provided. Furthermore, it is also possible to guide the valve element on the inner wall of the receiving space or on a valve insert resting on 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 to the valve seat to the plant, this allows the flow path to close completely. This is particularly preferred for the second flow path when it is used to supply heated heat transfer medium to a floor circuit. Thus, this flow path, when no heated heat carrier is required to be completely closed.
  • the flow cross section through the flow paths can be varied by varying the spacing of the valve element from the associated valve seat.
  • 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 in such a way that, on movement of the valve element, a valve surface moves away from one of the valve seats and at the same time the other valve surface approaches the other valve seat.
  • a flow path is opened and at the same time the other flow path is closed.
  • 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 are preferably facing each other and the at least one valve element is located between the valve seats. That is, the valve surfaces of the valve element are preferably located at two opposite axial ends of the valve element.
  • the at least one valve element is sleeve-shaped, wherein the second flow path extends through the interior of the sleeve and the sleeve in a wall has an outlet opening, which arranged an inlet opening of a flow path to the suction side of the impeller so opposite is that it can be brought to different cover by movement of the valve element with the inlet opening.
  • the inlet opening can thus be further closed and / or opened to to 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 embodiment, 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 such that it closes with its outer side depending on the positioning of the valve element, a flow connection from the first flow path to the inlet opening to different degrees.
  • a functionality is thus achieved in which the first flow path runs along the outside of the valve element and is opened or closed via the positioning of the outside, while the second flow path through the interior of the valve element runs.
  • 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 such that the second flow path is closed.
  • an additional closure function is thus created.
  • an axially acting valve surface sealingly abuts against the valve seat, while the flow regulation is achieved by varying coverage of the inlet opening. That is, in the parallel displacement of the wall of the valve element relative to the inlet opening no complete seal must be achieved, but this is realized via a separate sealing surface with a separate valve seat. So a simple ⁇ e mobility of the valve element to regulate the flow and yet a reliable seal in an end position can be realized.
  • 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 a second axial end opposite in the direction of its longitudinal axis.
  • these openings can serve directly as a suction connection or receive a suction fume forming the suction connection.
  • the openings allow the easy formation of the receiving space by removable cores. Incidentally, the accessibility for machining or other machining of the inner surfaces of the receiving space is ensured by the openings.
  • the components which form the venfil element, in particular a Venfileinsafz can also be inserted or inserted easily through one of the openings or both of the openings in the receiving space.
  • one of the openings forms the second suction stages or is connected to the second suction stages.
  • a building part defining or querying the second suction gap can be inserted into the opening.
  • a Venfileinsafz which is connected to the second Saugsfutzen, extending outwardly from the opening. The heif so the Saugsfutzen nichf not direkf at the opening, but at the Venfileinsafz, which is inserted into the opening and extending out of the opening to the outside.
  • the second suction stage then lies at the axial end of the Venfil facedes.
  • 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 will not be used during operation.
  • the actuator is arranged on the closure element and / or it extends to an associated with the valve element actuating element of the actuator through the closure element into the interior of the receiving space.
  • an opening of the receiving space serve as a second suction and in the other opening is a closure element, which carries the actuator or has the implementation of an actuator of the actuator arranged. This allows a space-saving arrangement of the required components.
  • 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 outwardly through a wall of the receiving space and / or a valve insert inserted into the receiving space extends.
  • a pivotable lever can rather be passed through an elastic sleeve or an elastic wall portion, so that a very simple seal is possible.
  • an actuating element in the manner of a piston rod can be guided through a linear feedthrough into the interior of the receiving space.
  • a spindle operation could be arranged for linear movement of the valve element.
  • FIG. 1 shows schematically a heating system with a centrifugal pump unit according to the invention
  • FIG. 2 shows a side view of a centrifugal pump unit according to the invention in accordance with a first embodiment of the invention
  • FIG. 2 is an exploded view of the centrifugal pump assembly according to FIG. 2
  • FIG. 4 is a plan view of the rear side of the centrifugal pump assembly according to FIGS. 2 and 3
  • Fig. 5 is a Schniftansichf the Kreiselpumpenaggregafes according to
  • Fig. 6 is a Schniftansichf the Kreiselpumpenaggregafes according to
  • FIG. 7 shows a view according to FIG. 6 with the Venfilelemenf in a second switching operation
  • Fig. 8 is a Schnansansichf along the line E-E in Fig. 2 with the
  • FIG. 9 is a Schniftansichf of FIG. 8 with the Venfilelemenf in a second Drucksfellung
  • 10 is an exploded view of a centrifugal pump assembly according to a second embodiment of the invention
  • Hg. 1 1 is a plan view of the centrifugal pump assembly according to
  • Fig. 10 from the back
  • Fig. 12 is a sectional view of the centrifugal pump assembly according to
  • FIG. 13 shows a sectional view according to FIG. 12 with the valve element in a second switching position
  • FIG. 14 shows an exploded view of a centrifugal pump assembly according to a third embodiment of the invention
  • FIG. 15 shows a sectional view of the centrifugal pump assembly according to FIG
  • Fig. 14, Fig. 1 6 a side view of the centrifugal pump assembly according to
  • Fig. 1 is a sectional view taken along the line EE in Fig. 16 with a valve element in a first switching position
  • Fig. 18 is a sectional view corresponding to Fig. 1 7 with the valve element in a second switching position
  • Fig. 19 is an exploded view of a centrifugal pump assembly according to a fourth Embodiment of the invention
  • Fig. 20 is a plan view of the centrifugal pump assembly according to
  • Fig. 21 is a sectional view of the centrifugal pump assembly according to
  • Fig. 22 is a sectional view of the centrifugal pump assembly according to
  • Fig. 23 is a sectional view corresponding to FIG. 22 with the valve element in a second switching position.
  • Fig. 1 shows schematically a heating system in which the centrifugal pump assembly according to the invention, as will be described below, can be used.
  • the heating system described has at least one heating circuit 2, which is shown here as underfloor heating circuit 2.
  • This heating circuit 2 is supplied via a mixing device 4 with a liquid heat carrier or heating medium.
  • 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. It should be understood that the centrifugal pump unit could 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 by way of example of a heating system.
  • the boiler 6 may be for example a gas boiler or an oil boiler or other suitable heat source.
  • the centrifugal pump assembly 10 or circulating pump unit 10, which includes 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 through this back to the centrifugal pump unit 10. From the return line 12, a return line 16 branches off to the boiler 6.
  • a feed line 18 also leads to the mixing point 14, wherein in the flow line 18, a mixing valve 20 is arranged, via which the flow of the heated heating medium, which is supplied to the mixing point 14, can be metered. Also in the return line 12, a mixing valve 21 is arranged, via which the flow from the return flow line 12 to the mixing point 14 is adjustable.
  • the two mixing valves 20 and 21 can be coupled so that whenever one of the valves 20, 21 closes to reduce the flow, the other valve simultaneously opens by a corresponding amount to increase the flow.
  • both mixing valves 20, 21 combined may be formed as a three-way valve, in which a valve element, both the flow line 18 and the return line 12 is influenced to the mixing ratio of the heated heating medium, which is supplied via the flow line 18, with the cold heat transfer medium, which is supplied via the return line 12 to set or change the mixing point 14 can.
  • a centrifugal pump assembly 10 is now provided, in which the entire mixing device 4, that is also the mixing valve 20 and the mixing point 14, are integrated.
  • the centrifugal pump unit has, as usual circulating pump units for heating systems. gene a drive motor, which is arranged in a stator or motor housing 22. At an axial end in the direction of the axis of rotation X, a pump housing 24 is arranged on the motor housing 22. At the opposite end, in this exemplary embodiment, an electronics housing 26 is arranged, in which an electronic control unit 28 for controlling or regulating the drive motor is arranged.
  • the drive motor has in the usual way a stator 30 and a rotor 32, which may preferably be designed as a permanent magnet rotor.
  • the drive motor is designed as a wet-running motor with a split tube 34 between the stator 30 and the rotor 32.
  • the rotor 32 is connected via a rotor shaft 36 with an impeller 38, which is located in the pump housing 24.
  • the impeller 38 can be driven in rotation.
  • the pump housing 24 has, as known Umisselzpumpen-, a discharge nozzle 40, which branches off from a surrounding the impeller 38 pressure chamber 42 in the interior of the pump housing 24. Furthermore, the pump housing 24, as well known heating circulating pump units, a first suction port 44. The discharge port 40 and the first intake port 44 are directed away from each other along a common installation axis Y. The pressure port 40 and the suction port 44 are also spaced apart by a degree which corresponds to the length of conventional or conventional Umisselzpumpenaggregate so a conventional Um internationalezpumpenaggregat can be easily replaced by the inventive centrifugal pump unit.
  • 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 formed in a shape known from conventional heating circulating pumps.
  • the pump housing 24 has a receiving space 50 which intersects the first suction channel 46.
  • the wall bounding the receiving space 50 is integrally formed with the rest of the pump housing 24 as a cast component.
  • the receiving space 50 has a circular-cylindrical inner 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 plane.
  • the receiving space 50 is tubular and has at its distal axial ends a first opening 52 and a second opening 54.
  • 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 inner cross section through the openings 52 and 54, which the assembly of components in the interior of the receiving space 56 and the processing of the inner surfaces the receiving space 50 favors.
  • the receiving space 50 divides the first suction channel 46 into two sections 46a and 46b.
  • the first portion 46a extends from the first suction port 44 to the or in the receiving space 50 and the second portion 46b of the receiving space 50 to the suction side or to the suction mouth 48 of the impeller 38th
  • a valve insert 56 is inserted or inserted into the receiving space 50 through the first opening 52.
  • the valve insert 56 has a second suction port 58 at one longitudinal end.
  • the valve insert 56 is sealed in the periphery of the opening 52 with respect to the wall of the receiving space 50.
  • the valve insert 56 interrupts with its inserted into the receiving space 50 section 60, the flow path through the first suction channel 46 so that it is divided into the aforementioned sections 46 a and 46 b.
  • the first portion 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 56th
  • a valve element 64 is movably guided in the direction of the longitudinal axis Z of the receiving space 50.
  • the valve member 64 slides to the inner circumference of the valve core 56, which is tubular, along in the longitudinal direction Z.
  • the valve element 64 has radially directed projections 66.
  • valve seat 68 and 70 In the interior of the valve insert 56, two spaced apart and facing valve seats 68 and 70 are formed.
  • the valve seat 68 adjacent to the portion of the interior of the valve insert 56, in which the opening 62 opens, from the remaining interior of the valve core.
  • the second valve seat 70 is spaced near the second suction port 58.
  • the two valve seats 68 and 70 are spaced from each other and facing each other.
  • the valve element 64 lies between the two valve seats 68 and 70, viewed in the direction of the longitudinal axis Z.
  • the second section 46b of the suction channel 46 branches off to the impeller 38 through a further opening in the valve insert 56.
  • the valve member 64 has at its opposite axial ends a first valve face 72 and a second valve face 74.
  • the axial distance between the opposite valve surfaces 72 and 74 in the direction of the longitudinal axis Z is smaller than the distance between the valve seats 68 and 70.
  • the valve member 64 may also be held in intermediate positions so that the valve seats 68, 70 and the valve surfaces 72, 74 formed flow paths can be opened differently wide.
  • an electric servomotor 76 is provided in this embodiment as an actuator, which may be designed in particular as a stepping motor and a pivotable lever 78 moves, which passes through an opening in the valve core 56 into the interior of the valve core 56 extends and engages in the valve element 64.
  • the lever extends essentially transversely to the longitudinal axis Z of the receiving space through a circumferential 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 servo motor 76, the required gear means and the lever 78 are already known from other applications, so that here an existing component can be connected to the valve core 56 as a drive unit.
  • the valve element 64 in the direction of the longitudinal axis Z has an axial length such that the recess 79 in the valve element 64, in which the lever 78 engages, is located in the valve core 56 in a portion which is located outside of the receiving space 50 is.
  • This extended design of the valve element 64 thus has the advantage that the drive unit with the servomotor 76 can be arranged laterally of the motor housing 22.
  • the attachment for the drive unit with the positioning motor 46 which is embodied here as a bayonet coupling 81, can thus be formed on the preferably made of plastic valve insert 56.
  • the corresponding receptacle or bayonet coupling 81 is easier to train than at the receiving space 50, whose wall is preferably formed together with the pump housing 24 as a metal casting.
  • the servo motor 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 formed substantially symmetrically with respect to the installation axis Y. This makes it possible to insert the valve insert 56 from the opposite opening 54 into the receiving space 50 and to insert the closure element 80 into the opening 52.
  • the position of the second suction nozzle 58 can be changed very easily and adapted to a respective installation situation in a heating system.
  • the first suction port 44 is connected to the supply line 18 in the heating system according to FIG. 1, while the second intake port 58 is connected to the return line 12.
  • the discharge port 40 is connected to the conduit leading 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 takes over the function of the mixing valve 20 together with the valve seat 68.
  • the mixing valves 20 and 21 are thus combined here to form a three-way valve.
  • the valve seat 70 could alternatively be removed or omitted, so that then only the functionality of the mixing valve 20 would remain as a pure two-way valve.
  • the sealing surface 72 seals against the valve seat 68, so that the flow path through the first suction port 44 and the portion 46 a of the suction channel 46 to the receiving space 50 is closed.
  • the valve surface 74 is maximally spaced from the second valve seat 70, so that a second flow path, starting from the second suction port 58 through the receiving space 50 to the second section 46b of the suction channel 46, is maximally open. This is how the run wheel 38 during rotation, the heating medium through the heating circuit 2 via the return line 12 in a circle.
  • the valve element 64 is moved linearly along the longitudinal axis Z in the direction of a second switching or valve position.
  • valve face 72 out of engagement with the first valve seat 68, so that the first flow path through the first portion of the suction channel 46a is opened and heating medium from the supply line 18 to the second portion 46b of the suction channel 46 and via this to the impeller 38th can flow.
  • this intermediate position of the valve element 64 thus heating medium flows from the first suction port 44 and from the second suction port 58 to the impeller 38, so that the two heating medium streams are mixed.
  • the valve element 64 is in its second end position, which is shown in FIGS. 7 and 9, the second flow path via the return line 12 is completely closed because the valve surface 74 abuts against the valve seat 70. Then heating medium is conveyed only via the flow line 18 in the underfloor 2.
  • intermediate positions of the valve element 64 between the two switching positions different mixtures of heated and cold heating medium can be achieved, wherein the mixing point 14 is located in the region of the branch of the portion 46 b of the first suction channel of the receiving space 50.
  • FIGS. 10 to 13 A second embodiment of the centrifugal pump assembly according to the invention will be described with reference to FIGS. 10 to 13.
  • the pump housing 24 and the drive motor in the motor housing 22 with the electronics housing 26 are identical to the first embodiment in this second embodiment. In this respect, reference is made to the preceding description.
  • the receiving space 50 is configured identically to the first embodiment.
  • the opening 54 at the second axial end of the receiving space 50 is here closed by a closure element 80 '.
  • a Venfileinafz 56 ' is inserted into the first opening 52, wherein the Venfileinsafz 56' opposite the inner periphery of the receiving space 50 adjacent to the opening 52 is sealed.
  • the Venfileinsafz 56 'could also be inserted through the second opening 54 in the receiving space 50, as described with reference to the first embodiment.
  • a second Saugsfutzen 82 arranged on the Venfileinsafz 56 'isf soap in this embodiment.
  • a first valve seat 86 is arranged inside the valve seat 56.
  • the valve seat 86 lies between a region 88, in 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 portion 46b of the suction channel 46 branches off to the impeller 38.
  • a Ventilelemenf 90 come to rest.
  • the valve element 90 is guided linearly movable in the direction of the longitudinal axis Z in the interior of the valve insert 56 '.
  • the closure element 60 On the closure element 60 'is located on a return spring or a biasing spring 92 which presses with its opposite axial end against the Ventilelemenf 90 and the Ventilelemenf 90 toward an open position in which it is lifted from the valve seat 86, biases or loaded with a compressive force.
  • the valve element 90 In the opposite direction, the valve element 90 is acted upon by a thermosensor element or expander element 94.
  • the thermostatic element 94 has in its interior a medium which expands with increasing temperature, so that the length of the thermostatic valve 94 in the direction of the longitudinal axis Z increases.
  • thermosafety member 94 lies in a flow path from the opening 84 to the mouth of the second portion 46b of the first suction channel which leads to the suction mouth 48 of the impeller 38 (see FIG. He embodiment according to FIGS. 2 to 9). That is, the thermostat element 94 responds to the temperature of the heating medium, which is supplied through the return line 12, provided that it 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 the extent that the valve element 90 is pressed against the force of the return spring 92 to the valve seat 86 and so the first flow path starting from the first suction port 44 and the first suction channel 46 is closed.
  • the thermostatic element 94 contracts in the direction of the longitudinal axis Z, so that the return spring 92, the valve element 90 moves so that it is lifted from the valve seat 86 and the flow path through the first portion 46 a 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 mixed. That is, according to the second embodiment, a purely temperature-controlled mixing valve is integrated into the receiving space 50. An adjustment of the temperature is possible via the adjusting screw 96, by the rotation of 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 arranged, which faces the valve 86, but spaced therefrom.
  • a second valve face 97 cooperates with the second valve seat 95.
  • the second valve seat 95 assumes with the second valve face 97 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 face 87 of the valve element 90 takes over the function of the mixing valve 20.
  • D. h. Also in this embodiment, a three-way valve is realized, which combines the functionality of the two mixing valves 20 and 21.
  • a valve insert 56 is inserted into the receiving space 50 through the opening 52 of the receiving space 50.
  • the latter has a section 60 with the opening 62 which extends into the interior of the receiving space 50.
  • an additional bore which forms a pressure channel 96 is introduced into the pump housing 24.
  • the pressure channel 96 establishes a pressure connection between the pressure chamber 42 and the receiving space 50.
  • the valve insert 56 "interrupts the first suction channel 46.
  • the first section 46a opens on a first side of a valve seat 98 in the receiving space 50. On the other side of the valve seat 98 branches off the second portion 46 b of the first suction channel to the impeller 38 back.
  • a valve element 100 is movably guided in the direction of the longitudinal axis Z.
  • the valve element 100 can be connected to the valve seat 98 in FIG Enclosure to close the flow passage through the valve seat 98.
  • a biasing element is provided in the form of a spring 102, which in this example, the valve element 100 in the direction of the longitudinal axis Z applied with a pre-clamping force, which presses the valve element 100 against the valve seat 98.
  • the spring 102 rests with its longitudinal end remote from the valve element 100 against an adjusting screw 104, via which the pretensioning 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 at its longitudinal end a pressure surface, which is located in a pressure region 108 which is connected via the pressure channel 56 with the pressure chamber 42 in the interior of the pump housing 24.
  • An elastic bellows 106 seals the pressure region 108 with respect to the suction channels or the suction-side flow paths.
  • the valve insert 56 has laterally a second suction port 110, similar to the second suction port 82 in the second exemplary embodiment .
  • This second suction port 110 is connected in the heating system to the return line 12.
  • the second suction port 1 10 opens over an opening 1 12 in the interior of the valve core 56 ".
  • the opening 1 12 is communicated inside the valve core 56 "with the second portion 46b of the first suction channel leading to the impeller 38.
  • a flow path from the second suction port 110 to the impeller 38 is provided by increasing the speed of the drive motor the output pressure of the impeller 38 increases which, as described, acts on the piston 105.
  • a pressure force is generated on the piston 105 which is opposite to the spring pressure force of the spring 102.
  • valve element 100 when the pressure continues to rise, the valve element 100 can be displaced further to the right until it abuts against a second valve seat 14. In this second end position, the flow path from the opening 12 to the second section 46b of the first suction channel is closed, so that only one flow connection is released from the first suction port 44 via the first suction channel 46 to the impeller 38.
  • the valve element 100 can also be moved into one or more intermediate positions, whereby the flow paths between the valve seat 1 14 and the valve element 100 and the valve seat 98 and the valve element 100 are opened differently wide.
  • a three-way valve is also realized here, which unites the functionalities of the valves 20 and 21, as described above.
  • the mixing ratio alone can be regulated pressure-dependent, wherein the pressure of the rotational speed of the impeller 38 is dependent.
  • the mixing ratio can be changed by speed variation of the drive motor.
  • a preset temperature that is, a preset of a certain mixing ratio for a certain pressure is possible via the adjusting screw 104, via which the bias of the spring 102 is adjusted.
  • a pressure-dependent actuator is thus provided, which can be very easily in an identical pump housing 24 with the receiving space 50, as found in the first two embodiments use, integrate. It is only necessary to introduce the additional bore for the pressure channel 96 into the pump housing 24.
  • valve insert 56 "could be inserted instead into the opening 52 into the opening 54 of the receiving space 50 in order to displace the second suction port 110 to the other side of the receiving space 96 may be arranged at the opposite longitudinal end of the receiving space 50 or two pressure channels 96 would have to be provided, of which an unused would be closed by the portion 60 of the valve insert 56 ".
  • a fourth embodiment is shown in FIGS. 19 to 23. This embodiment relates to a centrifugal pump unit of greater power, which is dimensioned correspondingly larger.
  • 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 'in the interior of the pump housing 24' in order to drive the impeller 38 'in rotation.
  • the drive motor as a wet-running motor with a split tube 34 'between the rotor 32' and stator 30 'is formed.
  • an electronics housing 26' with control electronics 28 'arranged therein is arranged.
  • the control electronics 28 ' serves to control the drive motor and optionally a drive of a mixing valve, such as it has been described above.
  • the pump housing 24 ' has along a mounting axis Y facing away from each other a first suction port 44' and a discharge nozzle 40 ', which is connected to the pressure chamber 42', which surrounds the impeller 38 'on the output side.
  • first suction channel 46' From the first suction port 44 'extends a first suction channel 46' to the suction port of the impeller 38 ', wherein here the suction channel 46' is cut through a receiving space 50 ', wherein the receiving space 50' the first suction channel 46 'in a first section 46'a and a second portion 46'b share, as is the case with the first three 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 embodiments.
  • a second suction port 1 16 is inserted into the receiving space 50 'through its first opening 52'.
  • This arrangement has the advantage that the second suction nozzle is attached directly to the receiving space 50 ', which is preferably made in one piece with the pump housing 24' in the metal casting.
  • a valve insert 120 is inserted into the receiving space 54 'through the second opening 54'.
  • the valve insert 20 is tubular and communicates with the open end, which is arranged in the receiving space 50 ', with the suction nozzle 1 1 6 in connection.
  • a closure element 122 is used with an electric servomotor 124.
  • the servo motor 124 can be controlled by the control electronics 28 'or a further external mixer control electronics.
  • the servomotor 124 moves via a spindle drive an actuating element in the form of a drive rod 126, 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 of the servo motor 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 core 120 in the direction of the longitudinal axis Z.
  • the valve element 128 is longitudinally movably guided in the interior of the valve core 120.
  • the valve element 128 has a groove 130, in which a projection 132 on the inner circumference of the valve element 120 engages in order to prevent rotation of the valve element 128.
  • valve member 128 which is connected to the drive rod 126 is formed closed, while the opposite end is formed open and engages the interior of the second suction nozzle 1 16, wherein a flow path from the second suction port 1 16 in the Inside the valve element 128 is given in.
  • the valve element 128 In its outer circumferential surface, the valve element 128 has an opening 134.
  • 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 in the interior of the valve core 120, can be made to coincide with an inlet opening 136 in a circumferential wall of the valve core 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 port 136 coincides with the mouth of the portion 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 is brought to overlap with the inlet opening 136 to different degrees, so that the flow path through the interior of the Valve element 128 to the impeller 38 'is opened differently wide.
  • the return line 12 is preferably connected when installed in the heating system according to FIG. To completely close this flow path, the Venfilelemenf 128 with its radially projecting closed axial end axially to a valve seat 1 18 inside the Ventileinsafzes 120 come to rest, so that this suction-seepage flow path is completely closed.
  • the first portion 46'a of the suction channel 46 opens via a further opening into the interior of the Venfil facedes 120 in the region of the outer circumference of the Venfiliatas 128.
  • the wetter the Ventilelemenf 128 is moved in the direction of the closure element 122 and the opening 134 covers the Einfritfsö réelle 136, the more the remaining flow path on the outer circumference of the Venfilides 128 is closed over past the Einfritfsö réelle 136, so that the first suction-side Sfrömungsweg is further closed by the Saugkanalab- section 46 'a.
  • the Saugsfutzen 44 ' is preferably connected to the Vorlaufleifung 18 in the Schuungssysfem shown in Fig. 1.
  • a valve which acts both in the supply run 18 and in the return run 12, that is, the more the flow path is opened from the supply run 18, the more the Sfrömungsweg from the return run 12 is closed.
  • D. h. Again, thus, a three-way Venfil is formed, which combines the functionality of the valves 20 and 21.
  • the tubular or sleeve-shaped Ausffolding of the Venfiliatas 128 has the advantage that a maximum cross-section is realized by both Sfrömungswege, so that the hydraulic resistance is minimized.
  • the separation of the Dichffunkfion on the axial seal on the valve seat 1 18 of the fürflußregelfunkfion mif Vietnamese the opening 134 also has the advantage that the friction in the system is reduced, so that a smaller actuator sufficient to move.
  • the elliptical shape of the Austriftsö Anlagen 136 also has the advantage that with constant linear movement of the Venfilettis 128 towards the end of the free Sfrömungsquerschniff is reduced more, so that overall a favorable control behavior over the entire travel, in particular a linear control behavior can be realized.
  • valve elements are moved linearly.
  • the linear movement has the advantage that a spindle motor can be used to drive.
  • the spindle motor realized in a very simple way a gear which simultaneously converts the rotary motion into a linear movement and slows down the movement for good controllability.
  • the servomotor with the gearbox can be arranged in the dry area. It is only a linear feedthrough or, in the case of the described lever, a sealing sleeve can be provided to introduce the actuator in the wet room.

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

Abstract

L'invention concerne un ensemble pompe centrifuge doté d'un moteur d'entraînement électrique et d'au moins une roue à aubes (38; 38') entraînée en rotation par ledit moteur d'entraînement, laquelle est montée dans un corps de pompe (24, 24') dans lequel est réalisé un premier canal d'aspiration (46; 46') qui constitue une première voie d'écoulement allant d'une première tubulure d'aspiration (44; 44') vers le côté aspiration de la roue à aubes (38; 38'), le corps de pompe (24; 24') présentant un espace de réception (50; 50') coupant le premier canal d'aspiration (46; 46'), ledit espace de réception étant relié à une seconde tubulure d'aspiration (58; 82; 110; 116) et un élément de soupape (64; 90; 100; 128) mobile étant disposé à l'intérieur de l'espace de réception, ledit élément de soupape étant relié à un mécanisme de réglage (76; 94; 105; 124) et étant conçu de sorte que le déplacement de l'élément de soupape (64; 90; 100; 128) permet de moduler un rapport de section entre la première voie d'écoulement qui part de la première tubulure d'aspiration (44; 44') et une seconde voie d'écoulement qui part de la seconde tubulure d'aspiration (58; 82; 110; 116).
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

Publications (2)

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EP3596342A1 true EP3596342A1 (fr) 2020-01-22
EP3596342B1 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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EP17161065.2A Active EP3376052B1 (fr) 2017-03-15 2017-03-15 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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CN116263164B (zh) * 2022-12-19 2025-09-16 利欧集团浙江泵业有限公司 一种带自吸阀的离心泵结构

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.

Also Published As

Publication number Publication date
EP3596342B1 (fr) 2022-01-12
US20210156396A1 (en) 2021-05-27
EP3376052B1 (fr) 2020-11-04
CN110431312B (zh) 2021-09-28
CN110431312A (zh) 2019-11-08
WO2018166639A1 (fr) 2018-09-20
EP3376052A1 (fr) 2018-09-19

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