EP3376037B1 - Groupe pompe centrifuge - Google Patents

Groupe pompe centrifuge Download PDF

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Publication number
EP3376037B1
EP3376037B1 EP17160836.7A EP17160836A EP3376037B1 EP 3376037 B1 EP3376037 B1 EP 3376037B1 EP 17160836 A EP17160836 A EP 17160836A EP 3376037 B1 EP3376037 B1 EP 3376037B1
Authority
EP
European Patent Office
Prior art keywords
valve element
movable
construction unit
wall
unit according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17160836.7A
Other languages
German (de)
English (en)
Other versions
EP3376037A1 (fr
Inventor
Thomas Blad
Christian 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 EP17160836.7A priority Critical patent/EP3376037B1/fr
Priority to PCT/EP2018/056187 priority patent/WO2018167031A1/fr
Priority to US16/493,125 priority patent/US11073161B2/en
Priority to CN201880018332.9A priority patent/CN110418893B/zh
Publication of EP3376037A1 publication Critical patent/EP3376037A1/fr
Application granted granted Critical
Publication of EP3376037B1 publication Critical patent/EP3376037B1/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0686—Mechanical details of the pump control unit
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/48—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps
    • F04D29/486—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a hydraulic structural unit with a centrifugal pump unit and at least one valve element which can be moved by a flow of liquid caused by the centrifugal pump unit.
  • Centrifugal pump units which have valve elements which are moved by the flow in the pump unit.
  • Centrifugal pump units are known in which the flow inside the pump housing can be directed in two different directions by reversing the direction of rotation of the drive motor, so that a switching element can be moved between two outputs or two inputs of the centrifugal pump unit in order to selectively flow through one of these promote.
  • Disadvantages of these known centrifugal pump units are relatively complex mechanics or the occurrence of efficiency losses due to the switching elements required in the flow path or the required reversal of the direction of rotation.
  • Such centrifugal pump units are for example from U.S. 5,924,432 , DE 44 18 153 A1 , EP 0 394 140 A1 and EP 1 403 521 A1 known.
  • the object of the invention is to improve a hydraulic unit with a centrifugal pump unit and a valve element that can be moved via the flow generated by the centrifugal pump unit in such a way that reliable actuation of the valve element with a simple construction of the valve element and a high degree of efficiency is possible .
  • the hydraulic assembly according to the invention has a centrifugal pump unit which has an electric drive motor and at least one impeller which is driven in rotation by this.
  • the electric drive motor is preferably a wet-running motor, that is to say a drive motor with a can or can between the stator and the rotor, so that the rotor can rotate in the liquid to be conveyed.
  • the hydraulic assembly according to the invention has at least one valve element which is arranged and configured such that it can be moved by a fluid flow caused by the impeller, in particular between at least two different switching positions.
  • the hydraulic structural unit preferably includes at least those flow channels or flow paths that are required for connecting the centrifugal pump unit to external elements, for example pipelines of a heating circuit. More preferably, the hydraulic unit comprises at least some of the flow paths that are required for the connection between the centrifugal pump unit and the valve element, the valve element particularly preferably forming an integrated unit with the centrifugal pump unit. So z. B. the valve element in the pump housing, in which the impeller rotates, be arranged.
  • the hydraulic unit is designed for use in a heating and / or air conditioning system, that is, the centrifugal pump assembly is preferably designed for use as a circulating pump assembly to use a liquid heat transfer medium such as in particular water to circulate in a circuit of a heating or air conditioning system.
  • the hydraulic unit can be designed as an integrated hydraulic unit for a heating system, in particular a compact heating system.
  • Such integrated units usually include all essential flow paths and hydraulic components of the compact heating system.
  • a secondary heat exchanger for heating domestic water can also be integrated into the hydraulic structural unit.
  • Such a hydraulic assembly then essentially only has the connections for one or more heating circuits, for at least one heat source and, if necessary, an input for cold service water and an output for heated service water.
  • Required valves, sensors and the centrifugal pump assembly are preferably integrated into the hydraulic structural unit, wherein at least some of the required flow paths can furthermore preferably be formed in one-piece cast components, in particular plastic injection molding.
  • At least a section of a wall delimiting a flow path in the hydraulic structural unit is designed to be movable.
  • This is preferably a flow path through which the liquid conveyed by the centrifugal pump assembly flows.
  • the liquid thus flows along the wall and thus also along the at least one movable section.
  • This movable section of the wall is part of the valve element or is coupled or connected to the valve element for its movement.
  • the movable wall can thus transmit force or kinetic energy directly to the valve element for its movement.
  • the movable section is in turn movable by the liquid flow running along the wall.
  • the liquid flow over the movable section of the wall can bring about a movement of the valve element coupled to this section of the wall.
  • the transfer of kinetic energy from the flow to the movable section of the wall takes place according to the invention at least partially by means of frictional forces between the liquid flow and the wall.
  • the entire force or energy transmission takes place by friction of the liquid flow on the movable section of the wall.
  • Such a configuration has the advantage that essentially only a loss of energy is used for the movement of the valve element, which energy would occur in the interior of the flow path anyway due to the friction that occurs.
  • the surface of the movable section of the wall has a surface configuration or roughness which essentially does not deviate from the properties of the surfaces of the remaining wall of the flow path. Additional elements protruding into the flow and causing resistance are preferably not provided.
  • the valve element can be, for example, a switch valve or a mixing valve.
  • the valve element is preferably movable between two switching positions or end positions, it being able to be moved back and forth between these end positions by the flow.
  • the reversal of direction can be achieved, for example, by changing the direction of the flow, for example, by changing the direction of rotation of the impeller.
  • an additional restoring element for example a spring or a weight, could be provided which, when the flow is switched off, ensures that the valve element moves back into a predetermined starting position.
  • the at least one movable section of the wall is preferably arranged in such a way that it can be moved parallel to the liquid flow running along the wall. This means that the flow can flow along this movable section of the wall as it does on adjacent wall parts, without being more strongly decelerated or impaired by the movable section of the wall.
  • the flow takes the movable section of the wall with it, preferably solely through frictional forces in the flow direction, and thus moves the coupled valve element.
  • the at least one movable section of the wall can delimit a flow path extending from the centrifugal pump unit on the pressure side or a flow path extending from the centrifugal pump unit on the suction side.
  • a flow flowing towards the centrifugal pump unit on the suction side or a flow flowing away from the centrifugal pump unit on the pressure side can move the movable section and thus the valve element.
  • two movable sections are provided in two flow paths, which are both part of the valve element or are coupled to the valve element to drive it.
  • the movable section of the wall is preferably designed and arranged in such a way that it can be moved together with the at least one valve element due to energy loss caused by the frictional forces on the wall of the flow path. There are essentially no losses in efficiency due to the valve element and its actuating elements, which move the valve element via the flow.
  • the at least one section of the wall is rotatably mounted in a pump housing and preferably rotatably mounted together with the at least one valve element in the pump housing.
  • the impeller rotates in the pump housing.
  • the impeller generates a rotating flow in the circumferential area. If the section of the wall and preferably also the valve element are rotatable, this rotating flow can very easily be converted into a movement of the valve element, since the rotating flow can move the rotatably movable section of the wall in the direction of flow by frictional forces.
  • the axis of rotation of the at least one movable section of the wall is particularly preferably aligned with the axis of rotation of the drive motor and the at least one impeller. More preferably, the axis of rotation of a rotatable valve element is also aligned with the axis of rotation of the drive motor and the impeller.
  • the at least one movable section of the wall is expediently designed in such a way that the frictional forces acting on it through the liquid flow are greater than those frictional forces that occur in a bearing or the bearings of the movable section of the wall and the at least one valve element.
  • This can be achieved, for example, by a correspondingly large surface area of the movable section of the wall will.
  • the surface of the movable wall could also be structured in order to cause greater friction. It is essential that the design is such that the forces transmitted by the flow to the movable wall section are greater than the holding or frictional forces which act on the movable section of the wall and the at least one valve element. A movement of the valve element can thus be caused by the flow.
  • the movable section of the wall particularly preferably has a disk-shaped and, in particular, circular outer contour, the outer diameter of the disk preferably being at least as large as the diameter of the impeller in the pump housing.
  • a movable separating element which separates a suction chamber inside a pump housing of the centrifugal pump unit from a pressure chamber surrounding the impeller, a surface facing the pressure chamber and / or a surface of the separating element facing the suction chamber forming or having the at least one movable section of the wall .
  • the separating element can preferably be rotatable about an axis of rotation which is aligned with the axis of rotation of the impeller. More preferably, the separating element is formed directly from the valve element, that is, the separating element is part of the valve element. A direct drive of the valve element on a surface of the valve element which forms the movable section of the wall in the flow path can thus be caused.
  • the separating element surrounds a suction mouth of the impeller in the shape of a ring, wherein the separating element can have a central opening which is aligned with the suction mouth, in particular is in sealing engagement therewith.
  • the separating element thus forms a conventional deflector plate between the suction chamber and pressure chamber of the pump unit and is simultaneously movable in order to be able to drive the valve element when the separating element is moved by the flow acting on it or the flow flowing along it.
  • the valve element is preferably rotatably mounted on a central bearing, the axis of rotation of the valve element, as described, preferably extending in alignment with the axis of rotation of the drive motor.
  • the central bearing has the advantage that the bearing diameter can be made very small, so that the friction losses on the bearing surfaces can be minimized. If the movable section of the wall is part of the valve element, it can also be located radially outside the bearing, preferably at a radial distance from the bearing, so that a greater torque for moving the valve element is caused by the flow acting on the movable section.
  • the valve element can be moved between at least two switching positions, it being possible for these switching positions to be limited or defined by stops, for example. However, it is also conceivable that the valve element can assume more than two switching positions.
  • the valve element can act as a switchover valve between two flow paths, a first flow path then being opened and a second flow path being closed in a first switching position. Conversely, in a second switching position, the first flow path is closed and the second flow path is open.
  • the valve element can alternatively or additionally act as a mixing valve.
  • the valve element can preferably interact with at least two valve openings of two flow channels in such a way that the valve openings of the flow channels are opened differently depending on the switching position of the valve element. In the case of a switching valve, this means that the valve openings are either completely closed or completely open. When designed as a mixing valve, intermediate positions are also possible in which the valve openings are only partially open. When using the mixing valve, the valve element is preferably designed in such a way that, when it moves, it further closes one of the valve openings and at the same time further opens the other valve opening. This is preferably done to the same extent. It can be achieved in a particularly simple manner in that a one-piece valve element is provided which can cover both valve openings. According to the invention, however, a valve element is also to be understood as an arrangement of two valve elements which are coupled to one another in a suitable manner for common movement.
  • the at least two valve openings each span a surface which extends parallel to a direction of movement of the valve element between the at least two switching positions. That is to say, the valve element for opening and closing the valve openings is preferably moved parallel to these or the surfaces spanned by the valve openings and is not moved closer to and away from the valve openings for opening and closing.
  • This enables a very simple structural design of two valve openings to be opened and closed alternately by a valve element.
  • preferably acts on the The pressure prevailing in the valve openings is not in the direction of movement of the valve element.
  • the valve element is designed and arranged in such a way that it can be moved between at least two switching positions by the flow of liquid along a first movement path or a first movement path and, additionally, along a second movement path or along a second movement path as a result of a pressure generated by the impeller Force can be applied or moved, wherein the second movement path is angled to the first movement path.
  • This enables the change between the switching positions to be carried out with very little friction, since in this state the valve element preferably does not rest against the necessary valve seats and / or contact surfaces or against these with relatively little friction.
  • the pressure can apply force to the valve element in such a way that it comes into contact with the valve seats or is pressed against the valve seats and / or contact surfaces with greater force in a sealing manner. In this state, greater friction or holding force then occurs between the valve element and the valve seats or further contact surfaces, which can simultaneously serve to hold the valve element in the switching position that has been reached.
  • the valve element is preferably movable along the second movement path between a first released position in which the valve element can be moved between the at least two switching positions and an adjacent position in which it is in contact with at least one contact surface.
  • a first released position in which the valve element can be moved between the at least two switching positions
  • an adjacent position in which it is in contact with at least one contact surface.
  • the valve element in the first position the valve element can optionally also rest against the contact surface, but in such a way that it can slide along the contact surface with relatively little friction.
  • the valve element In the second position, however, the valve element is pressed against the contact surface in such a way that a stronger one Friction occurs between the valve element and the system, which generates a holding force which prevents further movement of the valve element over the liquid flow, as described above.
  • Such a configuration makes it possible to move the valve element by appropriate drive of the drive motor and formation of a liquid flow, as long as such a liquid pressure is not reached that presses the valve element into contact with the contact surface.
  • a pressure can be achieved by increasing the speed and, in particular, by increasing the speed of the drive motor very quickly, so that the valve element can then be specifically held in a switching position that has been reached.
  • the pressure at which the valve element comes to rest on the contact surface is preferably selected such that it is lower than the lowest operating pressure during normal operation of the centrifugal pump assembly.
  • the pressure can be adjusted by a return element such as a return spring, which is arranged to move the valve element into the released first position at a lower pressure.
  • valve element and the contact surface are preferably designed in such a way that they come into force and / or form-fitting engagement with one another in the adjacent position, whereby a greater force can preferably be transmitted via this engagement than between the liquid flow and the at least one movable section of the wall. This ensures that the valve element, when it is in contact with the contact surface, is held in the switching position that has been reached and cannot be moved further by the flow of liquid. The liquid flow can then continue to flow along the movable section of the wall, this no longer being moved along with it.
  • the exemplary embodiments of the centrifugal pump unit according to the invention described in the following description relate to applications in heating and / or air conditioning systems in which the centrifugal pump unit circulates a liquid heat transfer medium, in particular water.
  • the centrifugal pump unit has a motor housing 2 in which an electric drive motor is arranged.
  • This has, in a known manner, a stator 4 and a rotor 6, which is arranged on a rotor shaft 8.
  • the rotor 6 rotates in a rotor space which is separated from the stator space in which the stator 4 is arranged by a can or can 10. This means that it is a wet-running electric drive motor.
  • the motor housing 2 is connected to a pump housing 12, in which an impeller 14 that is non-rotatably connected to the rotor shaft 8 rotates.
  • an electronics housing 16 is arranged, which contains control electronics or a control device for controlling the electric drive motor in the pump housing 2.
  • the electronics housing 16 could also be arranged on another side of the stator housing 2 in a corresponding manner.
  • a movable valve element 18 is arranged in the pump housing 12.
  • This valve element 18 is rotatably mounted on an axis 20 inside the pump housing 12, specifically in such a way that the axis of rotation of the valve element 18 is aligned with the axis of rotation X of the impeller 14.
  • the axis 20 is fixed in a rotationally fixed manner on the bottom of the pump housing 12.
  • the valve element 18 is not only rotatable about the axis 20, but also movable to a certain extent in the longitudinal direction X. In In one direction, this linear mobility is limited by the pump housing 12 on which the valve element 18 strikes with its outer circumference. In the opposite direction, the mobility is limited by the nut 22 with which the valve element 18 is attached to the axis 20. It is to be understood that instead of the nut 22, another axial fastening of the valve element 18 on the axis 20 could also be selected.
  • the valve element 18 forms a separating element which separates a suction chamber 24 from a pressure chamber 26 in the pump housing 12.
  • the impeller 14 rotates in the pressure chamber 26.
  • the pressure chamber 26 is connected to the pressure connection or pressure connection 28 of the centrifugal pump assembly, which forms the outlet of the centrifugal pump assembly.
  • Two intake-side inlets 28 and 30 open into the suction chamber 24, of which the inlet 28 is connected to a first suction connection 32 and the inlet 30 is connected to a second suction connection 34 of the pump housing 12.
  • the valve element 18 is disc-shaped and at the same time assumes the function of a conventional deflector plate which separates the suction chamber 24 from the pressure chamber 26. That is, it serves to guide the flow in the area of the pressure chamber and forms part of the wall of the pressure chamber 26.
  • the valve element 18 has a central suction opening 36 which has a protruding circumferential collar which engages with the suction mouth 38 of the impeller 14 and is essentially in tight contact with the suction mouth 38. Facing the impeller 14, the valve element 18 is essentially smooth.
  • the valve element On the side facing away from the impeller 14, the valve element has two ring-shaped sealing surfaces 40 which, in this exemplary embodiment, are located on closed tubular connections.
  • the two annular sealing surfaces 40 are at two diametrically opposite positions on the sealing element 18 with respect to it Axis of rotation X arranged so that they can come into tight contact with the bottom of the pump housing 12 in the circumferential area of the inlets 28 and 30 in order to close the inlets 28 and 30.
  • support elements 42 are arranged, which can also come to rest on the circumferential area of the inlets 28, 30, but are spaced from one another so that they then do not close the inlets 28, 30.
  • the inputs 28 and 30 do not lie on a diameter line with respect to the axis of rotation X, but on a radially offset straight line, so that when the valve element 18 is rotated about the axis of rotation X in a first switching position, the input 38 is closed by a sealing surface 40, while the support elements 42 lie at the input 30 and open it.
  • a second switching position the inlet 30 is closed by a sealing surface 40, while the support elements 42 rest in the circumferential area of the inlet 28 and open it.
  • the first switching position, in which the input 38 is closed and the input 30 is open is in FIG Fig. 5 shown.
  • the second switching position, in which the input 30 is closed and the input 28 is open is in FIG Fig. 6 shown. This means that by rotating the valve element by 90 ° around the axis of rotation X, it is possible to switch between the two switching positions.
  • the two switch positions are limited by a stop element 44 which alternately strikes two stops 46 in the pump housing 12.
  • a spring 48 pushes the valve element 18 into a released position in which the outer circumference of the valve element 18 is not close to the pump housing 12 and the sealing surfaces 40 are not close to the circumference of the inlets 28 and 30 rest so that the valve element 18 can rotate about the axis 20.
  • the drive motor is now set in rotation by the control device 17 in the electronics housing 16, so that the impeller 14 rotates, the pressure chamber 26 generates a circulating flow which, via friction on the end face of the valve element 18, rotates the valve element along in the direction of rotation of the flow.
  • the valve element 18 thus forms a movable section of the wall of the pressure chamber 26, which is moved along by the flow.
  • the control device 17 is designed so that it can optionally drive the drive motor in two directions of rotation.
  • the valve element 18 can also be moved in two directions of rotation about the axis of rotation X depending on the direction of rotation of the impeller 14 via the flow set in rotation by the impeller 14, since the flow in the circumferential area of the impeller 14 always runs in its direction of rotation.
  • the valve element 18 can thus be rotated between the two switching positions limited by the stops 46.
  • the support elements 42 come to rest on the other inlet, so that this inlet remains open and a flow path is provided from this inlet 28, 30 to the suction opening 36 and from there into the interior of the impeller 14.
  • a frictional contact between the valve element 18 and the pump housing 12 is created at the same time. This frictional contact ensures that the valve element 18 is held in the switch position that has been reached. This enables the drive motor to be taken out of operation again for a short time and put into operation again in the opposite direction of rotation without the valve element 18 being rotated.
  • the centrifugal pump unit described according to the first embodiment of the invention can be used, for example, in a heating system as shown in FIG Fig. 7 is shown.
  • a heating system is usually used in apartments or houses and is used to heat the building and to provide heated service water.
  • the heating system has a heat source 52, for example in the form of a gas boiler.
  • a heating circuit 54 which, for example, leads through various radiators in a building.
  • a secondary heat exchanger 56 is provided, via which domestic water can be heated.
  • a changeover valve is usually required, which directs the heat transfer medium flow either through the heating circuit 54 or the secondary heat exchanger 56.
  • this valve function is taken over by the valve element 18, which is integrated into the centrifugal pump unit 1.
  • the control takes place by the control device 17 in the electronics housing 16.
  • the heat source 52 is connected to the pressure connection 27 of the pump housing 12.
  • a flow path 58 is connected to the suction connection 32, while a flow path 60 through the suction connection 34 is connected Heating circuit 54 is connected.
  • Heating circuit 54 is connected.
  • the second embodiment according to Figs. 8-10 differs from the first embodiment in the structure of the valve element 18 '.
  • the valve element 18 'as a separating element separates the pressure chamber 26 from a suction chamber 24 of the pump housing 12 and forms a movable section of the flow-guiding wall of the pressure chamber 26.
  • the valve element 18 has a central suction opening 36' into which the suction mouth 38 of the Impeller 14 engages sealingly.
  • the valve element 18 ' Opposite the suction opening 36, the valve element 18 'has an opening 62 which, depending on the switching position of the valve element 18', can optionally be made to coincide with one of the inlets 28, 30.
  • the inlets 28 ', 30' in this exemplary embodiment differ in their shape from the inlets 28, 30 according to the previous embodiment.
  • the valve element 18 ′ has a central projection 64 which engages in a central hole 60 in the bottom of the pump housing 12 and is mounted there to rotate about the axis of rotation X.
  • the projection 64 in the hole 66 also allows an axial movement along the axis of rotation X, which is limited in one direction by the bottom of the pump housing 12 and in the other direction by the impeller 14.
  • the valve element 18 ′ On its outer circumference, has a pin 68 which engages in a semicircular groove 70 on the bottom of the pump housing 12.
  • the ends of the groove 70 serve as stop surfaces for the pin 68 in the two possible switching positions of the valve element 18 ', wherein in a first switching position the opening 62 is above the input 28' and in a second switching position the opening 62 is above the input 30 'and the other entrance is closed by the bottom of the valve element 18 '.
  • the rotary movement of the valve element 18 ′ between the two switching positions also takes place in this exemplary embodiment by the flow caused in the pressure chamber 26 by the impeller 14. In order to transfer this even better to the valve element 18 ′, it is provided with projections 72 directed in the pressure chamber 26.
  • valve element 18 ' is in the Fig. 9 Depressed position shown, in which the valve element 18 'comes to rest on the bottom of the pump housing 12 in the circumferential area of the inlets 28' and 30 'and at the same time the pin 24 is lifted from the end face of the rotor shaft 8. In this position, the impeller 14 then rotates during normal operation of the circulating pump assembly.
  • the third embodiment according to Figures 11 to 13 shows a further possible embodiment of the valve element 18 ".
  • This embodiment differs from the previous embodiments in the structure of the valve element 18".
  • This is designed as a valve drum.
  • the pump housing 12 essentially corresponds to the structure shown in FIG Figs. 1 to 6 , wherein in particular the arrangement of the inputs 28 and 30 corresponds to the arrangement described with reference to the first exemplary embodiment.
  • the valve drum of the valve element 18 ′′ consists of a pot-shaped lower part which is closed by a cover 78.
  • the cover 78 faces the pressure chamber 26 and has the central suction opening 36, which engages the suction mouth 38 of the impeller 14 with its axially directed collar
  • the cover 78 thus forms a movable section the flow-guiding walls of the pressure chamber 26.
  • the bottom of the lower part 36 has an inlet opening 80 which, depending on the switching position, is brought into congruence with one of the inlets 28, 30, while the other inlet 28, 30 passes through the bottom of the Lower part 26 is closed.
  • the valve element 18 ′′ is rotatably mounted on an axis 20 which is fastened in the bottom of the pump housing 12, the axis of rotation defined by the axis 20 corresponding to the axis of rotation X of the impeller 14.
  • the valve element 18 ′′ can be axially displaced by a certain amount along the axis 20, a spring 48 being provided here as well, which in the rest position moves the valve element 18 ′′ into its in Fig. 13 shown released position presses.
  • This axial position is also limited by the nut 22 in this exemplary embodiment.
  • the valve element 18 ′′ as described above, can be rotated by the flow caused by the impeller 14, that is, a hydraulic coupling is established between the impeller 14 and the valve element 18 ′′.
  • the adjacent position which is in Fig. 12 is shown, one of the inputs 28, 30 is tightly closed depending on the switching position.
  • the mounting of the valve element 18 ′′ on the axle 20 is furthermore encapsulated by two sleeves 82 and 84, so that these areas are protected from contamination by the conveyed fluid and, if necessary, can be lubricated beforehand.
  • the aim is to ensure that the mounting is as smooth as possible in order to ensure the easy rotatability of the valve element 18 ′′ by the flow caused by the impeller 14. It is to be understood that the mounting could also be encapsulated accordingly in the other exemplary embodiments described here.
  • Fig. 14 and 15th show a fourth exemplary embodiment in which the structure of the pump housing 12 corresponds to the structure of the pump housing 12 according to the first and third exemplary embodiments.
  • the rotary movement of the valve element 18c is supported by the flow on the suction side, that is, the flow entering the suction mouth 38 of the impeller 14.
  • the valve element 18c is essentially drum-shaped and has a cover 28 facing the pressure chamber 26 with the central suction opening 36 which engages with the suction mouth 38, as described above.
  • the lower part 76b shown here has two inlet openings 80 which, depending on the switching position, can be brought to overlap with one of the inputs 28, 30, the respective other input 28, 30 being tightly closed by the bottom of the lower part 46b, as in the previous one Embodiment has been described.
  • a stator 86 with blades into which the flow enters radially from the inlet openings 80 and exits axially to the central suction opening 36.
  • the stator 86 is a flow-guiding component which, with its walls, serves to guide the flow and can be moved along with the flow as a movable part of the flow-guiding walls.
  • the blades of the stator 86 also generate a torque about the axis 20, by means of which the valve element 18c can be moved between the switching positions. This works essentially as described above.
  • a spring 48 as described above, can also additionally be provided in order to move the valve element 18c into a released position. Since the shape of the blades of the stator 86 always generates a torque in the same direction, regardless of the direction in which the impeller 14 rotates, in this exemplary embodiment the return movement is effected by a weight 88.
  • the centrifugal pump assembly is in operation always in the installation position, which in Fig. 15 is shown in which the axis of rotation X extends horizontally.
  • valve element 18c When the centrifugal pump unit is switched off, the valve element 18c always rotates about the axis 20 so that the weight 88 is below. Due to the torque generated by the stator 86, the valve element 18c can be rotated against this restoring force generated by the weight 88, whereby by very quickly starting up the drive motor in the pressure chamber 26, a pressure can be built up so quickly that the valve element 18c is in its adjacent position occurs, as described above, in which it is held non-rotatably on the pump housing 12 without being moved out of its rest position. It is to be understood that resetting of the valve element by gravity or another resetting force could also be used in the other exemplary embodiments described here, independently of the drive.
  • the fifth embodiment according to Figures 16-18 again differs from the preceding exemplary embodiments in the construction of the valve element.
  • the valve element 18d is conical.
  • the valve element 18d has a conical, pot-shaped lower part 76d which is closed by a cover 78d, with a central suction opening 36 being formed in the cover 78d which engages with the suction mouth 38 of the impeller 14 in the manner described above.
  • the cover 78d adjoins the pressure chamber 26 and there forms a movable section of the flow-guiding wall.
  • inlet openings 90 are formed, which, by rotating the valve element 18d with inlets which are connected to the suction connections 32 and 34, can optionally be brought to overlap in order to create a flow path through the interior of the valve element 18d to the suction opening 36 to manufacture. Between the inlet openings 90 are on the conical lower part sealing surfaces 92 formed which can close the other input.
  • the valve element 18d has a pin-shaped projection 64 which engages in a recess on the bottom of the pump housing 12 and there the valve element 18d rotates about the axis of rotation X.
  • there is an axial movement between a released position as shown in Fig.
  • valve element 18d on the other hand it is held non-positively so that, as long as the pressure in the pressure chamber 26 is sufficiently high, it is not moved between the switching positions even when the direction of rotation of the impeller 14 changes.
  • the pump housing 12 serves as a combined valve and pump housing which is in one piece is trained. It is to be understood, however, that the pump housing 12 could be designed in a corresponding manner in several parts.

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

Claims (16)

  1. Ensemble hydraulique muni d'un groupe de pompage centrifuge, qui présente un moteur d'entraînement électrique (4, 6) et au moins une roue (14) entraînée par celui-ci, ainsi qu'au moins un élément formant clapet (18) agencé de telle manière qu'il puisse être mis en mouvement grâce à l'une des circulations de liquide provoquées par la roue (14),
    au moins une section (18; 78) d'une paroi délimitant une voie de circulation dans l'ensemble hydraulique étant conçue de manière à être mobile,
    ladite section mobile (18; 78; 86) de la paroi faisant partie de l'élément formant clapet (18) ou étant reliée à l'élément formant clapet (18) en vue de sa mise en mouvement, et
    ladite section mobile (18; 78; 86) étant mobile de manière au moins partiellement provoquée par des forces de frottement de la circulation de liquide longeant la paroi, caractérisé par un élément de séparation mobile (18; 78) qui sépare un espace d'aspiration (24), présent à l'intérieur d'un carter de pompe (12) du groupe de pompage centrifuge, par rapport à une chambre de pression (26) entourant la roue (14), une surface, faisant face à la chambre de pression (26), de l'élément de séparation (18 ; 78) et/ou une surface, faisant face à la chambre d'aspiration (24), de l'élément de séparation (18; 78) formant ladite au moins une section mobile de la paroi.
  2. Ensemble hydraulique selon la revendication 1, caractérisé en ce que ladite au moins une section mobile (18; 78; 86) de la paroi est agencée de telle manière qu'elle soit mobile parallèlement à la circulation de liquide longeant la paroi.
  3. Ensemble hydraulique selon la revendication 1 ou 2, caractérisé en ce que ladite au moins une section mobile (18; 78) de la paroi délimite une voie de circulation (26) s'étendant côté refoulement à partir du groupe de pompage centrifuge.
  4. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que ladite au moins une section mobile de la paroi délimite une voie de circulation (86) s'étendant côté aspiration à partir du groupe de pompage centrifuge (1).
  5. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que la section mobile (18; 78; 86) de la paroi est conçue et agencée de telle manière qu'elle soit mobile en commun avec ledit au moins un élément formant clapet (18) grâce à une dissipation d'énergie provoquée par les forces de frottement s'exerçant sur la paroi de la voie de circulation.
  6. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que ladite au moins une section (18; 78 ; 86) de la paroi est montée rotative au sein d'un carter de pompe (12) et est de manière préférée montée rotative en commun avec ledit au moins un élément formant clapet (18) au sein du carter de pompe (12).
  7. Ensemble hydraulique selon la revendication 6, caractérisé en ce que ladite au moins une section mobile (18; 78; 86) est conçue de telle manière que les forces de frottement agissant sur elle du fait de la circulation de liquide soient supérieures aux forces de frottement apparaissant au sein d'un montage de la section mobile (18 ; 78 ; 86) et dudit au moins un élément formant clapet (18).
  8. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément de séparation (18; 78) entoure de manière annulaire une ouïe d'aspiration (38) de la roue (14).
  9. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément de séparation (18; 78) est formé par l'élément formant clapet (18).
  10. Ensemble hydraulique selon la revendication 9, caractérisé en ce que l'élément formant clapet (18) est monté rotatif sur un palier central (20), l'axe de rotation (X) de l'élément formant clapet (18) s'étendant, de manière préférée, de manière alignée par rapport à l'axe de rotation (X) du moteur d'entraînement (4, 6).
  11. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément formant clapet (18) est mobile entre au moins deux positions de commutation.
  12. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément formant clapet (18) coopère avec au moins deux ouvertures de clapet (28, 30) de deux canaux de circulation de telle manière que les ouvertures de clapet (28, 30) des canaux de circulation soient ouverts différemment en fonction de la position de commutation de l'élément formant clapet (18).
  13. Ensemble hydraulique selon la revendication 12, caractérisé en ce que lesdites au moins deux ouvertures de clapet (28, 30) enjambent respectivement une surface qui s'étend entre lesdites au moins deux positions de commutation parallèlement à une direction de déplacement de l'élément formant clapet (18).
  14. Ensemble hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément formant clapet (18) est conçu et agencé de telle manière qu'il soit mobile le long d'un premier chemin de déplacement entre au moins deux positions de commutation grâce à la circulation de liquide et puisse en outre être soumis à une force ou être mobile le long d'un second chemin de déplacement grâce à une pression générée par la roue (14), le second chemin de déplacement étant incliné par rapport au premier chemin de déplacement.
  15. Ensemble hydraulique selon la revendication 14, caractérisé en ce que l'élément formant clapet (18) est mobile le long du second chemin de déplacement entre une première position hors d'appui dans laquelle l'élément formant clapet (18) est mobile entre lesdites au moins deux positions de commutation et une position en appui dans laquelle il repose contre au moins une surface d'appui.
  16. Ensemble hydraulique selon la revendication 15, caractérisé en ce que l'élément formant clapet (18) et la surface d'appui sont conçus de telle manière que, dans la position en appui, ils viennent en prise l'un avec l'autre par complémentarité de force et/ou de forme, une force supérieure à celle existant entre la circulation de liquide et ladite au moins une section mobile (18 ; 78 ; 86) de la paroi pouvant, de manière préférée, être transmise par l'intermédiaire de ladite mise en prise.
EP17160836.7A 2017-03-14 2017-03-14 Groupe pompe centrifuge Active EP3376037B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17160836.7A EP3376037B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge
PCT/EP2018/056187 WO2018167031A1 (fr) 2017-03-14 2018-03-13 Ensemble pompe centrifuge
US16/493,125 US11073161B2 (en) 2017-03-14 2018-03-13 Centrifugal pump assembly
CN201880018332.9A CN110418893B (zh) 2017-03-14 2018-03-13 离心泵机组

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17160836.7A EP3376037B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge

Publications (2)

Publication Number Publication Date
EP3376037A1 EP3376037A1 (fr) 2018-09-19
EP3376037B1 true EP3376037B1 (fr) 2021-01-27

Family

ID=58347146

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17160836.7A Active EP3376037B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge

Country Status (4)

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US (1) US11073161B2 (fr)
EP (1) EP3376037B1 (fr)
CN (1) CN110418893B (fr)
WO (1) WO2018167031A1 (fr)

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WO2023165900A1 (fr) 2022-03-01 2023-09-07 Grundfos Holding A/S Procédé de commande de système hydronique
WO2024061892A1 (fr) 2022-09-21 2024-03-28 Grundfos Holding A/S Procédé de commande pour un système hydronique

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EP3376051B1 (fr) * 2017-03-14 2022-08-24 Grundfos Holding A/S Groupe motopompe
EP3904689A1 (fr) * 2020-04-28 2021-11-03 Grundfos Holding A/S Ensemble pompe centrifuge

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US5261786A (en) * 1991-03-05 1993-11-16 A. R. Wilfley & Sons, Inc. Actuator mechanism for pump sealing apparatus
DE4418153A1 (de) * 1994-05-25 1995-11-30 Wilo Gmbh Kreiselpumpe
US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system
JP4313557B2 (ja) * 2002-09-26 2009-08-12 日本電産シバウラ株式会社 ポンプ
DE102011086934A1 (de) * 2011-11-23 2013-05-23 Schaeffler Technologies AG & Co. KG Regelbare Kühlmittelpumpe mit einer elektro-hydraulischen Leitblechverstellung
EP2818726B1 (fr) * 2013-06-27 2017-08-23 Grundfos Holding A/S Pompe centrifuge avec roue à aubes déplaçable axialement pour l'alimentation de circuits différents
EP3150923B2 (fr) * 2015-10-02 2022-06-08 Grundfos Holding A/S Systeme hydraulique
EP3156659B1 (fr) * 2015-10-12 2020-09-16 Grundfos Holding A/S Pompe et système hydraulique

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023165900A1 (fr) 2022-03-01 2023-09-07 Grundfos Holding A/S Procédé de commande de système hydronique
WO2024061892A1 (fr) 2022-09-21 2024-03-28 Grundfos Holding A/S Procédé de commande pour un système hydronique

Also Published As

Publication number Publication date
US20200116161A1 (en) 2020-04-16
EP3376037A1 (fr) 2018-09-19
WO2018167031A1 (fr) 2018-09-20
CN110418893A (zh) 2019-11-05
US11073161B2 (en) 2021-07-27
CN110418893B (zh) 2021-10-22

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