EP3376040B1 - Groupe motopompe - Google Patents

Groupe motopompe Download PDF

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Publication number
EP3376040B1
EP3376040B1 EP17160832.6A EP17160832A EP3376040B1 EP 3376040 B1 EP3376040 B1 EP 3376040B1 EP 17160832 A EP17160832 A EP 17160832A EP 3376040 B1 EP3376040 B1 EP 3376040B1
Authority
EP
European Patent Office
Prior art keywords
drive motor
pump assembly
valve element
control device
assembly according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17160832.6A
Other languages
German (de)
English (en)
Other versions
EP3376040A1 (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
Priority to EP17160832.6A priority Critical patent/EP3376040B1/fr
Priority to PCT/EP2018/056080 priority patent/WO2018166969A1/fr
Priority to US16/493,211 priority patent/US20200072227A1/en
Priority to CN201880018500.4A priority patent/CN110418895B/zh
Publication of EP3376040A1 publication Critical patent/EP3376040A1/fr
Application granted granted Critical
Publication of EP3376040B1 publication Critical patent/EP3376040B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • 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
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/0209—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the working fluid
    • 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
    • F04D15/0005—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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0207—Pumps

Definitions

  • the invention relates to a pump unit with an electric drive motor, at least one of the electric drive motor rotatably driven impeller and a control device which drives the drive motor.
  • US 2016/0268937 A1 discloses an electrically driven pump assembly in which prior to starting the electric motor determines the rotor position and the rotor is moved in a position that the poles are aligned in a defined manner to the stator.
  • DE 1958 277 discloses a pump unit with an integrated valve element in which the valve element can be rotated via a clutch from the motor shaft driving an impeller. This coupling can be brought into and out of engagement via an adjusting element, wherein at the same time a holding element for fixing the valve element in and can be brought out of engagement.
  • the pump unit according to the invention has an electric drive motor and at least one of this rotationally driven impeller.
  • the impeller may be connected in a known manner with the rotor of the drive motor.
  • the rotor is particularly preferably a permanent magnet rotor.
  • the drive motor as a wet-running electric drive motor with a split tube or split pot, which separates the rotor space from the stator space formed. That is, the rotor preferably rotates in the fluid to be delivered by the pump unit.
  • the pump unit may preferably be designed as a circulating pump unit and more preferably as a heating circulation pump unit.
  • the control device of the drive motor which controls the drive motor and in particular controls the energization of stator coils in the stator of the drive motor, is designed such that it selectively drives the drive motor in at least one first or in a second operating mode.
  • the first mode is a conventional mode in which the drive motor is controlled by the controller such that the rotor of the drive motor rotates continuously over a plurality of revolutions. In this mode, the impeller is driven to produce the pressure and flow desired to operate the pump set.
  • the control device controls the drive motor in such a way that the rotor of the drive motor is advanced only stepwise in at least one selected, in particular adjustable angular step, wherein these angular steps are preferably less than 360 degrees.
  • This rotation in at least one selected angular step serves to rotate the rotor to a desired angular position.
  • control device is designed so that the drive motor rotates in the first mode at a higher angular velocity than in the second mode. This is advantageous for drive and positioning functions in which smaller movements are to be carried out with greater accuracy.
  • the control device is further preferably designed such that in the first operating mode, the drive motor is adjustable in its speed and preferably adjustable.
  • the drive motor in its control device preferably have a frequency converter, via which the speed of the drive motor is variable.
  • the control device is also preferably designed so that the drive motor is controlled in the second mode by the control device in an open loop, that is in the so-called open-loop operation, in which no position control is performed in the energization of the stator coils.
  • the induced reverse voltage (back-EMF) is not used in the control or regulation in open loop operation.
  • This control makes it possible to turn the drive motor at specific angles in a targeted manner by energizing the coils in the stator.
  • the stator can be provided in a known manner with a plurality of stator poles and associated stator coils, which are designed for example for three-phase operation.
  • the control device is designed such that in the second operating mode, the drive motor is controlled by the control device with a frequency ⁇ 10 hertz. That is, the stator coils are supplied with voltage or current with a frequency ⁇ 10 Hertz. Alternatively or additionally, a higher motor current than in the first mode is used. Thus, in the operating mode, a motor current can be used or For example, the stator coils can be supplied with a current which corresponds to two to four times the nominal current for which the drive motor is designed. Optionally, the current may also be higher than four times the nominal current. It is essentially only limited by the fact that no demagnetization of the rotor may occur.
  • control device is designed such that the number and / or the size of the individual angular steps in which the rotor is moved in the second operating mode are selectable. So it is possible to rotate the rotor targeted to a desired angular position.
  • control device selectively energizes the individual stator coils.
  • control device may be configured such that it controls the drive motor so that its direction of rotation in the second mode is opposite to the direction of rotation in the first mode. This makes it easier to use the different operating modes for different applications, because in addition to the impeller, for example, other components could be coupled to the rotor via a direction-dependent coupling, so that in one direction only the rotor is driven, while in the other direction of rotation, which preferably in the second mode is used, even another coupled component could be moved.
  • the pump unit has a further movable component, which is coupled in addition to the at least one rotor via a releasable coupling with the rotor of the drive motor.
  • the coupling can act directly on the rotor, on a rotor shaft connected to the rotor or on the impeller, which is arranged rotationally fixed on the rotor shaft.
  • the at least one further movable component may for example be a valve element, wherein the valve element is preferably part of a mixing and / or switching valve.
  • a switching valve may be, for example, a switching valve, which is used in a heating system to switch the flow path between a heating circuit and a hot water heat exchanger.
  • a mixing valve may for example be a mixing valve, as used in a heating system for the application to regulate the flow temperature of the heating medium by mixing in cooled heating medium.
  • the coupling described for coupling the at least one further movable component is preferably detachable depending on the direction of rotation, so that in one direction of rotation the additional component can be moved in the manner described while in the opposite direction of rotation, which is preferably used in the first mode, the impeller in normal operation can rotate and undisturbed can perform a pumping function.
  • the impeller may have blades, which are adapted to these preferred for normal operation direction of rotation.
  • Said coupling can be further preferably formed at a front end of the rotor shaft of the rotor.
  • the component to be moved then has a corresponding mating coupling, which can engage with this coupling.
  • the additional movable component is preferably also rotatable and more preferably rotatable about the same axis as the rotor shaft.
  • the coupling at the front end of the rotor shaft may in particular have a sawtooth profile, that is to say have a sawtooth profile in a development in the circumferential direction.
  • this profile has two slopes whose axially projecting end edges extend transversely to the axis of rotation of the rotor shaft along a diameter line.
  • engagement surfaces are preferably created starting from these end edges, which are in a plane parallel to the axis of rotation and the diameter of the rotor shaft extend. Facing away from these engagement surfaces, starting from the end edges of the profile, the bevels or wedge surfaces may extend, which in the opposite direction of rotation cause the clutch is pressed out of engagement. This disengagement occurs then by an axial displacement of the counter-coupling and / or the coupling to the rotor shaft.
  • the additionally rotationally moving component is a valve element, which is designed and arranged such that it can be moved in rotation between at least two switching positions.
  • the axis of rotation of the valve element is preferably aligned with the axis of rotation of the drive motor. This allows a simple construction of the coupling described.
  • the valve element is preferably additionally axially displaceable along its axis of rotation, wherein the axial displacement of the valve element, for example, a coupling, as described above, can be disengaged.
  • the valve element is arranged in the pump unit such that it has a pressure surface on which an output side of the at least one impeller prevails pressure. That is, the pressure surface preferably adjoins the pressure space in which the impeller rotates. Furthermore, the valve element is preferably movably mounted in a direction transverse to the pressure surface between an abutment position in which it bears against at least one abutment surface and a released position in which it is detached or spaced from the abutment surface.
  • the movement path, along which the valve element is movable between the adjacent position and the released position preferably differs from the movement path between the at least two switching positions of the valve element.
  • the valve element is axially movable along the axis of rotation about which it is movable between the switching positions.
  • a restoring or biasing element which generates a restoring force, which is directed opposite to the pressure force generated by the pressure on the pressure surface.
  • a return element may for example be a spring.
  • the return element is preferably arranged so that the restoring force generated presses the valve element in the released position.
  • the valve element In the released position, the valve element is preferably substantially freely movable and in particular rotatable, so that it can be easily moved between its switching positions. In the adjacent position, however, the valve element is preferably held non-positively and / or positively on the contact surface, so that it is fixed in its assumed switching position.
  • the at least one contact surface may preferably be a sealing surface at the same time.
  • the valve element is simultaneously sealed in the desired switching position, wherein the sealing surface preferably surrounds an input or switching opening and acts as a valve seat.
  • the pump unit according to the invention makes it possible to drive the drive motor according to a novel method, which is also the subject of the invention.
  • the second operating mode is preferably used to move an additional component, in particular a valve element in a desired position, in particular a desired angular position with respect to a rotational axis.
  • the o-pen-loop operation is used in the control of the drive motor.
  • the coupling is designed so that it engages in at least one angular position, in the embodiment described above in two angular positions offset by 180 °. Since in normal operation in the first mode, the clutch in the manner described above by the pressure prevailing in the pressure chamber disengaged, when changing to the second mode is not sure that the valve element has not shifted slightly. In this respect, it is preferred that at the start of the second mode of operation, the drive motor is not rotated exactly in the angular position in which he was at the last time the end of the second mode of operation, but in an angular position moves, which is set back by a certain amount.
  • this orientation of the rotor initially takes place in an angular position slightly before the angular position in which the rotor was located during the last decommissioning of the second operating mode. This ensures that in the further rotation, the clutch engages in any case and the valve element is moved in the desired manner.
  • the rotor is then rotated by the control device by corresponding energization of the stator coils in the manner described above in exactly the desired new angular position.
  • This is preferably time-controlled in that the stator is supplied with a predetermined frequency for a period of time determined by the control device, the frequency preferably being in the very low range mentioned above.
  • the valve element in the switching position achieved becomes.
  • the valve element can be Position very precisely so that various switching functions, such as switching functions, switching functions of a distributor valve and / or settings of a mixer valve can be made.
  • centrifugal pump assembly according to the invention described in the following description relate to applications in heating and / or air conditioning systems, in which of the centrifugal pump unit, a liquid heat carrier, in particular water, is circulated.
  • the centrifugal pump assembly has a motor housing 2, in which an electric drive motor is arranged.
  • This has in 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 split tube or a split pot 10. That is, it is a wet-running electric drive motor.
  • the motor housing 2 is connected to a pump housing 12, in which a rotatably connected to the rotor shaft 8 impeller 14 rotates.
  • an electronics housing 16 is arranged, which has an electronic control system 17 for controlling the electric drive motor in the pump housing 2 includes.
  • the electronics housing 16 could also be arranged in a corresponding manner on another side of the stator housing 2.
  • a movable valve element 18 is arranged in the pump housing 12.
  • This valve element 18 is rotatably mounted on an axis 20 in the interior of the pump housing 12, 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 rotatably fixed to the bottom of the pump housing 12.
  • the valve element 18 is not only rotatable about the axis 20, but by a certain amount in the longitudinal direction X movable. In one direction, this linear mobility is limited by the pump housing 12, against which the valve element 18 abuts with its outer circumference.
  • the valve element 18 separates in the pump housing 12 a suction chamber 24 from a pressure chamber 26.
  • a suction chamber 24 In the pressure chamber 26 rotates the impeller 14.
  • the pressure chamber 26 is connected to the pressure connection or discharge nozzle 27 of the centrifugal pump assembly, which forms the outlet of the centrifugal pump assembly.
  • a mechanical coupling between the drive motor and the valve element is provided, wherein in these embodiments, the drive motor can be controlled by the control device 17 in two different operating modes or operating modes.
  • a first mode which corresponds to the normal operation of the circulating pump unit
  • the drive motor rotates in a conventional manner with a desired, in particular adjustable by the control device 17, speed.
  • the second operating mode the drive motor is activated in open-loop mode, so that the rotor can be gradually rotated in individual predetermined by the control device 17 angular steps, which are smaller than 360 °, can be rotated.
  • the drive motor in the manner of a stepping motor can be moved in individual steps, which is used in these embodiments, the valve element targeted to move in small angular increments in a defined position, as will be described below.
  • a mixing valve as it can be used for example for temperature adjustment for underfloor heating.
  • the motor housing 2 with the electronics housing 16 corresponds to the embodiment described above.
  • the pump housing 12 has, in addition to the pressure port 27, two suction-side ports 32 and 34 which open at the bottom of the pump housing 12 in inputs 28 and 30, which are located in a plane transverse to the axis of rotation X.
  • the valve element 18 is drum-shaped and consists of a cup-shaped lower part 76, which is closed on its side facing the impeller 14 by a cover 78. In the central region of the lid 78, a suction opening 36 is formed. The suction opening 36 is in engagement with the suction mouth 38 of the impeller 14.
  • the valve element 18 is rotatably mounted on an axle 20, which is arranged in the bottom of the pump housing 12. The axis of rotation of the valve element 18 corresponds to the axis of rotation X of the rotor shaft 8.
  • the valve element 18 is also axially displaceable along the axis X and is by a spring 48 in the in Fig.
  • the valve element 18 As an axial stop acting in the released position, the front end of the rotor shaft 8, which is designed as a coupling 108.
  • the clutch 108 engages with a counter-coupling 110, which is arranged non-rotatably on the valve element 18 in engagement.
  • the coupling 108 has tapered coupling surfaces which essentially describe a sawtooth profile along a circumferential line in such a way that torque transmission from the coupling 108 to the counterpart coupling 110 is possible only in one direction of rotation, namely in the direction of rotation A in FIG Fig.
  • the direction of rotation B is the direction of rotation in which the pump unit is driven in normal operation.
  • the direction of rotation A is used for targeted adjustment of the valve element 18. That is, here is a direction of rotation dependent coupling is formed.
  • the mating coupling 110 disengages from the coupling 108 by the pressure in the pressure chamber 26. If the pressure in the pressure chamber 26 increases, a pressure force acting on the cover 78, which is opposite to the spring force of the spring 48 and exceeds this, so that the valve element 18 is pressed into the applied position, which in Fig. 4 is shown.
  • the lower part 76 is located on the bottom side of the pump housing 12, so that on the one hand the valve element 18 is frictionally held and on the other hand, a tight system is achieved, which seals the pressure and the suction side in the manner described below against each other.
  • the suction port 32 opens at the inlet 28 and the suction port 34 opens at the inlet 30 in the bottom of the pump housing 12 in the interior, that is, the suction chamber 24 into it.
  • the lower part 76 of the valve element 18 has in its bottom an arcuate opening 112, which extends substantially over 90 °.
  • Fig. 6 shows a first switching position in which the opening 112 only the input 30 is covered, so that a flow path is given only from the suction port 34 to the suction port 36 and thus to the suction port 38 of the impeller 14.
  • the second input 28 is sealed by the voltage applied in its peripheral region bottom of the valve element 18.
  • Fig. 8 shows the second switching position in which the opening 112 covers only the input 28 while the input 30 is closed.
  • FIG. 7 now shows an intermediate position in which the opening 112 covers both inputs 28 and 30, the input 30 is only partially released.
  • a mixing ratio between the flows from the inputs 28 and 30 can be changed.
  • about the stepwise adjustment of the rotor shaft 8 and the valve element 18 can be adjusted in small steps to change the mixing ratio.
  • the centrifugal pump assembly with the integrated valve, as described above, characterized by the dashed line 1.
  • the hydraulic circuit has a heat source 114 in the form of, for example, a gas boiler, whose outlet opens into, for example, the suction port 34 of the pump housing 12.
  • a floor heating circuit 116 connects to the pressure connection 27 of the centrifugal pump assembly 1, the return of which is connected both to the inlet of the heat source 114 and to the suction connection 32 of the centrifugal pump unit.
  • a further heating circuit 120 can be supplied with a heat carrier, which has the output-side temperature of the heat source 114.
  • the floor heating circuit 116 can be regulated in its flow temperature in such a way that cold water from the return to the hot water output side the heat source 114 is mixed, and by changing the opening ratios of the inputs 28 and 30 in the manner described above, the mixing ratio by rotation of the valve element 18h can be changed.
  • the second embodiment according to Fig. 10 to 19 shows a centrifugal pump unit, which in addition to the above-described mixer functionality still has a switching functionality for additional supply of a secondary heat exchanger for domestic water heating.
  • valve element 18i in this embodiment, is the same as in the ninth embodiment.
  • valve element 18i in addition to the opening 112 on a passage 122 which extends from an opening 124 in the lid 78i to an opening in the bottom of the lower part 76i and thus connects the two axial ends of the valve element 18i together.
  • the valve element 18i is still an only to the bottom, that is, to the bottom of the lower part 76i and thus open to the suction chamber 24 toward arcuate bridging opening 126 is formed, which is closed to the pressure chamber 26 through the lid 78i.
  • the pump housing 12 has, in addition to the pressure port 27 and the two previously described suction ports 34 and 32, a further port 128.
  • the port 128 opens into an inlet 130 in the bottom of Umisselzpumpenaggregates 12 in addition to the inputs 28 and 30 in the suction chamber 24 into it.
  • the lid 78i of the valve element 18i is shown partially opened to illustrate the position of the underlying openings.
  • Fig. 15 shows a first switching position in which the opening 112 facing the input 30, so that a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is made. In the switching position according to Fig.
  • the opening 112 is located above the inlet 130 so that a flow connection is created from the connection 128 to the suction opening 36 and via this into the suction mouth 38 of the impeller 14.
  • Fig. 17 shows, the opening 112 is located above the input 30, so that in turn a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is given.
  • a partial overlap of the opening 124 and the through hole 122 with the input 28 takes place, so that a connection between the pressure chamber 26 and the suction port 32 is made, which acts as a pressure port.
  • the bypass opening 126 concurrently covers the input 130 and a portion of the input 28, so that also a connection from the terminal 128 via the input 130, the bypass opening 126 and the input 28 to the terminal 32 is provided.
  • Fig. 18 shows a fourth switching position in which the passageway 122 completely covers the input 28, so that the terminal 32 is connected via the passage 122 and the opening 124 with the pressure chamber 26. At the same time, the bridging opening 126 only covers the entrance 130. The opening 112 also covers the entrance 30.
  • the heating system in turn has a primary heat exchanger or a heat source 114, which may be, for example, a gas boiler.
  • a first heating circuit 120 which may be formed for example by conventional radiators or radiators.
  • a flow path branches off to a secondary heat exchanger 56 for heating service water.
  • the heating system further includes a floor heating circuit 116. The returns of the heating circuit 120 and the floor heating circuit 116 open into the suction port 34 on the pump housing 12. The return from the secondary heat exchanger 56 opens into the port 128, which, as will be described below, offers two functionalities.
  • the connection 32 of the pump housing 12 is connected to the flow of the underfloor heating circuit 116.
  • the impeller 14 promotes liquid from the suction port 34 via the pressure port 27 through the heat source 140 and the heating circuit 120 and back to the suction port 34.
  • the valve element 18i in the second switching position which in Fig. 16 is shown, the plant is switched to domestic water operation, in this state, the pump assembly or the impeller 14 promotes liquid from the port 128, which serves as a suction port, through the pressure port 27, via the heat source 114 through the secondary heat exchanger 56 and back to the terminal 128.
  • the valve element 18i in the third switching position which in Fig. 17 is shown, the underfloor heating circuit 116 is additionally supplied.
  • the water flows into the suction mouth 38 of the impeller 14 and is conveyed via the pressure connection 27 via the heat source 114 in the manner described by the first heating circuit 120.
  • the liquid emerges on the output side of the impeller 14 from the pressure chamber 26 into the opening 124 and through the through-passage 122 and thus flows to the connection 32 and via this into the underfloor heating circuit 116.
  • FIG. 17 The switch position shown flows simultaneously via the bridging opening 126 liquid via the terminal 128 and the input 130 into the terminal 32. That is, here water flows through the heat source 114 through the secondary heat exchanger 26 and the terminal 128 to the terminal 32. Since in this heating operation on Secondary heat exchanger 56 is removed substantially no heat, so the port 32 hot water in addition to the cold water, which flows from the pressure chamber 26 via the passage 122 to the port 32, admixed. By varying the degree of opening via the valve position 18i, the amount of hot water mixed in at port 32 can be varied.
  • Fig. 18 shows a switching position in which the admixture is turned off and the terminal 32 is exclusively in communication with the pressure chamber 26 directly.
  • the rotor 6 is preferably initially positioned when the second change of mode is performed again in such a way that the control device 17 rotates the rotor 6 by appropriate control of the stator 4 is not quite up to the stored angular position rotates, but preferably shortly before stops. Ie.
  • the rotor 6 is rotated into a previously stored angular position or into an angular position which is slightly ahead of the last stored angular position in the direction of rotation.
  • the rotor can be rotated together with the valve element 18, 18i in a desired second angular position, wherein the control device 17 controls the stator 6 so that the rotor 6 rotates in this second mode exactly to the desired angle.
  • the counter-coupling 110 is taken over the clutch 108, so that the valve element 18, 18i is then rotated to the desired angular position.
  • the rotor 6 is stopped and the control device 17 switches back to the first mode or the first operating mode and starts the rotor 6 in the opposite direction of rotation, so that the clutch 108 can disengage from the mating coupling 110 and the rest by the axial Displacement of the valve element 18, 18i by the pressure generated in the pressure chamber 26, the clutch 108 and the counter-coupling 110 completely disengage and the valve element 18, 18i is held by engagement with the bottom of the pump housing 12 in the achieved switching position.
  • the coupling 108 has two slopes or wedge surfaces 132, which extend from two end edges 134, which in Substantially in the diametrical direction with respect to the axis of rotation X run.
  • engagement surfaces 136 which essentially run in a plane which is spanned by the rotation axis X and a diameter line to this rotation axis X extend.
  • the counter-coupling 110 has a web-shaped projection 138 extending in the diameter direction with respect to the axis of rotation X, which protrudes in the axial direction and has two substantially mutually parallel side surfaces, which in turn extend in planes which are substantially of the diameter line and the rotation axis X or be clamped to these parallel axes.
  • the side surfaces of the projection 138 engage the engagement surfaces 136 when the clutch is engaged.
  • the projection 138 slides on the wedge surfaces 137 under axial displacement.
  • the pump housing 12 is integrally formed.
  • the pump housing can also be designed in several parts.
  • a separate from the pump housing valve housing may be provided, in which the valve element described is arranged, while in the pump housing, only the impeller is arranged.
  • Such a valve and pump housing can be connected to each other in a suitable manner.

Claims (16)

  1. Groupe motopompe muni d'un moteur d'entraînement électrique, d'au moins une roue mobile (14) entraînée en rotation par le moteur d'entraînement électrique, ainsi que d'un dispositif de commande (17) qui commande le moteur d'entraînement, dans lequel
    le dispositif de commande (17) est conçu de manière à commander le moteur d'entraînement au choix dans au moins un premier ou un second mode de fonctionnement, où, dans le premier mode de fonctionnement, le moteur d'entraînement est commandé par le dispositif de commande (17) de telle manière qu'un rotor (6) du moteur d'entraînement tourne de manière continue afin de générer un flux et une pression au niveau de la roue mobile et, dans le second mode de fonctionnement, le moteur d'entraînement est commandé par le dispositif de commande (17) de telle manière que le rotor (6) du moteur d'entraînement est mû pas-à-pas à raison d'au moins un pas angulaire sélectionné, et de manière préférée inférieur à 360°, afin d'atteindre une position angulaire déterminée, caractérisé en ce que le rotor (6) du moteur d'entraînement, en plus de la roue mobile (14), au moins au nombre de une, est couplé à au moins un autre élément mobile (18, 18i) par l'intermédiaire d'un accouplement désaccouplable (108, 110).
  2. Groupe motopompe selon la revendication 1, caractérisé en ce que le dispositif de commande (17) est conçu de telle manière que, dans le premier mode de fonctionnement, le moteur d'entraînement tourne à une vitesse angulaire qui est plus élevée que dans le second mode de fonctionnement.
  3. Groupe motopompe selon la revendication 1 ou 2, caractérisé en ce que le dispositif de commande (17) est conçu de telle manière que, dans le premier mode de fonctionnement, le régime du moteur d'entraînement peut être ajusté, et de manière préférée peut être réglé.
  4. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande (17) est conçu de telle manière que, dans le second mode de fonctionnement, le moteur d'entraînement est commandé en boucle ouverte par le dispositif de commande (17).
  5. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande (17) est conçu de telle manière que, dans le second mode de fonctionnement, le moteur d'entraînement est amorcé par le dispositif de commande (17) à une fréquence inférieure à 10 Hz et/ou le courant de moteur correspond à deux à quatre fois l'intensité de courant nominale pour laquelle le moteur d'entraînement est conçu.
  6. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande (17) présente un convertisseur de fréquence.
  7. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande (17) est conçu de telle manière que le nombre et/ou la taille des pas angulaires individuels à raison desquels le rotor (6) est mû dans le second mode de fonctionnement peu(ven)t être sélectionné(e)(s).
  8. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande (17) est conçu de manière à commander le moteur d'entraînement de telle manière que son sens de rotation (A) dans le second mode de fonctionnement est opposé au sens de rotation (B) dans le premier mode de fonctionnement.
  9. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que l'accouplement (108, 110) peut être désaccouplé en fonction du sens de rotation de telle manière qu'il se trouve en prise dans un premier sens de rotation (A) et n'est plus en prise dans le second sens de rotation (B) opposé.
  10. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que l'accouplement (108) est réalisé au niveau d'une extrémité avant d'un arbre de rotor (8) du rotor et présente en particulier un profil en dents de scie.
  11. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que l'autre composant mobile, au moins au nombre de un, est un élément de vanne (18; 18i), l'élément de vanne (18; 18i) faisant de manière préférée partie d'une vanne de mélange et/ou de commutation.
  12. Groupe motopompe selon la revendication 11, caractérisé en ce que l'élément de vanne (18; 18i) est conçu et agencé de manière à pouvoir être mû en rotation entre au moins deux positions de commutation, un axe de rotation (X) de l'élément de vanne (18 ; 18i) étant agencé de manière préférée dans l'alignement de l'axe de rotation (X) du moteur d'entraînement.
  13. Groupe motopompe selon la revendication 11 ou 12, caractérisé en ce que l'élément de vanne (18; 18i) est agencé dans le groupe motopompe de manière à présenter une surface de pression (78 ; 78i) sur laquelle s'exerce une pression régnant du côté sortie de la roue mobile (14), au moins au nombre de une, et l'élément de vanne (18 ; 18i) est installé mobile dans une direction perpendiculaire à la surface de pression (78 ; 78i) entre une position d'appui, dans laquelle il appuie contre au moins une surface d'appui, et une position hors de prise, dans laquelle il n'est plus en prise avec la surface d'appui ou se trouve espacé par rapport à la surface d'appui, un élément de rappel (48) qui génère une force de rappel étant de préférence prévu, celui-ci étant orienté à l'opposé d'une force de pression générée par la pression au niveau de la surface de pression (78, 78i).
  14. Groupe motopompe selon la revendication 13, caractérisé en ce que la surface d'appui est une surface d'étanchéité.
  15. Groupe motopompe selon la revendication 13 ou 14, caractérisé en ce qu'un trajet de mouvement (X) entre la position d'appui et la position hors de prise est différent d'un trajet de mouvement entre les positions de commutation, au moins au nombre de deux, de l'élément de vanne (18 ; 18i).
  16. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce qu'elle est conçue sous la forme d'une motopompe de circulation et en particulier sous la forme d'un circulateur de chauffage.
EP17160832.6A 2017-03-14 2017-03-14 Groupe motopompe Active EP3376040B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17160832.6A EP3376040B1 (fr) 2017-03-14 2017-03-14 Groupe motopompe
PCT/EP2018/056080 WO2018166969A1 (fr) 2017-03-14 2018-03-12 Groupe motopompe
US16/493,211 US20200072227A1 (en) 2017-03-14 2018-03-12 Pump assembly
CN201880018500.4A CN110418895B (zh) 2017-03-14 2018-03-12 泵机组

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17160832.6A EP3376040B1 (fr) 2017-03-14 2017-03-14 Groupe motopompe

Publications (2)

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EP3376040A1 EP3376040A1 (fr) 2018-09-19
EP3376040B1 true EP3376040B1 (fr) 2019-10-30

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US (1) US20200072227A1 (fr)
EP (1) EP3376040B1 (fr)
CN (1) CN110418895B (fr)
WO (1) WO2018166969A1 (fr)

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Publication number Priority date Publication date Assignee Title
US11060441B2 (en) 2019-04-05 2021-07-13 Perkins Engines Company Limited Water pump with twin return ports
WO2023161017A1 (fr) * 2022-02-25 2023-08-31 Grundfos Holding A/S Dispositif de pompe doté d'une pompe centrifuge et d'une unité de mélange
US20230400037A1 (en) * 2022-06-08 2023-12-14 Cooper-Standard Automotive Inc Multiport fluid pump with integrated valve

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Publication number Priority date Publication date Assignee Title
DE1958227B2 (de) * 1969-11-20 1978-04-27 Pneu-Powr Press Inc., New York, N.Y. (V.St.A.) Pneumatische Presse
JP5920438B2 (ja) * 2013-11-12 2016-05-18 株式会社デンソー 駆動制御装置、および、燃料ポンプ駆動システム
CN103953542B (zh) * 2014-05-17 2017-08-08 王洪继 一种叶片泵
EP3067564B1 (fr) * 2015-03-09 2019-02-06 Grundfos Holding A/S Groupe motopompe de circulation
CN105464919B (zh) * 2016-01-20 2017-12-26 江苏雷利电机股份有限公司 泵及应用该泵的自动投放系统

Non-Patent Citations (1)

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Publication number Publication date
CN110418895B (zh) 2020-11-20
US20200072227A1 (en) 2020-03-05
CN110418895A (zh) 2019-11-05
EP3376040A1 (fr) 2018-09-19
WO2018166969A1 (fr) 2018-09-20

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