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WO2018167047A1 - Ensemble pompe centrifuge - Google Patents

Ensemble pompe centrifuge Download PDF

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Publication number
WO2018167047A1
WO2018167047A1 PCT/EP2018/056213 EP2018056213W WO2018167047A1 WO 2018167047 A1 WO2018167047 A1 WO 2018167047A1 EP 2018056213 W EP2018056213 W EP 2018056213W WO 2018167047 A1 WO2018167047 A1 WO 2018167047A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve element
centrifugal pump
drive motor
valve
pump assembly
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.)
Ceased
Application number
PCT/EP2018/056213
Other languages
German (de)
English (en)
Inventor
Thomas Blad
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Grundfos Holdings AS filed Critical Grundfos Holdings AS
Publication of WO2018167047A1 publication Critical patent/WO2018167047A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D13/021—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
    • F04D13/028—Units comprising pumps and their driving means the driving means being a planetary gear
    • 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 centrifugal pump assembly having a drive motor, at least one impeller driven thereby and a valve device having a valve element movable by the drive motor.
  • a centrifugal pump unit is known in the pump housing, a valve element is integrated to switch the conveying path of the centrifugal pump assembly between two possible flow paths.
  • the valve element is rotatable via the drive motor by means of a releasable coupling.
  • an additional locking device is required in order to position the valve element accurately. More precise control tasks are difficult to implement with such a valve element.
  • the centrifugal pump assembly has a drive motor, in particular an electric drive motor, which rotatably drives at least one impeller.
  • the drive motor is preferably designed as a wet-running electric drive motor with a split tube or containment shell between the stator and the rotor space, so that the rotor rotates in the liquid to be conveyed.
  • Such a centrifugal pump unit can be designed in particular for use as a circulation pump unit and more preferably as a heating circulation pump unit.
  • the centrifugal pump unit according to the invention also has a valve device with a valve element, which can be moved by the drive motor, which also drives the impeller.
  • the valve device is preferably integrated into the pump housing of the centrifugal pump assembly, in which also the impeller rotates.
  • a transmission is provided, which is designed such that a movement speed and / or a movement direction between the drive motor and the valve element is changed.
  • the valve element is moved slower and / or in a different direction than the drive motor, resulting in improved opportunities for accurate adjustment of the valve element and thus improved and new switching functions of the valve element.
  • so that valve element can be moved much more precise. This is advantageous for control tasks in which a flow through a flow path is to be regulated.
  • the transmission is particularly preferably designed such that it converts a rotational movement of the drive motor into a linear movement of the valve element, wherein the linear movement preferably takes place in the direction of the axis of rotation of the drive motor.
  • Such an amendment tion of the direction of movement from a rotational movement into a linear movement has the advantage that substantially longer adjustment paths for the valve element can be realized, which in turn allow other or more switching functions and / or enable a more precise positioning of the valve element in its different switching positions.
  • the transmission can be further preferably designed so that it generates a linear movement in addition to the rotational movement, so that the valve element rotates and moves linearly.
  • the transmission can be, for example, a spindle drive, wherein the valve element is moreover in threaded engagement with a stationary spindle. Ie. the valve element rotates on the spindle. Conversely, a spindle could turn in a fixed nut.
  • the valve element can be driven in rotation by the drive motor and then moves linearly during its rotational movement on the spindle or with the spindle.
  • the valve element is further preferably designed so that the switching or setting functions, which is to accomplish the valve element, are ideally caused by the linear movement.
  • the spindle can be firmly anchored in the pump housing.
  • the spindle preferably extends in the direction of rotation of the drive motor in alignment with the axis of rotation of the drive motor.
  • the valve element is particularly preferably movable linearly between at least two switching positions. This allows a longer Verstellweg between the different switching positions and / or better controllability of the positioning of the valve element in comparison to switching positions, which would be defined by different angular positions of the valve element.
  • the transmission can be designed such that it converts a rotational movement of the drive motor into a rotational movement of the valve element with preferably reduced speed. This embodiment also allows a more accurate positioning of the valve element in its switching position, since it can be achieved via such a transmission that the drive motor must perform a large number of revolutions, for example, to cause a rotational movement of the valve element, which is smaller than 360 °. This simplifies the control of the drive motor and leaves at the same time a good Steuer, Regulating the positioning of the valve element to.
  • the valve element is rotatable about an axis of rotation between at least two switching positions, wherein this axis of rotation is preferably aligned with the axis of rotation of the drive motor.
  • a rotatability between two switch positions can be provided as an alternative to a linear mobility between two switch positions or else in addition to this.
  • a precise control or regulation of the position of the valve element is possible even with a rotational movement between two switching positions.
  • a bearing of the valve element and / or the transmission is encapsulated, wherein the elements are preferably surrounded by a sleeve, in particular an elastic sleeve.
  • a cuff may be formed, for example, as a bellows.
  • the encapsulation has the advantage that the transmission and / or the bearing can in principle be arranged in the region of the flow paths of the pump unit or the valve device in the liquid to be conveyed, but at the same time be protected from contaminants in this liquid.
  • the bearings and / or the gearbox can be prelubricated or also permanently lubricated.
  • the storage and / or the transmission are lubricated by the fluid to be pumped itself, in which case the enclosure can be designed so that the liquid, preferably free of impurities penetrate into the bearing and / or gear compartment can and there, for example, long-term dilute or replace a previously filled lubricant.
  • the spindle is surrounded by an elastic sleeve, such as a bellows, which encapsulates the spindle and protects against contamination in the fluid to be delivered.
  • the elasticity or the folds make it possible for the sleeve to change in length as a function of the linear positioning of the valve element.
  • the valve device may preferably be designed as a switching valve and / or as a mixing valve.
  • a switching valve can for example be used in a heating system to direct the flow path for the heating medium or the heat carrier either by heating circuits for space heating or a heat exchanger for domestic water heating.
  • a switching valve could also be designed as a distributor valve in order to selectively open or close various heating circuits, ie to distribute the heat carrier to different heating circuits.
  • the valve device can be designed so that several valve openings can be opened simultaneously in order to be able to supply a plurality of heating circuits in a targeted manner simultaneously with a heat transfer medium.
  • the valve device may have the functionality of a mixing valve, for example, to see two liquid flows and thereby to be able to change the mixing ratio.
  • a mixing valve for example, to see two liquid flows and thereby to be able to change the mixing ratio.
  • Such applications are used, for example, in heating systems.
  • tion to adjust the temperature of a heat carrier can.
  • the valve element of the valve device may be located in the centrifugal pump assembly according to the invention in a flow path through the centrifugal pump assembly upstream or downstream of the impeller, ie make switching functions on the pressure side or the suction side of the impeller.
  • the valve device may have, for example, two inputs and one output, wherein the valve element is movable between at least two switch positions in which the two inputs are opened differently.
  • the valve element can be moved continuously between two switching positions acting as end positions. In one of the two end positions, a first input can be opened and a second input closed and in the second end position, conversely, a first input closed and the second input opened. In the intermediate positions both inputs are in variable ratio opened to each other.
  • a valve device can be arranged on the pressure side or alternatively also on the suction side of the impeller, depending on where in the heating circuit such a centrifugal pump unit is to be positioned.
  • the valve element is further preferably coupled to the drive motor via a magnetic, mechanical and / or hydraulic clutch, wherein preferably the transmission is arranged between the clutch and the valve element or the valve element is mounted in a transmission.
  • a mechanical coupling can be realized by a positive and / or positive engagement of two coupling elements.
  • a hydraulic coupling can be realized in particular via the liquid to be delivered itself. In a pressure chamber of the pump housing, which surrounds the impeller, the fluid flow is also set in rotation during rotation of the impeller. This rotational movement of the liquid can be transmitted to a rotatable valve element or a rotatable drive of a valve element, so that the valve element or its drive is rotated.
  • Such a valve element may, for example, have an annular disc which surrounds the suction mouth and / or have an annular circumferential wall which surrounds the outer circumference of the impeller. These walls thus limit the pressure or flow space surrounding the impeller and a flow prevailing in this space can act on these walls to move the valve element. If the valve element itself is rotated, this can for example be mounted on a spindle, so that it rotates on the spindle while doing a linear movement. If a separate drive element is provided, which in this way is hydraulically or also magnetically or mechanically coupled to the drive motor, the transmission can be arranged between the drive element and the valve element. in order to change the movement speed and / or the direction of movement from the drive element to the valve element.
  • the valve element can rotate slower than the drive element and thus the drive motor.
  • the transmission could be designed so that the valve element performs a linear movement, while the drive element and the drive motor only perform a rotational movement.
  • the combination of a transmission with a hydraulic coupling between the valve element and the drive motor, as described above, is particularly advantageous. In the hydraulic coupling between the drive motor and the valve element, a precise positioning of the valve element may be difficult. The positionability is thereby improved via the transmission, since the transmission can be designed so that only a relatively small distance of the valve element is traveled with a large number of revolutions of the drive motor.
  • the valve element can preferably be driven by a drive element in the form of a disc and / or annular wall, which adjoin the pressure or flow space which surrounds the impeller.
  • This drive element can drive the actual valve element via a gear or be stored in a gear such as a spindle, so that the drive movement is converted into an actuating movement of the valve element, wherein the actuating movement either a different direction than the drive movement and / or a different speed than the Can have drive movement.
  • the adjusting movement can be linear while the drive element is rotated on a spindle.
  • the drive element can be taken over the flow in the vicinity of the impeller and rotated, where it rotates, for example, several times to realize a relatively small actuating movement via a transmission.
  • the coupling described is further preferably detachable in such a way that it is rotationally dependent, speed-dependent, pressure-dependent and / or releasable by slip.
  • a releasability of the coupling has the advantage that after reaching a certain switching position of the valve element, the clutch can be released and the drive motor can then drive only the impeller to go into the normal pump operation. This can then be done for example by changing the direction of rotation or speed change, in particular speed increase. By increasing the speed, the output side pressure of the impeller can also be increased so that the release of the clutch can then be caused by this pressure increase.
  • the drive motor is preferably provided with a control device via which the drive motor can be adjusted in its rotational speed and preferably regulated. More preferably, the control device is designed so that it can accelerate or decelerate the drive motor also different degrees. Alternatively or additionally, the control device may be designed so that the drive motor can rotate selectively in different directions of rotation. The control device is designed so that it also controls or regulates the switching function of the valve device by appropriate control of the drive motor.
  • the control device can have at least one sensor connection via which a sensor signal, for example a temperature sensor, is received as a basis for regulating the valve position.
  • the centrifugal pump unit has a holding device, which cooperates with the valve element and is designed to hold the valve element in an achieved switching position, wherein the holding device can preferably be brought into and out of engagement with pressure is trained.
  • the holding device thus acts as a second clutch, which serves to hold the valve element in a desired switching position.
  • Such functionality can be achieved, for example, by the valve element being movable between a released and an abutting position, in which the valve element abuts against at least one abutment surface in such a way that it is held positively and / or positively. In the released position, this holding force is canceled and the valve element is preferably spaced from the contact surface or it can slide along the contact surface.
  • Such a movement can, for example, be realized as a function of pressure by selecting the direction of movement between the released and the adjacent position so that the movement can be caused by a pressure force which is caused by the pressure prevailing in the pressure chamber. Contrary to the pressure force preferably acts a restoring force, which presses the valve element in the rest position in the released position.
  • This can be realized for example by a compression spring.
  • the valve element has a pressure area, which surrounds the impeller, facing pressure surface on which the pressure in the pressure chamber acts.
  • This pressure surface may be an annular surface surrounding a suction opening which engages the suction mouth of the impeller.
  • the contact surface as has been described, further preferably simultaneously serves as a sealing surface, which, for example, forms the valve seats, so that the valve element can preferably be pressed simultaneously sealingly against these valve seats.
  • the valve element further preferably has an engagement surface or is connected to an engagement surface which delimits a pressure space surrounding the impeller and to which a pressure prevailing in the pressure space and / or a flow prevailing in the pressure space acts. Due to the effect of the flow, the attack surface can be moved together with the flow, so that the Ven- Tilelement or a drive element on which the attack surface is formed, are moved by the flow and in particular rotated. This rotational movement is then optionally transmitted via a transmission to the valve element in order to move this specifically between its switching positions. If the pressure acts on this or another attack surface, this can be used in the manner described, for example, to selectively move the valve element in the sense of a second clutch between a dissolved and an adjacent position.
  • the valve element can be held in an reached switching position by pressure increase, which can be caused by speed increase of the drive motor.
  • the drive motor is preferably first driven at a lower speed to move the valve member. After reaching the switching position, the pressure is then increased to keep the valve element in the achieved switching position, for example, by abutment against a contact surface.
  • the function of the holding device can also be achieved by blocking the gearbox or the spindle drive.
  • the valve element is arranged rotatably on a spindle and acts on the valve element via a pressure surface axial force in the longitudinal direction of the spindle, this leads to higher contact forces in the spindle drive, which with appropriate choice of the pitch and the design of the spindle drive to an inhibition in the spindle drive and thus can lead to the fixation of the valve element.
  • the engagement surface on which a pressure acts in the pressure chamber further preferably extends transversely to a movement path, along which the valve element is movable between the described applied and the released position. If, as described, a provision Lelemen ⁇ or biasing element is provided which generates a biasing force or restoring force, it also preferably acts in a direction opposite to the attack surface of the force acting on the engagement surface pressure force.
  • FIG. 1 is an exploded perspective view of a centrifugal pump assembly according to a first embodiment of the invention
  • Fig. 2 is an exploded view of the centrifugal pump assembly of FIG. 1 in another perspective
  • Hg. 3 is a plan view of the centrifugal pump assembly according to
  • Hg. 4 is a sectional view of the centrifugal pump assembly according to
  • FIG. 5 shows a sectional view according to FIG. 4 with the valve element in a second switching position
  • FIG. 6 shows schematically the hydraulic construction of a heating system with a centrifugal pump assembly according to FIGS. 1-5, a plan view of a centrifugal pump assembly according to a second embodiment of the invention, 7 is a sectional view of the centrifugal pump assembly according to FIG. 7, wherein the section has been laid so that both inputs can be seen in section,
  • FIG. 9 is an exploded perspective view of a centrifugal pump naggregates according to a third embodiment of the invention.
  • Fig. 10 is a sectional view of the centrifugal pump assembly according to
  • FIG. 10 is a sectional view of FIG. 10 with the valve element in a released position
  • Fig. 13 is a view according to FIG. 12 with the valve element in a second switching position.
  • the centrifugal pump assembly according to FIG. 1 has a stator or motor housing 2 with an electric drive motor arranged therein.
  • the electric drive motor has a stator 4 with a rotating rotor 6 therein, which is fixed to a rotor shaft 8.
  • the drive motor is designed as a wet-running motor with a can 10 between the stator and the rotor space.
  • a pump housing 12 Connected to the motor housing 2 is a pump housing 12, which simultaneously forms a valve housing for a valve device described below.
  • the impeller 14 is arranged, which is non-rotatably attached to the rotor shaft, so that it together with the rotor 6 rotates.
  • an electronics housing 16 is arranged with control electronics or control device 18 arranged therein for controlling the drive motor.
  • the impeller 14 is surrounded in the pump housing by a pressure chamber 20, which opens into a pressure port 22 of the pump housing.
  • the pump housing 12 has four further connections 24, 26, 28 and 30, which each open into an opening on the inner circumferential wall of the pump housing 12.
  • a drum-shaped valve element 32 is arranged, which is formed from a cup-shaped lower part 34 and a lid 36 which closes this at its open axial end.
  • the cover 36 has a central suction opening 38 into which the impeller 14 engages with its suction mouth 40.
  • the peripheral surface surrounding the suction opening 38 forms a pressure or attack surface which limits the pressure chamber 20 on an axial side in the peripheral region of the suction mouth 40. Ie. On this surface of the lid 36, the prevailing in the peripheral region of the impeller 14 flow and the pressure in the pressure chamber 20 may act.
  • the cover 36 also has in the mentioned pressure surface on a pressure port 42, to which a pressure channel 44 connects in the interior of the lower part 34.
  • This pressure channel 44 opens to the outer circumference of the valve element 32 in a first circumferential groove 46.
  • the circumferential groove 46 extends completely around the outer circumference of the valve element 32 or its lower part 34.
  • Axially staggered extends around the outer circumference of the valve element 32 or its lower part 34 a second annular circumferential groove 48, which is open via an opening 50 to the interior of the valve element 32 and thus fluidly connected to the suction port 38.
  • the lower part 34 of the valve element 32 also has an inlet opening 52 at its bottom, which is also open to the interior. The bottom is the end facing away from the cover 36 of the valve element 32, which faces a bottom at the axial end of the pump housing 12.
  • the valve element 32 is rotatably arranged in the interior of the pump housing 12 about the rotational axis X of the impeller 14. From the bottom of the pump housing 12, a fixed spindle 54 extends in the direction of the longitudinal axis X into the interior of the pump housing 12. The spindle 54 engages in a central threaded hole 56 in the bottom of the lower part 34 of the valve element 32 a. A rotation of the valve element 32 about the longitudinal axis X leads to a rotation of the threaded hole 56 on the spindle 54, so that the valve member 32 simultaneously displaced in the axial direction X. By changing the direction of rotation, a reciprocating movement of the valve element 32 can be achieved.
  • the spindle 54 is surrounded on the outside of the valve element 32 by a first bellows 58 and in the interior of the valve element 32 by a second bellows 60, which has a closed end face. Characterized the spindle 54 is encapsulated or separated by the bellows 58 and 60 of the liquid inside the valve member 32 and inside the pump housing 12 and in particular protected from contamination in the liquid. In addition, inside the sleeves or bellows 58, 60, a lubricant for lubricating the spindle drive can be arranged. However, it is also possible that intentional leaks are provided, so that the spindle can be lubricated by the liquid, in particular water, in the system, the bellows 58 and 60 only impurities from the spindle keep away.
  • a first hydraulic coupling between the drive motor and the valve element 32 is provided for driving or for movement of the valve element 32, which acts such that in the pressure chamber 20 in the vicinity of the impeller 14 rotating flow to the lid 36 of Valve element 32 acts such that this is rotated by friction.
  • the control device 18 is designed so that it can drive the drive motor in two directions of rotation.
  • the valve element 32 can be rotated so that it moves on the spindle 54 along the longitudinal axis X to the impeller 14 to or from this.
  • the pressure in the pressure chamber 20 may rise to such an extent that it generates on the cover 36 a compressive force acting in the direction of the longitudinal axis X, which is transmitted via the valve element 32 and the Windeloch 36 transmits to the threads of the spindle 54.
  • the valve element 32 is held in its reached switching position.
  • the coupling formed by the impeller 14 and the cover 36 disengages by slip.
  • the heating system has the described centrifugal pump unit 1, which is characterized in Fig. 6 by the dashed line and two valve means, which are realized by the valve member 32 includes.
  • the heating system also has a heat source 62, which may be, for example, a gas boiler.
  • a first heating circuit 64 and a second heating circuit in the form of a floor heating circuit 66 are provided.
  • a secondary heat exchanger 58 is arranged, which serves to heat domestic water.
  • the output of the heat source 62 opens via the node 70 directly into the first heating circuit 64, which has, for example, normal radiators or radiators.
  • the return of the heating circuit 64 opens into the connection 24 on the pump housing 12.
  • the pressure connection 22 of the pump housing 12 is connected to the input of the heat source 62. the, so that the circulating pump unit 1 via the pressure port 22, the heating medium, such as water, through the heat source 62, the heating circuit 64 and back into the port 24 can promote.
  • the underfloor heating circuit 66 also opens with its outlet into the return line, which is connected to the connection 24.
  • the entrance of the underfloor heating circuit 66 is connected to the connection 30 on the pump housing.
  • the return of the secondary heat exchanger, the flow diverging from the node 70 opens at the port 26 of the pump housing. Another connection from node 70 leads to port 28 on the pump housing.
  • valve element 32 can now take over the function in this system to switch the heating medium flow between the two heating circuits 64 and 66 on the one hand and the secondary heat exchanger 58 on the other side.
  • valve element 32 can act as a mixer to regulate the temperature for the flow of the underfloor heating circuit 66 by heating medium from the return with heating medium from the flow, that is, the output of the heat source 62 is mixed.
  • valve element 32 is in a first end position in abutment with the bottom of the pump housing 12, so that the inlet opening 52 of the valve element 32 is closed and thus a flow path from the port 24 into the interior of the valve element 32 and thus to the suction opening 38th is closed.
  • the second circumferential groove 48 lies over the opening of the connection 26, so that a connection is created from the connection 26 via the circumferential groove 48 and the opening 50 into the interior of the valve element 32.
  • the impeller 14 through the suction port 18 suck liquid from the port 26.
  • FIG. 4 shows a switching position in which the valve element 32 is moved further towards the impeller 14.
  • the second circumferential groove 48 is no longer in register with the opening of the terminal 26, so that it is now blocked by a peripheral wall of the lower part 34 of the valve element 32.
  • the flow path through the secondary heat exchanger 68 is closed.
  • the inlet opening 52 is lifted off the bottom of the pump housing 12, so that a connection is created from the connection 24 via the inlet opening 52 into the interior of the valve element 32 and thus to the suction opening 38.
  • the opening to the connection 28 can also be completely closed so that only unheated water would be circulated through the underfloor heating circuit 66.
  • a temperature control can take place by the control device 18 being actuated by a corresponding drive of the system. drive motor, the valve element 32 in the direction of the longitudinal axis X back and forth. This is preferably done at a lower speed than the usual operating speed of the impeller 14. Via the spindle 54, the rotational movement of the valve element 32 is simultaneously converted into a linear movement, whereby the speed can be reduced by the thread pitch on the spindle at the same time.
  • Figs. 7 and 8 show a second embodiment of the invention, which differs from the first embodiment in that the valve means merely provides a mixing function.
  • the pump housing 12 has only three connections, namely the pressure connection 22 and two connections 24' and 26 'acting as inputs.
  • the pressure port 22 also branches off from the pressure chamber 20 here, which, however, can not be seen in the sectional plane according to FIG. 8.
  • a valve element 32 ' is provided, which is hollow and is closed at its side facing the pressure chamber 20 by a lid 36', wherein the lid 36 'again as an attack surface for the flow and the pressure in the pressure chamber 20th serves.
  • the opposite axial end of the valve member 32 is formed open and forms in the switching position shown in Fig. 8 is a connection to the opening of the terminal 26 '.
  • a spindle 72 is arranged, which engages in a threaded hole 74 at the bottom of the pump housing 12 '.
  • the spindle 72 is surrounded by a bellows 76 having the same function as the bellows 58 and 60.
  • An annular groove 78 is formed on the outer circumference of the valve element 32 ', which opens into the interior of the valve element 32' via an opening 80.
  • the valve shown acts as a mixing valve. In the switching position shown in FIG. 8, the circumferential wall of the valve element 32 'largely covers the opening to the port 24'.
  • valve element 32 If the rotation of the valve element 32 with the spindle 72 in the winch If the valve element 32 'moves even further in the direction of impeller 14, the circumferential wall of the valve element 32' would completely cover the opening to the connection 74 'so that it is closed and a flow path only the connection 26' into the interior of the valve element 32 into and from there via the suction opening 38 in the suction mouth 40 would be given in.
  • valve element 32 ' when the valve element 32 'is moved by rotation to the bottom of the pump housing 12', the peripheral edge of the valve housing 32 'abuts the bottom of the pump housing 12' so that the flow path from the port 26 'is closed while the circumferential groove 78 closes the opening the port 74 'completely covers and the flow path from the port 74' into the interior of the valve element 32 'and from there through the suction port 38 to the suction port 40 completely releases. In intermediate positions different mixing ratios are possible.
  • the drive and the displacement of the valve element 32 is carried out as described with reference to the first embodiment.
  • a valve element is provided, which is rotationally moved between different switching positions.
  • the centrifugal pump assembly according to the third exemplary embodiment also has a drive motor, which is arranged in a motor housing 2 and its construction corresponds to the description according to the first two exemplary embodiments, so that reference is made to this description at this point.
  • the impeller 14 is rotatably connected to the rotor shaft 8 and the impeller surrounding the pressure chamber 20 opens into a pressure port 22.
  • a valve element 32 is provided, which is also drip-shaped with a cup-shaped lower part 82 and a this
  • the lid 85 has centrally the suction opening 38, which is in engagement with the suction mouth 40 by an axially projecting collar of the suction opening 38 in this embodiment. example engages in the interior of the suction mouth 40.
  • the suction opening 38 surrounding annular surface of the lid 84 forms a politiciansg. Pressure surface on which the pressure in the pressure chamber 20 can act.
  • a drive shaft 86 which carries a coupling part 88 at its axial end facing the impeller 14, extends centrally through the valve element 32 'or its lower part 32. This meshes with a corresponding coupling part 90 on the axial end face of the rotor shaft 8.
  • the two coupling parts 88 and 90 are designed so that they act only in one direction of rotation, that is, the coupling part 90 preferably has a sawtooth in the circumferential direction, which the Clutch part 88 entrains in a rotational direction. In the opposite direction of the coupling member 88 slides over the sawtooth under axial displacement of the drive shaft 86.
  • the drive shaft 86 is rotatably mounted in a blind hole 92 in the bottom of the pump housing 12 'about the axis of rotation X, about which the rotor shaft 8 is rotatable. Axially, the drive shaft 86 is acted upon in the blind hole 92 by a spring force of a compression spring 94.
  • the compression spring 94 presses the drive shaft 86 with the coupling part 88 into engagement with the coupling part 90 at the axial end of the rotor shaft 8.
  • the drive shaft 86 can move axially against the spring 94.
  • the lower part 82 of the valve element 32 "is axially fixed on, but rotatable about, the drive shaft 86.
  • the valve element 32" is coupled to the drive shaft 86 via a planetary gear 96.
  • the planetary gear 96 has a planetary gear 98, which is also rotatably mounted in the bottom of the pump housing 12 ', wherein it meshes with a toothing on the outer circumference of the drive shaft 86 so that it is driven in rotation by the drive shaft 86.
  • the axis of rotation of the planetary gear 98 extends parallel to the axis of rotation of the drive shaft 86 and thus the aligned axis of rotation X of the rotor shaft 8.
  • the valve element 32 "or its lower part 82 has at its bottom a recess or recess 100, which by an invagination in the interior of the valve element 32 'is formed and has on its inner periphery a toothing, which meshes with the planetary gear 98.
  • This planetary gear 96 forms a reduction gear, which ensures that upon rotation of the rotor shaft 8, the valve element 32 "rotates at a lower speed about the axis of rotation X. This allows a more accurate adjusting movement.
  • the valve element 32 is also axially movable together with the drive shaft 86 to a certain extent along the longitudinal axis X. Such a movement can take place on the one hand in the manner described on the coupling parts 88, 90, on the other hand by the Pressure in the pressure chamber 20 which acts on the cover 84.
  • the entire valve element 32 ' is displaced against the spring 94 to the bottom of the pump housing 12 ", so that the coupling parts 88, 90 disengage.
  • the clutch formed by the coupling parts 88, 90 thus releases not only rotational direction dependent, but also pressure-dependent, i. Depending on the pressure in the pressure chamber 20.
  • the pump housing 12 has two suction ports 24" and 26 ", which in each case in a connection opening 102 and 104 in the bottom of the pump housing 2 'open.
  • the lower part 82 of the valve element 32 has an arcuate switching opening 106 at its bottom in the peripheral area of the planetary gear 96.
  • the switching opening 106 covers one or both of the connection openings 102, 104
  • the rotation of the valve element 32" is preferable in a first direction of rotation of the drive motor, so that no turning back and forth takes place, but always a turn must be performed to move back.
  • the pump housing 12, 12 ', 12 forms a combined pump and valve housing housing both the valve element 32, 32', 32" and the impeller 14.
  • the pump housing 12, 12 ', 12 could also be designed in several parts, In particular, it would be possible to form a separate pump housing and a separate valve housing, wherein the pump housing only the impeller 14 and the valve housing, the valve element 32, 32nd ', 32 ", such a pump housing could then be suitably connected to such a valve housing.

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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)

Abstract

L'invention concerne un ensemble pompe centrifuge comprenant un moteur d'entraînement, au moins un rotor (14) entraîné en rotation par celui-ci, ainsi qu'au moins un dispositif faisant office de vanne (32) qui présente un élément vanne (32). Une transmission de mouvement du moteur d'entraînement à l'élément vanne (32) s'effectue par l'intermédiaire d'une transmission (54 ; 72 ; 96) qui fait varier une vitesse de déplacement et/ou une direction de déplacement entre le moteur d'entraînement et l'élément vanne (32).
PCT/EP2018/056213 2017-03-14 2018-03-13 Ensemble pompe centrifuge Ceased WO2018167047A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17160835.9 2017-03-14
EP17160835.9A EP3376036A1 (fr) 2017-03-14 2017-03-14 Groupe motopompe

Publications (1)

Publication Number Publication Date
WO2018167047A1 true WO2018167047A1 (fr) 2018-09-20

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WO (1) WO2018167047A1 (fr)

Cited By (1)

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DE102019202975A1 (de) * 2019-03-05 2020-09-10 Hanon Systems Efp Deutschland Gmbh Elektrisch angetriebene Fluidmaschine

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Publication number Priority date Publication date Assignee Title
EP3540234A1 (fr) 2018-03-13 2019-09-18 Grundfos Holding A/S Groupe pompe centrifuge et procédé pour déplacer une valve dans un groupe pompe centrifuge
CN110129929A (zh) * 2019-05-29 2019-08-16 合肥经新纺织科技有限公司 一种单锭可控集聚纺纱装置和集聚方法
DE102022202217A1 (de) * 2022-03-04 2023-09-07 Vitesco Technologies GmbH Ventil-Pumpen-Einheit
DE102022202216A1 (de) * 2022-03-04 2023-09-07 Vitesco Technologies GmbH Ventil-Pumpen-Einheit
DE102022111976A1 (de) * 2022-05-12 2023-11-16 Woco Industrietechnik Gmbh Stellventil und Leitungssystem
EP4621243A1 (fr) * 2024-03-19 2025-09-24 Volvo Car Corporation Système de soupape

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CH463896A (de) * 1963-09-21 1968-10-15 Louis Dipl Ing Siber Misch- und Temperaturregelvorrichtung in einem Gehäuse mit mehreren Anschluss-Stutzen für Warmwasserheizungs- und -bereitungsanlagen
DE1958277B1 (de) 1969-11-20 1971-02-25 Karl Schichl Umwaelzpumpe fuer warmwasser heizungsanlagen mit einem im pumpengehaeuse angeordneten vierwegemischerventil
DE10207653C1 (de) * 2002-02-22 2003-09-25 Gpm Geraete Und Pumpenbau Gmbh Elektrische Kühlmittelpumpe mit integriertem Ventil, sowie Verfahren zu dessen Steuerung
US20160258340A1 (en) * 2013-11-16 2016-09-08 Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg Electromotive coolant pump

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
CH463896A (de) * 1963-09-21 1968-10-15 Louis Dipl Ing Siber Misch- und Temperaturregelvorrichtung in einem Gehäuse mit mehreren Anschluss-Stutzen für Warmwasserheizungs- und -bereitungsanlagen
DE1958277B1 (de) 1969-11-20 1971-02-25 Karl Schichl Umwaelzpumpe fuer warmwasser heizungsanlagen mit einem im pumpengehaeuse angeordneten vierwegemischerventil
DE10207653C1 (de) * 2002-02-22 2003-09-25 Gpm Geraete Und Pumpenbau Gmbh Elektrische Kühlmittelpumpe mit integriertem Ventil, sowie Verfahren zu dessen Steuerung
US20160258340A1 (en) * 2013-11-16 2016-09-08 Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg Electromotive coolant pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019202975A1 (de) * 2019-03-05 2020-09-10 Hanon Systems Efp Deutschland Gmbh Elektrisch angetriebene Fluidmaschine

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