WO2018166979A1 - Ensemble pompe centrifuge - Google Patents

Ensemble pompe centrifuge Download PDF

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Publication number
WO2018166979A1
WO2018166979A1 PCT/EP2018/056099 EP2018056099W WO2018166979A1 WO 2018166979 A1 WO2018166979 A1 WO 2018166979A1 EP 2018056099 W EP2018056099 W EP 2018056099W WO 2018166979 A1 WO2018166979 A1 WO 2018166979A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve element
centrifugal pump
impeller
bearing
pump unit
Prior art date
Application number
PCT/EP2018/056099
Other languages
German (de)
English (en)
Inventor
Thomas Blad
Peter Mønster
Original Assignee
Grundfos Holding A/S
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 Holding A/S filed Critical Grundfos Holding A/S
Publication of WO2018166979A1 publication Critical patent/WO2018166979A1/fr

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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
    • 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
    • F04D13/06—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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • 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
    • F04D29/08—Sealings
    • F04D29/086—Sealings 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings 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
    • 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 unit with an electric drive motor, an impeller driven by the latter and a rotatable valve element integrated in the centrifugal pump unit.
  • centrifugal pump units which have a movable, in particular pivotable valve element in the pump housing in order to selectively direct the liquid flow conveyed by the centrifugal pump assembly into two different pressure-side flow paths, in particular depending on the direction of rotation of the drive motor.
  • Arrangements are also known in which a switching device is integrated between two suction-side flow paths in the centrifugal pump unit. Such an arrangement is known for example from DE 90 139 92 U l.
  • This known switching device has a flow element located on the pressure side of the impeller, which switches the valve device on the suction side depending on the direction of rotation. This requires a relatively complex mechanism.
  • the object of the invention is to improve a centrifugal pump assembly with an integrated valve element in such a way that a simpler design of the centrifugal pump assembly is achieved with simultaneously increased reliability of the switching function of the valve element.
  • the centrifugal pump assembly has an electric drive motor, by means of which at least one impeller can be driven in rotation.
  • the impeller is rotatably connected to the magnet rotor of the drive motor, either directly or z. B. via a shaft.
  • the drive motor is preferably designed as a wet-running electric drive motor, d. H. it preferably has a split tube or a split pot between the stator and rotor, so that the rotor rotates in the fluid to be conveyed by the impeller.
  • the impeller is disposed in a pump housing defining the flow paths to and from the impeller.
  • a valve element is further arranged, which is rotatable between at least two switching positions. This may be for example a valve element of a switching valve or mixing valve, as described below.
  • the valve element is rotatably supported in the interior of the pump housing on a bearing.
  • the bearing is arranged in a storage space which is separated from the remaining interior of the pump housing, which accommodates a fluid to be delivered or a liquid to be delivered, by at least one seal.
  • the pump unit is designed for water as the fluid to be delivered. So is the centrifugal pump unit z. B. for use as a circulation pump in a heating and / or air conditioning.
  • the seal of the storage space relative to the interior of the pump housing has the advantage that impurities in the fluid to be pumped from the storage in the Essentially kept away. At the same time, however, no absolutely hermetic seal is required which would be required if the bearing were located outside the pump housing. Some leakage in the bearing can be tolerated. However, liquid can not escape to the outside of the pump housing. The fact that impurities are kept away from the camp, a smooth bearing of the valve element can be ensured. The smooth bearing is advantageous if the valve element is to be moved by the drive motor without an additional drive, in particular by hydraulic coupling via the fluid to be delivered.
  • the storage space can be formed integrally with the valve element. Ie. at least a portion of a wall bounding the storage space is integrally formed with at least one wall of the valve element. Particularly preferably, the storage space is formed by a recess on a wall of the valve element, in particular an end face of the valve element.
  • the storage space preferably has a tubular or blind-hole-like shape.
  • the at least one bearing may be lubricated inside the storage space by a lubricant, preferably at the factory.
  • the lubricant may be, for example, a grease or other suitable lubricant.
  • the lubricant is preferably introduced at the factory, ie the lubricant is already arranged in the storage room at delivery of the centrifugal pump unit. If the seal of the storage space is not absolutely tight, but lets through a certain amount of the liquid to be conveyed, it is possible that in the course of time the lubricant in the operation of the Krepelspumpenaggregates by the liquid to be conveyed or to promotional fluid is diluted and replaced. Then, over time, the fluid to be pumped can take over the function of the lubricant. That is, the bearing is preferably designed so that the fluid to be delivered or the liquid to be conveyed can serve as a lubricant.
  • the bearing is designed as a sliding bearing. This allows a very simple storage structure. Furthermore, such a bearing can also be lubricated by the liquid to be delivered.
  • the seal for that fluid or the liquid to the promotion of the centrifugal pump unit is formed, not be completely sealed.
  • the fluid to be pumped is water, so that the seal is adjusted accordingly so that it passes a certain amount of liquid or water.
  • the seal can be made more easily and, moreover, the friction in the region of the seal can be reduced.
  • a permanent lubrication of the bearing can advantageously be ensured if the penetrating liquid, in particular the penetrating water takes over the function of a lubricant over time.
  • the seal is designed such that it retains particles in the fluid to be delivered by the impeller.
  • the storage space can be designed so that it is open only on one side to the interior of the pump housing, so that only one side of the bearing a seal is arranged.
  • the storage space is formed so that on each of two sides of the bearing a seal is arranged, which the storage space in the manner described seals against the remaining interior of the pump housing.
  • the at least one bearing is arranged centrally on the valve element. That is, the bearing surrounds centrally the axis of rotation of the valve element.
  • the bearing can be made very small in diameter, so that the friction in the bearing is reduced.
  • the valve element preferably protrudes in the radial direction over the bearing, so that in this area favorable lever ratios for rotation of the valve element to the at least one bearing exist.
  • the diameter of the bearing is preferably less than a quarter of the diameter of the valve element.
  • the at least one bearing lies in a region of the pump housing located on the suction side of the impeller. This means that at least one bearing is located in the region of the pump housing, through which the liquid drawn in by the impeller flows. This has the advantage that the bearing of the valve element does not collide with the impeller and the drive motor.
  • the at least one valve element is mechanically, magnetically and / or hydraulically coupled to its movement between the switching positions with the drive motor.
  • a coupling between the drive motor and the valve element may be provided, for example between a rotor shaft or the impeller on one side and the valve element on the other side.
  • the coupling can be designed to be non-positive and / or frictionally engaged. More preferably, the coupling can be detachable, so that it can be selectively disengaged. This can be done, for example, as a function of the rotational speed of the drive motor and / or the pressure in the pressure-side region of the pump housing.
  • the drive motor is hydraulically coupled to the valve element
  • this hydraulic coupling is preferably carried out via the fluid set in motion by the impeller.
  • the fluid or the fluid in the pump housing can be set by the impeller in a rotational movement, which is transmitted by friction to the valve element, so that the valve element is rotated by the flow and can be moved between the switching positions.
  • the drive motor and thus the impeller can preferably be driven in two opposite directions of rotation, so that the rotating flow in the pump housing optionally extends in different directions of rotation.
  • the hydraulic see coupling has the advantage that it can easily disengage from slippage.
  • At least one force generating means may be present, which exerts a force on the at least one valve element in the direction of one of the at least two switching positions, wherein the force is preferably a spring force, a magnetic force and / or gravity.
  • the valve element can be automatically turned into an outlet by the force generating means when the drive motor is switched off. transition position, which preferably corresponds to one of the switching positions are moved back. That is, in this embodiment, no reversal of the direction of rotation of the drive motor is required to move the valve element back to its original position. From the initial position into the other switching position, the valve element can be moved by virtue of its rotation due to a coupling with the drive motor. In particular, in order to keep the valve element in the initial position during operation of the drive motor, a second clutch can be provided, which fixes the valve element in this position in particular frictionally.
  • This coupling can be pressed, for example, by the pressure in the interior of the pump housing, which is caused by the impeller, in a coupled and thus holding position. Whether the valve element is moved from the initial position or not can be achieved in such a configuration by appropriate actuation of the drive motor.
  • the drive motor is preferably provided with a control device which makes it possible to regulate the speed and / or acceleration of the drive motor. If, for example, the drive motor is accelerated very quickly, this can lead to a pressure building up very quickly in the pump chamber, which can be used to quickly engage a coupling which fixes the valve element before the valve element is moved by a flow the other switching position is moved. Thus, the valve element can be kept in its initial position. In contrast, when the drive motor is slowly accelerated, a rotating flow may form in the pump housing before the pressure is high enough to fix the valve member. Thus, the valve element can then be moved by the flow in the other switching position.
  • the at least one bearing preferably permits axial movement of the valve element between a first and a second position.
  • This embodiment makes it possible to axially close the valve element move it to z. B. in the second position in a sealing and holding system to bring the pump housing or connected to the pump housing bearing surface. In this position, the valve element can then rest, for example, sealingly against at least one valve seat.
  • the system can take over the function of the above-described second coupling for fixing the valve element.
  • the valve element In the first position, however, the valve element is preferably spaced from the contact surfaces, so that it can preferably rotate freely around the at least one bearing.
  • the first position and / or the second position are preferably limited by a stop, wherein preferably at least one of the stops is located within the storage space.
  • the stop may for example be formed by a contact surface, in which the valve element comes to rest.
  • a second stop is preferably provided in the opposite direction so that the valve member can not move further than a predetermined amount away from the abutment surface or pump housing.
  • At least one return element in particular a return spring is provided, which exerts a restoring force in the axial direction on the valve element.
  • the return element is arranged so that it moves the valve element in a position in which it is spaced from a abutment and / or sealing surface and is freely rotatable about the at least one bearing.
  • the valve element is preferably pressed by a pressure force generated in the pump housing.
  • the valve element preferably has a pressure surface, which faces a pressure chamber in the interior of the pump housing and on which the fluid pressure, which is generated by the impeller in the interior of the pump housing, acts. If the generated by the reset element E force is exceeded by this pressure force, the valve element moves against the return element in a holding and / or sealing position, as described above.
  • the return element is arranged within the storage space. So it is protected from contamination by the at least one seal.
  • the valve element is arranged in the pump housing such that it separates a suction chamber connected to a suction side of the impeller from a pressure chamber connected to the pressure side of the impeller.
  • the differential pressure between the suction chamber and the pressure chamber can be used to press the valve element against a sealing or contact surface, on the one hand to seal the suction side against the pressure side and on the other hand to seal valve openings in the desired manner.
  • a coupling can be created, which fixes the valve element in contact with the contact surface in a desired switching position. Facing the pressure chamber, the valve element has in the manner described preferably a pressure surface on which the output side pressure of the impeller acts.
  • the centrifugal pump assembly on two alternative flow paths, wherein the at least one valve element is arranged in these flow paths such that in the at least two switching positions, the flow paths are opened differently.
  • the valve element can be designed as a pure changeover valve so that it opens a first flow path in a first switching position and shoots a second flow path and conversely closes the first flow path in a second switching position and opens the second flow path.
  • Under a valve element in the sense of this invention is also a coupled arrangement of two Ventilelemen- ⁇ e, which are coupled with each other to move to understand.
  • the valve element can provide a mixing function in that, for example, it can also assume intermediate positions between the described two switching positions, in which both flow paths are opened to a certain extent. By displacing the valve element in these intermediate positions, the flow paths can be opened differently wide, so that a mixing ratio of the flows through the two flow paths can be changed.
  • the valve element is formed and arranged such that, during its movement, it opens one of the flow paths by the same amount about which the other flow path is simultaneously closed.
  • the two flow paths are particularly preferably located on the suction side of the impeller. That is, the impeller sucks depending on the position of the valve element from one of the two flow paths or from both flow paths, in which case by displacement of the valve element, the mixture of the flows from the two flow paths can be changed.
  • the valve element can also be situated on the pressure side of the impeller, so that it switches over the flow between two pressure-side flow paths or mixes it as a mixing valve when configured.
  • FIG. 1 is an exploded view of the centrifugal pump assembly according to a first embodiment of the invention
  • FIG. 2 is a perspective view of the centrifugal pump assembly of FIG. 1 with removed pump housing and valve element, a perspective view of the motor shaft of the centrifugal pump assembly of FIG. 1 and 2 and the coupling part of the valve element, a sectional view of the centrifugal pump assembly of FIG. 1 with the valve element in a first position, a sectional view of FIG. 4 with the valve element in a second position, a 1 to 3 with the valve element in a first switching position, a view according to FIG. 6 with the valve element in a second switching position, a view according to FIGS.
  • FIG. 6 and 7 with the valve element in a third switching position 1 is an exploded view of a centrifugal pump assembly according to a second embodiment of the invention, a perspective view of the open valve element of the centrifugal pump assembly of FIG. 10, Hg. 1 2 is a perspective view of the closed valve element according to FIG. 1 1, Fig. 1 3 is a sectional view of the centrifugal pump assembly according to
  • Fig. 10 with the valve element in a first position
  • Fig. 1 4 is a sectional view of FIG. 13 with the valve element in a second position
  • Fig. 1 5 is a plan view of the open pump housing of
  • Fig. 1 is a view according to Fig. 1 5 with the valve element in a second switching position
  • Hg. 1 7 is a view according to FIGS. 15 and 16 with the valve element in a third switching position
  • Fig. 1 8 is a view according to FIG. 15 to 1 7 with the valve element in a fourth switching position
  • Hg. 1 9 schematically shows the hydraulic structure of a heating system with a centrifugal pump assembly according to FIG. 10 to 1 8, Fig. 20 enlarges a representation of the mounting of the valve element 18, 18i in the embodiments of FIGS. 1 to 1.
  • the exemplary embodiments of the centrifugal pump assembly described in the following description relate to applications in heating and / or air conditioning systems, in which a liquid heat carrier, in particular water, is circulated by the centrifugal pump unit.
  • the centrifugal pump assembly 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 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 contains an electronic control unit 17 for controlling the electric drive motor in the pump housing 2.
  • the electronics housing 1 6 could be arranged in a corresponding manner also 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 axle 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 periphery.
  • 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 port 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 of the control device 1 7 in two different operating modes or operating modes can be controlled.
  • a first operating 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 by the control device 1 7 adjustable, speed.
  • the second operating mode the drive motor is activated in open-loop operation, so that the rotor can be turned stepwise in individual angular steps predetermined by the control device 17, which are smaller than 360 °.
  • 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 is integrated in the pump housing 2, as can be used, for example, for adjusting the temperature of a floor heating system.
  • 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 pot-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 pressed by a spring 48 in the rest position shown in Fig.
  • valve element 18 in a dissolved Position is in which the lower part 76 is not applied to the bottom of the pump housing 12, so that the valve member 18 is substantially free to rotate about the axis 20.
  • the front end of the rotor shaft 8 which is designed as a coupling 108.
  • the clutch 108 engages with a counter-coupling 1 10, which is arranged non-rotatably on the valve element 18 in engagement.
  • the coupling 108 has tapered coupling surfaces which essentially describe a saw tooth profile along a circumferential line in such a way that torque transmission from the coupling 108 to the counter coupling 110 is possible only in one direction of rotation, namely in the direction of rotation A in FIG. 3.
  • the direction of rotation B is the direction of rotation in which the pump unit in the normal mal plante is driven.
  • 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 counter-coupling 1 10 of the clutch 108 by the pressure in the pressure chamber 26 is disengaged. If the pressure in the pressure chamber 26 increases, a pressure force acting on the cover 78 which opposes and exceeds the spring force of the spring 48, so that the valve element 18 is pressed into the abutting position, which is shown in Fig. 4.
  • 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 a tight contact is achieved, which seals the pressure and 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 1 12, which extends substantially over 90 °. 6 shows a first switching position, in which the opening 1 12 only covers the input 30, so that a flow path is given only from the suction connection 34 to the suction opening 36 and thus to the suction mouth 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 1 12 covers only the input 28, while the input 30 is closed.
  • FIG. 7 now shows an intermediate position in which the opening 1 12 covers both inputs 28 and 30, wherein the input 30 is only partially released.
  • a mixing ratio between the flows be changed from the inputs 28 and 30.
  • 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.
  • Such functionality may be used, for example, in a hydraulic system as shown in FIG.
  • the hydraulic circuit has a heat source 14 in the form of, for example, a gas boiler, whose outlet opens into, for example, the suction connection 34 of the pump housing 12.
  • a floor heating circuit 1 1 6 connects to the pressure port 27 of the centrifugal pump assembly 1, whose return is connected both to the input of the heat source 1 14 and to the suction port 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 14.
  • the floor heating circuit 1 1 6 can be regulated in its flow temperature in such a way that cold water from the return to the hot water on the output side of the heat source 1 14 is mixed, whereby by changing the opening conditions of the inputs 28 and 30 in the above described manner, the mixing ratio can be changed by rotation of the valve element 18h.
  • the second embodiment according to FIGS. 10 to 19 shows a centrifugal pump unit which, in addition to the above-described mixer functionality, also has a switching functionality for the additional supply of a secondary heat exchanger for heating service water.
  • the bearing and the drive of the valve element 18i in this embodiment are the same as in the ninth embodiment.
  • valve element 18i in addition to the opening 1 12 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 , Furthermore, in the valve element 18i, an arcuate bypass opening 126, which is open only to the underside, that is, to the bottom of the lower part 76i and thus to the suction chamber 24, is formed, which is closed to the pressure chamber 26 by the cover 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.
  • FIGS. 15 to 18 wherein in these figures the cover 78i of the valve element 18i is shown partially open in order to clarify the position of the openings below it.
  • FIG. 15 shows a first switching position, in which the opening 1 12 faces the inlet 30, so that a flow connection is produced from the suction connection 34 to the suction mouth 38 of the impeller 14. In the switching position according to FIG.
  • the opening 12 lies 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.
  • a further switching position which shows Fig. 17, the opening 1 12 is located above the input 30, so that in turn a flow connection from the suction port 34 is given to the suction port 38 of the impeller 14.
  • 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 here.
  • the bypass opening 126 simultaneously covers the input 130 and a part of the input 28, so that a connection is also provided from the terminal 128 via the input 130, the bypass opening 126 and the input 28 to the terminal 32.
  • FIG. 18 shows a fourth switching position in which the through-channel 122 completely covers the input 28, so that the connection 32 is connected to the pressure space 26 via the through-channel 122 and the opening 124.
  • the bridging opening 126 only covers the entrance 130.
  • the opening 12 also covers the entrance 30.
  • Such a centrifugal pump unit can be used, for example, in a heating system as shown in FIG. There, the dashed line bounds the centrifugal pump unit 1, as has just been described with reference to FIGS. 10 to 18.
  • the heating system in turn has a primary heat exchanger or a heat source 1 14, 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 comprises a floor heating circuit 1 1 6. The returns of the heating circuit 120 and the floor heating circuit 1 1 6 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 terminal 32 of the pump housing 12 is connected to the flow of the floor heating circuit 1 1 6.
  • the impeller 14 conveys 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 pump unit or the impeller 14 delivers fluid from the port 128, which serves as a suction port, through the pressure port 27 , Via the heat source 1 14 through the secondary heat exchanger 56 and back to the terminal 128.
  • valve element 18i in the third switching position which is shown in Fig. 1 7, in addition the floor heating circuit 1 1 6 is supplied.
  • the suction connection 34 the water flows into the suction mouth 38 of the impeller 14 and is conveyed via the pressure connection 27 via the heat source 14 in the manner described by the first heating circuit 120.
  • the liquid on the output side of the impeller 14 exits from the pressure chamber 26 into the opening 124 and through the passage 122 and thus flows to the port 32 and via this into the underfloor 1 16.
  • the switching position shown in Fig. 17 flows at the same time, via the bridging opening 126, liquid flows via the connection 128 and the inlet 130 into the connection 32.
  • Fig. 18 shows a switching position in which the admixture is switched off and the Terminal 32 is exclusively in communication with the pressure chamber 26 directly. In this state, the water is conveyed in the floor circle 1 1 6 without heat in a circle.
  • both a switching between heating and domestic water heating can be achieved and at the same time the supply of two heating circuits with different temperatures, namely a first heating circuit 120 with the output temperature of Heat source 1 14 and a floor heating circuit 1 16 with a temperature reduced via a mixing function.
  • 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. In a first step, the rotor 6 is rotated in a previously stored angular position or in an angular position, wel in the direction of rotation slightly before the last stored angular position.
  • the rotor can be rotated together with the valve element 18, 18i in a desired second angular position, wherein the control device 1 7 controls the stator 6 so that the rotor 6 rotates in this second mode exactly to the desired angle.
  • the counter coupling 1 10 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 operating 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 counter-coupling 1 10 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 1 10 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 bevels 132 which extend from two end edges 134 which extend substantially diametrically with respect to the axis of rotation X.
  • 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 mating coupling 10 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 essentially of the diameter line and the axis of rotation X. or be clamped to these parallel axes.
  • the side surfaces of the projection 138 come to the engagement surfaces 136 to the plant when the clutch is engaged. In the reverse direction of rotation D, the projection 138 slides on the wedge surfaces 137 under axial displacement.
  • this embodiment of the coupling 108 and the counter-coupling 1 10 there are exactly two offset by 180 ° to each other positions in which the rotor 6 and the valve element 18, 18i can be coupled together.
  • valve element 18, 18i in the exemplary embodiments described above will be described in detail again with reference to FIG.
  • the storage is identical in both embodiments.
  • a fixed axis extends in the direction of the axis of rotation X in the interior of the pump housing 12.
  • the valve element 18, 18i is rotatably mounted.
  • the axis 20 engages in a blind hole 140 in the bottom of the valve element 18, 18i, which faces the impeller 14, a.
  • a seal 142 is arranged, which is on the outer circumference of the axis 20 slidably in abutment. The seal 142 seals the interior of the blind hole 140 to the outside.
  • a lubricant can be arranged to lubricate the slide bearing permanently or pre-lubricate.
  • the seal 142 allows a slight leakage, so that long-term liquid from the pump housing 12, in particular water, can penetrate into the interior of the blind hole 140 and there the lubrication between the valve element 18, 18i and axis 20 is used.
  • the seal 142 is designed so that particles and impurities are retained, so that a permanent ease of storage is ensured.
  • the radial bearing of the valve element 18, 18i takes place on the outer circumference of the spring 48. It is understood, however, that alternatively the radial bearing could also be made directly on the outer circumference of the axis 20, for example in the on the Seal 142 adjacent portion of the storage space or blind hole 140th
  • the axis 20 also has a the impeller 14 facing circumferential shoulder 144, at which the axis 20 tapers. Between this shoulder 144 and the bottom of the blind hole 140, which is located on the impeller 14 facing the end, the spring 48 is supported, whose function has already been described above. In this way, the spring 48 is completely located in the interior of the blind hole 140, which defines the storage space, so that the spring 48 is protected from contamination from the fluid pumped by the Pumpenaggre-.
  • valve element 18, 18i could also be used together with the valve element 18, 18i, if this would be hydraulically coupled instead of the mechanical coupling 108, 110 described above. If the said coupling 108, 110 is omitted, the valve element could instead be rotated by the flow rotated by the impeller 14 in the pressure space 26 by the flow acting on the cover 78, 78i. In addition, in such an embodiment could be stops which define the switching positions of the valve element 18, 18i. The movement between these switching positions could then be achieved by reversing the direction of rotation of the impeller 14.
  • the pump housing 12 which also serves as a valve housing, integrally formed.
  • the pump housing 12 could also be composed of several individual parts or could be designed in several parts.
  • a pump housing separate from the valve housing could be provided, wherein the valve housing accommodates the valve element 18, 18i, while the pressure chamber 26 is formed in the pump 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 électrique, au moins un rotor (14) entraîné par celui-ci, ainsi qu'un corps de pompe (12) qui entoure le rotor (14) et dans lequel est disposé au moins un élément vanne (18, 18i) pouvant tourner entre deux positions de commande, l'élément vanne étant maintenu rotatif sur au moins un palier dans le compartiment intérieur du corps de pompe (12), ledit palier étant disposé dans un compartiment de palier (140) qui est séparé, par l'intermédiaire d'au moins un joint d'étanchéité (142), du reste du compartiment intérieur du corps de pompe (12) qui reçoit un fluide à refouler.
PCT/EP2018/056099 2017-03-14 2018-03-12 Ensemble pompe centrifuge WO2018166979A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17160841.7 2017-03-14
EP17160841.7A EP3376039B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge

Publications (1)

Publication Number Publication Date
WO2018166979A1 true WO2018166979A1 (fr) 2018-09-20

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Citations (5)

* Cited by examiner, † Cited by third party
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
DE1928839A1 (de) * 1968-06-17 1969-12-18 Heinrich Gieselmann Umwaelzpumpe
FR2074692A2 (fr) * 1970-01-19 1971-10-08 Materiel Telephonique Pompe-vanne, en particulier pour le chaffage central
DE9013992U1 (de) 1990-10-08 1991-10-24 Grundfos International A/S, Bjerringbro Motorpumpenaggregat für Kreislaufsysteme mit zwei parallelen Kreisläufen
US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2646212B1 (fr) * 1989-04-21 1994-04-15 Icf Appareil de circulation et de distribution de fluide
DE10207653C1 (de) * 2002-02-22 2003-09-25 Gpm Geraete Und Pumpenbau Gmbh Elektrische Kühlmittelpumpe mit integriertem Ventil, sowie Verfahren zu dessen Steuerung

Patent Citations (5)

* Cited by examiner, † Cited by third party
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
DE1928839A1 (de) * 1968-06-17 1969-12-18 Heinrich Gieselmann Umwaelzpumpe
FR2074692A2 (fr) * 1970-01-19 1971-10-08 Materiel Telephonique Pompe-vanne, en particulier pour le chaffage central
DE9013992U1 (de) 1990-10-08 1991-10-24 Grundfos International A/S, Bjerringbro Motorpumpenaggregat für Kreislaufsysteme mit zwei parallelen Kreisläufen
US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system

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EP3376039B1 (fr) 2021-08-04

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