EP3376051B1 - Pump unit - Google Patents

Description

The invention relates to a pump unit, in particular a centrifugal pump unit, with an electric drive motor and at least one valve device located in a flow path through the pump unit, which valve device can be moved at least between a first and a second switching position.

Pump units are known which contain a valve device which makes it possible to switch between two possible flow paths through which the pump unit delivers. Valve devices are known which switch over depending on the direction of rotation of the centrifugal pump unit or direct the flow into different flow paths depending on the direction of rotation. For example off DE 9013992 U1 such a pump unit is known, which has a switching device, with the help of which it is possible to switch between two inputs of the pump unit in order to selectively suck in liquid from one of the two inputs. The pump unit disclosed there has a relatively complex mechanism, which has an inflow element located on the pressure side, which is subjected to the flow generated by the centrifugal pump unit on the output side and can be moved into two different positions depending on the direction of rotation and thus the direction of flow. A valve element on the suction side of the pump unit is switched between two inlets via a lever system connected to the inflow element.

Out of WO 2016/202723 A1 a pump unit with an integrated valve element is known, in which the valve element surrounds the impeller in a ring shape and can be moved into two different switching positions by the flow generated by the impeller, depending on the direction of rotation.

Out of U.S. 2016/0258340 A1 a cooling water pump unit with an integrated valve element is known, the valve element being movable via an actuating piston. The actuating piston can be pressurized under the control of solenoid valves.

In view of this state of the art, it is the object of the invention to improve a pump unit with an integrated valve device in such a way that a simpler design of the pump unit is achieved while at the same time increasing the reliability of the switching function of the valve device.

This object is achieved by a pump unit with the features specified in claim 1. Preferred embodiments result from the dependent claims, the following description and the attached figures.

The pump unit according to the invention is a centrifugal pump unit. The pump unit has an electric drive motor, which is preferably designed as a wet-running electric drive motor, ie as a canned motor. The pump unit according to the invention can, for example, be designed as a circulating pump for use in a heating and/or air conditioning system. The pump assembly is designed in particular to pump water.

The pump unit has at least one impeller which is driven by the drive motor. Furthermore, a valve device is integrated into the pump unit, which can be moved at least between a first and a second switching position. The valve device is designed in such a way that it provides a valve function for the flow of liquid conveyed through the pump unit.

According to the invention, the valve device is designed in such a way that it can be moved via the electric drive motor of the pump unit, ie the drive motor driving the impeller. For this purpose, the valve device is connected to the drive motor via a first clutch coupled in that the valve device can be moved from the first to the second switching position by a rotary movement of the drive motor. This means that the movement of the drive motor can be transmitted to the valve device by the first clutch, so that the valve device is moved directly or indirectly by the drive motor. If the drive motor is designed so that it can be driven in two directions of rotation, it would be possible according to a preferred embodiment of the invention to also move the valve device back from the second to the first switching position via the corresponding rotary movement of the drive motor. According to the invention, the first clutch is also designed such that it can be released by increasing the speed of the drive motor and/or increasing the pressure on the output side of the impeller and/or slip in such a way that the clutch effect between the drive motor and the valve device is reduced or eliminated. This makes it possible to use the drive motor specifically in certain operating conditions to move the valve device, while in other operating conditions, when z. B. the increased pressure or the increased speed is provided, but not to move the valve device. The valve device is expediently designed such that in the normal operating state of the pump unit, ie when liquid is conveyed by the impeller in normal operation, the clutch is released so that the valve element remains in an assumed switching position in this state.

According to a special embodiment of the invention, a gear can be provided between the drive motor and the valve device, which changes or converts the direction of movement and/or the speed of movement between the drive motor and the valve device. For example, the gear can be designed as a reduction gear, which counteracts a rotational speed of the valve device or of a valve element of the valve device the speed of the drive motor is reduced. Alternatively or additionally, a rotary movement of the drive motor could be converted into a linear movement of the valve element by a gear, such as a spindle drive.

The drive motor is preferably electronically controlled or regulated so that it can be driven at different speeds and/or in different directions of rotation. For this purpose, a control device can be provided which regulates or controls the drive motor in a corresponding manner. In particular, the control device can be equipped with a frequency converter for changing the speed of the drive motor. According to a further preferred embodiment of the invention, the control device is designed so that it not only controls the drive motor in such a way that the drive motor runs at different speeds, but also different acceleration profiles can be implemented when accelerating and/or braking the drive motor.

The configuration according to the invention has the advantage that on the one hand a separate drive motor for the valve device can be dispensed with, but on the other hand complex mechanisms for transmitting a force generated by the flow to a valve element can also be dispensed with. Rather, the power can be transmitted by the first clutch. In addition, the efficiency of the pump unit can be improved since the valve device essentially does not impair normal operation.

According to a preferred embodiment of the invention, at least one stop can be provided which holds the valve device in a defined switching position, for example the first or the second switching position. More preferably, two stops can be provided, each of the two stops having a switching position defined by the valve device and the valve device can be moved between the two switching positions. This movement takes place via the first clutch and by appropriate control of the drive motor, in particular via the control device described.

The valve device preferably has no further electrically actuated switching elements for switching and/or holding the valve device. Rather, the valve device is moved between the switching positions solely by the drive motor.

The pump unit has at least one second releasable coupling between at least one movable part of the valve device and a valve housing surrounding the impeller. This second releasable clutch can be moved from a released first clutch position into a holding clutch position by the pressure on the output side of the impeller. The at least one releasable coupling does not have to act directly on the pump housing, but rather can also act indirectly on the pump housing in a holding manner, in that the coupling engages with a component connected to the pump housing. What is essential in the design of the second releasable coupling is that it prevents movement of the valve device in its holding second coupling position. In this case, the second releasable clutch preferably enters into holding engagement in an operating state of the pump assembly, ie into its holding second clutch position, in which the first clutch reaches its released position. Thus, in an operating state of the drive motor, in particular an operating state with a lower speed and/or lower acceleration, the valve device can be moved into a desired switching position. It can then be achieved by increasing the speed and/or, in particular, strong acceleration of the drive motor that the second releasable clutch engages in a holding manner occurs, so that the valve device remains and is held in the switching position reached. At the same time, the first clutch preferably disengages or slips, which allows the second rotation of the drive motor with the impeller.

The first and the second clutch are preferably designed in such a way that the first clutch has a lower holding force in its released position than the second clutch in its holding second clutch position. Conversely, the first clutch preferably has a greater holding force in its engaged position than the second clutch in its released first clutch position. This means that the first clutch, when engaged, can transmit greater force or torque than the second clutch in its released first clutch position. In this switching state, the valve element can be moved between the switching positions. If the first clutch is in its released position and the second clutch is in its holding clutch position, the second clutch can transmit a greater force or torque than the first clutch, so that the valve device is held in the switching position it has reached and not by the Drive motor can be moved via the first clutch.

The drive motor is also preferably designed in such a way that during operation of the pump assembly it generates a torque which is greater than the holding force of the first clutch in its coupled position. This prevents the first clutch from preventing the drive motor and thus the impeller from rotating during normal operation of the pump assembly.

The valve device can preferably be embodied as a switching valve, which enables switching between two flow paths. Alternatively or additionally, the valve device Be mixing device, in which fluid is mixed from two flow paths, wherein the mixing device is designed such that the mixing ratio is different in the two switching positions of the valve device. When configured as a mixing device, the valve device preferably has more than two switching positions, and can be movable, for example, between two switching positions that define the end positions, in a number of stages or continuously. The use as a switching valve can be used, for example, in a heating system in which a switching valve is required to switch a heat transfer medium flow between a heat exchanger for heating service water and at least one heating circuit for heating a building. A mixing device can also be used in a heating system, for example in order to reduce the temperature of a heat transfer medium by admixing liquid from a return of the heating system. This can e.g. B. be useful for use for underfloor heating, in which it is usually necessary to reduce the flow temperature provided by a boiler by adding heat carrier from the return.

The valve means can preferably provide a valve function in a flow path on the suction side of the impeller and/or a valve function in a flow path on the pressure side of the impeller. The valve device can be arranged in particular as a switching device on the suction side, so that depending on the switching position of the valve device, the impeller sucks in liquid from a first or a second flow path on the suction side. Alternatively, a switchover device could be arranged on the pressure side, so that the pump assembly pumps into a first or a second flow path on the pressure side, depending on the switching position of the valve device. If the valve device is designed as a mixing device, it can be arranged, for example, on the pressure side in such a way that on the pressure side, two flow paths in the mixing device open into a mixing point and that the mixing ratio between the two flow paths is changed depending on the switching position of the valve device. In this case, one of the two flow paths preferably runs downstream of the pump unit through a heat exchanger of a heating or cooling device in order to temper the liquid delivered by the pump unit, ie to heat or cool it. In the other flow path there is preferably non-temperature-controlled liquid, which can then be mixed with the temperature-controlled liquid in the mixing device. Alternatively, a mixing device could also be arranged on the suction side of the pump unit, so that the pump unit z. B. draws in a liquid mixed from two flow paths.

According to a further preferred embodiment, the valve device has at least one movable valve element and stop elements which define the first and the second switching position and of which at least one is preferably adjustable in its position. The adjustability of one or more stop elements makes it possible to regulate the end positions or the switching positions of the valve device. The stop elements prevent the valve device or the valve element from being moved beyond the desired switching position. The stop element thus leads to a positive engagement between the valve element and the stop element, so that further movement of the valve element is prevented.

According to a further preferred embodiment of the invention, the valve device has at least one movable valve element which interacts with two valve openings in such a way that a first valve opening is more covered by the valve element in the first switching position of the valve device than in the second Switching position and a second valve opening is covered by the valve element in the second switching position more than in the first switching position. If the valve element is designed as a switching valve, the second valve opening is open and the first valve opening is closed in the first switching position. Conversely, in the second switching position, the second valve opening is closed and the first valve opening is open. If the valve device is designed as a mixing device, intermediate positions or intermediate switching positions are preferably possible, in which the two valve openings are open simultaneously, but to different extents. A mixing ratio can be changed by changing the degree of opening of the two valve openings. The at least one movable valve element is preferably designed in such a way that when one valve opening is opened by a certain amount, the other valve opening is simultaneously closed by the same amount.

Such an interaction of the closing of the two valve openings can be realized with one valve element, but also with two valve elements if these are mechanically coupled to one another.

According to a further preferred embodiment, the valve device has a movable valve element, which has at least one sealing surface and one pressure surface, the pressure surface being connected to a pressure chamber surrounding the impeller in such a way that the valve element is counteracted by the pressure acting on the pressure surface with the sealing surface a contact surface is pressed, the contact surface preferably forming a valve seat. In such a configuration, the valve element, together with the contact surface, can assume the function of the second clutch described above. When the valve element is pressed against the contact surface by the pressure in the pressure chamber, between the sealing surface and the contact surface preferably such a friction fit that the valve element is fixed in the switching position reached. This frictional connection could also be supported by a positive connection with a corresponding configuration of the sealing surface and contact surface. If the system is a valve seat, a seal is achieved at the same time via the system of the sealing surface. If the pressure in the pressure chamber is lower, the sealing surface preferably disengages from the contact surface or preferably from a valve seat, so that easy mobility of the valve element with reduced friction is ensured. The valve seats may preferably surround valve openings as previously described. The contact of the at least one sealing surface then seals off the flow paths to the outside. Furthermore, a sealing surface can also be pressed against a contact surface or a valve seat in such a way that the contact achieves a seal between the suction chamber and the pressure chamber of the pump assembly. Thus, several valve seats can be provided, on which one or more sealing surfaces of the valve element come into contact with a sufficiently high pressure in the pressure chamber in order to achieve the necessary sealing of the flow paths. A restoring element, for example a restoring spring, can preferably be provided, which disengages the valve element from the contact surface with the sealing surface when the pressure in the pressure chamber falls below a predetermined value, i.e. the force generated by the pressure in the pressure chamber on the pressure surface is lower becomes the restoring force generated by the restoring element. This ensures easy mobility of the valve element at low pressure.

The valve device can more preferably have a rotatable valve element. That is to say, the valve element is moved between the switch positions by a rotating movement, with the axis of rotation more preferably being aligned with the axis of rotation of the impeller or of the drive motor aligned, which allows a particularly simple coupling without additional transmission means. The rotatable valve element is preferably releasably coupled to a rotor of the drive motor via the first coupling, with the coupling not having to act on the actual magnet rotor but also on a component connected to the magnet rotor, such as a shaft or the impeller. When the first clutch is engaged, the rotatable valve element is rotated by the rotor of the drive motor.

The drive motor can preferably be driven in two directions of rotation and the valve device is designed such that its first switch position is reached by driving the drive motor in a first direction of rotation and its second switch position is reached by driving the drive motor in a second direction of rotation. Instead of a movement of the valve element by the drive motor in two directions of rotation, a restoring means or force-generating means can also be provided, which rotates the valve element back into a predetermined starting position or switching position when the drive motor is switched off. This can be, for example, a magnetic restoring means, a restoring means acting by spring force or by gravity.

The first and/or the second clutch can preferably be a friction clutch, a magnetic clutch and/or a hydraulic clutch, which more preferably exhibit slip. If the first clutch slips, this allows the drive motor to continue rotating after a predetermined switching position has been reached, when the valve element of the valve device or the valve device is fixed in the switching position, without being blocked by the fixing of the valve device. For example, a valve element can hit a stop, whereupon the clutch then slips or the drive motor can continue to turn due to the slippage in the clutch. Especially preferred a hydraulic coupling can be realized via the liquid conveyed by the impeller. Thus, the liquid can be set in rotation by the impeller inside a pump housing in the direction of rotation of the impeller and can move this via the friction on a part of the valve device, in particular directly on the valve element. When the valve element or the valve device reaches a switching position and is fixed there, the hydraulic flow continues, with the usual hydraulic friction losses occurring only on the surfaces. In other words, to move the valve device, it is essentially possible to use energy loss which is present anyway and is converted into a movement of the valve device or the valve element.

More preferably, the first clutch has at least one clutch element that can be moved between a clutched and a released position, the direction of movement between the clutched and the released position preferably running transversely to a force direction of the force to be transmitted from the clutch to the valve device. In the coupled position, there is a non-positive and/or positive engagement between the coupling element and an opposite coupling surface. The clutch element can be moved in such a way that it can disengage from the clutch surface, so that the valve element is then no longer moved or carried along and remains in its switched position. The direction of movement between the coupled and released position is preferably in a direction deviating from the direction of force transmission, which ensures that the coupling element is not moved out of engagement by the force to be transmitted. The direction of movement particularly preferably runs normal to the direction of force or to a plane in which the direction of force runs. The latter can be the case, for example, when the clutch is used to transmit torque. Then the direction of movement runs preferably along the axis of rotation and thus transverse and in particular normal to the plane in which the force is transmitted.

A valve element of the valve device can particularly preferably form the movable coupling element at the same time. Thus, the valve element can have a coupling surface, which can engage with an opposite coupling surface, which is preferably arranged on the rotor or impeller, in order to move the valve element, in particular to move it in rotation. In this case, a non-positive and/or positive engagement can be provided. Furthermore, the coupling element can expediently be acted upon by a prestressing force, which forces the coupling element into the coupled position. This means that in the rest position the first clutch is engaged. This engagement is then preferably disengaged by the pressure occurring in the pressure chamber or by a higher speed of the drive motor. When the drive motor is switched off, this force disengaging the clutch is removed, so that the biasing force forces the clutch back into the engaged position.

More preferably, the coupling element has a pressure surface which is connected to a pressure chamber surrounding the impeller and is arranged in such a way that a pressure acting on the pressure surface generates a force which is directed in the opposite direction to the prestressing force. When the pressure in the pressure chamber increases to such an extent that the pressure force generated at the pressure surface exceeds the preload force, the clutch element is displaced, being arranged so that on this displacement it is moved to its released position, ie the first clutch engages disengaged and the valve element is no longer moved by the drive motor, but remains in its adopted switching position. When the pressure decreases, for example when the pump unit is switched off is released, the pushing force decreases and the preloading force becomes the larger force again, so that the clutch is moved to the coupled position again. The next time the drive motor starts up, the valve element or the valve device can then be moved back into another switching position.

According to a further preferred embodiment of the invention, the clutch element can have a clutch surface which, in the coupled position, is in frictional contact with a counter-coupling surface, the clutch surface and the counter-coupling surface being designed in such a way and being surrounded by a lubricant that between the clutch surface and the counter - When the speed of the drive motor increases, the clutch surface forms a lubricating film that eliminates the frictional contact. The liquid conveyed by the pump unit, for example water, is preferably used as the lubricant. The clutch then functions in the manner of a slide bearing. At a sufficiently high speed, a lubricating film forms between the clutch surface and the mating clutch surface, so that the frictional contact between the surfaces is eliminated and they slide over one another in the manner of a sliding bearing. In this way, a clutch can be created which is disengaged by increasing the speed. That is, when the drive motor is moved at a low speed, the valve element or the valve device is moved via the frictional contact between the coupling surface and the counter-coupling surface, which is located between the rotor and the valve device or the valve element, so that the switching position is changed can be. The speed of the drive motor can then be increased to such an extent that the frictional contact is eliminated as described and the valve device remains in the switching position that has been reached.

If a purely hydraulic coupling is used between the drive motor and the valve device, disengagement can be achieved by hydraulic slippage, in which case the valve device is then preferably fixed in the desired switching position in the manner described above by a second clutch. With such a configuration, it is possible to keep the valve element in its initial position when the drive motor accelerates accordingly, without it being moved by the hydraulic clutch. This can be achieved by accelerating the drive motor so quickly that a pressure build-up which moves the second clutch into the coupled clutch position occurs so quickly that the second clutch engages before there is displacement of the valve element and thus there is a change in the switching position of the valve device.

Fig. 1

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer ersten Ausführungsform der Erfindung,

Fig. 2

eine perspektivische Ansicht der Unterseite des Ventilelementes des Kreiselpumpenaggregates gemäß Fig. 1,

Fig. 3

eine perspektivische Ansicht des Pumpengehäuses des Kreiselpumpenaggregates gemäß Fig. 1 im geöffneten Zu-stand,

Fig. 4

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 1,

Fig. 5

eine Schnittansicht des Pumpengehäuses des Kreiselpumpenaggregates gemäß Fig. 4 mit dem Ventilelement in einer ersten Schaltstellung,

Fig. 6

eine Schnittansicht entsprechend Fig. 5 mit dem Ventilelement in einer zweiten Schaltstellung,

Fig. 7

schematisch den hydraulischen Aufbau mit einer Heizungsanlage mit einem Kreiselpumpenaggregat gemäß Fig. 1 bis 6,

Fig. 8

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer zweiten Ausführungsform der Erfindung,

Fig. 9

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 8 mit dem Ventilelement in einer ersten Position,

Fig. 10

eine Schnittansicht entsprechend Fig. 9 mit dem Ventilelement in einer zweiten Position,

Fig. 11

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer dritten Ausführungsform der Erfindung,

Fig. 12

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 11 mit dem Ventilelement in einer ersten Position,

Fig. 13

eine Schnittansicht entsprechend Fig. 12 mit dem Ventilelement in einer zweiten Position,

Fig. 14

eine Explosionsansicht eines Pumpengehäuses mit einem Ventilelement gemäß einer vierten Ausführungsform der Erfindung,

Fig. 15

eine Schnittansicht eines Kreiselpumpenaggregates gemäß der vierten Ausführungsform der Erfindung,

Fig. 16

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer fünften Ausführungsform der Erfindung,

Fig. 17

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 16 mit dem Ventilelement in einer ersten Position,

Fig. 18

eine Schnittansicht entsprechend Fig. 17 mit dem Ventilelement in einer zweiten Position,

Fig. 19

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer sechsten Ausführungsform der Erfindung,

Fig. 20

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 19,

Fig. 21

eine Draufsicht auf das geöffnete Pumpengehäuse des Kreiselpumpenaggregates gemäß Fig. 19 und 20 mit dem Ventilelement in einer ersten Schaltstellung,

Fig. 22

eine Draufsicht entsprechend Fig. 21 mit dem Ventilelement in einer zweiten Schaltstellung,

Fig. 23

eine Explosionsansicht eines Pumpengehäuses mit einem Ventilelement gemäß einer siebten Ausführungsform der Erfindung,

Fig. 24

eine Explosionsansicht des Pumpengehäuses mit Ventilelement gemäß der siebten Ausführungsform von einer anderen Seite her gesehen,

Fig. 25

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer achten Ausführungsform der Erfindung,

Fig. 26

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 25,

Fig. 27

eine Draufsicht auf das geöffnete Pumpengehäuse des Kreiselpumpenaggregates gemäß Fig. 25 und 26 mit dem Ventilelement in einer ersten Schaltstellung,

Fig. 28

eine Ansicht gemäß Fig. 27 mit dem Ventilelement in einer zweiten Schaltstellung,

Fig. 29

eine Explosionsansicht des Kreiselpumpenaggregates gemäß einer neunten Ausführungsform der Erfindung,

Fig. 30

eine perspektivische Ansicht des Kreiselpumpenaggregates gemäß Fig. 29 mit abgenommenem Pumpengehäuse und Ventilelement,

Fig. 31

eine perspektivische Ansicht der Motorwelle des Kreiselpumpenaggregates gemäß Fig. 29 und 30 sowie des Kupplungsteils des Ventilelementes,

Fig. 32

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 29 mit dem Ventilelement in einer ersten Position,

Fig. 33

eine Schnittansicht gemäß Fig. 32 mit dem Ventilelement in einer zweiten Position,

Fig. 34

eine Draufsicht auf das geöffnete Pumpengehäuse des Kreiselpumpenaggregates gemäß Fig. 29 bis 33 mit dem Ventilelement in einer ersten Schaltstellung,

Fig. 35

eine Ansicht gemäß Fig. 34 mit dem Ventilelement in einer zweiten Schaltstellung,

Fig. 36

eine Ansicht gemäß Fig. 34 und 35 mit dem Ventilelement in einer dritten Schaltstellung,

Fig. 37

schematisch den hydraulischen Aufbau einer Heizungsanlage mit einem Kreiselpumpenaggregat gemäß Fig. 29 bis 36,

Fig. 38

eine Explosionsansicht eines Kreiselpumpenaggregates gemäß einer zehnten Ausführungsform der Erfindung,

Fig. 39

eine perspektivische Ansicht des geöffneten Ventilelementes des Kreiselpumpenaggregates gemäß Fig. 38,

Fig. 40

eine perspektivische Ansicht des geschlossenen Ventilelementes gemäß Fig. 39,

Fig. 41

eine Schnittansicht des Kreiselpumpenaggregates gemäß Fig. 38 mit dem Ventilelement in einer ersten Position,

Fig. 42

eine Schnittansicht gemäß Fig. 41 mit dem Ventilelement in einer zweiten Position,

Fig. 43

eine Draufsicht auf das geöffnete Pumpengehäuse des Kreiselpumpenaggregates gemäß Fig. 38 bis 42 mit dem Ventilelement in einer ersten Schaltstellung,

Fig. 44

eine Ansicht gemäß Fig. 43 mit dem Ventilelement in einer zweiten Schaltstellung,

Fig. 45

eine Ansicht gemäß Fig. 43 und 44 mit dem Ventilelement in einer dritten Schaltstellung,

Fig. 46

eine Ansicht gemäß Fig. 43 bis 45 mit dem Ventilelement in einer vierten Schaltstellung und

Fig. 47

schematisch den hydraulischen Aufbau einer Heizungsanlage mit einem Kreiselpumpenaggregat gemäß Fig. 38 bis 46.

The invention is described below by way of example with reference to the accompanying figures. In these shows:

1

an exploded view of a centrifugal pump unit according to a first embodiment of the invention,

2

a perspective view of the underside of the valve element of the centrifugal pump unit according to 1 ,

3

a perspective view of the pump housing of the centrifugal pump unit according to 1 in the open state,

4

a sectional view of the centrifugal pump unit according to FIG 1 ,

figure 5

a sectional view of the pump housing of the centrifugal pump unit according to FIG 4 with the valve element in a first switching position,

6

a sectional view accordingly figure 5 with the valve element in a second switching position,

7

Schematically the hydraulic structure with a heating system with a centrifugal pump unit according to Figures 1 to 6 ,

8

an exploded view of a centrifugal pump unit according to a second embodiment of the invention,

9

a sectional view of the centrifugal pump unit according to FIG 8 with the valve element in a first position,

10

a sectional view accordingly 9 with the valve element in a second position,

11

an exploded view of a centrifugal pump unit according to a third embodiment of the invention,

12

a sectional view of the centrifugal pump unit according to FIG 11 with the valve element in a first position,

13

a sectional view accordingly 12 with the valve element in a second position,

14

an exploded view of a pump housing with a valve element according to a fourth embodiment of the invention,

15

a sectional view of a centrifugal pump unit according to the fourth embodiment of the invention,

16

an exploded view of a centrifugal pump unit according to a fifth embodiment of the invention,

17

a sectional view of the centrifugal pump unit according to FIG 16 with the valve element in a first position,

18

a sectional view accordingly 17 with the valve element in a second position,

19

an exploded view of a centrifugal pump unit according to a sixth embodiment of the invention,

20

a sectional view of the centrifugal pump unit according to FIG 19 ,

21

a top view of the opened pump housing of the centrifugal pump unit according to FIG 19 and 20 with the valve element in a first switching position,

22

a top view accordingly 21 with the valve element in a second switching position,

23

an exploded view of a pump housing with a valve element according to a seventh embodiment of the invention,

24

an exploded view of the pump housing with valve element according to the seventh embodiment seen from another side,

25

an exploded view of a centrifugal pump unit according to an eighth embodiment of the invention,

26

a sectional view of the centrifugal pump unit according to FIG 25 ,

27

a top view of the opened pump housing of the centrifugal pump unit according to FIG 25 and 26 with the valve element in a first switching position,

28

a view according to 27 with the valve element in a second switching position,

29

an exploded view of the centrifugal pump unit according to a ninth embodiment of the invention,

30

a perspective view of the centrifugal pump unit according to FIG 29 with removed pump housing and valve element,

31

a perspective view of the motor shaft of the centrifugal pump unit according to 29 and 30 and the coupling part of the valve element,

32

a sectional view of the centrifugal pump unit according to FIG 29 with the valve element in a first position,

Figure 33

a sectional view according to FIG 32 with the valve element in a second position,

34

a top view of the opened pump housing of the centrifugal pump unit according to FIG Figures 29 to 33 with the valve element in a first switching position,

Figure 35

a view according to 34 with the valve element in a second switching position,

Figure 36

a view according to 34 and 35 with the valve element in a third switching position,

37

Schematically the hydraulic structure of a heating system with a centrifugal pump unit according to Figures 29 to 36 ,

38

an exploded view of a centrifugal pump unit according to a tenth embodiment of the invention,

Figure 39

a perspective view of the open valve element of the centrifugal pump unit according to 38 ,

figure 40

a perspective view of the closed valve element according to FIG Figure 39 ,

Figure 41

a sectional view of the centrifugal pump unit according to FIG 38 with the valve element in a first position,

Figure 42

a sectional view according to FIG Figure 41 with the valve element in a second position,

Figure 43

a top view of the opened pump housing of the centrifugal pump unit according to FIG 38 to 42 with the valve element in a first switching position,

Figure 44

a view according to Figure 43 with the valve element in a second switching position,

Figure 45

a view according to 43 and 44 with the valve element in a third switching position,

Figure 46

a view according to Figures 43 to 45 with the valve element in a fourth switching position and

Figure 47

Schematically the hydraulic structure of a heating system with a centrifugal pump unit according to Figures 38 to 46 .

The exemplary embodiments of the pump unit according to the invention in the form of a centrifugal pump unit 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 unit according to the first embodiment of the invention has a motor housing 2 in which an electric drive motor is arranged. In a known manner, this has a stator 4 and a rotor 6 which is arranged on a rotor shaft 8 . The rotor 6 rotates in a rotor space, which of the Stator space, in which the stator 4 is arranged, is separated by a can or a can 10 . This means it is a wet-running electric drive motor. At one axial end, the motor housing 2 is connected to a pump housing 12 in which an impeller 14 rotatably connected to the rotor shaft 8 rotates.

An electronics housing 16 is arranged on the axial end of the motor housing 2 opposite the pump housing 12 and contains control electronics or a control device for controlling the electric drive motor in the pump housing 2 . The electronics housing 16 could also be arranged on another side of the stator housing 2 in a corresponding manner.

In addition, a valve device with a movable valve element 18 is arranged in the pump housing 12 . This valve element 18 is rotatably mounted on an axis 20 inside the pump housing 12 in such a way that the axis of rotation of the valve element 18 is aligned with the axis of rotation X of the impeller 14 . The axis 20 is fixed in a rotationally fixed manner on the bottom of the pump housing 12 . The valve element 18 is not only rotatable about the axis 20, but also movable to a certain extent in the longitudinal direction X. This linear mobility is limited in one direction by the pump housing 12, against which the valve element 18 abuts with its outer circumference. In the opposite direction, the movability is limited by the nut 22, with which the valve element 18 is fastened on the axle 20. It is to be understood that instead of the nut 22, a different axial fastening of the valve element 18 on the axle 20 could also be selected.

The valve element 18 separates a suction chamber 24 from a pressure chamber 26 in the pump housing 12. In the pressure chamber 26 rotates the impeller 14. The pressure chamber 26 is connected to the pressure connection or pressure connection 28 of the centrifugal pump unit, which forms the outlet of the centrifugal pump unit. Two inlets 28 and 30 on the suction side open into the suction chamber 24 , of which the inlet 28 is connected to a first suction connection 32 and the inlet 30 is connected to a second suction connection 34 of the pump housing 12 .

The valve element 18 is disk-shaped and at the same time assumes the function of a conventional deflector plate, which separates the suction chamber 24 from the pressure chamber 26 . The valve element 18 has a central suction opening 36 which has a projecting peripheral collar which engages the suction mouth 38 of the impeller 14 and is in substantial sealing abutment with the suction mouth 38 . Facing the impeller 14, the valve element 18 is designed to be essentially smooth. On the side facing away from the impeller 14, the valve element has two ring-shaped sealing surfaces 40, which in this exemplary embodiment are located on closed tubular sockets. The two annular sealing surfaces 40 are arranged in two diametrically opposite positions on the sealing element 18 with respect to its axis of rotation X, so that they can come into tight contact in the peripheral area of the inlets 28 and 30 on the bottom of the pump housing 12 in order to close the inlets 28 and 30. be. Arranged in an angular position 90° offset from the sealing surfaces 40 are supporting elements 42, which can also come into contact with the peripheral area of the inlets 28, 30, but are spaced apart from one another in such a way that they then do not close the inlets 28, 30. The inlets 28 and 30 do not lie on a diameter line with respect to the axis of rotation X, but rather on a radially offset straight line, so that when the valve element 18 rotates about the axis of rotation X in a first switching position, the inlet 38 is closed by a sealing surface 40, while the support elements 42 lie at the entrance 30 and open it. In a second switching position, the input 30 is of a Sealing surface 40 closed, while the support elements 42 rest in the peripheral area of the input 28 and open it. The first switch position, in which inlet 38 is closed and inlet 30 is open, is in figure 5 shown. The second switch position, in which input 30 is closed and input 28 is open, is in 6 shown. This means that by turning the valve element by 90° around the axis of rotation X, it is possible to switch between the two switch positions. The two switching positions are limited by a stop element 44 which alternately strikes two stops 46 in the pump housing 12 .

In a rest position, i.e. when the centrifugal pump unit is not in operation, a spring 48 presses the valve element 18 into a released position in which the outer circumference of the valve element 18 is not tight against the pump housing 12 and the sealing surfaces 40 are not tight in the peripheral area of the inlets 28 and 30 abut so that the valve element 18 can rotate about the axis 20. If the drive motor is rotated by the control device 17 in the electronics housing 16 so that the impeller 14 rotates, a circulating flow is generated in the pressure chamber 26 which rotates the valve element 18 in its direction of rotation via friction. This means that a first hydraulic clutch is formed between the drive motor and the valve element via the rotating flow. The control device 17 is designed in such a way that it can selectively drive the drive motor in two directions of rotation. Depending on the direction of rotation of the impeller 14, the valve element 18 can also be moved about the axis of rotation X in two directions of rotation via the flow set in rotation by the impeller 14, since the flow in the peripheral region of the impeller 14 always runs in its direction of rotation. The valve element 18 can thus be rotated between the two switch positions delimited by the stops 46 .

When the impeller 14 rotates at a sufficient speed, a pressure builds up in the pressure chamber 26, which generates a compressive force on the surface of the valve element 18 which surrounds the suction opening 36, which is opposed to the spring force of the spring 48, so that the valve element 18 is moved against the spring force of the spring 48 in the axial direction X in such a way that it comes into sealing contact on its outer circumference with an annular bearing shoulder 50 on the pump housing 12 . At the same time, depending on the switching position, one of the sealing surfaces 40 comes into sealing contact on the circumference of one of the inlets 28 and 30, so that one of the inlets 28, 30 is closed. The support elements 42 come into contact with the other inlet, so that this inlet remains open and a flow path is provided from this inlet 28, 30 to the suction opening 36 and from there into the interior of the impeller 14. The contact of the valve element 18 on the contact shoulder 50 and the sealing surface 40 in the peripheral area of one of the inlets 28, 30 creates a frictional contact between the valve element 18 and the pump housing 12 at the same time. This frictional contact forms a second clutch which fixes the valve element. This frictional contact ensures that the valve element 18 is held in the switching position it has reached. This makes it possible to take the drive motor out of operation again for a short time and to put it back into operation in the opposite direction of rotation without the valve element 18 being rotated. If the engine is switched off and restarted quickly enough, the pressure in the pressure chamber 26 does not decrease to such an extent that the valve element 18 can move again in the axial direction into its released position. During operation of the centrifugal pump unit, this makes it possible to always drive the impeller in its preferred direction of rotation, for which the blades are designed, and to use the opposite direction of rotation only to move the valve element 18 in the opposite direction of rotation. When the valve element 18 is in its seated position, in which a frictional seat is given and the second clutch thus formed is engaged, the impeller 14 can continue to rotate. The flow continues in the pressure chamber 26 without the valve element 18 also rotating. This means that the hydraulic first clutch formed between the impeller 14 and the valve element 18 is disengaged due to slippage.

The centrifugal pump unit described, according to the first embodiment of the invention, can be used, for example, in a heating system as shown in 7 is shown. Such a heating system is usually used in apartments or residential buildings and is used to heat the building and to provide heated service water. The heating system has a heat source 52, for example in the form of a gas boiler. There is also a heating circuit 54 which, for example, runs through various radiators in a building. In addition, a secondary heat exchanger 56 is provided, via which process water can be heated. In such heating systems, a switching valve is usually required, which directs the flow of heat transfer medium either through the heating circuit 54 or the secondary heat exchanger 56 . With the centrifugal pump unit 1 according to the invention, this valve function is taken over by the valve element 18 which is integrated into the centrifugal pump unit 1 . The control is carried out by the control device 17 in the electronics housing 16. The heat source 52 is connected to the pressure connection 27 of the pump housing 12. A flow path 58 is connected to the suction port 32 , while a flow path 60 through the heating circuit 54 is connected to the suction port 34 . Depending on the switching position of the valve element 18, it is possible to switch between the flow path 58 through the secondary heat exchanger 56 or the flow path 60 through the heating circuit 54, without a valve having an additional drive being required.

The second embodiment according to Figures 8 to 10 differs from the first exemplary embodiment in the structure of the valve element 18'. In this exemplary embodiment too, the valve element 18' separates the pressure chamber 26 from a suction chamber 24 of the pump housing 12. The valve element 18 has a central suction opening 36', into which the suction mouth 38 of the impeller 14 engages in a sealing manner. Opposite the suction opening 36, the valve element 18' has an opening 62 which, depending on the switching position of the valve element 18', can optionally be brought to coincide with one of the inlets 28, 30. In this exemplary embodiment, the inputs 28', 30' differ in their shape from the inputs 28, 30 according to the previous embodiment. The valve element 18' has a central projection 64 which engages in a central hole 60 in the bottom of the pump housing 12 and is mounted there so as to rotate about the axis of rotation X. At the same time, the projection 64 in the hole 66 also allows an axial movement along the axis of rotation X, which is limited in one direction by the bottom of the pump housing 12 and in the other direction by the impeller 14. On its outer circumference, the valve element 18 ′ has a pin 68 which engages in a semi-circular groove 70 on the bottom of the pump housing 12 . The ends of the groove 70 serve as stop surfaces for the pin 68 in the two possible switching positions of the valve element 18', with the opening 62 being above the inlet 28' in a first switching position and the opening 62 being above the inlet 30' in a second switching position and the respective other input is closed by the base of the valve element 18'. The rotational movement of the valve element 18' between the two switch positions also takes place in this exemplary embodiment by the flow caused by the impeller 14 in the pressure chamber 26, which flow forms a first hydraulic clutch. In order to transfer this even better to the valve element 18 ′, it is provided with projections 72 directed in the pressure chamber 26 . When the centrifugal pump unit 1 is taken out of operation is, the spring 48 presses the valve element 18' in the in 10 released position shown clear of the ground in the perimeter of the entrances 28' and 30'. Ie the second clutch is released. In this position, the valve element 18′ abuts axially with a central pin 74 on the end face of the motor shaft 8 and is limited in its axial movement by this stop. If the pressure in the pressure chamber 26 is sufficiently high, the valve element 18 'in the in 9 shown applied position, in which the valve element 18 'at the bottom of the pump housing 12 in the peripheral area of the inputs 28' and 30 'comes to rest and at the same time the pin 24 is lifted from the end face of the rotor shaft 8. Ie the second clutch is engaged. In this position, the impeller 14 then rotates during normal operation of the circulating pump assembly. Ie the hydraulic first clutch is disengaged due to slip.

The third embodiment according to Figures 11 to 13 shows another possible embodiment of the valve element 18". This embodiment differs from the previous embodiments in the structure of the valve element 18". This is designed as a valve drum. The pump housing 12 essentially corresponds to the structure shown in FIG Figures 1 to 6 , wherein in particular the arrangement of the inputs 28 and 30 corresponds to the arrangement described with reference to the first exemplary embodiment. The valve drum of the valve element 18" consists of a pot-shaped lower part, which is closed by a cover 78. The cover 78 faces the pressure chamber 26 and has the central suction opening 36, which engages in the suction mouth 38 of the impeller 14 with its axially directed collar On the opposite side, the bottom of the lower part 36 has an inlet opening 80 which, depending on the switch position, is brought to coincide with one of the inlets 28, 30, while the respective other inlet 28, 30 is closed by the bottom of the lower part 26 . The valve element 18" is rotatable on an axis 20 mounted, which is fixed in the bottom of the pump housing 12, wherein the axis of rotation, which is defined by the axis 20, the axis of rotation X of the impeller 14 corresponds. In this exemplary embodiment, too, the valve element 18" can be displaced axially along the axis 20 by a certain amount, with a spring 48 also being provided here which, in the rest position, moves the valve element 18" into its in 13 shown released position presses. In this way, a releasable second coupling for holding the valve element 18" is also created here. The released axial position is also limited in this exemplary embodiment by the nut 22. In the released position, the valve element 18" is, as described above, by the flow which caused by the impeller 14, rotatably, i.e. a hydraulic coupling (first coupling) is established between impeller 14 and valve element 18" as previously described. In the abutting position shown in 12 is shown, depending on the switching position, one of the inputs 28, 30 is tightly closed. On the other hand, there is also a seal between the suction chamber 24 and the pressure chamber 26 through the contact of the valve element 18" with the contact shoulder 50.

In this exemplary embodiment, the mounting of the valve element 18" on the axle 20 is also encapsulated by two sleeves 82 and 84, so that these areas are protected from contamination by the fluid being pumped and can be lubricated beforehand if necessary. to ensure the easy rotation of the valve element 18" by the flow caused by the impeller 14. It is to be understood that the bearing could also be correspondingly encapsulated in the other exemplary embodiments described here.

14 and 15 12 show a fourth embodiment in which the structure of the pump housing 12 is the same as that of the pump housing 12 according to the first and third embodiments is equivalent to. In this exemplary embodiment, the rotational movement of the valve element 18c is supported by the flow on the suction side, ie the flow entering the suction mouth 38 of the impeller 14 . Since, in a circulatory system in which a centrifugal pump unit as described here is used, the suction-side flow is also generated by the centrifugal pump unit, an indirect coupling of the impeller 14 to the valve element 18c is also created via the suction-side flow, which represents the first hydraulic clutch. In this exemplary embodiment, too, the valve element 18c is essentially drum-shaped and has a cover 28 facing the pressure chamber 26 with the central suction opening 36, which engages with the suction mouth 38, as described above. The lower part 76b shown here has two inlet openings 80 which, depending on the switching position, can be brought to overlap with one of the inlets 28, 30, the respective other inlet 28, 30 being sealed tightly by the bottom of the lower part 46b, as in the previous embodiment has been described. Between the lower part 76b and the cover 78 there is arranged a guide wheel 86 with vanes, into which the flow from the inlet openings 80 enters radially and exits axially to the central suction opening 36 . The vanes of the guide wheel 86 also generate a torque about the axis 20, by means of which the valve element 18c can be moved between the switching positions. This works essentially as described above. A spring 48 as described above may also be additionally provided to move the valve element 18c to a released position. Since the shape of the blades of guide wheel 86 always generates a torque in the same direction, regardless of the direction in which impeller 14 rotates, in this exemplary embodiment the restoring movement is carried out by a weight 88. During operation, the centrifugal pump unit is always in the installed position , what a 15 is shown in which the axis of rotation X extends horizontally. When the centrifugal pump unit is switched off, the valve element 18c always rotates about the axis 20 in such a way that the weight 88 is at the bottom. The torque generated by the guide wheel 86 allows the valve element 18c to be rotated against this restoring force generated by the weight 88, and by very rapid activation of the drive motor in the pressure chamber 26 a pressure can be built up so quickly that the valve element 18c moves into its adjacent position occurs, as described above, in which it is held non-rotatably on the pump housing 12 without being moved out of its rest position. This means that a second clutch, as described above, is also implemented here. It is to be understood that a return of the valve element by gravity or another restoring force could also be used in the other exemplary embodiments described here, independently of the drive. When the valve member 18c is in the applied position, the first clutch formed by the stator 86 slips out of engagement, i.e. flow continues through the stator but without being able to cause rotation of the valve member 18c.

The fifth embodiment according to Figures 16 to 18 differs from the preceding exemplary embodiments in turn in the structure of the valve element. In this embodiment, the valve element 18d is conical. The valve element 18d has a conical pot-shaped lower part 76d, which is closed by a cover 78d, with a central suction opening 36 being formed in the cover 78d, which engages with the suction mouth 38 of the impeller 14 in the manner described above. In the conical peripheral surface of the lower part 76b inlet openings 90 are formed, which can be made to overlap by rotating the valve element 18d with inlets which are connected to the suction ports 32 and 34 selectively flow path through the interior of the valve member 18d to the suction port 36 to establish. Sealing surfaces 92 are formed on the conical lower part between the inlet openings 90 and can close the respective other inlet. As well as the embodiment according to two Figures 8 to 10 Here the valve element 18d has a pin-shaped projection 64 which engages in a recess on the bottom of the pump housing 12 and supports the valve element 18d there so that it can rotate about the axis of rotation X. Here, too, an axial movement between a released position, as shown in 18 is shown, and an abutting position as shown in 17 shown, is possible to form a releasable second coupling. In the released position, the lower part 76d of the valve element 18d is essentially not in contact with the pump housing 12, so that it can be rotated as a first hydraulic clutch by the flow in the pressure chamber 26, as was described in the exemplary embodiments described above. Here, depending on the direction of rotation of the impeller 14, a back and forth movement of the valve element 18d can be achieved, with the rotary movement of the valve element 18d again being able to be limited by stops (not shown). In the fitting position according to 17 on the one hand there is a tight contact of the valve element 18d, on the other hand it is held in a non-positive manner so that it is not moved between the switching positions even when the direction of rotation of the impeller 14 changes as long as the pressure in the pressure chamber 26 is sufficiently high.

The sixth embodiment according to Figures 19 to 22 is similar to the embodiment according to FIG Figures 8 to 10 . The pump housing 12 essentially corresponds to the structure shown and described there. The motor housing 2 with the electronics housing 16 and the can 10 correspond to the structure according to the second embodiment. The valve element 18e has a very similar construction to the construction of the valve element 18'. It's just missing the projections 72 and the pin 74. The opening 62, however, is formed in the same way. The suction opening 36e also essentially corresponds to the structure of the suction opening 36'. The valve element 18e is journaled for rotation on a hollow axle which is inserted in the hole 66 in the bottom of the pump housing 12. As shown in FIG. In this embodiment, the spring 48 is positioned inside the hollow axle 94 .

Depending on the switching position of the valve element 18e, the opening 62 comes to rest either over the inlet 28' or the outlet 30' in order to open either a flow path from the suction connection 32 to the impeller 14 or from the suction connection 34 to the impeller 14. In this exemplary embodiment too, the valve element 18e is additionally movable axially along the axis of rotation X, which is the axis of rotation of the impeller 14 and the valve element 18e, in order to form a second clutch. In a rest position, in which the centrifugal pump unit is not in operation, the valve element 18e is pressed by the spring 48 into a released position in which the surface of the valve element 18e facing away from the impeller 14 is spaced from the bottom of the pump housing 12, so that the valve element 18e is substantially free to reciprocate about axis 94 between the stops formed by pin 68 and groove 70. 21 shows the first switch position, in which the opening 62 is opposite the input 28', 22 shows the second switching position, in which the opening 62 is opposite the second input 30'.

In this exemplary embodiment, the rotation of the valve element 18e takes place via the impeller 14, but here a mechanical coupling is provided as the first coupling, which is implemented in that the impeller 14 frictionally engages with its area surrounding the suction mouth 38 on the circumference of the suction opening 36e comes. Thus the valve element 18e is rotated with the impeller 14 until the pin 68 reaches a stop. Then the clutch kicks in disengaged due to slippage. As the pressure in the pressure chamber 26 increases, the valve element 18e is then, as described above, moved axially into its abutting position, in which the second clutch is thus engaged and the first clutch is disengaged from the impeller 14, so that the impeller 14 then can rotate essentially without friction.

According to the seventh embodiment 23 and 24 differs from the sixth exemplary embodiment described above in that a tongue 96 which extends into the pressure chamber 26 and serves as an additional valve element in the pressure chamber 26 is arranged on the valve element 18f. The pump housing 12 has an additional pressure connection 98 which opens into the pressure chamber 26 separately from the pressure connection 27 . Depending on the switching position of the valve element 18f, the tongue 96 can release the pressure connection 27 or the pressure connection 28 which the respective other pressure connection covers. In this exemplary embodiment, a pressure-side changeover is provided on the pressure side of the impeller 14 . A mixing function can be implemented at the same time via the inputs 28' and 30', in which the opening 92 is positioned in such a way that it covers these two inputs 28', 30' in a first switch position, so that liquid flows out of the two inputs 28', 30'. through the opening 62 and further through the suction mouth 38 flows. In the second switching position, on the other hand, the opening 62 only covers the inlet 28', while the inlet 30' is closed by the bottom of the valve element 18f in the manner described above. At the same time, the pressure port 27 is closed and the pressure port 98 is released. The movement of the valve element 18f can be realized in the manner described above via the impeller 14 and a mechanical clutch, which disengages through axial displacement of the valve element 18f when the pressure in the pressure chamber 26 is sufficiently high will. In this exemplary embodiment, the valve element 18f is mounted on the rotor shaft 8.

The eighth embodiment according to Figures 25 to 28 differs from the sixth embodiment in the formation of the first mechanical coupling between the rotor shaft 8 and the valve element 18g. In this embodiment, the valve element 18g is mounted directly on the rotor shaft 8, which is elongated and extends into the hole 66 in the bottom of the pump housing 12. Inside the valve element 18g are two ring segments 100 with plain bearing properties, in particular made of ceramic. The ring segments 100 are held together by a clamping ring 102 and pressed against the rotor shaft 8 . In this example, the two ring segments 100 essentially form a 2/3 ring. In the area of the missing ring segment for a complete ring, the valve element 18g engages with a projection 104 on its inner circumference, so that the two ring segments 100 are arranged in a rotationally fixed manner inside the valve element 18g. In the area of the missing ring segment, that is to say adjacent to the projection 104, a passage 106 remains in the valve element 18g, which causes the valve function.

The passage 106 can be in a first switch position, which is in 27 is shown, the input 30 'opposite and in a second switch position, which in 28 shown, opposite the entrance 28'. The other entrance is locked. For this purpose, according to the above-described embodiments, the valve element 18g can be pressed by the pressure prevailing in the pressure chamber 26 in the axial direction against the base of the pump housing 2 surrounding the inlets 28' and 30'.

The valve element 18g is moved via a first clutch by driving the impeller 14. At the start, the rotor shaft 8 rests non-positively on the inner circumference of the ring segments 10 and rotates them, and thus the valve element 18g as well. Stops can be formed in the pump housing 12 in the manner described above for the two switching positions. If the valve element 18g reaches one of these stops, the pump shaft 8 slips inside the ring segments 100, i.e. the clutch is disengaged. With increasing speed of the rotor shaft 8, a lubricating film in the manner of a slide bearing can also form between the outer circumference of the rotor shaft 8 and the inner surfaces of the ring segments 100, so that the rotor shaft 8 can then rotate essentially without friction inside the ring segments 100. This means that in order to adjust the valve element 18g between its two switch positions, the drive motor is preferably moved by the control device 17 at a lower speed than the speed at which the impeller 14 is rotated during operation. In order to move the valve element 18g back and forth, the drive motor can be driven in two directions of rotation, in the manner described above remains due to the pressure in the pressure chamber 26 and its system at the bottom of the pump housing 12 in the switching position previously reached.

According to the ninth and tenth embodiments Figures 29 to 37 and 38 to 47, a mechanical coupling is also provided between the drive motor and the valve element, with the drive motor being controllable by the control device 17 in two different operating modes in these embodiments. In a first operating mode, which corresponds to the normal operation of the circulating pump unit, the drive motor rotates in the conventional manner Way with a desired, in particular by the control device 17 adjustable speed. In the second operating mode, the drive motor is controlled in open-loop operation, so that the rotor can be rotated step by step in individual angular steps that are less than 360°. The drive motor can thus be moved in individual steps in the manner of a stepping motor, which is used in these exemplary embodiments to move the valve element in small angular steps into a defined position, as will be described below.

According to the ninth embodiment Figures 29 to 37 A mixing valve is integrated in the pump housing 2, as can be used, for example, to set the temperature for underfloor heating.

The motor housing 2 with the electronics housing 16 corresponds to the embodiment described above. The pump housing 12 has essentially the same structure as the pump housing according to the first embodiment Figures 1 to 6 , only the external configuration differs. The valve element 18h is also drum-shaped in this ninth embodiment and consists of a pot-shaped lower part 76h, which is closed on its side facing the impeller 14 by a cover 78h. A suction port 36 is formed in the central portion of the lid 78h. The valve element 18h 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 18h corresponds to the axis of rotation X of the rotor shaft 8h, as in the examples described above. The valve element 18h is also axially displaceable along the axis X to form a second releasable coupling and is pushed by a spring 48 into the in Figure 33 Pressed rest position shown, in which the valve element is 18h in a released position in which the lower part 76h does not rest against the bottom of the pump housing 12, so that the valve member 18h is substantially free to rotate about the axis 20. In the released position, the front end of the rotor shaft 8h, which is designed as the first clutch 108, acts as an axial stop. The clutch 108 engages a mating clutch 110 which is non-rotatably mounted on the valve member 18h. The clutch 108 has beveled clutch surfaces which essentially describe a sawtooth profile along a peripheral line in such a way that a torque transmission from the clutch 108 to the mating clutch 110 is only possible in one direction of rotation, namely in the direction of rotation A in 31 . In the opposite direction of rotation B, on the other hand, the clutch slips, causing an axial movement of the valve element 18h. Direction of rotation B is the direction of rotation in which the pump unit is driven during normal operation. The direction of rotation A, on the other hand, is used for the targeted adjustment of the valve element 18h. This means that a first clutch that is dependent on the direction of rotation is formed here. In addition, however, the counter-coupling 110 is also disengaged from the clutch 108 by the pressure in the pressure chamber 26 in this embodiment. If the pressure in the pressure chamber 26 increases, a compressive force acts on the cover 78h, which is opposite to and exceeds the spring force of the spring 48, so that the valve element 18h is pressed into the abutting position, which is shown in 32 is shown. In this, the lower part 76h rests against the bottom side of the pump housing 12, so that on the one hand the valve element 18h is held in a non-positive manner and on the other hand a tight contact is achieved, which seals the pressure and suction sides against one another in the manner described below.

The pump housing 12 has two suction connections 32 and 34 , of which the suction connection 32 opens at an inlet 28h and the suction connection 34 at an inlet 30h in the bottom of the pump housing 12 into its interior, ie the suction chamber 24 . The lower part 76h of the valve element 18h has a bottom in its base arcuate opening 112 extending substantially 90°. 34 shows a first switching position, in which the opening 112 only covers the inlet 30h, so that a flow path is only provided from the suction connection 34 to the suction opening 36 and thus to the suction mouth 38 of the impeller 14. The second inlet 28h is tightly closed by the base of the valve element 18h lying in its peripheral area. Figure 36 shows the second switching position, in which the opening 112 only covers the entrance 28h, while the entrance 30h is closed. In this switching position, only one flow path from the suction connection 32 to the suction mouth 38 is open. Figure 35 12 now shows an intermediate position in which the opening 112 covers both entrances 28h and 30h, the entrance 30h being only partially uncovered. By changing the degree of opening of the port 30h, a mixing ratio between the flows from the inlets 28h and 30h can be changed. The valve element 18h can also be adjusted in small steps via the stepwise adjustment of the rotor shaft 8h in order to change the mixing ratio.

Such functionality can be used, for example, in a hydraulic system as in 37 is shown to apply. There, the centrifugal pump unit with the integrated valve, as described above, is identified by the dashed line 1. The hydraulic circuit has a heat source 114 in the form of a gas boiler, for example, whose outlet opens into, for example, the suction connection 34 of the pump housing 12 . In this example, a floor heating circuit 116 is connected to the pressure connection 37 of the centrifugal pump unit 1, the return of which is connected both to the input of the heat source 114 and to the suction connection 32 of the centrifugal pump unit. A second circulating pump assembly 118 can be used to supply a further heating circuit 120 with a heat transfer medium, which Temperature of the heat source 114 has. The flow temperature of underfloor heating circuit 116, on the other hand, can be regulated in such a way that cold water from the return is mixed with the hot water on the outlet side of heat source 114, with changing the opening ratios of inlets 28h and 30h in the manner described above Mixing ratio can be changed by rotating the valve element 18h.

The tenth embodiment according to Figures 38 to 47 shows a centrifugal pump unit which, in addition to the mixer functionality described above, also has a switchover functionality for the additional supply of a secondary heat exchanger for domestic water heating.

In this embodiment, the valve element 18i is mounted and driven in exactly the same way as in the ninth embodiment. In contrast to the valve element 18h, the valve element 18i has, in addition to the opening 112, a through channel 122 which extends from an opening 124 in the cover 78i to an opening in the bottom of the lower part 76i and thus connects the two axial ends of the valve element 18i to one another. Furthermore, an arcuate bridging opening 126 is formed in the valve element 18i which is open only to the underside, ie to the bottom of the lower part 76i and thus to the suction chamber 24, which is closed to the pressure chamber 26 by the cover 78i.

In addition to the pressure connection 27 and the two suction connections 34 and 32 described above, the pump housing 12 has a further connection 128 . The connection 128 opens into an inlet 130 in the base of the circulating pump unit 12 in addition to the inlets 28h and 30h into the suction chamber 24. Based on Figures 43 to 46 the various switch positions are explained, with these Figures the cover 78i of the valve member 18i is shown partially open to show the position of the underlying openings. Figure 43 shows a first switch position, in which the opening 112 is opposite the inlet 30h, so that a flow connection is established from the suction connection 34 to the suction mouth 38 of the impeller 14. In the switching position according to Figure 44 For example, the opening 112 is 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. In another switching position, which Figure 45 shows, the opening 112 is above the inlet 30h, so that in turn there is a flow connection from the suction connection 34 to the suction mouth 38 of the impeller 14. At the same time, the opening 124 and the through hole 122 partially overlap with the inlet 28h, so that a connection is established between the pressure chamber 26 and the suction connection 32, which acts as a pressure connection here. At the same time, the bridging opening 126 simultaneously covers the inlet 130 and part of the inlet 28h, so that a connection from the connection 128 via the inlet 130, the bridging opening 126 and the inlet 28h to the connection 32 is also created.

Figure 46 12 shows a fourth switching position, in which the through-channel 122 completely covers the inlet 28h, so that the connection 32 is connected to the pressure chamber 26 via the through-channel 122 and the opening 124. At the same time, the bridging opening 126 only covers the entrance 130. The opening 112 continues to cover the entrance 30h.

Such a centrifugal pump unit can be used, for example, in a heating system as described in Figure 47 is shown, find use. There the dashed line limits the centrifugal pump unit 1, as is just based on the Figures 38 to 46 was described. The heating system in turn has a primary heat exchanger or a heat source 114, which can be a gas boiler, for example. On the outlet side, the flow path runs into a first heating circuit 120, which can be formed, for example, by conventional heaters or radiators. At the same time, a flow path branches off to a secondary heat exchanger 56 for heating service water. The heating system also has a floor heating circuit 116 . The returns from the heating circuit 120 and the underfloor heating circuit 116 flow into the suction connection 34 on the pump housing 12. The return from the secondary heat exchanger 56 flows into the connection 128 which, as will be described below, offers two functionalities. The connection 32 of the pump housing 12 is connected to the flow of the underfloor heating circuit 116 .

When the valve element 18i is in the first in Figure 43 switching position shown, the impeller 14 conveys liquid from the suction connection 34 via the pressure connection 27 through the heat source 140 and the heating circuit 120 and back to the suction connection 34. If the valve element 18i is in the second switching position, which is shown in Figure 44 is shown, the system is switched to service water operation, in this state the pump unit or the impeller 14 conveys liquid from the connection 128, which serves as a suction connection, through the pressure connection 27, via the heat source 114 through the secondary heat exchanger 56 and back to the connection 128. If the valve element 18i is in the third switch position, which is in Figure 45 is shown, the underfloor heating circuit 116 is also supplied. The water flows via the suction connection 34 into the suction mouth 38 of the impeller 14 and is conveyed through the first heating circuit 120 via the pressure connection 27 via the heat source 114 in the manner described. At the same time, the liquid exits the impeller 14 from the pressure chamber 26 into the opening 124 and through the through-channel 122 through and thus flows to connection 32 and via this into the underfloor heating circuit 116.

in the in Figure 45 Switching position shown flows at the same time via the bridging opening 126 via the connection 128 and the inlet 130 into the connection 32. This means here water flows via the heat source 114 through the secondary heat exchanger 26 and the connection 128 to the connection 32. Since in this heating mode at the secondary heat exchanger 56 essentially no heat is removed, so the connection 32 is mixed with hot water in addition to the cold water, which flows from the pressure chamber 26 via the through-channel 122 to the connection 32 . The amount of warm water mixed in at connection 32 can be varied by changing the degree of opening via valve position 18i. Figure 46 shows a switching position in which the admixture is switched off and the connection 32 is only directly connected to the pressure chamber 26 . In this state, the water in the floor circuit 116 is conveyed in a circuit without supplying heat. It can be seen that by changing the switching positions of the valve element 18i in this embodiment, both a switchover 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 the heat source 114 and a floor heating circuit 116 with a temperature reduced via a mixing function.

It is to be understood that the various embodiments described above can be combined with one another in various ways. Thus, the different drive types of the valve element described can be combined with different geometric configurations of the valve element, as they were also described above, in essentially any way will. The various valve functionalities (e.g. mixing and switching) can also be implemented and combined with different drive types. These different possible combinations, which result from the preceding exemplary embodiments, are expressly included in the invention.

In the examples described, the valve element is always arranged with the impeller in a common pump housing, which thus forms a combined valve and pump housing. It is to be understood that this pump housing can also be made in several parts.

Reference List

1

centrifugal pump unit

2

motor housing

4

stator

6

rotor

8th

rotor shaft

10

cracking tube

12

pump housing

14

Wheel

16

electronics housing

17

control device

18,18', 18", 18c, 18d, 18e,18f, 18g, 18h, 18i

valve element

20

axis

22

mother

24

suction chamber

26

pressure room

27

pressure connection

28, 30

inputs

28', 30', 28h, 30h

inputs

32.34

suction connections

36, 36', 36e

suction port

38

suction mouth

40

sealing surfaces

42

support elements

44

stop element

46

attacks

48

Feather

50

contact shoulder

52

heat source

54

heating circuit

56

secondary heat exchanger

58, 60

flow paths

62

opening

64

head Start

66

Hole

68

Pen

70

groove

72

protrusions

74

cones

76, 76b, 76dm 76h, 76i

lower part

78, 78d, 78h, 78i

lid

80

entry opening

82, 84

Pods

86

idler wheel

88

weight

90

entry opening

92

sealing surfaces

94

axis

96

Tongue

98

pressure connection

100

ring segment

102

clamping ring

104

head Start

106

passage

108

coupling

110

counter-coupling

112

opening

114

heat source

116

Floor heating circuit

118

circulating pump unit

120

heating circuit

122

through channel

124

opening

126

bypass opening

128

connection

130

Entry

X

axis of rotation

AWAY

directions of rotation

Claims (16)

1. A pump assembly with an electric drive motor (4, 6), with at least one impeller which is driven by the drive motor (4, 6) and with at least one valve device (18) which is situated in a flow path through the pump assembly and which is movable at least between a first and a second switching position,
   wherein

   the valve device (18) is coupled to the drive motor via a first coupling in a manner such that a movement of the drive motor (4, 6) is transmitted onto the valve device (18) and the valve device is movable from the first into the second switching position by way of a rotation movement of the drive motor (4, 6) and wherein

   the first coupling is releasable by way of increasing the speed of the drive motor (4, 6) and/or increasing the pressure at the outlet side of the impeller and/or by way of slip, in a manner such that the coupling between the drive motor (4, 6) and the valve device (18) is reduced or lifted,

   characterised in that

   a second releasable coupling is provided between at least one movable part of the valve device (18) and a pump casing which surrounds the impeller (14), said second releasable coupling being movable from a released, first coupling position into a holding, second coupling position by way of the pressure at the outlet side of the impeller (14).
2. A pump assembly according to claim 1, characterised in that the first and the second coupling are designed in a manner such that the first coupling in its released position has a lower holding force than the second coupling in its holding, second coupling position and the first coupling in its coupled position has a greater holding force than the second coupling in its released, first coupling position.
3. A pump assembly according to one of the preceding claims, characterised in that on operation of the pump assembly, the drive motor (4, 6) produces a torque which is larger than the holding force of the first coupling in its coupled position.
4. A pump assembly according to one of the preceding claims, characterised in that the valve device (18) is designed as a switch-over valve which permits a switching-over between two flow paths and/or is a mixing device, in which fluid is mixed from two flow paths, wherein the mixing device is designed in a manner such that the mixing ratio is different in the two switching positions.
5. A pump assembly according to one of the preceding claims, characterised in that the valve device (18) has a valve function in a flow path at the suction side of the impeller (14) and/or in a flow path at the delivery side of the impeller (14).
6. A pump assembly according to one of the preceding claims, characterised in that the valve device comprises at least one movable valve element (18) as well as stop elements which define the first and the second switching position and of which preferably at least one is adjustable in its position.
7. A pump assembly according to one of the preceding claims, characterised in that the valve device (18) comprises at least one movable valve element (18) which interacts with two valve openings in a manner such that in the first switching position of the valve device, a first valve opening (28) is covered by the valve element (18) to a greater extent than in the second switching position and in the second switching position a second valve opening (30) is covered to a greater extent than in the first switching position.
8. A pump assembly according to one of the preceding claims, characterised in that the valve device comprises a movable valve element (18) which comprises at least one sealing surface and a pressure surface, wherein the pressure surface is connected to a delivery chamber (26) which surrounds the impeller (14), in a manner such that the valve element (18) is pressed with the sealing surface against a contact surface by way of the pressure which acts upon the pressure surface, wherein the contact surface preferably forms a valve seat.
9. A pump assembly according to one of the preceding claims, characterised in that the valve device comprises a rotatable valve element (18) which via the first coupling is releasably coupled to a rotor (6) of the drive motor, wherein the rotation axis (X) of the valve element is preferably aligned with the rotation axis (X) of the drive motor.
10. A pump assembly according to one of the preceding claims, characterised in that the drive motor (4, 6) can be driven in two rotation directions and the valve device (18) is designed in a manner such that its first switching position is achieved by the drive of the drive motor in a first rotation direction (A) and its second switching position is reached by the drive of the drive motor in a second rotation direction (B).
11. A pump assembly according to one of the preceding claims, characterised in that the first and/or the second coupling is a friction coupling, a magnetic coupling and/or a hydraulic coupling, which preferably has slip.
12. A pump assembly according to one of the preceding claims, characterised in that the first coupling comprises at least one coupling element which is movable between a coupled and a released position, wherein the movement direction between the coupled and the released position preferably runs transversely to a force direction of the force which is to be transmitted by the coupling onto the valve device.
13. A pump assembly according to claim 12, characterised in that a valve element of the valve device simultaneously forms the movable coupling element.
14. A pump assembly according to claim 12 or 13, characterised in that the coupling element is subjected to a biasing force via a biasing element (48), said biasing force forcing the coupling element into the coupled position.
15. A pump assembly according to claim 14, characterised in that the coupling element comprises a pressure surface, the connection of said pressure surface to a delivery chamber (26) which surrounds the impeller (14) and the arrangement of said pressure surface being such that a pressure acting upon the pressure surface produces a force which is directed oppositely to the biasing force.
16. A pump assembly according to one of the claims 12 to 15, characterised in that the coupling element comprises a coupling surface (100) which in the coupled condition is in frictional contact with a counter coupling surface (8), and that the coupling surface (100) and the counter coupling surface (8) are designed and surrounded by a lubricant, in a manner such that a lubricant film which overcomes the frictional contact forms between the coupling surface (100) and the counter coupling surface (8) on increasing the speed of the drive motor.

Images