EP3376050A1 - Centrifugal pump assembly - Google Patents

Abstract

The invention relates to a centrifugal pump assembly comprising an electric drive motor (4, 6), an impeller (14) driven therefrom and at least one valve element (18) which is driven by the electric drive motor (4, 6) directly or indirectly along a first path of travel between at least two switching positions is movable, wherein at least a part of the valve element (18) additionally along a second, different from the first path of movement between a disengaged position in which the valve element is spaced from at least one contact surface and an adjacent position in which the valve element the at least one contact surface is applied, is movable

Description

The invention relates to a centrifugal pump assembly with an electric drive motor, an impeller driven by this and a valve element.

There are known centrifugal pump units, which have an integrated valve device which can be moved for example by different directions of rotation of the drive motor and thus directed in different directions flows inside a pump housing between two switching positions. These valve devices can easily switch between two possible flow paths on the output side of the pump unit. Switching between two flow paths on the suction side of the pump unit, however, is only possible via a complex mechanism.

In view of this problem, it is an object of the invention to improve a centrifugal pump assembly with a movable between at least two switching positions valve element to the effect that on the one hand a simple construction of the valve device and at the same time a reliable movement of the valve element is ensured.

This object is achieved by a centrifugal pump unit having the features specified in claim 1. Preferred embodiments will become apparent from the subclaims, the following description and the accompanying figures.

The centrifugal pump assembly according to the invention has an electric drive motor and at least one impeller which can be driven in rotation by this electric drive motor. The electric drive motor is preferably a wet running engine, i. h., As a motor with a split tube between the stator and rotor formed. In such a motor, the rotor rotates in the liquid to be conveyed. The centrifugal pump unit, in particular with the use of a wet-running electric motor, can be provided, for example, for use in a heating or air conditioning. There it can be used as Umwälzpumpenaggregat use.

The centrifugal pump assembly according to the invention further comprises at least one valve element, which is movable by the electric drive motor, which drives the impeller, directly or indirectly along a first movement path between at least two switching positions. A direct movement can be achieved, for example, by a suitable releasable coupling, in particular a magnetic or mechanical coupling, between the rotor or impeller of the drive motor and the valve element. Indirect movement can be caused, for example, by the fluid conveyed by the impeller, by the liquid flow and / or the pressure of the liquid acting on the valve element so that it can be moved. In this way, a movement along a first movement path between at least two switching positions is effected. The trajectory may be linear or curved or be a rotary motion.

According to the invention, the at least one valve element is designed and arranged such that at least a part or section of the valve element is movable along the first movement path along a second movement path, which is different from the first movement path. That is, it is one Movement of the valve element in at least two different, preferably mutually angled directions possible. Along the second movement path, the valve element or a part of the valve element between a dissolved position in which it is solved by at least one contact surface and in particular spaced, and an adjacent position in which it is pressed against the at least one contact surface, movable. In the released position, the valve element is preferably movable, in particular along the first movement path between the at least two switching positions movable. In this case, the valve element may be spaced in the released position of the contact surface or be located so that it can easily slide along the contact surface. In the second adjacent position, on the other hand, the valve element preferably rests against the contact surface so firmly that it is held in a previously assumed switching position, ie, the movement along the first movement path is prevented. In the adjacent position, the valve element is pressed against the contact surface so that the friction between the valve element and contact surface is greater than in the released position. This makes it possible to operate in this state, the centrifugal pump assembly by operating the electric drive motor in a conventional manner, in particular to regulate the speed without the valve element leaves its previously assumed switching position. In order to move the valve element in another switching position, it is previously moved along the second movement path in the released position, so that it can then move, driven by the drive motor, in a different switching position. The movement along the second movement path is preferably likewise initiated directly or indirectly by the electric drive motor. This movement can in particular be pressure-dependent, so that when a predetermined outlet pressure of the centrifugal pump assembly is exceeded, the valve element is pressed into the adjacent position. If the centrifugal pump unit with lower pressure or differential pressure is operated, a movement of the valve element between the switching positions is possible.

According to the invention, either the valve element as a whole may be movable along the second movement path or only a portion of the valve element may be movable along the second movement path, for example an elastically deformable portion of the valve element, such as an elastic seal. If in this description of a mobility of the valve element along the second movement path is mentioned, it is always an embodiment in which only a portion or a portion of the valve element along the second movement path is movable, expressly includes.

The at least one valve element is preferably mechanically and / or hydraulically coupled to the drive motor such that it can be moved by the drive motor along the first and / or the second movement path. The movement along the first movement path can be effected, for example, by a hydraulic flow, which is caused by the impeller, by this flow acting on the valve element or entraining it in the flow direction by friction. Alternatively, a mechanical or magnetic coupling may be provided, in particular a frictionally engaged coupling. Such a coupling can be further preferably designed so that it can be disengaged pressure-dependent, ie, upon reaching a certain output pressure of the pump unit dissolves, so that the drive motor can continue to rotate freely without moving the valve element on. Along the second movement path, the valve element can be moved, for example, purely pressure-dependent in that upon reaching a certain output pressure of the fluid conveyed by the impeller, this pressure acts on the valve element, that it against the contact surface is pressed and there is preferably frictionally and / or positively held, so that in particular a flow or other coupling, the valve element can not move between the switching positions. The different flow speeds or pressures on the output side of the impeller can be adjusted via a control device which controls the drive motor. In this case, the control device is preferably designed so that it can adjust in particular the speed and more preferably also the acceleration characteristics of the drive motor.

The second movement path preferably extends transversely to the first movement path or transversely to a plane in which the second movement path extends or runs. In particular, the planes in which the trajectories run are directed normal to each other. For example, the first trajectory may be a rotational movement about an axis of rotation and the second trajectory may be a linear movement along this axis of rotation.

Preferably, the axis of rotation about which the valve member is rotatable along the first trajectory is parallel or aligned with the axis of rotation of the impeller. This allows a particularly simple coupling between the drive motor and impeller on one side and valve element on the other side.

The valve element is suitably rotatably mounted such that it is rotatable in the released position about a bearing and in particular a central bearing between the at least two switching positions and is preferably held non-rotatably in the second adjacent position on the contact surface. In this case, the central bearing is preferably designed such that the valve element in the released position preferably abuts substantially only in the bearing, so that it is particularly easy to rotate. In addition, the valve element if necessary, still rest against a return element, which forces it into the released position. The storage is preferably permanently lubricated or lubricated by the liquid to be conveyed, so that a special ease of storage is achieved. In the adjacent position, the valve element forms with the contact surface a non-positive and / or positive coupling, which prevents the rotation and thus holds the valve element in the assumed switching position.

The second movement path is preferably a straight line and more preferably a straight line which extends parallel to or along the axis of rotation of the at least one valve element. Thus, the valve element may be rotatably mounted in its central region, wherein the bearing is preferably designed such that it allows a certain linear movement along the axis of rotation to allow the movement along the second path of movement.

The at least one contact surface is preferably at least one sealing surface. The sealing surface can for example be formed by a valve seat which surrounds a valve opening of a flow path. By conditioning the valve element on this sealing surface, a sealing of the valve opening is achieved at the same time. In addition, the friction described to prevent the movement of the valve element can be achieved by this system. Alternatively or additionally, a sealing surface may also be arranged so that the valve element in its adjacent position seals the suction side with respect to the pressure side of the centrifugal pump assembly when the valve element is located between the suction and pressure sides.

More preferably, the at least one valve element has a pressure surface which communicates with a pressure side of the impeller in such a way that a pressure prevailing on the pressure side the pressure surface acts and thus generates a pressure force acting on the valve element, wherein the pressure surface is located so that this pressure force is at least partially directed along the second movement path of the valve element and in particular directed along the second movement path to the adjacent position. Thus, at sufficiently high pressure on the pressure side of the impeller, ie in a pressure chamber of a pump housing, which surrounds the impeller, generates such a high pressure force that this displaces the valve element or a portion of the valve element from the dissolved into the adjacent position and against Pressing contact surface, there to hold the valve element force and / or frictional engagement and / or to provide a sufficient seal when applied to at least one sealing surface.

According to a further preferred embodiment, the valve element is coupled to at least one restoring element, in particular a restoring spring, which exerts on the valve element a restoring force along the second movement path, in particular directed towards the released position. The return element ensures that, when the pump unit is taken out of service, the valve element is moved to a starting position, which preferably corresponds to the released position. In this, the valve element is then, as described above, preferably freely movable between the switching positions. If the drive motor is driven in this state, it is possible to move the valve element between the switching positions by appropriate control of the drive motor. In order to bring the valve element in the applied position, a force can be exerted on the valve element, which overcomes the restoring force to move the valve element in the applied position. This can be done, for example, that the output side of the impeller, as described above, a pressure is built up, which is a pressure force on a pressure surface of the valve element generated, which is directed opposite to the described restoring force. If the pressure force is greater than the restoring force, the valve element is moved to the applied position.

According to another possible embodiment, the function of the return element can be achieved by an elastic deformability of a portion of the valve element which is movable along the second movement path. The reset function is then taken over by elastic restoring forces.

The centrifugal pump assembly according to a further preferred embodiment, a force generating means which exerts on the valve element, a force 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 switching position, in the direction of which the force generated by the force generating means is directed, preferably forms a starting position or rest position. The force generating means is preferably designed and arranged so that it forces the valve element in this initial position or a predetermined switching position at standstill of the centrifugal pump assembly. From this, the valve element can then be moved by suitable drive of the drive motor in a different switching position. However, if the movement of the valve element takes place first along the second movement path and the valve element thus comes into contact with the abutment surface, the valve element can also be held in operation when the centrifugal pump assembly is in the switching position which corresponds to the starting position. This can be done for example by very fast acceleration of the drive motor, whereby directly such a pressure on the output side of the impeller is formed, which can act on the valve element on a pressure surface and press against the contact surface.

Particularly preferably, the coupling between the drive motor and valve element is formed hydraulically, wherein the at least one valve element is preferably configured such that it can be moved along the first movement path by a fluid flow set in motion by the impeller. This fluid flow is particularly preferably a rotating fluid flow in the exit region of the impeller, which surrounds the impeller during its rotation. This flow can act, for example, by friction on the valve element and this move, in particular, when the valve element is formed so that it is rotatable about an axis of rotation, which corresponds to the axis of rotation of the impeller, between the switching positions. This hydraulic coupling has the advantage that after reaching the desired switching position, the flow in the pump housing can continue to flow unhindered, while the valve element is held by a stop and / or contact with the contact surface in the achieved switching position. In this state, the flow on the surface of the valve element preferably causes only a friction which corresponds to the normal friction in the interior of the pump housing, so that substantially no additional power loss is created in the centrifugal pump assembly by the switching functionality.

According to a particular embodiment of the invention, the drive motor is designed or driven by a control device that it can be driven in two different directions of rotation. The impeller is further preferably configured such that, depending on its direction of rotation, it generates differently directed fluid flows through which the at least one valve element can be moved in opposite directions along the first movement path. Thus, by reversing the direction of rotation of the drive motor and thus of the impeller, the valve element between the at least two switching positions are moved back and forth. When, as described above, a force generating means for generating a force, which the valve element is moved back to a starting position, is provided, can be dispensed with this direction of rotation reversal of the drive motor, since the return movement of the valve element is then carried out by the force generating means, while the movement can be made from the starting position via the drive motor in the manner described.

Particularly preferably, the drive motor has a control device which controls the drive motor such that the rotational speed and / or the acceleration and / or the direction of rotation of the drive motor can be selectively changed in order to achieve the above-described processes.

According to a further preferred embodiment of the invention, the valve element is arranged and configured such that it can be moved along the first movement path by a flow generated by the impeller and can be moved along the second movement path by a fluid pressure generated on the output side by the impeller. The drive motor preferably has a control device which is designed such that the drive motor can be approached with a first acceleration profile, in which the pressure builds up faster than the flow, and with a second acceleration profile, in which the flow builds up faster than the pressure is. The first acceleration curve preferably corresponds to a stronger acceleration than the second acceleration curve. If such a pressure is quickly reached that the valve element can be pressed by the pressure against a contact surface, as described, before a sufficient flow builds up, which can move the valve element in the manner described, the valve element can thus be held in that switching position which corresponds to the starting position. If, however, the acceleration is slower, no such high pressure is achieved that the valve element along the second movement path in the applied position is moved, and it may initially form a flow, which can move the valve element in the manner described in another switching position. Thus, solely by driving the drive motor, the valve element can be selectively moved to a desired switching position and kept in this for further operation of the pump unit. The pressure at which the valve element comes into contact with the contact surface is preferably chosen so that it corresponds to a pressure which is lower than the usual operating pressure of the centrifugal pump assembly, so that the normal operation of the centrifugal pump assembly is not affected after reaching the switching position.

According to a further preferred embodiment, the at least one valve element may be coupled to its movement along the first movement path with the impeller or a shaft driving the impeller of the drive motor or directly to the rotor of the drive motor via a coupling which preferably pressure and / or speed and / or rotational direction dependent solvable. This may be a mechanical clutch which transmits the rotational movement of the drive motor to the valve member to move it between the shift positions. The coupling may be designed such that it disengages on the output side of the impeller upon reaching a certain fluid pressure. It may also be configured so that it disengages at a certain speed, for example, by forming a lubricant film between the coupling parts, which essentially eliminates the frictional engagement, so that the coupling parts then slide on each other in the manner of a sliding bearing. The lubricating film can be built up, for example, by the fluid conveyed by the impeller. The liquid is particularly preferably water. Further, a direction of rotation dependent coupling is possible, which acts, for example, in the manner of a pawl or ratchet only in one direction of rotation, while in the opposite direction of rotation slide the coupling elements on each other. So z. As a direction of rotation of the drive motor, which preferably does not correspond to the normal direction of rotation of the impeller, be used to move the valve element in a desired switching position, while in the other direction of rotation, which then preferably corresponds to the normal operating direction of rotation, the clutch does not act, so the valve element remains in the reached switching position. Such a coupling can be used particularly preferably in combination with the force generating means described above for generating a force which moves the valve element back into a starting position. In addition, a hydraulic clutch between the impeller and the drive motor is possible, as described above.

According to a further preferred embodiment, the at least one valve element may be designed and arranged such that it separates in a pump housing surrounding the impeller a suction chamber communicating with a suction side of the impeller from a pressure chamber communicating with the pressure side of the impeller. In this case, the valve element can further preferably surround a suction mouth of the impeller ring. The arrangement of the valve element between suction and pressure side has the advantage that the differential pressure between suction and pressure side can be used to move the valve element along the second path of movement. The pressure-side pressure acts on one side of the valve element, while the suction-side pressure acts on the opposite side. Moreover, it is possible that liquid flows engage on one or both sides of the valve element, ie on the pressure side and / or the suction side, in order to move the valve element along the first movement path.

More preferably, the at least one valve element is designed and arranged such that it separates in a surrounding the impeller pump housing connected to a suction side of the impeller suction from a communicating with a pressure side of the impeller pressure chamber, wherein in the pressure chamber one of the Impeller generated flow acts on the valve element to the movement along the first movement path and the suction chamber is configured such that the prevailing flow exerts no force on the valve element in the direction of the first trajectory. Thus, the valve element targeted by the pressure in the space, preferably surrounding the impeller running flow or move the valve element to move it between the switching positions. On the suction side, less or no forces counteract. Alternatively, however, it is also possible to design the suction-side flow paths in such a way that the flow prevailing there exerts a corresponding force on the valve element for its movement.

According to a further particular embodiment of the invention, the centrifugal pump unit has at least 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 these flow paths are opened differently. For example, the valve element can take over the function of a changeover valve by alternately opening the two flow paths. Ie. in a first switching position, the first flow path is closed and the second flow path is opened, while in a second switching position the first flow path is opened and the second flow path is closed. It is also possible to form the valve element as a mixing valve in which the flows from the two flow paths are mixed in variable proportions. In such an embodiment, it is preferred that the valve element can occupy more than two switching positions in which the flow paths are opened differently wide. In this case, the valve element is preferably designed such that it shuts off a flow path by a certain amount during its displacement, while at the same time the other flow path is opened by the same amount.

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 Zustand,

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 flow paths described are preferably located on the suction side of the impeller, that is, for example, if, for example, the valve element acts as a switching valve in the manner described, the impeller can suck depending on the position of the valve element from one of the two flow paths liquid. The reversing valve can be used, for example, in a heating system to selectively direct the circulation of the liquid pumped by the centrifugal pump unit through a heat exchanger for generating service water and through a heating circuit. In particular, when the valve element operates as a mixing valve, it is also possible that the two flow paths are located on the pressure side of the impeller, in which case one of the flow paths before the mixing valve preferably passes through a heat source or a heat exchanger to temper the liquid during the other flow path runs directly to the mixing valve. Thus, a tempered flow can be mixed with a non-tempered flow in the mixing valve.
The invention will now be described by way of example with reference to the accompanying drawings. In these shows:

Fig. 1

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

Fig. 2

a perspective view of the underside of the valve element of the centrifugal pump assembly according to Fig. 1 .

Fig. 3

a perspective view of the pump housing of the centrifugal pump assembly according to Fig. 1 in the open state,

Fig. 4

a sectional view of the centrifugal pump assembly according to Fig. 1 .

Fig. 5

a sectional view of the pump housing of the centrifugal pump assembly according to Fig. 4 with the valve element in a first switching position,

Fig. 6

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

Fig. 7

schematically the hydraulic structure with a heating system with a centrifugal pump assembly according to Fig. 1 to 6 .

Fig. 8

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

Fig. 9

a sectional view of the centrifugal pump assembly according to Fig. 8 with the valve element in a first position,

Fig. 10

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

Fig. 11

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

Fig. 12

a sectional view of the centrifugal pump assembly according to Fig. 11 with the valve element in a first position,

Fig. 13

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

Fig. 14

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

Fig. 15

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

Fig. 16

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

Fig. 17

a sectional view of the centrifugal pump assembly according to Fig. 16 with the valve element in a first position,

Fig. 18

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

Fig. 19

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

Fig. 20

a sectional view of the centrifugal pump assembly according to Fig. 19 .

Fig. 21

a plan view of the open pump housing of the centrifugal pump assembly according to Fig. 19 and 20 with the valve element in a first switching position,

Fig. 22

a plan view accordingly Fig. 21 with the valve element in a second switching position,

Fig. 23

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

Fig. 24

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

Fig. 25

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

Fig. 26

a sectional view of the centrifugal pump assembly according to Fig. 25 .

Fig. 27

a plan view of the open pump housing of the centrifugal pump assembly according to Fig. 25 and 26 with the valve element in a first switching position,

Fig. 28

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

Fig. 29

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

Fig. 30

a perspective view of the centrifugal pump assembly according to Fig. 29 with removed pump housing and valve element,

Fig. 31

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

Fig. 32

a sectional view of the centrifugal pump assembly according to Fig. 29 with the valve element in a first position,

Fig. 33

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

Fig. 34

a plan view of the open pump housing of the centrifugal pump assembly according to FIGS. 29 to 33 with the valve element in a first switching position,

Fig. 35

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

Fig. 36

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

Fig. 37

schematically the hydraulic structure of a heating system with a centrifugal pump assembly according to FIGS. 29 to 36 .

Fig. 38

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

Fig. 39

a perspective view of the open valve element of the centrifugal pump assembly according to Fig. 38 .

Fig. 40

a perspective view of the closed valve element according to Fig. 39 .

Fig. 41

a sectional view of the centrifugal pump assembly according to Fig. 38 with the valve element in a first position,

Fig. 42

a sectional view according to Fig. 41 with the valve element in a second position,

Fig. 43

a plan view of the open pump housing of the centrifugal pump assembly according to Fig. 38 to 42 with the valve element in a first switching position,

Fig. 44

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

Fig. 45

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

Fig. 46

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

Fig. 47

schematically the hydraulic structure of a heating system with a centrifugal pump assembly according to FIGS. 38 to 46 ,

The embodiments of the centrifugal pump assembly according to the invention described in the following description relate to applications in heating and / or air conditioning systems, in which of the centrifugal pump unit, a liquid heat carrier, in particular water, is circulated.

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

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

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

The valve element 18 separates in the pump housing 12 a suction chamber 24 from a pressure chamber 26. In the pressure chamber 26 rotates the impeller 14. The pressure chamber 26 is connected to the pressure port or discharge port 28 of the centrifugal pump assembly, which forms the outlet of the centrifugal pump assembly. In the suction chamber 24 open two suction-side inputs 28 and 30, of which the input 28 is connected to a first suction port 32 and the input 30 to a second suction port 34 of the pump housing 12.

The valve element 18 is disc-shaped and at the same time performs 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 circumferential collar which engages the suction mouth 38 of the impeller 14 and is substantially in close contact with the suction mouth 38. Facing the impeller 14, the valve member 18 is formed substantially smooth. On the side facing away from the impeller 14, the valve element has two annular sealing surfaces 40, which are located in this embodiment on closed tubular nozzle. The two annular sealing surfaces 40 are arranged at two diametrically opposite positions on the sealing element 18 with respect to the axis of rotation X, so that they can in the peripheral region of the inputs 28 and 30 at the bottom of the pump housing 12 in tight contact with each other to close the inputs 28 and 30. In an angular position 90 ° offset from the sealing surfaces 40 support members 42 are arranged, which can also come to rest on the peripheral portion of the inputs 28, 30, but are spaced apart so that they do not close the inputs 28, 30 then. The inputs 28 and 30 are not on a diameter line with respect the rotation axis X, but on a radially offset straight line, so that upon rotation of the valve member 18 about the rotation axis X in a first switching position, the input 38 is closed by a sealing surface 40, while the support members 42 are located at the entrance 30 and open. In a second switching position, the input 30 is closed by a sealing surface 40, while the support elements 42 abut in the peripheral region of the input 28 and open it. The first switching position, in which the input 38 is closed and the input 30 is opened, is in Fig. 5 shown. The second switching position, in which the input 30 is closed and the input 28 is open, is in Fig. 6 shown. This means, by a rotation of the valve element by 90 ° about the axis of rotation X can be switched between the two switching positions. The two switching positions are limited by a stop element 44 which abuts alternately on two stops 46 in the pump housing 12.

In a rest position, that is, when the centrifugal pump assembly is not in operation, a spring 48 pushes the valve member 18 in a disengaged position in which the outer periphery of the valve member 18 is not close to the pump housing 12 and the sealing surfaces 40 not tight in the peripheral region of the inputs Abut 28 and 30, so that the valve element 18 can rotate about the axis 20. Now, 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. The control device 17 is designed so that it can selectively drive the drive motor in two directions of rotation. Thus, the valve element 18 about the rotational axis X depending on the direction of rotation of the impeller 14 via the offset from the impeller 14 in rotation flow can also be moved in two directions, since the flow in the peripheral region of the impeller 14 always runs in the direction of rotation. Thus, the valve element 18 between the two limited by the stops 46 switching positions are rotated.

When the impeller 14 rotates at a sufficient speed, a pressure builds up in the pressure chamber 26, which generates a pressure force on the surface of the valve element 18, which surrounds the suction opening 36, which is opposite 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 so that it comes to sealing contact on its outer circumference at an annular abutment shoulder 50 on the pump housing 12. At the same time comes depending on the switching position, one of the sealing surfaces 40 in the periphery of one of the inputs 28 and 30 sealingly to the system, so that one of the inputs 28, 30 is closed. At the other input, the support elements 42 come to rest, so that this input remains open and a flow path from this input 28, 30 is given to the suction port 36 and from there into the interior of the impeller 14. By the installation of the valve element 18 on the abutment shoulder 50 and the sealing surface 40 in the peripheral region of one of the inputs 28, 30 a frictional engagement between the valve element 18 and the pump housing 12 is simultaneously created. This frictional engagement ensures that the valve element 18 is held in the achieved switching position. This makes it possible to temporarily take the drive motor out of operation again 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 put back into operation quickly enough, the pressure in the pressure chamber 26 does not decrease so much that the valve element 18 can again move in the axial direction to its released position. This makes it possible to drive the impeller during operation of the centrifugal pump assembly always in its preferred direction of rotation, for which the blades are designed to drive and the opposite direction of rotation only for Move the valve element 18 to use in the opposite direction of rotation.

The described centrifugal pump assembly according to the first embodiment of the invention can be used, for example, in a heating system as shown in FIG Fig. 7 is shown. Such a heating system is commonly used in homes or homes 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. Further, a heating circuit 54 is present, which leads, for example, by different radiators of a building. In addition, a secondary heat exchanger 56 is provided, via which service water can be heated. In such heating systems usually a switching valve is required, which selectively directs the heat transfer stream through the heating circuit 54 or 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 in the centrifugal pump unit 1. The control is carried out by the control device 17 in the electronics housing 16. At the pressure port 27 of the pump housing 12, the heat source 52 is connected. To the suction port 32, a flow path 58 is connected, while to the suction port 34, a flow path 60 is connected through the heating circuit 54. Thus, depending on the switching position of the valve element 18 can be switched between the flow path 58 through the secondary heat exchanger 56 or the flow path 60 through the heating circuit 54 without a valve with an additional drive would be required.

The second embodiment according to Fig. 8 to 10 differs from the first embodiment in the construction of the valve element 18 '. Also in this embodiment, the valve element separates 18 'the pressure chamber 26 from a suction chamber 24 of the pump housing 12. The valve element 18 has a central suction opening 36', in which the suction port 38 of the impeller 14 sealingly engages. 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 inputs 28, 30. The inputs 28 ', 30' in this embodiment 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 rotatably mounted there about the axis of rotation X. At the same time, the projection 64 in the hole 66 also allows 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 semicircular groove 70 at the bottom of the pump housing 12. The ends of the groove 70 serve as abutment surfaces for the pin 68 in the two possible switching positions of the valve element 18 ', wherein in a first switching position, the opening 62 via the input 28' and in a second switching position the opening 62 on the input 30 'and the other input through the bottom of the valve element 18 'is closed. The rotational movement of the valve element 18 'between the two switching positions also takes place in this embodiment by the flow caused in the pressure chamber 26 by the impeller 14. To better transfer this to the valve element 18 ', it is provided with projections 72 directed in the pressure space 26. When the centrifugal pump assembly 1 is taken out of service, the spring 48 presses the valve element 18 'in the in Fig. 10 shown dissolved position in which it does not abut the ground in the periphery of the inputs 28 'and 30'. In this it abuts axially with a central pin 74 on the front side of the motor shaft 8 and is through limits this stop in its axial movement. If the pressure in the pressure chamber 26 is sufficiently large, the valve element 18 'in the in Fig. 9 Pressed applied position shown in which the valve element 18 'at the bottom of the pump housing 12 in the peripheral region of the inputs 28' and 30 'comes to rest and at the same time the pin 24 is lifted from the front side of the rotor shaft 8. In this position, the impeller 14 then rotates during normal operation of the circulating pump unit.

The third embodiment according to Fig. 11 to 13 shows a further possible embodiment of the valve element 18 ". This embodiment differs from the preceding embodiments in the construction of the valve element 18". This is designed as a valve drum. The pump housing 12 substantially corresponds to the structure according to Fig. 1 to 6 In particular, the arrangement of the inputs 28 and 30 corresponds to the arrangement described with reference to the first 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 with its axially directed collar in the suction mouth 38 of the impeller 14 On the opposite side, the bottom of the lower part 36 has an inlet opening 80 which, depending on the switching position, is brought into coincidence with one of the entrances 28, 30, while the respectively other inlet 28, 30 is closed by the bottom of the lower part 26 Valve element 18 "is rotatably mounted on an axis 20 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. Also in this embodiment, the valve element 18 "along the axis 20 to a certain extent axially displaceable, whereby also a spring 48 is provided, which in the rest position the valve element 18" in his in Fig. 13 shown solved Position presses. This axial position is limited in this embodiment by the nut 22. In the released position, the valve element 18 ", as described above, by the flow, which is caused by the impeller 14, rotatable, that is, there is a hydraulic coupling between the impeller 14 and valve element 18" made. In the adjacent position, which in Fig. 12 is shown, depending on the switching position to one of the inputs 28, 30 sealed. On the other hand, there is also a seal between the suction chamber 24 and the pressure chamber 26 by the contact of the valve element 18 "on the abutment shoulder 50th

In this embodiment, the bearing of the valve element 18 "on the axis 20 is further encapsulated by two sleeves 82 and 84, so that these areas are protected from contamination by the pumped fluid and can optionally be pre-lubricated. to ensure the easy rotation of the valve element 18 "by the flow caused by the impeller 14. It should be understood that even with the other embodiments described herein, the storage could be suitably encapsulated.

Fig. 14 and 15 show a fourth embodiment in which the structure of the pump housing 12 corresponds to the structure of the pump housing 12 according to the first and the third embodiment. In this embodiment, the rotational movement of the valve element 18c by the suction-side flow, that is, the entering into the suction port 38 of the impeller 14, supported flow. Also in this embodiment, the valve element 18c is formed substantially drum-shaped and has a pressure chamber 26 facing the cover 28 with the central suction opening 36, which with the suction mouth 38, as described above, is engaged. The lower part 76b shown here has two inlet openings 80 which, depending on the switching position with one of the inputs 28, 30 can be made to cover, the other input 28, 30 is sealed by the bottom of the lower part 46 b, as described in the previous embodiment. Between the lower part 76b and the lid 78, a guide wheel 86 is arranged with blades, in which the flow from the inlet openings 80 enters radially and axially to the central suction opening 36 exits. By the blades of the stator 86, a torque is also generated about the axis 20, through which the valve element 18c can be moved between the switching positions. This essentially works as described above. In addition, a spring 48, as described above, may also be provided to move the valve element 18c to a released position. Since the shape of the blades of the stator 86 always generates a torque in the same direction, regardless of which direction the impeller 14 rotates, in this embodiment, the return movement is performed by a weight 88. In operation, the centrifugal pump unit is always in the installed position , what a Fig. 15 is shown, in which the rotation axis X extends horizontally. When the centrifugal pump assembly is turned off, the valve member 18c always rotates about the axis 20 so that the weight 88 is below. By the torque generated by the stator 86, the valve element 18c can be rotated against this restoring force generated by the weight 88, whereby by rapid commissioning of the drive motor in the pressure chamber 26 so quickly a pressure can be built up that the valve element 18c in its adjacent position occurs, as described above, in which it is non-positively rotatably held on the pump housing 12 without being moved out of its rest position. It should be understood that a provision of the valve member by gravity or other restoring force regardless of the drive could also be used in the other embodiments described herein.

The fifth embodiment according to Fig. 16 to 18 differs from the preceding embodiments again in the construction of the valve element. In this embodiment, the valve element 18d is conical. The valve element 18d has a conical cup-shaped lower part 76d, which is closed by a cover 78d, wherein in the lid 78d in turn a central suction opening 36 is formed, which in the manner described above with the suction port 38 of the impeller 14 is engaged. In the conical peripheral surface of the lower part 76b, there are formed entrance ports 90 which can be selectively made to overlap by rotating the valve element 18d having entrances connected to the suction ports 32 and 34 to a flow path through the inside of the valve element 18d to the suction port 36 produce. Between the inlet openings 90 sealing surfaces 92 are formed on the conical lower part, which can close the respective other input. As well as the embodiment 2 according to Fig. 8 to 10 Here, the valve element 18d has a pin-shaped projection 64, which engages in a recess at the bottom of the pump housing 12 and there rotatably supports the valve element 18d about the axis of rotation X. Here, too, is an axial movement between a released position, as in Fig. 18 is shown, and an adjacent position, as in Fig. 17 shown is possible. In the released position, the lower part 76d of the valve element 18d is substantially not abutted on the pump housing 12, so that it is rotatable by the flow in the pressure chamber 26, as described in the embodiments described above. Here, depending on the direction of rotation of the impeller 14, in turn, a reciprocating movement of the valve element 18d can be achieved, wherein the rotational movement of the valve element 18d can also be limited here by stops, not shown. In the adjacent position according to Fig. 17 on the one hand, a tight contact of the valve element 18d, on the other hand, it is held strong, so it in turn, as long as the pressure in the pressure chamber 26 is sufficiently large, even with a change of direction of the impeller 14 is not moved between the switching positions.

The sixth embodiment according to Fig. 19 to 22nd is similar to the embodiment 2 according to Fig. 8 to 10 , The pump housing 12 essentially corresponds to the structure shown and described there. Also, 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 structure to the construction of the valve element 18 '. It lacks only the projections 72 and the pin 74. The opening 62, however, is designed in the same way. Also, the suction port 36e substantially corresponds to the structure of the suction port 36 '. The valve member 18e is rotatably supported on a hollow shaft which is inserted into the hole 66 in the bottom of the pump housing 12. In this embodiment, the spring 48 is disposed inside the hollow axle 94.

Depending on the switching position of the valve element 18 e, the opening 62 comes to rest either above the inlet 28 'or the outlet 30' in order to open either a flow path from the suction port 32 to the impeller 14 or from the suction port 34 to the impeller 14. In this 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 of the valve element 18e. In a rest position, in which the centrifugal pump assembly is not in operation, the valve element 18 e is pressed by the spring 48 in a released position in which the impeller 14 remote from the surface of the valve element 18 e is spaced from the bottom of the pump housing 12, so that the valve element 18e is substantially freely rotatable about the axis 94 between the stops formed by the pin 68 and the groove 70 back and forth. Fig. 21 shows the first switch position, in which the opening 62 is opposite the entrance 28 ', Fig. 22 shows the second switching position in which the opening 62 opposite the second input 30 '.

In this embodiment, the rotation of the valve element 18e again via the impeller 14, but here a mechanical coupling is provided, which is realized in that the impeller 14 comes frictionally with its surrounding the suction mouth 38 area on the circumference of the suction port 36e to rest. Thus, the valve element 18e is rotated with the impeller 14 until the pin 68 reaches a stop. Then the clutch disengages due to slip. With increasing pressure in the pressure chamber 26, the valve element 18e is then moved axially into its abutting position as described above, whereby the clutch is disengaged from the impeller 14 so that the impeller 14 can then rotate substantially without friction.

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

The eighth embodiment according to Fig. 25 to 28 differs from the sixth embodiment in the formation of the mechanical coupling between the rotor shaft 8 and the valve element 18g. In this embodiment, the valve element 18 g is mounted directly on the rotor shaft 8, which is formed extended and extends into the hole 66 in the bottom of the pump housing 12. Inside the valve element 18g, two ring segments 100 with slide bearing properties, in particular of ceramic, are arranged. The ring segments 100 are held together by a clamping ring 102 and pressed against the rotor shaft 8. The two ring segments 100 in this example 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 drehfst inside the valve element 18g. In the region of the missing ring segment, that is to say adjacent to the projection 104, a passage 106, which effects the valve function, remains in the valve element 18g.

The passage 106 may in a first switching position, which in Fig. 27 is shown, the input 30 'opposite and in a second Switch position, which in Fig. 28 is shown, the input 28 'opposite. The other entrance is closed in each case. For this purpose, the valve element 18g according to the above-described embodiments of the pressure prevailing in the pressure chamber 26 pressure in the axial direction in abutment against the inputs 28 'and 30' surrounding the bottom of the pump housing 2.

The movement of the valve element 18g via the drive of the impeller 14. The rotor shaft 8 is at the start non-positively on the inner circumference of the ring segments 10 and rotates these and thus the valve element 18g with. For the two switching positions stops in the pump housing 12 may be formed in the manner described above. If the valve element 18g reaches one of these stops, the pump shaft 8 slips inside the ring segments 100. As the rotational speed of the rotor shaft 8 increases, a lubricant film of the type 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 substantially friction-free inside the ring segments 100. This means that for adjusting the valve element 18g between its two switching positions of 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. For reciprocating the valve element 18g, the drive motor can be driven in the manner described above in two directions of rotation, in turn, after reaching the desired switching position in the manner described above can be achieved by rapid speed increase, that the valve element 18g due to the Pressure in the pressure chamber 26 and its system at the bottom of the pump housing 12 remains in the previously reached switching position.

In the ninth and tenth embodiments according to FIGS. 29 to 37 and 38 to 47, a mechanical coupling between the drive motor and the valve element is also provided, wherein in these embodiments, the drive motor of the control device 17 in two different operating modes or operating modes can be controlled. In a first mode, which corresponds to the normal operation of the circulating pump unit, the drive motor rotates in a conventional manner with a desired, in particular adjustable by the control device 17, speed. In the second operating mode, the drive motor is activated in open-loop mode, so that the rotor can be rotated incrementally in individual angular steps which are smaller than 360 °. Thus, 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.

According to the ninth embodiment according to FIGS. 29 to 37 is integrated in the pump housing 2, a mixing valve, as it can be used for example for temperature adjustment for underfloor heating.

The motor housing 2 with the electronics housing 16 corresponds to the embodiment described above. The pump housing 12 is constructed substantially the same as the pump housing according to the first embodiment Fig. 1 to 6 , only the outer configuration is different. The valve element 18h is also drum-shaped in this ninth embodiment and consists of a cup-shaped lower part 76h, which is closed on its side facing the impeller 14 by a cover 78h. In the central region of the lid 78h, a suction opening 36 is formed. The valve element 18 h is rotatably mounted on an axis 20, which is arranged in the bottom of the pump housing 12. It corresponds the axis of rotation of the valve element 18h, as in the examples described above, the axis of rotation X of the rotor shaft 8h. In this case, the valve element 18h is also axially displaceable along the axis X and by a spring 48 in the in Fig. 33 shown rest position, in which the valve element 18h is in a released position in which the lower part 76h is not applied to the bottom of the pump housing 12, so that the valve element 18h is substantially freely rotatable about the axis 20. As an axial stop acting in the released position, the front end of the rotor shaft 8 h, which is designed as a coupling 108. The clutch 108 engages with a counter-coupling 110, which is non-rotatably arranged on the valve element 18h in engagement. The coupling 108 has tapered coupling surfaces which essentially describe a sawtooth profile along a circumferential line in such a way that torque transmission from the coupling 108 to the counterpart coupling 110 is possible only in one direction of rotation, namely in the direction of rotation A in FIG Fig. 31 , In the opposite direction of rotation B, however, the clutch slips through, resulting in an axial movement of the valve element 18h. The direction of rotation B is the direction of rotation in which the pump unit is driven in normal operation. The direction of rotation A, however, is used for targeted adjustment of the valve element 18h. That is, here is a direction of rotation dependent coupling is formed. In addition, however, occurs in this embodiment, the mating coupling 110 of the clutch 108 by the pressure in the pressure chamber 26 disengaged. If the pressure in the pressure chamber 26 increases, a pressure force which opposes and exceeds the spring force of the spring 48 acts on the cover 78h, so that the valve element 18h is pressed into the abutting position, which in FIG Fig. 32 is shown. In this, the lower part 76h is located on the bottom side of the pump housing 12, so that on the one hand the valve element 18h is frictionally held and on the other hand a tight contact is achieved, which seals the pressure and the suction side in the manner described below against each other.

The pump housing 12 has two suction ports 32 and 34, of which the suction port 32 opens at an inlet 28h and the suction port 34 at an inlet 30h in the bottom of the pump housing 12 in its interior, that is, the suction chamber 24 inside. The lower part 76h of the valve element 18h has in its bottom an arcuate opening 112 which extends substantially through 90 °. Fig. 34 shows a first switching position in which the opening 112 covers only the input 30h, so that a flow path is given only from the suction port 34 to the suction port 36 and thus to the suction port 38 of the impeller 14. The second input 28 h is sealed by the voltage applied in its peripheral region bottom of the valve element 18 h. Fig. 36 shows the second switching position in which the opening 112 covers only the input 28h, while the entrance 30h is closed. In this switching position, only one flow path from the suction port 32 to the suction mouth 38 is opened. Fig. 35 now shows an intermediate position in which the opening 112 covers both inputs 28h and 30h, the input 30h is only partially released. By changing the degree of release of the port 30h, a mixing ratio between the flows from the inputs 28h and 30h can be changed. By way of the stepwise adjustment of the rotor shaft 8h, the valve element 18h can also be adjusted in small steps in order to change the mixing ratio.

Such functionality can be found, for example, in a hydraulic system, as in Fig. 37 shown is used. There, the centrifugal pump assembly with the integrated valve, as described above, characterized by the dashed line 1. The hydraulic circuit has a heat source 114 in the form of, for example, a gas boiler, whose outlet opens into, for example, the suction port 34 of the pump housing 12. At the pressure port 37 of the centrifugal pump assembly 1 closes in In this example, a floor heating circuit 116, whose return is connected both to the inlet of the heat source 114 and to the suction port 32 of the centrifugal pump assembly. Via a second circulating pump assembly 118, a further heating circuit 120 can be supplied with a heat carrier, which has the output-side temperature of the heat source 114. The floor heating circuit 116, however, 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 114 is mixed, by changing the opening ratios of the inputs 28h and 30h in the manner described above, the mixing ratio Rotation of the valve element 18h can be changed.

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

The storage and the drive of the valve element 18i in this embodiment is the same as in the ninth embodiment. In contrast to the valve element 18h, the valve element 18i has, in addition to the opening 112, a passage 122 which extends from an opening 124 in the lid 78i to an opening in the bottom of the base 76i and thus connects the two axial ends of the valve element 18i. Furthermore, in the valve element 18i, an arcuate bridging 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 lid 78i.

The pump housing 12 has, in addition to the pressure port 27 and the two previously described suction ports 34 and 32, a further port 128. The port 128 opens into an inlet 130 in the bottom of Umwälzpumpenaggregates 12 in addition to the inputs 28h and 30h in the suction chamber 24 into it. Based on FIGS. 43 to 46 the various switching positions are explained, in which case the lid 78i of the valve element 18i is shown partially opened to illustrate the position of the underlying openings. Fig. 43 shows a first switching position, in which the opening 112 facing the input 30h, so that a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is made. In the switching position according to Fig. 44 the opening 112 is located above the inlet 130 so that a flow connection is created from the connection 128 to the suction opening 36 and via this into the suction mouth 38 of the impeller 14. In another switching position, which Fig. 45 shows, the opening 112 is located above the entrance 30h, so that in turn a flow connection from the suction port 34 to the suction port 38 of the impeller 14 is given. At the same time, a partial overlap of the opening 124 and the through-hole 122 with the input 28h takes place, so that a connection between the pressure chamber 26 and the suction port 32 is made, which acts as a pressure port. At the same time, the bypass opening 126 concurrently covers the input 130 and a portion of the input 28h, thus also providing a connection from the terminal 128 via the input 130, the bypass opening 126 and the input 28h to the terminal 32.

Fig. 46 shows a fourth switching position in which the passageway 122 completely covers the entrance 28h, so that the connection 32 is connected via the through-passage 122 and the opening 124 to the pressure space 26. At the same time it covers the bridging opening 126 only the entrance 130. The opening 112 still covers the entrance 30h.

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

When the valve element 18i in the first in Fig. 43 is shown, the impeller 14 promotes liquid from the suction port 34 via the pressure port 27 through the heat source 140 and the heating circuit 120 and back to the suction port 34. Is the valve element 18i in the second switching position, which in Fig. 44 is shown, the plant is switched to domestic water operation, in this state, the pump assembly or the impeller 14 promotes liquid from the port 128, which serves as a suction port, through the pressure port 27, via the heat source 114 through the secondary heat exchanger 56 and back to the terminal 128. Is the valve element 18i in the third switching position, which in Fig. 45 shown is, the Bodenheizkreis 116 is additionally supplied. Via 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 114 in the manner described by the first heating circuit 120. At the same time, the liquid emerges on the output side of the impeller 14 from the pressure chamber 26 into the opening 124 and through the through-passage 122 and thus flows to the connection 32 and via this into the underfloor heating circuit 116.

In the in Fig. 45 The switch position shown flows simultaneously via the bridging opening 126 liquid via the terminal 128 and the input 130 into the terminal 32. That is, here water flows through the heat source 114 through the secondary heat exchanger 26 and the terminal 128 to the terminal 32. Since in this heating operation on Secondary heat exchanger 56 is removed substantially no heat, so the port 32 hot water in addition to the cold water, which flows from the pressure chamber 26 via the passage 122 to the port 32, admixed. By varying the degree of opening via the valve position 18i, the amount of hot water mixed in at port 32 can be varied. Fig. 46 shows a switching position in which the admixture is turned off and the terminal 32 is exclusively in communication with the pressure chamber 26 directly. In this state, the water is conveyed in the floor circuit 116 without heat in a circle. It can be seen that by changing the switching positions of the valve element 18i in this embodiment, 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 the heat source 114th and a floor heating circuit 116 having a reduced temperature via a mixing function.

It is to be understood that the various embodiments described above may be combined in various ways. Thus, the different types of drive described the valve element with different geometrical configurations of the valve element, as they have also been described above, can be combined essentially arbitrarily. The various valve functionalities (for example, mixing and switching) can also be implemented and combined with different drive types. These various combination possibilities, which result from the preceding embodiments, are insofar expressly included in the invention. In all embodiments shown, the valve element is arranged directly in the pump housing, that is, the pump housing forms a combined pump and valve housing. However, it is understood that the pump housing could also be designed in several parts. In particular, the valve element could also be arranged in a separate housing from the pump housing, which is connected to the pump housing, in which the impeller rotates, only via suitable connecting channels or pipelines.

LIST OF REFERENCE NUMBERS

1

A centrifugal pump unit

2

motor housing

4

stator

6

rotor

8th

rotor shaft

10

canned

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

26

pressure chamber

27

pressure connection

28, 30

inputs

28 ', 30', 28h, 30h

inputs

32.34

suction ports

36, 36 ', 36e

suction opening

38

saugmund

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

projections

74

spigot

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

lower part

78, 78d, 78h, 78i

cover

80

inlet opening

82.84

sleeves

86

stator

88

Weight

90

inlet opening

92

sealing surfaces

94

axis

96

tongue

98

pressure connection

100

ring segment

102

clamping ring

104

head Start

106

passage

108

clutch

110

counter-coupling

112

opening

114

heat source

116

Floor heating

118

circulation pump assembly

120

heating circuit

122

Through channel

124

opening

126

bridge opening

128

connection

130

entrance

X

axis of rotation

A, B

directions

Claims (20)

Centrifugal pump assembly with an electric drive motor (4, 6), an impeller driven by this (14) and at least one valve element (18) which is movable by the electric drive motor (4, 6) directly or indirectly along a first movement path between at least two switching positions .
characterized in that
at least a part of the valve element (18) additionally along a second, different from the first path of movement between a disengaged position in which the valve element is spaced from at least one contact surface and an adjacent position in which the valve element is applied to the at least one contact surface, is movable. Centrifugal pump unit according to claim 1, characterized in that the at least one valve element (18) with the drive motor (4, 6) mechanically and / or hydraulically coupled such that it by the drive motor (4, 6) along the first and / or the second movement path is movable. Centrifugal pump assembly according to claim 1 or 2, characterized in that the second movement path transverse to the first movement path or transversely to a plane in which the second movement path extends runs. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) along the first trajectory around a rotational axis (X) is rotatable, wherein the axis of rotation (X) is preferably parallel to or along the axis of rotation (X) of the impeller (14) extends. Centrifugal pump unit according to claim 4, characterized in that the at least one valve element (18) is rotatably mounted such that it is rotatable in the released position to a bearing and in particular a central bearing between the at least two switching positions and preferably non-rotatably in the second adjacent position is held on the contact surface. Centrifugal pump unit according to one of the preceding claims, characterized in that the second movement path is a straight line (X). Centrifugal pump assembly according to one of claims 4 to 6, characterized in that the second movement path is parallel to or along the axis of rotation (X) of the at least one valve element (18). Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one contact surface is a sealing surface. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) has a pressure surface which communicates with a pressure side (26) of the impeller (14) such that a pressure prevailing on the pressure side (26) the pressure surface acts and thus generates a compressive force acting on the valve element (18), wherein the pressure surface is located such that the pressure force is directed at least partially along the second movement path of the valve element (18) and in particular along the second movement path to the adjacent position is directed. Centrifugal pump assembly according to one of the preceding claims, characterized in that the at least one valve element (18) with at least one return element (48), in particular a return spring is coupled, which on the valve element (18) a restoring force along the second movement path, in particular to the in the released position. Centrifugal pump assembly according to one of the preceding claims, characterized by a force generating means which exerts a force on the valve element in the direction of one of the switching positions, wherein the force is preferably a spring force, a magnetic force and / or gravity. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) is designed such that it is movable by a by the impeller (14) in motion offset fluid flow along the first movement path. Centrifugal pump unit according to claim 12, characterized in that it is designed such that the impeller (14) depending on its direction of rotation generates differently directed fluid flows, through which the at least one valve element (18) along the first movement path in opposite directions is movable. Centrifugal pump unit according to one of the preceding claims, characterized in that it comprises a control device (17) which controls the electric drive motor (4, 6) such that the rotational speed and / or direction of rotation of the drive motor (4, 6) is variable. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) by a flow generated by the impeller (14) along the first movement path movable and by a by the impeller (14) generated fluid pressure along the second movement path is movable and the drive motor (4, 6) preferably has a control device (17) which is designed such that the drive motor (4, 6) has a first acceleration profile, in which the pressure builds up faster than the flow, and with a second acceleration profile , in which the flow builds up faster than the pressure, is approachable. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) for its movement along the first movement path with the impeller (14) or a shaft (8) of the drive motor (4, 6) driving the impeller (14). is coupled via a coupling, which is preferably pressure and / or speed and / or rotational direction dependent solvable. Centrifugal pump unit according to one of the preceding claims, characterized in that the at least one valve element (18) is designed and arranged such that in a pump housing (12) surrounding the impeller (14) one with a suction side (24) of the impeller (14). in connection with the suction chamber (24) separated by a pressure chamber with a side of the impeller (14) communicating pressure chamber (26). Centrifugal pump assembly according to one of the preceding claims, characterized in that the at least one valve element (18) is designed and arranged such that it is in a the pump housing (12) surrounding the impeller (14) separates a suction chamber (24) communicating with a suction side of the impeller (14) from a pressure chamber (26) communicating with a pressure side of the impeller (14), wherein in the pressure chamber ( 26) a flow generated by the impeller (14) acts on the valve element (18) to move along the first movement path and the suction space (24) is configured such that the flow prevailing there does not exert any force on the valve element (14) in the direction the first trajectory exerts. Centrifugal pump unit according to one of the preceding claims, characterized in that it comprises at least two alternative flow paths, wherein the at least one valve element (18) is arranged in these flow paths such that in the at least two switching positions these flow paths are opened differently. Centrifugal pump unit according to claim 19, characterized in that the two flow paths are located on the suction side of the impeller (14).

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