WO2018166975A1 - Pump assembly - Google Patents

Abstract

The invention relates to a pump assembly having an electric drive motor (4, 6), at least one impeller which is driven by the drive motor (4, 6), and at least one valve device (18) which lies in a flow path through the pump assembly and can be moved 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 such a way that a movement of the drive motor (4, 6) is transmitted to the valve device (18), and the valve device can be moved from the first into the second switching position by way of a rotational movement of the drive motor (4, 6), and that the first coupling can be released by way of an increase of the rotational speed of the drive motor (4, 6) and/or an increase of the pressure on the output side of the impeller and/or by way of slip, in such a way that the coupling action between the drive motor (4, 6) and the valve device (18) is reduced or cancelled.

Description

 pump unit

description

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

[02] Pump units are known, which include a valve device that makes it possible to switch between two possible flow paths through which the pump unit promotes. In this case, valve devices are known which switch depending on the direction of rotation of the centrifugal pump assembly, or depending on the direction of rotation to direct the flow in different flow paths. For example, from DE 9013992 U l such a pump unit is known, which has a switching device, with the aid of which can be switched between two inputs of the pump unit to selectively suck liquid from one of the two inputs. The pump unit disclosed therein has a relatively complicated mechanism, which has a flow-side element located on the pressure side, which is flowed by the output-side flow generated by the centrifugal pump unit and can be moved into two different positions, depending on the direction of rotation and flow direction. About a connected to the flow element lever system, a valve element is switched on the suction side of the pump unit between two inputs. [03] In view of this prior art, it is an object of the invention to improve a pump unit with an integrated valve device to the effect that a simpler construction of the pump unit is achieved with increased reliability of the switching function of the valve device.

[04] This object is achieved by a pump unit having the features specified in claim 1. Preferred embodiments will become apparent from the subclaims, the following description and the accompanying figures. [05] The pump unit according to the invention is a centrifugal pump unit. The pump unit has an electric drive motor, which is preferably a wet-running electric drive motor, d. h., Is designed as a canned motor. The pump unit according to the invention can be designed, for example, for use in a heating and / or air conditioning system as a circulating pump. The pump unit is designed in particular for the delivery of water.

[06] The pump unit has at least one impeller, which is driven by the drive motor. Furthermore, a valve device, which is movable at least between a first and a second switching position, is integrated in the pump unit. In this case, the valve device is preferably designed such that it provides a valve function for the fluid flow conveyed by the pump unit. [07] According to the invention, the valve device is designed such 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. † or coupled, that the valve device is movable by a rotational movement of the drive motor from the first to the second switching position. This means that the movement of the drive motor can be transmitted by the first clutch to the valve device, 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, via the corresponding rotational movement of the drive motor to move the valve device back again from the second to the first switching position. According to the invention, the first clutch is further designed so that it can be released by increasing the rotational speed of the drive motor and / or increasing the pressure on the output side of the impeller and / or slip such that the coupling action between the drive motor and the valve device is reduced or eliminated. This makes it possible to use the drive motor targeted 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 means. Expediently, the valve device is designed so that in the normal operating state of the pump unit, ie when fluid is delivered by the impeller in normal operation, the clutch is released, so that the valve element remains in a switched position in this state. [08] According to a specific embodiment of the invention, a transmission 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 transmission can be designed as a reduction gear, which has a rotational speed of the valve device or of a valve element of the valve device. reduced compared to the speed of the drive motor. Alternatively or additionally, a rotational movement of the drive motor could be converted into a linear movement of the valve element by a gear, such as a spindle drive. [09] The drive motor is preferably electronically controlled or controlled, so that it can be driven at different speeds and / or in different directions of rotation. For this purpose, a control device may be provided which controls or controls the drive motor in a corresponding manner. In particular, the control device may be equipped with a frequency converter for speed change 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 such that the drive motor runs at different speeds, but also different acceleration gradients during acceleration and / or deceleration of the drive motor can be realized.

[10] The embodiment according to the invention has the advantage that, on the one hand, a separate drive motor for the valve device can be dispensed with, and on the other hand, complicated mechanisms for transmitting a force generated by the flow to a valve element can be dispensed with. The power transmission can rather be done by the first clutch. In addition, the efficiency of the pump unit can be improved because the valve device does not affect the normal operation substantially. [1 1] 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 a switching position the valve means defined and the valve means between the two switching positions is movable. This movement takes place via the first clutch and by appropriate control of the drive motor, in particular via the described control device. [12] Preferably, the valve device has no further electrically operated switching elements for switching and / or holding the valve device. Rather, the valve device is moved solely by the drive motor between the switching positions.

[13] According to a preferred embodiment of the invention, 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 coupling is movable by the pressure on the output side of the impeller from a dissolved first coupling position to a holding coupling position. In this case, the at least one releasable coupling does not have to act directly on the pump housing, but rather can also indirectly stop the pump housing by engaging the coupling with a component connected to the pump housing. It is essential in the design of the second releasable coupling that it prevents a movement of the valve device in its holding second coupling position. In this case, the second releasable coupling preferably engages in an operating state of the pump unit in holding engagement, ie, in its holding second coupling 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 rotational speed and / or a lower acceleration, the valve device can be moved into a desired switching position. Subsequently, it can be achieved by a speed increase and / or in particular a strong acceleration of the drive motor that the second releasable clutch engages in a holding engagement † ri †† so that the valve device remains in the switching position and is held. At the same time, preferably the first clutch is disengaged or has a slip which allows the second rotation of the drive motor with the impeller. Preferably, the first and the second clutch are formed such that the first clutch in its released position has a lower holding force than the second clutch in its holding second coupling position. Conversely, the first clutch in its coupled position preferably has a greater holding force than the second clutch in its dissolved first coupling position. This means that the first clutch, when engaged, can transmit greater force or torque than the second clutch in its disengaged first clutch position. Thus, in this switching state, the valve element can be moved between the switching positions. When the first clutch is in its released position and the second clutch 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 its reached switching position and not by the Drive motor can be moved over the first clutch.

[15] More preferably, the drive motor is configured so that it generates a torque during operation of the pump unit, which is greater than the holding force of the first clutch in its coupled position. This prevents that the first clutch would prevent the rotation of the drive motor and thus of the impeller in normal operation of the pump unit.

[16] The valve device may preferably be designed as a changeover valve, which allows switching between two flow paths. Alternatively or additionally, the valve device may have a Be mixing means 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, for example, between two switching positions, which define the end positions, in several stages or continuously movable. The use as a switching valve can be used for example in a heating system in which a changeover valve is required to switch a heat transfer fluid flow between a heat exchanger for heating domestic water and at least one heating circuit for heating a building. Also, a mixing device can be used in a heating system, for example, to reduce the temperature of a heat carrier by mixing liquid from a return of the heating system. This can be z. B. be useful for use for underfloor heating, in which it is usually necessary to reduce the flow of a boiler provided flow temperature by mixing heat transfer medium from the return. [17] The valve device may 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. Thus, the valve device may 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 from a first or a second suction-side flow path sucks liquid. Alternatively, a switching device could be arranged on the pressure side, so that the pump unit promotes depending on the switching position of the valve device in a first or a second pressure-side flow path. If the valve device is designed as a mixing device, this may for example be arranged on the pressure side, that two flow paths in the mixing device open into a mixing point on the pressure side and that, depending on the switching position of the valve device, the mixing ratio between the two flow paths is changed. In this case, preferably one of the two flow paths downstream of the pump unit passes through a heat exchanger of a heating or cooling device in order to temper the liquid conveyed by the pump unit, ie to heat or cool it. In the other flow path is preferably non-tempered liquid, which can then be mixed with the tempered liquid in the mixing device. Alternatively, a mixing device could be arranged on the suction side of the pump unit, so that the pump unit z. B. sucks a mixed from two flow paths liquid.

[18] 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 preferably at least one is 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 past the desired shift 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.

[19] According to another preferred embodiment of the invention, the valve device has at least one movable valve element which cooperates with two valve openings such that a first valve opening in the first switching position of the valve device is covered more by the valve element than in the second Switching position and a second valve opening of the valve element in the second switching position is more covered than in the first switching position. If the valve element is designed as a changeover valve, in the first switching position the second valve opening is opened and the first valve opening is closed. In the second switching position, conversely, the second valve opening is closed and the first valve opening is opened. In the case of the configuration of the valve device as a mixing device preferably intermediate positions or intermediate switching positions are possible in which the two valve openings are open simultaneously, but at different levels. By changing the opening degrees of the two valve openings, such a mixing ratio can be changed. Preferably, the at least one movable valve element is designed so that, when a valve opening is opened by a certain amount, at the same time the other valve opening is closed by the same amount.

[20] Such an interaction of the closing of the two valve openings can be realized with a valve element, but also with two valve elements, when they are mechanically coupled together. According to a further preferred embodiment, the valve device has a movable valve element, which has at least one sealing surface and a pressure surface, wherein the pressure surface is in communication with a pressure chamber surrounding the impeller such that the valve element by the pressure acting on the pressure surface the sealing surface is pressed against a contact surface, wherein the contact surface preferably forms a valve seat. In such an embodiment, the valve element can take over the function of the second clutch described above, together with the contact surface. If the valve element is pressed against the contact surface by the pressure in the pressure chamber, see the sealing surface and the contact surface preferably such a frictional engagement that the valve element is fixed in the reached switching position. This frictional engagement could be additionally supported by a form fit with appropriate design of sealing surface and contact surface. If the system is a valve seat, a seal is simultaneously achieved by the installation of the sealing surface. When the pressure in the pressure space is lower, the sealing surface preferably disengages from the abutment surface or preferably a valve seat, thus ensuring easy movability of the valve element with reduced friction. The valve seats may preferably surround valve openings as described above. By the system of at least one sealing surface then a sealing of the flow paths is achieved to the outside. Furthermore, a sealing surface can also be pressed against a contact surface or a valve seat such that a seal between the suction chamber and the pressure chamber of the pump unit is achieved by the system. Thus, a plurality of valve seats may be provided, on which one or more sealing surfaces of the valve element come into contact with the sufficiently high pressure in the pressure chamber to achieve the required seals the flow paths. Preferably, a return element, such as a return spring, may be provided, which disengages the valve element with the sealing surface of the contact surface when the pressure in the pressure chamber below a predetermined value, ie, the force generated by the pressure in the pressure chamber at the pressure surface less is determined as the restoring force generated by the return element. So easy mobility of the valve element is ensured at low pressure.

[22] The valve device may further preferably comprise a rotatable valve element. D. h., The valve element is moved between the switching positions by rotating movement, wherein the axis of rotation more preferably with the axis of rotation of the impeller or the drive motors aligned, which allows a particularly simple coupling without further gear means. The rotatable valve element is preferably detachably coupled via the first coupling to a rotor of the drive motor, wherein the coupling does not have to engage the actual magnet rotor, but can also engage a component connected to the magnet rotor, such as a shaft or the impeller. When the first clutch engages, the rotatable valve element is rotationally moved via the rotor of the drive motor.

[23] The drive motor is preferably drivable in two directions of rotation and the valve device is designed such that its first switching position is achieved by driving the drive motor in a first rotational direction and the second switching position by driving the drive motor in a second rotational direction. Instead of a movement of the valve element by the drive motor in two directions of rotation and a restoring means or force generating means may be provided which rotates the valve element when switching off the drive motor in a predetermined starting position or switching position. This may be, for example, a magnetic return means, a return means acting by spring force or by gravity. [24] The first and / or the second clutch may preferably be a friction clutch, a magnetic clutch and / or a hydraulic clutch, which more preferably have a slip. If the first clutch has slippage, this makes it possible for the drive motor, after reaching a predetermined switch position, when the valve element of the valve device or the valve device is fixed in the switch position, to be able to continue rotating without being blocked by the fixation of the valve device. Thus, for example, a valve element abut against a stop, whereupon the clutch then slips or the drive motor can continue to rotate due to the slip in the clutch. Especially train † a hydraulic coupling can be realized via the liquid jet conveyed by the impeller. Thus, the fluid from the impeller inside a pump housing can be contaminated in the rotational direction of the impeller in Rofafion and move by friction on a part of the Venfileinrichfung, in particular directly on the Venfilelemenf, this. When the Venfilelemenf or Venfileinrichfung reaches a Schalfsfellung and is fixed there, sfrömf the hydraulic flow weir, with only the usual hydraulic friction losses occur on the surfaces. D. h., Can be used to move the Ventileinrichfung essentially existing anyway Verlusfenergie, which is converted into a movement of the Ventileinrichfung or the Ventilelemenfes.

[25] More preferably, the first coupling has at least one coupling element movable between a coupled position and a released position, the direction of movement between the coupled and the released position preferably being transverse to a force of the force to be transmitted by the coupling to the Venfil device. In the coupled position there is a Krff- and / or positive engagement between the Kupplungselemenf and an opposite coupling surface. The Kupplungselemenf is movable so that it can be disengaged from the clutch surface, so that the Venfilelemenf is then no longer moved or taken and remains in its assumed Schalfsfellung. The direction of movement between the coupled and disengaged position is preferably in a direction other than the force transmission direction, thereby ensuring that the coupling element is not disengaged by the force to be transmitted. Particularly preferably, the direction of movement is normal to the Kraffrichtung or a plane in which the Kraffrichtung runs. The latter may for example be the case when the clutch is used to transmit a torque. Then the movement direction Preferably along the axis of rotation and thus transversely and in particular normal to the plane in which the force is transmitted.

[26] Particularly preferably, a valve element of the valve device can simultaneously form the movable coupling element. Thus, the valve member may have a coupling surface engageable with an opposed coupling surface, which is preferably disposed on the rotor or impeller, for moving the valve element, in particular for rotational movement. In this case, a positive and / or positive engagement may be provided. The coupling element may also be expediently acted upon by a biasing element with a biasing force, which forces the coupling element in the coupled position. This means, in the rest position, the first clutch is in coupling engagement. 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 turned off, this clutch disengaging force drops again so that the biasing force forces the clutch back into the coupled position.

[27] More preferably, the coupling element has a pressure surface which is in communication with a pressure chamber surrounding the impeller and is arranged such that a pressure acting on the pressure surface generates a force which is opposite to the biasing force. When the pressure in the pressure space increases to such an extent that the compressive force generated at the pressure surface exceeds the pre-tension force, the coupling element is displaced, being arranged to move to its released position during this displacement, ie the first one Clutch is disengaged and the valve element is not moved further by the drive motor, but remains in its assumed switching position. When the pressure drops, for example, when the pump set stops. is switched, the compressive force decreases and the biasing force is again the larger force, so that the clutch is moved back into the coupled position. The next time the drive motor starts, the valve element or the valve device can then be moved again into another switching position.

[28] According to a further preferred embodiment of the invention, the coupling element may have a coupling surface which is in frictional contact with a counter-coupling surface in the coupled position, the coupling surface and the counter-coupling surface being formed and surrounded by a lubricant which is between the clutch surface and the counter-coupling surface forms a friction film canceling the friction contact when the rotational speed of the drive motor is increased. The lubricant used is preferably the liquid conveyed by the pump unit, for example water. The coupling then works like a plain bearing. At sufficiently high speed forms between the clutch surface and the counter-coupling surface of a lubricating film, so that the frictional contact between the surfaces is canceled and these slide off each other in the manner of a sliding bearing. Thus, a clutch can be created, which is disengaged by speed increase. That is, when the drive motor is moved at a low speed, the valve element is moved via the frictional contact between the clutch surface and the counter-clutch surface located between the rotor and the valve device, so that the shift position is changed can be. Subsequently, the drive motor can be increased in its speed so far that the frictional contact is canceled as described and the valve device remains in the achieved switching position. [29] When a purely hydraulic clutch is used between the drive motor and the valve device, the disengagement can be achieved by hydraulic slippage, in which case the valve device is preferably fixed in the desired switching position in the manner described above by a second clutch. In such an embodiment, it is possible to hold the valve element with appropriate acceleration of the drive motor in its initial position without being moved by the hydraulic clutch. This can be achieved by accelerating the drive motor so fast that a pressure build-up which moves the second clutch into the coupled clutch position takes place so fast that the second clutch engages before there is a displacement of the valve element and thus comes to a change in the switching position of the valve device. [30] The invention will now be described by way of example with reference to the accompanying drawings. In these shows:

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

2 is a perspective view of the underside of the valve element of the centrifugal pump assembly of FIG. 1,

Fig. 3 is a perspective view of the pump housing of

 Centrifugal pump unit according to FIG. 1 in the opened state,

Hg. 4 is a sectional view of the centrifugal pump assembly according to

Fig. 1, 5 shows 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 shows a sectional view corresponding to FIG. 5 with the valve element in a second switching position, FIG.

7 shows schematically the hydraulic construction with a heating system with a centrifugal pump assembly according to FIGS. 1 to 6, FIG. 8 shows an exploded view of a centrifugal pump assembly according to a second embodiment of the invention,

9 is a sectional view of the centrifugal pump assembly according to

 FIG. 10 shows a sectional view corresponding to FIG. 9 with the valve element in a second position, FIG. 11 shows an exploded view of a centrifugal pump assembly according to a third embodiment of the invention, FIG. 12 shows a sectional view of the centrifugal pump assembly according to

1 with the valve element in a first position, FIG. 13 is a sectional view corresponding to FIG. 12 with the valve element in a second position, FIG. 14 is an exploded view of a pump housing having a valve element according to a fourth embodiment of the invention; FIG. 15 is a sectional view of a centrifugal pump assembly according to the fourth embodiment of the invention;

Fig. 1 6 is an exploded view of a centrifugal pump assembly according to a fifth embodiment of the invention, Hg. 1 7 is a sectional view of the centrifugal pump assembly according to

 Fig. 1 6 with the valve element in a first position, Fig. 18 is a sectional view corresponding to Fig. 1 7 with the valve element in a second position, Fig. 19 is an exploded view of a centrifugal pump assembly according to a sixth embodiment of the invention, Fig. 20 is a sectional view of Centrifugal pump units according to

 Fig. 19,

Fig. 21 is a plan view of the opened pump housing of

Centrifugal pump assemblies according to FIGS. 19 and 20 with the valve element in a first switching position, Hg. 22 is a plan view corresponding to FIG. 21 with the valve element in a second switching position, FIG. 23 is an exploded view of a pump housing with a valve element according to a seventh embodiment of the invention; FIG. 24 is an exploded view of the pump housing with valve element according to the seventh embodiment seen from another side;

Fig. 25 is an exploded view of a centrifugal pump assembly according to an eighth embodiment of the invention, Fig. 26 is a sectional view of the centrifugal pump assembly according to

 Fig. 25,

Fig. 27 is a plan view of the opened pump housing of

 Centrifugal pump assemblies according to FIGS. 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,

29 shows an exploded view of the centrifugal pump assembly according to a ninth embodiment of the invention, FIG. 30 shows a perspective view of the centrifugal pump assembly according to FIG. 29 with the pump housing and valve element removed,

31 is a perspective view of the motor shaft of the centrifugal pump assembly of FIG. 29 and 30 and the coupling part of the valve element, FIG. 32 shows a sectional view of the centrifugal pump assembly according to FIG. 29 with the valve element in a first position, FIG. 33 shows a sectional view according to FIG. 32 with the valve element in a second position, FIG. 34 shows a plan view of the opened pump housing of FIG

 Centrifugal pump unit according to FIGS. 29 to 33 with the valve element in a first switching position,

36 shows a view according to FIGS. 34 and 35 with the valve element in a third switching position, FIG. 37 shows schematically the hydraulic structure of a heating system with a centrifugal pump unit according to 39 to 36, Fig. 38 is an exploded view of a centrifugal pump assembly according to a tenth embodiment of the invention, Fig. 39 is a perspective view of the open valve element of the centrifugal pump assembly of FIG. 38, Fig. 40 is a perspective view of the closed valve element of FIG.

Hg. 41 is a sectional view of the centrifugal pump assembly according to

38 with the valve element in a first position, a sectional view according to FIG. 41 with the valve element in a second position, a plan view of the opened pump housing of the centrifugal pump assembly according to FIGS. 38 to 42 with the valve element in a first switching position, a view according to FIG. 43 with the valve element in a second switching position, FIG. a view according to FIGS. 43 and 44 with the valve element in a third switching position, a view according to FIGS. 43 to 45 with the valve element in a fourth switching position and schematically the hydraulic structure of a heating system with a centrifugal pump assembly according to FIGS. 38 to 46 ] The embodiments described in the following description of the pump unit according to the invention in the form of a centrifugal pump assembly relate to applications in heating and / or air conditioning systems in which of the centrifugal pump unit, a liquid heat transfer medium, in particular water is circulated. [32] 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 Gate space, in which the stator 4 is arranged, is separated by a split tube or a split pot 10. That is, this 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 axial end of the motor housing 2, which is opposite the pump housing 12, an electronics housing 16 is arranged, which contains an electronic control unit or control device for controlling the electric fresh drive motor in the pump housing 2. The electronics housing 16 could be arranged in a similar manner to another soap of the Sfatorgehäuses 2.

[34] In addition, a venfil device with a movable venfil 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 Ventilelemenfes 18 is aligned with the axis of rotation X of the impeller 14. The axis 20 is fixed drehfesf at 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 Bewegbarkeif is limited by the pump housing 12, against which the Venfilelement 18 with its outer circumference. In the opposite direction, the movable bar is limited by the nut 22 with which the valve element 18 is mounted on the axle 20. It should be understood that instead of the nut 22, another axial attachment of the valve element 18 to the axle 20 could be selected.

The Venfilelement 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 Pressure port 28 of the centrifugal pump unit connected, which forms the outlet of the centrifugal pump unit. In the suction chamber 24 open two suction-side inputs 28 and 30, of which the input 28 to a first suction port 32 and the input 30 to a second suction port 34 of the pump housing 12 is connected.

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 in this exemplary embodiment are located on closed tubular connecting pieces. 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 to the axis of rotation X, but on a radially offset straight line, so that upon rotation of the valve element 18 about the rotation axis X in a first switching position, the input 38 is closed by a sealing surface 40, while the support elements 42nd lie at the entrance 30 and open it. In a second switching position, the input 30 is closed by a sealing surface 40, while the support elements 42 in Um- catch area of the input 28 and open this. The first switching position, in which the input 38 is closed and the input 30 is open, is shown in FIG. The second switching position, in which the input 30 is closed and the input 28 is opened, is shown in FIG. 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 element 18 is not close to the pump housing 12 and the sealing surfaces 40 not tight in the peripheral region the inputs 28 and 30 abut, 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 1 6, 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. That is, via the rotating flow, a first hydraulic clutch between the drive motor and the valve element is formed. 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 can be rotated between the two limited by the stops 46 switching positions. [38] When the impeller 14 rotates at a sufficient speed, a pressure builds up in the pressure space 26, which generates on the surface of the valve element 18, which surrounds the suction opening 36, a pressure force which is opposite to the spring force of the spring 48 in 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 sealingly abuts 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 device forms a second clutch which fixes the valve element. 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 service 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, and to use the opposite direction of rotation only for moving the valve element 18 in the opposite direction of rotation. When the valve element 18 is in its adjacent position in which a frictional engagement ge 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 turning the valve element 18. That is, the hydraulic first clutch formed between the impeller 14 and valve member 18 is disengaged by slip.

[39] The described centrifugal pump unit according to the first embodiment of the invention can be used, for example, in a heating system as shown in FIG. 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. [40] The second embodiment according to FIGS. 8 to 10 differs from the first embodiment in the construction of the valve element 18 '. Also in this embodiment, 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', 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 by the impeller 14 in the pressure chamber 26, which forms a first hydraulic clutch. 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 unit 1 is taken out of service, Pressing the spring 48, the valve element 18 'in the position shown in Fig. 10 dissolved position in which it does not abut the bottom in the periphery of the inputs 28' and 30 '. That is, 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 by this stop in its axial movement. When the pressure in the pressure space 26 is sufficiently large, the valve element 18 'is pressed into the fitting position shown in FIG. 9, in which the valve element 18' comes to rest at the bottom of the pump housing 12 in the peripheral area of the inputs 28 'and 30' and at the same time the pin 24 is lifted from the end face of the rotor shaft 8. That is, the second clutch is engaged. In this position, the impeller 14 then rotates during normal operation of the circulating pump unit. That is, the hydraulic first clutch is disengaged by slip. [41] The third embodiment according to Figures 1 1 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 essentially corresponds to the structure according to FIGS. 1 to 6, the arrangement of the inputs 28 and 30 corresponding in particular to the arrangement described with reference to the first embodiment. The valve drum of the valve element 18 "consists of a cup-shaped bottom part, which is closed by a cover 78. The lid 78 faces the pressure chamber 26 and has the central suction opening 36, which with its axially directed collar into 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 inputs 28, 30, while the respective other inlet 28, 30 passes through 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. Also in this embodiment, the valve element 18 "along the axis 20 by a certain amount axially displaceable, whereby also a spring 48 is provided, which presses the valve element 18" in its rest position in Fig. 13 shown dissolved position. Thus, here too, a releasable second coupling is provided for holding the valve element 18 ".The released axial position is also limited in this embodiment by the nut 22. In the released position, the valve element 18" is, as described above, by the flow which is rotatable, that is to say a hydraulic coupling (first coupling) is produced between impeller 14 and valve element 18 '' as described above, in the abutting position which is shown in FIG. Depending on the switching position, one of the inlets 28, 30 is sealed tightly on the other hand, and sealing between the suction chamber 24 and the pressure chamber 26 takes place by abutment of the valve element 18 "on the abutment shoulder 50.

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

[43] FIGS. 14 and 15 show a fourth embodiment in which the structure of the pump housing 12 is the structure of the pump housing 12 according to the first and third embodiments equivalent. 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. Since in a circulatory system, in which a centrifugal pump unit, as described here, is used, and the suction-side flow is generated by the centrifugal pump unit, an indirect coupling of the impeller 14 is provided with the valve element 18c also on the suction-side flow, which a represents first hydraulic coupling. Also in this embodiment, the valve element 18c is formed substantially drum-shaped and has a pressure chamber 26 facing the lid 28 with the central suction port 36, which with the suction mouth 38, as described above, is engaged. The lower part shown here 76b has two inlet openings 80, which can be brought to cover depending on the switching position with one of the inputs 28, 30, wherein the respective other input 28, 30 is sealed by the bottom of the lower part 46b, as in the preceding Embodiment has been described. 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 , which is shown in FIG. 15, in which rather, 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. That is, here is a second clutch, as described above, realized. It is to be understood that a provision of the valve element by gravity or another restoring force independently of the drive could also be used in the other embodiments described here. When the valve member 18c is in the abutting position, the first clutch formed by the stator 86 disengages from slippage, that is, the flow continues through the stator but without causing rotation of the valve member 18c. [44] The fifth embodiment according to FIGS. 1 to 18 differs from the preceding embodiments 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 inlet openings 90 are formed, which can be brought by rotation of the valve element 18d with inputs, which are connected to the suction ports 32 and 34, optionally to cover to a Flow path through the interior of the valve element 18 d 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 exemplary embodiment two according to FIGS. 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 rotatably supports the valve element 18d about the rotation axis X there. Here, too, an axial movement between a released position, as shown in Fig. 18, and an abutting position, as shown in Fig. 1 7, possible to form a releasable second clutch. 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 a first hydraulic clutch, 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 again by stops, not shown. In the adjacent position shown in FIG. 17, on the one hand, a tight contact of the valve element 18d, on the other hand it is frictionally held, so that it again, 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 between the switching positions is moved. [45] The sixth embodiment according to FIGS. 19 to 22 is similar to the exemplary embodiment two according to FIGS. 8 to 10. The pump housing 12 substantially 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 '. Only the missing Projections 72 and the pin 74. The opening 62, however, is also formed. 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.

[46] Depending on the switching position of the valve element 18e, the opening 62 comes to rest either above the inlet 28 'or the outlet 30' 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 , Also in this embodiment, the valve element 18e is additionally movable axially along the rotation axis X, which is the rotation axis of the impeller 14 and the valve element 18e, to form a second clutch. In a rest position, in which the centrifugal pump naggregat 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 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 switching position, in which the opening 62 opposite the input 28 ', Fig. 22 shows the second switching position, in which the opening 62 opposite the second input 30'.

[47] In this embodiment, the rotation of the valve element 18e again takes place via the impeller 14, but here a mechanical coupling is provided as the first coupling, which is realized by the impeller 14 frictionally engaging on its circumference with its region surrounding the suction mouth 38 the suction port 36e comes to rest. Thus, the valve element 18e is rotated with the impeller 14 until the pin 68 reaches a stop. Then the coupling occurs reason of slip disengaged. With increasing pressure in the pressure chamber 26, the valve element 18e is then axially moved to its abutting position, as described above, in which thus the second clutch is engaged and the first clutch disengages from the impeller 14, so that the impeller 14 then can rotate substantially frictionless.

The seventh exemplary embodiment according to FIGS. 23 and 24 differs from the sixth exemplary embodiment described above in that a tongue 96 extending into the pressure chamber 26 is arranged on the valve element 18f, which tongue serves as an additional valve element in the pressure chamber 26. The pump housing 12 has an additional pressure port 98, which opens separately to the pressure port 27 into the pressure chamber 26. Depending on the switching position of the valve element 18f, the tongue 96 can release the pressure port 27 or the pressure port 28 which 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 simultaneously 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 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 In this embodiment, the Venfilelemenf 18f is mounted on the Roforwelle 8.

The eighth embodiment according to FIGS. 25 to 28 differs from the sixth embodiment in the design of the first 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 are arranged with slide 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. 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 remains in the valve element 18g which effects the valve function.

The passageway 106 may face the entrance 30 'in a first switching position shown in FIG. 27 and be opposite the entrance 28' in a second switching position shown in FIG. 28. 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 a first clutch by the drive of the impeller 14. The rotor shaft 8 is at the start of non-positively on the inner circumference of the ring segments 10 and turns them, 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. When the valve element 18g reaches one of these stops, the pump shaft 8 slips inside the ring segments 100, ie the coupling disengages. With increasing speed of the rotor shaft 8 can see between the outer periphery of the rotor shaft 8 and the inner surfaces of the ring segments 100 form a lubricating film in the manner of a sliding bearing beyond, so that the rotor shaft 8 can then rotate substantially frictionless in the interior of the ring segments 100. This means that for adjusting the valve element 18g between its two switching positions of the drive motor of the control device 1 7 is preferably moved 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, in the manner described above, are driven 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 attachment to the bottom of the pump housing 12 remains in the previously reached switching position. In the ninth and tenth embodiment of 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 1 7 in two different modes or operating modes is controllable. In a first mode, which corresponds to the normal operation of the circulating pump unit, the drive motor rotates in conventional Way 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. [53] In the ninth embodiment according to FIGS. 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.

[54] The motor housing 2 with the electronics housing 16 corresponds to the embodiment described above. The pump housing 12 is substantially the same as the pump housing according to the first embodiment shown in 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 lid 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. In this case, the axis of rotation of the valve element 18h, as in the examples described above, corresponds to 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 for forming a second releasable coupling and is urged by a spring 48 into the rest position shown in FIG. 33, 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, the valve element 18h is rotatable substantially freely about the axis 20. As an axial stop acting in the released position, the front end of the Roforwelle 8h, which is designed as a first clutch 108. The clutch 108 engages with a counter-clutch 110 which is rotationally fixed to the venfil element 18h. 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 counter-coupling 110 is possible only in one rotational direction, namely in the direction of rotation A in FIG. 31. In the opposite direction of rotation B, however, the clutch slips through, resulting in an axial movement of the Ventilelemenf 18h. The rotational direction B is the direction of rotation in which the pump unit is driven in normal operation. The direction of rotation A, on the other hand, is used for the targeted adjustment of the Venfil element 18h. This means that a rotation-dependent first clutch is formed here. In addition, however, occurs in this embodiment, the counter-coupling 1 10 of the clutch 108 by the pressure in the pressure chamber 26 disengaged. If the pressure in the pressure chamber 26 increases, a pressure kraff acts on the cover 78h which opposes 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 FIG. In this, the lower part 76h is located on the bottom side of the pump housing 12, so that on the one hand the Venfilelement 18h is held kraffschlüssig and on the other a dense system is achieved, which seals the pressure and the suction side in the manner described below against each other.

[55] 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 into its interior, that is to say the suction chamber 24. The lower part 76h of the valve element 18h has in its bottom a arcuate opening 1 12, which extends substantially over 90 °. FIG. 34 shows a first switching position, in which the opening 1 12 only covers the entrance 30 h, so that a flow path is given only from the suction connection 34 to the suction opening 36 and thus to the suction mouth 38 of the impeller 14. The second input 28 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 1 12 covers only the input 28h, while the entrance 30h is closed. In this switching position, a flow path from the suction connection 32 to the suction mouth 38 is merely open. Fig. 35 now shows an intermediate position in which the opening 1 12 covers both inputs 28h and 30h, wherein 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.

[56] Such functionality may be used, for example, in a hydraulic system as shown in FIG. 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 1 14 in the form of, for example, a gas boiler, whose outlet opens into, for example, the suction connection 34 of the pump housing 12. The pressure connection 37 of the centrifugal pump assembly 1 is followed in this example by a floor heating circuit 16 whose return is connected both to the inlet of the heat source 14 and to the suction connection 32 of the centrifugal pump unit. A second circulating pump unit 1 18 can supply a further heating circuit 120 with a heat carrier, which supplies the output side Temperature of the heat source 1 14 has. The floor heating circuit 1 1 6, however, can be regulated in its flow temperature in such a way that cold water from the return to the hot water on the outlet side of the heat source 1 14 is mixed, whereby by changing the opening conditions of the inputs 28h and 30h, in the manner described above, the mixing ratio can be changed by rotation of the valve element 18h.

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

[58] The bearing and the drive of the valve element 18i are the same in this embodiment as in the ninth embodiment. In contrast to the valve element 18h, the valve element 18i has, in addition to the opening 12, a passage 122 which extends from an opening 124 in the lid 78i to an opening in the bottom of the lower part 76i and thus connects the two axial ends of the valve element 18i , Furthermore, in the valve element 18i, an arcuate bypass opening 126, which is open only to the underside, that is to the bottom of the lower part 76i and thus to the suction chamber 24, is formed which is closed to the pressure chamber 26 by the cover 78i.

The pump housing 12 has, in addition to the pressure port 27 and the two previously described suction ports 34 and 32, a further port 128. The port 128 opens into an inlet 130 in the bottom of Umwälzpumpenaggregates 12 in addition to the inputs 28h and 30h in the suction chamber 24 into it. The various switching positions are explained with reference to FIGS. 43 to 46, in which Figures of the cover 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 1 12 faces the entrance 30h, so that a flow connection is produced from the suction connection 34 to the suction mouth 38 of the impeller 14. In the switching position according to FIG. 44, the opening 12 lies above the inlet 130, so that a flow connection is created from the connection 128 to the suction opening 36 and via this into the suction mouth 38 of the impeller 14. In a further switching position, which shows Fig. 45, the opening 1 12 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 simultaneously covers the input 130 and a part of the input 28h, so that a connection is also provided 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 through-channel 122 completely covers the input 28h, so that the connection 32 is connected to the pressure space 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 12 also covers the entrance 30h.

[61] Such a centrifugal pump unit can be used, for example, in a heating system as shown in FIG. 47. There, the dashed line bounds the centrifugal pump unit 1, as has just been described with reference to FIGS. 38 to 46. The heating system In turn, † em has a primary heat exchanger or a heat source 14, which may be, for example, a gas boiler. On the output side, the flow path extends into 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 comprises a floor heating circuit 1 1 6. The returns of the heating circuit 120 and the floor heating circuit 1 1 6 open into the suction port 34 on the pump housing 12. The return from the secondary heat exchanger 56 opens into the port 128, which, as will be described below, offers two functionalities. The terminal 32 of the pump housing 12 is connected to the flow of the floor heating circuit 1 1 6.

[62] When the valve element 18i is in the first switching position shown in FIG. 43, the impeller 14 conveys liquid from the suction port 34 via the pressure port 27 through the heat source 140 and the heating circuit 120 and back to the suction port 34 Valve element 18i in the second switching position, which is shown in Fig. 44, the system 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, over the heat source 1 14 through the secondary heat exchanger 56 and back to the terminal 128. If the valve element 18i in the third switching position, which is shown in Fig. 45, in addition the underfloor heating circuit 1 16 is 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 14 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 passage 122 through and flows to the terminal 32 and via this in the floor heating 1 16.

In the switching position shown in FIG. 45, liquid flows via the connection 128 and the inlet 130 into the connection 32 at the same time via the bridging opening 126. That is to say, water flows via the heat source 14 through the secondary heat exchanger 26 and the connection 128 the terminal 32. Since in this heating mode at the secondary heat exchanger 56 substantially no heat is removed, so the terminal 32 hot water in addition to the cold water, which flows from the pressure chamber 26 via the passage 122 to the terminal 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 switched off and the terminal 32 is exclusively in communication with the pressure chamber 26 directly. In this state, the water is conveyed in the floor circle 1 1 6 without heat in a circle. It can be seen that by changing the switching positions of the valve element 18i in this embodiment, both a switching between heating and hot water heating can be achieved, as well as the supply of two heating circuits with different temperatures, namely a first heating circuit 120 with the output temperature the heat source 1 14 and a Fußbodenheizkreises 1 16 with a reduced mixing function via a temperature. [64] It is to be understood that the various embodiments described above may be combined in various ways. Thus, the different types of drive described of the valve element with various geometric configurations of the valve element, as also described above, can be combined essentially as desired. the. Also, the various valve functions (for example, mixing and switching) can also be implemented and combined with different drive types. These various combination possibilities, which result from the preceding exemplary embodiments, are expressly covered by the invention.

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

LIST OF REFERENCE NUMBERS

1 centrifugal pump unit

2 motor housing

4 stator

6 rotor

8 rotor shaft

10 can

12 pump housing 14 impeller

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 entrances

32, 34 suction connections

36, 36 ', 36e suction opening

38 suction mouth

40 sealing surfaces

42 support elements

44 stop element 46 stops

48 spring

50 contact shoulder

52 heat source

54 heating circuit 56 secondary heat exchanger

58, 60 flow paths

 62 opening

 64 lead

 66 holes

 68 pen

 70 groove

 72 protrusions

 74 pegs

 76, 76b, 76dm 76h, 76i lower part

 78, 78d, 78h, 78i cover

 80 inlet opening

 82, 84 pods

 86 stator

 88 weight

 90 entrance opening

 92 sealing surfaces

 94 axis

 96 tongue

 98 pressure connection

 100 ring segment

 102 clamping ring

 104 advantage

 106 passage

 108 clutch

 1 10 counter coupling

 1 12 opening

 1 14 heat source

 1 16 floor heating circuit

1 18 Circulation pump unit

120 heating circuit

122 passageway 124 opening

 126 Bypass opening

128 connection

 130 entrance

X axis of rotation

 A, B Turning

Claims

claims Pump unit with an electric drive motor (4, 6), at least one of the drive motor (4, 6) driven impeller and at least one located in a flow path through the pump unit valve means (18) which is movable at least between a first and a second switching position characterized in that the valve device (18) is coupled to the drive motor via a first clutch in such a way that a movement of the drive motor (4, 6) is transmitted to the valve device (18) and the valve device is moved by a rotational movement of the drive motor (4, 6) from the first in the second switching position is movable, and that the first clutch can be released by increasing the rotational speed of the drive motor (4, 6) and / or increasing the pressure on the output side of the impeller and / or by slipping such that the coupling between drive motor (4, 6) and valve device (18) is reduced or eliminated becomes. Pump unit according to claim 1, characterized in that a second releasable coupling is provided between at least one movable part of the valve device (18) and a pump housing surrounding the impeller (14), which by the pressure on the output side of the impeller (14) from a dissolved first coupling position is movable in a holding second coupling position. Pump unit according to claim 2, characterized in that the first and the second clutch are formed such that the first clutch in its released position a smaller Holding force than the second clutch in its holding second coupling position and the first clutch in its coupled position has a greater holding force than the second clutch in its dissolved first coupling position. Pump unit according to one of the preceding claims, characterized in that the drive motor (4, 6) generates during operation of the pump unit, a torque which is greater than the holding force of the first clutch in its coupled position. Pump unit according to one of the preceding claims, characterized in that the valve device (18) is designed as a switching valve, which allows switching between two flow paths and / or a mixing device, in which fluid is mixed from two flow paths, wherein the mixing device is configured in that the mixing ratio is different in the two switching positions. Pump unit according to one of the preceding claims, characterized in that the valve device (18) has a valve function in a flow path on the suction side of the impeller (14) and / or in a flow path on the pressure side of the impeller (14). Pump unit according to one of the preceding claims, characterized in that the valve device has at least one movable valve element (18) and stop elements which define the first and the second switching position and of which preferably at least one is adjustable in its position. Pump unit according to one of the preceding claims, characterized in that the valve device (18) has at least one movable valve element (18) which cooperates with two valve openings such that a first valve opening (28) in the first switching position of the valve device of the valve element (18 ) is more covered than in the second switching position and a second valve opening (30) is more covered by the valve element in the second switching position than in the first switching position. Pump unit according to one of the preceding claims, characterized in that the valve device has a movable valve element (18) which has at least one sealing surface and a pressure surface, wherein the pressure surface with a surrounding the impeller (14) pressure chamber (26) in such a connection is that the valve element (18) by the on Pressure-acting surface pressure is pressed with the sealing surface against a contact surface, wherein the contact surface preferably forms a valve seat. Pump unit according to one of the preceding claims, characterized in that the valve device comprises a rotatable valve element (18) which is detachably coupled via the first coupling with a rotor (6) of the drive motor, wherein the axis of rotation (X) of the valve element preferably with the axis of rotation (X) of the drive motor is aligned. Pump unit according to one of the preceding claims, characterized in that the drive motor (4, 6) can be driven in two directions of rotation and the valve device (18) is designed such that its first switching position by driving the drive motor in a first direction of rotation (A) and its second Switching position is achieved by driving the drive motor in a second direction of rotation (B). 12. Pump unit according to one of the preceding claims, characterized in that the first and / or the second clutch is a friction clutch, a magnetic clutch and / or a hydraulic clutch, which preferably has a slip. 13. Pump unit according to one of the preceding claims, characterized in that the first clutch has at least one movable between a coupled and a disengaged position coupling element, wherein the direction of movement between the coupled and the disengaged position preferably transversely to a direction of force of the clutch on the Valve device extends to be transmitted force. 14. Pump unit according to claim 13, characterized in that a valve element of the valve device simultaneously forms the movable coupling element. 15. Pump unit according to claim 13 or 14, characterized in that the coupling element via a biasing member (48), is acted upon by a biasing force, which forces the coupling element in the coupled position. 16. Pump unit according to claim 15, characterized in that the coupling element has a pressure surface which communicates with a the impeller (14) surrounding the pressure chamber (26) in such a way and is arranged such that a on the Pressure acting surface generates a force which is opposite to the biasing force. 17. Pump unit according to one of claims 13 to 1 6, characterized in that the coupling element has a coupling surface (100), which in the coupled position with a Is in frictional contact, and that the coupling surface (100) and the counter-coupling surface (8) are formed and surrounded by a lubricant that between the coupling surface (100) and the counter-coupling surface (8 ) When the rotational speed of the drive motor is increased, a lubricating film which releases the frictional contact is formed.