Hydraulic valve device and centrifugal pump assembly comprising the same

Abstract

The present invention relates to a hydraulic valve device and a centrifugal pump device including the hydraulic valve device, the hydraulic valve device comprising a first inlet (20) and a second inlet (22) and a valve element (24) for selectively closing one of the first inlet (20) and the second inlet (22), wherein the valve element (24; 24') is rotatable between two valve positions such that the surface of the valve element moves in a direction parallel to the opening of the inlet (20, 22), wherein the valve element (24; 24') comprises two separate sealing portions (72, 74), namely a first sealing portion (72) for closing the first inlet (20) and a second sealing portion (74) for closing the second inlet (22), the two sealing portions (72, 74) being configured such that, in a first valve position, the first sealing portion (72) closes the first inlet (20), and in a second valve position, the second sealing portion (74) closes the second inlet (22).

Description

[0001] Especially in smaller buildings, compact heating systems are used to heat the building and provide domestic hot water. These systems typically include hydraulic valve units to switch the flow of the heating medium between the building's heating circuit and the heat exchanger used to heat domestic water.

[0002] EP 3 376 049 discloses integrating such a valve device into a heating pump device, such that the valve element of the valve device is transferred between two possible valve positions by utilizing the water flow generated by the pump.

[0003] Based on existing technology, the purpose of this invention is to further improve the hydraulic valve device so that further functions can be introduced into this integrated device to produce a more complex and compact heating device.

[0004] This objective is achieved by a hydraulic valve device having the features defined in claim 1 and a centrifugal pump assembly having the features defined in claim 14. Preferred embodiments are disclosed in the dependent claims, the following description, and the accompanying drawings.

[0005] For example, the hydraulic valve device according to the invention can be used in a heating system to switch the flow of a heating medium between at least one heating circuit within a building and a heat exchanger for heating domestic hot water. The hydraulic valve device includes a first inlet and a second inlet, and a valve element. The valve element is configured and provided for selectively closing one of the first and second inlets. Therefore, fluid flow can be switched between flowing through the first inlet and flowing through the second inlet. According to a first embodiment, one of the two inlets is always closed; that is, in a first valve position, the first inlet is closed, and in a second valve position, the second inlet is closed. However, in an alternative embodiment, a positionable valve element can be provided such that in one possible valve position, both inlets are open. By moving the valve element, the opening ratio between the two inlets can be changed to achieve a variable mixing ratio between the fluids flowing through the two inlets.

[0006] According to the invention, the valve element is a rotatable valve element, meaning that the valve element moves between at least two possible valve positions by rotation. Therefore, the valve element and the two inlets are configured such that the surface of the valve element moves in a direction parallel to the openings of the inlets. For example, the openings of the two inlets may extend in a plane extending transversely to (more preferably perpendicular to) the axis of rotation of the valve element. This valve element design is advantageous for use in hydraulic valve devices, in which the valve element is driven by a fluid flow generated by a pump, as described in more detail below. Therefore, according to the invention, the valve element does not move between the two possible valve positions in a direction perpendicular to the openings of the inlets, but rather moves parallel to the surface extending from the openings of the inlets.

[0007] According to the present invention, the valve element includes two separate sealing portions for closing two inlets: a first sealing portion for closing a first inlet and a second sealing portion for closing a second inlet. These two sealing portions are configured such that in a first possible valve position, the first sealing portion closes the first inlet, and the second sealing portion is located adjacent to the second inlet, thereby opening the second inlet. However, in a second possible valve position, the second sealing portion faces and closes the second inlet, while the first sealing portion is away from the first inlet, leaving the first inlet open. This means that, according to the present invention, the two inlets are not selectively closed by the same sealing portion, but rather by using two different sealing portions, each inlet having a separate sealing portion. This makes the design of the hydraulic valve device more flexible, as the two sealing portions and inlets can be designed differently according to further purposes or requirements. This allows for the introduction of more functionality into the valve device. For example, the two inlets and the two sealing portions can provide different cross-sections and hydraulic characteristics for the fluid flowing through the two inlets. This allows for optimization of the flow path for each fluid flow, i.e., flowing through the first and second inlets independently of each other.

[0008] According to a preferred embodiment of the invention, the first sealing portion is fully and permanently closed, and the second sealing portion includes a valve, particularly a bypass valve. The bypass valve can be designed to open the second inlet based on a pressure differential acting on the valve element when the second sealing portion closes the second inlet. This means that, preferably, the bypass valve opens if a predetermined pressure differential on the bypass valve (i.e., the pressure differential between the closed second inlet and the outlet side of the hydraulic valve) exceeds a predetermined threshold. For example, in the case of a closed heating circuit connected to the first inlet, such a bypass valve can be used in a heating system to open a flow path through a heat exchanger used for heating domestic water. The bypass valve then allows a certain flow rate to be maintained within the heating equipment to avoid, for example, overheating of a boiler. The integration of the bypass valve with the second sealing portion allows for a very compact and fully integrated hydraulic valve assembly, including complete valve functionality for changing the flow rate between the heating circuit and the heat exchanger in a heating system. For this design, it is important that there are two separate sealing portions because the first sealing portion can be designed independently of the bypass valve (i.e., without such a valve as a fully or permanently closed sealing portion). In this design, in the first valve position, when the first inlet is closed, the bypass valve does not function, making the closure of the first inlet independent of the pressure differential across the valve.

[0009] For example, a bypass valve can be a spring-loaded check valve. The spring limits the opening pressure. However, the opening differential pressure also depends on the size and design of the check valve's valve element. Alternatively, the bypass valve's valve element can be preloaded in different ways (e.g., by magnetic force).

[0010] According to another possible preferred embodiment, the openings for the first and second inlets of the valve element are disposed on a single surface (preferably a plane). Preferably, this surface extends perpendicular to the axis of rotation of the valve element. However, the surface where the openings for the first and second inlets are disposed may also be inclined toward the axis of rotation of the valve element. For example, this surface may be a truncated conical surface or a conical surface. However, according to a preferred solution, this surface does not extend parallel to the axis of rotation. This allows for better sealing by additionally moving the valve element in a direction parallel to the axis of rotation, as described below.

[0011] According to a preferred embodiment, the valve element can additionally move in the axial direction (preferably along the axis of rotation) to bring the sealing portion into sealing contact with the valve seat of the opposing inlet. The valve seat preferably surrounds the opening of the inlet such that the opening is closed by the sealing contact between the sealing portion and the opposing or facing valve seat. An advantage of this design is that the movement of the valve element between two possible valve positions can be independent of the actual sealing of each inlet. This means that, in order to change the valve position in the first step, the valve element moves axially to lift the sealing portion from the opposing valve seat. In the second step, the valve element can move to another valve position by rotation about the axis of rotation, and then in the third step, the valve element moves rearward in the axial direction to press an additional sealing portion against the respective opposing valve seat. Therefore, as the valve element moves between valve positions, the sealing portion and the valve seat disengage, thereby reducing friction. This is particularly advantageous if the valve element is moved by fluid flow and / or hydraulic pressure.

[0012] According to another possible embodiment, the valve element includes a support element, a cover element, and a movable bypass valve element disposed between the support element and the cover element. This allows the bypass valve to be easily integrated into the valve element. The valve element is assembled from two parts, namely the support element and the cover element. The bypass valve element can be easily integrated during valve element assembly. According to a preferred embodiment, the support element and the cover element are connected by a snap fit. This facilitates assembly, and furthermore, according to the snap fit design, the valve element can be disassembled, for example, to replace the bypass valve element. In addition to the bypass valve element, a spring for preloading the bypass valve element can also be integrated and secured between the support element and the cover element. Furthermore, the necessary guide element for guiding the bypass valve element can preferably be integrated into the support element and / or the cover element, particularly with at least one of these components. Preferably, the guide device is designed to guide the movable bypass valve element along a predetermined, preferably linear, path. According to another preferred embodiment, this linear path or axis extends parallel to the rotation axis of the valve element.

[0013] The first and second sealing portions are preferably disposed on the support element. The sealing portions may include elastic portions to improve sealing performance when in contact with the opposing valve seat. Preferably, the support element is rotatable on a fixed shaft or connected to a bearing element guided or supported on the fixed shaft.

[0014] The bypass valve element can be replaceable, for example, by opening the connection between the cover element and the support element as described above. According to a preferred embodiment, at least two replaceable bypass valve elements of different sizes are provided, wherein the size of the bypass valve element defines the opening pressure of the bypass valve. For example, the opening pressure can be defined by the surface area ratio of the two sides of the bypass valve elements facing away from each other. By replacing the bypass valve element, the opening pressure of the bypass valve can be changed. Preferably, the bypass valve elements of different sizes can be used with the same spring element, such that to define the opening pressure threshold, only the bypass valve element needs to be changed without changing the spring element preloaded by the bypass valve element.

[0015] According to another possible embodiment, the second sealing portion includes a sealing element configured to contact the valve seat of the second inlet and to make sealing contact with the bypass valve element of the bypass valve. For example, the sealing element is made of an elastic material. The sealing element can be formed as a separate component connected to the valve element, particularly the support element of the valve element. The sealing element, and preferably all other sealing elements, can also be connected to the valve element (particularly the support element of the valve element) via injection molding. If the sealing element is used to seal both the second inlet and the bypass valve, the number of necessary components can be reduced, and assembly can be simplified.

[0016] According to another possible embodiment of the invention, the valve element includes at least one inlet facing the first inlet in one possible valve position (e.g., a second valve position). In this valve position, a second sealing portion of the valve element is closing or sealing the second inlet. The inlet of the valve element forms a flow path through the valve element from the first inlet. In another possible valve position, such as the first valve position, the inlet faces the second inlet, thereby forming a flow path through the valve element from the second inlet. In this position, the first sealing portion closes the first inlet. According to a preferred embodiment, at least one inlet is fluidly connected to an outlet of the valve element. There may be a channel or free space inside the valve element connecting the inlet and outlet. Preferably, the inlet and outlet are open toward opposite surfaces of the valve element (i.e., in opposite directions, preferably in opposite directions parallel to the axis of rotation of the valve element). For example, the outlet may be open toward the front of the valve element, while the inlet is open toward the opposite back of the valve element.

[0017] If the valve element is used in conjunction with a pump as described in more detail below, the outlet of the valve element may open toward the inlet of the pump impeller.

[0018] According to another preferred embodiment, the valve element includes at least one mechanical end stop for defining at least one of two valve positions. More preferably, the valve element includes two opposing mechanical end stops defining two different valve positions. One or more end stops may be designed to face and abut against a stop element formed on the surrounding valve housing. Preferably, one or more end stops are radially disposed within the sealing portion, for example, in the central region of the valve element about its axis of rotation. Thus, the end stops, disposed in the central region of the rotating valve element, create a damping effect if the valve element reaches the end position defined by the end stops. The end stops contact opposing stop elements disposed in the valve housing. Impact on the end stops can be mitigated by at least a portion of the elasticity of the valve element.

[0019] Preferably, the valve element includes at least one mechanical end stop defining at least one of two valve positions. The end stop includes a stop element connected to the valve element via an elastic element and preferably via a spring. This spring can be a spring that actuates the valve element axially along the axis of rotation. Therefore, the spring can have a dual function: actuating the valve element into one of two possible positions along the axis of rotation and ensuring damping if the valve element engages with the end stop defining one of the valve positions in the direction of rotation. The spring can be a helical spring, generating axial force through compression and damping effect through torsion. According to another possible embodiment, the spring is located between the aforementioned valve element or its support element and a bearing element supported on a fixed shaft or a pivot for rotation of the valve element about the fixed shaft. By compressing the spring disposed between the bearing element and the valve element or support element, the bearing element can move longitudinally relative to the support element. The bearing element can be guided longitudinally on the support element, wherein the guidance has a certain clearance, allowing limited movement in the direction of rotation under the torsion of the spring disposed between the support element and the bearing element.

[0020] Besides the aforementioned hydraulic valve device, the subject of this invention is also a centrifugal pump assembly. The centrifugal pump assembly according to the invention includes an electric drive motor and at least one impeller driven by the drive motor. The centrifugal pump assembly is preferably a circulating pump used in heating systems. The electric drive motor can be, in particular, a wet-operated motor with a rotor shield between a dry stator region and a rotor space containing the rotor, the rotor space being filled with the liquid to be pumped. The rotor can be connected to the impeller via a rotor shaft. Furthermore, the centrifugal pump assembly according to the invention includes the hydraulic valve device as described above. This hydraulic valve device serves as a valve for switching the flow path between two suction ports of the pump assembly, thereby allowing the impeller to draw fluid from either a first suction port or a second suction port depending on the valve position of the hydraulic valve device. Thus, a first inlet of the hydraulic valve device forms a first suction port, and a second inlet of the hydraulic valve device forms a second suction port. Therefore, the flow path can be switched between the two suction ports by rotating the valve element. Such a centrifugal pump assembly can be used, for example, in compact heating systems for circulating heating fluid. The hydraulic valve can be used to switch fluid flow between a heating circuit within a building and a heat exchanger for heating domestic hot water. Therefore, the valve element is preferably located on the suction side of the impeller, so that the outlet of the valve element is fluidly connected to the inlet or nozzle of the impeller.

[0021] According to a preferred embodiment, depending on the switching of the valve element or the valve position, a first suction port or a second suction port is selectively fluid-conductingly connected to the nozzle of at least one impeller. In the first valve position, the second suction port is preferably fluidly connected to the impeller; in the second valve position, the first suction port is fluidly connected to the impeller. The other suction ports are respectively closed by corresponding sealing portions of the valve element.

[0022] According to another preferred embodiment, the cover element of the valve element (particularly the cover element as described above) includes an outlet that engages with the impeller's inlet. The outlet of the valve element is preferably located at the center of the valve element, concentric with the rotation axis of the valve element and the rotation axis of the impeller. Furthermore, the outlet preferably has a circular shape that engages with the impeller's inlet. The impeller's inlet can be rotatably engaged with the outlet of the cover element. Thus, during impeller rotation, fluid can flow through the valve element, exit from the outlet, and directly flow into the impeller's inlet.

[0023] According to another possible embodiment, the centrifugal pump assembly including the hydraulic valve device is designed such that, when moving between a first valve position and a second valve position, the valve element is driven by a fluid flow generated by an impeller. For this purpose, the valve element can be arranged concentrically with the impeller such that the cover plate of the valve element is substantially parallel to the impeller surface. Such a valve element can be driven by a rotating fluid flow generated by the impeller, as described, for example, in EP 3 376 049 A1.

[0024] Furthermore, preferably, the valve element is positioned between the suction and pressure sides of the pump assembly, so that the pressure generated by the impeller acts on one side of the valve element, and depending on the valve position, the first sealing portion of the valve element is pushed against the valve seat of the first inlet, or the second sealing portion is pushed against the valve seat of the second inlet. In this arrangement, preferably the impeller cover plate faces the impeller, and the sealing portion is located on the opposite side away from the impeller. Due to the axial mobility of the valve element, the valve element may be shifted by the pressure generated by the impeller, causing it to be pushed against the valve seat to ensure a safe seal. If the impeller speed decreases or the pump is shut down, the impeller outlet pressure decreases, and the valve element can move backward in the axial direction, for example by a spring element, causing the sealing portion to lift off the valve seat, and the valve element can be easily rotated to different valve positions. Attached Figure Description

[0025] The invention will be described below by way of example with reference to the accompanying drawings. Herein:

[0026] Figure 1 This is an exploded view of the centrifugal pump assembly according to the present invention.

[0027] Figure 2 It is based on the axial end side of the electronic device housing. Figure 1 A top view of a centrifugal pump unit.

[0028] Figure 3 It is based on Figure 1 and Figure 2 centrifugal pump unit along Figure 2 A cross-sectional view along line III-III, showing the valve assembly in its sealed position.

[0029] Figure 4 It is similar to Figure 3 A cross-sectional view showing the valve assembly in its released and rotatable position.

[0030] Figure 5 It is based on Figures 1 to 4 A top view of the centrifugal pump unit with the pump casing open.

[0031] Figure 6 It is based on Figures 1 to 5 A cross-sectional view of the valve assembly in a centrifugal pump unit, with the valve element in the first valve position.

[0032] Figure 7 It is based on Figure 6 A cross-sectional view of the valve assembly, with the valve element in the second valve position.

[0033] Figure 8 It is a centrifugal pump device along Figure 2 A cross-sectional view along line VIII-VIII, showing the valve element in the second valve position.

[0034] Figure 9 It is based on Figures 1 to 8 A three-dimensional view of the valve components in a centrifugal pump unit.

[0035] Figure 10 This is a plan view of the bottom side of the valve element, including the sealing portion.

[0036] Figure 11 This is a cross-sectional view of a valve element; the bypass valve is in the closed position.

[0037] Figure 12 It is based on Figure 11 The cross-sectional view shows the bypass valve in the open position.

[0038] Figure 13 yes Figure 12 The enlarged cross-sectional view of the bypass valve 86 shown is shown.

[0039] Figure 14 It is based on Figure 9 Exploded view of the valve components.

[0040] Figure 15 According to the views from different directions Figure 9 Exploded view of the valve components.

[0041] Figure 16 It is the pump casing along Figure 3 A cross-sectional view along line XIII-XIII, showing the valve element in the second valve position, and...

[0042] Figure 17 It is based on Figure 18 The cross-sectional view shows the valve element in the first valve position.

[0043] Figure 18 It is a schematic diagram of the hydraulic circuit of a heating system including the centrifugal pump according to the present invention, and

[0044] Figure 19 This is an exploded view of the valve element according to the second embodiment, and

[0045] Figure 20 It includes Figure 19 A perspective view of the open pump casing of the valve element shown. Detailed Implementation

[0046] The centrifugal pump described as an example is a centrifugal pump provided for a heating system. This centrifugal pump assembly includes a hydraulic valve assembly that can be used in the heating system to alter the fluid flow between the heating circuit through the building and the heat exchanger used to heat domestic water.

[0047] The centrifugal pump unit has an electric drive motor 2, including a motor housing 4, within which a stator and rotor are disposed. At one axial end of the motor housing, in the direction of the longitudinal axis X, is an electronics housing 6, which includes control electronics 7 for the electric drive motor. At the opposite axial end of the motor housing 4 is a pump housing 8, which includes an outlet connector 10 connected to an outlet 12 located inside the pump housing 8. The outlet 12 is located on the outer periphery of a pump space in which an impeller 14 is disposed. Furthermore, the pump housing 8 includes two inlet connectors 16 and 18. The first inlet connector is for connection to a heating circuit within the building, and the second inlet connector 18 is for connection to a heat exchanger for heating domestic hot water. The first inlet connector 16 is in fluid connection to a first inlet 20 within the pump housing 8. The second inlet connector 16 is connected to a second inlet 22 within the pump housing 8. Inlets 20 and 22 are disposed in a plane perpendicular to the longitudinal axis or the axis of rotation X. The axis of rotation X is the axis of rotation of the impeller 14 and valve element 24, which will be described in more detail later. Viewed along the longitudinal direction X, the first inlet and the second inlet are located at the bottom of the pump casing 8.

[0048] Valve element 24 is configured to switch the flow path toward impeller 14 between two inlet fittings 16 and 18. Essentially, the function of this hydraulic valve assembly is similar to that disclosed in EP 3 376 049. Valve element 24 has a central outlet 26 that faces or engages with the suction nozzle 28 of impeller 14, allowing fluid to flow from the outlet 26 into the suction nozzle 28.

[0049] Valve element 24 is rotatable about a rotation axis X, which corresponds to the rotation axis X of impeller 14. Valve element 24 is mounted on a pivot or bearing post 30 fixed to the bottom of pump housing 8. In this embodiment, the pivot is molded into the material of pump housing 8, for example, during injection molding. However, the bearing post can be fixed to the bottom of pump housing 8 in different ways, such as screwed into a threaded hole or integrally formed with pump housing 8. Bearing post 30 extends from the bottom of pump housing 8 along the longitudinal direction X into the interior of pump housing 8. Valve element 24 is rotatable about the longitudinal axis X and can move a certain distance along the longitudinal axis X in a straight line on bearing post 30. This certain distance is limited by an O-ring 32 forming an axial stop or support for valve element 24. O-ring 32 engages with a circumferential groove or notch 34 located near the free distal end of bearing post 30. O-ring 32 forms a resilient axial stop and allows for easy assembly without special tools.

[0050] In this embodiment, the valve element 24 consists of two parts: a support element 36 and a cover element 38, which are connected by a snap-fit ​​mechanism. A hook 40 is provided on the inner surface of the cover element 38, which surrounds or engages a shoulder or protrusion 42 inside the support element 36. The cover element 38 has a cover plate 104, i.e., a plate-shaped cover, which is completely closed except for the central outlet 36. When disposed within the pump housing 8, the cover plate 104 of the cover element 38 forms an axial wall of the pump space 44 in which the impeller 14 rotates. The opposite axial wall of the pump space 44 is formed by a support plate 46, which has a bearing for the rotor shaft 50. On the opposite side of the cover element 38, a spring support member 52 connected to the support element 36 is provided. A helical compression spring 54 is provided between the spring support member 52 and the support element 36. One axial end of the spring 54 abuts against the inner bottom surface of the spring support member 52, and the opposite axial end abuts against a portion of the support element 36. The spring support 52 overlaps with the elastic engaging hook 56, such that the engaging hook 56 engages from the interior of the spring support 2 with an opening or cutout 58 on the outer periphery of the spring support 52. Therefore, the spring support 52 is guided axially in the X direction outside the leg of the engaging hook 56, allowing the spring support 52 to move axially in this direction outside the leg of the engaging hook 56. Furthermore, a rib 60 is provided in the spring support 52 on the support element 38. The rib 60 and the slot 62 allow relative movement in the axial direction but ensure torque transmission; therefore, except for a limited clearance in the circumferential direction between the rib 60 and the slot 62, the spring support 52 connected to the support element 36 is essentially torsion-proof. This clearance ensures the damping effect provided by the torsion of the compression spring 54, as the spring 54 is in flux in the rotational direction until the rib 60 abuts against one edge of the slot 62.

[0051] At the axial end opposite to the support element 36, the spring support 52 includes a support portion 64 movably supported on the bearing post 30, i.e., sliding on the outer periphery of the bearing post 30. Another support portion 66, in contact with the bearing post 30, is formed in the support element 36. The support portion 66 includes a shoulder projecting in the radial direction. The axial end of the compression spring 54 abuts against this shoulder.

[0052] The compression spring 54 pushes the support portions 64 and 66 away from each other and pushes the valve element 24 axially toward the motor housing 4. Under the compression of the spring 54, the valve element 24 can move toward the bottom side of the pump housing 8, that is, away from the impeller 14 and the motor housing 4. Figure 3 and Figure 4 These two possible axial positions of valve element 24 are shown. Figure 4In the first axial position, valve element 24 abuts against a circular shoulder 68 inside the pump housing 8. The shoulder 68 extends radially from the inner circumference of the pump housing 8, providing a circular sealing surface substantially perpendicular to the longitudinal axis X. Valve element 24 makes sealing contact with the shoulder 68 via a resilient seal 70 on the outer periphery of the support element 36. This seal 70 ensures a seal of the pump space 44 to the suction side of the pump assembly. Figure 4 The second axial position of valve element 24 is shown, in which valve element 24 moves toward impeller 14 so that seal 70 is no longer in contact with shoulder 68, but is instead away from shoulder 68. In this position, valve element 24 can rotate freely about longitudinal axis X. However, if seal 70 is in contact with shoulder 68, rotation of valve element 24 is prohibited due to friction between seal 70 and shoulder 68. Therefore, shoulder 68 and seal 70 act as a detachable coupling or clutch. Under the spring force of compression spring 54, valve element 24 is moved to... Figure 4 The release position is shown. Valve element 24 is moved into position by the pressure generated by impeller 14. Figure 3 In the fixed position shown, the seal 70 contacts the shoulder 68, and pressure is applied to the cover element 38 surrounding the outlet 26. Therefore, based on the pressure generated by the pump at the outlet side of the impeller 14, the valve element 24 can be selectively moved in the axial direction. This can be controlled by speed control and regulation performed by the control electronics 7 disposed in the electronics housing 6.

[0053] Valve element 24 includes two sealing portions 72 and 74, namely a first sealing portion 72 and a second sealing portion 74. The two sealing portions 72 and 74 are disposed on the outer axial surface of support element 36, specifically on the axial face of valve element 24 opposite to the impeller and opposite to the first inlet 20 and the second inlet 22. The two sealing portions 72 and 74 are disposed in a common plane extending perpendicular to the rotation axis X. The two sealing portions 72 and 74 are radially positioned relative to the axis X, specifically offset by 180° around the rotation axis X. Each of the two sealing portions 72 and 74 includes resilient sealing elements 76 and 78, which, in this embodiment, are integrally formed with a seal 70 on the outer periphery of the support element. The seal 70 and sealing elements 76 and 78 can be formed as separate components or sealing arrangements connected to the support element 36, or connected to the support element 36 via an injection molding process.

[0054] The first sealing portion 72 is configured to selectively close the first inlet 20, and the second sealing portion 24 is configured to selectively close the second inlet 22. Between the two sealing portions 72 and 74, an opening 80 is provided in the support element 36, which is in fluid connection with the outlet 26 and forms the inlet of the valve element 24.

[0055] Valve element 24 can have two different valve positions in the direction of rotation about the longitudinal axis X. Figure 6 The diagram shows the first valve position, in which the first sealing portion 72 closes the first inlet 20. In this first valve position, the second inlet 22 opens to the opening 80 in the valve element 24, allowing fluid to flow from the inlet 22 to the outlet 26 and into the suction nozzle 28 of the impeller 24. Therefore, in this first valve position, the impeller 14, and thus the entire pump, draws fluid through the first inlet connector 60 connected to the first inlet 20. In this first valve position, when the valve element 24 is in... Figure 3 When in the engaged or sealed position as shown, the first sealing portion 72 and its sealing element 76 are pressed against the valve seat 82 formed around or at the edge of the inlet 20. Thus, the first inlet 20 is completely closed.

[0056] exist Figure 7 In the second valve position shown, the first sealing portion 72 rotates away from the first inlet 20, opening the first inlet 20 toward the opening 80, providing a flow path from the first inlet 20 toward the outlet 26 and the suction nozzle 28 of the impeller 14. In this second valve position, the second sealing portion 24 is moved to a position where it covers the second inlet 22, thereby closing the second inlet 22. In the engaged or sealed position of the valve element 24, the sealing element 78 of the second sealing portion 24 is pressed against the valve seat 84 formed on the outer periphery or edge of the second inlet 22.

[0057] Unlike the first sealing portion 76, the second sealing portion 78 is not completely closed, but instead includes an additional valve in the form of a check valve, forming a... Figures 10-13 The bypass valve 86 is best shown in the diagram. The bypass valve 86 has an opening 92 on the second sealing portion 74, such as... Figure 7As shown, the opening 92 faces the second inlet 22 in the second valve position. The bypass valve 86 includes a bypass valve element 88 disposed between the support element 36 and the cover element 38 of the valve element 24. The bypass valve element 88 is guided in a linear direction parallel to the rotation axis X on a guide element 90 that engages with the bypass valve element 88. In its closed position, the bypass valve element 88 abuts against a valve seat formed by a sealing element 78, which defines the opening 92 around or within a second sealing portion 74. The bypass valve element 88 is held in the closed or sealed position by being pushed into the shown sealed or sealed position by a compression spring 94. By pressure acting on the bypass valve element 88, the bypass valve element 88 can move along the guide element 90 against the force provided by the compression spring 94 to open the opening 92. The back of the bypass valve element 88, away from the orifice 92, contacts the opening 80 and the outlet 26, i.e., the flow path of the pump's suction side and the suction nozzle 28 facing the impeller 14. Therefore, the pressure on the pump's suction side acts on the back of the bypass valve element 88. If the pressure difference across the bypass valve 86 or the bypass valve element 88 exceeds a predetermined threshold, defined by the dimensions of the bypass valve element 88 and the spring 94, the bypass valve 86 opens to allow fluid to flow from the second inlet 22 to the impeller 14 even though the second inlet 22 is closed by the second sealing portion 74. This function is available for heating systems when a heating circuit in the building is connected to the first inlet connector 16. If all radiators in the heating circuit are closed, no fluid flows through the first inlet connector 16. In this situation, the pressure on the suction side of impeller 14, and thus the pressure on the back of bypass valve element 88, will decrease to such a degree that the pressure difference across bypass valve 86 exceeds a predetermined threshold, and bypass valve 86 opens to ensure fluid flows through the second inlet 22, to which a heat exchanger for heating domestic water can be connected. Therefore, in a heating system, fluid flow through the boiler can be ensured, preventing boiler overheating.

[0058] The threshold for opening the bypass via the bypass valve 86 is preferably adjusted by replacing the bypass valve element 88. Replaceable bypass valve elements 88 of different sizes can be provided, particularly those with different back faces to which the pump's suction side pressure acts. Since the opposing surfaces are always defined by the cross-section of the opening 92, the forces acting on the bypass valve element 88 in both directions can be adjusted by changing the dimensions of the back face. Alternatively or additionally, the dimensions of the surface closing the opening 92 can also be adjusted by changing the diameter of the circular protrusion 93 on the bypass valve element 88 that contacts the valve seat in the sealing element 78.

[0059] Similar to that known in EP 3 376 049, valve element 24 moves between two valve positions via a circulating flow generated by impeller 14. If the speed of the electric drive motor decreases or the motor is shut off by control electronics 7, the pressure in pump space 44 decreases, causing compression spring 44 to move valve element 24 to its release position, as... Figure 4 As shown. In this position, valve element 24 can be rotated about the rotation axis X by the circulating fluid flow within pump space 44. The direction of the fluid flow depends on the rotation direction of impeller 14. Two valve positions are defined by end stops. For this purpose, a circular groove 96 is provided on the bottom wall of pump housing 8. This circular groove 96 does not define the entire circle, but has an interruption in the form of a web 98. Opposite surfaces of the web 98 define two end stops for the rotational movement of valve element 24, i.e., end stops defining two possible valve positions. The spring support 52 of valve element 24 has an axial extension forming a stop element 100. The stop element 100 has a finger-like form that is offset from the rotation axis X and engages in the groove 96. The stop element 100 can abut against two opposite surfaces of the web 98 to define two rotational positions corresponding to the possible valve positions described above. In this case, it is advantageous that the stop is located in the center, allowing a damping effect due to the elasticity of the components, especially by the torsion of the aforementioned compression spring 54. Figure 13 The stop element 100 is shown to be in contact with... Figure 7 The second valve position corresponding to the position shown. Figure 14 The stop element 100 is shown to be in contact with... Figure 6 The first valve position shown corresponds to the valve position indicated. It can be seen that valve element 24 rotates 270° to change the valve position.

[0060] To enhance the rotation of valve element 24 without increasing flow resistance during normal pump operation, radial protrusions 102 are provided distributed across the entire outer periphery of valve element 24. These protrusions 102 are positioned on the back side of cover plate 104 on cover element 38, such that cover element 38 has a cover plate 104 facing impeller 14, which extends radially beyond these protrusions 102, so that the protrusions 102 are completely covered by the cover plate 104 on the side facing impeller 14. Therefore, the protrusions 102 are positioned on the back side of cover plate 104. The diameter of cover plate 104 is smaller than the inner diameter of pump casing 8, thus providing a circular gap 106 on the outer periphery of cover plate 104. This gap 106 provides a flow connection between pump space 44 and the area where the protrusions 102 are located. If valve element 24 is in… Figure 3 In the sealed or engaged position shown, virtually no fluid flows through gap 106 because the flow path through gap 106 is closed by seals 70 at the opposite ends. However, if valve element 24 is in... Figure 4In the release position shown, a gap exists between the seal 70 and the shoulder 68, opening the flow path through the gap 106 to the opening 80 of the valve element 24 (i.e., on the suction side of the valve element 24). Therefore, if the impeller 14 rotates, a portion of the fluid flow leaving the impeller 14 will enter the gap 106 and flow towards the opening 80 around the valve element 24 toward the outlet 26. Due to the rotation of the impeller 14, this lateral flow through the gap 106 has rotation in the direction of impeller rotation, acting on the ribbed or toothed protrusions 102, generating torque on the valve element 24, causing it to rotate until the stop element 100 abuts against the end stop provided by the web 98. If the impeller speed is increased at this time by the control electronics 7, the external pressure of the impeller 14 increases, causing the valve element 24 to enter the sealing position, where the seal 70 contacts the shoulder 68 and one of the sealing portions 72, 74 contacts the opposing valve seats 82, 84. In this operating state, the valve reaches a sealed position. Thereafter, the impeller's rotation direction can be quickly changed without moving valve element 24 out of its current position. To achieve this, the electric drive motor rapidly accelerates due to the control of the various controls of the control electronics 7, causing the external pressure on impeller 24 to generate an axial force that overcomes the spring force of compression spring 54 before establishing a circulating flow to rotate valve element 24 to another position. This allows the valve element 24 to be selectively moved to the desired position, after which the impeller 14's rotation direction can be changed again, ensuring that the impeller 14 always rotates in the desired optimized rotation direction during operation of the centrifugal pump unit. The protrusions 102 located on the back of cover plate 104 have the advantage that they only function when valve element 24 is in the released position. During normal operation with the valve element in the sealed position, the protrusions 102 have little effect, and in particular, they do not increase the hydraulic resistance of the pump space 44.

[0061] The motor within the motor housing 4 is a wet-running motor, having a rotor shield 108 forming a rotor space, in which a rotor shaft 50 with a rotor 110 rotates. This rotor space is filled with the liquid to be pumped (i.e., preferably water). In a dry stator space within the motor housing 4, the stator 112 is disposed outside the rotor shield 108.

[0062] Figure 18 An example of the use of the aforementioned centrifugal pump assembly 114 is shown. The centrifugal pump assembly including the aforementioned features, namely valve element 24 and bypass valve 86, is... Figure 18The components enclosed by the dashed line. The centrifugal pump assembly 114 includes a centrifugal pump 116 with an electrically driven motor 2 and an impeller 14. A valve element 24 constituting a switching valve is disposed on the suction side of the centrifugal pump 116, allowing switching of the flow path between two possible inlet connections, namely a first inlet connection 16 and a second inlet connection 18. On the pressure side, the centrifugal pump 116 is connected to an outlet connection 10. In this example, the outlet connection 10 is connected to a boiler 118 that heats the liquid (particularly water) in the heating circuit. On the outlet side of the boiler 118, the heating circuit branches into a first branch and a second branch. The first branch forms a central heating circuit CH, which may, for example, include several radiators 120 or one or more floor heating circuits. The second branch is used to heat domestic hot water (DHW). The second branch includes a heat exchanger 122 for heating domestic hot water (DHW). It can be seen that a bypass valve is connected to the second branch, i.e., the branch containing the heat exchanger 122. If valve element 24 is in the open position, where the flow path through the central heating circuit CH is open, then bypass valve 86 can prevent boiler 118 from overheating. In this position, if radiator 120 is closed, the flow of liquid through central heating circuit CH is interrupted. In this case, bypass valve 86 can open due to the pressure difference overcoming the bias force of compression spring 94, thereby opening the flow path through heat exchanger 122. Water circulates through the second branch of the heating system via centrifugal pump 116, i.e., through heat exchanger 122, thereby distributing the heat generated by boiler 180 into the system to prevent boiler 118 from overheating.

[0063] Figure 19 A second embodiment of valve element 24' is shown. In this embodiment, the support element 36, including the bypass valve 86, is substantially the same as described above. In this second embodiment, the cover element 38' of valve element 24' has a different design. In this embodiment, the protrusion 102' extends radially from the outer peripheral surface 124. Furthermore, the protrusion 102' is inclined in the circumferential direction, such that the protrusion 102' forms inclined blades on the outer peripheral surface 124 of the valve element. In this embodiment, the cover plate 104' does not extend beyond the outer periphery of the peripheral wall 124, i.e., it does not cover the axial end side of the protrusion 102'. Therefore, by using this valve element 24', the gap 106' or annular space between the outer peripheral wall 124 of the valve element and the inner peripheral wall 126 of the pump housing 8' is open toward the space including the impeller 14, as... Figure 20 As can be seen, the fluid flow generated by the impeller 14 can directly impact the protrusion 102'. Due to its inclination, the protrusion 102' generates a greater torque, acting on the valve element 24' around the axis of rotation X. Figure 20 The pump housing 8' shown with valve element 24' can be connected to, for example... Figure 1 The electric drive motor 2 shown above is the same as the one described above. Furthermore, the impeller 14 can be the same as that shown in the first embodiment.

[0064] List of reference numerals

[0065] 2: Electric drive motor

[0066] 4: Motor housing

[0067] 6: Electronic component housing

[0068] 7: Control electronic devices

[0069] 8, 8': Pump casing

[0070] 10: Outlet connector

[0071] 12: Exports

[0072] 14: Impeller

[0073] 16, 16': First inlet connector

[0074] 18, 18': Second inlet connector

[0075] 20: First Import

[0076] 22: Second Import

[0077] 24, 24': Valve element

[0078] 26: Exit Hole

[0079] 28: Suction nozzle

[0080] 30: Pivot, bearing column

[0081] 32: O-ring

[0082] 34: Notch

[0083] 36: Supporting element

[0084] 38, 38': Cover element

[0085] 40: Connecting hook

[0086] 42: Joint shoulder

[0087] 44: Pump Space

[0088] 46: Support plate

[0089] 48: Bearing

[0090] 50: Rotor shaft

[0091] 52, 52': Spring support

[0092] 54: Compression spring

[0093] 56: Connecting hook

[0094] 58: Incision

[0095] 60: Ribs

[0096] 62: Slot

[0097] 64: Support section

[0098] 66: Supporting part

[0099] 68: Shoulders

[0100] 70: Seals

[0101] 72: First sealing part

[0102] 74: Second sealing section

[0103] 76, 78: Sealing elements

[0104] 80: Opening

[0105] 82, 84: Valve seat

[0106] 86: Bypass valve

[0107] 88: Bypass valve element

[0108] 90: Guiding element

[0109] 92: Opening

[0110] 93: Protrusion

[0111] 94: Compression Spring

[0112] 96: slot

[0113] 98: Web

[0114] 100: Stopping element

[0115] 102, 102': protrusion

[0116] 104, 104': Cover plate

[0117] 106, 106': Gap

[0118] 108: Rotor shielding sleeve

[0119] 110: Rotor

[0120] 112: Stator

[0121] 114: Centrifugal pump unit

[0122] 116: Centrifugal pump

[0123] 118: Boiler

[0124] 120: Radiator

[0125] 122: Heat exchanger

[0126] 124: Peripheral wall

[0127] 126: Inner peripheral wall

[0128] CH: Central Heating

[0129] DHW: Domestic Hot Water

[0130] X: Axis of rotation

Claims

1. Hydraulic valve arrangement comprising a first inlet (20) and a second inlet (22) and a valve element (24; 24') for selectively closing one of the first inlet (20) and the second inlet (22), wherein the valve element (24; 24') is rotatable between two valve positions such that a surface of the valve element moves in a direction parallel to the openings of the inlets (20, 22), characterized in that the valve element (24; 24') comprises two separate sealing portions (72, 74), a first sealing portion (72) for closing the first inlet (20) and a second sealing portion (74) for closing the second inlet (22), the two sealing portions (72, 74) are arranged such that, in a first valve position, the first sealing portion (72) closes the first inlet (20) and, in a second valve position, the second sealing portion (74) closes the second inlet (22), the first sealing portion (72) is completely closed and the second sealing portion (74) comprises a bypass valve (86) designed to open the second inlet (22) depending on a pressure difference acting on the valve element (24; 24') when the second sealing portion (74) closes the second inlet (22).

2. The hydraulic valve device according to claim 1, characterized by the bypass valve (86) is a spring-loaded check valve.

3. Hydraulic valve arrangement according to claim 1 or 2, characterized in that the openings of the first inlet (20) and the second inlet (22) facing the valve element (24; 24') are arranged on one face.

4. The hydraulic valve device according to claim 1 or 2, characterized by the valve element (24; 24') is additionally movable in axial direction along the axis of rotation (X) to bring the sealing portions (72, 74) into sealing contact with valve seats (82, 84) of the opposite inlets (20, 22).

5. The hydraulic valve device according to claim 1 or 2, characterized by the valve element (24; 24') comprises a support element (36), a cover element (38) and a movable bypass valve element (88) arranged between the support element (36) and the cover element (38; 38').

6. The hydraulic valve device of claim 5, wherein the support element (36) and the cover element (38; 38') are connected by snap fit.

7. The hydraulic valve device of claim 5, wherein the first sealing portion (72) and the second sealing portion (74) are arranged on the support element (36).

8. The hydraulic valve device of claim 5, wherein the support element (36) and / or the cover element (38; 38') comprise guiding means (90) guiding the movable bypass valve element (88) along a predetermined movement path.

9. The hydraulic valve device of claim 8, wherein the guiding means (90) guide the movable bypass valve element (88) along a linear movement path.

10. The hydraulic valve device of claim 5, wherein at least two exchangeable bypass valve elements (88) differ in size, wherein the size of the bypass valve element (88) defines the opening pressure of the bypass valve (86).

11. The hydraulic valve device of claim 1, wherein the second sealing portion (74) comprises a sealing element (78) arranged to contact a valve seat (84) of the second inlet (22) and to contact the bypass valve element (88) of the bypass valve (86).

12. The hydraulic valve device according to claim 1 or 2, characterized by The valve element (24; 24') comprises at least one inlet opening (80) facing the first inlet (20) in one valve position and facing the second inlet (22) in the second valve position.

13. The hydraulic valve device of claim 12, wherein The at least one inlet opening (80) is in fluid connection with an outlet opening (26) of the valve element (24; 24').

14. The hydraulic valve device according to claim 1 or 2, characterized by The valve element (24; 24') comprises at least one mechanical end stop (98, 100) defining at least one of the two valve positions, the end stop (98, 100) being radially arranged within the sealing portion (72, 74).

15. The hydraulic valve device according to claim 1 or 2, characterized by The valve element (24; 24') comprises at least one mechanical end stop (98, 100) defining at least one of the two valve positions, the end stop comprising a stop element (100) connected to the valve element (24; 24') via a spring (54).

16. The hydraulic valve device of claim 15, wherein The stop element (100) is connected to the valve element (24; 24') via a spring (54) pushing the valve element (24; 24') in axial direction along the rotation axis (X).

17. A centrifugal pump assembly comprising an electric drive motor (2), at least one impeller (14) driven by the drive motor and two suction inlets (20, 22), characterized in that The hydraulic valve arrangement according to one of the preceding claims, wherein the first inlet (20) of the hydraulic valve arrangement forms a first suction inlet and the second inlet (22) of the hydraulic valve arrangement forms a second suction inlet.

18. The centrifugal pump assembly of claim 17, wherein, The first suction inlet (20) and the second suction inlet (22) are in fluid conductive connection with a suction nozzle (28) of the at least one impeller (14).

19. The centrifugal pump assembly of claim 18, wherein, The valve element (24; 24') comprises an outlet opening (26) engaging the suction nozzle (28) of the impeller.

20. The centrifugal pump assembly of claim 19, wherein, The cover element (38) of the valve element comprises an outlet opening (26) engaging the suction nozzle (28) of the impeller.

21. The centrifugal pump assembly of any one of claims 17-20, wherein, The valve (24; 24') is driven by the fluid flow generated by the impeller (14) to move between the first valve position and the second valve position.

22. The centrifugal pump assembly of any one of claims 17-20, wherein, The valve element (24; 24') is arranged between a suction side and a pressure side of the pump assembly such that a pressure generated by the impeller (14) acts on one side of the valve element (24; 24') and depending on the respective valve position either the first sealing portion (72) of the valve element (24; 24') is urged against a valve seat of the first inlet (20) or the second sealing portion (74) is urged against a valve seat of the second inlet (22).

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