阅读说明：本技术 用于流体的流量控制的多路阀组 (Manifold block for flow control of fluids ) 是由 D·伯克哈尔特 C·波尔特拉 O·施密德 于 2018-09-20 设计创作，主要内容包括：本发明的第一方面涉及一种用于流体的流量控制的多路阀组(M)。阀组件具有至少第一阀门和第二阀门(12a-12h)和用于致动阀门(12a-12h)的致动机构(70)。阀门被布置成使得能与致动机构(70)的位置有关地选择和致动至少一个预定的阀门(12a)。致动机构(70)布置成可平移地移位。在致动机构(70)的第一平移位置,可以致动第一阀门(12a),并且在不同于第一平移位置的第二平移位置,可以致动第二阀门(12b)。(A first aspect of the invention relates to a multiple valve group (M) for flow control of a fluid. The valve assembly has at least first and second valves (12a-12h) and an actuating mechanism (70) for actuating the valves (12a-12 h). The valves are arranged such that at least one predetermined valve (12a) can be selected and actuated in relation to the position of the actuating mechanism (70). The actuation mechanism (70) is arranged to be translatably displaceable. In a first translational position of the actuation mechanism (70), the first valve (12a) may be actuated, and in a second translational position different from the first translational position, the second valve (12b) may be actuated.)

1. A multiple valve group (M) for fluid flow control having at least a first and a second valve (12a-12h) and an actuating mechanism (70) for the actuating valves (12a-12h), wherein the valves (12a-12h) are arranged such that at least one predetermined valve can be selected and actuated in relation to the position of the actuating mechanism (70), wherein the actuating mechanism is arranged to be translationally displaceable,

characterized in that, in a first translational position of the actuating mechanism (70), said first valve (12a) can be actuated and in a second translational position, different from said first translational position, said second valve (12b) can be actuated.

2. Valve group (M) for flow control according to claim 1, wherein the actuation mechanism (4) comprises a shaft (76) and wherein the shaft (76) is arranged axially displaceable along its axis so that in a first axial position of the shaft the first valve (12a) is actuatable and in a second axial position different from the first axial position the second valve (12b) is actuatable.

3. The multiple valve group (M) for flow control according to claim 1 or 2, wherein the pressure balancing means (4), in particular the member (80), is actuatable in the third axial position.

4. Valve group (M) for flow control according to any of the claims from 1 to 3, wherein the valve group has a third valve (12c), wherein in a first translational position of the actuation mechanism the first valve (12a) and the third valve (12c) are actuatable, wherein in particular the first valve or the third valve can be selected and actuated in relation to the amount of rotational angle of the actuation mechanism.

5. Valve group (M) for flow control according to claim 4, wherein the first valve (12a) can be selected by an actuating mechanism (70) in a first rotational position and the third valve (12c) can be selected in a second rotational position different from the first rotational position, wherein preferably the rotational position can be selected in a third translational position.

6. The multiple valve group (M) for flow control according to claim 4 or 5, wherein the first valve (12a) is actuatable by means of a rotation of an actuation mechanism (70) in a first direction, and the third valve is actuatable by means of a rotation in a second direction different from the first direction.

7. A multiway valve block (M) for flow control according to claims 2 and 3.

8. Valve group (M) for flow control according to any of the previous claims, wherein the valve (12) has a valve body (50) and an orifice plate (40), wherein the orifice plate (40) is movable, preferably rotatable, with respect to the valve body (50) and is movable via the actuation mechanism (70).

9. The multiple valve block (M) for flow control according to claim 8, wherein at least one of the orifice plates (40) has a stem (45) for the actuating mechanism (70), wherein the orifice plate (40) has at least a first and an offset second housing (42a) for the driver.

10. A multiple valve group (M) for the flow control and distribution of fluids, having

-at least a first and a second valve line (2a-2h) and a common main line (1),

-at least a first and a second valve (12) for closing and opening the first and second valve line (2a-2h), respectively, wherein the valves (12a-12h) are arranged between the valve lines (2a-2h) and the main line, and

-an actuating mechanism (4) for actuating the valve, and

-wherein an actuatable pressure balancing device (5) for balancing pressure is provided in the pipeline (1), in particular in a component.

11. A multiple valve group (M) for flow control according to claim 10, wherein the pressure balancing means (5) is arranged so that the fluid flowing through the assembly flows substantially completely through the pressure balancing means.

12. Multiple valve group (M) for flow control according to claim 10 or 11, wherein the pressure balancing means comprise a shutter (83), wherein the shutter is slidable, preferably rotatable, in particular in the outlet cross section.

13. Multiple valve group (M) for flow control according to any of the claims from 10 to 12, wherein the pressure balancing means (5) are designed to partially close the outlet (8).

14. A multiway valve block (M) for flow control according to any of claims 10 to 13, wherein the pressure balancing means (5) is actuatable by a drive.

15. Valve group (M) for flow control according to claim 14, wherein the pressure balancing means are actuatable by the actuation mechanism (70) common to the valves.

16. A multiple valve group (M) for the flow control and distribution of fluids, having

-at least a first and a second valve line (2a-2h) and a common main line (1),

-at least a first and a second valve (12) for closing and opening the first and second valve line (2a-h), respectively, wherein the valves (12a-12h) are arranged between the valve lines (2a-2h) and the main line, and

-an actuating mechanism (4) for actuating the valve (12), and

-an actuating mechanism for actuating the valve (12), and

-wherein the actuating mechanism has a shaft arranged in the main line, and wherein the shaft is of a hollow configuration (73) such that fluid can flow through the shaft.

17. Multiple valve group (M) for flow control according to claim 16, wherein the shaft has a hole (71) so that the fluid can flow through from the outside to the inside and out of the shaft at one end of the shaft.

18. Multiple valve group (M) for flow control according to one of claims 16 to 17, wherein the shaft (76) is open at least at one end (74), wherein this end is preferably arranged towards the outlet of the valve assembly.

19. Multiway valve group (M) for flow control according to any of the previous claims,

-wherein the component (80) has a measuring unit (87).

20. The multiple valve group (M) for flow control according to claim 19, wherein the measuring unit (87) is replaceable.

21. Multiway valve group (M) for the flow control and distribution of a fluid, in particular according to one of the preceding claims, having

-at least a first and a second valve line (2a, b) and a common main line (1),

-at least a first and a second valve (12a, b) for closing and opening the first and second valve line (2a, b), respectively, wherein the valves are arranged between the valve lines and the main line,

-an actuating mechanism (70) for actuating the valve (12),

-wherein the valve assembly has a drive unit (9) for the actuating mechanism (70),

-wherein the drive unit (9) has a drive shaft (16) for a motor, the direction of rotation of which is perpendicular to the longitudinal direction of the main pipeline.

22. Valve manifold (M) according to claim 21, wherein the electric motor for the drive unit (9) is arranged laterally to the longitudinal axis of the main line.

23. Valve manifold (M) according to claim 21 or 22, wherein the drive unit is designed to axially displace and rotate the actuation means with respect to the main line.

24. Valve manifold for flow control (M), in particular according to any one of the preceding claims, wherein the valves each have a valve body (50) with an opening (52) for the valve line (2), which opening can be closed by an orifice plate (40), wherein a seal (56) is mounted between the opening and the orifice plate (40), wherein the seal is pressed against the orifice plate (40), preferably by a spring element (57).

25. The multiple valve group (M) for flow control according to any of the previous claims, the arrangement having a drive unit (9) and wherein the drive unit has a pivoting arm (25) and one end of the pivoting arm is connected to the actuating mechanism (70, 23), wherein the pivoting arm is arranged such that the actuating mechanism (70) is axially displaceable by means of rotation of the pivoting arm.

26. Multiple valve group (M) for flow control according to any of the previous claims, wherein the pivoting arm (25) and the actuating means (70) are connected such that only forces in the axial direction of the main line (1) can be transmitted from the pivoting arm (25) to the actuating means (70).

27. Valve multiplex group (M) for flow control according to any of the previous claims, wherein said actuation mechanism (70) has a shaft (76), wherein said drive unit has a worm gear for rotating said shaft around its own axis.

28. Multiple valve group (M) for flow control according to any of the previous claims, wherein all the seals around the movable part are annular.

29. Multiple valve group (M) for flow control according to any of the previous claims, wherein the first and second valves (12) each have a valve body (50) and these valve bodies (50) are arranged adjacent to each other in the longitudinal direction of the main line.

30. Valve group (M) for flow control according to any of the previous claims, wherein at least one sliding element (41, 56) is arranged between the valve body (50) of the valve (12) and the orifice plate (40) of the valve.

31. Valve group (M) for flow control according to any of the previous claims, wherein at least one valve (12), preferably all valves, respectively have a movable, preferably rotatable orifice plate (40), wherein the preferably rotational movement of the orifice plate (40) is limited by a stop mechanism (44, 51).

32. Valve manifold (M) for flow control according to claim 31, wherein the orifice plate (40) has a hollow cylindrical configuration and is arranged rotatable about its axis, wherein the stop means are preferably configured as pins guided in slots.

33. Multiple valve group (M) according to one of the previous claims, for flow control of air conditioning systems or heating systems.

34. Use of a multiway valve block (M) according to any of the preceding claims for flow control in an air conditioning system or a heating system.

Technical Field

The present invention relates to a multi-way valve block of the kind described in the preamble of the independent claim.

Background

In the control of the mix in hvac technology, irrigation technology and processes, valves of very different construction (in particular shutters and other diaphragm valves, as well as solenoid valves and ball valves) are often used for flow control. In particular, in heating and cooling systems, it is often necessary and desirable to control a plurality of local areas to be heated or cooled independently of each other, starting from a central supply and/or a central discharge, for example when heating/ventilating different rooms of a house. Today, such applications usually employ individually adjustable valves, wherein in different cases all valves have all mechanical and/or electrical means required for the adjustment. As a result, a modular construction of the multiple valve block is possible. However, this results in a highly complex apparatus due to the fully autonomous construction of the individual valves. As a result, the cost and space requirements of such systems are disadvantageous.

A multiple valve for supplying gas to a fuel cell system is disclosed in document EP 2918879. The multiport valve has a tubular passage with an inlet. A plurality of outlets are provided on the passage, which can be opened and closed by the closing body. However, the disclosed mechanism for operating the closing body is complicated and does not allow pressure equalization between the different lines.

DE102012214845 discloses a multiway valve for a motor vehicle cooling system. The valve has a single actuator that actuates a plurality of passage bodies that are generally cylindrical. However, the control of the channel body causes a plurality of channel bodies to be coupled together. Therefore, this document has the following disadvantages: the channel bodies cannot generally be controlled independently of one another.

Patent EP1515073 discloses a multiple valve group for flow control. The multi-way valve block has a plurality of valves that can be actuated by an actuating mechanism. The valves are of the same construction and can be selected and actuated depending on the amount of angular rotation of the actuating mechanism.

Disclosure of Invention

The object of the present invention is to remedy the drawbacks of the prior art. In particular, it is intended to provide a valve assembly which allows a plurality of valves to be actuated independently of one another. Particular embodiments may have the advantage that a plurality of valves may be actuated in a narrow space by means of a simple and compact device.

A first aspect of the invention relates to a multiple valve block for flow control of a fluid. The fluid may be a liquid or a gas. Thus, for example, water and/or air flow may be controlled by a valve assembly. The valve assembly has at least first and second valves and an actuating mechanism for actuating the valves. The valves are preferably of the same construction. The valve is arranged such that at least one predetermined valve can be selected and actuated in relation to the position of the actuating mechanism. The actuation mechanism is arranged to be translatably displaceable. Preferably, the actuating mechanism is translationally displaceable along the longitudinal axis of the main line of the valve. In a first translational position of the actuation mechanism, the first valve may be actuated, and in a second translational position different from the first translational position, the second valve may be actuated. The further valve is actuatable when the actuation mechanism is in the further translational position.

The first valve and the second valve (and optionally further valves) are connected together, in particular fixed together, by fastening means. The fastening means may comprise one or more screws.

The valves are preferably hollow and may together form a main line. The first valve and the second valve are preferably configured for opening and closing the first valve line and/or the second valve line fed into the main line. In a preferred variant, the actuating mechanism is arranged at least partially in the main line. In a preferred variant, the actuating mechanism is at least partially surrounded by the valve. The actuating mechanism preferably has an elongated configuration and extends along the axis of the main line.

An advantage of the valve assembly according to claim 1 is that all valves can be actuated and can be actuated by a common actuation mechanism. In addition, the number of valves that can be actuated by the actuation mechanism is limited only by the translational displacement of the actuation mechanism.

Another optional advantage is that simple control is provided since the actuating mechanism is able to actuate all valves.

In preferred embodiments, the device has three, four, five or more individually actuatable valves. In a particular embodiment, the device has eight valves. In another preferred embodiment, the device has 12 individually actuatable valves.

In a preferred embodiment, the actuation mechanism comprises a shaft, wherein the shaft is preferably arranged axially displaceable along its axis such that in a first axial position of the shaft the first valve is actuatable and in a second axial position different from the first axial position the second valve is actuatable. As a result, a particularly simple actuation mechanism can be provided. In one embodiment, the shaft may only move and rotate axially about its own axis.

In a preferred embodiment, the assembly is further provided with a pressure balancing device. The pressure balancing device is preferably actuatable in another (e.g. third) translational position of the actuation mechanism. As a result, a hydrostatic equilibrium can be created between the valve lines of the valve.

The third translational position is preferably the final translational position in the displacement direction of the actuating mechanism. As a result, adaptation of the valve and adaptation of the hydrostatic balance can be achieved more quickly, since the valve can be actuated first, then the hydrostatic balance (and vice versa) without having to displace the actuating mechanism back and forth.

In a preferred embodiment, the valve assembly has a third valve. In the first translational position of the actuation mechanism, the first valve and the third valve are actuatable. In this case, in particular the first valve and the third valve can be selected and actuated in relation to the amount of rotational angle of the actuating mechanism. As a result, multiple valves may be brought close to each other at the same translational position, which allows for a compact valve assembly.

In a variant, the actuation mechanism may be as embodied in EP 1515073. In a preferred embodiment, the first valve is selectable by a first rotational position of the actuating mechanism, and the third valve is selectable by a second rotational position of the actuating mechanism different from the first rotational position. The rotational position may be a specific angle, but may also be an angular range in which the respective valve may be actuated.

Preferably, in the third translational position, the actuating mechanism is moved either to the first rotational position or to the third rotational position, and then the actuating mechanism is displaced to the first translational position. Thus, in the first displaced position, the selected valve (i.e., the first valve or the third valve) may be actuated.

In the third, translated position, the actuation mechanism is preferably not engaged. In other words, no valve can be actuated in the third translational position, or a different device can be actuated.

In a preferred embodiment, the first valve may be actuated by rotation of the actuating mechanism in a first direction, and the valve, e.g., the third valve, may be actuated by rotation in a second direction different from the first direction. In particular, the actuation mechanism may be rotatable about its own axis to selectively actuate the first valve or the third valve. In particular, the first valve may be opened by rotation, while the second valve may be closed by reverse rotation. In the second rotational position, the actuation may be reversed, i.e. the first valve is closed when rotated in the second direction and the second valve is open when rotated in the first direction.

In alternative embodiments, two or more valves may be actuated simultaneously by an actuation mechanism.

In a preferred embodiment, the valve has a body and an orifice plate. The orifice plate may be movably, preferably rotatably, arranged relative to the body. Preferably, the orifice plate is rotatable about the axis of the main line. The orifice plate may be rotated to a first position in which a valve line of the valve is open. In addition, the orifice plate may be rotated to a second position in which the lines of the valve are closed.

Also, the orifice plate may be movable relative to the valve body by an actuation mechanism. In a variant, the orifice plate has the shape of a hollow tube. The orifice plate may include at least one drive for actuating the mechanism. The actuating mechanism may be designed to actuate the drive member. The driver preferably extends in a radially inner direction of the hollow tube. The drive member may be elongate, particularly preferably the drive member is configured as a pin.

Preferably, the or all of the orifice plates have one or two or more drives for the actuating mechanism. An advantage of two or more driving members is that forces and moments can be transmitted more efficiently. The orifice plate is preferably disposed in a cavity of the valve body. Particularly preferably, the perforated plate(s) is/are arranged in the main line. The perforated plate or the perforated plates preferably have at least one first receptacle for the drive element and a second receptacle offset from it. The receptacle may preferably be configured as a circular through-hole. The receptacles are preferably offset relative to one another in the circumferential direction along the longitudinal axis of the orifice plate. Due to the axially offset receptacles, individual orifice plates may be selected when actuated by the actuation mechanism.

This has the advantage that the orifice plate can be made of the same construction, but only with a different mounting of the drive member.

Alternatively, different orifice plates may have different configurations, and the pins may be attached at different axial positions.

Another aspect of the invention relates to a multiple valve block for flow control and distribution of fluids. The assembly comprises at least a first valve line and a second valve line having a common main line. The first and second valve lines preferably branch off from the main line. The assembly has at least a first valve and a second valve for closing and opening the first valve line and the second valve line, respectively. The valve is arranged between the valve line and the main line. The assembly also has an actuation mechanism for actuating the valve.

According to this aspect, an actuatable pressure balancing device is provided for pressure balancing in a main line, in particular in a component.

In a building, individual users (e.g., heating systems) are located on different floors. As a result, the fluid has a variable pressure, for example, when it flows back into the manifold block. The pressure balancing device adapts these pressures to the desired pressure downstream of the valve assembly, in particular in the return line. At the same time, the pressure ratios of the respective fluids from the valve lines are equal to each other.

In a preferred embodiment, the pressure equalization means is arranged such that the fluid flow is substantially completely through the pressure equalization means. As a result, the pressure of the entire fluid is ensured to be equal.

The valves are preferably of the same construction. The component is preferably connectable to a valve. This component is used in particular for hydrostatic balancing. The main line is preferably tubular. Preferably, the component forms part of the main pipeline. The longitudinal axis of the main line is preferably at right angles to the longitudinal axis of the valve line. The valve preferably has a valve body with a through-opening for the valve line.

In a preferred embodiment, the pressure equalizing device comprises a shutter. The shutter is located in the outlet cross section shutter. Preferably, the shutter is rotatable. In a particularly preferred embodiment, the shutters are arranged in a cross section of the main pipeline. The rams may be secured to a web extending through a cross-section of the main pipeline. In a first position, in which the shutter does not block the outlet, the shutter may extend along the web. In the second position, the shutter may at least partially cover the outlet.

In a preferred embodiment, the pressure equalization means are designed to at least partially close the outlet.

In a preferred embodiment, the pressure equalization means is actuatable by a drive. Particularly preferably, the pressure equalising means is actuatable by the same actuating mechanism as the valve. As a result, the pressure equalization means can be actuated in a simple manner.

Another aspect of the invention relates to a multiple valve block for flow control and distribution of fluids. The valve assembly has at least one first valve line and a second valve line, which have a common main line. The assembly also has at least a first valve and a second valve for closing or opening the first valve line and the second valve line, respectively. The valves are arranged between the respective valve lines and the main line. In addition, the assembly has an actuation mechanism for actuating the valve. The actuating mechanism has a shaft disposed in the main line and of hollow construction.

As a result, fluid may flow through the shaft. As a result, the flow through the main line can be increased, so that the assembly can, for example, have a smaller construction or can handle a larger volume.

In a preferred embodiment, the shaft has a bore such that fluid can flow from the outside to the inside and out of the shaft at one end of the shaft. The holes are preferably distributed in the axial direction of the shaft.

In a preferred embodiment, the orifices are arranged according to a desired volumetric flow rate. For example, the holes in the first portion may have a first spacing from each other, while the holes in the second portion may have a second, shorter spacing. Thus, the spacing between the bores in the axial direction may be shorter in valves where high volume flow is expected and larger in valves where low volume flow is expected.

In an alternative embodiment, the holes are evenly distributed over the length of the shaft. Alternatively, the holes may also be distributed non-uniformly. Thus, for example in valves with high volume flows, a relatively large number of holes and/or larger holes may be arranged.

In a preferred embodiment, the shaft is open at least at one end. Preferably, the end is arranged towards the outlet of the valve assembly. As a result, the flow conditions in the shaft are optimized.

Another aspect of the invention relates to a multiple valve manifold, preferably a valve assembly as described above. The valve assembly has a measuring unit for measuring the volume flow. The measuring unit is preferably arranged in the main line. Alternatively, each valve line may have a measurement unit. Particularly preferably, the measuring unit is arranged in the component. The measuring unit may comprise an impeller for measuring the flow. In a preferred embodiment, the measuring unit is replaceable. Furthermore, one or more sensors may be provided within the measurement unit for temperature measurement.

Another aspect of the invention relates to a multiple valve block for flow control and distribution of fluids. The valve assembly is in particular a valve assembly as described above. The actuating mechanism has a switch. The switch is preferably a shaft. The valve assembly also has a drive unit for the actuating mechanism. One or more electric motors for the drive unit are arranged laterally offset with respect to the longitudinal axis of the main line.

The drive unit transmits the motion of the motor to an actuating mechanism (e.g., a shaft). The drive units are preferably arranged along the axis of a common main line.

During installation of the above-described assembly, space is often limited. In particular, a space is generally limited in the longitudinal direction of the main pipeline. The proposed drive unit makes it possible to mount the electric motor laterally offset with respect to the longitudinal axis and thus saves space.

In a preferred embodiment, the drive unit has a drive shaft, the direction of rotation of which is perpendicular to the longitudinal direction of the main line. Further preferably, the drive unit has a worm gear in order to convert a rotation of the drive shaft into a longitudinal movement and/or translation of the actuation mechanism. The drive shaft is preferably the worm shaft of a worm gear. As a result, the motor can be arranged in a space-saving manner.

In a preferred embodiment, the drive unit is designed to move and rotate the switch member axially in the main direction. Further preferably, the axial displacement and the rotation are independent of each other.

Another aspect of the invention relates to a multiple valve manifold for flow control, and more particularly to a valve assembly designed as described above. The multi-way valve group comprises a first valve and a second valve. The valves each have a valve body with an opening. The opening may be closed by an orifice plate. A seal is attached between the opening and the orifice plate. The seal is pressed against the orifice plate. Preferably, the sealing member is pressed against the orifice plate by a spring member. In one embodiment, the seal may be made of polytetrafluoroethylene.

As a result, a seal may be provided between the valve body and the orifice plate. Preferably, the spring element is annular.

Another aspect of the invention relates to a multiple valve manifold for flow control. The actuation mechanism may have a shaft and/or include a switch for transmitting translational and/or rotational motion to the shaft. The switch may be immovably connected to the shaft.

The assembly may have a drive unit for the actuating mechanism. The drive unit may comprise a pivot arm which is coupled to the actuating mechanism, in particular the switch. The pivot arm is arranged such that the shaft is axially displaceable by rotation of the pivot arm.

In a multiple valve block in which a fluid is transported, it is difficult to achieve a reliable seal, mainly if an element movably arranged in the fluid chamber is to be driven from the outside. Control via the pivot arm allows for example a simple annular seal. Seals intended to seal against axial movement through the housing are complex and in some cases fail more quickly. Such seals can be avoided by pivoting arms.

In a preferred embodiment, the pivot arm and the shaft are coupled such that only forces acting axially to the shaft can be transmitted from the pivot arm to the shaft. Preferably, the shaft has a switch or is axially connected to a switch. The pivot arm may have a pin which is guided through the switch in a direction transverse to the longitudinal axis. In this case, the pin is preferably free perpendicularly to the longitudinal axis, and forces can be transmitted along the longitudinal axis.

In a preferred embodiment, the motor has a rotary motor to rotate the shaft about its own axis. Particularly preferably, the rotating electrical machine is coupled to the shaft by a worm gear.

In a preferred embodiment, all seals around the movable part are annular. Particularly preferably, the force is transmitted from the electric motor to the drive unit exclusively by rotation.

In a preferred embodiment, the first valve and the second valve each have a valve body, and the valve bodies are arranged adjacent to one another in the longitudinal direction relative to the main line.

In a preferred embodiment, at least one sliding element is arranged between the valve body and the orifice plate. Preferably, the sliding element is arranged on a radially outer surface of the orifice plate. The orifice plate may be more easily moved between the open and closed positions by a sliding element.

In a preferred embodiment, the valves each have a movable orifice plate. The movement, particularly the rotation, of the orifice plate is limited by a stop mechanism. As a result, the movement of the orifice plate can be restricted and the operation of the orifice plate can be simplified.

In a preferred embodiment, the orifice plate has a hollow cylindrical configuration and is arranged to be rotatable about its axis. The stop means is preferably formed by a stop pin which is guided in a groove of the perforated plate. Alternatively, a slot or elongated recess may also be configured in the valve body, and the orifice plate receives the pin (kinematically reversed).

The multi-way valve set is particularly suitable for controlling the flow of an air conditioning system or a heating system, particularly a water heating system in a building.

Another aspect of the invention relates to the use of a multiway valve block as described above for flow control in an air conditioning system or a heating system.

Another aspect of the invention relates to a heating system and/or a cooling system comprising at least one multi-way valve block as described above.

Drawings

In the following, the invention is described in more detail with reference to the appended drawings, which only show exemplary embodiments. In the drawings, schematically:

FIG. 1: a multi-way valve block according to the invention is shown,

FIG. 2A: showing valves for a multi-way valve block according to figure 1,

fig. 2B and 2C: a cross-sectional view of the valve assembly according to figure 2A is shown,

FIG. 3: a valve with an orifice plate for a valve assembly is shown,

fig. 4A and 4B: various perspective views of the orifice plate of figure 3 are shown,

FIG. 5A: a perspective view of the actuation mechanism and orifice plate of the multiple valve block according to figure 1 is shown,

FIG. 5B: a cross-sectional view of the actuation mechanism of figure 5A is shown,

FIG. 6A: a first internal perspective view of the drive unit is shown,

FIG. 6B: a second inner perspective view of the drive unit is shown,

FIG. 7A: a third inner perspective view of the drive unit is shown,

FIG. 7B: an exploded perspective view of the drive unit is shown,

FIG. 8A: a perspective view of the components for a multiple valve block according to fig. 1 is shown, an

FIG. 8B: an internal perspective view of the component according to fig. 8A is shown.

Detailed Description

Fig. 1 shows a perspective view of a multiple valve block M. The valve assembly M includes a plurality of valves 12a to 12h and a driving unit 9. The valve 12 is constructed as a tubular part and is hollow on the inside. The valves 12 together form the main line 1 (see fig. 2A to 2C). A valve line 2a to 2h extending transversely from the main line 1 is configured on each valve 12a to 12 h. At the valve lines 2a to 2h, a fluid (in particular water) is guided into the main line 1 or branched off from the main line 1. The main line 1 leads to a similar tubular component 80. Fluid flows out of or into the valve assembly M through an outlet or inlet 8. In the following, it is assumed that fluid flows in through the valve lines 2a to 2h and out from the outlet 8 via the main line 1. Of course, a reverse path is also conceivable, i.e. fluid flows in through the inlet 8 and out through the valve lines 2a to 2 h.

The valves 12 are of identical construction and are arranged adjacent to one another. The valves 12 can be snap-fit to each other and held together by the screw 6. The screw 6 is fixed on one side of the outlet 8 to a flange 81 of the part 80 and on the other side to a connection 11 for attachment to the screw of the drive unit 9. The valves 12 are held together by nuts that can be attached to the sides of the flanges.

Fig. 2A to 2C show one of the valves 12 in detail. Fig. 2A is a perspective view of the valve 12 alone, while different cross-sectional views of the valve 12 are shown in fig. 2B and 2C.

The valve 12 includes a generally circular tubular valve body 50. As described in connection with fig. 1, the valves are connected together by plugging. For plugging, the valve body has one or more pins 61. The pins 61 are inserted into the corresponding receiving portions 62 of the adjacent other valves 2, respectively. In addition, the body 50 has a seal 54 on a connecting surface 64 that is adjacent to the next valve 12 (or component 80 or drive unit 9). The seal 54 is designed as an O-ring. The valves 12 are pressed against each other by the screw 6 (see fig. 1), whereby the seals 54 prevent fluid from escaping between the respective valves 12.

The valve main body 50 has a first receiving opening 53 at an upper portion for receiving the closing cap 63. A closure cap 63 is inserted into the opening 53 and secured to the valve body 50, for example by threads. By tightening the screw thread, the O-ring seal 60 is pressed against the valve body 50 and the closing cap 63, and seals the accommodation opening 53. In addition, a stopper pin 51 is fixed in the closing lid 63. The stop pin 51 extends into the main line 1 and in particular perpendicularly to the longitudinal axis L of the main line 1.

Further, the valve main body 50 has a second receiving opening 52 for receiving a pipe portion 55. The conduit part 55 is also hollow and tubular and thus forms a valve line (here indicated for example with one of the valve outputs 2a to 2h as 2). The conduit portion 55 is screwed by the screw thread between the valve body 50 and the conduit portion 55, thereby pressing the O-ring 59 against the valve body 50. A seal is formed between the valve body 50 and the conduit portion 55 by another O-ring 59 (see fig. 2C).

In addition, the conduit portion 55 has a line seal 56. The line seal 56 provides a seal between the orifice plate 40 (see fig. 3 and 4A and 4B) and the conduit portion 55. For this purpose, a third O-ring 58 is provided between the seal 56 and the conduit portion 55. An elastic member, preferably an elastic spring member 57, is arranged between the line sealing member 56 and the conduit portion 55 in the axial direction of the valve line. The elastic spring member 57 presses the line sealing member 56 toward the main line 1. As a result, the line seal 56 is pressed against the orifice plate 40, so that when the orifice plate is closed, no or only little leakage fluid enters the main line 1 from the valve line 2.

Fig. 3 shows the complete valve 12. In addition to the valve body 50 (with components according to fig. 2A to 2C), the valve 12 also contains an orifice plate 40. The orifice plate 40 is rotatably mounted in the valve body 50.

Hereinafter, the orifice plate 40 will be described in detail with reference to fig. 4A and 4B, which show a perspective view of the orifice plate 40. The orifice plate 40 is a tubular member having a sliding pad 41 on a radially outer surface. The sliding pad 41 allows the orifice plate 40 to be rotatably held in the main line 1 by the valve body 50 about its own axis.

In addition, the orifice plate 40 has an elongated stop slot 44. A stop pin 51 (see fig. 2B and 2C) is guided in the stop groove 44. The rotation of the orifice plate 40 in the main line 1 is limited within a certain angular range by the stopper groove 44.

The orifice plate 40 has a circular orifice plate opening 43 on the side opposite the stop slot 44. If the orifice plate opening 43 overlaps the outlet of the valve line 2, fluid can flow from the valve line 2 into the main line 1. If the orifice plate 40 is rotated, it closes the valve line 2.

The perforated plate is driven by a driver designed as a pin 45. The pin 45 is held in the accommodating portion 42 for accommodating the pin 45. The perforated plate 40 shown has a series of eight adjacent receptacles 42a to 42h for the pins 45 in the longitudinal direction of the perforated plate 40. In addition, the perforated plate has four such series in the circumferential direction, each series having eight adjacent receptacles 42a to 42h for the pins 45. In the circumferential direction, each string is angularly spaced apart by 90 °.

As can be seen in fig. 4B, the pins 45 are only fixed in two (opposite) receptacles (i.e. spaced 180 ° apart). The pin 45 is selected and actuated by an actuating mechanism 70 (see fig. 5A and 5B). Each of the eight valves 12 of fig. 1 has an orifice plate 40. For example, the orifice plate shown in fig. 4B may be part of the valve 12a because the pin 45 is secured in the receptacle 42 a. In the valve body 2b, the pin may then be fixed in the opposing housing portion 42b or the like.

Fig. 5A shows the actuator mechanism 70 and the orifice plate 40. The actuating mechanism 70 has a shaft 76 and a switch 23. Switch 23 is fixed to shaft 76 by rivet 75 (see fig. 5B). The shaft 76 is arranged in the main line 1 and can be axially displaced in the longitudinal direction L. In addition, the shaft 76 may rotate about its own axis. A plurality of drivers 71 are disposed on a radially outer surface of the shaft 76. The driver 71 is engageable with the pin 45 of the orifice plate 40. Thus, the driver 71 is flat in the longitudinal direction L on the circumferential side of the shaft. The drive member 71 is configured as an elongated pin that is inserted through the shaft 76.

To actuate the orifice plate 40, the shaft 76 is displaced in the longitudinal direction L until the driver 71 and the pin 45 are in the same axial position. The shaft is then rotated so that the drive rotates the pin 45, thereby rotating the orifice plate 40. Depending on the direction in which the orifice plate 40 is intended to rotate, the shaft 76 must rotate circumferentially to the respective side of the pin 45. Since the shaft 76 and the orifice plate 40 each have two pins 45/drivers 71 at the same axial position, both pins are always driven in the case of actuation.

For example, if the orifice plate is to be rotated in one direction U1, shaft 76, as shown for example, is displaced in the axial direction A1 and then rotated in direction U1 until the desired position is reached. For the opposite direction U2, before engaging pin 45 and driver 71, shaft 76 must be rotated in direction U1 to pass the driver behind pin 45. The shaft may then be axially displaced again so that it engages the pin 45 and the orifice plate is rotated in the direction U2.

A plurality of drivers 71 are arranged at equal intervals on the shaft 76. Since each of the valves 12a to 12h is intended to be individually actuatable, the pins 45 are fastened to different receptacles 42a to 42h in different orifice plates 40a to 40h of the valves 12a to 12 h. Thus, which valve 13 is actuated can be determined by the axial position of the shaft. For example, in the first axial position, the orifice plate for the valve 12a is actuatable, since in this position the driver 71 can engage the orifice plate 40a for the valve 12 a. In this axial position, only the orifice plate 40a is actuatable. The pins of the remaining orifice plates are located elsewhere so that, upon actuation of the valve 40a, the corresponding actuators 71 rotate without engagement.

In the second axial position, the orifice plate 40B can be used to control the valve 12B, since in this position one of the actuators 71 can engage with the corresponding pin 45 of the orifice plate 40B of the valve 12B. The same applies to the other valves 12c to 12 h. In another axial position, no valve may be actuated by shaft 76. In this position, the shaft may be free to rotate, and the rotational position of the shaft may be selected to determine in which direction the valve is intended to be actuated.

In one variation, both valves may be actuated in a first axial position. In this case, the plurality of pins 45 are arranged in the orifice plate between the two valves 12 offset by 90 ° at the same position (see the series of empty links 42a-h in fig. 4A). If the first valve is to be actuated, the shaft 76 is first moved to the respective rotational position and then axially displaced until the driver 71 overlaps the respective pin 45. To actuate the second valve, the shaft must first be displaced back again and rotated by 90 ° to be able to turn into the first axial position. Thus, multiple valves may be actuated simultaneously in one axial position. An example of such a rotary selection is disclosed in patent application EP 1515073.

As shown in fig. 5B, the shaft 76 is hollow inside and has an inner cavity 73. One end 74 of the shaft is open. A plurality of holes 72 are arranged between the drivers 71. Fluid may flow into the interior 73 of the shaft through the aperture 72 and then out at one end of the shaft 74. As a result, the flow rate of the valve can be increased since the cross-section of the shaft 76 is also utilized.

The switch 23 is described in detail in connection with the following figures.

Fig. 6A to 7B show different views of the drive unit 9.

Fig. 6A shows shaft 76 with switch 23. The switching piece 23 is mounted on one end of the shaft and has a cam receiving portion 29 at one end thereof. The cam receiving portion 29 is engaged with the spline shaft 14 through the cam 30. The actuating mechanism (shaft 76 and switch 23) is movable in their longitudinal direction L and can be pushed onto the splined shaft 76 and accommodate the splined shaft 14 in its interior 73. As a result, the rotation can be transmitted to the switching member 23 through the spline shaft 14, and thus to the shaft 76. Since the spline shaft 14 is axially displaceable relative to the switching piece 23, no axial force is transmitted to the spline shaft 14. The spline shaft 14 is axially immovable.

Fig. 6B shows how rotation is transmitted to the spline shaft 14. The spline shaft is fixed by a rotation bearing (ball bearing 32, fig. 6A) and sealed to the outside by a seal. A seal to externally seal the spline shaft 14 is disposed between the ball bearing support 33 and the housing 15 (see fig. 7B). The rotation is transmitted to the spline shaft 14 through the worm wheel. The worm shaft is held by two swivel bearings, which are sealed by V-rings, respectively. The worm shaft 16 has a square head 34 at one end, and the motor may be attached to the square head 34. The rotation of the worm shaft 16 is transmitted to the worm wheel 22 via the shaft thread 21. The worm wheel 22 is fixedly connected to the axis of the spline shaft 14, so that the rotation of the worm shaft 16 is transmitted to the spline shaft 14 via the worm wheel 22.

Fig. 7A shows another view of the combination of the drive unit 9 and the actuating mechanism 70 (shaft 76, switch 23). Fig. 7A shows how the actuating mechanism 70 moves axially. The axial movement is transmitted to the shaft 76 by the rotating arm 25. The swivel arm 25 swivels at a first end about a swivel bearing 27 and has at a second end a pin 24 extending at right angles to the swivel arm 25. The drive shaft 18 extending through the housing 15 is fixed to a first end of the rotating arm 25.

The switch 23 has a disk 31 at its end facing the drive unit 9, which disk is connected to the remaining switches 23 by a cam 30. The pin 24 is guided between the plate 31 and the remaining switch 23. It should be mentioned that any radial groove which may also extend in the circumferential direction may also be suitable.

By guidance, the pin 24 is able to transmit forces in the axial direction, while the pin 24 is free in the radial direction of the shaft. If the pin 24 is moved about the rotary bearing 27 via the swivel arm 25, the shaft 76 moves back and forth in its axial direction without radial forces acting on it. Meanwhile, in the proposed device, the driving in the radial direction and the driving in the axial direction are not related to each other and can be actuated independently of each other.

Fig. 7B shows the complete housing 15 for the drive unit 9. The housing 15 comprises a first housing part 17 on which four connecting pieces 11 for the threaded rods 6 are arranged. The housing 15 has a first opening 35, and the valve 12h is attached to the first opening 35. The cover 13 closes the second opening 36, wherein a square 39 of the drive shaft 18 extends through the cover 13 for driving the arm 25. Furthermore, the cover 13 has an opening 37 for ventilation or emptying. Since the holes are oriented downwards (in particular in the direction of the valve line 2) when used as required, residual fluid in the main line can optionally be discharged through the holes 37 in the case of maintenance. The aperture 37 may be closed by a closure 38.

Fig. 8A shows a perspective view of the component 80. The member 80 has a flange 81 with a through hole 82. The through hole 82 accommodates the screw 6. By means of the nut, the flange 81 can be pushed towards the drive unit 9 and thus fix the valve 12. The component 80 has a component body 83. The body 83 is tubular and abuts the valve 12 as shown in fig. 1. In this case, the component 80 forms part of the main line 1. A pressure equalizing device 5 is arranged in the component 1 in the main line 1. The pressure compensation device 5 comprises a hydraulic stator 84 and a slide designed as a hydraulic rotor 83.

The hydraulic stator 84 is fixed transversely to the main line 1. The hydraulic rotor 83 is fixed to the hydraulic stator 84. The hydraulic rotor has two pins 85 that can be actuated by the actuating mechanism 70. If the hydraulic rotor 83 is actuated, it rotates about the longitudinal axis of the main line 1. In this case, the hydraulic rotor 83 is at least partially fixed to a web 86 extending through the main line 1.

If the volume flow through the component 80 is too large, the hydraulic rotor 83 can rotate, covering a larger cross section of the main line 1. As a result, the volume flow in the return line is reduced. Furthermore, the pressure on the inflow side can be increased, thereby reducing the flow rate.

Fig. 8B also shows the component 80, but rotated 90 ° relative to fig. 8A. In contrast to fig. 8A, the hydraulic rotor 83 and the hydraulic stator 84 are not visible. As shown, the component 80 also includes a flow sensor 87, which may be configured as an impeller. The impeller measures the flow through the enclosure portion 80. The sensor 87 may be inserted into the main line 1 through a lateral opening 88. As a result, the sensor 87 can also be easily removed or replaced again.

Since the sensor is arranged at the outlet 8 of the module M, the entire flow through the module can be measured.