CN220668478U

CN220668478U - Valve system

Info

Publication number: CN220668478U
Application number: CN202322003013.1U
Authority: CN
Inventors: U·西克斯特; S·穆勒
Original assignee: Festo SE and Co KG
Current assignee: Festo SE and Co KG
Priority date: 2022-07-27
Filing date: 2023-07-27
Publication date: 2024-03-26
Anticipated expiration: 2033-07-27
Also published as: DE102022118801A1

Abstract

The utility model relates to a valve system for influencing a fluid flow, comprising a base body, on which an input connection, a working connection and an output connection are formed; and a first fluid passage extending between the input port and the first valve seat, a second fluid passage extending between the output port and the second valve seat, a third fluid passage extending between the second valve seat and the working port, and a fourth fluid passage extending between the first valve seat and the third fluid passage; and having first and second control valves. According to the utility model, the first smallest cross section of the first fluid channel and/or the first valve seat and/or the fourth fluid channel is selected smaller than the second smallest cross section of the second fluid channel and/or the second valve seat and/or the third fluid channel.

Description

Valve system

Technical Field

The present utility model relates to a valve system.

Background

The utility model relates to a valve system for influencing a fluid flow, comprising a base body, on which an input connection, a working connection and an output connection are formed, wherein a first fluid channel extending between the input connection and a first valve seat, a second fluid channel extending between the output connection and a second valve seat, a third fluid channel extending between the second valve seat and the working connection, and a fourth fluid channel extending between the first valve seat and the third fluid channel are formed in the base body; and having a first control valve with a first valve member that is relatively movable with respect to the first valve seat and a second control valve with a second valve member that is relatively movable with respect to the second valve seat.

Disclosure of Invention

The object of the present utility model is to provide a valve system with which an advantageous compressed air supply to a compressed air load can be ensured.

This task is solved with the following features:

a valve system for influencing a fluid flow, the valve system having a base body on which an input port, a working port and an output port are formed, wherein a first fluid channel extending between the input port and a first valve seat, a second fluid channel extending between the output port and a second valve seat, a third fluid channel extending between the second valve seat and the working port, and a fourth fluid channel extending between the first valve seat and the third fluid channel are formed in the base body; and the valve system has a first control valve and a second control valve, wherein the first control valve has a first valve component which can be adjusted in a relatively movable manner relative to the first valve seat, and the second control valve has a second valve component which can be adjusted in a relatively movable manner relative to the second valve seat, characterized in that a first minimum cross section of the first fluid channel and/or a first minimum cross section of the first valve seat and/or a first minimum cross section of the fourth fluid channel is configured smaller than a second minimum cross section of the second fluid channel and/or a second minimum cross section of the second valve seat and/or a second minimum cross section of the third fluid channel.

It is provided that the first minimum cross section of the first fluid channel and/or the first valve seat and/or the fourth fluid channel is configured or selected to be smaller than the second minimum cross section of the second fluid channel and/or the second valve seat and/or the third fluid channel.

The respective (first or second) smallest cross section of the respective fluid channel or valve seat is the smallest cross section available in the respective fluid channel or at the respective valve seat, as specified using the valve system for a fluid flow to be influenced by means of the valve system, in particular compressed air. It can be provided here that the respective fluid channel has a constant, minimum cross section over its entire length, or that a sharp local constriction like a throttle orifice is formed in the respective fluid channel, or that the fluid channel is configured at least in regions with a conical section taper, and that the respective minimum cross section is determined thereby. The first valve seat or the second valve seat can preferably be configured as a circular bore, which is surrounded in particular by an annular, preferably cut-off, seat ring, wherein the inner diameter of this bore can possibly define a first or a second minimum cross section.

When the valve system is used as intended, a compressed air source is connected to the inlet connection, the outlet connection serves as an outlet connection, which can be connected in particular to a muffler, and a fluid load, for example a single-acting pneumatic cylinder, is connected to the working connection. The inflow of compressed air from the compressed air source through the first fluid channel, the first valve seat, the fourth fluid channel and the partial section of the third fluid channel extending from the fourth fluid channel up to the working connection can take place here by means of the first valve member of the first control valve which is selectively sealingly resting against the first valve seat or which releases the first valve seat. In this case, it is preferably provided that the second control valve keeps the second valve seat closed by means of an associated second valve member. Alternatively, it can be provided that the first control valve closes the first valve seat with the first valve member, thereby interrupting the fluid-communication connection between the compressed air source and the working connection, and that the second control valve lifts the second valve member from the second valve seat, so as to ensure a fluid-communication connection between the working connection and the compressed air load mounted thereon, the third fluid channel, the second valve seat, the second fluid channel and possibly a muffler connected to the output connection. In this connection, a targeted ventilation and venting for the compressed air load can be provided by appropriate actuation, in particular electrical actuation or pneumatic pilot actuation, of the first control valve and the second control valve.

In the field of industrial automation, it is typical to operate with a compressed air source providing a supply pressure of 6bar, whereas the compressed air load is usually operated at a maximum pressure level of 2 bar. As a result, a pressure difference of up to 6bar between the supply connection and the working connection can occur for the ventilation of the compressed air load by means of a fluid flow between the compressed air source and the working connection with a corresponding actuation of the first control valve. During the exhaust process, a maximum pressure difference of 2bar between the working connection and the output connection is also obtained by purely exemplary setting of the maximum working pressure for the compressed air load of 2 bar. In order to avoid that the exhaust process runs much slower than the venting process due to a significantly lower pressure difference, in the valve system according to the utility model a larger minimum cross section is provided in the exhaust path from the working interface comprising the third fluid channel, the second valve seat and the second fluid channel than in the venting path comprising the first fluid channel, the first valve seat and the fourth fluid channel. Correspondingly, the exhaust gas path has a significantly lower flow resistance than the ventilation path. The duration of the complete ventilation of the compressed air load is thus at least substantially the same as the duration of the subsequent ventilation process of the compressed air load, starting from the complete ventilation of the compressed air load that occurred before.

Advantageous developments of the utility model are the subject matter of the dependent claims.

Advantageously, the base body comprises a base body lower part and a base body upper part connected to the base body lower part, wherein a first fluid channel, a second fluid channel, a third fluid channel, a fourth fluid channel, a first valve seat and a second valve seat are formed in the base body lower part, and wherein an electronic control device, a first valve drive for the first valve member and a second valve drive for the second valve member are arranged in the base body upper part. Thus, the valve system has a modular structure, wherein a partition is present between a lower base body part for the fluid and an upper base body part for the control technology. By means of the partition, it is possible to adapt the valve system to different compressed air loads by selecting a suitable base body lower part from the group of several base body lower parts realized with different minimum cross sections, without the need to forcibly replace the much more complex base body upper part together with the components accommodated therein, such as the valve drive and the control device. Preferably, a large number of differently designed base bodies can be mounted at the base body upper part in order thereby to create a modular system which enables an advantageous adaptation to the requirements and the use conditions of the respective compressed air load.

Advantageously, a first interface is formed on the upper base part and a second interface is formed on the lower base part, wherein the first interface and the second interface are configured for fluid-tight coupling of the upper base part to the lower base part at least in regions. The first interface on the upper part of the base body and the second interface on the lower part of the base body are designed such that a reliable mechanical connection and a fluid-tight connection are ensured between the lower part of the base body and the upper part of the base body. Preferably, the first and second interface are configured such that the base body lower part can be removed from the base body upper part in an easy manner, for example using only a hand tool such as a screwdriver, and can be replaced by a base body lower part which is designed in other ways, with which an advantageous adaptation to the respective compressed air load is achieved.

In a development of the utility model, a pressure sensor is provided, which is connected to the electronic control device and is configured to detect the fluid pressure in the first fluid channel or the second fluid channel or the third fluid channel or the fourth fluid channel. The pressure sensor is capable of determining a supply pressure provided by the compressed air source when the pressure sensor is placed in the first fluid passage. When placed in the third fluid passage or the fourth fluid passage, the pressure sensor provides information about the operating pressure provided to the compressed air load. Monitoring of the exhaust pressure can be achieved when the pressure sensor is placed in the second fluid channel.

Preferably, the electronic control device is configured for processing the pressure signal of the pressure sensor and for performing a pressure regulation at the working interface. For this purpose, it is provided, for example, that the electronic control device is able to set the pressure at the working output to a constant value or to set it according to a predetermined pressure profile on the basis of an external pressure signal, which can be provided in particular by a superordinate control device, for example a machine control device, and that a pressure signal of a pressure sensor is used for this purpose, which pressure sensor is preferably arranged in the third fluid channel or in the fourth fluid channel. Particularly preferably, the first control valve and the second control valve are actuated by the electronic control device in such a way that they can perform a proportional pressure control.

In a further embodiment of the utility model, provision is made for the first valve drive to be configured for freely selectable electrical adjustment of the position of the first valve member between a blocking position, in which it rests sealingly against the first valve seat, and a release position, which is arranged away from the first valve seat; and/or the second valve actuating means is configured for freely selectable electrical adjustment of the position of the second valve member between a blocking position sealingly abutting against the second valve seat and a release position arranged away from the second valve seat. The movement performed by the respective valve member between the blocking position and the release position is also referred to as valve lift. The first control valve and/or the second control valve are preferably configured in such a way that a movement of the respective valve member can be preset, in particular proportional, by the electrical control device in a predefinable manner, in particular proportional, as a function of the respective signal level of the first actuating signal or of the second actuating signal.

Advantageously, the control device is designed to adjustably preset the maximum valve lift as a distance between the blocking position and the release position of the first valve drive and/or of the second valve drive. Advantageously, the limits on the valve lift can be set as a function of the characteristics of the two control valves and the ventilation path, the exhaust path and the compressed air load, so that advantageous characteristics, in particular advantageous movement characteristics, for the compressed air load can be preset. Such a limitation of the valve lift can be achieved by an electronic control device in the case of electrically controllable control valves, in which case the electronic control device does not provide a control signal which would cause the valve lift to be higher than the respective preset limit, even if, for example, a particularly rapid ventilation or venting for the compressed air load is to be provided.

Suitably, the first control valve and the second control valve are selected from the group consisting of: solenoid valve, fluid pilot controlled pneumatic valve, piezo-electric bending valve. In the solenoid valve, the lift motion of the introduction valve member is achieved by changing the magnetic field. For this purpose, it is generally provided that the coil current of the energized coil is varied, and thus also a change in the magnetic interaction between the magnetic field provided by the coil and an active or passive magnetic component, for example a further magnetic coil, a permanent magnet or a yoke, is present, as a result of which a movement, in particular a linear movement, of the respective valve member can be brought about. Alternatively, at least one valve from the group of first and second control valves is configured as a fluid pilot controlled pneumatic valve, wherein the lift movement of the valve member is dependent on the fluid pilot control pressure. In a further alternative, at least one valve from the group of the first control valve, the second control valve is configured as a piezo bending valve, wherein the movement of the valve member is caused by a change in curvature of a bending piece clamped on one side and made at least regionally of piezo material. For this purpose, an electrical control voltage is supplied to the respective piezo bending valve by the control device.

In an advantageous further development of the utility model, a plurality of second fluid channels extend from the third fluid channel, which flow together into the output connection, wherein each of the second fluid channels is provided with a second valve seat, a second control valve and a second valve member. In this embodiment, a plurality of second control valves is used to ensure that the free cross section of the exhaust gas path is influenced, wherein it can optionally be provided that all second control valves are actuated in parallel or that a sequential switching of the control valves is performed as a function of the exhaust gas cross section to be released.

In a further embodiment of the utility model, it is provided that the first and second minimum cross-sections are predefined to be constant through the respective fluid channel and/or valve seat. In this case, the geometric configuration of the first to fourth fluid passages is fixedly preset, and the same applies to the geometric configurations of the first valve seat and the second valve seat. This ensures that the fluid flow in the ventilation path and in the exhaust path always has a flow profile that depends on a fixedly predefined geometry and not on an adjustable component, for example an adjustable orifice or a throttle valve. The predictable behavior of the valve system is thus ensured for a wide range of applications, in particular within a defined supply pressure range and when using the compressed air load for which the valve system is configured.

Drawings

Advantageous embodiments of the utility model are shown in the drawings. Here:

FIG. 1 shows an overall perspective view of a valve system;

FIG. 2 shows the valve system according to FIG. 1 with the cover removed; and is also provided with

Fig. 3 shows a strictly schematic and not to scale illustration of the valve system.

Detailed Description

The valve system 1, which is shown in perspective in fig. 1 and 2, respectively, is provided for use with a compressed air load, not shown, such as a single-acting pneumatic cylinder, which should be ventilated and exhausted by the valve system 1. The valve system 1 comprises a base body 2, which is formed by a base body upper part 3 and a base body lower part 4, as shown in fig. 1, wherein the base body upper part 3 is covered by a cover 5, as shown in fig. 1. As can be seen from the illustration in fig. 1 and 2, the base body lower part 4 is of hexahedral design and can be inserted with mutually opposite, respectively essentially planar sides 6, 7 between the functional modules of the valve group, not shown. Alternatively, the valve system 1 can also be operated as a separate component.

An inlet connection 10 is formed on the side 6 of the base body lower part 4, to which an inlet connection, not shown, can be connected, or the compressed air supply can be carried out by adjacently arranged functional modules with the valve system 1 arranged between the functional modules of the valve group. An output connection 11 and a working connection 12 are provided on the front face 8 of the base body lower part 4, which is arranged adjacent to the side face 6 and is oriented at right angles to the side face 6.

As shown in fig. 1, the housing upper part 3 comprises a cover 5, which is provided purely by way of example with a display 21, a first function key 22, a second function key 23 and a third function key 24 and is penetrated by a control input 25. The display device 21 can be configured, for example, as a liquid crystal display and serves to display functional states and parameters which are important for the operation of the valve system 1. User inputs can be performed and confirmed with the function keys 23 to 24 in order to enable a user to influence the functional status and/or parameters of the valve system 1. The control input 25 can be used, for example, to supply the valve system 1 with control signals of a higher-level control device, not shown, in particular a machine control device. These control signals can be, inter alia, the following information: what working pressure should be provided at the working interface 12.

The base upper part 3 is designed for coupling with the base lower part 4 and for this purpose has an interface 15, which is schematically shown in fig. 3, designed for functional connection with an interface 16 of the base lower part 4.

Purely by way of example, the basic body upper part 3 shown in fig. 2 comprises an assembly 30 of a first valve drive 31, a second valve drive 32 and a control circuit board 33. The two valve drives 31, 32 and the control circuit board 33 form both a mechanical and an electrical connection. Illustratively, it is provided that the component 30 can be preassembled and tested separately and then fastened with its interface 15 at the interface 16 of the base body lower part 4.

Starting from the inlet connection 10 in the base body lower part 4, a first fluid channel 41 is provided, which is only partially visible in fig. 1 and 2. From the output interface 11, a second fluid channel 42 extends, which is only partially visible in fig. 1 and 2. Extending from the working interface 12 is a third fluid passage 43 which is only partially visible in fig. 1 and 2. The fluid channels 41 to 43 and the fourth fluid channel 44, which is only visible in fig. 3, are implemented in the housing lower part 4, which is embodied purely by way of example as a plastic injection molding, and the housing lower part 4 also accommodates the first valve seat 61 and the second valve seat 62, which are visible in fig. 3.

In the schematic illustration according to fig. 3, the first valve drive 31 and the second valve drive 32 are designed more compactly than in the illustrations of fig. 1 and 2 for the sake of presentation. Furthermore, in contrast to the illustration in fig. 2, the first valve drive 31 and the second valve drive 32 are each accommodated in a separately constructed housing block 17, wherein, in contrast to the illustration in fig. 2, the control circuit board 33 is mounted on the upper side 18 of the housing block. Furthermore, a sensor recess 19 is provided in the housing block 17, in which a pressure sensor 20 is arranged, which seals the sensor recess 19 from the housing block 17 and which is electrically connected to the control circuit board 33 via a sensor line 70. The pressure sensor 20 is provided purely by way of example for detecting the fluid pressure in a branch channel 58 which is formed in the base body lower part 4 and which is connected in fluid communication with the working connection 12.

The underside 26 of the housing block 17 facing the base body lower part 4 is configured as an interface 15 and is provided for coupling with the interface 16 of the base body lower part 4.

The first valve drive 31 and the second valve drive 32 are electrically connected to the control circuit board 33 via a first or a second control line 71, 72, respectively. Furthermore, the first valve drive 31 and the second valve drive 32 are each embodied purely by way of example as a magnetic drive which is embodied in the same way, so that the following description applies to both the first magnetic drive and the second magnetic drive.

The following construction and principle of action are provided for the first valve drive 31 and the second valve drive 32: the excitation coil 83 accommodated in the annular gap between the guide sleeve 81 and the magnetic core 82 in a linearly movable manner along the movement axis 99 is electrically connected to the control circuit board 33 via the respective control line 71 or 72. The magnetic core 82 includes permanent magnets 84 having a circular shape, which are provided with yokes 85 having a circular shape, respectively, on end surfaces opposite to each other. The core 82 is inserted onto a holding mandrel 86, which is fixed on its side to a carrier plate 87 connected to the guide sleeve 81. The assembly of the carrier plate 87 and the guide sleeve 81 is accommodated in a fixed manner in the recess of the housing block 17.

The excitation coil 83 is wound on a winding body 88, which forms a sliding bearing with an inner surface 92 of the guide sleeve 81 and which has a purely exemplary cup-shaped valve member carrier 89. On an axially oriented end face 93 of the valve member carrier 89, a valve member 90 is mounted, which is made of a rubber-elastic material and is embodied purely by way of example in a cylindrical form, and is provided for selectively sealing or releasing a first valve seat 61 or 62, which is embodied in the lower base body part 4 and is described in more detail below.

When a coil current is supplied to the exciter coil 83 from the control circuit board 33, an interaction occurs between the energized coil winding of the exciter coil 83 and the magnetic flux supplied by the magnetic core 82, whereby a lorentz force occurs onto the energized coil winding, which lorentz force is oriented parallel to the axis of motion 99 and causes a linear movement of the rotor assembly 94, which is formed by the winding body 88, the valve member carrier 89, the valve member 90 and the exciter coil 83. It is merely exemplary that a return spring 91 is accommodated in the space section delimited by the valve member carrier 89, which is supported on the magnetic core 82 and the valve member carrier 89 and which exerts a closing force directed downward along the movement axis 99 on the valve member 90 as shown in fig. 3. By energizing the respective excitation coil 83, a lorentz force occurs that opposes this closing force, so that the valve member 90 can be lifted from the first valve seat 61 or from the second valve seat 62.

Purely by way of example, according to fig. 3, the first control valve 63, which is formed by the first valve drive 31 and the associated rotor assembly 94 and the first valve seat 61, is in the closed position, while the second control valve 64, which is formed by the second valve drive 32 and the associated rotor assembly 94 and the second valve seat 62, is in the open position.

In the base body lower part 4, starting from the inlet connection 10, a first fluid channel 41 extends, which opens out into a first receiving bore 45 for receiving the first valve drive 31 and an associated rotor assembly 94. The fourth fluid channel 44 merges at a bottom region 46 of the first receiving bore 45, wherein the converging opening 46 of the fourth fluid channel 44 is surrounded by a ring 47, which is configured as a conical section, and forms a first valve seat 61. The fourth fluid channel 44 merges into the third fluid channel 43 in a converging region 48. The third fluid channel 43 extends between the working connection 12 and the second receiving bore 49, wherein the flow-collecting opening 50 of the third fluid channel 43 is surrounded by a ring 51 embodied as a conical section and forms a second valve seat 62.

The second receiving bore 49 serves to receive the second valve drive 32 and the associated rotor assembly 94, wherein the valve member 90 can, depending on the position of the rotor assembly 94, bear sealingly against the ring 51 in order to interrupt the fluid-communication connection between the third fluid channel 43 and the second receiving bore 50 and the second fluid channel 42 connected to the second receiving bore 50. The second fluid channel 42 is connected to the output interface 11 on its side.

As can be seen from the illustration of fig. 3, the smallest diameter 52 of the first valve seat 61 and the smallest diameter 57 of the section of the fourth fluid channel 44 connected to this first valve seat are significantly smaller than the smallest diameter 54 of the first fluid channel 41, the smallest diameter 55 of the second fluid channel 42, the smallest diameter 56 of the third fluid channel 43 and the smallest diameter 53 of the second valve seat 62. Purely by way of example, the minimum diameter 52 of the first valve seat 61 is about 50 percent of the minimum diameters 53, 54, 55 and 56.

It is ensured thereby that the ventilation path defined by the first fluid channel 41 and the first valve seat 61 and the fourth fluid channel 44 has a substantially greater flow resistance than the exhaust path defined by the third fluid channel 43, the second valve seat 62 and the second fluid channel 42.

This measure makes it possible for a compressed air load, not shown, which is mounted on the working connection 12, for example a single-acting pneumatic cylinder, to be ventilated with the associated first control valve 63 fully open and the second control valve fully closed, in a similar time period to the venting of the compressed air load with the second control valve 64 fully open and the first control valve 63 fully closed.

Claims

1. A valve system (1) for influencing a fluid flow, having a base body (2) on which an input port (10), a working port (12) and an output port (11) are formed, wherein a first fluid channel (41) extending between the input port (10) and a first valve seat (61), a second fluid channel (42) extending between the output port (11) and a second valve seat (62), a third fluid channel (43) extending between the second valve seat (62) and the working port (12) and a fourth fluid channel (44) extending between the first valve seat (61) and the third fluid channel (43) are formed in the base body (2); and the valve system has a first control valve (63) having a first valve component which can be adjusted in a relatively movable manner with respect to the first valve seat (61) and a second control valve (64) having a second valve component which can be adjusted in a relatively movable manner with respect to the second valve seat (62), characterized in that the first minimum cross section of the first fluid channel (41) and/or the first minimum cross section of the first valve seat (61) and/or the first minimum cross section of the fourth fluid channel (44) is/are configured smaller than the second minimum cross section of the second fluid channel (42) and/or the second minimum cross section of the second valve seat (62) and/or the second minimum cross section of the third fluid channel (43).

2. Valve system (1) according to claim 1, characterized in that the base body (2) comprises a base body lower part (4) and a base body upper part (3) connected to the base body lower part (4), wherein the first fluid channel (41), the second fluid channel (42), the third fluid channel (43), the fourth fluid channel (44), the first valve seat (61) and the second valve seat (62) are configured in the base body lower part (4), and wherein the base body upper part (3) is provided with electronic control means (33), first valve drive means (31) for the first valve member and second valve drive means (32) for the second valve member.

3. Valve system (1) according to claim 2, characterized in that a first interface (15) is formed on the base body upper part (3) and a second interface (16) is formed on the base body lower part (4), wherein the first interface (15) and the second interface (16) are configured for fluid-tight coupling of the base body upper part (3) with the base body lower part (4) at least in regions.

4. A valve system (1) according to claim 2 or 3, characterized in that a pressure sensor (20) is connected to the electronic control device (33), which pressure sensor is configured for detecting a fluid pressure in the first fluid channel (41) or in the second fluid channel (42) or in the third fluid channel (43) or in the fourth fluid channel (44).

5. Valve system (1) according to claim 4, characterized in that the electronic control device (33) is configured for processing a pressure signal of the pressure sensor (20) and for performing a pressure regulation at the working interface (12).

6. Valve system (1) according to claim 2, characterized in that the first valve drive means (31) are configured for freely selectable electrical adjustment of the position of the first valve member between a blocking position sealingly against the first valve seat (61) and a release position arranged away from the first valve seat (61), and/or the second valve drive means (32) are configured for freely selectable electrical adjustment of the position of the second valve member between a blocking position sealingly against the second valve seat (62) and a release position arranged away from the second valve seat (62).

7. Valve system (1) according to claim 2, characterized in that the control device (33) is configured for adjustably presetting a maximum valve lift for the first valve drive (31) and/or for the second valve drive (32) to a distance between a blocking position of the valve member and a release position of the valve member.

8. Valve system (1) according to claim 6 or 7, characterized in that the first control valve (63) and the second control valve (64) are selected from the group of: solenoid valve, fluid pilot controlled pneumatic valve, piezo-electric bending valve.

9. Valve system (1) according to claim 1 or 2, characterized in that a plurality of second fluid channels extend from the third fluid channel (43), which together merge into the output interface (11), wherein each of the second fluid channels is provided with a second valve seat, a second control valve and a second valve member.

10. Valve system (1) according to claim 1 or 2, characterized in that the first and second minimum cross-sections are preset to constantly pass through the respective fluid channel (41, 42, 43, 44) and/or valve seat (61, 62).