Valve

Abstract

The invention relates to a valve, in particular a seat valve, comprising: a valve housing (10) which has two fluid ports (1, 2) for conducting fluid; an actuating device (12) for actuating a valve piston (14) which is longitudinally displaceably guided in the valve housing (10); a first fluid port (1) which opens axially in the direction of a free end face of the valve piston (14); a second fluid port (2) which opens radially in the direction of a circumferential wall (13) of the valve piston (14); and a check valve function which is integrated into the valve, wherein an extension (54) is provided at the free end face of the valve piston (14) in order to realise a diaphragm function, which extension, in a position which prevents the fluidic connection (56) between the fluid ports (1, 2), engages into the valve housing (10) with the axial fluid port (1), wherein, when fully engaged, a closed seat valve (58) is formed between parts of the valve housing (10) and the valve piston (14), wherein, when the fluidic connection (56) is released, the fluid flow between the two fluid ports (1, 2) is throttled, and wherein, at least when the valve seat (58) is closed, the check valve function is realised in which a fluidic connection (56) from the axial (1) to the radial fluid port (2) is enabled.

Description

[0001] valve

[0002] The invention relates to a valve, in particular a seat valve, with a valve housing which has two fluid connections for conducting fluid and with an actuating device for actuating a valve piston which is guided longitudinally displaceably in the valve housing, with a first fluid connection which opens axially in the direction of a free end face of the valve piston and with a second fluid connection which opens radially in the direction of a circumferential wall of the valve piston, as well as with a check valve function integrated in the valve.

[0003] From DE 10 2012 015 354 A1 a valve is known, in particular a pilot-operated proportional directional control valve, with a valve housing which has a fluid inlet and a fluid outlet, wherein the fluid flow between the fluid inlet and the fluid outlet can be regulated by a valve piston, wherein a pilot valve chamber is provided on a rear side of the valve piston with a pilot valve closing element which can be moved by an actuating device and with which the fluid flow between the pilot valve chamber and the fluid outlet can be regulated, wherein an inlet orifice is arranged between the fluid inlet and the pilot valve chamber, the opening cross-section of which can be reduced by a control element.Furthermore, a maximum volume flow regulator is provided within the valve housing. This regulator, similar to a spring-loaded check valve, has a control piston that is acted upon on one side by the pressure of the fluid flowing from the pilot chamber and on the other side by a compression spring. A flow regulator is thus integrated within the valve, and the inlet orifice cross-section, which can be reduced by means of the control element, causes the pressure in the pilot valve chamber to drop, thus opening up the possibility of actively regulating the opening stroke of the valve piston in addition to the regulation at the pilot valve seat. The smaller the differential pressure between the fluid inlet and fluid outlet, the larger the opening stroke of the valve can be adjusted, which is what enables the flow control function.

[0004] From the subsequently published patent application DE 10 2022 004 033.6, a generic valve is known with a valve housing which has two fluid connection points for conducting fluid and with an actuating device for actuating a valve piston of a seat valve accommodated in the valve housing, wherein a check valve is accommodated in the valve housing together with the seat valve and wherein at least one bypass line runs in the valve housing, which bypasses the check valve and forwards a fluid flow present at one fluid connection point, which is controllable by the valve piston of the seat valve, in the open state of the latter in the direction of a valve chamber.The check valve integrated in the valve housing is capable, if required, of discharging fluid on the consumer side via the valve into the subsequent fluid circuit at a very low opening pressure and with low flow loss, while again having a relatively large opening cross-section.

[0005] The known valve can therefore be very well combined with hydraulic damping cylinders as the respective consumer, especially in the form of so-called stabilizers as part of a vehicle's chassis. This allows the respective stabilizer to be designed to be stiffer for cornering than for off-road driving, where a soft suspension deflection is generally desired.

[0006] Based on this prior art, the object of the invention is to further improve the known valve solutions while retaining their aforementioned advantages.

[0007] A valve having the features of patent claim 1 in its entirety solves this problem.

[0008] Because, according to the characterizing part of patent claim 1, an extension is provided on the free end face of the valve piston for the realization of a diaphragm function, which extension engages in the valve housing with the axial fluid connection in a position that prevents the fluid connection between the fluid connections, that a closed seat valve is formed with a complete engagement between parts of the valve housing and the valve piston, that when the fluid connection is released, the fluid flow between the two fluid connections is throttled, and that when the seat valve is closed, the check valve function is realized, in which a fluid connection from the axial to the radial fluid connection is released, the volume flow can be directed in one flow direction via a check valve with a very low opening pressure and low flow losses,In the opposite direction, the volume flow can be opened (NO - Normally Open) or closed depending on the application of an electric current to the seat valve, in particular in the form of a seat-tight 2 / 2-way valve. The volume flow in the main direction is influenced by the orifice function of an integrated orifice. The generic valve in the prior art integrates, in addition to the solenoid-operated directional seat valve, a check valve and an orifice in a common valve housing in the manner of a combination valve, the implementation of which requires numerous components and, in addition, the machining of the valve body is complex, in particular due to the long,A thin bore for the bypass line past the check valve is very complex to implement and therefore costly. The inventive solution allows the same objective for the valve function to be pursued as for the generic prior art, but the required functions are achieved with fewer valve components. Furthermore, the inventive valve solution is significantly more compact, allowing the valve to be reliably integrated even in cramped installation conditions. Furthermore, due to the structurally simpler design—without a bypass line—the valve can be implemented cost-effectively.

[0009] In a preferred embodiment of the valve according to the invention, provision is made for a valve pilot control with a valve or control part, in particular in the form of a control cone, which controls an orifice in a fluid channel of the valve piston and is part of a valve control system consisting of at least two adjacent parts, between which a decoupling device is arranged. The valve control system is preferably designed rod-like in the form of an actuating rod, which has two adjacent rod parts, between which the decoupling device is arranged. Without such decoupling by means of the decoupling device, the check valve function required in the energized state would only respond at a significantly increased pressure level, which is undesirable in itself.In a further preferred embodiment of the valve according to the invention, the decoupling device comprises a spring arrangement with a main spring, which serves to adjust the actuating force of the actuating device, and with an additional or auxiliary spring, which serves to adjust the opening pressure for the check valve function. In this respect, the additional or auxiliary spring, designed as a check valve spring, also simultaneously serves to decouple within the framework of the decoupling device, so that the magnetic force does not act directly on the valve piston, but only indirectly on the main spring. Both the main spring and the additional or auxiliary spring each represent an energy storage device, in particular in the form of a single compression spring with a predeterminable spring stiffness.

[0010] In a further preferred embodiment of the valve according to the invention, it is provided that the decoupling device has a hollow cylinder-like receiving bushing which has at least one transverse bore, and that the main spring comprising the receiving bushing is supported with one free end on the valve housing and with its other free end on the receiving bushing, which is guided so as to be longitudinally displaceable in the valve housing. It is preferably further provided that the additional or auxiliary spring is supported with one free end on one part and with its other free end on the other part of the valve control, directly or indirectly via intermediate parts. In this way, the decoupling device with the aforementioned spring arrangement is integrated in a particularly space-saving manner within the valve housing with the longitudinally displaceable valve piston and is small in size, particularly when viewed in the axial actuation direction of the valve.

[0011] For a reliable control of the valve, it is intended that the

[0012] An additional or auxiliary spring is designed with a lower spring stiffness than the main spring and is mounted coaxially with the main spring within the mounting bushing. This ensures a functionally reliable, obstruction-free design for the decoupling device.

[0013] In a preferred embodiment of the valve according to the invention, the extension is formed from a hollow cylindrical wall section which, when the seat valve is closed, engages a hollow cylindrical recess in the valve housing with the axial fluid connection, forming a gap. In this way, the hollow cylindrical components of the valve ensure reliable guidance of the valve piston, with a defined opening or closing of the orifice cross-section via the extension. The gap in question serves to implement the orifice effect or throttling, whereby the gap size in detail, and thus the orifice effect, can be specified depending on the valve design.

[0014] In a further preferred embodiment of the valve according to the invention, the part on the valve piston that forms the valve seat of the seat valve is formed from an annular surface that tapers into a cone in the direction of the axial fluid connection, in particular in the form of a truncated cone, and that adjoins the extension in the direction of the actuating device. In this way, a fluid-tight blocking of the fluid connections from one another is achieved via the conical valve seat.

[0015] In a further preferred embodiment of the valve according to the invention, it is provided that the conical annular surface is adjoined in the direction of the actuating device by a further annular surface which is interrupted and projects transversely to the actuating direction on the valve piston, at least when the check function is triggered, and is guided so as to be at least partially movable along an inner side of the valve housing, which at least partially surrounds the valve piston. In this way, the valve piston can be reliably controlled by means of the further annular surface in the valve housing when there is appropriate fluid pressure at the radial fluid connection. In a further preferred embodiment of the valve according to the invention, it is provided that the valve piston is penetrated by a fluid channel in which the valve cone of the valve pilot control is guided at least partially longitudinally movable and controls the orifice in the fluid channel with its cone tip.In this case, a closing part, in particular in the form of a closing ball, is preferably accommodated in a receiving space in the valve piston in the fluid channel between the aperture for the valve cone and the hollow cylindrical wall section of the extension.

[0016] In this context, it is preferably further provided that a radial orifice is introduced into the valve piston, which at least when the seat valve is closed creates a fluid-carrying connection between the radial fluid connection in the valve housing and the receiving space in the valve piston with the valve cone received therein. Advantageously, the valve cone is part of the rod-like valve control, which, whether designed in one piece or interrupted, at least partially engages with its one free end opposite the valve cone in a magnet armature of the energizable actuating device and can be controlled by means of the same in a longitudinally movable manner. In this way, functionally reliable pilot control for the valve piston or main piston is achieved.

[0017] In another particularly preferred embodiment of the valve according to the invention, it is provided that a restoring force is exerted on a magnet armature actuated by the actuating device by means of at least one energy accumulator, preferably in the form of a main or compression spring. Preferably, several compression springs are used as energy accumulators, with a main spring being provided against which the magnet armature of the actuating device works, and a further auxiliary spring allowing an opening pressure to be specified at which the check valve function is activated. Furthermore, the invention relates to a method for operating a valve as presented above, wherein, with a "pressing" actuating device, a fluid connection from the radial fluid port to the axial fluid port can be released when de-energized; when energized, the seat valve is closed and the fluid connection between the two fluid ports is blocked.

[0018] - a check valve function is enabled from axial to radial fluid connection both when de-energized and when energized.

[0019] In the following, the solution according to the invention is explained in more detail using an exemplary embodiment according to the drawing. In this diagram, the

[0020] Figures 1 to 4 show in the form of a longitudinal section the valve with

[0021] "push" designed operating device in the positions

[0022] - de-energized with the possibility of a fluid connection from radial fluid connection to axial fluid connection (Figure 1),

[0023] - energized in the closed state (Figure 2),

[0024] - de-energized or energized with actuated check valve function from axial fluid connection to radial fluid connection (Figure 3 or 4).

[0025] The valve shown in longitudinal section in Figure 1 as an exemplary embodiment forms a seat valve, with a valve housing 10 that has two fluid connections 1, 2 for conducting fluid. While the fluid connection 1 engages axially at the front in the free end of the valve housing 10, the fluid connection 2 is formed as a radial fluid connection from several bores, for example four bores, which are grouped diametrically opposite one another around the longitudinal or actuating axis of the valve and which penetrate the valve housing 10 and are arranged radially. In this respect, the fluid connection 2 opens radially inwards in the direction of a peripheral wall 13 of a valve or main piston 14. The valve housing 10 and thus the valve as a whole can be accommodated in the usual way in a valve block (not shown in detail) by means of appropriate sealing and guiding systems.In particular, the fluid connections 1, 2, which are connected to fluid guides in the valve block, are separated from each other in a fluid-tight manner by the lower sealing and guide system as viewed in the direction of Figure 1. The fluid is preferably a hydraulic medium, such as hydraulic oil; however, other fluids can also be controlled using the valve shown.

[0026] The valve as a whole has an actuating device, designated 12, for actuating the valve piston 14 or main piston, which is guided longitudinally in the valve housing 10. The actuating device 12, which is also technically referred to as an actuating magnet system, typically has a coil winding 16, which can be energized by means of a plug part 18 arranged on the head side. The plug part 18 is to be connected to a suitable power source with a suitable switch or control arrangement. The coil winding 16 is accommodated in a coil receptacle 20, which is preferably made of an electrically insulating plastic material. The coil winding 16, together with the associated coil receptacle 20, typically comprises a pole tube 22 with a magnetic separation 24 introduced on the outer circumference.As viewed in the direction of Figure 1, the pole tube 22 is integrally closed at its upper end by a base part 26 as part of the pole tube 22. On its lower, free end face, the pole tube 22 partially encompasses a pole core 28, with a seal being provided between the pole core 28 and the pole tube 22.

[0027] The pole core 28 is provided on its underside with a cylindrical recess 30 into which an upper end of the valve housing 10 engages. A seal is introduced between the valve housing 10 and the pole core 28 in the region of the recess 30. The pole tube 22 is firmly connected to the pole core 28 in the region of its free end face by means of a flanged connection 32. Furthermore, a magnet armature 34 is guided longitudinally in the pole tube 22 and is in its uppermost, unactuated position as viewed in the direction of Figure 1. To avoid hindrances during operation, the magnet armature 34 is completely penetrated by a through-bore 36 which opens into the open at the free end faces of the magnet armature 34. In its upper stop position shown in Figure 1, one free end face of the magnet armature 34 is in contact with the bottom part 26 of the pole tube 22.

[0028] The actuating device 12 is enclosed on the outside by a hollow-cylindrical receiving body 38 in the form of a housing shell, preferably made of metal material, which in turn is secured to the pole core 28 on its lower free end face via a further flanged connection 40 on an annular outer circumferential groove along the outside of the pole core 28. Any remaining free space between the receiving body 38 and the actuating device 12 is filled with a potting compound 42, which is sealed at its upper exit area from the receiving body 38 in the direction of the plug part 18 by a sealing connection with respect to the inside of the receiving body 38.

[0029] A rod-like valve control 44 engages the magnet armature 34 in the form of an actuating rod, which engages at its one free upper end region in a coaxial direction to the magnet armature 34 into a continuous receiving opening 46 in the magnet armature 34 and is thus firmly connected to it. In the unactuated state, the lower free end face of the magnet armature 34 has a predeterminable axial distance from the adjacent upper side of the pole core 28 in the form of an annular space 48.If, as already indicated, the coil winding 16 is energized via the associated plug part 18, the magnet armature 34 moves from its unactuated upper end position to its lower functional position, which actuates the valve, as viewed in the direction of Figure 1. It thus exerts a pressing magnetic or actuating force on the downstream components via the rod-like valve control 44 or the actuating rod, respectively, which will be explained in more detail below. In particular, to transmit the pressing movement, the actuating rod is guided longitudinally in a cylindrical hollow recess 50 in the stationary pole core 28. Actuating magnet systems 12 that, as in the present case, exert a pressing force via their magnet armature 44, are referred to as "pressing."

[0030] Furthermore, the valve has a check valve for the check valve function, designated as a whole by 52, which will be explained in more detail below. However, to implement a so-called orifice function, an extension 54 is provided on the free end face of the valve piston 14 in the manner of an extension, which engages in the valve housing 10 with the axial fluid connection 1 in a position that prevents the fluid connection 56 between the fluid connections 1, 2. When the extension 54 is fully engaged in the annular housing parts of the valve housing 10 which delimit the axial fluid connection 1, as shown in Figures 1 and 2, a closed seat valve 58 is formed between adjacent parts of the valve housing 10 and the valve piston 14, wherein the seat valve 58 initially throttles the fluid flow between the two fluid connections 1, 2 upon release of the fluid connection 56.Furthermore, when the seat valve 58 is closed, the check valve function is realized using the check valve 52 formed in this way, in which a fluid connection 56 from the axial fluid connection 1 to the radial fluid connection 2 is ultimately released as soon as the fluid pressure at the axial fluid connection 1 is greater than the closing pressure of the valve. While in the de-energized state of the actuating device 12 according to Figure 1, the seat valve 58 is open and the extension 54 visibly comes out of engagement with the valve housing parts of the fluid connection 1, Figure 2 shows the energized state of the valve according to Figure 1, in which the magnet armature 34 is actuated accordingly and moved downwards, actively pressing the valve piston 14 into its seat, i.e. creating a closed state of the seat valve 58, in which the two fluid connections 1, 2 are fluid-tightly separated from one another.In this respect, it follows from the energized, closed valve state according to Figure 2 that the downwardly directed extension 54 formed from a hollow cylindrical wall section 59 (Figure 3) is fully retracted into the hollow cylindrical recess 60 in the valve housing 10 with the axial fluid connection 1 when the seat valve 58 is closed. In this respect, the outer circumference of the wall section 59 then moves in both actuation directions of the valve, forming a radial gap, preferably forming a circumferential annular gap 61, along the circular cylindrical inner wall of the recess 60, seen in cross-section, until it comes out of engagement with the recess 60 when the valve is in the open state. The part on the valve piston 10 which forms the valve seat of the seat valve 58 consists of an inclined annular surface 62 which tapers into a cone in the direction of the axial fluid connection 1.Furthermore, the seat valve 58 on the side of the valve housing 10 at the transition point to the radial fluid connection 2 is formed, on the one hand, from a circumferential inclined surface 64, against which, on the other hand, the conical annular surface 62 of the valve piston 14 can run, in order to thus establish the fluid-tight connection between the connections 1, 2. The corresponding annular surface 62 of the valve piston 14 directly adjoins the extension 54 in the direction of the actuating device 12.Furthermore, the aforementioned conical annular surface 62 is adjoined in the direction of the actuating device 12 by a further annular surface 66, which is preferably circumferentially interrupted for a fluid passage in the direction of the fluid connection 2, projects outwardly transversely to the actuating direction on the valve piston 14, and is guided so as to be at least partially movable along an inner side 68 of the valve housing 10 in this area, at least when the check valve function is triggered (Figures 3 and 4), wherein the respective inner side 68 at least partially encloses the valve piston 14 in a rotationally symmetrical and coaxial manner. The further annular surface 66 is in any case larger in terms of its outer diameter than the components of the seat valve 58 and larger than the outer diameter of the extension 54.

[0031] As can further be seen from the figures, the valve piston 14 is centrally penetrated by a fluid channel 70, in which a valve or control cone 72 is guided so as to be at least partially longitudinally movable, with its cone tip at its lower end, and controls an orifice 74 in the fluid channel 70. In the aforementioned fluid channel 70, between the orifice 74 for the valve cone 72 and the hollow cylindrical wall section 59 of the extension 54, a closing part 76, in particular in the form of a closing ball, is received in a receiving space 78 in the valve piston 10, wherein the receiving space 78 is closed off in the direction of the axial fluid connection 1 by a fluid-permeable plate 80, such as a sieve plate, in order to prevent the closing part 76 from accidentally falling out of the valve.

[0032] A radial orifice 82 or throttle is incorporated in the valve piston 14 in the usual manner, which, at least when the seat valve 58 is closed, exclusively establishes a fluid-carrying connection between the radial fluid connection 2 in the valve body 10 and a valve or receiving chamber 84 in the valve piston 14 with the valve cone 72 accommodated therein. The valve cone 72 in the valve chamber 84 is part of a valve pilot control of the valve.

[0033] As can be further seen from the figures, the valve piston 14 is guided along its upper outer circumference along circumferential guide and lubrication grooves 86 along the cylindrical inner side 68 of the valve housing 10. Between the area of ​​the valve piston 14 with the guide grooves 86 and the further projecting annular surface 66 there is arranged an annular groove 88 (Figure 4), the axial length of which is in any case dimensioned such that in the closed state of the valve, for example as shown in Figure 2, the radial fluid connection 2 is in fluid-conducting connection with the valve chamber 84, namely via the radially introduced orifice 82. In the thus closed position of the valve, the further annular surface 66 opens out approximately centrally to the central bore axis of the bores of the radial fluid connection 2 and opens up a fluid path starting from the fluid connection 2 via the annular groove 88 in the direction of the orifice 82.In this respect, the annular surface 66 forms the pressure-effective rear side of a transversely extending shoulder between the conical annular surface 62 and the circumferential annular groove 88 in the valve piston 14.

[0034] Preferably, the valve cone 72 is part of a rod-like valve control 44 in the form of an actuating rod, which is divided into two parts according to the embodiment shown in Figures 1 to 4. In this embodiment, the two parts 90, 92 of the rod-like valve control 44 are separated from each other by a decoupling device 94. The decoupling device 94 has a hollow-cylindrical receiving bushing 96 with transverse bores 98 formed in its upper edge region. A first compression spring, designed as the main spring 100 and forming one energy storage device, surrounds the receiving bushing 96 from the outside, with the main spring 100 being supported with one free spring end on an inwardly projecting shoulder 102 of the valve housing 10, and with its other free spring end being in contact with a projecting flange 104 of the receiving bushing 96.Furthermore, the receiving bushing 96 is closed off in the direction of the other part 92 of the actuating rod by a cover part 106, which is in permanent contact with the other part 92 in every travel position of the magnet armature 34. Between the cover part 106 and the one part 90 of the actuating rod 44, which engages in the receiving bushing 96 via an extension 108, there is arranged a further energy storage device in the form of an additional spring 110, which is arranged coaxially to the main spring 100 and has a lower spring stiffness than the main spring 100. In this way, the decoupling device 94 is a type of spring assembly arrangement with the proviso that the main spring 100 primarily serves to adjust the actuating force for the magnet armature 34 and ensures its reset in the de-energized state, whereas the additional or auxiliary spring 110 sets an adjustable opening pressure at which the check valve function, which will be shown later, begins.

[0035] Furthermore, one part 90 of the actuating rod between the valve cone 72 and the flange-like widening 108 is at least partially provided with circumferential, channel-like recesses 112, so that a permanent fluid guide is produced between the valve chamber 84 and a rear region 114 of the valve piston 14, which extends as an annular space between the upper free end face of the valve piston 14 and the opposite adjacent side of the receiving bushing 96.For further fluid flow, the outer circumference of the receiving bushing 96 is guided at a radial distance within the inner side 68 of the valve housing 10, so that fluid can reach the inner side of the receiving bushing 96 via the aforementioned annular gap and the spring chamber with the main spring 100 as well as the aforementioned transverse bores 98, and thus to a spring chamber with the additional spring 110, even though the relevant bushing 96 is closed on one side by the cover part 106 and a continuous receiving shoulder on the opposite side of the bushing 96 is essentially closed by one part 90 of the actuating rod 44. In any case, the relevant fluid guides ensure unhindered operation of the valve using the springs 100, 110.

[0036] The valve solution according to the invention is explained in more detail below based on its function. Based on the prior art, the valve according to the invention is based on conventional pilot-operated 2 / 2-way seat valves. Starting with an electrically actuated valve, the valve is closed in the energized state as shown in Figure 2. The load pressure should now be present at the radial connection 2 and continues via the inlet orifice bore or orifice 82 in the valve piston 14 to the rear area 114 of the valve piston 14. Since the pressure-effective area of ​​the rear area 114 is larger than the pressure-effective frontal area of ​​the valve piston 14 in the area of ​​the axial fluid connection 1, a closing force acts on the valve or main piston 14.If the actuation or energization of the pushing actuating magnet system 12 is canceled, the main spring 100, via the decoupling device 94, displaces the magnet armature 34 away from the pole core 28 as shown in Figure 1, taking the rod-like valve control 44 with it, namely both parts 90, 92 together, which in turn now open the pilot control orifice in the valve piston 14 by the valve cone 72 lifting off the orifice opening 74 in the valve piston 14. In this way, a pilot control volume flow is established via the orifice 74, the pressure drop of which leads to an opening force on the valve piston 14, whereby the latter follows the movement of the rod-like valve control 44.

[0037] During the opening movement starting from the representation in Figure 1, the seat valve 58 is opened and the extension 54 of the valve piston 14 visibly comes out of engagement with the hollow cylindrical recess 60 in the area of ​​the axial fluid connection 1, with the result that, in the de-energized state of the valve, fluid flows from the radial fluid connection 2 to the axial fluid connection 1 in a throttled manner within the scope of the orifice function. Since the possible stroke of the main spring 100 is small, the valve piston only carries out a type of partial opening for a fluid connection 56 between the radial fluid connection 2 and the axial fluid connection 1, with an improved orifice function in this respect.

[0038] When the valve is electrically actuated as shown in Figure 2, the magnet armature 34 is moved back toward the pole core 28, thereby compressing the main spring 100. The additional or auxiliary spring 110, which serves as a check valve spring and is supported with one free end on the underside of the cover part 106 of the decoupling device 94 and with its other free end on the flange-like widened portion 108 of one part 90 of the rod-like valve control 44 with the connected valve cone 72, serves to displace the valve cone 72 such that the pilot bore or orifice opening 74 in the valve piston 14 is closed. In this respect, the additional or auxiliary spring 110 serves as a check valve spring at the same time for decoupling within the framework of the decoupling device 94, so that the magnetic force does not act directly on the valve piston 14, but only indirectly on the main spring 100.Without such decoupling by means of the decoupling device 94, the check valve function required in the energized state would only respond at a significantly increased pressure level, which is not desired.

[0039] If, according to the illustrations in Figures 3 and 4, both in the de-energized and in the energized state of the valve according to Figures 1 and 2, a higher pressure is present at the axial fluid connection 1 than at the radial fluid connection 22, this pressure acts on the front side of the valve piston 14 in the area of ​​the axial fluid connection 1, opens the valve and releases the fluid connection 56 between the axial fluid connection 1 and the radial fluid connection 2, provided that the respective inherent closing force of the valve is overcome.The fluid pressure present at the axial fluid connection 1 passes through the inside of the hollow cylindrical wall section 59 of the extension 54 and through the fluid-permeable end part, usually in the form of a sieve plate 80, to the side with the closing part 76 and presses the closing part 76 into its associated valve seat in the valve piston 14, so that a fluid connection via the hollow cylindrical wall section 59 in the direction of the receiving space 78 is effectively prevented. Thus, within the scope of the check valve function, no pressure is present at the orifice 74 via the spherical closing part 76, so that in this respect, no force can be exerted on the pilot control in this way. In the case of the check valve function according to Figures 3 and 4, the additional or auxiliary spring 110 serving as a check valve spring is compressed, as shown, the spring force of which defines the possible opening stroke of the check valve function.This opening stroke is designed to be larger than the stroke of the solenoid-operated valve opening according to Figures 1 and 2, so that flow with low pressure loss is possible within the scope of the check valve function.

[0040] With the illustrated embodiment of a valve solution according to Figures 1 to 4, the volume flow can be directed via the check valve 52 in a flow direction from the axial fluid connection 1 to the radial fluid connection 2 at a very low opening pressure and with low flow losses. In the opposite direction, i.e. from the radial fluid connection 2 to the axial fluid connection 1, the volume flow is released (NO - Normally Open) or blocked depending on the application of an electrical current to the seat-tight 2 / 2-way valve. The volume flow in the main direction is influenced by the integrated orifice using the axial extension 54 on the valve piston 14 in conjunction with the hollow cylindrical recess 60 in the valve housing 10 in the area of ​​the axial fluid connection 1. This has no equivalent in the prior art.

Claims

Patent claims 1. A valve, in particular a seat valve, comprising a valve housing (10) having two fluid connections (1, 2) for conducting fluid, and comprising an actuating device (12) for actuating a valve piston (14) guided longitudinally in the valve housing (10), comprising a first fluid connection (1) opening axially toward a free end face of the valve piston (14), and a second fluid connection (2) opening radially toward a circumferential wall (13) of the valve piston (14), as well as a check valve function integrated in the valve, characterized in that an extension (54) is provided on the free end face of the valve piston (14) to implement a diaphragm function, which extension engages the valve housing (10) with the axial fluid connection (1) in a position preventing the fluid connection (56) between the fluid connections (1, 2),that upon complete engagement between parts of the valve housing (10) and the valve piston (14), a closed seat valve (58) is formed, that upon release of the fluid connection (56), the fluid flow between the two fluid connections (1, 2) is throttled, and that at least when the seat valve (58) is closed, the check valve function is realized, in which a fluid connection (56) from the axial (1) to the radial fluid connection (2) is released.

2. Valve according to claim 1, characterized in that a valve pilot control with a valve or control part, in particular a control cone (72), is present, which controls an orifice (74) in a fluid channel (70) of the valve piston (14) and which is part of a valve control (44) which consists of at least two adjacent parts (90, 92), between which a decoupling device (94) is arranged.

3. Valve according to claim 1 or 2, characterized in that the decoupling device (94) has a spring arrangement with a main spring (100) which serves to adjust the actuating force of the actuating device (12) and with an additional or auxiliary spring (110) which serves to adjust the opening pressure for the check valve function.

4. Valve according to one of the preceding claims, characterized in that the decoupling device (94) has a hollow cylinder-like receiving bushing (96) which has at least one transverse bore (98) and in that the main spring (100) comprising the receiving bushing (96) is supported with one of its free ends on the valve housing (10) and with its other free end on the receiving bushing (96).

5. Valve according to one of the preceding claims, characterized in that the additional or auxiliary spring (110) is supported with its one free end on one part (92) and with its other free end on the other part (90) of the valve control (44) directly or indirectly via intermediate parts (106, 108).

6. Valve according to one of the preceding claims, characterized in that the additional or auxiliary spring (110) is designed with a lower spring stiffness than the main spring (100) and is accommodated coaxially therewith within the receiving bushing (96).

7. Valve according to one of the preceding claims, characterized in that the extension (54) is formed from a hollow cylindrical wall section (59) which, when the seat valve (58) is closed, engages in a hollow cylindrical recess (60) in the valve housing (10) with the axial fluid connection (1) in a gap-forming manner.

8. Valve according to one of the preceding claims, characterized in that the part on the valve piston (14) which forms the valve seat of the seat valve (58) is formed from an annular surface (62) which tapers into a cone in the direction of the axial fluid connection (1) and which adjoins the extension (54) in the direction of the actuating device (12).

9. Valve according to one of the preceding claims, characterized in that the conical annular surface (62) is adjoined in the direction of the actuating device (12) by a further annular surface (66), which is designed in an interrupted manner and projects transversely to the actuating direction (12) on the valve piston (14), at least when the non-return function is triggered, is guided at least partially displaceably along an inner side (68) of the valve housing (10), which at least partially surrounds the valve piston (14) in contact.

10. Valve according to one of the preceding claims, characterized in that the valve piston (14) is penetrated by a fluid channel (70) in which the valve cone (72) of the valve pilot control is guided at least partially longitudinally and controls the orifice opening (74) in the fluid channel (70) with its cone tip.

11. Valve according to one of the preceding claims, characterized in that a closing part (76), in particular in the form of a closing ball, is accommodated in a receiving space (78) in the valve piston (14) in the fluid channel (70) between the aperture (74) for the valve cone (72) and the hollow cylindrical wall section (59) of the extension (54).

12. Valve according to one of the preceding claims, characterized in that a radial aperture (82) is introduced into the valve piston (14), which at least when the seat valve (58) is closed, establishes a fluid-carrying connection between the radial fluid connection (2) in the valve housing (10) and the receiving space (84) in the valve piston (14) with the valve cone (72) received therein.

13. Valve according to one of the preceding claims, characterized in that the valve cone (72) is a part of the rod-like valve control (44) which is designed in two pieces or interrupted and at least partially engages with its one free end opposite the valve cone (72) in a magnet armature (34) of the energizable actuating device (12) and can be controlled in a longitudinally movable manner by means of the same.

14. Valve according to one of the preceding claims, characterized in that by means of at least one energy storage device, preferably in the form of the main or compression spring (100), a restoring force can be exerted on a magnet armature (34) which can be actuated by means of the actuating system (12).

15. Method for operating a valve according to one of the preceding claims, characterized in that in the case of a pushing actuating device (12), a fluid connection from the radial fluid connection (2) to the axial fluid connection (1) is released when de-energized, when energized the seat valve (58) is closed and the fluid connection between the fluid connections (1, 2) is blocked, and both when de-energized and energized a check valve function from the axial (1) to the radial (2) fluid connection is released.

Images