Solenoid valve for controlling fluid flows

Abstract

Solenoid valve for controlling fluid flows (S), comprising a valve housing (2), at least one valve inlet (14) and at least one valve outlet (15) which are flow-connected to each other via a valve seat (12), and a plunger (3) movable along an actuating direction (R), which is adjustable by energizing a solenoid coil (4) between an opening position releasing the valve seat (12) and a closing position closing the valve seat (12), wherein the plunger (3) is connected at its end facing the valve seat (12) to a diaphragm (6) fixed relative to the valve housing (2), characterized in that the diaphragm (6) has a transverse deformation area (9) for compensating actuating movements of the plunger (3).

Description

[0001] The present invention relates to a solenoid valve for controlling fluid flows, comprising a valve housing, at least one valve inlet and at least one valve outlet, which are fluidly connected to one another via a valve seat, and a plunger movable along an actuating direction, which can be adjusted by energizing a solenoid coil between an open position releasing the valve seat and a closed position closing the valve seat, wherein the plunger is connected at its end facing the valve seat to a diaphragm fixed relative to the valve housing. The invention further relates to a solenoid valve arrangement comprising a main valve and a pilot valve for controlling the main valve.

[0002] Such solenoid valves are used in fluid systems in a wide variety of technical fields to switch fluid flows. For example, such solenoid valves can be used in the water supply systems of beverage vending machines, such as espresso machines, to selectively block or release a water flow.

[0003] In a valve housing, which often at least partially encloses at least some of the components of the solenoid valve, a valve seat is usually provided in the flow path between a valve inlet and a valve outlet in such solenoid valves. The valve seat usually interacts with a tappet, which is designed to be movable along an actuating direction. In an open position, the tappet is arranged such that the valve seat is exposed and the fluid can flow from the valve inlet towards the valve outlet. In a closed position, however, the tappet is arranged such that the valve seat is closed and the fluid cannot flow from the valve inlet to the valve outlet.

[0004] In conventional solenoid valves, the plunger, which in practice is sometimes also referred to as the armature or core, is arranged at least partially within the effective range of a solenoid coil. By energizing the solenoid coil, the plunger can generally be adjusted along the actuating direction between the closed position and the open position. Solenoid valves are known in the prior art, both in which the plunger is in the open position when the solenoid coil is de-energized and in which the plunger is in the closed position when the solenoid coil is de-energized. The solenoid coil allows contactless actuation of the solenoid valve.

[0005] Such solenoid valves often also feature a diaphragm, which, for example, allows for the separation of the fluid-flowing area from the non-fluid-flowing area of ​​the solenoid valve. For example, EP 1 596 109 B1 discloses a solenoid valve in which the plunger is connected to a diaphragm fixed relative to the valve housing, which separates a fluid-flowing valve chamber from the solenoid coil.

[0006] Such solenoid valves have proven themselves to be highly effective at switching fluid flows. However, under adverse conditions, such solenoid valves can fail. Since the diaphragm is fixed to the valve body on the one hand, but is also connected to the movable stem on the other, the diaphragm is either stretched or compressed depending on the actuating movements between the open and closed positions of the stem. These alternating mechanical loads can, under unfavorable conditions, lead to premature failure of the diaphragm during operation of the solenoid valve, and thus to failure of the solenoid valve.

[0007] Against this background, the invention has the object of providing a solenoid valve of the type mentioned at the outset, which is characterized by improved reliability.

[0008] This object is achieved in a solenoid valve of the type mentioned above by the features of claim 1. Advantageous further developments are specified in the dependent subclaims.

[0009] Because the diaphragm has a transverse deformation area to compensate for the actuating movements of the plunger, its mechanical stress during operation of the solenoid valve can be reduced. The transverse deformation area allows the diaphragm to deform transversely to the actuating direction of the plunger. This prevents excessive stretching or compression in the actuating direction, which under unfavorable conditions can lead to premature failure of the diaphragm material.

[0010] In this context, it is proposed that at least two folds be arranged in the transverse deformation region. Such folds allow for the compensation of the adjusting movements of the tappet in a kinematically and mechanically advantageous manner. The folds are wave-like bulges in the membrane. They can also be referred to as kinks or bends.

[0011] In this context, it has proven advantageous if the at least two folds are arranged one behind the other in the direction of travel. This results in a space-saving design that can also enable reliable compensation of the adjusting movements of the plunger. The at least two folds can have the same or different dimensions.

[0012] Furthermore, it is preferred if the at least two folds are elastically deformable, in particular accordion-like, as a result of the actuating movements of the plunger. Such accordion-like deformability of the at least two folds allows compensation of the actuating movements of the plunger in a way that protects the membrane material and saves installation space. In particular, the at least two folds can be designed to be foldable and / or unfoldable along the actuating direction of the plunger. The at least two folds are preferably unfolded when the plunger is moved from the open position to the closed position and folded when the plunger is moved from the closed position to the open position. However, a reverse design can also prove advantageous for certain applications.

[0013] In this context, a structurally advantageous development of the invention provides that the at least two folds are designed and arranged such that their vertices are movable transversely to the adjustment direction. The vertices can be movable transversely to the adjustment direction, in particular when the at least two folds are unfolded and / or folded. The vertices preferably move radially outward when the folds are folded closed and radially inward when the folds are unfolded.

[0014] In a further, structurally advantageous embodiment, the at least two folds extend circumferentially around the plunger. Such a design can prove particularly space-saving. Furthermore, a uniform compensation of the plunger's actuating movements can be achieved. Furthermore, any angular offset of the plunger relative to the actuating direction can be compensated for by such a membrane design. The vertices of the cross-sectional contours of the folds form a vertex line circumferentially encircling the plunger.

[0015] In a preferred development of the invention, it is proposed that the diaphragm be designed and arranged such that it has the same stress state along a travel path extending between the open position and the closed position of the tappet. In this respect, the same stress state exists if the stress acting on the diaphragm does not change sign along the travel path. Thus, there is always either a tensile or a compressive stress state, but not an alternating stress state. The magnitudes of the acting stresses can, however, differ along the travel path. As a result, changing stress states of the diaphragm can be avoided, which can increase the service life of the diaphragm.

[0016] In this context, it has proven advantageous for the diaphragm to exhibit a tensile stress state along the travel path. If the diaphragm is arranged and designed in such a way that it is constantly subjected to tensile stress along the travel path, this generally results in advantages for the diaphragm's durability. The tensile stress state can preferably be achieved by connecting the diaphragm to the valve housing and the valve stem under a certain preload. Alternatively, the diaphragm can also exhibit a compressive stress state along the entire travel path.

[0017] The diaphragm is preferably designed and arranged in such a way that it applies a restoring force to the plunger. This results in advantages for the switching behavior of the solenoid valve. In particular, the diaphragm can be designed and arranged in such a way that it supports the opening. This means that the restoring force acts in the direction of the open position of the plunger. As a result, the opening process, i.e. the release of the valve seat, can be supported by the diaphragm. Such an opening-supporting effect can be particularly advantageous when ambient pressure acts on the plunger, which preloads it into the closed position. The ambient pressure can be increased in particular when the diaphragm is arranged in a valve chamber through which fluid flows. Alternatively, however, the diaphragm can also be designed and arranged to support the closing, with the restoring force acting in the direction of the closed position of the plunger.

[0018] In a preferred design embodiment, the diaphragm is rotationally symmetrical and has a central section radially inward for closing and releasing the valve seat, a sealing section radially outward for sealing the valve housing, and a support section between them for supporting the valve housing. This results in a diaphragm structure that not only allows for reliable closure of the valve seat but also ensures sealing of the valve housing. Furthermore, a rotationally symmetric diaphragm structure offers advantages for its manufacturing.

[0019] In this context, it is also structurally advantageous if the transverse deformation region is arranged in the central section. In this way, the transverse deformation region can preferably be arranged near the plunger, whose adjusting movements are to be compensated via the transverse deformation region.

[0020] Another preferred design provides for the diaphragm to be connected to the plunger in the central section. With such a configuration, the plunger's mobility along the actuating direction can be ensured, allowing it to reliably execute the required actuating movements.

[0021] It can further be provided that the diaphragm is positively connected to the tappet via a circumferential first connecting undercut formed on the tappet and a first connecting projection formed on the diaphragm corresponding to the first connecting undercut. This results in a secure positive connection between diaphragm and tappet that does not come loose even after numerous adjusting movements. Furthermore, such a design can prove to be easy to assemble, as it can allow assembly personnel to connect the tappet to the diaphragm in a time-saving manner. However, depending on the application, it can also be advantageous if the first connecting projection is formed on the tappet and the first connecting undercut is formed on the diaphragm. Furthermore, the connecting undercut and / or the connecting projection do not have to be circumferential, but can also be interrupted.Furthermore, another type of connection, for example another form-fitting connection, a material connection or fastening by means of a separate fastening means, may be preferred in individual cases.

[0022] A further advantageous development of the invention provides that the diaphragm is positively connected to the valve housing in its sealing section via a second connecting undercut formed on the valve housing. This also results in a simple and time-saving installation option for the diaphragm. Furthermore, the attachment between the diaphragm and the valve housing can also be achieved in other ways, such as by means of a material bond or a separate fastening device.

[0023] Furthermore, it is proposed that the diaphragm have an annular sealing element in its sealing section. The annular sealing element can provide a circumferential seal around the valve housing. Preferably, the sealing element can be provided integrally with the diaphragm, resulting in a captive, easy-to-assemble arrangement.

[0024] Another easy-to-install design is characterized by the fact that the diaphragm is detachably arranged between an upper and lower part of the valve housing. This allows for user-friendly replacement of the diaphragm, if necessary, simply by separating the upper part from the lower part of the valve housing. Furthermore, the diaphragm can be easily positioned between the upper and lower parts of the valve housing. Furthermore, the arrangement between the upper and lower parts of the valve housing allows for precise fastening of the diaphragm.

[0025] It has also proven advantageous if the diaphragm separates the valve housing into a dry zone and a wet zone, with the solenoid coil being arranged in the dry zone. The diaphragm has a dual function in this design. On the one hand, it supports the control processes of the fluid flows, as its central region can interact with the valve seat. On the other hand, it enables the valve housing to be separated into a wet zone through which fluid flows and a dry zone through which no fluid flows. As a rule, the wet zone through which fluid flows is arranged below the diaphragm in the actuating direction of the tappet, and the dry zone through which no fluid flows is arranged above the diaphragm. Thanks to the separation of the dry zone from the wet zone, the solenoid coil can be operated fail-safe and without the risk of damage from the fluid.Furthermore, the separation of dry and wet areas can also prevent contamination of the fluid flowing through the wet area from outside, which can result in hygiene benefits.

[0026] A further, advantageous design provides for the diaphragm to have a support shoulder, which is arranged across the entire section, both in the support section and in the central section. The support shoulder advantageously supports the diaphragm against the tappet. Furthermore, the support shoulder can facilitate user-friendly assembly, as it can serve as a kind of positioning aid.

[0027] In this context, it can be advantageous if the support shoulder forms a stop for the plunger in its closed position. This allows the plunger's travel to be limited in a reliable and material-friendly manner. The shape and arrangement of the support shoulder also allows the maximum travel of the plunger to be adjusted, allowing different maximum travels to be set using appropriately differently designed diaphragms.

[0028] In this context, it is proposed that the support shoulder be designed and arranged in such a way that, in the closed position of the tappet, it interacts with a shoulder of the tappet. This results in an advantageous flat stop pairing that limits the closed position of the tappet. Misalignment of the tappet and / or damage to the solenoid valve, in particular the valve seat, due to excessive actuating movement of the tappet can be avoided.

[0029] An advantageous development of the invention provides that the diaphragm has a clamping area clamped relative to the valve housing and an adjustment area movable with the tappet, which are arranged offset from one another in the adjustment direction. A diaphragm designed in this way can be clamped securely and precisely in position relative to the valve housing via its clamping area. At the same time, the adjustment range allows the diaphragm to flexibly follow the adjustment movements of the tappet. This results in an arrangement in which the diaphragm is rigidly and immovably fixed relative to the valve housing in its clamping area and at the same time is arranged and designed to be movable with the tappet relative to the valve housing in its adjustment area. The clamping area and the adjustment area are preferably located at opposite ends of the diaphragm in the adjustment direction.Furthermore, it may be advantageous if the clamping area is arranged at an upper end of the membrane facing the solenoid coil and the adjusting area is arranged at a lower end of the membrane associated with the valve seat.

[0030] In this context, it can be advantageous if the transverse deformation region is arranged between the clamping region and the adjustment region. Such an arrangement of the transverse deformation region ensures compensation of the adjustment movements between the movable adjustment region and the rigid clamping region. Failure of the membrane material due to the relative movements of the adjustment region relative to the clamping region can be prevented by the transverse deformation region.

[0031] It is further proposed that the transverse deformation region and the clamping region overlap axially in the actuating direction. This allows for the implementation of a diaphragm that is comparatively short and compact axially, which can also be used in solenoid valves in confined spaces.

[0032] In this context, it can be advantageous from a design perspective if the diaphragm has a radially circumferential, substantially V-shaped recess in its clamping area. This is a circumferential depression with a substantially V-shaped cross-sectional contour. Such a substantially V-shaped recess can benefit a material-saving design. The legs of the substantially V-shaped recess can be arranged asymmetrically or symmetrically to the vertical. In particular, with an asymmetrical arrangement, one of the legs of the substantially V-shaped recess can extend parallel to the tappet.

[0033] In a preferred design embodiment, the substantially V-shaped recess is open toward the valve seat. The tip of the substantially V-shaped recess points toward the solenoid coil in such a configuration. The substantially V-shaped recess also allows the volume of a chamber of the solenoid valve, which is delimited by the diaphragm, to be advantageously increased.

[0034] In this context, it is further proposed that the transverse deformation region extend at least partially into the essentially V-shaped recess. Such a configuration promotes a compact, axially short design of the diaphragm. This easily enables an axial overlap between the transverse deformation region and the clamping region. In this context, the axial overlap refers to an overlap in the actuating direction of the tappet.

[0035] It is further proposed as structurally advantageous that at least one of the at least two folds is arranged within the substantially V-shaped recess. The arrangement within the substantially V-shaped recess allows the at least one fold to unfold and close without hindrance. Furthermore, the apex of the fold can move freely transversely to the adjustment direction. In this context, however, it can also be advantageous if several of the at least two folds or all of the at least two folds are arranged within the substantially V-shaped recess. In this way, a greater axial overlap can be achieved between the clamping region and the transverse deformation region. The greater this axial overlap, the shorter the membrane can be axially and thus the more compact it can be.

[0036] A further advantageous embodiment of the invention provides that the diaphragm has an elastically stretchable region in which the diaphragm is designed to compensate for actuating movements of the plunger. Thanks to the elastic region, in which the diaphragm can be reversibly deformed, damage to the diaphragm resulting from the actuating movements of the plunger can be avoided, particularly when the plunger moves from the closed position to the open position. The elastic region can act in particular in addition to the transverse deformation region. The elastic region is preferably designed to elastically absorb tensile stresses.

[0037] In this context, it is structurally advantageous if the stretching region is arranged in the clamping region. With such an arrangement, damage to the membrane, particularly in the clamping region, caused by elastic deformations in the stretching region can be avoided. Furthermore, it can be advantageous if the stretching region has an axial overlap with the transverse deformation region. Furthermore, it is proposed that the stretching region be arranged radially outward on the membrane compared to the transverse deformation region.

[0038] From an ecological perspective, it can be advantageous if the membrane is made of a non-fluorinated material, especially one that is free of per- and polyfluorinated alkyl compounds. Such a PFAS-free membrane can reduce environmental impact. Furthermore, impurities or contamination of the fluid can be avoided. This also allows compliance with legal requirements for the membrane material. The membrane can preferably be made of rubber-elastic rubber. Examples of suitable materials for the membrane include ethylene-propylene-diene rubber, fluororubber, perfluororubber, nitrile rubber, tetrafluoroethylene / propylene rubber, silicone rubber, thermoplastic elastomers, and many other materials. The membrane material is preferably selected depending on the specific application, such as the fluid to be controlled with the solenoid valve, and the operating conditions.

[0039] From a manufacturing perspective, it may be preferable for the membrane to be manufactured by vulcanization or an injection molding process. This offers particular advantages in terms of rapid and cost-effective membrane production. Furthermore, the membrane's properties can be adapted to the specific application.

[0040] A further, structurally preferred embodiment of the solenoid valve provides that the valve seat is arranged in one piece on the valve housing. This results in a structurally simple design with an advantageously small number of sealing points. Furthermore, the valve seat is connected to the valve housing in a non-detachable and thus captively manner. In addition, due to the one-piece design, the valve housing and the valve seat can be manufactured in a single work step. In this context, it is particularly advantageous if the valve seat is arranged in one piece on a lower part of the valve housing. Furthermore, the valve inlet and / or the valve outlet are preferably also formed in one piece with the valve housing, in particular with the lower part of the valve housing. With such a design, the valve housing, in particular its lower part, can be manufactured, handled and assembled in a user-friendly manner as a modular unit.

[0041] It is further proposed that the plunger be preloaded in the adjustment direction by a return element. Depending on the arrangement and design of the return element, the plunger can be preloaded either toward its closed position or toward its open position. The return element can ensure reliable maintenance of the respective position. Furthermore, pressure fluctuations acting on the plunger can be compensated for by the return element. Furthermore, the return element can be used to minimize the forces required to execute the adjustment movements, if necessary, by supporting the respective adjustment movement.

[0042] Furthermore, it has proven advantageous if the valve inlet and / or the valve outlet are arranged transversely to the actuating direction of the tappet. This can result in an upright arrangement of the tappet in comparison to the valve inlet and / or the valve outlet, which is characterized by good accessibility of the tappet and the solenoid coil. The actuating direction of the tappet can in particular run transversely to an inflow axis and / or an outflow axis of the valve. Such a design of the solenoid valve can be comparatively easy to integrate into existing fluid systems. Alternatively, the valve inlet and / or the valve outlet can also be arranged in the actuating direction of the tappet, which can result in a horizontal arrangement of the tappet.

[0043] Furthermore, it is proposed that the flow direction of the fluid stream at the valve inlet and the valve outlet be identical. Such a solenoid valve can be particularly easily integrated into an existing fluid system, in particular an existing, straight fluid line. The inflow axis and the outflow axis of the solenoid valve can preferably run parallel or coaxially. Furthermore, it is preferred if the actuating direction of the tappet runs transversely to the inflow axis and / or the outflow axis. To implement such an arrangement, it can be advantageous if the fluid stream is deflected at least once within the valve housing, in particular in the region of the valve seat.

[0044] Alternatively, it may also be advantageous in the respective application if the flow direction of the fluid stream at the valve outlet is changed, in particular rotated, relative to the valve inlet. This allows a redirection of the fluid stream as it flows through the solenoid valve. A redirection of the flow direction by approximately 90 degrees may be preferred. In such a configuration, the inflow axis can extend in the actuating direction of the tappet, and the outflow axis can extend perpendicular to it, or vice versa.

[0045] With regard to easy replacement and / or simple installation of the solenoid valve, it has proven advantageous if the valve inlet and / or the valve outlet are connected to a hose connection means. Using such a hose connection means, an inlet and / or outlet-side hose can be connected to the valve inlet and / or the valve outlet in a user-friendly and time-saving manner. The hose connection means preferably allows a reliable mechanical fastening of the hose, which withstands the prevailing pressures, and at the same time also a fluidic seal. It can be advantageous for a connection that can be established and / or released particularly quickly if the hose connection means is designed as a plug-in connector, in particular as a quick connector.

[0046] Furthermore, to achieve the above object, a solenoid valve arrangement with a main valve and a pilot valve for controlling the main valve is proposed, in which the pilot valve is designed as a solenoid valve. Such a solenoid valve arrangement offers the same advantages as those explained above with regard to the solenoid valve. All of the aforementioned features can also be combined, either alone or in combination with the pilot valve of the solenoid valve arrangement, which is designed as a solenoid valve.

[0047] In this context, it is preferred if the main valve and the pilot valve form a pilot-operated servo solenoid valve. A pilot-operated servo solenoid valve allows fluid flows to be controlled with an advantageously low actuation force and smooth switching behavior.

[0048] Further details and advantages of a solenoid valve according to the invention and a solenoid valve assembly according to the invention are explained below with the aid of the accompanying drawings of exemplary embodiments. These drawings show, partly in section: Fig. 1 is a partially sectioned side view of a solenoid valve with its plunger in the closed position; Fig. 2 is a further, partially sectioned side view of another solenoid valve with its plunger in the closed position; Fig. 3 and Fig. 4 two further, partially sectioned side views of further solenoid valves with their plungers in the closed position; Fig. 5 a partially sectioned partial view of the solenoid valve according to Fig. 1; Fig. 6 a further, partially sectioned partial view of the solenoid valve according to Fig. 1, with its plunger in the open position; Fig. 7 a partially sectioned partial view of the solenoid valve according to Fig. 2; Fig. 8 a further, partially sectioned partial view of the solenoid valve according to Fig. 2, with its plunger in the open position; Fig. 9 a sectional side view of a diaphragm of a solenoid valve.

[0049] The representations according to Fig. 1 to 4 show various embodiments of solenoid valves 1 according to the invention for controlling fluid flows S. The solenoid valves 1 are used, for example, for switching water flows in beverage vending machines, in particular in espresso machines. The solenoid valves 1 are integrated into corresponding fluid systems or fluid control arrangements of the beverage vending machines. However, such solenoid valves 1 can also be used for other applications, even outside the drinking water sector, for switching fluid flows.

[0050] The solenoid valves 1 according to Fig. 1 to 4 all have the same basic structure, but differ in the arrangement and orientation of the respective valve inlets 14 and valve outlets 15 as well as their orientation to the valve seat 12. The different embodiments according to Fig. 1 to 4 will be explained in detail in later paragraphs. However, first, the essential components and parts of the solenoid valves 1 will be explained using the illustration in Fig. 1 will be presented.

[0051] The solenoid valve 1 has a valve housing 2. The valve housing 2 comprises an upper part 2.1 and a lower part 2.2, which are connected to one another. The lower part 2.2 of the valve housing 2 is designed to carry fluid, while the upper part 2.1 of the valve housing 2 does not carry fluid. A valve inlet 14 is provided on the lower part 2.2, through which the fluid to be controlled can flow into the valve housing 2. A valve outlet 15 is provided on the downstream side, through which the fluid can leave the valve housing 2. The valve inlet 14 and the valve outlet 15 are fluidly connected to one another via a valve seat 12.

[0052] As shown in Fig. 1, the valve inlet 14 is adjoined by a flow channel 23, through which the fluid stream S flows along the inflow axis E toward the valve seat 12. The flow channel 23 opens into a flow channel 18 which extends at an angle of approximately 90 degrees thereto and has a smaller diameter. The flow channel 18 extends essentially vertically and has the valve seat 12 at its upper end, which is designed as an annular opening of the flow channel 18.

[0053] A tappet 3 interacts with the valve seat 12. The tappet 3 is an elongated, rod-like element which is arranged to be movable along an actuating direction R. In a closed position of the tappet 3, as for example in Fig. As shown in Figure 1, the valve seat 12 is closed by the tappet 3. The fluid cannot leave the flow channel 18 via the valve seat 12. To seal the valve seat 12, the end of the tappet 3 facing the valve seat 12 is connected to a membrane 6, see Figure 1. Fig. 1. The rotationally symmetrical membrane 6 covers the end face of the tappet 3 facing the valve seat 12 with a sealing surface 25 provided in a radially inner central region 6.1 and ensures a fluid-tight seal of the valve seat 12 in its closed position.

[0054] The plunger 3 is made of a magnetic material and is arranged at least partially in the effective range of a magnetic coil 4, cf. Fig. 1. The magnetic coil 4 encloses an upper area of ​​the plunger 3 in the circumferential direction. By energizing the magnetic coil 4, the plunger 3 can be moved along the actuating direction R. In addition to the closed position, the solenoid valve 1 also has an open position of the plunger 3, which, for example, Fig. 6. In the open position of the tappet 3, the valve seat 12 is released, and the fluid can flow from the flow channel 18 into a chamber 5. The chamber 5 is sealed from the dry area T of the solenoid valve 1 by the diaphragm 6 and is fluidly connected to the outlet-side flow channel 24. In the open position of the tappet 12, the fluid can thus flow from the valve inlet 14 via the valve seat 12 to the valve outlet 15.

[0055] The membrane 6 connected to the tappet 12 is fixed relative to the valve housing 2, cf. Fig. 5. The fixing takes place in a sealing section provided radially on the outside (6.3), see Fig. 9. Since the diaphragm 6 is fixed relative to the valve housing 2 on the one hand, but is also movably connected to the tappet 3 in an adjustment range 6.5, a compensation of the adjustment movements of the tappet 3 is necessary. For this purpose, a transverse deformation area 9 is provided on the diaphragm 6, the structure and function of which are described below with reference to the illustrations in Fig. 5, Fig. 6 and Fig. 9 is explained.

[0056] As shown in Fig. 9, the transverse deformation region 9 is provided in the adjustment direction R between the adjustment region 6.5, which is provided in the region of the end of the tappet 3 facing the valve seat 12, and the clamping region 6.4, which is arranged in the adjustment direction R at the upper end of the diaphragm 6. The adjustment region 6.5 is movable with the tappet 3, whereas the clamping region 6.4 is rigidly clamped relative to the valve housing 2.

[0057] As this is Fig. 9, the membrane 6 is not flat or smooth in the transverse deformation region 9, but has two folds 9.1, 9.2. The folds 9.1, 9.2 are wave-like kinks or radial bulges of the membrane 6, which is thin-walled in this region. The two folds 9.1, 9.2 are arranged one behind the other in the adjustment direction R, with the first fold 9.1 being arranged closer to the adjustment region 6.5 than the second fold 9.2, which in turn is arranged closer to the clamping region 6.4 than the first fold 9.1. The two folds 9.1, 9.2 have approximately the same dimensions and extend in the circumferential direction around the tappet 3.

[0058] Depending on the position of the plunger 3, the folds 9.1, 9.2 are more or less strongly unfolded. As can be seen from the comparison of the Fig. 5 and Fig. 6, the folds 9.1, 9.2 are in the closed position of the plunger 3 (which in Fig. 5) is more unfolded than in the open position of the plunger 3 (which is shown in Fig. 6). In other words, when the tappet 3 is moved from the open to the closed position, the membrane 6 rests against the tappet 3 in the transverse deformation region 9. The vertices of the cross-sectional contours of the folds 9.1, 9.2 move radially outward transversely to the adjustment direction R.

[0059] The adjusting movements of the plunger 3 can be compensated for by the accordion-like, elastic unfolding and closing of the folds 9.1, 9.2 in the transverse deformation region 9. The bulging, elastic, and thus reversible deformation ensures that the stresses occurring in the membrane material as a result of the adjusting movements of the plunger 3 are reduced and do not lead to failure of the material of the membrane 6.

[0060] However, elastic deformation does not only take place in the transverse deformation region 9, but also in a stretching region 22, which is arranged in the clamping region 6.4 of the membrane 6, cf. Fig. 9. Again, comparing the representations according to Fig. 5 and Fig. 6 shows that when the plunger 3 is moved from the closed position to the open position, an elastic stretching occurs in the stretching area 22. In the open position of the plunger 3, the diaphragm 6 is stretched in the stretching area 22 and correspondingly elastically thinned. In the closed position of the plunger 3, in contrast, the diaphragm 6 is slightly compressed in this area. The elastic deformation of the diaphragm 6 in the stretching area 22 largely prevents excessive stress on the diaphragm material, which could lead to failure under unfavorable circumstances.

[0061] The following is intended to be used with the aid of the illustration according to Fig. 9 the structural design of the membrane 6, which is characterized in particular by a compact axial length, will be examined in more detail.

[0062] As already explained above, the transverse deformation region 9 is provided in the axial direction, i.e. in the adjustment direction R of the tappet 3, between the clamping region 6.4 arranged at the top and the adjustment region 6.5 arranged at the opposite end of the diaphragm 6. In order to be able to design the diaphragm 6 to be axially short and in this way to be able to install the diaphragm 6 in the valve housing 2 even in confined spaces, the transverse deformation region 9 and the clamping region 6.4 overlap in the axial direction. The transverse deformation region 9 extends in its upper region at least partially into a substantially V-shaped recess 11 in the diaphragm 6, cf. Fig. 9. The upper fold 9.2 is arranged within the substantially V-shaped recess 11, whereas the lower fold 9.1 is arranged outside the substantially V-shaped recess 11.

[0063] The substantially V-shaped recess 11 is arranged in the clamping area 6.4 of the membrane 6 and in the direction of the valve seat 12, i.e. according to the illustrations in Fig. 5 and Fig. 9 downwards, open. The recess 11 runs circumferentially around the tappet 3 and has a cross-sectional shape reminiscent of a "V". However, the legs of the "V" are not arranged symmetrically to the vertical or to the adjustment direction R, but asymmetrically. The radially inner leg extends essentially in the adjustment direction R, whereas the radially outer leg extends obliquely to the adjustment direction R. The angle between the radially outer leg and the vertical can preferably be between 10 and 50 degrees. The essentially V-shaped recess 11 increases the volume of the chamber 5 in which the membrane 6 is arranged, cf. e.g. Fig. 5 and Fig. 6.

[0064] The following explains how the membrane 6 is fixed relative to the valve housing 2 and connected to the tappet 3, for which purpose the Fig. 5, Fig. 6 and Fig. 9 is referred to.

[0065] The membrane 6 is rotationally symmetrical and has a central section 6.1 on the radial inside, a sealing section 6.3 on the radial outside and a support section 6.2 in between, see. Fig. 9. In the central section 6.1, the transverse deformation region 9 is located. On the other hand, the membrane 6 is also connected to the tappet 3 in the central section 6.1.

[0066] A positive connection is provided between the tappet 3 and the diaphragm 6. A first connecting projection 7.2 is provided on the diaphragm 6 in its adjustment area 6.5 for this purpose, see. Fig. 9. The first connecting projection 7.2 extends radially inward and has a trapezoidal cross-sectional contour. The first connecting projection 7.2 extends in a ring-shaped circumferential manner. Correspondingly, a first connecting undercut 7.1 is formed on the tappet 3 (see FIG. Fig. 5 and Fig. 6. The first connecting undercut 7.1 is provided in the region of the end of the tappet 3 near the valve seat and extends circumferentially around the tappet 3. The cross-sectional contour of the first connecting undercut 7.1 is also trapezoidal and adapted to the cross-sectional contour of the first connecting projection 7.2. The tappet diameter is reduced in the region of the first connecting undercut 7.1 compared to the rest of the tappet 3. Below the first connecting undercut 7.1, at the end of the tappet 3 facing the valve seat 12, the tappet 3 has a diameter which is larger than the diameter in the region of the first connecting undercut 7.1, but smaller than the diameter in the remaining regions of the tappet 3. The membrane 6 is also designed in a similar way and, for example, has thicker walls in its region facing the valve seat 12 than in the transverse deformation region 9, cf. Fig. 9.

[0067] By engaging the first connecting projection 7.2 of the diaphragm 6 in the first connecting undercut 7.1 of the tappet 3, the diaphragm 6 is fixed relative to the tappet 3 at least in the actuating direction R. The actuating movements of the tappet 3 between the open position and the closed position along the actuating path W (cf. e.g. Fig. 8) are carried out synchronously by the adjustment range 6.5 of the membrane 6.

[0068] In its sealing section 6.3, the membrane 6 is positively secured relative to the valve housing 2 via a second connecting undercut 8 formed on the valve housing 2, cf. Fig. 5 and Fig. 6. The second connecting undercut 8 is formed in the upper region of the lower part 2.2 of the valve housing 2 and has a substantially rectangular cross-sectional contour that is open at the top. The second connecting undercut 8 is circumferential and is designed to correspond to the membrane 6 in its sealing section 6.3.

[0069] The annular sealing element 21, which is provided in the sealing section 6.3 of the diaphragm 6 and is connected to the support section 6.2 via a narrow web, is arranged in the second connecting undercut 8 when installed and thus ensures the positive connection to the valve housing 2. The upper part 2.1 of the valve housing 2 closes off the second connecting undercut 8 and the sealing element 21 arranged therein at the top. The annular sealing element 21 has a dual function as a connecting and sealing element. It serves to seal the fluid-carrying wet area N of the solenoid valve 1 from its dry area T, see. Fig. 5 and Fig. 6. The sealing element 21 prevents fluid from flowing, for example, from the chamber 5 in the direction of the magnetic coil 4, which is arranged in the dry area T.

[0070] To provide support against the tappet 3 and the upper part 2.1 of the valve housing 2, the diaphragm 6 has a support shoulder 10. The support shoulder 10 is provided circumferentially at the upper end of the diaphragm 6 and is arranged across sections, both in the support section 6.2 and the central section 1.1. The support shoulder 10 has a substantially rectangular cross-sectional contour. Radially inward, the support shoulder 10 is supported against the cylindrical tappet 3, and radially outward, the support shoulder 10 is supported against the upper part 2.1 of the valve housing 2, cf. e.g. Fig. 7 .

[0071] The support shoulder 10 also serves as a stop for the plunger 3 in its closed position. For this purpose, the upper side of the support shoulder 10 can interact with a circumferential shoulder 3.2 of the plunger 3, see also Fig. 7. The shoulder 3.2 of the plunger 3 is provided at the transition between a tapered area extending into the chamber 5 and an area having a larger diameter and arranged in the effective area of ​​the magnetic coil 4, cf. Fig. 5. The upper side of the support shoulder 10 and the underside of the shoulder 3.2 lie flat against each other in the closed position of the plunger 3.

[0072] The following explains how the membrane 6 can be manufactured and mounted in the solenoid valve 1.

[0073] The Fig. The membrane 6 shown in Figure 9 is preferably made of a PFAS-free material. PFAS is the abbreviation for per- and polyfluorinated alkyl compounds. Vulcanization processes or injection molding processes are particularly suitable as manufacturing processes for the membrane 6. The membrane 6 can be mounted with the valve housing 2 disassembled. The membrane 6 is positioned on the lower part 2.2 of the valve housing 2 such that the annular sealing element 21 engages the second connecting undercut 8, see Figure 9. Fig. 5. The tappet 3 is positively connected to the diaphragm 6 so that the first connecting projection 7.2 of the diaphragm 6 interacts with the first connecting undercut 7.1 of the tappet 3. The upper part 2.1 of the valve housing 2 is then placed on top and connected to the lower part 2.2. The shoulder 3.2 rests against the support shoulder 10 of the diaphragm 6. The connection between the upper part 2.1 and the lower part 2.2 can be designed as a detachable connection with separate or integrated fastening means, for example locking hooks or bolts. After the upper part 2.1 has been saddled and fastened, the diaphragm 6 is detachably clamped between the upper part 2.1 and the lower part 2.2 via the sealing section 6.3. Between the upper part 2.1 and the

[0074] A collar of a tappet guide 19 is clamped to the membrane 6, which encloses the area of ​​the tappet 3, which is located in the effective range of the magnetic coil 4, cf. Fig. 6.

[0075] The diaphragm 6 is installed in the valve housing 2 and connected to the tappet 3 in such a way that it is subjected to tensile stress along the travel W of the tappet 3, which extends between the open position and the closed position. The diaphragm 3 is therefore prestressed with tensile stress in every operating state, regardless of the travel W. In particular, during operation of the solenoid valve 1, the prestress does not change from tensile stress to compressive stress. In this respect, the diaphragm 6 is not subjected to any alternating load which would exceed a neutral, stress-free state. Due to the prestress of the diaphragm 6, it applies a restoring force F to the tappet 3, see Fig. 1 and Fig. 2. The restoring force F results from the elastic deformation of the membrane 6 in the transverse deformation region 9. It acts in the direction of the opening position of the tappet 3 and can therefore support the release of the valve seat 12.

[0076] For certain applications, however, it may be advantageous if the diaphragm 6 is installed in the valve housing 2 in such a way that it exhibits a compressive stress state along the entire travel W of the tappet 3. A pure compressive stress state independent of the travel W also avoids alternating loads on the diaphragm 6. Such a compressive stress state can also contribute to preloading the tappet 3 in its closed position.

[0077] The plunger 3 is further preloaded in the actuating direction R by a return element 13 designed as a helical spring. Depending on the arrangement and design of the return element 13, which is provided in a recess in the upper region of the plunger 3 arranged in the effective range of the magnetic coil 4, the latter can be preloaded in its open position or in its closed position.

[0078] In the following, further technical details of the solenoid valve 1 are described, in particular with regard to the differences between the embodiments according to Fig. 1 to 4, explained.

[0079] The solenoid valves 1 according to Fig. 1 to 4 differ in the arrangement and orientation of the respective valve inlet 14 and valve outlet 15. In the two solenoid valves 1 according to Fig. 1 and Fig. 2, the main flow direction of the fluid flow S at the valve inlet 14 and at the valve outlet 15 is identical - the fluid flows into the valve from the left in the image plane and leaves it to the right, transverse to the actuating direction R of the tappet 3. This results in a continuous design in which the inflow axis E and the outflow axis A are coaxial to each other. In the two solenoid valves 1 according to Fig. 3 and Fig. 4, the flow direction of the fluid stream S at the valve outlet 15 is rotated by approximately 90 degrees relative to the valve inlet 14.

[0080] In the embodiment according to Fig. 1 and Fig. 5, the fluid is guided in such a way that the fluid flows from below to the valve seat 12 via the flow channel 23 and the flow channel 18. In the closed position of the tappet 3, as in Fig. 1, the fluid pressurizes the underside of the plunger 3 and the sealing surface 25 of the diaphragm 6. When the plunger 3 is lifted by actuating the solenoid 4 and moved into the open position, the valve seat 12 is released and the fluid flows through the flow channel 18 into the chamber 5 and then via the flow channel 24 to the valve outlet 15, see also Fig. 6.

[0081] In the alternative embodiment according to Fig. 2 and Fig. 7, the fluid flow within the solenoid valve 1 occurs in a slightly different way.

[0082] The fluid flows through the flow channel 23 directly into the chamber 5. In the closed position of the plunger 3, as in Fig. As shown in Figure 2, the chamber 5 is filled with fluid and pressurizes the diaphragm 6 and the plunger 3 in the radial direction. When the plunger 3 is lifted by actuating the solenoid 4 and moved into the open position, the valve seat 12 is released and the fluid flows through the flow channel 18 and the flow channel 24 to the valve outlet 15, see also Fig. 8.

[0083] The representations according to Fig. 3 and Fig. 4 do not show a continuous design in which valve inlet 14 and valve outlet 15 are coaxial to each other, but corner designs. Fig. 3 shows an embodiment in which the inflow axis E of the solenoid valve 1 extends in the actuating direction R of the tappet 3. The flow channel 23 connected to the valve inlet 14 opens directly into the flow channel 18 connected to the valve seat 12. In the closed position of the tappet 3, as is also shown in Fig. 3, the fluid pressure acts on the underside of the tappet 3. When the tappet 3 is lifted by actuating the solenoid 4 and moved into the open position, the valve seat 12 is released and the fluid flows into the chamber 5 and then via the flow channel 24 to the valve outlet 15, see also Fig. 6. The outflow axis A extends transversely to the inflow axis E and thus also to the adjustment direction R of the tappet 3.

[0084] The representation according to Fig. 4 shows an arrangement in which the inflow axis E extends transversely to the direction of travel R of the plunger 3 and transversely to the outflow axis A. The fluid flows via the flow channel 23 directly into the chamber 5. In the closed position of the plunger 3, as in Fig. As shown in Figure 2, the chamber 5 is filled with fluid and pressurizes the diaphragm 6 and the plunger 3 in the radial direction. When the plunger 3 is lifted by actuating the solenoid 4 and moved into the open position, the valve seat 12 is released and the fluid flows through the flow channel 18 and the flow channel 24 to the valve outlet 15, see also Fig. 8. The outflow axis A extends in the adjustment direction R of the tappet 3.

[0085] All embodiments according to Fig. 1 to 4 have in common that the valve seat 12 is arranged integrally on the valve housing 2, specifically on the lower part 2.2 of the valve housing 2. Furthermore, all valve inlets 14 and valve outlets 15 have a hose connection means 16, via which a corresponding hose can be connected to the solenoid valve 1 on the inlet or outlet side. The hose connection means 16 is designed as a plug-in connector and enables a user-friendly, time-saving, and detachable connection of hoses to the solenoid valve 1.

[0086] In the following, details of the operation of the plunger 3 of the solenoid valve 1 are described with the aid of the illustrations in Fig. 5 and Fig. 6, which shows the two bistable positions of the solenoid valve 1. The upper, cross-sectionally forked portion of the cylindrical plunger 3 is enclosed by the solenoid coil 4, cf. Fig. 5. The coil windings of the magnetic coil 4 extend around the magnetic plunger 3, which is not shown in detail in the figures. A pole 20 is arranged above the plunger 3. In the closed position of the plunger 3, as shown in Fig. As shown in Figure 5, the magnetic coil 4 is de-energized and there is an air gap between the pole 20 and the plunger 3. As soon as the magnetic coil 4 is energized, the air gap is closed and the plunger 3 is pulled to the pole 20 and the plunger 3 moves into its open position, see. Fig. 6. The return element 13, which applies a return force to the plunger 3, is also arranged between the pole 20 and the plunger 3. The magnetic coil 4 is supplied with electrical current via the contact 17, which is arranged in an upper region of a housing of the magnetic coil 4, see. Fig. 1 to 4.

[0087] Comparing the representations according to Fig. 5 and Fig. 6 shows that, regardless of whether a gap exists between the pole 20 and the plunger 3, the shoulder 3.2 of the plunger 3 rests against the support shoulder 10 of the diaphragm 6. The required deformation of the diaphragm 6 takes place in the transverse deformation region 9 and the stretching region 22.

[0088] The representations in Fig.1 to 8 each show a direct-switching solenoid valve 1 according to the invention. However, the solenoid valve 1 can also be used in a solenoid valve arrangement as a pilot valve for controlling a main valve. The pilot valve designed as solenoid valve 1 and the main valve form a servo solenoid valve in such a solenoid valve arrangement. Such a servo solenoid valve can prove advantageous in practice for many applications, as it enables reliable switching of the main valve with comparatively low actuation force. In servo solenoid valves, the opening and closing process of the main valve is assisted by the fluid to be switched.

[0089] The solenoid valve 1 and the solenoid valve arrangement described above are characterized in that excessive mechanical stress on the diaphragm 6 can be avoided, thereby extending its service life. Reference symbol: 1 solenoid valve 2 valve housings 2.1 Top 2.2 Lower part 3 pestles 3.1 End 3.2 Shoulder 4 Solenoid coil 5 chamber 6 Membran 6.1 Middle section 6.2 Support section 6.3 Sealing section 6.4 Clamping area 6.5 Setting range 7.1 Connection undercut 7.2 Connecting projection 8 Connection undercut 9 Transverse deformation area 9.1 Folding 9.2 Folding 10 Support heel 11 Recess 12 Valve seat 13 Reset element 14 Valve inlet 15 Valve outlet 16 hose connectors 17 Contacting 18 flow channel 19 Tappet guide 20 pole 21 Sealing element 22 Stretching area 23 Flow channel 24 flow channel 25 Sealing surface A outflow axis E Inflow axis F Restoring force N Wet area R Adjustment direction S fluid flow T Dry area W travel QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] EP 1 596 109 B1

[0005]

Claims

[1] Solenoid valve for controlling fluid flows (S), comprising a valve housing (2), at least one valve inlet (14) and at least one valve outlet (15), which are fluidly connected to one another via a valve seat (12), and a tappet (3) which is movable along an actuating direction (R) and which is adjustable by energising a magnetic coil (4) between an open position releasing the valve seat (12) and a closed position closing the valve seat (12), wherein the tappet (3) is connected at its end facing the valve seat (12) to a membrane (6) fixed relative to the valve housing (2), characterized by that the membrane (6) has a transverse deformation area (9) to compensate for adjusting movements of the tappet (3). [2] Solenoid valve according to claim 1, characterized by that at least two folds (9.1, 9.2) are arranged in the transverse deformation region (9). [3] Solenoid valve according to claim 2, characterized bythat the at least two folds (9.1, 9.2) are arranged one behind the other in the setting direction (R). [4] Solenoid valve according to one of claims 2 or 3, characterized by that the at least two folds (9.1, 9.2) are elastically deformable, in particular accordion-like, as a result of the adjusting movements of the plunger (3). [5] Solenoid valve according to one of claims 2 to 4, characterized by that the at least two folds (9.1, 9.2) are designed and arranged such that their vertices are movable transversely to the adjustment direction (R). [6] Solenoid valve according to one of claims 2 to 5, characterized by that the at least two folds (9.1, 9.2) extend in the circumferential direction around the plunger (3). [7] Solenoid valve according to one of the preceding claims, characterized bythat the membrane (6) is designed and arranged in such a way that it has the same stress state along an adjustment path (W) extending between the open position and the closed position of the tappet (3). [8] Solenoid valve according to claim 7, characterized by that the membrane (6) has a tensile stress state along the travel (W). [9] Solenoid valve according to claim 8, characterized by that the membrane (6) is designed and arranged in such a way that it applies a restoring force (F) to the tappet (3). [10] Solenoid valve according to one of the preceding claims, characterized by that the membrane (6) is constructed rotationally symmetrically and has a central section (6.1) radially inside for closing and releasing the valve seat (12), a sealing section (6.3) radially outside for sealing the valve housing (2) and in between a support section (6.2) for supporting against the valve housing (2). [11] Solenoid valve according to claim 10, characterized by that the transverse deformation region (9) is arranged in the central section (6.1). [12] Solenoid valve according to one of claims 10 or 11, characterized by that the membrane (6) is connected to the tappet (3) in the central section (6.1). [13] Solenoid valve according to one of claims 10 to 12, characterized by that the membrane (6) is positively connected to the tappet (3) via a circumferential first connecting undercut (7.1) formed on the tappet (3) and a first connecting projection (7.2) formed on the membrane (6) corresponding to the first connecting undercut (7.1). [14] Solenoid valve according to one of claims 10 to 13, characterized by that the membrane (6) is positively connected to the valve housing (2) in its sealing section (6.3) via a second connecting undercut (8) formed on the valve housing (2). [15] Solenoid valve according to one of claims 10 to 14, characterized by that the membrane (6) has an annular sealing element (21) in its sealing section (6.3). [16] Solenoid valve according to one of the preceding claims, characterized by that the membrane (6) is detachably arranged between an upper part (2.1) and a lower part (2.2) of the valve housing (2). [17] Solenoid valve according to one of the preceding claims, characterized by that the membrane (6) separates the valve housing (2) into a dry area (T) and a wet area (N), wherein the magnetic coil (4) is arranged in the dry area (T). [18] Solenoid valve according to one of claims 10 to 17, characterized by that the membrane (6) has a support shoulder (10) which is arranged across sections both in the support section (6.2) and in the central section (6.1). [19] Solenoid valve according to claim 18, characterized bythat the support shoulder (10) forms a stop for the plunger (3) in its closed position. [20] Solenoid valve according to claim 18 or 19, characterized by that the support shoulder (10) is designed and arranged in such a way that it cooperates with a shoulder (3.2) of the plunger (3) in the closed position of the plunger (3). [21] Solenoid valve according to one of the preceding claims, characterized by that the membrane (6) has a clamping area (6.4) clamped relative to the valve housing (2) and an adjusting area (6.5) movable with the tappet (3), which are arranged offset from one another in the adjusting direction (R). [22] Solenoid valve according to claim 21, characterized by that the transverse deformation area (9) is arranged between the clamping area (6.4) and the adjustment area (6.5). [23] Solenoid valve according to one of claims 21 or 22, characterized bythat the transverse deformation area (9) and the clamping area (6.4) overlap axially in the adjustment direction (R). [24] Solenoid valve according to one of claims 21 to 23, characterized by that the membrane (6) has a radially circumferential, substantially V-shaped recess (11) in its clamping area (6.4). [25] Solenoid valve according to claim 24, characterized by that the substantially V-shaped recess (11) is open in the direction of the valve seat (12). [26] Solenoid valve according to one of claims 24 or 25, characterized by that the transverse deformation region (9) extends at least partially into the substantially V-shaped recess (11). [27] Solenoid valve according to claim 26, characterized by that at least one of the at least two folds (9.1, 9.2) is arranged within the substantially V-shaped recess (11). [28] Solenoid valve according to one of claims 21 to 27, characterized bythat the membrane (6) has an extension region (22) in which the membrane (6) is designed to be elastically stretchable in order to compensate for adjusting movements of the tappet (3). [29] Solenoid valve according to claim 28, characterized by that the stretching area (22) is arranged in the clamping area (6.4). [30] Solenoid valve according to one of the preceding claims, characterized by that the membrane (6) is made of a non-fluorinated material, in particular a material which is free of per- and polyfluorinated alkyl compounds. [31] Solenoid valve according to claim 30, characterized by that the membrane (6) is manufactured by vulcanization or by an injection molding process. [32] Solenoid valve according to one of the preceding claims, characterized by that the valve seat (12) is arranged in one piece on the valve housing (2). [33] Solenoid valve according to one of the preceding claims, characterized bythat the plunger (3) is preloaded in the setting direction (R) via a return element (13). [34] Solenoid valve according to one of the preceding claims, characterized by that the valve inlet (14) and / or the valve outlet (15) are arranged transversely to the actuating direction (R) of the tappet. [35] Solenoid valve according to one of the preceding claims, characterized by that the flow direction of the fluid stream (S) at the valve inlet (14) and the valve outlet (15) is identical. [36] Solenoid valve according to one of the preceding claims, characterized by that the flow direction of the fluid stream (S) at the valve outlet (15) is changed, in particular rotated, relative to the valve inlet (14). [37] Solenoid valve according to one of the preceding claims, characterized by that the valve inlet (14) and / or the valve outlet (15) are connected to a hose connection means (16). [38] Solenoid valve arrangement with a main valve and a pilot valve for controlling the main valve, characterized by that the pilot valve is designed as a solenoid valve (1) according to one of claims 1 to 37. [39] Solenoid valve arrangement according to claim 38, characterized by that the main valve and the pilot valve form a pilot-operated servo solenoid valve.

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