Normally closed solenoid valve

Abstract

A normally closed solenoid valve (1) with a valve sleeve (5, 6) in which a pole core (2) is fixedly arranged and an armature (3) is axially displaceable, wherein a compression spring (4) acts between the pole core (2) and the armature (3) to force a closing element (9) cooperating with the armature (3) into a valve seat (10), wherein a means (11) for hydraulic damping of the displacement of the armature (3) is formed between the pole core (2) and the armature (3), characterized in that the means (11) for hydraulic damping is formed from at least one spring washer, and that a preload force of the compression spring (4) causes a deformation of the means (11), wherein a striking of the moving armature (3) against the pole core (2) is dampened by means of a return of this deformation.

Description

[0001] The invention relates to a normally closed solenoid valve with a valve sleeve in which a pole core is fixed and an armature having a valve tip is axially displaceable, wherein a helical spring acts between the pole core and the armature to force the valve tip into a valve seat. State of the art

[0002] Solenoid valves of the type mentioned above are known from the prior art. Such a solenoid valve is, for example, in Fig. The solenoid valve 1 is shown in Figure 1. It comprises a solenoid actuator consisting of an energizable solenoid coil (not shown) and a pole piece 2, which acts on an armature 3 that is axially displaceable within the valve sleeve 5, 6. The valve sleeve 5, 6 can be configured as a two-part valve sleeve with an upper valve sleeve 5 and a lower valve sleeve 6. The valve sleeve 5 is positioned within the valve bushing 7. A filter 8 surrounds the inlet in the valve sleeve 6. The armature 3 also has a closing element 9, which is pressed against a valve seat 10 when the solenoid actuator is de-energized. For this purpose, the armature 3 is held under preload within the valve sleeve 5, 6. Typically, a compression spring 4, in particular a helical spring, is provided to apply the preload. This spring acts between the pole piece 2 and the armature 3 and is held under preload.The compression spring 4 is supported at one end by the fixed pole core 2 and at the other end by the movable armature 3. For this purpose, the armature 3 has a recess in which the helical spring is essentially seated and guided. In an alternative embodiment, the pole core 2 can also have a recess in which the helical spring is essentially seated and guided – however, this embodiment is not shown in [reference]. Fig. Figure 1 shows the section of the compression spring 4 extending beyond the recess. The section rests against the pole core 2 and extends from the end face of the armature 3 facing the pole core 2 to the end face of the pole core 2 facing the armature 3. The distance between these two faces in the de-energized state forms the so-called working air gap. This working air gap determines the maximum possible displacement of the armature 3, and thus the stroke of the solenoid valve 1. When the solenoid valve 1 is energized, the air gap between the pole core 2 and the armature 3 is closed by the armature 3 moving upwards until it abuts the pole core 2. When the energization is de-energized, the compression spring 4 moves the armature downwards against the valve sleeve 5, 6 until the closing element 9 rests against the valve seat 10, thus closing the valve. Typically, when the energization is applied, the magnetic force increases as the working air gap decreases.This increasing magnetic force curve makes it difficult to continuously adjust the solenoid valve 1. To improve adjustability, it is known to provide a compression spring 4 with progressive spring characteristics, or, for example, to provide an additional disc spring (not shown) with a progressive spring characteristic.

[0003] For example, German patent application DE 103 254 42 A1 is known from the prior art. This document relates to a solenoid valve comprising a pole core, an armature, and a return element arranged between the pole core and the armature to return the armature to its initial position, wherein a stop surface of the pole core facing the armature has at least one circumferentially extending web projecting towards the armature, and / or a stop surface of the armature facing the pole core has at least one circumferentially extending web projecting towards the pole core.

[0004] For example, the prior art includes German patent application DE 10 2014 200 574 A1. This document relates to a solenoid valve, in particular for actuating an injection device for injecting a reducing agent into the exhaust system of an internal combustion engine of a vehicle, with a solenoid group for actuating a valve element actuated by a return spring, which opens or closes a valve seat, wherein a stroke stop is provided between the valve element and the solenoid group, limiting a liquid-filled squish gap, and wherein a counter surface corresponding to the stroke stop is stepped.

[0005] Furthermore, DE 103 55 706 A1 discloses a normally closed solenoid valve in which the means for hydraulically damping the displacement of the armature, arranged between a pole core (stationary element 13) and an armature (movable element 18), are designed as an annular washer (24) with a damping chamber R3 arranged inside it. This damping chamber communicates via a fixed throttle (26) with connecting grooves (22). A compression spring (14) of this solenoid valve is supported at one end on the pole core (13) and at a second, opposite end, on the armature (18), with the end of the compression spring (14) facing the armature (18) extending through the opening of the washer (24).

[0006] According to the prior art of US 2013 / 0020514 A1, the means for hydraulically damping armature displacement are designed as a piston / cylinder unit with a damping chamber. This damping chamber is connected to a valve chamber via a throttle cross-section. Damping of the armature movement is achieved by fluid exchange between the chambers via the throttle cross-section.

[0007] In new, so-called 1-box brake systems, the hydraulic unit is bolted directly to the vehicle's firewall. This places increased demands on the noise, vibration, and harshness (NVH) behavior of all components within the hydraulic unit, as noises generated, for example, by the switching of the hydraulic unit's solenoid valves, are transmitted directly into the passenger compartment through this mounting method. For instance, a normally closed exhaust valve can produce an opening click when the armature, usually made of steel, strikes the pole piece, also made of steel, when energized. Disclosure of the invention

[0008] For the use of solenoid valves with this type of mounting, it would be advantageous to reduce or, ideally, completely eliminate such noises. This would allow for an opening behavior that is acceptable from an NVH (noise, vibration, and harshness) perspective. Furthermore, it would be beneficial to be able to dampen both the opening and closing noises.

[0009] It is therefore a normally closed solenoid valve, provided with a valve sleeve in which a pole piece is fixed and an armature is axially displaceable, wherein a compression spring acts between the pole piece and the armature to force a closing element, which interacts with the armature, into a valve seat. Means for hydraulically damping the displacement of the armature are provided between the pole piece and the armature.

[0010] Damping of the displacement is understood to mean both the actual movement of the armature and a change in the movement, in particular a stopping of the movement, e.g., by impact. For example, such damping can achieve a slowing of the movement. Furthermore, such damping can enable a force-reduced impact of the moving component against another component. The damping of the displacement acts in both directions, that is, both when opening and when closing the valve. According to the invention, the means used enables hydraulic damping. Hydraulic damping is understood to mean damping as described above, which is achieved by means of a fluid, or damping that is achieved by means of effects resulting from a generated hydraulic fluid flow.A mechanical element is provided as a means of achieving hydraulic damping. According to the invention, this element is positioned between the armature and the pole core. This means, in particular, that it is positioned axially between the two components, whereby contact with one or both components is of course possible.

[0011] Axial displacement of the armature in a normally closed valve is understood to mean displacement towards the open position when energized by electromagnetic forces, as well as retraction by a compression spring when de-energized. A helical spring is typically used as the compression spring. In the prior art, when the armature displaces during energization, it often strikes the pole core without damping. Furthermore, a smaller working gap between the pole core and the armature increases the attractive forces, meaning the armature experiences acceleration as it approaches. This hydraulic damping of the displacement can reduce the effects of such impact. In particular, the transmission of structure-borne noise within the system can be reduced or eliminated.The term "anchoring" refers to any type of force and / or momentum transmission between the two components. This naturally includes indirect impact of the anchor on the pole core via another component, such as a spring washer positioned between the anchor and pole core. This allows for an opening behavior that is acceptable from an NVH (noise, vibration, and harshness) perspective, even with a direct connection of the hydraulic unit to the firewall.

[0012] According to the invention, the solenoid valve is characterized in that the means is formed from at least one spring disc and a preload force of the compression spring causes a deformation of the means, whereby a striking of the moving armature against the pole core is dampened by means of a return of this deformation.

[0013] According to the invention, a compression spring present in the system leads to a specific, defined deformation of the means in the unenergized state of the solenoid valve. When the valve is energized, the working air gap between the pole core and the armature closes. The armature moves upwards, and the deflection of the spring plates increases due to the rising spring force. Shortly before the end of the stroke, the spring discs, which are pre-curved at their outer edge, contact the pole core, and the impact is dampened by this pre-curvature, which acts as a stop spring, until the end position is reached. The return of this specific, defined deformation dampens any impact of the armature against the pole core. This damping advantageously reduces the effects of such an impact.

[0014] The device is designed to provide both hydraulic damping of anchor displacement and mechanical damping of anchor impact. Both damping effects are thus generated by a single component, namely the device itself, or through the interaction of this component with other components. The combined effects of hydraulic and mechanical damping result in a significant improvement in NVH (noise, vibration, and harshness) performance.

[0015] In an advantageous embodiment, the solenoid valve is characterized in that the means for controlling the displacement speed of the armature is designed.

[0016] This means that the hydraulic damping device for the displacement of the anchor achieves such damping by enabling control of the displacement speed. Control refers to regulation and / or influencing of the relevant parameter. Specifically, the device is designed to reduce the displacement speed, i.e., the speed of movement, of the anchor. By controlling the speed, the impact of the anchor against the pole core can be influenced. Advantageously, this impact is dampened. This allows for the achievement of desired noise characteristics.

[0017] In a preferred embodiment, the solenoid valve is characterized in that the means is designed as a hydraulic orifice.

[0018] This means that the device is designed in such a way that its positioning within the valve causes it to act as a hydraulic orifice. A hydraulic orifice is a localized flow resistance. This is created, for example, by abruptly narrowing the flow cross-section. Since the fluid is backed up in the flow direction upstream of the orifice, the pressure upstream of the orifice is higher than the pressure downstream. The volumetric flow rate is primarily determined by the resulting pressure differential. By positioning the device on the armature, a hydraulic orifice is created that moves with the armature stroke. The volumetric flow rate in the valve can be influenced by the use and design of an orifice. Due to the essentially incompressible nature of the fluid, an orifice can thus be used to advantageously control the armature's movement speed and, consequently, the impulse upon impact.

[0019] In an advantageous further development, the solenoid valve is characterized by the fact that the means has a defined fluid passage opening.

[0020] This means that the device is designed to allow fluid passage at a specific point. Such a fluid passage can, for example, be designed as an orifice and achieve corresponding effects. In particular, it is intended to create an orifice by means of a central fluid passage in the device, for example, as a central hole. The effect and strength of the damping can be adjusted, for example, by the diameter of the hole to achieve the desired damping effect. The design of the fluid passage must therefore be coordinated with the required fluid flow rate. This takes into account both the overall design of the valve and the desired movement characteristics of the armature.

[0021] In one possible embodiment, the solenoid valve is characterized in that a defined fluid passage channel is formed between the means and the valve sleeve by means of the means.

[0022] This means that hydraulic damping during armature movement can be achieved not only by means of fluid guidance through a passage within the element, but also advantageously by means of fluid guidance around the outside of the element. Analogous to the previously described embodiment of a central fluid passage, a specific design of a fluid channel between the element and the valve sleeve can also advantageously achieve the desired hydraulic damping. For this purpose, the fluid channel, and thus the possible volume flow, must be defined accordingly. If an armature groove is present, a damping effect occurs even if the fluid flow through the armature groove is impaired, i.e., if, for example, the element partially covers the armature groove. Complete coverage of the armature groove leads to an increase in the effect.Furthermore, the channel between the center and the valve sleeve can be designed to be narrower than the channel between the armature and the valve sleeve in order to achieve a high amplification of the effect and a more pronounced damping.

[0023] In an advantageous further development, the solenoid valve is characterized in that the means is positioned on an end face of the armature facing the pole core.

[0024] This means that, in the de-energized state of the valve, the element is positioned and mounted such that it is located on the end face of the armature and connected to it. Movement of the armature therefore also results in movement of the element. The specific arrangement of the spring washer assembly allows, for example, the creation of a hydraulically actuated orifice that moves with the armature stroke. The fluid in the valve, located between the element and the pole piece, is displaced during the stroke and flows downwards past the element. The element acts as an orifice that the fluid must flow around or through during the stroke. This reduces the armature speed compared to the prior art and results in less structure-borne noise during switching. When the solenoid valve is de-energized, the spring force of the compression spring moves the armature, together with the spring washer assembly, downwards towards the closed position.Here too, the spring washer assembly acts as a hydraulic orifice. The fluid flows back over the spring washer assembly into the area above the spring washer assembly between the armature and the pole piece, thus dampening the closing impulse.

[0025] It is further advantageous that the solenoid valve is characterized in that the means is in contact with the end face of the armature facing the pole core. This means that the means is in direct contact with the end face of the armature facing the pole core. Such contact is naturally achieved when the means is in contact with a region of the described armature step. In an advantageous embodiment, the solenoid valve is characterized in that the compression spring is arranged, at least partially, between the means and the armature.

[0026] In an advantageous further development, the solenoid valve is characterized in that a preload force of the compression spring causes a deformation of the means, whereby a striking of the moving armature against the pole core is dampened by means of a return of this deformation.

[0027] It has already been explained that a hydraulic damping device is provided, whereby the hydraulic damping of the armature's displacement leads to a reduction in velocity and thus to a damping of the armature's impact on the pole core. It is now further explained that additional damping is provided by the device: As already described, the hydraulic damping device is positioned between the pole core and the armature. A compression spring present in the system causes a specific, defined deformation of the device when the solenoid valve is unenergized. When the valve is energized, the working air gap between the pole core and the armature closes. The armature moves upwards, and the deflection of the spring plates increases due to the rising spring force.

[0028] Shortly before the end of the stroke, the spring discs, which are pre-curved on their outer wheel, contact the pole core, and the impact is dampened by this pre-curvature, which acts as a stop spring, until the end position is reached. Here, the return of the specific, defined deformation dampens any impact of the armature against the pole core. This damping effectively reduces the effects of such an impact.

[0029] The device is designed to provide both hydraulic damping of anchor displacement and mechanical damping of anchor impact. Both damping effects are thus generated by a single component, namely the device itself, or through the interaction of this component with other components. The combined effects of hydraulic and mechanical damping result in a significant improvement in NVH (noise, vibration, and harshness) performance.

[0030] In an advantageous embodiment, the solenoid valve is characterized in that the means is formed from at least one spring disc, in particular from a spring disc assembly.

[0031] This means that a spring washer can be used to achieve the mechanical damping effects described above. The number of spring washers can be adjusted depending on the dimensions and material characteristics of the washers, as well as the application and the desired damping level. The described effect of deformation and subsequent recovery occurs even with a single spring washer. However, using multiple washers can lead to further effects, such as friction and the reduction of unevenness between them. For example, a stack of spring washers can be advantageously used to enhance these effects. The spring washers can be manufactured as stamped parts from standard sheet metal. They can also be handled in bulk. This makes the solution cost-effective.

[0032] In a preferred embodiment, the solenoid valve is characterized in that an end face of the armature facing the pole core has an axially formed contour over the diameter, wherein this contour in particular forms a radially outer bearing option for the means on the armature as well as a radially inner cavity between the means and the armature.

[0033] This means that a surface texture of an existing component (e.g., a stepped armature) can be used as a support point. This texture can be radially single-stepped or multi-stepped. Besides steps, smooth transitions or hybrid forms are also conceivable. Such a step can be created, for example, by machining processes such as turning and milling. The armature step is typically applied circumferentially around the armature. The step can include one or more indentations distributed around the circumference, for example, to accommodate fluid volume displacement.

[0034] In an advantageous embodiment, the solenoid valve is characterized by an inner diameter of the bearing surface that is larger than the outer diameter of the compression spring. This design feature advantageously achieves a desired curvature of the spring discs. At the point of contact between the compression spring and the spring disc, deformation occurs in the direction of the spring's preload force. At the bearing surface, i.e., the support point, deformation of the spring disc is prevented. This allows for a counter-deformation of the spring disc in the outer region, i.e., radially further outward than the bearing surface, i.e., against the spring's preload force.

[0035] In a preferred embodiment, the solenoid valve is characterized in that the means is essentially flat in its undeformed state, and the deformation causes the means to bulge.

[0036] This means that the component, in particular the spring washer, essentially has the flat surface of a disc. The basic shape of the component is therefore disc-shaped and essentially flat in its original, uninstalled state. This allows for the advantageous use of very simple and cost-effective standard components. The required shape for damping the impact, i.e., the desired curvature, is generated solely by the preload force of the compression spring within the system. Therefore, no preliminary shaping step is necessary. The curvature is created purely through the regular assembly of the components. It is therefore neither necessary nor advantageous for the component to have a defined, shaped spring structure, such as a Belleville spring.

[0037] In an advantageous embodiment, the solenoid valve is characterized in that the preload force of the compression spring causes an outer edge of the means to be curved in the opposite direction to the acting preload force of the compression spring, whereby a collision of the armature against the pole core is dampened by means of at least partial and / or partial regression of this curvature.

[0038] This means that the components are dimensioned, characterized, and coordinated in such a way that the following effects occur: The compression spring has a preload and is supported on the armature via the center, i.e., in particular via the spring washers, and a support point (e.g., an armature step or a residual air gap washer). Due to the acting preload force of the compression spring, the spring washers are curved towards the armature at the support point of the compression spring, i.e., in the center of the spring washers. The support point can, of course, also be understood to be a surface or partial surface, e.g., a circular segment against which the spring washer rests. This deflection lifts the spring washer assembly away from the armature step or the residual air gap washer at its outer diameter when the valve is de-energized. That is, the outer edge of the spring washer, or...The spring washer assembly is curved from the support point towards the pole core, in the opposite direction to the compression spring's pressure direction. When the valve is energized, the existing working air gap between the armature and pole core is closed by the armature's movement. However, unlike in prior art, the armature does not impact the pole core without restraint, but is decelerated by the spring travel provided by the pre-curvature of the spring washers until it reaches its end position. Naturally, at least partial and / or partial re-curvature of the washer also results in a damping effect. The combination of the spring washer with a support point creates a damping system that, when installed between the pole core and the armature, dampens the impact impulse and thus reduces structure-borne noise in the system.

[0039] In an advantageous embodiment, the valve is characterized in that the compression spring is positioned in a recess of the pole core. As already described, the armature has a recess for receiving and guiding the compression spring. The compression spring is positioned and guided within this cavity.

[0040] In one possible embodiment, the solenoid valve is characterized by the fact that the element is held axially against the end face of the armature by means of a compression spring. This means that the spring washers are held in a defined position even when de-energized. For this purpose, the compression spring has a preload. This preload can be applied during the assembly of the valve. The compression spring is further supported against the armature via the spring washers. In addition to direct support, indirect support by means of another component, e.g., a residual air gap washer, is also possible. Designs

[0041] The figures show: Fig. 1 a schematic sectional view of a prior art solenoid valve, and Fig. 2 a section of a sectional view of an embodiment of the solenoid valve with a hydraulic damping means, and Fig. 3 a section of an oblique view of the armature with an armature step according to an embodiment of the solenoid valve, and Fig. 4 a schematic representation of the mode of operation when the valve is de-energized and when it is energized, and Fig. 5 a finite element representation of the mode of action when the valve is de-energized and when it is energized.

[0042] Fig. Figure 1 shows a schematic sectional view of a prior art solenoid valve 1 for a hydraulic power unit for a vehicle. A description of this solenoid valve can be found in the prior art documentation.

[0043] Fig. Figure 2 shows a section of a sectional view of an embodiment of the solenoid valve 1 with a hydraulic damping element 11. Specifically designed spring washers 12 are used as the damping element 11. In the illustrated embodiment, three spring washers 12 are used. Here, the spring washers 12, i.e., the damping element 11, are positioned directly on the armature 3. In the radially outer region, the armature 3 has a continuous armature groove 13 along its entire length. In the illustrated embodiment, two armature grooves 13 are formed. The armature 3 also has a stepped section 14 in its outer region, against which the damping element 11 rests directly. Due to the stepped section 14, a radially inner cavity is formed between the damping element 11 and the armature 3. The stepped section 14 has a recess in the region of the armature grooves 13. Alternatively, the armature groove 13 can also extend through the stepped section 14.A compression spring 4, designed as a helical spring, is positioned in a recess of the pole core 2, in which the compression spring 4 essentially rests and is guided. The compression spring 4 has a preload and is supported at one end by the pole core 2 and at the other end by the means 11 and the armature step 14 on the armature 3. This holds the means 11 axially against the pole core 2. Furthermore, the preload of the compression spring 4 causes the means 11 to bulge towards the armature 3.

[0044] Fig. Figure 3 shows a section of an oblique view of the armature 3 with an armature step 14 according to an embodiment of the solenoid valve 1.

[0045] The end face facing the pole core 2 is shown here. Two anchor grooves 13 are also shown. The anchor step 14 is omitted at the locations of the anchor grooves 13 and is therefore only partially or partially circumferentially executed. As already described, the anchor step 14 serves to support the means 11 in the installed state.

[0046] Fig. Figure 4 shows a schematic representation of the operation of the valve 1 in the unenergized state S1 (left illustration) and in the energized state S2 (right illustration). The means 11 is further represented by three spring washers 12. The spring washers are specifically adapted to enable hydraulic damping. Their position on the moving armature is particularly noteworthy. A central fluid passage 15 is also shown. Furthermore, the means 11 forms an outer fluid channel 16 between the means 11 and the sleeve 5. In the illustrated embodiment, this fluid channel 16 is narrower than the regular fluid channel 17 between the armature 3 and the sleeve 5. The desired damping hydraulic effect occurs as soon as the means 11 influences the regular fluid flow through the outer fluid channel 17 or the fluid flow through the armature groove 13. This occurs even when the means 11 partially covers the armature groove.This occurs, for example, when the diameter of the means 11 is larger than the distance between the radially deepest points of the anchor grooves 13.

[0047] While the left representation in Fig. Figure 4 depicts the de-energized state S1, while the right-hand figure illustrates the energized state S2. The fluid flow patterns are depicted using arrows. In the valve shown, the cavities are completely filled with fluid 18 in both states. Due to the movement of the armature 3 from state S1 to state S2, the fluid 18 located between the armature 3 and the pole core 2 must be displaced. During this displacement, the fluid 18 is directed, for example, through the central fluid passage 15 into the cavity between the center 11 and the armature 3. From there, the fluid 18 is directed to the armature grooves 13. Through the armature grooves 13, the fluid 18 reaches the fluid chamber below the moving armature 3 for pressure equalization. The depicted flow of the fluid 18 results in hydraulic effects, such as turbulence caused by a hydraulic orifice. These effects dampen the armature movement.The anchor grooves 13, which remain, allow the fluid 18 to flow freely, i.e., without obstruction. Alternatively, or as shown in the embodiment, in addition to the other methods, the fluid 18 is also directed via the outer fluid channel 16, which can achieve further effects or enhance the effect. Fig. Figure 4 illustrates in particular the hydraulic damping of the movement of the anchor 3 by means of the device 11. A specific damping can be set by defining the design of the device 11. Suitable methods for this include, for example, the dimensioning of the diameter of the central fluid passage 15 or the outer diameter and thus of the outer fluid channel 16.

[0048] Fig.Figure 5 shows a finite element representation of the operation of the solenoid valve 1 in the de-energized state S1 and the energized state S2. The diagram illustrates the operation, in particular the mechanical damping of the armature 3 striking the pole core 2 by means of the means 2. To the left of the line of symmetry, the initial position S1 with the solenoid valve 1 de-energized is shown. The preload of the means 11, designed as a spring washer assembly, is visible, due to the compression spring 4 shown centrally in position S1_4, as is the bending of the means 11 at its outer diameter into position S1_11 in the direction of the pole core 2. The pole core remains in the same position in both states S1 and S2, which, for the sake of simplicity, will be referred to as S1_2 and S2_2, respectively. Furthermore, the starting position S1_3 of the armature 3 for the unenergized state S1 is shown, with a working air gap between the center 11 and the pole core S1_2.To the right of the line of symmetry, the armature 3 is shown in its end position S2_3 for the energized state S1, with the working air gap between the means 11 in its position S2_11 and the pole core 2 reduced. The compression spring 4 is also in the end position S2_4. The desired additional damping of the armature 3 striking the pole core 2 is achieved by the fact that the armature 3 is decelerated by the section of the means 11 bent towards the pole core 2 before it reaches its end position. Part of the kinetic energy of the armature 3 is thereby converted by a return deformation of the curved means 11.

Claims

[1] A normally closed solenoid valve (1), comprising a valve sleeve (5, 6) in which a pole core (2) is fixed and an armature (3) is axially displaceably arranged, wherein a compression spring (4) acts between the pole core (2) and the armature (3) to urge a closing element (9) cooperating with the armature (3) into a valve seat (10), wherein a means (11) for hydraulically damping the displacement of the armature (3) is formed between the pole core (2) and the armature (3), characterized by that the means (11) for hydraulic damping is formed from at least one spring washer, and that a prestressing force of the compression spring (4) causes a deformation of the means (11), wherein a striking of the moving armature (3) against the pole core (2) is dampened by means of a recovery of this deformation. [2] Solenoid valve (1) according to claim 1, characterized by that the means (11) is designed to control the displacement speed of the armature (3). [3] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) is designed as a hydraulic orifice. [4] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) has a defined fluid passage opening (15). [5] Solenoid valve (1) according to one of the preceding claims, characterized by that by means of the means (11) a defined fluid passage channel (16) is formed between the means (11) and the valve sleeve (5). [6] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) is positioned on an end face of the armature (3) facing the pole core (2). [7] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) is formed from a spring washer package. [8] Solenoid valve (1) according to one of the preceding claims, characterized bythat an end face of the armature (3) facing the pole core (2) has an axially formed contour over the diameter, said contour forming a radially outer support possibility for the means (11) on the armature (3) and a radially inner hollow space between the means (11) and the armature (3). [9] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) is substantially flat in the non-deformed state, and the deformation causes a curvature of the means (11). [10] Solenoid valve (1) according to one of the preceding claims, characterized by that by the prestressing force of the compression spring (4) an outer edge of the means (11) is curved in the opposite direction to the acting prestressing force of the compression spring (4), wherein by means of an at least regional and / or partial regression of this curvature a striking of the armature (3) on the pole core (2) is dampened. [11] Solenoid valve (1) according to one of the preceding claims, characterized by that the compression spring (4) is positioned in a recess of the pole core (2). [12] Solenoid valve (1) according to one of the preceding claims, characterized by that the means (11) is held axially on the end face of the armature (3) by means of the compression spring (4).

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