Actuator arrangement for an electromagnetically actuated valve

Abstract

Actuator arrangement (10) for an electromagnetically actuated valve (42, 66, 72), comprising: - a housing with a first housing wall (12) and a second housing wall (14) opposite the first housing wall (12), - a magnetic armature (16) arranged in the housing between the first housing wall (12) and the second housing wall (14), which is movable between the first housing wall (12) and the second housing wall (14) along an axis (18), wherein the magnetic armature (16) has a first axial armature end face (20) facing the first housing wall (12) and a second axial armature end face (22) facing the second housing wall (14), and the magnetic armature (16) is movable between a first position in which the first armature end face (20) contacts the first housing wall (12) and a second position in which the first armature end face (20) is detached from the first housing wall (12), - at least one damping element (24, 24A, 24B) made of an elastomeric material arranged on the second armature end face (22) and extending from the second armature end face (22) in the direction of the second housing wall (14), wherein the at least one damping element (24, 24A, 24B) contacts the second housing wall (14) both in the first position and in the second position of the magnet armature (16), and - a stop element (26) made of an elastomeric material, arranged on the second armature end face (22) and extending from the second armature end face (22) in the direction of the second housing wall (14), which stop element is detached from the second housing wall (14) in the first position of the magnet armature (16) and contacts the second housing wall (14) in the second position of the magnet armature (16), - wherein the second housing wall (14) has a fluid opening (56) extending through the second housing wall (14) and the stop element (26) in the second position of the magnet armature (16) contacts a sealing seat of the fluid opening (56) in a fluid-tight manner.

Description

[0001] The present invention relates to an actuator assembly for an electromagnetically actuated valve. The actuator assembly can be used in particular for a pneumatic adjustment device of a vehicle seat.

[0002] Modern vehicle seats contain fluid chambers or fluid bladders that can be filled with a pressure medium, in particular a gaseous pressure medium such as compressed air, as actuating elements in the area of ​​the seat surface or seat back (collectively also referred to as the seat contact surface). Such fluid chambers can be supplied with the pressure medium via a respective pressure medium line. By filling or emptying a respective fluid chamber with pressure medium, its volume is increased or reduced so that the properties of the seat contact surface, in particular its contour, can be changed. To fill the respective fluid chamber with pressure medium, the pressure medium is first generated by a pressure medium source, for example a compressor or a compression unit, and is then guided to a respective fluid chamber in a controlled manner via a suitable valve.

[0003] Electromagnetic valves operated by an actuator arrangement are often used for this purpose. A disadvantage of such actuator arrangements, however, is the comparatively loud switching noise. This is because as soon as the armature is set in motion with sufficient current, the air gap between the armature and the electromagnetic core decreases. As a result, the magnetic force increases disproportionately with the distance traveled by the armature. If the spring force counteracting the movement of the armature by a return spring only increases linearly, this leads to a high speed of the armature, which is only suddenly decelerated when the armature strikes the opposite stop (e.g. the electromagnetic core). The result is a loud "click" from the valve.

[0004] US Patent No. 2,923,521 describes an AC solenoid actuator that is quiet and reliable. The solenoid piston is sealed to isolate it from the atmosphere and the controlled fluid. Flexible closures at the ends of the guide tube equalize the fluid pressure, so the piston remains unaffected by external pressure fluctuations.

[0005] DE 10 2016 211 852 A1 relates to a solenoid valve that reduces the audible noise of a hydraulic system by reducing oil pressure oscillations within an oil gallery network. The solenoid valve comprises a coil carrying a winding, an armature carrying a damper, a core, and a push pin that activates a valve body such that the valve body strikes a valve seat. The damper creates a non-linear characteristic that reduces the speed of the valve body upon impact against the valve seat.

[0006] DE 10 2011 087 964 A1 relates to a valve, in particular a tank venting valve, comprising a valve opening with a circumferential valve seat, a valve member that interacts with the valve seat to close and release the valve opening, and an annular sealing element arranged on the valve member and forming a seat seal with the valve seat. To generate a closing force acting on the valve member to close the valve opening, a spring-elastic sealing sleeve is arranged on the rear side of the valve member facing away from the valve seat. The sealing sleeve is axially clamped with preload between the valve member and a valve-fixed stop. The sealing sleeve simultaneously serves to seal a free space on the rear side of the valve member that is connected to the valve opening via at least one through-opening in the valve member, thereby ensuring pressure equalization at the valve member.

[0007] US 4,245,815 A discloses an electromagnetically controlled proportional flow valve comprising an actuating magnet with an axially extending coil and a valve body with an axially extending cavity having a fluid inlet, a fluid outlet, and a valve seat surrounding one of the passages on an end wall of the cavity. A valve piston is axially movable within the cavity to move with an end wall thereof toward and away from the valve seat. A biasing device is disposed between the opposite ends of the cavity and the piston. The biasing device comprises a generally conical abutment having a rounded free end biased into contact with an elastically deformable elastomeric spring whose diameter is at all times larger than the portion of the conical abutment member in contact therewith.The biasing device normally holds the valve piston in contact with the valve seat, and the solenoid moves the piston away from the valve seat in proportion to the current flowing through it. A connector allows the valve (as well as other valves of different designs) to be connected to a circuit board, with all pneumatic and electrical connections to the valve located on the opposite side of the circuit board.

[0008] DE 20 2014 006 875 U1 relates to a combined air distribution valve group in an inflation system, consisting of a housing with a control valve and at least two air valves. The control valve regulates the air flow from the air pump to the air valves, which in turn inflate air bags and maintain the air pressure. When the valve stems are activated, the air is either pumped into the air bags or released.

[0009] The object of the present invention is therefore to provide an actuator arrangement for an electromagnetically actuated valve which is characterized by reduced noise generation or by reduced switching noise.

[0010] This object is achieved by an actuator arrangement according to claim 1. Advantageous embodiments are the subject of the subclaims.

[0011] The actuator arrangement according to the invention comprises a housing with a first housing wall, a second housing wall opposite the first housing wall, and a magnet armature arranged in the housing between the first housing wall and the second housing wall. The magnet armature is movable between the first housing wall and the second housing wall along an axis. The magnet armature is preferably a cylindrical, in particular circular-cylindrical, magnet armature and comprises a first axial armature end face facing the first housing wall, and a second axial armature end face opposite the first axial armature end face and facing the second housing wall. The term "axial armature end face" means that the armature end faces of the magnet armature run perpendicular to the axis along which the magnet armature is movable.The magnet armature is movable between a first position in which the first armature end face contacts the first housing wall and a second position in which the first armature end face is detached from the first housing wall.

[0012] The actuator arrangement according to the invention further comprises at least one damping element made of an elastomeric material, which is arranged on the second armature end face and extends from the second armature end face in the direction of the second housing wall, wherein the at least one damping element contacts the second housing wall both in the first position and in the second position of the magnet armature, and at least one stop element made of an elastomeric material, which is arranged on the second armature end face and extends from the second armature end face in the direction of the second housing wall (and is different from the at least one damping element), which stop element is made of an elastomeric material and is detached from the second housing wall in the first position of the magnet armature and contacts the second housing wall in the second position of the magnet armature.

[0013] Because the at least one damping element is in contact with the second housing wall both in the first position and in the second position of the armature, no free-flying phase of the armature occurs when moving from the first position to the second position. Rather, the armature is in continuous contact with the second housing wall via the at least one damping element, thereby noticeably reducing noise generation from the actuator arrangement. In addition, the at least one damping element is made of an elastomeric material, so that the at least one damping element is compressed when the armature moves from the first position to the second position. The compression leads to a damped movement of the armature from the first position to the second position, thereby further reducing noise generation.The elastomeric material is selected in particular to achieve a progressive spring characteristic that dampens the movement of the magnet armature (in particular, absorbs energy). Elastomeric EPDM or silicone, for example, can be used as the elastomeric material. In addition, the at least one stop element, which only contacts the second housing wall in the second position of the magnet armature, is also made of an elastomeric material. The at least one stop element serves as a stop for the movement of the magnet armature from the first position to the second position and is also compressed upon impact with the second housing wall.All this contributes to the fact that the actuator arrangement has a comparatively low switching noise and thus does not contribute to any unnecessary noise development, particularly in pneumatic adjustment devices of vehicle seats, where the actuator arrangement is usually arranged very close to the vehicle occupant.

[0014] It is particularly advantageous if the at least one damping element and the at least one stop element are formed from the same elastomeric material. This allows for cost-effective production of the actuator assembly, particularly because both the at least one damping element and the at least one stop element can be attached to the second armature end face in a single production step using the same elastomeric material. For example, this can be achieved by injection-molding the two elements onto the second armature end face.

[0015] In a further preferred embodiment, in the first position of the magnet armature, an axial extent of the at least one damping element is greater than an axial extent of the at least one stop element. In other words, in the first position of the magnet armature, the at least one damping element protrudes further in the direction of the second housing wall than the at least one stop element. The at least one stop element can be formed almost planar on the second armature end face, so that the at least one stop element almost does not protrude from the second armature end face. However, the at least one stop element will also preferably protrude in the direction of the second housing wall or protrude from the second armature end face in the direction of the second housing wall.Since the at least one damping element protrudes more in the direction of the second housing wall than the at least one stop element, it is not necessary to provide the second housing wall with projections specially designed for the damping element and the stop element.

[0016] It is particularly advantageous if, in addition, a (magnitude-related) difference between the axial extent of the at least one stop element and the axial extent of the at least one damping element is substantially in the range of a stroke of the armature. The stroke of the armature describes the actuating path traveled by the armature during its movement from the first to the second position. This design ensures that, on the one hand, the damping element already rests against the second housing wall in the first position and, moreover, that almost no compression acts on the damping element in the first position of the armature. This reduces unnecessary pre-compression of the at least one damping element in the first position of the armature, thereby reducing material wear on the at least one damping element and increasing the service life and long-term stability of the at least one damping element.

[0017] According to a further preferred embodiment, the second housing wall has a fluid opening extending through the second housing wall, and the at least one stop element makes fluid-tight contact with a sealing seat of the fluid opening in the second position of the magnet armature. In this preferred embodiment, the stop element thus performs a dual function. It serves not only as a stop in the second position of the magnet armature, but also as a sealing element for fluid-tightly closing the fluid opening. This is particularly advantageous when the fluid opening is, for example, a nozzle seat for a fluid source or for a fluid connection to the environment, since in such a case the stop element can act as a sealing element integrally formed on the second armature end face.

[0018] In a further preferred embodiment, the at least one damping element has an axial damping element end face, and the size of the axial damping element end face is in a range of approximately 5% to approximately 50%, in particular in a range of approximately 10% to approximately 20%, of the size of the second armature end face. This embodiment achieves a particularly soft force-displacement characteristic during compression of the at least one damping element, which also contributes to a progressive spring characteristic that absorbs energy.

[0019] In a further preferred embodiment, in the first position of the magnet armature, an extension of the at least one stop element in the circumferential direction of the magnet armature is at least twice as large as an extension of the at least one damping element in the circumferential direction of the magnet armature. In other words, viewed in the circumferential direction of the magnet armature, the at least one stop element is wider than the at least one damping element. This embodiment ensures that the stop element has a harder force-displacement characteristic compared to the damping element. This has the effect that the maximum stroke of the magnet armature can be precisely adjusted for high repeatability of the response behavior of the actuator arrangement.

[0020] According to a further preferred embodiment, the at least one damping element has a first extension dimension in the axial direction of the magnet armature, a second extension dimension in the circumferential direction of the magnet armature and a third extension dimension in the radial direction of the magnet armature, wherein a ratio of the first extension dimension (axial direction) to the second extension dimension (circumferential direction) lies in a range between approximately 1 and approximately 2 and a ratio of the first extension dimension (axial direction) to the third extension dimension (radial direction) lies in a range between approximately 1 and approximately 2. In other words, the at least one damping element is preferably as high as it is wide (in the circumferential direction and / or radial direction), but at most twice as high as it is wide (in the circumferential direction and / or radial direction).The relationship between these three extension dimensions ensures that the at least one damping element has a sufficiently large extension in the axial direction so as not to have an excessively hard force-displacement characteristic, but at the same time does not have an excessively large extension in the axial direction so as not to be bent instead of compressed when the magnet armature moves from the first position to the second position.

[0021] In a further preferred embodiment, the actuator arrangement further comprises at least one further damping element arranged on the second armature end face and extending from the second armature end face in the direction of the second housing wall, which damping element contacts the second housing wall both in the first position and in the second position of the magnet armature, wherein the at least one further damping element is arranged at a distance from the at least one damping element such that, at least in the first position of the magnet armature, a fluid channel for a fluid flowing radially along the second armature end face is formed between the at least one damping element and the at least one further damping element. This ensures, even with an additional damping element, that a sufficiently large fluid channel is formed for a fluid flowing radially along the second armature end face, at least in the first position.

[0022] In a particularly preferred embodiment, the at least one further damping element has the same extension dimensions in the radial, axial, and circumferential directions as the at least one damping element. Particularly preferably, the at least one damping element and the at least one further damping element also have the same radial distance from or to the axis along which the magnet armature is movable, in particular if the axis represents, for example, a central axis of a cylindrical, in particular circular-cylindrical, magnet armature.

[0023] If the actuator arrangement has at least one further damping element in addition to the at least one damping element, a size of the damping element end face formed by the at least one damping element and by the at least one further damping element as a whole should again be in a range between approximately 5% and approximately 50%, in particular in a range between approximately 10% and approximately 20% of the size of the second armature end face, in order to ensure the already mentioned soft force-displacement characteristic of the damping elements.

[0024] In a further preferred embodiment, the second housing wall is at least partially formed as an electromagnetic core. In this embodiment, the magnet armature would thus be drawn into the second position against the electromagnetic core, which serves as a stop for the magnet armature. It is particularly advantageous if the fluid opening of the second housing wall is also formed in the electromagnetic core. This could, for example, allow the nozzle seat for fluid communication with, for example, the ambient pressure to be formed directly in the electromagnetic core.

[0025] In a further embodiment, alternatively or additionally, the first housing wall can have a fluid opening extending through the first housing wall, and the actuator arrangement can further have a sealing element arranged on the first armature end face and extending from the first armature end face in the direction of the first housing wall, which sealing element, in the first position of the magnet armature, makes fluid-tight contact with a sealing seat of the fluid opening arranged on the first housing wall. If both the first housing wall and the second housing wall each have a fluid opening, then it would be possible, for example, to control the filling of a fluid chamber or fluid bladder with a fluid located in a fluid source, or to vent the fluid chamber or fluid bladder filled with the fluid.

[0026] It is particularly advantageous if both the at least one damping element and the at least one stop element as well as the sealing element are formed from the same elastomeric material, since this in turn enables a cost-effective and time-saving production of the actuator arrangement.

[0027] Finally, in a further preferred embodiment, the actuator assembly further comprises a reset element designed to bias the magnet armature into the first position when not actuated, i.e., when electromagnetically deactivated. This can create, for example, an NO valve (normally open) or an NC valve (normally closed).

[0028] Further features and objects of the present invention will become apparent to those skilled in the art upon application of the present teachings and upon consideration of the accompanying drawings. Fig. 1 a schematic view of an embodiment of an actuator arrangement according to the invention with a magnet armature shown in a first position, Fig. 2 a schematic view of an embodiment of an actuator arrangement according to the invention, wherein the magnet armature is shown in a second position, Fig. 3 a schematic detailed view of an embodiment of an actuator arrangement according to the invention in side view, top view and sectional view, Fig. 4 a schematic detailed view of another embodiment of an actuator arrangement according to the invention in side view, top view and sectional view, Fig. 5 an enlarged schematic detail view of the actuator arrangement of Fig. 4 in side view and top view, Fig. 6 a schematic view of an embodiment of an actuator arrangement according to the invention in a 3 / 2 NO valve for a pneumatic adjustment device of a vehicle seat, showing a venting state, Fig. 7 a schematic view of the actuator arrangement of Fig. 6, showing a filling state, Fig. 8 is a schematic view of an embodiment of an actuator arrangement according to the invention in a 3 / 3 NO valve for a pneumatic adjustment device of a vehicle seat, showing a venting state, Fig. 9 a schematic view of the actuator arrangement of Fig. 8, showing a filling state, Fig. 10 is a schematic view of an embodiment of an actuator arrangement according to the invention in a 3 / 3 NC valve for a pneumatic adjustment device of a vehicle seat, showing a filling state, and Fig. 11 a schematic view of the actuator arrangement of Fig. 10, showing a venting state.

[0029] Elements of the same construction or function are provided with the same reference symbols throughout the figures.

[0030] It is initially Fig. 1, which shows a schematic view of an actuator assembly 10 according to the invention in simplified form. The actuator assembly 10 has a housing with a first housing wall 12 and a second housing wall 14 opposite the first housing wall 12. A magnet armature 16 is arranged within the housing between the first housing wall 12 and the second housing wall 14. In the specific example of Fig. 1, the magnetic armature 16 is shown as a cylindrical armature, in particular a circular cylindrical armature, but may have other configurations in other embodiments not shown.

[0031] The magnet armature 16 is axially movable between a first position and a second position along an axis 18 between the first housing wall 12 and the second housing wall 14. In Fig. 1, the magnet armature 16 is shown in a first position and in Fig. 2 the magnet armature 16 is shown in the second position.

[0032] The magnet armature 16 has a first axial armature face 20, which is substantially perpendicular to the axis 18, and a second axial armature face 22 opposite the first axial armature face 20, which is also substantially perpendicular to the axis 18. The first axial armature face 20 faces the first housing wall 12, and the second axial armature face 22 faces the second housing wall 14.

[0033] As in Fig. 1, in the first position of the magnet armature 16, the first armature face 20 contacts the first housing wall 12. As shown in Fig. 2, in the second position of the magnet armature 16, the first armature end face 20 is detached from the first housing wall 12.

[0034] As further stated in the Fig. 1 and Fig. 2, the second armature end face 22, i.e. the armature end face facing the second housing wall 14, has a damping element 24 arranged on the second armature end face 22 and extending from it in the direction of the second housing wall 14. In the specific example of Fig. 1 and Fig. 2, the damping element 24 has a first damping element 24A and a second damping element 24B, but in other embodiments not shown, it can also have more or fewer damping elements. In addition to the damping elements 24A, 24B, the second axial armature end face 22 also has a stop element 26. Both the damping elements 24A, 24B and the stop element 26 are made of an elastomeric material such as EPDM or silicone and can, for example, be injection-molded onto the second armature end face 22.

[0035] As a comparison of Fig. 1 with Fig. 2 shows, the damping elements 24A, 24B contact the second housing wall 14 both in the first position and in the second position of the magnet armature 16. In contrast, the stop element 26 contacts the second housing wall 40 only in the second position of the magnet armature 16 (see Fig. 2). When the magnet armature 16 moves from the first position to the second position, there is therefore no free-flight phase for the magnet armature 16. Instead, when the magnet armature 16 moves from the first position to the second position, the elastomeric damping elements 24A, 24B are compressed, thereby damping the movement of the magnet armature 16, in particular absorbing energy. The use of the elastomeric material also leads to a progressive spring characteristic, i.e., the spring characteristic of the damping elements 24A, 24B increases over the armature's travel path by a similar amount or more than the magnetic force, thus preventing the magnet armature 16 from traveling at high speed during the switching operation. In this context, it is advantageous if the magnetic field for actuating the actuator arrangement 10 is built up via a time ramp when the power supply is switched on and is also reduced via a time ramp when the power supply is switched off.This ensures a force balance at all times between the progressive spring characteristic of the damping elements 24, 24B and any return element used, on the one hand, and the magnetic force, on the other. Together with the absence of a free-flight phase of the magnet armature 16, this results in a low movement speed of the magnet armature 16 and thus in an overall very low noise level when moving the magnet armature 16 from the first position to the second position, as well as when moving the magnet armature 16 from the second position to the first position.

[0036] It is now on Fig. 3, which shows a schematic detailed view of the actuator arrangement 10 in side view, top view and sectional view.

[0037] In this specific example, the magnet armature 16 is also depicted as a circular cylindrical armature. In other embodiments not shown, the magnet armature 16 may, of course, have other configurations.

[0038] As in Fig. 3, the damping elements 24A, 24B have an axial extension 28 in the direction of the axis 18. This axial extension 28 is greater than an axial extension 29 of the stop element 26. In other words, the damping elements 24A, 24B project more in the direction of the second housing wall 14 than the stop element 26, at least in the first position of the magnet armature 16. A difference between the axial extension 28 of the damping elements 24A, 24B and the axial extension 29 of the stop element 26 is dimensioned such that the difference between the axial extensions 28, 29 lies essentially in the range of a stroke of the magnet armature 16, wherein the stroke of the magnet armature 16 describes the actuating path traveled by it during the movement from the first position to the second position.This ensures that, firstly, a free-flying phase of the magnet armature 16 is avoided and, secondly, that there is no unnecessary pre-compression of the damping elements 24A, 24B in the first position of the magnet armature 16.

[0039] As further stated in Fig. 3, the stop element 26 is in the position shown in Fig. 3 is further designed as a circular disk, ie the stop element 26 extends by 360° in the circumferential direction of the axis 18. In such a configuration, the stop element 26 can serve in the second position of the magnet armature 16 as a sealing element for sealing a fluid opening present in the second housing wall 14, as described in more detail, for example, in connection with Fig. 6 and Fig. 7 is described.

[0040] It is now on Fig. 4, which shows a further embodiment of the actuator assembly 10. In contrast to Fig. 3 is in Fig. 4 the stop element 30 is not designed as a circular disk extending 360° in the circumferential direction, but as two stop elements 30A and 30B, which in the concrete example of Fig. 4 are essentially opposite each other. The stop elements 30A, 30B also extend only over a comparatively small angular range in the circumferential direction of the axis 18, so that a fluid channel 32 is formed between the stop elements 30A, 30B and the damping elements 24A, 24B. The damping element 24A and the further damping element 24B are also arranged at a distance from one another (and from the stop elements 30A, 30B) such that fluid channels 32 are present both in the first position and in the second position of the magnet armature 16. By designing and arranging the elements 24A, 24B, 30A, 30B at a distance from one another and from one another such that fluid channels 32 are present, a flow of fluid over the second armature end face 22 is made possible.The elements 24A, 24B, 30A, 30B can further be designed and arranged spaced apart from one another and from one another in such a way that the flow of fluid over the second armature end face 22 is ensured both in the first position and in the second position of the magnet armature 16, as for example in connection with . Fig. 8 and Fig. 9 is explained in more detail.

[0041] It is now on Fig. 5, which shows an enlarged schematic detail view of the actuator arrangement 10 of Fig. 4 in side view and top view, where in Fig. 5 the magnet armature 16 is shown in the first position.

[0042] As in Fig. 5, in the first position of the magnet armature 16, an extension 34 of the stop element 30A or 30B in the circumferential direction of the axis 18 is more than twice as large as an extension 36 of the damping element 24A or 24B in the circumferential direction of the axis 18. In other words, the stop elements 30A, 30B are more than twice as wide as the damping elements 24A, 24B. Because the stop elements 30A, 30B are more than twice as wide as the damping elements 24A, 24B, the stop elements 30A, 30B have a comparatively harder force-displacement characteristic than the narrower damping elements 24A, 24B compared to the damping elements 24A, 24B.

[0043] In addition, a total axial damping element end face 38 of the damping elements 24A, 24B, which corresponds to the sum of the axial damping element end faces 38A, 38B of the respective damping elements 24A, 24B, is in a range between approximately 5% and approximately 50%, in particular in a range between approximately 10% and approximately 20%, of the size of the second armature end face 22. The axial damping element end face 38 thus occupies a comparatively small proportion of the second armature end face 22, whereby a particularly soft force-displacement characteristic is achieved for the damping elements 24A, 24B.

[0044] In addition, the damping elements 24A, 24B have a first extension or a first extension dimension 28 in the axial direction of the magnet armature 16, a second extension or a second extension dimension 36 in the circumferential direction of the magnet armature 16, and a third extension or a third extension dimension 40 in the radial direction of the magnet armature 16. A ratio of the first extension dimension 28 to the second extension dimension 36 is selected such that this ratio is in a range between approximately 1 and 2. Furthermore, a ratio of the first extension dimension 28 to the third extension dimension 40 is selected such that this ratio is in a range between approximately 1 and approximately 2. In other words, the damping elements 24A, 24B each have a shape that is approximately the same height as it is wide (seen in the circumferential and / or radial direction), but at most twice as high as it is wide (seen in the circumferential and / or radial direction).Such a shape ensures that the damping elements 24A, 24B have a sufficient height to avoid excessively harsh force-displacement characteristics, but at the same time are not too high to prevent them from being bent during the movement of the magnet armature 16 from the first position to the second position. It is not essential to the invention that the extension dimensions of the damping elements 24A, 24B be equal in the circumferential and radial directions.

[0045] It is now on Fig. 6 and Fig. 7, which shows a schematic view of the actuator assembly 10 in an electromagnetically actuated 3 / 2 NO valve 42. The designation "3 / 2 NO valve" means that this valve has three ports and two positions and is open in an inactive (de-energized) state (NO = normally open).

[0046] In the specific example of Fig. 6 and Fig. 7, the 3 / 2 NO valve 42 is part of a pneumatic adjustment device 43. This pneumatic adjustment device 43 is used to adjust a seat contact surface 44 of a vehicle seat 45 by means of a fluid bladder or fluid chamber 46 that can be filled with a fluid by filling or emptying the fluid bladder 46. Fig. 6 shows the 3 / 2 NO valve 42 in a de-energized state in which the fluid bladder 46 is vented or emptied. Fig. 7 shows the 3 / 2 NO valve 42 in an active state in which the fluid bladder 46 is filled.

[0047] It is now on Fig. 6, in which the 3 / 2 NO valve 42 is shown in a de-energized state. In this de-energized state, the magnet armature 16 is in the first position, in which the first armature face 20 contacts the first housing wall 12. The first housing wall 12 is in the specific example of Fig. 6 is designed such that it has a fluid opening 48 extending through the first housing wall 12, which is fluidly connected via a corresponding fluid connection to a fluid source 50 of the pneumatic adjusting device 43. In the first position of the magnet armature 16, the fluid opening 48 located in the first housing wall 12 is also closed in a fluid-tight manner by means of a sealing element 52 provided on the first armature end face 20 and specially designed for this purpose. For this purpose, the sealing element 52 is arranged on the first armature end face 20 and extends in the direction of the first housing wall 12, so that the magnet armature 16, in its first position, can make fluid-tight contact with a sealing seat of the fluid opening 48 by means of the sealing element 52 and thus fluidly close the fluid opening 48. In other words, in the first position of the magnet armature 16, an inflow of fluid from the fluid opening 48 into a valve chamber of the valve 42 is prevented.

[0048] On the second armature face 22 opposite the first armature face 20 are the already mentioned damping elements 24A and 24B, as well as the stop element 26. The stop element 26 is in the design of Fig. 6 and Fig. 7 is designed as a circular disk extending 360° in the circumferential direction of the magnet armature 16, as described in more detail in connection with Fig. 3. In addition, the second housing wall 14 is designed as a magnetic armature 54 and additionally has a fluid opening 56 extending in the second housing wall 14 or the magnetic armature 54, which is fluidly connected to the surroundings of the valve 42.

[0049] As further stated in Fig. 6, the first housing wall 12 also has a non-controllable fluid opening 58, which is fluidly connected to the fluid bladder 46 via a corresponding fluid connection. The non-controllable fluid opening 58 represents a non-controllable fluid connection to the valve chamber of the valve 42. Since the damping elements 24A and 24B also only make up a small proportion of the total size of the second armature end face 22, it is possible for fluid flowing from the fluid bladder 46 through the non-controllable fluid opening 48 to flow into the valve chamber of the valve 42 and from there radially over the second armature end face 22 and through the fluid opening 56 into the surroundings of the valve 42. In other words, the fluid bladder 46 can be emptied or ventilated in the first position of the magnet armature 16 by means of the fluid opening 56.

[0050] As already mentioned, the solenoid armature 16 is in the first position when the valve 42 is de-energized. For this purpose, the solenoid armature 16 is preloaded into the first position by means of a specially designed reset element 60.

[0051] The valve 42 now comprises, in addition to the magnet armature 16 and electromagnetic core 54 belonging to the actuator arrangement 10, also a magnetic coil 62 and a yoke 64. If the valve 42 is now energized, the magnet armature 16 moves in a manner known to the person skilled in the art from the position shown in Fig. 6 shown first position in the direction of the electromagnetic core 54, until the magnet armature 16 is finally in the position shown in Fig. 7 shown second position.

[0052] In the second position of the magnet armature 16, the second armature end face 20 and in particular the sealing element 52 are detached from the first housing wall 12. At the same time, not only the two damping elements 24A and 24B but also the stop element 26, designed as a circular disk, are in contact with the second housing wall 14 on the second armature end face 22. Since the stop element 26 is designed as a sealing element, in the second position of the magnet armature 16, the stop element 26 can make fluid-tight contact with a sealing seat of the fluid opening 56 and thus prevent fluid from flowing through the fluid opening 56.

[0053] At the same time, however, in the second position of the magnet armature 16, the fluid opening 48 of the first housing wall 12 is open, so that a fluid located in the fluid source 50 can flow into the fluid bladder 46 via the corresponding fluid connection, the fluid opening 48, and the non-controllable fluid opening 58. In other words, in the second position of the magnet armature 16, the fluid bladder 46 can be filled with fluid.

[0054] The Fig. 6 and Fig. The configuration of the actuator arrangement 10 in the 3 / 2 NO valve 42 shown in Fig. 7 thus enables filling and emptying of the fluid bladder 46, wherein the special configuration of the actuator arrangement 10 achieves a reduced switching noise when moving the magnet armature 16 from the first position to the second position or when moving the magnet armature 16 from the second position to the first position.

[0055] It is now on Fig. 8 and Fig. 9, which shows the application of the actuator arrangement described so far in another electromagnetically actuated valve. In the specific example of Fig. 8 and Fig. 9, two actuator assemblies 10 are used in a 3 / 3 NO valve 66. The designation "3 / 3 NO valve" means that this valve has three ports and three positions and is open in an inactive (de-energized) state (NO = normally open).

[0056] In the specific example of Fig. 8 and Fig. 9, the 3 / 3 NO valve 66 is part of a pneumatic adjustment device 68. This pneumatic adjustment device 68 is used to adjust the seat support surface 44 of the vehicle seat 45 by means of the fluid bladder 46, which can be filled with a fluid, by filling or emptying the fluid bladder 46. Furthermore, the pressure in the fluid bladder 46 can be maintained by means of the 3 / 3 NO valve 66. Fig. 8 shows the 3 / 3 NO valve 68 in a de-energized state in which the fluid bladder 46 is vented or emptied. Fig. Figure 9 shows the 3 / 3 NO valve 68 in an active state, filling the fluid bladder 46. The pressure holding state is not shown but will be explained.

[0057] The 3 / 3 NO valve 66 is essentially composed of two 2 / 2 valves, each having an actuator assembly 10 with a movable magnet armature 16, as well as an electromagnetic core 54, a magnet coil 62 and a yoke 64. The right 2 / 2 NO valve is largely identical in construction to the 3 / 2 NO valve used in conjunction with Fig. 6 and Fig. 7. This means that the right 2 / 2 NO valve has the magnet armature 16 with the damping elements 24A and 24B present on the second armature face 22 as well as the stop element 26 designed as a sealing element. Only the first housing wall 12 of the right 2 / 2 NO valve does not have any damping elements as described in connection with Fig. 6, but only has the non-controllable fluid opening 58. However, the non-controllable fluid opening 58 of the right 2 / 2 NO valve is connected to the pressure chamber of the left 2 / 2 NC valve. The left 2 / 2 NC valve, in turn, has an actuator arrangement 10, wherein the first housing wall 12 is now fluidly connected to the fluid source 50 via a corresponding fluid connection, and the second housing wall 14 is fluidly connected to the fluid bladder 46 via a fluid opening 70.

[0058] In contrast to the right magnet armature 16, the left magnet armature 16 also has on its second armature end face 22, in addition to the damping elements 24A and 24B, a stop element 30 which is designed as spaced-apart stop elements 30A, 30B, as described in connection with Fig. 4 and Fig. 5 was described.

[0059] Both the right magnet armature 16 and the left magnet armature 16 are movable between a first position and a second position. Fig. 8, the right magnetic armature 16 is shown in the first position and the left magnetic armature 16 is also shown in the first position.

[0060] In the first position of the right magnet armature 16, the damping elements 24A and 24B touch the second housing wall 14 of the right actuator assembly 10. Likewise, in the first position of the left magnet armature 16, the damping elements 24A and 24B touch the second housing wall 14 of the left actuator assembly 10. Furthermore, the damping elements 24A, 24B and the stop elements 30A, 30B of the left actuator assembly 10 are arranged at a distance from one another such that a radial flow is possible on the second armature end face 22 of the left magnet armature 16. This has the consequence that a fluid located in the fluid bubble 46 can flow through the fluid opening 70 and radially over the second armature end face 22 of the left magnet armature 16. From there, the fluid can flow further through the non-controllable fluid opening 58 into the valve chamber of the right 2 / 2 NO valve and from there through the fluid opening 56 into the environment.In other words, the fluid bladder 46 can be moved over the area shown in . Fig. 8 shown 3 / 3 NO valve 66 can be emptied or vented.

[0061] If the 3 / 3 NO valve 66 is now energized accordingly, the right-hand armature 16 moves from the first position to the second position, counter to the restoring force of the right-hand return element 60. In the second position, the right-hand stop element 26, designed as a sealing element, contacts a sealing seat of the fluid opening 56, thus interrupting fluid communication with the environment. Furthermore, if the 3 / 3 NO valve 66 is energized accordingly, the left-hand armature 16 is moved from the first position to the second position, counter to the restoring force of the left-hand return element 60. In the second position, in addition to the damping elements 24A, 24B, the stop elements 30A, 30B also contact the second housing wall 14, designed as an electromagnetic core 54, of the left-hand actuator arrangement 10.However, the damping elements 24A, 24B and the stop elements 30A, 30B are arranged at a distance from one another such that fluid flow through the fluid opening 70 is also possible in the second position of the left magnet armature 16. Since, in the second position of the left magnet armature 16, the first housing wall 12 is no longer in contact, fluid can flow from the fluid source 50 via the fluid opening 70 into the fluid bladder 46 (but not via the fluid opening 56 into the environment). In other words, in the position shown in . Fig. 9, the fluid bladder 46 can be filled with fluid.

[0062] If, as mentioned above, the pressure in the fluid bladder 46 is to be maintained, the 3 / 3 NO valve 66 simply needs to be energized in such a way that the left armature 16 is moved from the second position back to the first position. This interrupts the fluid connection to the fluid source 50 by means of the sealing element 52 of the left armature 16. At the same time, the right armature 16 remains in the second position, in which the fluid connection to the environment is also interrupted.

[0063] The Fig. 8 and Fig. The actuator arrangements 10 shown in Fig. 9 thus enable filling and emptying of the fluid bladder 46 in the 3 / 3 NO valve 66 as well as maintaining the pressure of the fluid bladder 46. However, due to the respective damping elements 24A, 24B present and the absence of free-flight phases of the magnet armatures 16, the switching noises of the 3 / 3 NO valve 66 are significantly reduced.

[0064] After all, it is Fig. 10 and 11, which shows the application of the actuator arrangement described so far in another electromagnetically actuated valve. In the specific example of Fig. 10 and Fig. 11, two actuator assemblies 10 are used in a 3 / 3 NC valve 72. The designation "3 / 3 NC valve" means that this valve has three ports and three positions and is closed in an inactive (de-energized) state (NC = normally closed).

[0065] In the specific example of Fig. 10 and Fig. 11, the 3 / 3 NC valve 72 is part of a pneumatic adjustment device 74. This pneumatic adjustment device 74 is used to adjust the seat support surface 44 of the vehicle seat 45 by filling or emptying the fluid bladder 46, which can be filled with a fluid. Furthermore, the pressure in the fluid bladder 46 can be maintained by means of the 3 / 3 NC valve 74. Fig. 10 shows the 3 / 3 NC valve 72 in a de-energized state in which the fluid bladder 46 is filled. Fig. Figure 11 shows the 3 / 3 NC valve 72 in an active state, in which the fluid bladder 46 is vented or emptied. The pressure-holding state is not shown but will be explained.

[0066] The 3 / 3 NC valve 72 is essentially composed of two 2 / 2 NC valves, each having an actuator assembly 10 with a movable magnet armature 16, as well as an electromagnetic core 54, a magnet coil 62 and a yoke 64. The left 2 / 2 NC valve is similar to the left 2 / 2 NC valve used in connection with Fig. 8 and Fig. 9. However, the first housing wall 12 of the left actuator assembly 10 has a fluid opening 76 which is not as in Fig. 8 and Fig. 9 is not connected to the fluid source 50, but to the environment. The first armature end face 20 has a sealing element 52, which closes the fluid opening 76 in a fluid-tight manner in the first position of the left armature 16. The second armature end face 22 has damping elements 24A, 24B and stop elements 30A, 30B, which allow a radial flow over the second armature end face 22 in both the first and the second position of the left armature 16. Furthermore (as in the embodiment of Fig. 8 and Fig. 9) The second housing wall 14 of the left actuator assembly 10 is designed as an electromagnetic core 54 with a fluid opening 70 extending therethrough. The fluid opening 70, in turn, establishes the fluid connection to the fluid bladder 46. The first housing wall 12 of the left actuator assembly 10 also has the non-controllable fluid opening 58, which ensures a fluid connection between the valve chamber of the left 2 / 2 NC valve and the valve chamber of the right 2 / 2 NC valve.

[0067] In the right actuator arrangement 10 of the right 2 / 2 NC valve, the first housing wall 12 is again formed with a fluid opening 48, similar to the design of Fig. 6 and Fig. 7. The first armature end face 20 of the right-hand magnet armature 16 is also formed with a sealing element 52 to close the fluid opening 48 in a fluid-tight manner. The second housing wall 14 is formed as an electromagnetic core 54. However, the second housing wall 14 or the core 54 does not have a fluid opening. However, the second armature end face 22 of the right-hand magnet armature 16 in turn has the damping elements 24A, 24B and either a stop element 26 with the design of Fig. 3 or a stop element 30 with the design of Fig. 4 and Fig. 5 on.

[0068] As in Fig. 10, the right-hand armature 16 is in the second position, in which the damping elements 24A, 24B and the stop element (26 or 30, depending on the design) contact the second housing wall 14. As a result, the sealing element 52 of the first armature end face 20 is detached from the first housing wall 12 of the right-hand actuator arrangement 10. Thus, fluid can flow in from the fluid source 50 via the fluid opening 48. From there, fluid can flow further through the non-controllable fluid opening 58 into the valve chamber of the left 2 / 2 NC valve. The left-hand armature 16 is in the Fig. 10, however, in the first position, so that the sealing element 52 of the left magnet armature 16 closes the fluid opening 76 and a fluid connection to the environment is interrupted. However, fluid can flow radially over the second armature end face 22 of the left magnet armature 16 and from there via the fluid opening 70 into the fluid bladder 46. In other words, the fluid bladder 46 can be filled via the 3 / 3 NC valve 72 in the Fig. 10 shown position.

[0069] If the fluid bladder 46 is now to be vented, the 3 / 3 NC valve 72 must be energized such that the left armature 16 moves from the first position to the second position and the right armature 16 moves from the second position to the first position. When the right armature 16 is in the first position, the inflow of fluid from the fluid source 50 is blocked. If the left armature 16 is also in the second position, the fluid opening 76 is opened because the sealing element 52 of the left armature 16 no longer closes the fluid opening 76. Since the damping elements 24A, 24B and the stop elements 30A, 30B are arranged at a distance from one another such that a fluid flow through the fluid opening 70 is also possible in the second position of the left magnet armature 16, fluid can flow from the fluid bladder 46 through the fluid opening 76 into the environment. In other words, in the Fig. 11 shown position of the 3 / 3 NC valve 72, the fluid bladder 46 can be emptied or vented.

[0070] If, as mentioned above, the pressure in the fluid bladder 46 is also to be maintained, the 3 / 3 NC valve 72 simply needs to be energized or de-energized in such a way that the left magnet armature 16 is moved from the second position back to the first position. This interrupts the fluid connection to the environment by means of the sealing element 52 of the left magnet armature 16. At the same time, the right magnet armature 16 must remain in the first position so that the fluid connection to the fluid source 50 is interrupted.

[0071] The Fig. 10 and Fig.The actuator arrangements 10 shown in Fig. 11 thus enable filling and emptying of the fluid bladder 46 in the 3 / 3 NC valve 72 as well as maintaining the pressure of the fluid bladder 46. However, due to the respective damping elements 24A, 24B present and the absence of free-flight phases of the magnet armatures 16, the switching noises of the 3 / 3 NC valve 72 are significantly reduced.

[0072] Further arrangements of the actuator arrangements 10 in corresponding designs are conceivable in order to obtain further valves suitable for the respective application.

Claims

[1] Actuator arrangement (10) for an electromagnetically actuated valve (42, 66, 72), comprising: - a housing with a first housing wall (12) and a second housing wall (14) opposite the first housing wall (12), - a magnetic armature (16) arranged in the housing between the first housing wall (12) and the second housing wall (14), which is movable between the first housing wall (12) and the second housing wall (14) along an axis (18), wherein the magnetic armature (16) has a first axial armature end face (20) facing the first housing wall (12) and a second axial armature end face (22) facing the second housing wall (14), and the magnetic armature (16) is movable between a first position in which the first armature end face (20) contacts the first housing wall (12) and a second position in which the first armature end face (20) is detached from the first housing wall (12), - at least one damping element (24, 24A, 24B) made of an elastomeric material arranged on the second armature end face (22) and extending from the second armature end face (22) in the direction of the second housing wall (14), wherein the at least one damping element (24, 24A, 24B) contacts the second housing wall (14) both in the first position and in the second position of the magnet armature (16), and - a stop element (26) made of an elastomeric material, arranged on the second armature end face (22) and extending from the second armature end face (22) in the direction of the second housing wall (14), which stop element is detached from the second housing wall (14) in the first position of the magnet armature (16) and contacts the second housing wall (14) in the second position of the magnet armature (16), - wherein the second housing wall (14) has a fluid opening (56) extending through the second housing wall (14) and the stop element (26) in the second position of the magnet armature (16) contacts a sealing seat of the fluid opening (56) in a fluid-tight manner. [2] Actuator assembly (10) according to claim 1, wherein the at least one damping element (24, 24A, 24B) and the at least one stop element (26, 30, 30A, 30B) are formed from the same elastomeric material. [3] Actuator arrangement (10) according to claim 1 or 2, wherein in the first position of the magnet armature (16) an axial extension (28) of the at least one damping element (24, 24A, 24B) is greater than an axial extension (29) of the at least one stop element (26, 30, 30A, 30B). [4] Actuator arrangement (10) according to claim 3, wherein a difference between the axial extent (29) of the at least one stop element (26, 30, 30A, 30B) and the axial extent of the at least one damping element (24, 24A, 24B) is substantially in the range of a stroke of the magnet armature (16) [5] Actuator arrangement (10) according to one of claims 1 to 4, wherein the at least one damping element (24, 24A, 24B) has an axial damping element end face (38) and a size of the at least one damping element end face (38) is in a range between approximately 5% and approximately 50% of a size of the second armature end face (22). [6] Actuator assembly (10) according to claim 5, wherein the size of the at least one damping element end face (38) is in a range between approximately 10% and approximately 20% of the size of the second armature end face (22). [7] Actuator arrangement (10) according to one of claims 1 to 6, wherein in the first position of the magnet armature (16) an extension (34) of the at least one stop element (30, 30A, 30B) in the circumferential direction of the magnet armature (16) is at least twice as large as an extension (36) of the at least one damping element (24, 24A, 24B) in the circumferential direction of the magnet armature (16). [8] Actuator arrangement (10) according to one of claims 1 to 7, wherein the at least one damping element (24, 24A, 24B) has a first extension dimension (28) in the axial direction of the magnet armature (16), a second extension dimension (36) in the circumferential direction of the magnet armature (16) and a third extension dimension (40) in the radial direction of the magnet armature (16), and a ratio of the first extension dimension (28) to the second extension dimension (36) is in a range between approximately 1 and approximately 2, and a ratio of the first extension dimension (28) to the third extension dimension (40) is in a range between approximately 1 and approximately 2. [9] Actuator arrangement (10) according to one of claims 1 to 8, further comprising: - at least one further damping element (24B) arranged on the second armature end face (22) and extending from the second armature end face (22) in the direction of the second housing wall (14), which makes contact with the second housing wall (14) both in the first position and in the second position of the magnet armature (16), wherein the at least one further damping element (24B) is arranged at a distance from the at least one damping element (24A) such that, at least in the first position of the magnet armature (16), a fluid channel (32) for a fluid flowing radially on the second armature end face (22) is formed between the at least one damping element (24A) and the at least one further damping element (24B). [10] Actuator arrangement (10) according to claim 9, wherein the at least one damping element (24A) and the at least one further damping element (24B) have an equal radial distance from the axis (18). [11] Actuator arrangement (10) according to one of claims 1 to 10, wherein the second housing wall (14) is at least partially formed as an electromagnetic core (54). [12] Actuator assembly (10) according to one of claims 1 to 11, wherein the first housing wall (12) has a fluid opening (48) extending through the first housing wall (12) and the actuator assembly (10) further comprises: - a sealing element (52) arranged on the first armature end face (20) and extending from the first armature end face (20) in the direction of the first housing wall (12), which sealing element (52) in the first position of the magnet armature (16) makes fluid-tight contact with a sealing seat of the fluid opening (48) arranged on the first housing wall (12). [13] Actuator assembly (10) according to claim 12, wherein the sealing element (52), the at least one damping element (24, 24A, 24B) and the at least one stop element (26, 30, 30A, 30B) are formed from the same elastomeric material. [14] Actuator arrangement (10) according to one of the preceding claims, wherein the actuator arrangement (10) further comprises a return element (60) which is designed to preload the magnet armature (16) in the first position when not actuated.

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