ACTUATOR ASSEMBLY FOR AN ELECTROMAGNETICALLY ACTUATABLE VALVE

An actuator arrangement for an electromagnetically actuatable valve comprises a housing having a first wall, and a second wall situated opposite the first wall, a solenoid armature, with first and second axial armature end surfaces facing toward the first and second housing walls respectively, movable along an axis between a first position, where the first end surface makes contact with the first wall, and a second position, where the first end surface is away from the first wall. A damping element of an elastomer material extends from the second end surface toward the second wall and contacts the second wall in the first and second positions of the solenoid armature, A stop element of an elastomer material extends from the second end surface toward the second wall and, in the first position, is away from the second wall and, in the second position, contacts the second wall.

The present invention relates to an actuator arrangement for an electromagnetically actuatable valve. The actuator arrangement may be used in particular for a pneumatic adjusting device of a vehicle seat.

In modern vehicle seats, fluid chambers or fluid bladders which can be filled with a pressure medium, in particular with a gaseous pressure medium such as compressed air, are situated as control elements in the region of the seat face or backrest (together also referred to as seat contact face). Such fluid chambers can be supplied with the pressure medium via a respective pressure medium line. The volume of said fluid chambers is increased by filling a respective fluid chamber with pressure medium, or decreased by emptying said fluid chamber, respectively, such that the properties of the seat contact face, in particular the contour of the latter, can be varied. For the filling of the respective fluid chamber with pressure medium, the pressure medium is firstly generated by a pressure medium source, for example by a compressor or a compressor unit, and guided via a suitable valve to a respective fluid chamber in controlled fashion.

Electromagnetic valves are commonly used for this purpose, which are actuated by an actuator arrangement. A disadvantage of such actuator arrangements is however the relatively loud switching noise. This is because, as soon as the solenoid armature is set in motion when sufficiently electrically energized, the air gap between the solenoid armature and the electromagnetic core decreases. The magnetic force thus increases overproportionately with the travel covered by the solenoid armature. In the case of an only linear increase of a restoring-spring-imparted spring force that counteracts the movement of the solenoid armature, this leads to a high speed of the solenoid armature, which is abruptly braked only when the solenoid armature strikes the oppositely situated stop (for example an electromagnetic core). The consequence is a loud “click” of the valve.

It is therefore an object of the present invention to provide an actuator arrangement for an electromagnetically actuatable valve, which is distinguished by reduced generation of noise or by a reduced switching noise.

This object is achieved by means of an actuator arrangement according to patent claim 1. Advantageous refinements are the subject matter of the dependent claims.

The actuator arrangement according to the invention comprises a housing having a first housing wall and having a second housing wall situated opposite the first housing wall, and a solenoid armature which is arranged in the housing between the first housing wall and the second housing wall. Here, the solenoid armature is movable between the first housing wall and the second housing wall along an axis. Preferably, the solenoid armature is a cylindrical, in particular circular cylindrical, solenoid actuator, and comprises a first axial end surface, which faces toward the first housing wall, and a second axial end surface, which is situated opposite the first axial end surface and which faces toward the second housing wall. The term “axial armature end surface” means that the armature end surfaces of the solenoid armature run perpendicular to the axis along which the solenoid actuator is movable. The solenoid armature is movable between a first position, in which the first armature end surface makes contact with the first housing wall, and a second position, in which the first armature end surface has been moved away from the first housing wall.

The actuator arrangement according to the invention furthermore comprises at least one damping element which is arranged on the second armature end surface and which extends from the second armature end surface in the direction of the second housing wall and which is composed of an elastomer material, wherein the at least one damping element makes contact with the second housing wall both in the first position and in the second position of the solenoid armature, and at least one stop element which is arranged on the second armature end surface and which extends from the second armature end surface in the direction of the second housing wall (and which differs from the at least one damping element) and which is composed of an elastomer material and which, in the first position of the solenoid armature, has been moved away from the second housing and, in the second position of the solenoid armature, makes contact with the second housing wall.

By virtue of the fact that 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 solenoid armature, no free-flight phase of the solenoid armature occurs during movement from the first position into the second position. Rather, the solenoid armature is continuously in contact with the second housing wall via the at least one damping element, whereby a generation of noise by the actuator arrangement is noticeably reduced. It is furthermore the case that the at least one damping element is formed from an elastomer material, such that the at least one damping element is compressed during the movement of the solenoid armature from the first position into the second position. The compression leads to a damped movement of the solenoid armature from the first position into the second position, whereby a generation of noise is further reduced. The elastomer material is in particular selected such that a progressive spring characteristic, which dampens the movement of the solenoid armature (and which in particular absorbs energy), is achieved. As elastomer material, use may for example be made of elastomer EPDM or silicone. It is furthermore also the case that the at least one stop element, which makes contact with the second housing wall only in the second position of the solenoid armature, is likewise formed from an elastomer material. The at least one stop element serves as a stop for the movement of the solenoid armature from the first position into the second position, and is likewise compressed when it strikes the second housing wall. All of this contributes to a situation in which the actuator arrangement has a relatively low switching noise, and thus, in particular in pneumatic adjusting devices of vehicle seats, in which the actuator arrangement is generally arranged very close to the vehicle occupant, does not contribute to an unnecessary generation of noise.

It is particularly advantageous if the at least one damping element and the at least one stop element are formed from the same elastomer material. It is thus possible to achieve inexpensive production of the actuator arrangement, in particular because both the at least one damping element and the at least one stop element can be applied to the second armature end surface in one common working step using the same elastomer material. This may for example be performed by virtue of both elements being injection-molded onto the second armature end surface.

In a further preferred refinement, in the first position of the solenoid 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 solenoid armature, the at least one damping element projects further than the at least one stop element in the direction of the second housing wall. Here, the at least one stop element may be of virtually planar form on the second armature end surface, such that the at least one stop element virtually does not project from the second armature end surface. Preferably, however, the at least one stop element will also project in the direction of the second housing wall or protrude from the second armature end surface in the direction of the second housing wall. By virtue of the fact that the at least one damping element projects further than the at least one stop element in the direction of the second housing wall, it is not necessary for the second housing wall to be provided with projections that are specially configured for the damping element and the stop element.

It is particularly advantageous if, furthermore, a difference (in terms of magnitude) 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 solenoid armature. The stroke of the solenoid armature describes the actuating travel covered by the solenoid armature during its movement from the first to the second position. It is ensured by means of this refinement that, on the one hand, the damping element already bears against the second housing wall in the first position and, furthermore, virtually no compression acts on the damping element in the first position of the solenoid armature. In this way, unnecessary pre-compression of the at least one damping element in the first position of the solenoid armature is reduced, whereby the material wear of the at least one damping element is reduced, and the service life or durability of the at least one damping element is increased.

According to a further preferred refinement, the second housing wall has a fluid opening which extends through the second housing wall, and the at least one stop element, in the second position of the solenoid armature, makes fluid-tight contact with a sealing seat of the fluid opening. In this preferred refinement, the stop element thus performs a dual function. It serves not only as a stop in the second position of the solenoid armature but also as a sealing element for the fluid-tight closure of the fluid opening. This is advantageous in particular if the fluid opening is for example a nozzle seat for a fluid source or for a fluid connection to the surroundings, because in such a situation, the stop element can act as a sealing element that is formed integrally on the second armature end surface.

In another advantageous refinement, the second housing wall has a fluid opening which extends through the second housing wall, and the at least one damping element is arranged spaced apart from the at least one stop element such that, both in the first position of the solenoid armature and in the second position of the solenoid armature, a fluid channel for a fluid flowing radially at the second armature end surface and through the fluid opening is formed between the at least one damping element and the at least one stop element. In this refinement, it is thus ensured that, even in the event of contact of the stop element and damping element in the second position of the solenoid armature, there is still a sufficiently large free space between the damping element and the stop element such that a sufficiently large fluid channel for a fluid flowing radially at the second armature end surface and through the fluid opening is provided between the damping element and the stop element. This refinement can for example be used to particular advantage if it is intended to use the fluid opening through the second housing wall exclusively as a fluid connection that cannot be completely closed.

In a further preferred refinement, the at least one damping element has an axial damping element end surface, and a size of the axial damping element end surface lies in a range from approximately 5% to approximately 50%, in particular in a range from approximately 10% to approximately 20%, of a size of the second armature end surface. By means of this refinement, a particularly soft force-travel characteristic during the compression of the at least one damping element is achieved, which furthermore also contributes to an in particular energy-absorbing, progressive spring characteristic.

In a further preferred refinement, in the first position of the solenoid armature, an extent of the at least one stop element in a circumferential direction of the solenoid armature is at least twice as great as an extent of the at least one damping element in the circumferential direction of the solenoid armature. In other words, as viewed in a circumferential direction of the solenoid armature, the at least one stop element is wider than the at least one damping element. By means of this refinement, it is achieved that the stop element has a force-travel characteristic that is hard in relation to the damping element. This has the effect that the maximum stroke of the solenoid armature can be precisely set, for high repeat accuracy of the response behavior of the actuator arrangement.

According to a further preferred refinement, the at least one damping element has a first extent dimension in an axial direction of the solenoid armature, has a second extent dimension in a circumferential direction of solenoid armature, and has a third extent dimension in a radial direction of the solenoid armature, wherein a ratio of the first extent dimension (axial direction) to the second extent dimension (circumferential direction) lies in a range between approximately 1 and approximately 2, and a ratio of the first extent dimension (axial direction) to the third extent dimension (radial direction) lies in a range between approximately 1 and approximately 2. In other words, the at least one damping element is preferably equally as tall as it is wide (in a circumferential direction and/or radial direction) but at most twice as tall as it is wide (in a circumferential direction and/or radial direction). By means of this ratio of these three extent dimensions with respect to one another, it is ensured that the at least one damping element has a sufficiently great extent in an axial direction, so as not to have too hard a force-travel characteristic, but at the same time does not have too great an extent in an axial direction, so as not to be buckled rather than compressed during the movement of the solenoid armature from the first position into the second position.

In a further preferred refinement, the actuator arrangement furthermore has at least one further damping element which is arranged on the second armature end surface and which extends from the second armature end surface in the direction of the second housing wall and which makes contact with the second housing wall both in the first position and in the second position of the solenoid armature, wherein the at least one further damping element is arranged spaced apart from the at least one damping element such that, at least in the first position of the solenoid armature, a fluid channel for a fluid flowing radially at the second armature end surface is formed between the at least one damping element and the at least one further damping element. It is thus also insured in the case of an additional damping element that, at least in the first position, a sufficiently large fluid channel for a fluid flowing radially at the second armature end surface is formed.

In a particularly preferred refinement, the at least one further damping element has the same extent dimensions in a radial, an axial and a circumferential direction as the at least one damping element. It is particularly preferable if the at least one damping element and the at least one further damping element furthermore have an equal radial spacing from or to the axis along which the solenoid armature is movable, in particular if the axis constitutes, for example, a central axis of a cylindrical, in particular circular cylindrical, solenoid armature.

If, in addition to the at least one damping element, the actuator arrangement furthermore has at least one further damping element, a size of the damping element end surface formed collectively by the at least one damping element and by the at least one further damping element should in turn lie 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 surface in order to ensure the soft force-travel characteristic of the damping elements as already discussed above.

In a further preferred refinement, the second housing wall is configured at least partially as an electromagnetic core. In this refinement, the solenoid armature would thus be pulled toward the electromagnetic core, which serves as a stop for the solenoid armature, into the second position. It is particularly advantageous if the fluid opening of the second housing wall is furthermore formed in the electromagnetic core. It would thus for example be possible for the nozzle seat for the fluidic connection to ambient pressure, for example, to be formed directly in the electromagnetic core.

In a further refinement, it is alternatively or additionally possible for the first housing wall to have a fluid opening that extends through the housing wall, and for the actuator arrangement to furthermore have a sealing element which is arranged on the first armature end surface and which extends from the first armature end surface in the direction of the first housing wall and which, in the first position of the solenoid armature, makes fluid-tight contact with a sealing seat, arranged at the first housing wall, of the fluid opening. If both the first housing wall and the second housing wall each have a fluid opening, then it would for example be possible to fill a fluid chamber or fluid bladder in controlled fashion with a fluid situated in a fluid source, or to ventilate the fluid chamber or fluid bladder that has been filled with the fluid.

It is particularly advantageous if both the at least one damping element and the at least one stop element and also the sealing element are formed from the same elastomer material, because this in turn allows inexpensive and time-saving production of the actuator arrangement.

Finally, in a further preferred refinement, the actuator arrangement furthermore has a restoring element which is configured to preload the solenoid armature into the first position in the absence of actuation, that is to say in the case of electromagnetic deactivation. In this way, it is for example possible for an NO valve (normally open valve) or an NC valve (normally closed valve) to be created.

Elements of identical design or function are provided with the same reference designations across all figures.

Reference is made firstly toFIG.1, which shows a schematic view of an actuator arrangement10according to the invention in simplified form. The actuator arrangement10has a housing having a first housing wall12and having a second housing wall14situated opposite the first housing wall12. A solenoid armature16is arranged within the housing between the first housing wall12and the second housing wall14. In the specific example ofFIG.1, the solenoid armature16is illustrated as a cylindrical armature, in particular circular cylindrical armature, though may also have other refinements in other embodiments that are not illustrated.

The solenoid armature16is, between the first housing wall12and the second housing wall14, movable axially along an axis18between a first position and a second position.FIG.1shows the solenoid armature16in a first position, andFIG.2shows the solenoid armature16in a second position.

The solenoid armature16has a first axial armature end surface20, which is substantially perpendicular to the axis18, and a second axial armature end surface22, which is situated opposite the first axial armature end surface20and which is substantially likewise perpendicular to the axis18. The first axial armature end surface20faces toward the first housing wall12, and the second axial armature end surface22faces toward the second housing wall14.

As shown inFIG.1, in the first position of the solenoid armature16, the first armature end surface20makes contact with the first housing wall12. As shown inFIG.2, in the second position of the solenoid armature16, the first armature end surface20has been moved away from the first housing wall12.

As is also shown inFIGS.1and2, the second armature end surface22, that is to say that armature end surface which faces toward the second housing wall14, has a damping element24which is arranged on the second armature end surface22and which extends from the latter in the direction of the second housing wall14. In the specific example ofFIGS.1and2, the damping element24has a first damping element24A and a second damping element24B, though may also have more or fewer damping elements in other embodiments that are not shown. Aside from the damping elements24A and24B, the second axial end surface22furthermore has a stop element26. Both the damping elements24A,24B and the stop element26are produced from an elastomer material such as EPDM or silicone, and may for example be injection-molded onto the second armature end surface22.

As shown by a comparison ofFIG.1withFIG.2, the damping elements24A,24B make contact with the second housing wall14both in the first position and in the second position of the solenoid armature16. By contrast, the stop element26makes contact with the second housing wall40only in the second position of the solenoid armature16(seeFIG.2). There is thus no free-flight phase for the solenoid armature16during a movement of the solenoid armature16from the first position into the second position. Instead, during the movement of the solenoid armature16from the first position into the second position, the elastomer damping elements24A,24B are compressed, whereby the movement of the solenoid armature16is dampened, in particular in energy-absorbing fashion. The use of the elastomer material furthermore leads to a progressive spring characteristic, that is to say the spring characteristic of the damping elements24A,24B increases similarly to or to a greater degree than the magnetic force over the movement travel of the armature, and thus prevents a high speed of the solenoid armature16during the switching process. It is advantageous in this context if the magnetic field for the actuation of the actuator arrangement10is built up in ramped fashion over time upon the activation of the electrical energization and is likewise depleted in ramped fashion over time upon the deactivation of the electrical energization. There is thus at all times force equilibrium between the progressive spring characteristic of the damping elements24,24B, and of a restoring element that may be used, on the one hand, and the magnetic force on the other hand. Together with the absence of a free-flight phase of the solenoid armature16, this leads to a low movement speed of the solenoid armature16and thus to an altogether very low generation of noise during the movement of the solenoid armature16from the first position into the second position and during the movement of the solenoid armature16from the second position into the first position.

Reference is now made toFIG.3, which shows a schematic detail view of the actuator arrangement10in a side view, a plan view and a sectional view.

In this specific example, too, the solenoid armature16is illustrated as a circular cylindrical armature. In other embodiments that are not shown, the solenoid armature16may self-evidently have other embodiments.

As can be seen inFIG.3, the damping elements24A,24B have an axial extent28in the direction of the axis18. This axial extent28is greater than an axial extent29of the stop element26. In other words, at least in the first position of the solenoid armature16, the damping elements24A,24B project further than the stop element26in the direction of the second housing wall14. A difference between the axial extent28of the damping elements24A,24B and the axial extent29of the stop element26is in this case such that the difference in the axial extents28,29lies substantially in the range of a stroke of the solenoid armature16, wherein the stroke of the solenoid armature16describes the actuating travel covered by the latter during the movement from the first position to the second position. This is achieved in that, firstly, a free-flight phase of the solenoid armature16is avoided, and secondly, there is also no unnecessary pre-compression of the damping elements24A,24B in the first position of the solenoid armature16.

As can also be seen inFIG.3, the stop element26in the refinement shown inFIG.3is furthermore configured as a circular disk, that is to say the stop element26extends through 360° in a circumferential direction of the axis18. In such a refinement, the stop element26can, in the second position of the solenoid armature16, serve as a sealing element for sealing a fluid opening that is present in the second housing wall14, as will be described in more detail for example in conjunction withFIGS.6and7.

Reference will now be made toFIG.4, which shows a further embodiment of the actuator arrangement10. By contrast toFIG.3, the stop element30inFIG.4is configured not as a circular disk extending through 360° in a circumferential direction but as two stop elements30A and30B, which in the specific example ofFIG.4are situated substantially opposite one another. The stop elements30A,30B furthermore extend only over a relatively small angle range in a circumferential direction of the axis18, such that a fluid channel32is formed between the stop elements30A,30B and the damping elements24A,24B. The damping element24A and the further damping element24B are also arranged spaced apart from one another (and from the stop elements30A,30B) such that fluid channels32are present both in the first position and in the second position of the solenoid armature16. By virtue of the elements24A,24B,30A,30B being configured and arranged to be spaced apart among themselves and from one another such that flow channels32are formed, a flow of fluid over the second armature end surface22is made possible. The elements24A,24B,30A,30B may furthermore be configured and arranged to be spaced apart among themselves and from one another such that the flow of fluid over the second armature end surface22is ensured both in the first position and in the second position of the solenoid armature16, as will be discussed in more detail for example in conjunction withFIGS.8and9.

Reference is now made toFIG.5, which shows an enlarged schematic detail view of the actuator arrangement10fromFIG.4in a side view and a plan view, wherein the solenoid armature16is shown in the first position inFIG.5.

As is shown inFIG.5, in the first position of the solenoid armature16, an extent34of the stop element30A,30B in a circumferential direction of the axis18is more than twice as great as an extent36of the damping element24A or24B in the circumferential direction of the axis18. In other words, the stop elements30A,30B are more than twice as wide as the damping elements24A,24B. By virtue of the fact that the stop elements30A,30B are more than twice as wide as the damping elements24A,24B, the stop elements30A,30B have, in relation to the damping elements24A,24B, a harder force-travel characteristic in relation to the relatively narrow damping elements24A,24B.

Furthermore, a collective axial damping element end surface38of the damping elements24A,24B, which corresponds to the sum of the axial damping element end surfaces38A,38B of the respective damping elements24A,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 surface22. Here, the axial damping element end surface38occupies a relatively small proportion of the second armature end surface22, as a result of which a particularly soft force-travel characteristic for the damping elements24A,24B is achieved.

Furthermore, the damping elements24A,24B have a first extent or a first extent dimension28in an axial direction of the solenoid armature16, a second extent or a second extent dimension36in a circumferential direction of the solenoid armature16, and a third extent or a third extent dimension40in a radial direction of the solenoid armature16. A ratio of the first extent dimension28to the second extent dimension36is in this case selected such that this ratio is in a range between approximately 1 and 2. Furthermore, a ratio of the first extent dimension28to the third extent dimension40is in this case selected such that this ratio is in a range between approximately 1 and approximately 2. In other words, this means: The damping elements24A,24B each have a shape that is approximately equally as tall as it is wide (as viewed in a circumferential direction and/or radial direction) but at most twice as tall as it is wide (as viewed in a circumferential direction and/or radial direction). Such a shape ensures that the damping elements24A,24B have a sufficient height, so as not to have too hard a force-travel characteristic, but at the same time are not too tall, so as not to be buckled during the movement of the solenoid armature16from the first position into the second position. It is not essential to the invention for the extent dimensions of the damping elements24A,24B in a circumferential direction and a radial direction to be equal.

Reference is now made toFIGS.6and7, which show a schematic view of the actuator arrangement10in an electromagnetically actuatable 3/2 NO valve42. The term “3/2 NO valve” means that this valve has three ports and two positions and is open (NO = normally open) in an inactive (electrically deenergized) state.

In the specific example ofFIGS.6and7, the 3/2 NO valve42is part of a pneumatic adjusting device43. This pneumatic adjusting device43is used to adjust a seat contact face44of a vehicle seat45by means of a fluid-fillable fluid bladder or fluid chamber46, by virtue of the fluid bladder46being filled or emptied.FIG.6shows the 3/2 NO valve42in an electrically deenergized state, in which the fluid bladder46is being ventilated or emptied.FIG.7shows the 3/2 NO valve42in an inactive state, in which the fluid bladder46is being filled.

Reference is now made toFIG.6, in which the 3/2 NO valve42is shown in an electrically deenergized state. In this electrically deenergized state, the solenoid armature16is situated in the first position, in which the first armature end surface20makes contact with the first housing wall12. In the specific example ofFIG.6, the first housing wall12is configured so as to have a fluid opening48which extends through the first housing wall12and which is fluidically connected via a corresponding fluid connection to a fluid source50of the pneumatic adjusting device43. In the first position of the solenoid armature16, the fluid opening48situated in the first housing wall12is furthermore closed in fluid-tight fashion by means of a sealing element52which is provided at the first armature end surface20and which is configured specifically for this purpose. For this purpose, the sealing element52is arranged on the first armature end surface20and extends in the direction of the first housing wall12, such that the solenoid armature16, in its first position, can make fluid-tight contact with a sealing seat of the fluid opening48by means of the sealing element52and thus fluidically close the fluid opening48. In other words, in the first position of the solenoid armature16, an inflow of fluid from the fluid opening48into a valve chamber of the valve42is prevented.

The above-discussed damping elements24A and24B, and the stop element26, are situated on the second armature end surface22, which is situated opposite the first armature end surface20. In the refinement ofFIG.6andFIG.7, the stop element26is configured as a circular disk which extends through 360° in a circumferential direction of the solenoid armature16, as has also been described in more detail in conjunction withFIG.3. Furthermore, the second housing wall14is configured as a magnetic armature54and additionally has a fluid opening56which extends in the second housing wall14or the magnetic armature54and which is fluidically connected to the surroundings of the valve42.

As can also be seen inFIG.6, the first housing wall12furthermore has a non-controllable fluid opening58that is fluidically connected via a corresponding fluid connection to the fluid bladder46. The non-controllable fluid opening58constitutes a non-controllable fluidic connection to the valve chamber of the valve42. Since the damping elements24A and24B furthermore make up only a small proportion of the total size of the second armature end surface22, it is possible for a fluid that flows from the fluid bladder46through the non-controllable fluid opening48to flow into the valve chamber of the valve42and, from there, radially over the second armature end surface22and through the fluid opening56into the surroundings of the valve42. In other words, in the first position of the solenoid armature16, the fluid bladder46can be emptied or ventilated by means of the fluid opening56.

As already discussed, the solenoid armature16is situated in the first position in the electrically deenergized state of the valve42. For this purpose, the solenoid armature16is preloaded into the first position by means of a restoring element60configured specifically for this purpose.

Now, in addition to the solenoid armature16and the electromagnetic core54, which belong to the actuator arrangement10, the valve42furthermore comprises a magnetic coil62and a yoke64. If the valve42is now electrically energized, the solenoid armature16moves, in a manner known to a person skilled in the art, from the first position shown inFIG.6in the direction of the electromagnetic core54, until the solenoid armature16is finally situated in the second position shown inFIG.7.

In the second position of the solenoid armature16, the second armature end surface20, and in particular the sealing element52, have been moved away from the first housing wall12. At the same time, on the second armature end surface22, not only the two damping elements24A and24B but also the stop element26, configured as a circular disk, are in contact with the second housing wall14. Since the stop element26is configured as a sealing element, it is possible in the second position of the solenoid armature16for the stop element26to make fluid-tight contact with a sealing seat of the fluid opening56and to thus prevent a flow of fluid through the fluid opening56.

At the same time, however, in the second position of the solenoid armature16, the fluid opening48of the first housing wall12is open, such that a fluid situated in the fluid source50can flow via the corresponding fluid connection, the fluid opening48and the non-controllable fluid opening58into the fluid bladder46. In other words, in the second position of the solenoid armature16, the fluid bladder46can be filled with fluid.

The refinement of the actuator10in the 3/2 NO valve42, as shown inFIGS.6and7, thus allows filling and emptying of the fluid bladder46, wherein, by means of the specific refinement of the actuator arrangement10, a reduced switching noise is achieved during the movement of the solenoid armature16from the first position into the second position and during the movement of the solenoid armature16from the second position into the first position.

Reference is now made toFIGS.8and9, which show the use of the hitherto described actuator arrangement in a further electromagnetically actuatable valve. In the specific example ofFIGS.8and9, two actuator arrangements10are used in a 3/3 NO valve66. The term “3/3 NO valve” means that this valve has three ports and three positions and is open (NO = normally open) in an inactive (electrically deenergized) state.

In the specific example ofFIGS.8and9, the 3/3 NO valve66is part of a pneumatic adjusting device68. This pneumatic adjusting device68is used to adjust the seat contact face44of the vehicle seat45by means of the fluid-fillable fluid bladder46, by virtue of the fluid bladder46being filled or emptied. Furthermore, by means of the 3/3 NO valve66, the pressure in the fluid bladder46can be held.FIG.8shows the 3/3 NO valve68in an electrically deenergized state, in which the fluid bladder46is being ventilated or emptied.FIG.9shows the 3/3 NO valve68in an inactive state, in which the fluid bladder46is being filled. The pressure-holding state is not shown, but will be explained.

The 3/3 NO valve66is made up substantially of two 2/2 valves, each of which has an actuator arrangement10with a movable solenoid armature16and has an electromagnetic core54, a magnet coil62and a yoke64. Here, the right-hand 2/2 NO valve is substantially structurally identical to the 3/2 NO valve that has been described in conjunction withFIGS.6and7. That is to say, the right-hand 2/2 NO valve has the solenoid armature16with the damping elements24A and24B provided on the second armature end surface22and with the stop element26configured as a sealing element. Only the first housing wall12of the right-hand 2/2 NO valve does not have a fluid opening48to the fluid source50as described in conjunction withFIG.6, but rather has only the non-controllable fluid opening58. However, the non-controllable fluid opening58of the right-hand 2/2 NO valve is connected to the pressure chamber of the left-hand 2/2 NC valve. The left-hand 2/2 NC valve in turn has an actuator arrangement10, wherein the first housing wall12is now fluidically connected via a corresponding fluid connection to the fluid source50, and the second housing wall14is fluidically connected via a fluid opening70to the fluid bladder46.

By contrast to the right-hand solenoid armature16, the left-hand solenoid armature16furthermore has, on its second armature end surface22, a stop element30in addition to the damping elements24A and24B, which stop element is configured as mutually spaced-apart stop elements30A,30B, as described in conjunction withFIGS.4and5.

Both the right-hand solenoid armature16and the left-hand solenoid armature16are movable between a first position and a second position. InFIG.8, the right-hand solenoid armature16is shown in first position and the left-hand solenoid armature16is likewise shown in the first position.

In the first position of the right-hand solenoid armature16, the damping elements24A and24B make contact with the second housing wall14of the right-hand actuator arrangement10. Likewise, in the first position of the left-hand solenoid armature16, the damping elements24A and24B make contact with the second housing wall14of the left-hand armature arrangement10. Furthermore, the damping elements24A,24B and the stop elements30A,30B of the left-hand actuator arrangement10are arranged spaced apart from one another such that a radial flow on the second armature end surface22of the left-hand solenoid armature16is possible. This has the result that a fluid situated in the fluid bladder46can flow through the fluid opening70and radially over the second armature end surface22of the left-hand solenoid armature16. From there, the fluid can flow onward through the non-controllable fluid opening58into the valve chamber of the right-hand 2/2 NO valve and, from there, through the fluid opening56into the surroundings. In other words, the fluid bladder46can be emptied or ventilated by means of the 3/3 NO valve66shown inFIG.8.

If the 3/3 NO valve66is now correspondingly electrically energized, then the right-hand solenoid armature16moves from the first position into the second position counter to the restoring force of the right-hand restoring element60. In the second position, the right-hand stop element26, configured as a sealing element, makes contact with a sealing seat of the fluid opening56, such that a fluidic connection to the surroundings is shut off. Furthermore, in the case of corresponding electrical energization of the 3/3 NO valve66, the left-hand solenoid armature16is moved from the first position into the second position counter to the restoring force of the left-hand restoring element60from the first position into the second position. In the second position, not only the damping elements24A,24B but also the stop elements30A,30B make contact with the second housing wall14, configured as an electromagnetic core54, of the left-hand actuator arrangement10. However, the damping elements24A,24B and the stop element30A,30B are arranged spaced apart from one another such that a fluid flow through the fluid opening70is possible also in the second position of the left-hand solenoid armature16. Since it is furthermore the case in the second position of the left-hand solenoid armature16that contact is no longer made with the first housing wall12, fluid can flow from the fluid source50via the fluid opening70into the fluid bladder46(but not via the fluid opening56into the surroundings). In otherwords, in the position of the 3/3 NO valve66shown inFIG.9, the fluid bladder46can be filled with fluid.

If it is now sought – as has been mentioned above – for the pressure in the fluid bladder46to be held, then it is merely necessary for the 3/3 NO valve66to be electrically energized such that the left-hand solenoid armature16is moved from the second position back into the first position. In this way, a fluidic connection to the fluid source50is shut off by means of the sealing element52of the left-hand solenoid armature16. At the same time, the right-hand solenoid armature16remains in the second position, in which a fluidic connection to the surroundings is also shut off.

The actuator arrangements10shown inFIGS.8and9thus, in the 3/3 NO valve66, allow filling and emptying of the fluid bladder46and holding of a pressure of the fluid bladder46. Owing to the respectively provided damping elements24A,24B and the absence of free-flight phases of the solenoid armature16, the switching noises of the 3/3 NO valve66are however considerably reduced.

Reference is finally made toFIGS.10and11, which show the use of the hitherto described actuator arrangement in a further electromagnetically actuatable valve. In the specific example ofFIGS.10and11, two actuator arrangements10are used in a 3/3 NC valve72. The term “3/3 NC valve” means that this valve has three ports and three positions and is closed (NC = normally closed) in an inactive (electrically deenergized) state.

In the specific example ofFIGS.10and11, the 3/3 NC valve72is part of a pneumatic adjusting device74. This pneumatic adjusting device74is used to adjust the seat contact face44of the vehicle seat45by means of the fluid-fillable fluid bladder46, by virtue of the fluid bladder46being filled or emptied. Furthermore, by means of the 3/3 NC valve74, the pressure in the fluid bladder46can be held.FIG.10shows the 3/3 NC valve72in an electrically deenergized state, in which the fluid bladder46is being filled.FIG.11shows the 3/3 NC valve72in an active state, in which the fluid bladder46is being ventilated or emptied. The pressure-holding state is not shown, but will be explained.

The 3/3 NC valve72is made up substantially of two 2/2 NC valves, each of which has an actuator arrangement10with a movable solenoid armature16and has an electromagnetic core54, a magnet coil62and a yoke64. Here, the right-hand 2/2 NC valve is similar to the left-hand 2/2 NC valve that has been described in conjunction withFIGS.8and9. However, the first housing wall12of the left-hand actuator arrangement10has a fluid opening76that is connected not to the fluid source50, as inFIGS.8and9, but to the surroundings. The first armature end surface20has a sealing element52that closes the fluid opening76in fluid-tight fashion in the first position of the left-hand solenoid armature16. The second armature end surface22has damping elements24A,24B and stop elements30A,30B, which allow a radial flow over the second armature end surface22both in the first and in the second position of the left-hand solenoid armature16. Furthermore (as in the refinement ofFIGS.8and9), the second housing wall14of the left-hand actuator arrangement10is configured as an electromagnetic core54having a fluid opening70extending through it. The fluid opening70again produces the fluidic connection to the fluid bladder46. Also, the first housing wall12of the left-hand actuator arrangement10has the non-controllable fluid opening58, whereby a fluidic connection between the valve chamber of the left-hand 2/2 NC valve and the valve chamber of the right-hand 2/2 NC valve is ensured.

In the case of the right-hand actuator arrangement10of the right-hand 2/2 NC valve, the first housing wall12is again configured with a fluid opening48, similarly to the refinement ofFIGS.6and7. The first armature end surface20of the right-hand solenoid armature16is also configured with a sealing element52in order to close the fluid opening48in fluid-tight fashion. The second housing wall14is configured as an electromagnetic core54. However, the second housing wall14or the core54does not have a fluid opening. However, the second armature end surface22of the right-hand solenoid armature16again has the damping elements24A,24B and either a stop element26with the refinement ofFIG.3or a stop element30with the refinement ofFIGS.4and5.

As can be seen inFIG.10, the right-hand solenoid armature16is situated in the second position, in which the damping elements24A,24B and the stop element (26or30, depending on the refinement) make contact with the second housing wall14. In this way, the sealing element52of the first armature end surface20has been moved away from the first housing wall12of the right-hand actuator arrangement10. Fluid from the fluid source50can thus flow in via the fluid opening48. From there, fluid can flow onward through the non-controllable fluid opening58into the valve chamber of the left-hand 2/2 NC valve. However, in the embodiment shown inFIG.10, the left-hand solenoid armature16is situated in the first position, such that the sealing element52of the left-hand solenoid armature16closes the fluid opening76and a fluidic connection to the surroundings is shut off. However, fluid can flow radially over the second armature end surface22of the left-hand solenoid armature16and from there via the fluid opening70into the fluid bladder46. In other words, the fluid bladder46can be filled via the 3/3 NC valve72in the position shown inFIG.10.

If it is now sought for the fluid bladder46to be ventilated, then the 3/3 NC valve72must be electrically energized such that the left-hand solenoid armature16moves from the first position into the second position and the right-hand solenoid armature16moves from the second position into the first position. If the right-hand solenoid armature16is situated in the first position, an inflow of fluid from the fluid source50is prevented. If the left-hand solenoid armature16is furthermore situated in the second position, the fluid opening76is opened up because the sealing element52of the left-hand solenoid armature16no longer closes the fluid opening76. Since the damping elements24A,24B and the stop element30A,30B are furthermore arranged spaced apart from one another such that a fluid flow through the fluid opening70is possible also in the second position of the left-hand solenoid armature16, fluid can flow from the fluid bladder46through the fluid opening76into the surroundings. In other words, in the position of the 3/3 NC valve72shown inFIG.11, the fluid bladder46can be emptied or ventilated.

If it is now also sought – as has been mentioned above – for the pressure in the fluid bladder46to be held, then it is merely necessary for the 3/3 NC valve72to be electrically energized, or electrically deenergized, such that the left-hand solenoid armature16is moved from the second position back into the first position. In this way, a fluidic connection to the surroundings is shut off by means of the sealing element52of the left-hand solenoid armature16. At the same time, the right-hand solenoid armature16must remain in the first position in order that a fluidic connection to the fluid source50is shut off.

The actuator arrangements10shown inFIGS.10and11thus, in the 3/3 NC valve72, allow filling and emptying of the fluid bladder46and holding of a pressure of the fluid bladder46. Owing to the respectively provided damping elements24A,24B and the absence of free-flight phases of the solenoid armature16, the switching noises of the 3/3 NC valve72are however considerably reduced.

Further arrangements of the actuator arrangements10in corresponding refinements are conceivable in order to realize further valves that are suitable for the respective application