Electromagnetic actuator

Abstract

The electromagnetic actuator includes a coil arrangement with at least one coil core and a coil arranged circumferentially around the coil core, a housing with a magnetic material and a rotationally symmetrical accommodation space in which the coil arrangement is at least partially accommodated, and a movable magnetic armature body as a movable actuator element movable by a magnetic field generated by the coil arrangement, the armature body being supported on one side by a bearing relative to the housing and movable along the bearing rotation axis from a first position to a second position, the armature body being configured in the shape of a disk and having a shape symmetrical transversely to the bearing rotation axis with respect to an axis of symmetry located in the plane of the disk, the armature body having a first maximum extension length between opposite ends of the armature body in the direction of the axis of symmetry and a second maximum extension length between opposite ends of the armature body in the direction of the axis of rotation of the bearing, the second maximum extension length being shorter than the first maximum extension length.

Description

Technical Field

[0001] The present invention relates to an electromagnetic actuator having a coil device including at least one coil core, a coil circumferentially arranged around the coil core, and a housing having a magnetic material, and a movable magnetic armature body as a movable actuator element, the armature body being movable by a magnetic field generated by the coil device, the armature body being supported on one side with respect to the housing by a support and being movable from a first position to a second position around a support rotation axis.

[0002] Such electromagnetic actuators are known, for example, in the form of electromagnetic switching devices or valve devices, for example in the form of electromagnetic relays or solenoid valves. For example, a solenoid valve in the form of a tilting armature valve is used as a control valve for air pressure control, for example, in a vehicle, for example, in a commercial vehicle or a bus for passenger transportation. For example, a vehicle braking system equipped with an electronic service brake system includes at least one control valve for pressure control.

[0003] The electromagnetic actuator in the form mentioned at the beginning is known, for example, in the form of a tilting armature valve from German Patent Application Publication No. 102016105532. The electromagnetic actuator has a coil device and a movable magnetic armature body.

[0004] Furthermore, other configurations of solenoid valves described, for example, in German Patent Application Publication No. 102014115207, German Patent Application Publication No. 102018123997 or German Patent Invention No. 102014115206 are also known.

[0005] For example, when using a cylindrical housing belonging to a magnetic circuit, tolerances may cause the armature body to be positioned eccentrically. This can result in a large lateral force being applied to the armature body from the side. This adds an additional load to the support structure that holds the armature body, reducing the magnetic force in the working direction, which can increase wear and decrease efficiency.

[0006] The fundamental objective of this invention is to provide an electromagnetic actuator of the type described above that enables improved durability and greater efficiency.

[0007] The present invention relates to an electromagnetic actuator of the type described in the appended claims. Advantageous embodiments and variations of the present invention are shown in the dependent claims and the following description.

[0008] One aspect of the present invention relates in particular to an electromagnetic actuator comprising a coil device having at least one coil core, coils arranged circumferentially around the coil core, and a housing having a magnetic material; a rotationally symmetric housing space in which the coil device is at least partially housed; and a movable magnetic armature body as a movable actuator element, movable by a magnetic field generated by the coil device. The armature body is supported on one side with respect to the housing by a support and is movable from a first position to a second position about the axis of rotation of the support. The armature body is configured in a disc shape and has a shape that is symmetrical laterally with respect to the axis of rotation of the support with respect to an axis of symmetry located on the disc surface. The armature body has a first maximum extension length between opposite ends in the direction of the axis of symmetry and a second maximum extension length shorter than the first maximum extension length between opposite ends in the direction of the axis of rotation of the support.

[0009] The electromagnetic actuator according to the present invention enables the armature body to move reliably and smoothly within the electromagnetic actuator. This is because the configuration of the armature body allows for greater tolerances in the position of the armature body within the housing. In particular, on the one hand, more economical manufacturing procedures can be used when fabricating individual components, and on the other hand, electromagnetic actuators, such as solenoid valves for commercial vehicle applications, can be manufactured with greater robustness and reliability with respect to wear of the armature support. Furthermore, the lateral force of the magnetic field acting through the air gap can be reduced in undesirable directions, and the magnetic field can be strengthened in the desired functional direction. Moreover, the electromagnetic actuator according to the present invention enables greater robustness with respect to manufacturing tolerances without negatively impacting magnetic force and manufacturing costs.

[0010] According to one embodiment of an electromagnetic actuator, the axis of symmetry is positioned perpendicular to the axis of rotation of the bearing. This allows the bearing reaction force of the armature body to be uniformly distributed with respect to the axis of rotation of the bearing. This results in a more uniform load on the bearing, which in turn allows the electromagnetic actuator to have improved durability.

[0011] According to one embodiment of an electromagnetic actuator, the first maximum extension length is the first diameter of the armature body, and the second maximum extension length is the second diameter of the armature body. This shape allows for a defined and relatively easy-to-manufacture armature body for improved positioning and reduced lateral forces under tolerance conditions.

[0012] According to one embodiment of an electromagnetic actuator, the first maximum extension length is the maximum diameter of the armature body, and the second maximum extension length is the minimum diameter of the armature body. This results in the armature body having a somewhat elongated, rounded shape, such as egg-shaped or elliptical, which improves the orientation of the armature body in the housing space and the orientation of the magnetic field acting on the armature body under tolerance conditions.

[0013] According to one embodiment of an electromagnetic actuator, the armature body has a convex, particularly elliptical, outer contour on the disk surface. Such an outer contour allows for sufficient clearance between the housing and the outer surface on the outer circumference of the armature body, even when the armature body is tilted laterally with respect to the bearing rotation axis. Due to the geometric shape of the armature body, the magnetic flux is strengthened and deflected in a favorable direction, thereby strengthening the magnetic flux in the longest lever arm, and consequently increasing the magnetic force acting on the armature body when the lateral force is reduced.

[0014] According to one embodiment of an electromagnetic actuator, the armature body has two first regions opposite to each other, each having a rounded outer contour in the direction of the axis of symmetry, and two second regions opposite to each other, each having an outer contour that is flattened relative to the first regions in the direction of the axis of rotation of the support body. This also enables improved positioning of the armature body and reduction of lateral forces under tolerance conditions.

[0015] According to one embodiment of an electromagnetic actuator, two first regions opposite each other each have a circular outer contour. Thus, the two first regions opposite each other allow for a sufficiently constant gap between the armature body and the housing near the opposite end of the support or armature body.

[0016] According to one embodiment of an electromagnetic actuator, each flattened outer contour is configured in a barrel shape. Specifically, the barrel shape means that the contour is flattened relative to an arc and may have different radii, with the central portion of the flattened outer contour having a larger radius than the adjacent end portions of the flattened outer contour. The end portions of the flattened outer contour connect, for example, to each circular outer contour.

[0017] According to one embodiment of an electromagnetic actuator, the housing space is configured to be cylindrical. This allows for good positioning and easy fabrication under tolerance conditions, together with the armature body.

[0018] According to one embodiment of an electromagnetic actuator, when the armature body is oriented symmetrically with respect to the housing space on the disk surface, the gap between the armature body at the position of the first maximum extension length and the adjacent portion of the housing in the direction of the axis of symmetry is smaller than the gap between the armature body at the position of the second maximum extension length and the adjacent portion of the housing in the direction of the axis of rotation of the support. The gaps of different widths cause the magnetic flux to be positively deflected, thereby strengthening the magnetic flux at the longest lever arm and consequently increasing the magnetic force at the armature body.

[0019] According to one embodiment of an electromagnetic actuator, the coil core has a rotationally symmetric region with an axis of symmetry, where the coil core is circumferentially surrounded by the coil, the support body is positioned radially displaced with respect to the axis of symmetry of the coil core, and the armature body extends radially beyond the coil core. This allows for precise movement of the armature body supported on one side, because the armature body can move, largely, and especially completely, within the generated magnetic field. Positioning of the support body enables advantageous one-sided support of the armature body. In this way, a robust and reliable electromagnetic actuator can be manufactured under tolerance conditions and reduced lateral forces.

[0020] According to one embodiment of an electromagnetic actuator, the electromagnetic actuator is configured as an electromagnetic switching device or valve device comprising an armature body as a switching element or valve element, particularly as an electromechanical relay or solenoid valve.

[0021] According to one embodiment of an electromagnetic actuator, the electromagnetic actuator is configured as a tilting armature valve.

[0022] According to one embodiment of an electromagnetic actuator, the electromagnetic actuator is configured as a solenoid valve for a vehicle's pressure control module.

[0023] The embodiments described herein can be applied in parallel or in any combination of them.

[0024] The present invention will be described in detail below based on the figures shown in the drawings. [Brief explanation of the drawing]

[0025] [Figure 1A] This is a schematic cross-sectional view showing an exemplary tilting armature valve in which an electromagnetic actuator according to the present invention can be basically used. [Figure 1B] Another schematic cross-sectional view showing an exemplary tilting armature valve in which the electromagnetic actuator according to the present invention can be basically used. [Figure 2] A perspective view showing an exemplary and known armature body for use in the exemplary tilting armature valve shown in FIG. 1. [Figure 3] A schematic cross-sectional view showing the armature body in the housing of one embodiment of the electromagnetic actuator according to the present invention along the disk surface of the armature body at an oriented position in the housing. [Figure 4] A schematic cross-sectional view showing the armature body in the housing of one embodiment of the electromagnetic actuator according to the present invention along the disk surface of the armature body, and showing the armature body at a position rotated under tolerance conditions.

[0026] FIG. 1 shows a simplified cross-sectional view of a tilting armature valve 100 based on FIGS. 1A and 1B, where the electromagnetic actuator 105 according to the present invention having an armature body 115 as shown in FIGS. 3 and 4 can be basically used. FIG. 1 attempts to show an exemplary and practical use of an electromagnetic actuator based on a tilting armature valve. In contrast, FIG. 2 shows an exemplary armature body 115 known from German Patent Application Publication No. 102016105532. Based on FIG. 2, the configuration of the armature body 115 according to the present invention can be more clearly explained. The configuration of the armature body 115 according to the present invention is shown in more detail in FIGS. 3 and 4 according to one embodiment and can be basically easily transferred by those skilled in the art to the tilting armature valve shown in FIG. 1. In this regard, it is pointed out that the basic operation mode of an electromagnetic device, such as a switching device or a valve device, having an armature body movable by a magnetic field as a switching element or a valve element, is known to those skilled in the art.

[0027] In FIGS. 1 to 4, the same components, components having the same function, or corresponding components are denoted by the same reference numerals.

[0028] The tilting armature valve 100 may basically be one embodiment of the tilting armature valve 100 shown in DE 10 2016 105 532 A1. In one variant, the tilting armature valve 100 may be the solenoid valve to which reference numeral 100 is assigned in FIG. 1 of DE 10 2016 105 532 A1. However, other embodiments are also conceivable, for example in connection with solenoid valves as described in other publications mentioned above. The plurality of embodiments of the solenoid valve described in DE 10 2016 105 532 A1, their components, and their use are also part of the disclosure of the present invention by reference.

[0029] Figure 1A shows a cross-sectional view of a tilting armature valve 100 with the armature body in a first position. The tilting armature valve 100 includes a coil element 110, an armature body (or simply armature) 115, a spring 120, a seal element 125, and a cover shell 130. The coil element 110, comprising a coil, coil core and coil bobbin as main components and configured rotationally symmetrically, includes at least one cylindrical coil core 135 having an axis of symmetry 137, a coil bobbin 128 circumferentially arranged around the coil core 135, and a coil 140 circumferentially arranged around the coil bobbin 128, comprising a packet (not clearly shown) consisting of coil windings. The end face of the armature 115 is supported against the housing 170 by a support 145. The armature body 115 is movable between a first position 147 and a second position 149. The armature body 115 is configured to move from a first position 147 to a second (suctioned) position 149 when the coil 140 is actuated. When the coil 140 is actuated, the armature body 115 can be held in the second position 149. A seal element 125 is further positioned on the side of the armature 115 that faces away from the coil element 110. The cover shell 130 has a valve seat 150 with an outlet 155 for the fluid 158 and an inlet 157. When the armature 115 is in the first position 147, the outlet 155 can be fluid-tightly closed by the seal element 125. Here, the seal element 125 may also act as a damper element to prevent the armature 115 from colliding with the valve seat 150. The seal element 125 may here be attached to the armature body 115 or a support element by a rubber coating. It is also conceivable that an angle is formed by the angled nozzle, or the angled seal element 125, or the curved armature 115, when the armature 115 or seal element 125 collides with the valve seat 150. Such a nozzle, not explicitly shown in Figure 1A, does not necessarily have to be incorporated into the tilting armature valve 100, but may be provided by an external housing portion.

[0030] Another possibility is that the valve seat 150 is located on the coil element 110, but this is not explicitly shown in Figure 1A for clarity. In this case, an operating part that mediates the opening of the outlet by the armature body 115 would be advantageous.

[0031] In this embodiment, the armature body 115 has at least one protrusion 160 on the support portion 162, which is at least partially rounded, and the protrusion 160 engages with, for example, a recess 165 or opening located in the portion of the housing 170 of the tilting armature valve 100 or the coil reel 128 that is opposite to the protrusion 160. This allows the armature body 115 to slide in the recess as it moves from a first position 147 to a second position 149 after the current flow through the coil 140 is switched on, and at the same time, it is held in a fixed position in the housing 170 or against the cover shell 130. The recess is formed in a trapezoidal shape, which creates as little friction as possible when the protrusion slides on the upper surface of the recess 165. The recess 165 may be made of, for example, a plastic material.

[0032] In this embodiment, the spring 120 is configured as a leaf spring and is positioned in the support portion on the opposite side of the armature 115 from the coil 140. The spring 120 is used here to press the support ball, which is press-fitted into the armature body 115, for example, into the opposing shell or recess 165 (e.g., trapezoidal) in the housing 170 of the coil element 110, without any play. The armature body 115 is fixed by the spring 120, thereby holding the armature 115 in a predetermined position by the spring 120. This provides the advantage that a constant preload force can be applied to the armature 115, and the force applied to the armature 115 by the spring 120 can be applied to the armature body 115 as close as possible to the point of force application located on the axis of rotation of the support.

[0033] Alternatively, the armature body 115 can be suspended from the coil element 110. In this case, the spring 120, which is formed as a leaf spring, can be omitted.

[0034] Figure 1B shows a cross-sectional view of the tilting armature valve 100 with the armature body 115 in the second position 149. In this case, the current through the coil 140 is switched on, and the armature body 115 is attracted, thereby forming a magnetic field indicated by the magnetic field lines 180. When the current through the coil 140 is switched off, the armature body 115 can fall back to its original position 147, for example, by gravity or the spring force of the illustrated return spring 195.

[0035] Figure 2 shows a perspective view of an exemplary known armature body 115 for use in a tilting armature valve 100. The armature body 115 is configured here as a plate armature. In addition to the seal element 125, the armature body 115 has two balls press-fitted as protrusions 160, 160a, which are positioned in a direction that forms the bearing rotation axis A of the armature body 115 when it rotates after the current through the coil 140 is switched on. This means that the protrusions 160, 160a are positioned on or along the bearing rotation axis A. The protrusions 160, 160a form part of a support device for positioning the armature body 115 on the end face of the coil element 110. A spring mounting portion 196 is provided in the center of the armature body 115, which works in cooperation with the return spring 195 to prevent the return spring 195 from slipping off the armature body 115. Through the spring mounting portion 196, the return spring 195 can preload the armature body 115 toward a first position, thereby closing the valve when the coil 140 is not energized.

[0036] Figure 3 shows a schematic cross-sectional view of the armature body 115 in the housing 170 along the disk surface of the armature body according to one embodiment of the electromagnetic actuator 105 according to the present invention. The armature body 115 in Figure 3 is arranged in a rotationally symmetric, particularly cylindrical (and similarly preferably cylindrical) housing space 171, thereby forming an annular gap between the outer circumference of the armature body 115 and the inner surface 172 of the housing 170. The armature body 115 is configured in a disc or plate shape and has a shape that is symmetric with respect to a symmetry axis S located on the disk surface (in particular, axisymmetric). The disc or plate shape specifically means that the armature body 115 has a thickness (perpendicular to the disk surface) that is smaller than the extended length of the armature body 115 on the disk surface. The armature body 115 is supported on one side by a support 145 relative to the housing 170, as illustrated with reference to Figure 1, and is movable between a first position 147 and a second position 149 along the support rotation axis A. The support 145 is located, for example, near the end of the armature body 115, particularly near the first end 116. The support rotation axis A is oriented laterally with respect to the axis of symmetry S, particularly perpendicularly, and parallel to the disk surface as well as the axis of symmetry S. The support is exemplary formed by two support portions 161, 161a located along and spaced apart along the support rotation axis A (for example, in the form of a recess in the armature body as shown in Figure 3), which allow the armature body 115 to rotate around the support rotation axis A. The support portions 161 and 161a may be configured, for example, as recesses, or as raised portions, for example, as illustrated in Figure 2 based on the raised portions 160 and 160a, according to various viewpoints. Numerous support configurations are available.

[0037] The support portions 161 and 161a are located in a region radially outward of the armature body 115 with respect to the center point M, which in this embodiment is the intersection of the central axis in the normal direction of the armature body 115 and the disk surface. This means that the support rotation axis A is also located in a region radially outward of the armature body 115. In the assembled state of the armature body 115, the center point M is positioned to be approximately aligned with the axis of symmetry 137 of the coil core 135. In the assembled state, the armature body 115 extends radially across the coil core 135 with respect to the axis of symmetry 137.

[0038] The armature body 115 is supported on one side relative to the housing 170, so that the majority of the armature body 115 forms a lever arm to which a magnetic force generated by the magnetic field of the coil device can be applied to move the armature body 115 to a second position 149. The lever arm substantially extends from the pivot axis A of the bearing to a second end 117 of the armature body 115, which is located away from the pivot axis A of the bearing. Support on one side of the armature body preferably means that the support portion is located at the end face side of the armature body, or in the region between the end face side and the center point.

[0039] The armature body 115 has a first maximum extension length D1 in the direction of the axis of symmetry S, i.e., between the first end 116 and the second end 117 in this embodiment. The maximum extension length D1 corresponds in particular to the maximum diameter of the armature body 115. The armature body 115 further has a second maximum extension length D2 in the direction of the bearing rotation axis A, between the third end 118 and the fourth end 119. The second maximum extension length D2 is shorter than the first maximum extension length D1. The second maximum extension length D2 corresponds in particular to the minimum diameter of the armature body 115.

[0040] In the armature body 115, the first maximum extending length D1 has a first, in particular, maximum diameter, and the second maximum extending length D2 has a second, in particular, minimum diameter. This means that the armature body 115 has a convex, in particular, elliptical outer contour. In particular, in this embodiment, the armature body 115 has a flat, rounded convex outer contour on the disk surface. The armature body 115 has two first regions 115a opposite to each other, each having a rounded (e.g., circular) outer contour K in the direction of the axis of symmetry S. The first end 116 and the second end 117 of the armature body 115 are located in the corresponding regions 115a. The armature body 115 has two second regions 115b opposite to each other, in the direction of the bearing rotation axis A. The second region 115b, which is opposite to the first region 115a, has a flatter or flattened outer contour F than the first region 115a.

[0041] In this embodiment, the circular outer contour K has a radius r1 that is slightly smaller than the inner radius of the housing space 171, starting from, for example, the central axis of the armature body 115, and as a result, a gap 191 remains between the first region 115a and the inner surface of the housing space 171.

[0042] In this embodiment, the barrel-shaped outer contour F has a radius r2 or r3 that is larger than radius r1. In Figure 3, the measurement point P1 for radius r2 is located between the central axis and the second region 115b on the right. In Figure 3, the measurement point P2 for radius r3 is located between the central axis and the second region 115b on the opposite side.

[0043] In line with the intent of this disclosure, a barrel-shaped contour particularly includes having at least one contour or sub-contour having a rounded or curved shape, especially an outwardly curved (convex) shape, particularly a shape different from an arc shape. In this case, for example, the exact barrel shape in a mathematical sense is not important, but the curved or rounded sides that narrow the disk shape, especially those that differ from an arc shape, are all the more important, as these sides may have special advantages with respect to positioning under tolerance conditions. Thus, for example, elliptical, oval, or other elongated rounded or curved contours should also be included by this concept. Furthermore, partially or locally linear contours may be provided in the contour region, located between the rounded contour regions.

[0044] Since the outer contour F is flatter than the outer contour K, when the armature body 115 is symmetrically oriented with respect to the housing space 171 of the housing 170 on the disk surface, the gap 191 in the direction of the axis of symmetry S between the armature body 115 at the position of the first maximum extension length D1 and the adjacent portion of the housing 170 is smaller than the gap 192 in the direction of the bearing rotation axis A between the armature body 115 at the position of the second maximum extension length D2 and the adjacent portion of the housing 170.

[0045] Figure 4 shows the armature body 115 in a deflected position, particularly when rotated under tolerance conditions, for example, in the attracted second position 149 in Figure 1, for example, under the influence of a magnetic force. Figure 4 also shows an exemplary position of the armature body 115 when a magnetic field is generated, for example, by a coil device. Due to tolerances during the manufacture of the actuator and / or the cutting of the component members, the armature body 115 may be positioned eccentrically due to tolerances. This is due, for example, tolerances in the support body 145, tolerances during the molding of the armature body 115, and / or tolerances in the housing 170. This can result in the generation of a relatively large lateral force, which acts on the armature body 115 in the direction of the support body rotation axis A, thereby adding an additional load to the support body 145 and reducing the magnetic force in the working direction. Even if the armature body 115 pivots in the direction of the bearing rotation axis and moves eccentrically toward a portion of the housing 170, for example to the left portion of the housing 170 in Figure 4, a reduced, preferably minimal, gap 191 can be formed in the direction of the axis of symmetry S due to the configuration of the armature body 115 according to the present invention. However, the still relatively small gaps on both sides of the armature body 115 in the direction of the axis of symmetry S cause the magnetic flux to be subsequently deflected positively in the working direction, particularly toward the longest lever arm.

[0046] In Figure 4, the armature body 115 is not only displaced radially with respect to the axis of symmetry 137, but is also rotated within the housing 170. This clearly demonstrates that the armature body 115 can be linearly displaced by the magnetic field, as well as rotated around the axis of symmetry 137 of the coil core 135. This means that the support portions 161 and 161a are loaded not only along the axis of rotation A, but also partially along the axis of symmetry S.

[0047] The gap between the armature and the housing can be reduced on both sides (in the direction of the axis of symmetry S), in particular, depending on the wear that may occur in the support and the tolerances of the components. For example, depending on the manufacturing method, a rotation axis (axis of symmetry) perpendicular to the rotation axis of the support body can be defined, depending on the tolerance. Theoretically, the armature body can be rotated around this axis to the maximum tolerance, and the outer contour of the armature can be formed by the defined minimum gap. This results in a round disc shape with a lateral barrel-shaped flattening portion relative to the original diameter. This provides greater robustness in terms of wear and manufacturing tolerances without significantly negatively impacting magnetic force and manufacturing costs. [Explanation of symbols]

[0048] 100 Tilting Armature Valve 105 Electromagnetic Actuator 110 coil elements 115 Armature Body 115a First area 115b Second area 116 First end 117 Second end 118 Third end 119 The fourth end 120 springs 125 seal elements 128 coil winding frame 130 Cover Shell 135 Coil Cores 137 Axis of Symmetry 140 coils 145 Supporting body 147 First Position 149 Second position 150 valve seats 155 Exit 157 Entrance 158 Fluid 160,160a ridge 161,161a Support part 162 Support part 165 recess 170 Housing 171 Containment Space 172 Inner surface 180 Magnetic field 191 void 192 void 195 Return spring 196 Spring mounting part A. Rotation axis of the support body D1 Extended length / diameter D2 Extended length / diameter F Flattened outer contour K Circular outer contour S axis of symmetry M center point P1 measurement point P2 measurement point r1 radius r2 radius r3 radius

Claims

1. An electromagnetic actuator (105), A coil device (135, 140) comprising at least one coil core (135) and coils (140) arranged circumferentially around the at least one coil core (135), A cylindrical housing (170) having a rotationally symmetric housing space (171) in which a magnetic material and the coil device (135, 140) are at least partially housed, A movable magnetic armature body (115) as a movable actuator element, wherein the armature body (115) is positioned in the housing space (171) of the housing (170) such that a circumferential gap is formed between the outer circumference of the armature body (115) and the inner surface (172) of the housing (170), and is movable by a magnetic field (180) generated by the coil device (135, 140), and is supported on one side by a support (145) with respect to the housing (170) and is movable from a first position (147) to a second position (149) around the rotation axis (A) of the support, The armature body (115) is configured in a disc shape and has a shape that is symmetrical in the lateral direction with respect to the bearing rotation axis (A) with respect to the axis of symmetry (S) located on the disc surface, the armature body (115) has a first maximum extension length (D1) between the opposite ends of the armature body (115) in the direction of the axis of symmetry (S), and a second maximum extension length (D2) shorter than the first maximum extension length (D1) between the opposite ends of the armature body (115) in the direction of the bearing rotation axis (A). The support body (145) has at least two support body portions (161, 161a) arranged along the support body rotation axis (A) and spaced apart from each other, the support body portions (161, 161a) are formed in the armature body (115) in the form of recesses or protrusions, and the support body portions (161, 161a) enable the armature body (115) to rotate around the support body rotation axis (A). The armature body (115) has two opposing first regions (115a) each having a rounded outer contour (K) in the direction of the axis of symmetry (S), and two opposing second regions (115b) each having a flattened outer contour (F) relative to the first region (115a) in the direction of the axis of rotation of the support body (A). Electromagnetic actuator (105).

2. The electromagnetic actuator (105) according to claim 1, wherein the axis of symmetry (S) is arranged perpendicular to the axis of rotation of the support body (A).

3. The electromagnetic actuator (105) according to claim 1, wherein the first maximum extending length is the first diameter (D1) of the armature body (115), and the second maximum extending length is the second diameter (D2) of the armature body (115).

4. The electromagnetic actuator (105) according to claim 1, wherein the first maximum extending length is the maximum diameter (D1) of the armature body (115), and the second maximum extending length is the minimum diameter (D2) of the armature body (115).

5. The electromagnetic actuator (105) according to claim 1, wherein the armature body (115) has a convex, particularly elliptical, outer contour on the disk surface.

6. The electromagnetic actuator (105) according to claim 1, wherein each of the two first regions (115a) opposite to each other has a circular outer contour (K).

7. The electromagnetic actuator (105) according to claim 1, wherein each of the flattened outer contours (F) is configured in a barrel shape.

8. The electromagnetic actuator (105) according to claim 1, wherein the housing space (171) of the housing (170) is configured in a cylindrical shape.

9. The electromagnetic actuator (105) according to claim 1, wherein, when the armature body (115) is oriented symmetrically with respect to the housing space (171) of the housing (170) on the disk surface, the gap (191) in the direction of the axis of symmetry (S) between the armature body (115) and the adjacent portion of the housing (170) at the position of the first maximum extension length (D1) is smaller than the gap (192) in the direction of the support rotation axis (A) between the armature body (115) and the adjacent portion of the housing (170) at the position of the second maximum extension length (D2).

10. The coil core (135) has a rotationally symmetric region with a symmetry axis (137) in which the coil core (135) is surrounded in the circumferential direction by the coil (140), The electromagnetic actuator (105) according to claim 1, wherein the support body (145) is positioned to be radially displaced with respect to the axis of symmetry (137) of the coil core (135), and the armature body (115) extends radially beyond the coil core (135).

11. The electromagnetic actuator (105) is configured as an electromagnetic switching device or valve device (100) comprising the armature body (115) as a switching element or valve element, and is particularly configured as an electromechanical relay or solenoid valve (100), according to claim 1.

12. The electromagnetic actuator (105) according to claim 1, wherein the electromagnetic actuator is configured as a tilting armature valve (100).

13. The electromagnetic actuator (105) according to any one of claims 1 to 12, wherein the electromagnetic actuator (105) is configured as a solenoid valve (100) for a vehicle pressure control module.

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