Electromagnet with damping element

Abstract

Electromagnet in which an armature (2) is movably mounted in an armature chamber (29), the electromagnet (9) has a coil (90) having windings of wire capable of carrying an electric current, and the armature (2) is in operative connection with an armature rod (20), wherein the armature rod (20) penetrates a magnetic core (91) which delimits the armature chamber (29) at least on one side, and the armature rod (20) carries a damping element (1) on the side facing away from the armature chamber (29). wherein the damping element serves to decelerate the anchor (2) or an anchor rod (20), wherein the damping element (1) has a penetration opening (11) bounded by an inner wall (10) and a radial outer area (12), and is made of elastic material and wherein the inner wall (10) carries or has an inner sealing arrangement (30) and / or the outer area (12) carries or has an outer sealing arrangement (32), wherein a spring element (5) is embedded in the damping element (1), which is made of a different material than the elastic material of the damping element (1), wherein the spring element (5) is designed in a ring-like form, wherein in section the ring (50) of the spring element (5) is at least partially V-shaped, N-shaped or W-shaped, wherein when the spring element is designed with a V-shaped cross-section the opening (54) of the V-shaped ring (50) is directed radially outwards or inwards, and wherein the anchor rod (20) projects through the penetration opening (11), and the anchor rod (20) carries on the side facing away from the anchor space (29) a baffle ring (21) which, when the electromagnet (9) is energized, in conjunction with the damping element (1) decelerates the anchor rod (20).

Description

[0001] The invention relates to an electromagnet in which an armature is movably mounted in an armature chamber, wherein the electromagnet has a coil having windings of wire capable of carrying an electric current and the armature is in operative connection with an armature rod, wherein the armature rod penetrates a magnetic core that delimits the armature chamber at least on one side.

[0002] The electromagnets described above are well known in the prior art. They are used, for example, as switching or lifting magnets, where a fast switching response is particularly important. This means that when current is energized into the coil, which carries the windings of current-conducting wire (i.e., wire capable of carrying current), the resulting magnetic field causes the armature, which is movably mounted in the armature chamber and consists of magnetizable material, to move. When the (electro)magnetic field is applied, the armature attempts to close the air gap at the end of the armature chamber, usually in the direction of the magnetic core.

[0003] This makes it possible to easily convert an electrical current signal into a mechanical movement. Typically, the armature is accelerated against the force of a return spring towards the magnetic core and then strikes the surfaces of the magnetic core that define the armature chamber with high energy. It is irrelevant whether the magnetic core completely defines the impact surface or only partially, i.e., whether the magnetic core and another element together form the impact surface. Both situations are encompassed by the definition of an armature chamber that is bounded at least on one side by the magnetic core.

[0004] Both the magnetic core and the armature are typically made of hard magnetic material, which is advantageous for guiding the magnetic field. The impact of the armature on the metal surface of the magnetic core is not silent, therefore noise reduction or damping is desirable.

[0005] Therefore, concepts exist in which a damping element is arranged in the armature chamber, in the area of ​​the air gap, to serve for noise reduction. However, this element is then located in the magnetically important air gap, i.e., the air gap that is significant for the configuration and formation of the magnetic field, and therefore impairs the magnetic efficiency and thus also the mechanical efficiency of the entire electromagnet.

[0006] Document DE 100 17 030 A1 discloses a solenoid valve with a fixed core arranged in a magnet and an armature movable between two end positions, which interacts with a valve seat fixed to the housing when the valve is actuated.

[0007] Document DE 101 61 995 A1 discloses a solenoid valve for tank venting in motor vehicles with at least one valve opening forming a sealing seat and a valve element cooperating with this sealing seat for releasing and closing the sealing seat.

[0008] Document DE 10 2007 030 311 A1 discloses a diaphragm pump with a diaphragm and a lifting magnet.

[0009] Document DE 10 2011 078 102 A1 discloses an electromagnetically actuated seat valve with a stop for a magnetic armature.

[0010] The invention therefore aims to improve the state of the art in such a way that an electromagnet with better efficiency is available.

[0011] To solve this problem, the invention starts with an electromagnet as described above, wherein the armature rod carries a damping element on its side facing away from the armature chamber, the damping element having a penetration opening through which the armature rod projects. The armature rod carries an impact ring on the side facing away from the armature chamber, which, when the electromagnet is energized, decelerates the armature rod in conjunction with the damping element.

[0012] The invention proposes that the damping element is no longer arranged in the armature chamber, but outside of it. This eliminates any impairment of the magnetic properties and thus also of the mechanical properties by the damping element.

[0013] Furthermore, the impact ring mounted on or positioned on the anchor rod significantly improves the guidance of the anchor rod towards the damping element. This results in an overall improvement in damping performance, as equivalent contact between the impact ring and the damping element is achieved via the guided anchor rod. Impact energy is thus efficiently and reliably dissipated, effectively minimizing or essentially preventing noise generation.

[0014] A damping element, in particular an anchor or anchor rod damping element, can be used to decelerate a moving anchor or anchor rod. The damping element has a through-opening bounded by an inner wall and a radial outer surface and is made of elastic material. The inner wall and / or the outer surface also incorporate or include a sealing arrangement.

[0015] Electromagnets of this type are often used in applications where they are in direct contact with potentially aggressive media. It is undesirable for these media, whether liquid or gaseous, to enter the interior of the electromagnet, for example, the armature chamber. Besides the risk of contamination, the operational readiness of the electromagnet must also be considered, as it can be impaired if a medium is unintentionally present in or penetrates the armature chamber.

[0016] Therefore, to solve the problem posed at the outset, an improved sealing element is cleverly proposed, which, as described, is equipped with a sealing arrangement on the inner wall and / or the outer surface. The damping element thus performs both a damping function and, depending on the configuration, a sealing function.

[0017] Typically, the damping element is installed in a stable position within the electromagnet (for example, in a pocket or recess). This allows the damping element to perform sealing functions both with respect to the interior of the electromagnet and / or sealing functions towards the armature rod. Simultaneously, the impact of the impact ring is dampened, and noise emissions are reduced.

[0018] It should be noted that the damping element can be located not only on the anchor rod, but also on or associated with the anchor in order to be usable as described.

[0019] A spring element is embedded in or arranged within the damping element. This spring element is made of a material different from that of the actual damping element. The spring element is preferably made of or formed from spring steel. For the purposes of this invention, spring steel is defined as a steel exhibiting high strength and elasticity.

[0020] The spring element used in the damper is ring-shaped. In cross-section, this ring of the spring element, or the ring forming the spring element, is at least partially V-shaped, N-shaped, or W-shaped. A bellows-like design of the spring element is also conceivable, with the individual folds of the bellows extending radially into the damper element, and deformation of the spring element occurring in the axial and / or radial direction when the spring element is compressed.

[0021] It is intended that, when the spring element is designed with a V-shaped cross-section, the opening of the V-shaped ring is oriented radially outwards or inwards. In the first embodiment, the apex of the two legs of the spring element forming the V-shaped ring is located on the inside of the damper element, i.e., where the anchor rod is guided within the damper element. The second alternative embodiment provides that the apex is located within the damper element itself, and that both legs of the V-shaped ring are oriented towards the interior of the damper element, with their ends or end regions further improving or supporting the guidance of the anchor rod. There is no difference in the actual spring action; rather, the spring action is independent of the orientation of the V-shaped ring or its arrangement within the damper element.

[0022] The damping element itself is preferably made of an elastic material. Rubber, synthetic rubber, fluororubber, low-temperature rubber, nitrile rubber (NBR), or polyurethane (PU) are particularly suitable in this context. The preceding list of usable elastic materials is not limited to those mentioned. Naturally, any elastic material known to those skilled in the art can be used for manufacturing the damping element. The choice of material is also determined by the ultimate application of the electromagnet equipped with the damping element. For example, if the electromagnet is intended for use in an aggressive atmosphere, the material of the elastic damping element is selected accordingly to minimize reactions with the surrounding atmosphere, such as dissolution or corrosion.Furthermore, a different material is chosen for use in oil-containing media than, for example, for use in oil-free media. All suitable materials are equally encompassed by the invention.

[0023] In an advantageous embodiment of the damping element, it has an impact zone at its end, which serves to interact with an impact ring or impact element provided therein when the anchor rod decelerates. The impact zone provides at least one impact surface and at least one recessed relief surface. Displacement of damping element material can occur in the direction of the relief surface at the moment of impact of the impact ring and during deceleration.

[0024] The impact surface can be segmented and feature a multitude of adjacent impact zones as well as recessed relief areas. The segments extend radially from the penetration opening towards the surrounding area of ​​the electromagnet or the area housing the damping element, or towards the outer surface of the damping element. Any further geometric or symmetrical subdivision is also possible.

[0025] To further improve the damping suitability and effect of the damping element, it is proposed to design the impact area as convex, domed, or spherical. This will particularly enhance the deformability of the damping element, resulting in even better damping performance. Furthermore, the structuring of the damping element and the impact area will improve sound insulation, further reducing noise emissions from the electromagnet due to the damping element's presence there.

[0026] The damping element is designed to have a support area on its side opposite the impact zone, or at its end furthest from the impact zone. This support area is preferably located on the radial outer surface of the damping element and serves, among other things, to accommodate a support ring. This support ring secures the entire damping element within the electromagnet, preferably within the magnetic core, and provides support for the damping element. The width of the support area can be arbitrarily selected and adapted to the specific application point or area within the electromagnet. A stepped or stair-like design of the support area is also conceivable, allowing for adaptation to the support ring to be inserted or placed upon it, which would then be partially recessed into the damping element.This significantly improves the functional connection between the support area and the support ring, and improves the arrangement of the damping element in the electromagnet.

[0027] One advantageous embodiment of the damping element provides that the damping element has an internal sealing arrangement on its side facing away from the impact area, corresponding to the penetration opening. This internal sealing arrangement is preferably formed by an annular sealing lip that rests against the anchor rod protruding through the damping element and thus performs an additional sealing function. The sealing lips are designed to be elastic or flexible relative to the anchor rod to a limited extent, allowing for virtually play-free guidance of the anchor rod by the sealing lips. The length of the sealing lips is determined by the installation situation as well as the overall height or axial length of the damping element.

[0028] In a preferred embodiment, the damping element is characterized by the fact that the support area is recessed relative to the inner sealing arrangement, which is formed by the annular sealing lip. "Recessed" in this context means that the damping element is axially shortened in the support area, thus exhibiting a greater thickness or axial length in the area of ​​the inner sealing arrangement than in the support area. Consequently, the inner sealing arrangement, formed by the annular sealing lip attached to the damping element, is extended relative to the support area. The inner sealing arrangement therefore projects beyond the rest of the damping element and, in particular, beyond the support area.

[0029] In a preferred embodiment, the damping element is provided with an external sealing arrangement. This external sealing arrangement is preferably formed by a hull-like sealing surface located on the outer circumference of the damping element, resembling a circumferential or hull-like surface. This sealing surface is in direct contact with the insertion area of ​​the damping element within the electromagnet or magnetic core and seals it against ingress of media or the like.

[0030] It is considered advantageous if the sealing surface additionally features at least one circumferential sealing strip or lip. This significantly improves the sealing effect and effectively increases the fit of the damper element when inserted into the insertion position. Besides the design with a single circumferential sealing strip, it is of course possible to provide a sealing structure with multiple sealing strips on the circumferential or shell-like sealing surface, for example, a labyrinth seal or the like, in order to further improve the sealing effect and effectively prevent media from creeping into the interior of the electromagnet. The sealing strips are slightly compressed when the damper element is inserted, which further improves the sealing performance.

[0031] In a particularly advantageous embodiment, the damping element is characterized by the fact that the inner diameter of the penetration opening is variable in the axial direction. This creates space in the event of impact from the impact ring, allowing the damping element to expand or evade the impact. Upon impact and during the deceleration of the anchor rod, the inner diameter portion of the penetration opening, which has a larger diameter than the anchor rod, is compressed and elastically deformed in the direction of the anchor rod or the free or compensating spaces provided in the magnetic core.The inner diameter of the penetration opening at the point where the anchor rod exits the damper element is smaller than the inner diameter at the point where it enters, allowing the internal sealing arrangement to rest against the anchor rod and provide a seal. Of course, the damper element is not limited to the configuration described above. Besides having the same inner diameter across its entire axial length, it is also possible for the inner diameter at the point where the anchor rod enters the damper element (i.e., at the end of the damper element facing the magnetic core or anchor) to be smaller than at the opposite point where it exits.Naturally, the inner diameter can be chosen to be the same size across the entire damping element; upon impact, the material of the damping element is then displaced away from the anchor rod into corresponding compensation spaces, which are provided in the operating area of ​​the damping element, for example, in a recess provided in the magnetic core.

[0032] The damping element has an axial length, that is, a length measured in the direction of movement of the armature or armature rod, which in this context is defined as the axial length. The axial length defines the overall thickness or depth of the damping element and is adapted to the available space in the operating area. In addition to its axial length, the damping element also has a width or diameter, which is likewise adapted to its position within the electromagnet.

[0033] An advantageous embodiment of the damping element provides that the axial length of the outer surface of the damping element, which carries the shell-like sealing surface, is approximately 30 to 60%, preferably 40 to 50%, of the total axial length of the sealing element. In contrast, the impact zone, which also has an axial length in relation to the overall structure of the damping element, is also axially defined. In addition, the impact zone naturally has a diameter that can vary along its axial length. This diameter variation is determined by the shape of the impact zone. It is considered advantageous if the axial length of the impact zone is approximately 30 to 60%, preferably approximately 40 to 50%, of the damping element.In preferred embodiments, the damping element also has a projection that includes the inner sealing arrangement, as described above, and is considered a region of the damping element that extends its axial length. In this context, it is considered advantageous if the axial length of the projection or the inner sealing arrangement is 0 to 40%, preferably 0% or 5 to 20%, of the total length of the damping element. The total axial length of the damping element is the sum of the axial lengths of the outer area, the impact area, and the projection, and thus also defines the length or depth of the insertion area of ​​the damping element or a recess in the electromagnet or magnetic core. These recesses can, of course, have an extension or widening at the point where the damping element is to be inserted.A cup-shaped recess or depression into which the damping element is inserted is also conceivable. The extension or cup-shaped depression is provided on the side of the electromagnet facing away from the armature chamber or the air gap provided there, or on the opposite side.

[0034] With respect to the axial length of the damping element, the spring element is preferably positioned centrally within the damping element. This means that the distances to the impact area and to the protrusion with the internal sealing arrangement are equal or nearly equal. The arrangement of the spring element can also be adapted to the specific functionality of the damping element or the spatial conditions at the point of application or location of the damping element. The damping performance or spring action of the spring element is also defined by its position within the damping element.In addition to the central arrangement with approximately equal distances to the entrance and exit of the penetration opening, a displacement of the position of the spring element in the damper element can be provided and this can be arranged further towards the area of ​​the entrance of the penetration opening, that is, the end of the damper element assigned to the anchor or anchor space, or in the opposite direction towards the exit area of ​​the anchor rod from the damper element.

[0035] An advantageous further development or alternative embodiment of the damping element provides that, viewed from the impact area to the support area, the spring element is arranged in front of the outer surface. Here, too, the positioning of the spring element depends on the spatial conditions within the electromagnet and / or the desired spring or damping effect.

[0036] One embodiment of the damping element, considered advantageous, provides that the inner diameter of the penetration opening in the inlet area, i.e., on the side facing the anchor or anchor chamber, is larger than at the outlet area of ​​the anchor rod, i.e., at the end of the damping element facing away from the anchor chamber. It is also considered advantageous if the ratio of the overall diameter to the diameter of the outlet or penetration opening is 3:1, with ratios of 2:1, 2.5:1, 3.5:1, and 4:1 being particularly conceivable and possible. All intermediate values ​​are also covered by the invention.

[0037] The spring element, which forms part of the damper element, can also be defined by the ratio of its outer diameter to its inner diameter. This ratio is preferably 1.5:1, although deviations from this ratio of ±25%, particularly ±20%, preferably ±10%, and particularly preferably ±5% are also possible and are equally covered by the invention. Advantages of this are that the spring constant of the spring element can be adjusted via the ratio of its outer diameter to its inner diameter, and at the same time, the dimensions of the spring element can be matched to the damper element.

[0038] In contrast, the outer diameter of the damping element to the outer diameter of the spring element preferably has a ratio of 1.6:1. Of course, this ratio can also be larger or smaller, preferably by 25% larger or smaller, particularly preferably by 20% larger or smaller, and most preferably by 10% larger or smaller.

[0039] It is advantageous if the spring element has an outer diameter that approximately corresponds to the outer diameter of the impact ring arranged on the anchor rod. This significantly improves the ability to transfer impact energy into the spring element and simplifies or improves the dissipation of the impact energy.

[0040] The damping element is characterized by a ratio of total axial length to the axial length of the outer sealing area or cladding-like sealing surface of 2.5:1. Of course, this ratio can also have an interval of 0 to 25%, preferably 0 to 20%, and particularly preferably 0 to 10%.

[0041] In the electromagnet described above, an armature is movably mounted in an armature chamber, and the electromagnet has a coil with windings of wire capable of carrying an electric current. The armature is operatively connected to an armature rod that penetrates a magnetic core which at least partially delimits the armature chamber. On its side facing away from the armature chamber, that is, in the region of the magnetic core facing away from the armature chamber, the armature rod carries a damping element, or a damping element is associated with the armature rod, which has a penetration opening through which the armature rod projects or is guided. The damping element is designed as described previously. The armature rod also carries an impact ring on its side facing away from the armature chamber.When the electromagnet is energized, and the armature and the attached armature rod are thereby accelerated, this impact ring interacts with the damping element and, upon contact with the damping element, decelerates the movement of the armature rod. The damping element is designed in such a way that the impact energy transferred to the damping element via the impact ring is effectively dissipated, compressed, or diverted.

[0042] In this context, it proves advantageous if the impact ring is positioned between the damping element and the magnetic core. It is particularly beneficial if both the damping element and the impact ring are located outside the armature chamber and outside the air gap. This results in advantages regarding the guidance and formation of the magnetic field and magnetic field lines. A disruptive element is no longer present in the armature chamber, as it is relocated to the magnetic core or to the area outside the armature chamber. This significantly simplifies the adjustment of the electromagnetic characteristics and improves the electromagnet's performance.

[0043] In contrast to electromagnets that do not have a damping element, or those electromagnets where the damping element is provided in the armature chamber, significantly lower noise emissions result from the impact of the impact ring or the armature in conventional electromagnets that do not have a damping element.

[0044] The impact ring, or an impact element such as a projection, a nose, a knob, a strip, or a flange, is preferably arranged integrally on the armature rod and can be taken into account during the manufacture of the armature rod or be integrally formed on it. An alternative embodiment of the electromagnet according to the invention provides that the impact ring is manufactured as a separate component and can be connected to the armature rod in a positionally stable manner in a joining, connecting, or pressing process. In this embodiment, after the armature rod or the armature has been inserted into the electromagnet and, for example, also after the magnetic core has been installed, the impact ring or impact element is pushed onto the armature rod and pressed to it or connected in another suitable manner, for example, by welding or bonding.

[0045] It is considered advantageous, also from the perspective of dissipating, absorbing, or compensating the impact energy by the damping element, if the ratio of the ring width of the impact ring to the ring width of the spring element is in the range of 0.8 to 1.2, preferably from 0.9 to 1.1. The impact ring advantageously impacts the impact area provided on the damping element. Here, the impact energy is already dissipated or absorbed by the elastic damping element. This element deflects away from the impact ring, particularly in the radial direction, thereby dissipating the transferred impact energy. This results in the effective deceleration of the anchor rod.If the damping element also includes a structured impact area, for example a segmented or segmentally subdivided impact area with protruding impact surfaces and recessed relief surfaces, then even more efficient deceleration or dissipation of the impact energy can take place, as additional space for the elastic material to move away from the impact is created.

[0046] A further development of the electromagnet, considered advantageous, involves arranging the damping element in a recess on or within the magnetic core. Naturally, the magnetic core may have a projection or attached collar, or a sleeve- or cup-shaped extension into which the damping element is inserted or held. The damping element, which preferably has a support area, allows a support ring, also insertable within the magnetic core or the insertion area for the damping element, to bear against this support area. The support ring is in close contact with the support area and prevents the damping element from being dislodged from the electromagnet or magnetic core upon impact with the impact ring. The support ring thus secures the damping element and its position within the electromagnet.

[0047] The invention is schematically illustrated in the drawings, particularly in one exemplary embodiment. The drawings show: Fig. 1 A preferred embodiment of the electromagnet according to the invention in sectional view Fig. 2a a preferred embodiment of the damping element according to the invention in a lateral sectional view Fig. 2b another embodiment of the damping element according to the invention, also in sectional view

[0048] In the figures, identical or corresponding elements are designated with the same reference symbols and are therefore not described again unless it is expedient.

[0049] Fig. Figure 1 shows an electromagnet 9 in a possible embodiment according to the present invention. The electromagnet 9 has an armature chamber 29 in which an armature 2 is movably mounted. The electromagnet 9 also has a coil 90 with windings of wire capable of carrying an electric current. The armature 2 is operatively connected to an armature rod 20. This armature rod 20 penetrates a magnetic core 91 that delimits the armature chamber 29 at least on one side. When the electromagnet 9 is energized, the armature 2 and the armature rod 20 arranged thereon move in the axial direction 17 of the electromagnet 9. The magnetic core 91 has an inserted damper element 1. This is inserted on the side of the magnetic core 91 facing away from the armature chamber 29. The armature rod 20 also penetrates the damper element 1 and then exits the armature chamber 29 or magnetic core 91.The damping element 1 has a penetration opening 11 for this purpose, such as that of the . Fig. 2a is removable. The anchor rod 20 also carries an impact ring 21. This is arranged between the anchor chamber 29 and the damping element 1 on the anchor rod 20. The impact ring 21 is located in the area of ​​the anchor rod 20 that lies outside the anchor chamber 29 and inside the magnetic core 91. When the electromagnet 9 is energized and the armature moves, the impact ring 21 strikes the damping element 1 and thereby decelerates the anchor rod 20.

[0050] The damping element 1 itself is inserted into a recess 92 of the magnetic core 91. In addition to the recess 92, the magnetic core 91 has a circumferential collar in the area of ​​the recess 92, which partially projects beyond the magnetic core 91 and partially provides the receptacle for the damping element 1.

[0051] When mounting the electromagnet 9, the damper element 1 is inserted into the recess 92 and additionally secured against falling out by the support ring 93. The support ring 93 contacts the support area 16 on the damper element 1. In conventional, in Fig. In the electromagnet 9 not shown, the damping element 1 is either completely absent or is arranged in the armature chamber 29 and thereby adversely affects the formation of an electromagnetic field. These disadvantages of conventional electromagnets 9 are overcome by the electromagnet 9 according to the invention.

[0052] In another alternative embodiment of the electromagnet 9 according to the invention, the damping element 1 is provided on the opposite side of the armature chamber 29, in the region of the armature 2, and dampens the impact energy of the armature 2 directly, for example, during its return movement. Further alternative embodiments of the electromagnet 9, which are likewise encompassed by the invention, provide for the arrangement of two damping elements 1 within the electromagnet 9. For example, one damping element 1 can still be arranged in the armature chamber 29, while a second damping element 1 is provided in the exit region of the armature rod 20. This significantly improves the damping performance.

[0053] In addition to its damping function, i.e., decelerating the anchor rod 20 and absorbing impact energy transmitted via the impact ring 21, the damping element 1 also performs a sealing function for the electromagnet 9. Thus, the damping element 1 effectively seals the exit area of ​​the anchor rod 20 and prevents the ingress of media located in the outer area of ​​the electromagnet 9. Sealing is achieved, firstly, via the outer sealing area 32 (see figure). Fig. 2a), which in the exemplary embodiment rests directly against the inner walls of the recess 92 and additionally has sealing strips 34 that enable an effective seal. Thus, the damping element 1 effectively prevents media from creeping into the interior of the electromagnet 9. Directly adjacent to the anchor rod 20, the damping element 1 has an internal sealing arrangement 30 (see figure 2a). Fig. 2a). This inner sealing arrangement 30 has a ring-shaped sealing lip 31 (see. Fig. 2a), which rests directly against the anchor rod 20 and ensures a seal. The length of the sealing lip 31 depends on the desired sealing performance and the type of medium against which the electromagnet 9 is to be sealed. Overall, the sealing lips 31 are designed to ensure permanent contact with the anchor rod 20. The sealing lips 31 also cause any media residue adhering to the anchor rod 20 to be wiped off on their surface facing away from the anchor rod 20, thus effectively preventing any ingress of the medium into the interior of the electromagnet 9. In addition to the support ring 93, a further end plate (in Fig. (1 not shown) are inserted into the recess 92 to close it and the damping element 1 arranged therein. This disc can then have a recess, opening, or bore through which the anchor rod 20 is guided. The recess 92 itself is, as shown in Fig. The recess 92 is recognizably shaped in a step- or staircase-like manner and has an overall cup-like configuration into which the damping element 1 is inserted. The damping element 1 rests with its outer sealing arrangement 32, or rather the section of the damping element 1 that defines the largest diameter of the damping element 1, on the first step 19 projecting into the recess 92 and is held by it. For this purpose, the damping element 1 has an additional shoulder 18 that is in contact with the step 19 in the recess 92. Otherwise, the damping element 1 has only a few contact points with the recess 92, so that some movement of the damping element 1, or of the elastic material forming the damping element, is possible within the recess 92.This allows the impact energy, which is introduced into the damping element 1 via the impact ring 21, to be effectively dissipated or compensated by the elastic deformation of the damping element 1.

[0054] Fig. Figure 2a shows a preferred embodiment of the damper element 1 according to the invention. This element has a damper body made of an elastically deformable material, in particular an elastomer. The damper element 1 can be manufactured, for example, by injection molding or in another suitable manner. Of course, cutting the damper element 1 from a solid material is also conceivable. To achieve a spring-like property, the damper element 1 incorporates the spring element 5, which in the exemplary embodiment is designed as a V-shaped ring 50 with a total of two legs 51, 52. The legs 51, 52 define an opening 54 of the spring element 5. The apex 53 of the V-shaped ring 50, or the leg 51, 52, is located in the exemplary embodiment of the Fig. 2a is inserted in or located in the damping element 1. In an alternative embodiment, the V-shaped ring 50 can also have a configuration reversed to that shown here. The apex 53 then lies in the area of ​​the opening 54, while the two legs 51, 52 of the V-shaped ring are received in the damping element 1. In addition to the configuration shown here as a V-shaped ring 50, it is of course also possible for the spring element 5 to be designed as a bellows-like spring, a disc spring, or the like. Naturally, the spring element 5 can also have an N-shaped, W-shaped, or Z-shaped configuration. The design of the spring element 5 must be selected depending on the desired spring action. The damping element 1 has a penetration opening 11 through which the anchor rod 20 protrudes when installed. As in Fig. In the embodiment of the damper element 1 shown in Figure 2a, the penetration opening 11 has an inner wall 10 that extends on both sides of the spring element 5 in the damper element 1. The penetration opening 11 in the exemplary embodiment of Fig. 2a, the area to the right of spring element 5 has a larger diameter d1, d2 than in the area of ​​the Fig. The damping element 1 is located to the left of the spring element 5. Due to the variable inner diameter d1, d2 of the damping element 1, an annular sealing lip 31 is formed, which rests against the anchor rod 20. In contrast, the increased diameter d2 of the damping element 1 provides space for the elastic material of the damping element to deflect when the damping element 1 is subjected to impact by the impact ring 21 on the anchor rod 20. The damping element 1 has an impact area 13 at its end, i.e., at the end facing the impact ring 21 in the installed state, which interacts with the impact ring 21 during deceleration. The impact area 13 provides an impact surface 14 for this purpose, which is directly contacted by the impact ring 21.In addition to the impact surface 14 or multiple impact surfaces 14, recessed relief surfaces 15 are provided in the impact area 13, arranged between the impact surfaces 14. This results in an overall segment-like subdivision of the impact surface 14. The projecting areas of the impact surface 14 are directly contacted by the impact ring 21 and absorb the impact energy. This causes elastic deformation of the damping element 1. The impact surfaces 14 expand in the direction of the relief surfaces 15, thus compensating for the impact energy transmitted via the impact ring 21. The remaining impact energy, which is not absorbed or compensated in this way, leads to compression of the spring element 5, resulting in further damping or deceleration of the anchor rod 20.

[0055] Naturally, the invention also includes embodiments of the damping element that have a continuous impact surface 14, i.e., without segmented subdivisions. In this case, the entire impact surface 14 serves as the impact surface for the impact ring 21, and the impact energy is transferred directly and immediately into the damping element 1 or the spring element 5. In addition to the flat design of the impact area 13 shown here, it is of course possible for this area to be convex, domed, or spherical. The arrangement of bead-, ring-, or groove-like structures in the impact area 13 or on the impact surface 14 is also conceivable.

[0056] The damping element 1, as in Fig. As shown in Figure 2a, the device additionally has an outer area 12 extending radially to the penetration opening 11, on the outer circumferential or lateral surface 32 of which an outer sealing arrangement 32 is provided. This outer sealing arrangement 32 has sealing strips 34 which are inserted directly into the recess 92 of the magnetic core 91 and interact with the inner surface there. The sealing strips 34, the number of which is not specified in Figure 2a, are arranged in a manner that allows for the connection of the sealing strips 34 to the recess 92 of the magnetic core 91. Fig. The limited space shown in 2a ensures a secure seal of the recess 92 in the magnetic core 91 against the ingress of media or the like. Associated with the radial outer area 12 and formed by the radial extension of the damping element 1 is a support area 16 on the side of the damping element 1 opposite the impact area 13. In the installed case, this support area 16 is supported as shown in Fig. 1 shown, on a support ring 93 and thus secures the damper element 1 in its position in the electromagnet 9.

[0057] Overall, the damping element 1 according to the invention, as it appears in one possible embodiment in the Fig. 2a and Fig. As shown in Figure 2b, magnetic noise reduction is also achieved because a significant portion of the impact energy of the moving anchor rod 20 is absorbed by the damping element 1 and therefore not converted into noise emission. The damping element 1, which is elastically designed, is elastically deformed upon impact with a baffle ring 21 provided on the anchor rod 20, thereby absorbing the impact energy. This results in the anchor rod 20 being decelerated and the noise emission being reduced or prevented. The sealing lip 31 provided on the projection 35 significantly improves the sealing performance.

[0058] Fig. 2b shows this in connection with Fig. 2a described damper element 1. Shown here are the different diameters d1, d2, d3 and lengths l1, l2, l3, l4, l5 of the damper element 1. Shown is the total axial length l1 of the damper element 1. This is composed of an axial length l3 of a projection 35 provided on the damper element 1 (see Figure 2a). Fig. 2a), the axial length l2 of the section of the damping element 1 having the outer surface 12, and the axial length l4 of the impact area 13, that is, the section which on the one hand provides the tarpaulin, possibly segmented, impact surface 14, and on the other hand, in the exemplary embodiment of the Fig. 2b has a convex shape to effectively transfer or dissipate the applied impact energy into the damping element 1 or the spring element 5.

[0059] The lengths l2 to l4 are preferably distributed in the ratio 1:2:2, l3:l2:l4, over the total length l1. Simultaneously, the axial length l2 of the outer area 12 of the damping element 1 may be between 20 and 70%, preferably between 30 and 60%, and particularly between 40 and 50%, of the total axial length l1 of the damping element 1. The axial length l4 of the impact area 13 can also be between 20 and 60%, preferably between 30 and 60%, and particularly between 40 and 50%, of the total axial length l1. The axial length l3 of the projection 35 of the inner sealing arrangement 30, which does not necessarily have to be provided on the damping element 1, is between 0 and 40%, in particular between 5 and 30%, and most preferably between 10 and 20% of the total length l1 of the damping element 1. The total axial length l1 of the damping element 1 is the sum of the axial lengths l2 to l4.

[0060] Out of Fig. It can be seen from Figure 2b that the inner diameter d1, d2 of the penetration opening 11 is variable. In the exemplary embodiment, it is provided that the inner diameter on the side of the damping element 1 supporting the impact surface 14 is larger than on the opposite side. The damping element 1, or rather the projection 35 provided there, is located on the opposite side (see Figure 2b). Fig. 2a) on the anchor rod 20, which is passed through the damping element 1, while the inner diameter or the inner wall 10 in the area where the anchor rod 20 is inserted into the damping element 1 is recessed relative to the anchor rod 20. The ratio of the diameter d3 of the damping element 1 to the diameter d1 of the penetration opening 11 is in the range of 1.5 to 4, preferably from 2 to 3.5, preferably from 2.8 to 3.1.

[0061] In one possible embodiment of the damping element 1, it is flush with the spring element 5 on its underside, i.e., on the side facing away from the anchor chamber 29. This results in a total axial length l5 of the damping element 1, which is less than that in the Fig. 2b shows the total axial length l1. This results in a ratio of the axial length l4 of the impact area 13 to the total axial length l5 of 1:3, or preferably 1:1, advantageously 1:4.

[0062] In order to achieve a particularly favorable dissipation of the impact energy, embodiments of the invention provide that the ratio of the total axial length l1 of the damping element 1 to the axial length l2 of the outer area 12 is in the range of 1 to 3, preferably from 1.5 to 2.8, preferably from 2.4 to 2.6.

[0063] The spring or damping performance of the damping element 1 can be adjusted by dimensioning the spring element 5. In this context, it is advantageous if the ratio of the total axial length l1 of the damping element to the axial length g1 of the spring element 5 is in the range of 1.5 to 3.5, preferably in the range of 2 to 3, and particularly preferably in the range of 2.3 to 2.6. A ratio of 2.6 is considered particularly advantageous. The ratio of the inner diameter f2 of the spring element 5 to the total axial length of the spring element is also crucial for the spring specification.

[0064] The ratio here is, for example, in the range of 1.5 to 3.5, preferably from 2.5 to 3.3, and particularly preferably in the range of 2.9 to 3.1.

[0065] The ratio of the inner diameter d1 of the penetration opening 11 to the total axial length l1 of the damper element 1 is in the range of 0.8 to 1.5, preferably in the range of 0.9 to 1.1, particularly preferably in the range of 1.

[0066] The spring element 5 is shown in the exemplary embodiment of the Fig. 2b a ratio of the outer diameter f1 to the inner diameter f2 which lies in the range of 0.5 to 2, preferably from 0.8 to 1.6, particularly preferably in the range of 1.6. From this ratio results the spring specification or the ability of the spring element 5 to absorb and dissipate impact energy.

[0067] The ratio of the outer diameter d3 of the damper element 1 to the outer diameter f1 of the spring element 5 is in a range of 0.7 to 2, preferably in a range of 1 to 1.7, particularly preferably in the range of 1.6.

[0068] The diameter of the impact ring 21 corresponds essentially to the outer diameter f1 of the spring element 5. This ensures a particularly advantageous dissipation of the impact energy or a satisfactory input of the impact energy into the spring element 5.

[0069] The support ring 93 typically covers between 10 and 40%, preferably between 15 and 30%, of the support area 16 of the damping element 1.

[0070] The proposal includes: A damping element as a component of the claims, in particular anchor or Anchor rod damper element, which serves to decelerate a moving anchor (29) or an anchor rod (20), wherein the damper element (1) has a penetration opening (11) bounded by an inner wall (10) and a radial outer area (12), and is made of elastic material, in particular an elastomer, and wherein the inner wall (10) has an inner sealing arrangement (30) and / or the outer area (12) has an outer sealing arrangement (30).

[0071] A damping element as previously described, wherein a spring element (5) is embedded in the damping element (1) which is made of a different material than the elastic material of the damping element (1).

[0072] A damping element as previously described, wherein the elastic material of the damping element (1) is rubber, synthetic rubber, fluororubber, low-temperature rubber, nitrile rubber (NBR) or polyurethane (PU).

[0073] A damping element as previously described, wherein the spring element (5) is made of spring steel.

[0074] A damping element as previously described, wherein the spring element (5) is ring-shaped, wherein, in section, the ring (50) of the spring element (5) is at least partially V-shaped (51), N-shaped or W-shaped.

[0075] A damping element as previously described, wherein the opening (52) of the V-shaped ring (50, 51) is directed radially outwards or inwards.

[0076] A damping element as previously described, wherein the damping element (1) has an impact area (13) at its end which interacts with an impact ring (21) in the event of deceleration and the impact area (13) has at least one impact surface (14) and at least one relief surface (15) set back from it.

[0077] A damping element as previously described, wherein the impact area (13) is convex, domed or spherical.

[0078] A damping element as previously described, wherein the damping element (1) has a support area (16) at the end facing away from the impact area (13), in particular arranged in the radial outer area (12).

[0079] A damping element as previously described, wherein the damping element (1) has an annular sealing lip (31) forming an inner sealing arrangement (30) on the side facing away from the impact area (13) at the penetration opening (11).

[0080] A damping element as previously described, wherein the support area (16) is set back relative to the inner sealing arrangement (30).

[0081] A damping element as previously described, wherein the outer sealing arrangement (32) is formed by a shell-like sealing surface (33).

[0082] A damping element as previously described, wherein the sealing surface (33) additionally has at least one circumferential sealing strip (34).

[0083] A damping element as previously described, wherein the inner diameter (d1, d2) of the penetration opening (11) is variable in the axial direction (17).

[0084] A damping element as previously described, wherein the axial length (12) of the outer area (12) is approximately 30 to 60%, preferably 40 to 50% of the total axial length (l1) of the sealing element (1), the axial length (l4) of the impact area (13) is approximately 30 to 60%, preferably approximately 40 to 50%, and the axial length (l3) of the projection (35) of the inner sealing arrangement (30) is 0 to 40%, preferably 0 or 5 to 20% of the total length (l1) of the damping element (1), wherein the total axial length (l1) of the damping element (1) is formed from the sum of the axial length (l2) of the outer area (12), the impact area (13), and the projection (35).

[0085] A damping element as previously described, wherein the spring element (5) is arranged centrally in the damping element (1).

[0086] A damping element as previously described, wherein, viewed in the direction from the impact area (15) to the support area (16), the spring element (5) is arranged in front of the outer area (12).

[0087] The proposal, as claimed, also relates to an electromagnet in which the armature (2) is movably mounted in an armature chamber, the electromagnet (9) has a coil (90) with windings of wire capable of carrying an electric current, and the armature (2) is operatively connected to an armature rod (20), wherein the armature rod (20) penetrates a magnetic core (91) which delimits the armature chamber (29) at least on one side, and the armature rod (20) carries a damping element (1) on the side facing away from the armature chamber (29), wherein the damping element (1) has a penetration opening (11) through which the armature rod (20) projects and the damping element (1) is designed as described above, and the armature rod (20) carries a baffle ring (21) on the side facing away from the armature chamber (29), which, when the electromagnet (9) is energized, in conjunction with the damping element (1), deflects the armature rod (20) slows down.

[0088] An electromagnet as previously described, wherein the impact ring (21) is provided between the damping element (1) and the magnetic core (91).

[0089] An electromagnet as previously described, wherein the damping element (1) is arranged between the impact ring (21) and the magnetic core (91).

[0090] An electromagnet as previously described, wherein the impact ring (21) is arranged in one piece on the armature rod (20).

[0091] An electromagnet as previously described, wherein the impact ring (21) is manufactured as a separate component and can subsequently be connected to the anchor rod (20) in a positionally stable manner in a joining, connecting or pressing process.

[0092] An electromagnet as previously described, wherein the ratio of the ring width of the impact ring (21) to the ring width of the spring element (5) is in a range of 0.8 to 1.2, preferably from 0.9 to 1.1.

[0093] An electromagnet as previously described, wherein the damping element (1) is arranged in a recess (92) on or in the magnetic core (91) and the damping element (1) is supported on a support ring (93) via its support area (16).

[0094] An electromagnet as previously described, wherein the ratio of the outer diameter of the impact ring (21) to the inner diameter of the support ring (93) is in the range of 0.8 to 1.2, preferably from 0.9 to 1.1.

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