Electromagnetically actuated device and electromagnetically actuated braking or clamping device

Abstract

The invention relates to an electromagnetic actuating device and an electromagnetic actuating braking or clamping device. The electromagnetic actuating device comprises a stator with an energizable electromagnetic coil; the armature can move relative to the stator; a spring element such that an air gap having a first width is formed between the armature and the stator when the electromagnetic coil is not energized, and such that the width of the air gap between the armature and the stator is reduced relative to the first width when the electromagnetic coil is energized; the invention relates to an electromagnetic actuating device comprising a stator, an armature, and an actuating element operatively connected to the armature, the actuating element being designed to actuate a braking or clamping device as a function of the position of the armature, the electromagnetic actuating device further comprising at least one damping element having a speed-dependent damping force characteristic curve, the damping element being arranged between: a) the armature and the stator; or b) a side of the armature facing away from the stator and located between the armature and the support / housing part; or c) according to the combination of the scheme a) and the scheme b).

Description

Technical Field

[0001] The invention relates to an electromagnetic operating device for a braking or clamping device.

[0002] The present invention further relates to an electromagnetically operated braking or clamping device comprising the electromagnetic operating device according to the present invention. Background Art

[0003] Over the past 40 years, clamping devices or clamping units with hydraulic or pneumatic actuators or operating devices have been proven in safety-related applications (e.g. fall protection devices) and have been successfully certified internationally by BG / DGUV or other Certification (DIN ISO 13849).

[0004] The clamping device or clamping unit is preferably used in systems in which an object is to be braked by clamping a rod or similar elongated structure to prevent its movement relative to the rod or structure. For this purpose, a so-called clamping cage is often used, which clamps the rod from all sides. The term "clamping cage" is used below to represent any type of braking or clamping element without restriction. There is no strict distinction between clamping units and braking units (or brakes), as clamping can ultimately also achieve braking (down to zero speed).

[0005] These previously known systems are mechanically preloaded via hydraulic or pneumatic pressure, storing corresponding potential energy in a spring element, such as a compressed disc spring assembly. If an emergency situation is detected, the preload pressure (hydraulic or pneumatic force) is reduced, and the disc spring assembly transfers its potential energy to the clamping element, i.e., the clamping cage. This internal pressure reduction in the internal pressure chamber occurs via valves and openings in the housing. However, at the moment the pressure supply is shut off, the internal pressure chamber (of the brake or clamping unit) is still "loaded" with pressure, which must be reduced over a specific time via the openings and / or a dedicated (quick) exhaust valve. During this time, the (continuously decreasing) internal pressure acts against the spring element as a (spring) force and counteracts the movement / acceleration of the retracting clamping cage. Consequently, the speed of the retracting clamping cage is automatically reduced, depending on the corresponding properties of the valves, openings, and bores, and the mechanical time constant.

[0006] Electromagnetic electric clamping units do not have such "preloaded" pressure chambers. Therefore, when the electromagnet is switched off, the force of the spring assembly is converted almost impulsively into an acceleration of the clamping cage, which is subjected to maximum acceleration. This minimizes the response time of the brake. While this advantageously results in extremely fast response times, it also results in high wear on the guide elements and strong, impact-like shock pulses when opening and closing the actuator or actuators (i.e., electromagnetic operating devices). This can significantly shorten the service life. This shortened service life makes it difficult (or even impossible) to economically use electric clamping systems according to the prior art.

[0007] An electromagnetic operating device of this type is known from the prior art, in particular from EP 2 756 505 B1. A disadvantage here is that, as already explained, unlike hydraulic or pneumatic operating devices, the potential energy stored in the spring element is provided in an impact-like manner for braking or clamping purposes, which leads to the aforementioned service life problems.

[0008] Specifically, EP 2 756 505 B1 describes the use of electric actuators (particularly in the form of magnetic actuators) in electric clamping systems. It explicitly states that the (mechanical) preload discussed is achieved via a spring assembly. However, the issue of service life is not discussed, and therefore the subject matter described in this document can only be transferred to clamping systems if a relatively short service life is tolerated. Specifically, the impact loads caused by the collision between the armature and the stator when the actuator is closed (i.e., when the brake or clamping system is opened) place high demands on the system integrator due to the high loads on the surrounding components.

[0009] As a possible solution to this problem, EP 2504606 B1 proposes a damping device with a liquid (and a corresponding valve). This document discloses a bistable, magnetic damping assembly with an integrated piston and an opening contained therein, which allows a damped reciprocating flow of liquid between two chambers. Disadvantages of this arrangement are the additional structural complexity, the required installation space, the enclosed liquid medium, and the resulting (inherent) service life issues, such as tightness.

[0010] CN212004065U discloses a vibration damping device having mutually repelling magnets or magnetic forces. The counterforce or restoring force that inevitably occurs in this arrangement is considered disadvantageous. Such counterforces should be avoided because they counteract the force of the spring element and thus reduce the available clamping force of the clamping cage. Summary of the Invention

[0011] The object of the present invention is to simulate the speed limiting effect achieved by reducing the internal pressure (known from hydraulic / pneumatic systems) in order to extend the service life of the electric clamping or braking unit or the corresponding electromagnetic operating device for the braking or clamping device without causing other problems such as increased construction space, sealing problems or disruptive reaction forces.

[0012] The electromagnetic operating device is alternatively also referred to in this description as an “actuator” or “actuator”.

[0013] According to the invention, this object is achieved by an electromagnetic operating device for a braking or clamping device having the features of the invention and by an electromagnetically operated braking or clamping device according to the invention, which includes the electromagnetic operating device according to the invention.

[0014] Advantageous developments of the concept according to the invention are defined in the dependent claims.

[0015] According to the present invention, an electromagnetic operating device for a braking or clamping device includes: a stator having an energizable electromagnetic coil; an armature movable relative to the stator; and a spring element. The spring element is constructed and arranged, and mechanically connected to the armature, such that when the electromagnetic coil is not energized, an air gap having a first width is formed between the armature and the stator. The spring element then has a first preload force. When the electromagnetic coil is energized, the width of the air gap between the armature and the stator decreases relative to the first width, preferably to a minimum width, and most preferably to zero relative to the first width. The spring element then has a second preload force that is greater than the first preload force. The electromagnetic operating device also includes an operating element operatively connected to the armature, the operating element being configured to operate the braking or clamping device based on the position of the armature. The electromagnetic operating device has at least one damping element with a speed-dependent damping force characteristic curve, which is arranged: a) between the armature and the stator; or b) on the side of the armature facing away from the stator and between the armature and the support / housing part; or c) according to embodiment a) and embodiment b), that is, in embodiment c), at least two damping elements are present.

[0016] The damping element integrates purely speed-dependent damping into the actuator, that is, into the electromagnetic operating device: the damping element is therefore designed such that even without a movement or speed (of the armature), no damping occurs, so that no (or only very small) restoring forces occur. The relevant material damping curves for materials that are or can be used for the damping element will be referred to below. Figure 3Explain in more detail.

[0017] This distinguishes the present invention from devices with elastic damping elements (such as springs or magnets), which, while capable of exerting a counterforce and reducing acceleration or velocity, also generate a counterforce due to their function in the static state (i.e., v=0) that disadvantageously counteracts the force of the spring element and thus reduces the available clamping force of the clamping cage. In contrast, the damping elements currently used have no (or negligible) internal restoring force.

[0018] It is not important here whether the damping curve of the damping element is linear or nonlinear. The damping curve "only" affects the final velocity of the armature, which is an important but secondary design parameter.

[0019] The damping element can be designed in the form of a damping plate, which means that the material thickness of the damping element is small in relation to the surface dimensions (width, length). The shape of the damping element can be described particularly well by the so-called form factor, which is a function of the load-bearing area. and lateral surface area The quotient of is obtained. Thus, the sheet metal component can be well described by a shape factor ≥ 3.

[0020] In the following, the terms "vibration-damping plate" and "vibration-damping element" are used synonymously.

[0021] In a first embodiment of the present invention, the damping plate can be integrated between the armature and the stator (see embodiment a) above). When the actuator is closed (i.e., when the brake or clamping device is released or opened), the damping plate generates a purely velocity-dependent counterforce directed in the opposite direction to the magnetic force, which is (practically) zero for v=0. When the actuator is closed, this velocity-dependent counterforce limits the maximum velocity of the armature according to Newton's laws (once the spring force and counterforce cancel each other out) and thereby reduces the impact velocity of the armature against the stator. This directly reduces the force exerted by the armature on the stator during a collision, reduces noise emissions, and reduces impact loads (and thus also reduces material wear caused by the impact).

[0022] Optionally, by additionally providing a spacing film on the armature (or stator), the minimum achievable distance between the armature and the stator can be limited to the thickness of the spacing film, making it possible to introduce a defined air gap between the two components with a minimum width greater than zero. Due to the additional magnetic resistance, this air gap accelerates the separation of the armature from the stator when the brake is engaged, thereby ensuring an optimized response time of the clamping or braking unit.

[0023] In another embodiment of the invention, a damping element can also be integrated behind the moving armature (see option b above). In this case, when the actuator is open, that is, when the brake is engaged, the damping plate generates a speed-dependent counterforce to the spring force. This speed-dependent counterforce also limits the maximum speed of the armature according to Newton's laws.

[0024] As already explained, the two solutions a) and b) can also be combined with one another in order to jointly utilize the respective advantages, see solution c).

[0025] The design and calculation of the damping element, particularly with regard to its dimensions, specifically its thickness, are based on the available installation space, the material properties of the material used, specifically its damping characteristics, and the drive design, namely the displacement-force curve, which is highly nonlinear for the magnetic actuator / reciprocating magnet (hub magnet). In a preferred embodiment, the (annular) damping element has the following dimensions, for example: an inner diameter of approximately 55 mm and an outer diameter of approximately 75 mm. The outer diameter of the magnetic actuator is approximately 125 mm.

[0026] In yet another embodiment of the present invention, the damping element can be supported on the side facing away from the actuator on a housing or housing part connected to the stator in order to absorb the reaction force. This has been found to be particularly suitable and structurally well implementable.

[0027] Tests conducted by the applicant have shown that, within the scope of the present invention, a damping element made in particular of a viscoelastic PUR material is advantageously particularly well suited for absorbing impact-like loads.

[0028] For example, a mixed-pore polyurethane (PUR) elastomer can be used as the material for the vibration damping plate, which preferably has the following properties:

[0029]

[0030] The present invention achieves a reduced or adjustable armature speed when opening and closing the drive (i.e., when switching the coil on and off). In this case, no (or only a very low) restoring force is generated in the actuator in the static state (v = 0) because the counterforce of the damping plate is speed-dependent and thus only present during movement. Furthermore, there is no (or almost no) additional thermal load on the magnetic actuator. Overall, the reduced wear, particularly on the guide elements, results in a long service life for the correspondingly equipped clamping unit.

[0031] In the embodiment that takes both aspects into account (option c), the impact loads caused by the damped impact of the armature on the stator on the one hand and on the support / housing component on the other hand are significantly reduced. In addition, due to the speed limitation during opening and closing, the impact loads on the connected (customer) system (e.g., a press) are also significantly reduced, and noise emissions (impact noise) are also reduced.

[0032] Integration into existing actuators / systems can also be achieved simply and economically (retrofitability).

[0033] The already discussed adjustability in terms of speed regulation and adaptability can be achieved either by the size of the effective surface area of the damping element (while the material remains constant) or by the selection of material properties (softer, harder, while the surface area remains constant). Alternatively or additionally, the motor dimensions can also be adapted (selection of magnet material, number of coil windings, intensity of coil current, dimensions of the armature and / or stator, etc.).

[0034] In case of maintenance, simple replaceability is achieved.

[0035] From the applicant's point of view, the following embodiment of the operating device has proven to be particularly advantageous.

[0036] In an advantageous refinement of the electromagnetic operating device for a braking or clamping device, the spring element is arranged between the armature and the stator or between the armature and a first support / housing part connected to the stator. Preferably, in the second embodiment, the armature extends through the stator with an armature extension and is designed to act directly or indirectly on the spring element with the armature extension.

[0037] This means that the spring elements do not necessarily always have to be arranged on the same side, in particular on the stator, whereby a large number of advantageous structural forms can be achieved.

[0038] In another advantageous improvement of the electromagnetic operating device for a braking or clamping device, the damping element is composed of a material which, when a mechanical action occurs, generates an increasing reaction force as the action speed increases, the reaction force being opposite to the action direction, and preferably being essentially zero at a zero action speed.

[0039] This has already been pointed out above. In this way, the counterforce gradually compensates for the spring force and thus ensures speed limitation, although the operating device can advantageously still be "activated" immediately. However, in the open (resting) state, there is preferably no counterforce (virtually) that could reduce the available spring force.

[0040] In a further advantageous development of the electromagnetic operating device for a braking or clamping device, the damping element is composed of a viscoelastic plastic material, preferably a viscoelastic plastic foam.

[0041] Tests conducted by the applicant have shown that the desired effect can be optimized in this way.

[0042] In a further advantageous development of the electromagnetic operating device for a braking or clamping device, the damping element is composed of a polyurethane material.

[0043] This material has proven to be particularly suitable for cost reasons and also for reasons of its material properties and durability.

[0044] In a particularly advantageous development of the electromagnetic operating device for a braking or clamping device, according to solution c), the damping elements on both sides of the armature are made of the same material or of a material having the same damping properties.

[0045] Alternatively, however, it is also within the scope of the invention if, according to variant c), the damping elements on both sides of the armature are made of different materials or of materials with different damping properties.

[0046] In this way, the damping characteristic can be selected and adjusted according to the desired characteristic.

[0047] In another advantageous development of the electromagnetic operating device for a braking or clamping device, according to solution a), a spacing membrane having a membrane thickness, which defines the minimum width, is provided between the armature and the stator in a region separated from the damping element.

[0048] The particular advantages that can be achieved with this embodiment have already been pointed out above.

[0049] For example, the following film materials can be used without limitation.

[0050] Polyester / polyester nonwoven laminating tape with acrylate adhesive, compliant with RoHS Directive 2011 / 65 / EU, adhesive on one side and preferably having the following properties:

[0051]

[0052] In an advantageous development of this concept, the spacing film is applied, for example adhesively bonded, to the armature or to the stator.

[0053] In this way, the embodiment can be realized or modified particularly simply and easily.

[0054] In yet another advantageous refinement of the electromagnetic operating device for a braking or clamping device, at least the armature and the stator are rotationally symmetrical and each have a central through-hole through which a rod or the like to be braked or clamped is or can be guided. Accordingly, the damping element is preferably annular and arranged concentrically with respect to the through-hole.

[0055] This corresponds to previously known actuating devices for braking or clamping devices or to previously existing designs of the braking or clamping devices themselves, thereby enabling in particular the replacement or retrofitting of existing devices.

[0056] In yet another advantageous development of the electromagnetic operating device for a braking or clamping device, according to solution a), the spacer membrane is annular and concentrically arranged around the damping element and / or concentrically arranged with respect to the through-hole radially inside the damping element.

[0057] The applicant has thus achieved optimal results in practice. Furthermore, the damping effect is formed as uniformly as possible and the installation space available for damping is utilized as well as possible.

[0058] In another equally advantageous development of the electromagnetic operating device for a braking or clamping device, according to solution a) or solution c), the armature or stator has a retaining structure for the damping element (10), preferably an annular retaining structure.

[0059] In this way, it is ensured that the damping element remains permanently positioned in its intended position, in order to further increase the service life.

[0060] In another equally advantageous development of the electromagnetic operating device for a braking or clamping device, according to embodiment b), the support / housing part has a retaining structure for the damping element, preferably an annular retaining structure. Most preferably, the support / housing part is also designed rotationally symmetrically and has a central through-hole through which a rod or the like to be braked or clamped is or can be guided.

[0061] In this way, the advantages discussed above with respect to option a) can also be utilized within the scope of option b) or option c).

[0062] It has been pointed out that, in one embodiment of the present invention, the damping element has a linear or nonlinear velocity-dependent damping force characteristic curve, depending on specific requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0063] Further features and advantages of the present invention will become apparent from the following description of exemplary embodiments with reference to the accompanying drawings.

[0064] Figure 1 An electromagnetic operating device for a braking or clamping device according to the prior art is shown in a first state;

[0065] Figure 2 An electromagnetic operating device for a braking or clamping device according to the prior art is shown in a second state;

[0066] Figure 3 Two exemplary relationships between velocity and reaction force of cushioning materials used within the scope of the present invention are shown;

[0067] Figure 4 The electromagnetic operating device for a braking or clamping device according to the invention is shown in a first state;

[0068] Figure 5 The electromagnetic operating device for a braking or clamping device according to the invention is shown in a second state;

[0069] Figure 6 Another electromagnetic operating device for a braking or clamping device according to the present invention is shown in a first state;

[0070] Figure 7 Another electromagnetic operating device for a braking or clamping device according to the present invention is shown in a second state; and

[0071] Figure 8 A braking or clamping device according to the invention is shown. DETAILED DESCRIPTION

[0072] exist Figure 1 1 shows an electromagnetic operating device for a brake or clamping device as known from the prior art. However, this basic design also applies to the present invention; the main differences are explained in detail below.

[0073] The electromagnetic operating device 1, which can be configured specifically for use in a braking or clamping device, comprises a stator 2 having an energizable electromagnetic coil 3 and an armature 4 movable relative to the stator 2. The stator 2, the electromagnetic coil 3, and the armature 4 together form a so-called magnetic actuator (hub magnet). A power supply 5 is provided to supply power to the electromagnetic coil 3. A spring element 6 is provided between the armature 4 and a support / housing part 2a connected to the stator 2 (also referred to as a first support / housing part in the present case). The entire arrangement is rotationally symmetrical about an axis L and has a central through-hole 1a parallel to the axis in at least the stator 2, the support / housing part 2a, the electromagnetic coil 3, and the armature 4.

[0074] The spring element 6 (here a coil spring, not limited thereto) is constructed and arranged in such a way and mechanically connected to the armature 4 that Figure 1 As shown in FIG, when the electromagnetic coil 3 is not energized, in the first state of the operating device 1, an air gap 7 with a first width B is formed between the armature 4 and the stator 2. The spring element 6 has a first preload in this state and generates a corresponding spring force F 弹簧 , and the magnetic force between the stator 2 and the armature 4 is zero (F 磁力执行器 = 0). Accordingly, the spring element 6 pushes the stator and the armature 4 apart from each other. For this purpose, the armature 4 is guided axially within the arrangement, for example by a rod (in Figure 1 not shown).

[0075] Reference numeral 8 denotes a potting compound for closing the coil space inside the stator 2 .

[0076] Reference numeral 9 denotes an operating element operatively connected to the armature 4, which is configured to operate the braking or clamping device (in the embodiment of FIG. Figure 1 The operating element 9 is not shown in FIG. Figure 1 In contrast, the operating element can also extend through the stator 2 and thus act on its back side facing away from the armature 4 (see Figure 8 In other words, the armature 4 can extend with an armature extension (not shown here) through the stator 2 and in particular also be designed to act directly or indirectly with the armature extension on the correspondingly provided spring element 6 .

[0077] When the electromagnetic coil 3 is energized, Figure 2 As shown in FIG, the width of the air gap 7 between the armature 4 and the stator 2 is reduced to a dimension b relative to the first width B, preferably until it is reduced to a minimum width, most preferably until it is reduced to zero width, as shown in FIG. Figure 2 As in the example, since the armature 4 and the stator 2 are magnetically attracted to each other, at this time, relative to Figure 1 The compressed spring element 6 in the figure has a second preload force greater than the first preload force in the corresponding second state. However, the corresponding spring force F 弹簧 The value is smaller than the magnetic force F between the stator 2 and the armature 4. 磁力执行器 . Accordingly, the operating element 9 is Figure 1 The position in the middle is also shifted, thereby enabling the operation of the braking or clamping device.

[0078] The disadvantage of the above embodiment is that Figure 2 , the armature 4 hits the stator 2 with a large speed and impact force, which mainly causes wear and noise.

[0079] The present invention now surpasses the prior art in that, in addition to an actuating device 1 of the type described above, at least one damping element is provided, as will be explained in more detail below, in order to reduce the impact of the armature 4 on the stator 2. The damping element consists of a material which exhibits speed-dependent damping properties in the form of a damping reaction force. The speed here refers to the speed of the object that strikes the damping element, that is, in the present case, for example, the armature 4 (see Figure 2 ). The counterforce can be nonlinearly related to the speed according to option 1, or linearly related to the speed according to option 2. Both options can be used within the scope of the present invention. Other relationships can also be used within the scope of the present invention.

[0080] It is important to note that at no speed (v=0), the counterforce is also equal to zero, ie no counterforce is generated in the absence of movement.

[0081] Figure 4 The present invention shows an improved design of the actuating device 1 compared to the prior art, in which an annular damping element 10 is provided, which has a speed-dependent damping force characteristic curve and, as previously described, is arranged between the armature 4 and the stator 2, or more specifically, between the armature 4 and the potting compound 8 (of the electromagnetic coil 3). In the selected sectional view, the damping element 10 is designed as a circular ring, but the present invention is not limited to this.

[0082] In other respects, the operating device 1 is as Figure 1 and Figure 2 The operating element 9 is not shown; in principle, the operating element can be designed as briefly described above. The power supply is not shown here again.

[0083] When the magnetic actuator is closed, that is, when the electromagnetic coil 3 is energized (the power supply is not shown, see Figure 2 ),according to Figure 4 , the following force acts on the armature 4, where s represents the displacement, and Indicates speed:

[0084]

[0085] Speed-dependent damping force due to damping element 10 Ensure that the collision speed is limited. As long as the armature is not moving This damping force is (close to) zero.

[0086] exist Figure 5 Shown in Figure 4The closed state of the operating element 1 (the electromagnetic coil 3 is energized). When the magnetic actuator is subsequently opened (that is, when the power supply to the electromagnetic coil 3 is turned off), the following applies to the force:

[0087] F 衔铁 (s)=-F 弹簧 (s).

[0088] The magnetic actuator (consisting of the armature 4 , the electromagnetic coil 3 and the stator 3 ) is free of force, the damping element 10 generates no force due to v=0 and furthermore has (virtually) no internal restoring force, as is the case with a spring, for example.

[0089] exist Figure 6 and 7 A slightly modified embodiment of the operating device according to the invention is shown in FIG. 1 (the power supply and the operating elements are also not shown).

[0090] In this modified design, the support / housing part 2a is further extended along the axis L and overlaps the armature 4 with a radial projection 2aa at its end. Between the inner side of the projection 2aa, which faces the armature 4, and the armature 4, a further damping element 11 is provided on the side of the armature 4 facing away from the stator 2. This further damping element is also preferably annular in shape, but has different dimensions. This corresponds to embodiment c) of the present invention.

[0091] In principle, a variant b) can also be formed in which only the damping element 11 is present, ie, no damping element 10 is present.

[0092] The damping element 11 can in principle be designed identically to the damping element 10. However, in addition to their dimensions, the two damping elements 10, 11 can also be designed differently, for example with regard to materials, material properties, etc.

[0093] based on Figure 6 As shown in the diagram, when the magnetic actuator is opened (that is, when the power is disconnected), the following forces act:

[0094]

[0095] The speed-dependent damping force achieved by the damping element 11 Ensure that the collision speed is limited. As long as the armature is not moving Then the buffer force is (close to) zero.

[0096] exist Figure 7 Shown in Figure 6 The same operating device as in the example, but with the magnetic actuator in the open position. During closing, the same as in the reference Figure 4 The same content is described.

[0097] When the magnetic actuator is closed, that is, when the electromagnetic coil 3 is energized, according to Figure 7 The following forces act on the armature 4, where s represents the displacement, and Indicates speed:

[0098]

[0099] That is, the speed-dependent damping force achieved by the damping element 10 This also ensures that the collision speed is limited. As long as the armature is not moving Then the buffer force is (close to) zero.

[0100] Figure 8 An electromagnetically operated braking or clamping device 12 according to the invention is shown, comprising an electromagnetic operating device 1 such as has been described above. Identical reference numerals denote identical or at least identically acting elements.

[0101] As already explained, in Figure 8 In the embodiment, the armature 4 extends through the stator 2 with its central armature extension 4a, which corresponds functionally to the armature extension 4a. Figure 1 and 2 The operating element 9 in the stator 2 is provided. The bearing / housing part is constructed in two parts, wherein, as is customary, one part 2a (first bearing / housing part) is arranged on the side of the arrangement facing away from the armature 4, while the other part or bearing / housing part 2b is arranged on the armature side of the arrangement. Both parts 2a, 2b are fixedly connected to the stator 2.

[0102] The rod 13 to be clamped is guided through a through-hole 1a (and the armature extension 4a), also formed in the other support / housing part 2b. Reference numeral 6 further provides a spring element in the form of a compression spring, which is supported in a cup-shaped spring receptacle 6a and axially supported on the one support / housing part 2a. Reference numeral 14 designates the clamping cage, already mentioned several times, which surrounds the rod 13 and has a conical outer shape. The clamping cage is operatively connected to the armature 4 via the armature extension 4a of the armature and cooperates with a clamping part 15 surrounding the clamping cage in order to clamp the rod 13. The clamping part has a complementary conical shape on its inner side: when the clamping cage 14 is moved axially into the clamping part 15 due to the spring force of the spring element 6 (when the electromagnetic coil 3 is not energized), the clamping cage is compressed radially and thus clamps the rod 13. Conversely, when the electromagnetic coil 3 is energized, the magnetic actuator (armature 4 and electromagnetic coil 3 / stator 2) releases the clamping cage through the action of the armature extension 4a, thereby releasing the rod 13 again.

[0103] Reference numerals 10 and 11 also denote damping elements, as described in detail above. These are accommodated in an annular receptacle or retaining structure formed on the bearing / housing part 2 b or the armature 4 . Reference numeral 2 c denotes an annular groove for the damping element 11 , while reference numerals 4 b and 4 c denote concentric annular projections on the armature 4 , between which the damping element 10 is disposed.

[0104] According to the figure, the armature extension 4a forms the operating element (see Figure 1 and 2 9 in the figure), the operating element is designed to move the braking or clamping element (clamping cage 14) from a first position, in which it brakes or clamps the rod 13, to a second position, in which it releases the rod 13, the relevant position being dependent on the current supply state of the electromagnetic coil 3 and thus also on the width of the air gap between the armature 4 and the stator 2. Figure 8 The second position is shown in FIG.

[0105] The spring element 6 is designed to bring the braking or clamping element (i.e., the clamping cage 14) into the first position or to hold it in the first position when the electromagnetic coil 3 is not energized, and to move the braking or clamping element (i.e., also the clamping cage 14) to the second position by the operating element (armature extension 4a) against the action of the spring element 6 when the electromagnetic coil 3 is energized, as shown in the figure.

[0106] Finally, the electromagnetically operated brake or clamping device 12 or the electromagnetic operating device 1 contained therein also has a thin damping film or spacer film at reference numeral 16, which preferably consists of a polyester non-woven laminated tape with an acrylic adhesive and defines the minimum width of the air gap 7 by its thickness d, which is preferably approximately 0.2-0.3 mm, as already indicated.

[0107] The spacer film 16 is preferably self-adhesive and can be arranged on the armature 4 radially in the region inside and outside the projections 4b, 4c or on the stator 2 radially inside and outside the annular recess 2d for accommodating the electromagnetic coil 3. Figure 3 , the spacer membrane 16 itself may also have damping properties.

Claims

1. An electromagnetic operating device for a braking or clamping device (12), the electromagnetic operating device (1) comprising: A stator (2) having an electromagnetic coil (3) capable of being energized; an armature (4) capable of moving relative to the stator (2); A spring element (6), wherein the structure and arrangement of the spring element (6) and the mechanical connection with the armature (4) are such that when the electromagnetic coil (3) is not energized, an air gap (7) having a first width (B) is formed between the armature (4) and the stator (2), at which time the spring element (6) has a first preload force, and when the electromagnetic coil (3) is energized, the width (b) of the air gap (7) between the armature (4) and the stator (2) is reduced relative to the first width (B), preferably, reduced to a minimum width relative to the first width (B), and most preferably, reduced to a zero width relative to the first width (B), at which time the spring element (6) has a second preload force, which is greater than the first preload force; an operating element (4a, 9) operatively connected to the armature (4), the operating element (4a, 9) being configured to operate the braking or clamping device (12) in accordance with the position of the armature (4); It is characterized by: The electromagnetic operating device (1) further comprises at least one damping element (10, 11), wherein the damping element (10, 11) has a speed-dependent damping force characteristic curve, and the damping element (10, 11) is arranged: a) between the armature (4) and the stator (2); or, b) a side of the armature (4) facing away from the stator (2) and located between the armature (4) and the support / housing part (2b); or c) A combination of solution a) and solution b).

2. The electromagnetic operating device according to claim 1, wherein: The spring element (6) is arranged between the armature (4) and the stator (2), or the spring element (6) is arranged between the armature (4) and a first support / housing part (2a) connected to the stator (2). Preferably, in the second case, the armature (4) extends through the stator (2) with an armature extension (4a) and is configured to act directly or indirectly on the spring element (6) with the armature extension (4a).

3. The electromagnetic operating device according to claim 1 or 2, wherein: The damping elements (10, 11) are made of a material which, when mechanical action occurs, generates an increasing reaction force as the action speed increases, the reaction force being opposite to the action direction. Preferably, the reaction force is substantially zero when the action speed is zero.

4. The electromagnetic operating device according to any one of the preceding claims, wherein: The shock-absorbing elements (10, 11) are made of a viscoelastic plastic material, preferably, the shock-absorbing elements (10, 11) are made of a viscoelastic plastic foam.

5. The electromagnetic operating device according to any one of the preceding claims, wherein: The damping elements (10, 11) are made of polyurethane material.

6. The electromagnetic operating device according to any one of the preceding claims, wherein: According to solution c), the damping elements (10, 11) on both sides of the armature (4) are made of the same material or of a material having the same damping properties.

7. The electromagnetic operating device according to any one of claims 1 to 5, wherein: According to solution c), the damping elements (10, 11) on both sides of the armature (4) are made of different materials or materials with different damping properties.

8. The electromagnetic operating device according to any one of the preceding claims, wherein: According to solution a), a spacing membrane (16) having a membrane thickness (d) is provided between the armature (4) and the stator (2) in a region separated from the damping elements (10, 11), the minimum width being defined by the membrane thickness (d).

9. The electromagnetic operating device according to claim 8, wherein: The spacing film (16) is applied to the armature (4) or to the stator (2).

10. The electromagnetic operating device according to any one of the preceding claims, wherein: At least the armature (4) and the stator (2) are designed to be rotationally symmetrical and each have a central through-hole (1a), through which a rod (13) to be braked or clamped is guided or can be guided, and the damping elements (10, 11) are designed to be annular and are arranged concentrically with the through-hole (1a).

11. The electromagnetic operating device according to claim 8 or 9 and claim 10, wherein: According to solution a), the spacer membrane (16) is annular and is concentrically arranged around the damping element (10, 11) and / or is concentrically arranged with respect to the through hole (1a) radially inside the damping element (10, 11).

12. The electromagnetic operating device according to any one of the preceding claims, wherein: According to solution a) or solution c), the armature (4) or the stator (2) has a retaining structure (4b, 4c) for the damping element (10, 11), preferably, when citing claim 10 or 11, the retaining structure (4b, 4c) is an annular retaining structure.

13. The electromagnetic operating device according to any one of the preceding claims, wherein: According to option b), the support / housing part (2b) has a retaining structure (2c) for the shock-absorbing element (10, 11), preferably, when referring to claim 10, the retaining structure (2c) is an annular retaining structure, wherein, most preferably, the support / housing part (2b) is also constructed to be rotationally symmetrical and has a central through hole (1a), through which the rod (13) to be braked or clamped is guided or can be guided.

14. The electromagnetic operating device according to any one of the preceding claims, wherein: The damping elements (10, 11) have a linear or nonlinear speed-dependent damping force characteristic curve.

15. An electromagnetically operated braking or clamping device, said braking or clamping device (12) comprising: An electromagnetic operating device (1) according to any one of the preceding claims; at least one braking or clamping element (14) configured to act on an object (13) to be braked or clamped, in particular configured as a clamping cage for a clamping rod; wherein the operating element (4a) is configured to move the braking or clamping element (14) from a first position in which the braking or clamping element (14) brakes or clamps the object (13) to a second position in which the braking or clamping element (14) releases the object (13), or vice versa, the relevant position being related to the energized state of the electromagnetic coil (3); Preferably, the spring element (6) is configured to bring the braking or clamping element (14) into the first position or to maintain the braking or clamping element (14) in the first position when the electromagnetic coil (3) is not energized, and to move the braking or clamping element (14) to the second position via the operating element (4a) when the electromagnetic coil (3) is energized.

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