Method for producing an exciter system

Abstract

The present invention relates to a method for producing an exciter system (3), in particular an exciter system (3) of a braking device (1; 100; 200), comprising the following method steps: providing a ferromagnetic magnet housing (10; 110; 210), forming a circumferential annular groove (15) on an outer side of the magnet housing (10; 110; 210), inserting an insulator (25) into the annular groove (15), winding a coil (20), in particular a coiled wire, onto the insulator (25) in the annular groove (15).

Description

[0001] Method for producing an excitation system

[0002] The invention relates to a method for producing an excitation system, in particular an excitation system of a braking device according to the features of patent claim 1 and a braking device according to the features of patent claim 7.

[0003] Braking devices in the form of spring-applied brakes are used, among other things, in the fields of robotics and automated guided vehicles. In addition to high reliability and safety, spring-applied brakes with the lowest possible weight, the highest possible torque, and the lowest possible cost are required in these areas. Due to the weight reduction, power consumption is lower while maintaining the same application performance, which can extend the operating time, particularly in battery-operated applications. In mixed-current grids, this leads to a reduction in greenhouse gases and an overall more environmentally friendly application.

[0004] Spring-applied brakes in which weight has been optimized are known from patents EP 20 61 976 B1 and EP 26 23 815 B1. The material volume is reduced to the bare minimum for flux guidance. Both documents have a pot-shaped magnet housing with an inserted coil and a flat armature disk. Pot-shaped magnet housings have an inner pole and an outer pole, with a reduction in flux density in the outer pole due to the topology. The low flux density offers the potential to reduce the material in the area of ​​the outer pole. Reducing the outer pole reduces the pole area, which is directly proportional to the magnetic force. To counteract this, the inner pole area is enlarged. However, enlarging the inner pole makes it more difficult or even impossible to insert the coil into the magnet housing.

[0005] This problem is solved by a method for producing an excitation system having the features of patent claim 1 and a braking device having the features of patent claim 7.

[0006] Advantageous embodiments and further developments of the invention are specified in the dependent claims.

[0007] According to the invention, a method for producing an excitation system, in particular an excitation system of a braking device, comprising the following method steps: providing a ferromagnetic magnet housing, forming a circumferential annular groove on an outer side of the magnet housing, inserting an insulator into the annular groove, and winding the coil onto the insulator in the annular groove.

[0008] The present invention is based on the idea of ​​reducing the outer pole and, conversely, enlarging the inner pole. The magnet housing forms an annular groove. Due to its topology, inserting a coil into the annular groove is no longer possible, which is why the coil is wound directly into the annular groove. Before the coil is wound, an electrical insulator, i.e., a dielectric, is inserted into the annular groove.

[0009] Advantageously, the insulator is applied, in particular sprayed, to at least one of the inner surfaces of the radial annular groove. The radial annular groove typically has three surfaces: a peripheral surface that forms the bottom of the groove and two end faces that are arranged opposite one another and laterally delimit the groove.

[0010] The insulator must have an appropriate insulation thickness depending on its electrical insulation strength. The insulation thickness is voltage-dependent and, in conjunction with the insulation material, is specified by standards. Plastic, silicone, or similar can be used as insulation material, for example. In contrast to existing applications in which the coil is wound onto an insulation body and the insulation body is caulked with the coil in the magnet housing, the insulator according to the present invention does not have to be able to support the coil. The coil is wound directly, or in other words immediately, onto the insulator in the radial annular groove of the magnet housing. The magnet housing, in particular the radial annular groove, is mechanically load-bearing. This makes it possible to make the wall thickness of the insulator thinner, which means more space is available for the coil.

[0011] According to an advantageous method step of the invention, the insulator is applied to at least one of the inner surfaces of the radial annular groove by means of an injection molding process. Advantages of the injection molding process are its high reliability, low cost, high precision, and high production speed. It may also be advantageous for the magnet housing to be preheated before being overmolded with the insulating material to prevent premature solidification of the insulating material during insertion into the radial annular groove.

[0012] In a further advantageous method step, the insulator is applied to at least one of the inner surfaces of the radial annular groove by means of a coating process, in particular by means of a painting process, wherein the protective coating is applied by spraying, brushing, dipping, vapor deposition, deposition, or flooding. Polyurethane, resin, or silicone can be used as the insulation material. The thickness of the insulator depends on the voltage and the dielectric strength of the material used.

[0013] The insulation can also be applied by chemical vapor deposition with a coating of Parylene. In addition, the insulation can be incorporated into the radial annular groove by inserting insulating foils or insulating adhesive tapes. Glass fabric tapes or polyimide foils are frequently used for this purpose. Insulation in the form of aluminum oxide can also be introduced into the radial annular groove by plasma spraying. In addition, the insulation can be introduced into the radial annular groove by wet painting or powder coating. The coil can also be introduced into the radial annular groove of the magnet housing by another method. For example, the coil can be inserted as a whole, pressed into, or mortised into the radial annular groove lined with the insulating material.In particular, a two-part insulator or a two-part magnet housing enable the coil to be positioned within the magnet housing for the applications mentioned above.

[0014] In a further advantageous method step, a coil body consisting of at least two parts can be inserted into the radial groove, wherein the coil body is preferably made of an electrically insulating material.

[0015] According to an advantageous embodiment of the invention, an insulator is at least partially applied to the outer surface of the magnet housing during the coating process, in particular during the painting process. An insulator or another corrosion-inhibiting material can also be at least partially applied to the surface of the magnet housing using any other method. The application of the insulator primarily serves to protect against corrosion.

[0016] A further aspect of the present invention relates to a braking device, in particular a spring-loaded brake, comprising a magnet housing and an electromagnetic actuating device with a coil. The braking device according to the invention also has an armature movable along a longitudinal axis against the force of a compression spring and a friction disc, wherein the armature can come into operative contact with the friction disc to generate a braking force.

[0017] According to a preferred embodiment, the coil can be arranged in a radial groove of the magnet housing that runs around the longitudinal axis. An insulator is arranged between the magnet housing and the coil.

[0018] Advantageously, the magnet housing has an inner pole and preferably a pole plate projecting from the inner pole in a flange-like manner, wherein the inner pole encloses the radial annular groove. The outer diameter of the pole plate is preferably larger than the outer diameter of the inner pole. The radial annular groove is preferably formed in the outer diameter of the inner pole.

[0019] According to a further advantageous development of the invention, the magnet housing is rotationally symmetrical about the longitudinal axis. Furthermore, it can be advantageous if the components of the braking device, namely the friction disc, the armature, and the flange, are arranged rotationally symmetrically to the longitudinal axis. Rotationally symmetrical arrangements have the advantage that the load or stress is evenly distributed around a center, which in the present invention represents the longitudinal axis. This reduces the stress on the individual components, improves structural integrity, and reduces the generation of one-sided forces and moments.

[0020] In an advantageous embodiment of the invention, the armature is pot-shaped with a base and an outer wall protruding from the base along its longitudinal axis. The armature engages over the magnet housing such that a free end can touch the pole plate of the magnet housing and is thus in a magnetic field closure position. In an advantageous embodiment, the armature is shaped such that it closes the entire housing of the spring-applied brake and ensures the iron-guided magnetic flux to the outer pole. The outer wall for closing the entire housing can also be formed on the magnet housing, although this could make winding the coil more difficult. The armature preferably has a planar base body. In order to optimally guide the magnetic flux, the armature can preferably be made from a ferromagnetic material and has a high permeability.The armature is preferably manufactured by stamping and subsequent deep drawing. Recesses are arranged around the circumference of the armature through which the spacer elements, such as compression sleeves, can be inserted when assembled. The armature, flange, and friction disc are components of the braking device, which means that the friction surfaces of the armature, flange, and friction disc must have a specified minimum roughness.

[0021] In a particularly advantageous embodiment of the invention, the armature encloses a hollow space between the pole plate and the inner pole of the magnet housing. Due to the mostly rotationally symmetrical arrangement, a spring-applied brake can be broken down into a magnetic circuit. As already mentioned in the introduction, in pot-shaped magnet housings the magnetic flux density in the outer pole area is usually lower than in the inner pole area due to topology. Due to the circular arrangement of the pot-shaped magnet housing, the area of ​​the outer pole through which the magnetic flux density passes is usually larger than the area of ​​the inner pole. This effect is increased with increasing diameter of the spring-applied brake. Due to the larger area through which the magnetic flux density can pass, the magnetic flux density is reduced in the area of ​​the outer pole.This makes it possible to reduce the amount of material in the outer pole area, whereby the magnet housing is modified according to the invention in such a way that a cavity is formed.

[0022] In a simplified model, the magnetic force is quadratically proportional to the magnetic flux density, directly proportional to the area, and dependent on the permeability of the iron and air. The reduction in area resulting from the reduction in material in the outer pole region is partially or fully compensated for by an increase in the magnetic flux density. The area through which the flux passes must not be too small, as otherwise the ferromagnetic material may become saturated. In saturation, an increase in the magnetic flux density is hardly possible despite an increase in current. With a further increase in the magnetic flux density in the saturation region, the losses increase disproportionately due to the higher current.

[0023] Advantageously, compression springs arranged at a radial distance from the longitudinal axis or permanent magnets arranged at a radial distance from the longitudinal axis are arranged in the cavity. It is also possible for only one compression spring to be formed, with one compression spring being arranged rotationally symmetrically about the longitudinal axis. Preferably, four compression springs are arranged in the cavity of the spring-applied brake. However, more or fewer than four compression springs can be arranged at a radial distance from the longitudinal axis. The compression springs can be arranged on an imaginary circle, with the angular distance between the compression springs being constant on the circle. The angular distance between the compression springs can also be different from one another.

[0024] In an advantageous embodiment of the invention, the braking pressure between the armature, flange and friction disc can be provided by the compression spring or by a permanent magnet when the electromagnetic coil is not energized. The two friction surfaces of the friction disc act on the one hand against a friction surface and the other against the friction surface of the flange. This clamps the friction disc between the armature and the flange. The friction disc is positively connected to a shaft, for example via shaft teeth, a driver or the like, so that clamping of the friction disc results in clamping of the shaft. The armature, flange and friction disc can have more than one friction surface, in particular two, four or six friction surfaces.

[0025] When de-energized, an air gap forms between the magnet housing and the armature. The air gap must only be large enough for the magnetic force to overcome the spring force, although a safety factor must be taken into account. When energized, a magnetic force generated by the coil counteracts the spring force, so that the friction disc is free and can rotate about its longitudinal axis. The armature touches the magnet housing and is therefore in a magnetic field connection, with the effective magnetic force being at its greatest in this state. Permanent magnets can also be used instead of compression springs. Here, the magnetic force of the permanent magnet is weakened by a field directed opposite to that of the permanent magnet, thereby releasing the spring-applied brake. The opposing field is generated by a coil.

[0026] According to a further advantageous development of the invention, the compression springs, which are arranged radially spaced from the longitudinal axis, are guided in the cavity on preferably bolt-shaped spring guides, such as clamping sleeves. Clamping sleeves have the advantage that they are easy to install, offer high vibration resistance, and center the compression springs despite the cavity. The formation of the cavity enables a weight reduction of up to 30 percent compared to spring-applied brakes of the same geometric design in a conventional manner.

[0027] In a particularly advantageous embodiment of the invention, the inner pole forms a pole face parallel to the base of the armature. The pole face is a side wall of the radial annular groove. The longer the pole face, the greater the magnetic conductance and the easier it is for the magnetic flux to penetrate the air gap. However, the magnetic flux density is lower. In a design with a pole face and a small air gap, the magnetic force is lower than in a design without a pole face, but falls more gently as the air gap increases, so that a larger air gap can be formed overall for the same spring force to be overcome. The reduction in the magnetic force due to the pole face when the armature and magnet housing have no or only a small air gap between them is not critical because in this state the magnetic force significantly exceeds the spring force.The pole face causes the magnetic force characteristic curve to be flatter across the air gap, so that the magnetic force is greater with a pole face as the air gap increases than without a pole face.

[0028] Advantageously, the flange can be fastened to the magnet housing, preferably with countersunk screws. The countersunk screw is guided through the cavity of the spring-applied brake using one or more spacers, preferably compression sleeves. The compression sleeves are provided for air gap adjustment and to prevent rotation. The compression sleeves prevent the armature from moving with the friction disc. Countersunk screws have the advantage of forming a conical head, allowing a surface to be formed that is flush with the flange.

[0029] According to a further advantageous development of the invention, the insulator applied in the radial annular groove has an insulator thickness of preferably less than or equal to 0.6 mm, particularly preferably less than or equal to 0.4 mm. The advantage of making the insulator thickness as small as possible is that the groove area can be better utilized for the coil. This means that either the number of conductors can be increased, which is directly proportional to the magnetic flux density, or the cross-section of the coil, in particular of a coil wire, can be enlarged, whereby the current through the coil can be increased and the magnetic flux density can also be increased. However, the insulator thickness must be large enough so that no breakdown can occur between the magnet housing and the coil.Due to the reduction in material in the form of a cavity, the thermal properties of the spring-applied brake must be taken into account, since air is a much better thermal insulator than a ferromagnetic material such as iron.

[0030] An advantage of the inventive design is that the thinner insulation material separating the coil and magnet housing also improves thermal performance. Insulators are generally poor heat conductors, which is why heat dissipation is more difficult with a thicker insulation layer.

[0031] Several embodiments of the present invention are described in detail below with reference to the accompanying drawings. They show:

[0032] Fig. 1 is a perspective view of the braking device, which is designed as a spring-loaded brake, comprising a flange, a friction disc, an armature and an excitation system,

[0033] Fig. 2 is a perspective and partially sectioned view of the spring-loaded brake from Fig. 1,

[0034] Fig. 3 is a sectional view of the spring-applied brake according to Fig. 1,

[0035] Fig. 4 is a perspective partial view of a sectional view of the spring-applied brake from Fig. 1,

[0036] Fig. 5 is a sectional view of a second embodiment of a spring-loaded brake, and Fig. 6 is a sectional view of a third embodiment of a spring-loaded brake.

[0037] Identical or functionally equivalent parts or features are identified by the same reference numerals in the following detailed description of the figures. Likewise, not all identical or functionally equivalent parts or features are provided with a reference numeral in the figures.

[0038] In Fig. 1, a first embodiment of a braking device 1, which is designed as a spring-applied brake 2, is shown.

[0039] The spring-applied brake 2 has an excitation system 3, which is composed of a magnet housing 10 and a coil 20, an armature 40 movable on a longitudinal axis L, a friction disc 50 and a flange 30, wherein the components are arranged rotationally symmetrically about the longitudinal axis L. A shaft (not shown) can be pushed through all of the above-mentioned components, wherein the shaft is also arranged rotationally symmetrically about the longitudinal axis L.

[0040] The flange 30 has the shape of a circular ring, with the circular ring having three protrusions 33 on its outer diameter. The circular ring can have more or fewer than three protrusions 33, and the protrusions 33 can also be arranged on the inner diameter of the circular ring. The protrusions 33 have a bore 34 in their center.

[0041] The flange 30 can take a shape other than a circular ring, for example, a polygon, an oval, or a full circle. The outer diameter of the circular ring of the flange 30 can be smaller than the outer diameter of the outer wall 42 of the armature 40 and the pole plate 11 of the magnet housing 10.

[0042] The outermost point of the protrusion 33 is formed approximately in the area of ​​the outer wall 42 of the armature 40. A countersunk screw 32 can be passed through the bore 34 of the protrusion 33. The flange 30 is fixed at a defined distance from the magnet housing 10 by compression sleeves 31 and the countersunk screw 32 pushed through the bore 34 of the protrusion 33 of the flange 30. The flange 30 is preferably made of a flux-conducting material such as iron.

[0043] A friction disc 50 which is rotatable about the longitudinal axis L is arranged between the flange 30 and the armature 40.

[0044] The friction disc 50 has an inner wall 52 running in the circular ring of the flange 30 and a base plate 51 projecting from the inner wall 52 in the shape of a flange.

[0045] The base plate 51 of the friction disc 50 has at least one friction surface on both surfaces pointing in the direction of the longitudinal axis L. In the de-energized state, the friction surfaces of the friction disc achieve a braking effect with at least one friction surface of the armature 40 and at least one friction surface of the flange 30. As a result, the friction disc 50 is no longer mounted so as to be rotatable about the longitudinal axis L.

[0046] The inner wall 52 of the friction disc 50 has trapezoidal grooves 54 on its inside. The grooves 54 of the inner wall 52 can also have the shape of another polygon. Complementary, likewise trapezoidal, teeth 71 of the driver 70 engage in the grooves 54 of the inner wall 52, whereby a tooth 71 can also have the shape of another polygon.

[0047] The inner wall 52 preferably projects beyond the flange 30 in the direction of the longitudinal axis L.

[0048] The armature 40 is pot-shaped with a base 41 and an outer wall 42 protruding from the base 41 in the longitudinal axis L, wherein the armature 40 can overlap the excitation system, in particular the magnet housing 10, in such a way that a free end can touch the pole plate 11 of the magnet housing 10.

[0049] The armature 40 can also be designed to be planar, in which case the magnet housing 10 must then be designed in such a way that the entire housing consisting of the outer pole and the inner pole is formed on one plane in order to be able to ensure the necessary magnetic flux to generate the magnetic force required for ventilation.

[0050] The armature 40 has a recess 44 through which the countersunk screws 32 and compression sleeves 31 can be passed in order to fix the flange 30 to the magnet housing 10.

[0051] The bulge 44 of the anchor 40 extends over the outer wall 42 into the bottom 41 of the anchor 40.

[0052] The armature 40 also has protrusions 45 through which screws (not shown) can be passed, allowing the spring-applied brake 2 to be secured to an application. Furthermore, a recess 19 is formed in the pole plate 11 of the magnet housing 10, through which a coil connection 21 can be inserted into the spring-applied brake 2, the coil connection 21 supplying the required energy to the coil 20.

[0053] In Fig. 2 a perspective view of a sectional view of the spring-applied brake 2 according to Fig. 1 is shown.

[0054] The magnet housing 10 has an inner pole 12 and a pole plate 11 projecting from the inner pole 12 in a flange-like manner, wherein the inner pole 12 comprises the radial annular groove 15.

[0055] The radial annular groove 15 comprises three inner surfaces 26, namely a bottom formed by a lateral surface and two opposite end surfaces.

[0056] An insulator 25 is inserted into the radial annular groove 15, and a coil 20 is then wound directly thereon. Preferably, the insulator 25 is applied to all inner surfaces 26.

[0057] The diameter of the inner pole 12 is smaller than the diameter of the pole plate 11. The pole plate 11 has three threaded holes 18 in the edge area, into which the countersunk screws 32 can engage in order to fix the flange 30 to the magnet housing 10. However, more or fewer than three threaded holes 18 can be formed in the pole plate 11.

[0058] Furthermore, according to the illustrated embodiment, three additional holes 16 can also be arranged in the edge region of the pole plate 11 of the magnet housing 10. Screws (not shown) can be passed through these holes 16, which make the spring-applied brake 2 attachable to an application. The total of six holes 16, 18 can be arranged evenly distributed over the circumference of an imaginary circle whose center lies on the longitudinal axis L.

[0059] Furthermore, the magnet housing 10 can have a recess 19 through which a coil connection 21 can be inserted into the spring-loaded brake 2.

[0060] For weight optimization purposes, the pole plate 11 of the magnet housing 10 can be designed to be so thin in the direction of the longitudinal axis L that front-end mounting on an application is not possible. The material thickness of the pole plate 11 of the magnet housing 10 is preferably strong enough to enable the braking device 1 to be mounted on both sides of the application.

[0061] The trapezoidal teeth 71 of the driver 70 are inserted into the trapezoidal grooves 54 of the inner wall 52 of the friction disc 50. The driver 70 is non-positively connected to a shaft (not shown). The grooves 54 of the inner wall 52 of the friction disc 50 can also be square, hexagonal, polygonal, or similar. The teeth 71 of the driver 70 are complementary.

[0062] The radial annular groove 15 is formed along the outer diameter of the inner pole 12. An insulator 25 is inserted into this annular groove 15. A coil 20 is wound directly onto the insulator 25.

[0063] The insulator 25 can be applied to at least one of the inner surfaces 26, preferably to all inner surfaces, in the annular groove 15 on the magnet housing 10 by spraying, dipping, painting, vapor deposition, depositing, introducing a multi-part insert or in another way.

[0064] The coil 20 can also be pressed, stamped, or locked into the annular groove 15 as a whole. The coil 20 is preferably made of copper, but can also be made of aluminum or another electrically conductive material. An insulating material is already formed around the individual windings of the coil 20 when wound into the radial annular groove 15.

[0065] The section in Fig. 2 intersects one of the countersunk screws 32 in the center. The countersunk screw 32 is guided through the cavity 14 with the aid of a compression sleeve 31. The countersunk screw head 35 of the countersunk screw 32 is conical and sits in the bore 34 of the protrusion 33 of the flange 30 in such a way that the countersunk screw head 35 is almost flush with the flange 30. The countersunk screw head 35 can also be completely flush with the flange 30.

[0066] At the countersunk screw end 36, a thread is introduced which can be inserted into a complementary threaded bore 18 of the pole plate 11 of the magnet housing 10.

[0067] In addition, the sectional view in Fig. 2 cuts through the center of a clamping sleeve 17. The clamping sleeve 17 is hollow-cylindrical. The clamping sleeve 17 is inserted into the bore 16 of the pole plate 11 of the magnet housing 10 and extends in the direction of the longitudinal axis L to the bottom 41 of the armature 40. A compression spring 60 is arranged at least partially around the clamping sleeve 17. It can be seen from Fig. 3 that the coil 20 does not project beyond the radial annular groove 15 in the direction of the outer diameter. In other words, the coil 20 is completely embedded in the annular groove 15.

[0068] The number of windings of coil 20 and the diameter of coil 20 depend on the current and the space available in radial annular groove 15. The thicker the insulator 25, the less space is available for coil 20. The thickness of insulator 25 is preferably less than 0.6 millimeters, in particular less than 0.4 millimeters. The thickness of insulator 25 can also be smaller or thicker, although the voltage-dependent dielectric strength must always be guaranteed.

[0069] Due to the radial annular groove 15, the insulator 25 does not have to assume a load-bearing character.

[0070] The energized coil 20 causes field lines which surround the coil 20 or an individual conductor of the coil 20 in closed field lines, whereby the field lines of the individual conductors can overlap. The magnetic field strength is particularly dependent on the current. As already described, the magnetic force is quadratically proportional to the magnetic flux density and directly proportional to the interface, whereby the magnetic flux density depends on the material. The permeability is the proportionality factor between magnetic flux density and magnetic field. The permeability describes the magnetization of a material in an external magnetic field. In the flux-carrying components of the spring-applied brake 2, which are primarily the magnet housing 10 and the armature 40, ferromagnetic materials with a high permeability are used, whereby the magnetic field is increased.If an air gap is formed between the armature 40 and the magnet housing 10, a magnetic field enters from a region of high permeability into a region of low permeability, creating an interfacial force which is referred to as magnetic force and pulls the armature 40, which is movable in the direction of the longitudinal axis L, in the direction of the magnet housing 10.

[0071] This magnetic force is opposed by the spring force of the compression springs 60. In order to release the spring-applied brake 2, the magnetic force must exceed the spring force of the compression spring 60. As the air gap increases, the magnetic force becomes smaller and smaller for a constant current. This can be remedied by enlarging the pole face 13, which is part of the radial annular groove 15 and runs parallel to the base 41 of the armature 40. Although this arrangement reduces the magnetic flux density in the area of ​​the interface between the armature 40 and the magnet housing 10, the interface area is also enlarged, which almost compensates for the lower magnetic flux density and, with larger air gaps, leads to an increase in the magnetic force.

[0072] In the unreleased state, the coil 20 is de-energized. The compression springs 60, which are guided on the clamping sleeves 17 through the cavity 14, press on the base 41 of the armature 40. The armature 40 moves along the longitudinal axis L in the direction of the friction disc 50. The friction disc 50 is clamped between the flange 30 and the armature 40. The flange 30, the armature 40 and the friction disc 50 have friction surfaces which may need to have a minimum roughness so that the spring-applied brake 2 can apply the necessary braking force. The coil 20 is supplied with energy via a coil connection 26, wherein the coil connection can be inserted into the spring-applied brake 2 via a recess 19 in the magnet housing 10. Fig. 4 shows a perspective and sectional partial view of the spring-applied brake 2. The enclosed cavity 14 between magnet housing 10 and armature 40 can be clearly seen.The cavity 14 is enclosed by the pole plate 11 of the magnet housing 10 and the outer diameter of the inner pole 12 as well as the bottom 41 and the outer wall 42 of the armature 40.

[0073] Fig. 5 shows a sectional view of a second embodiment of a braking device 100, which is designed as a spring-applied brake 102. The structure of the spring-applied brake 102 differs from the previous embodiment by a different design of the magnet housing 110. With regard to the arrangement of the magnet housing 110 within the spring-applied brake 102 as well as the design and arrangement of the other components of the spring-applied brake 102, reference is made to the previous embodiment.

[0074] The magnet housing 110 is formed in two parts, wherein the magnet housing 110 has a base housing 115 and a pole housing 120.

[0075] The base housing 115 is flange-shaped. The base housing 115 has a base plate 116 with a circular cross-section, wherein the cross-section is cut orthogonally by the longitudinal axis L. In the assembled state, a base housing pole 117 extends along the longitudinal axis L in the direction of the armature 40 along an inner diameter of the circular base plate 116.

[0076] The pole housing 120 is hollow-cylindrical with a circular cross-section, wherein the cross-section is cut orthogonally by the longitudinal axis L. The pole housing 120 is arranged rotationally symmetrically to the longitudinal axis L. The pole housing 120 preferably has a smaller outer diameter than the base housing 115, preferably the base plate 116 of the base housing 115.

[0077] The pole housing 120 and the base housing 115 are mechanically fixed. The pole housing 120 is pressed onto the base housing 115. Preferably, the pole housing 120 is mechanically pressed in the region of the distal end 118 of the base housing pole 117.

[0078] The mechanical fixation between the base housing 115 and the pole housing 120 can be achieved by a press fit. The press fit is a firm, force-locking connection or fixation in which the pole housing 120 is connected to the base housing 115 by pressing. This creates a high frictional fit due to the interference fit, which securely fixes the components. The mechanical fixation between the base housing 115 and the pole housing 120 can also be achieved by an interference fit.

[0079] In the assembled state of the spring-applied brake 102, the distal end 118 of the base housing pole 117 and the side of the pole housing 120 facing the armature 40 together form the pole face 13. The base housing 115 and the pole housing 120 together form the radial annular groove 15. The insulator 25 is inserted or molded into the radial annular groove 15, with the coil 20 wound onto the insulator 25.

[0080] Fig. 6 shows a sectional view of a second embodiment of a braking device 200, which is designed as a spring-applied brake 202. The structure of the spring-applied brake 202 differs from the previous embodiment by a different design of the magnet housing 210. With regard to the arrangement of the magnet housing 210 within the spring-applied brake 202 as well as the design and arrangement of the other components of the spring-applied brake 202, reference is made to the first embodiment.

[0081] The magnet housing 210 is formed in two parts, wherein the magnet housing 210 has a base housing 215 and a pole housing 220.

[0082] The base housing 215 is flange-shaped. The base housing 215 has an annular base plate 216. In the assembled state, a base housing pole 217 extends along the inner diameter of the annular base plate 216 along the longitudinal axis L in the direction of the armature 40. The base housing 215 preferably has the same inner diameter as the pole housing 220.

[0083] The pole housing 220 is hollow-cylindrical with a circular cross-section, wherein the cross-section is cut orthogonally by the longitudinal axis L. The pole housing 220 is arranged rotationally symmetrically to the longitudinal axis L. The pole housing 220 preferably has a smaller outer diameter than the base housing 215, preferably the base plate 216 of the base housing 215.

[0084] The pole housing 220 is mechanically fixed to the base housing 215. In the assembled state of the spring-applied brake 202, the pole housing 220 is mechanically fixed with a side facing away from the armature 40 to a distal end 218 of the base housing pole 217 of the base housing 215. The pole housing 220 is mechanically fixed to the base housing 215 via a screw connection, an adhesive connection, a welded connection, or the like.

[0085] The base housing 215 and the pole housing 220 together form the radial annular groove 15. An insulator 25 is inserted or molded into the radial annular groove 15, with the coil 20 wound onto the insulator.

[0086] List of reference symbols

[0087] 1 braking device

[0088] 2 spring-applied brake

[0089] 3 pathogen system

[0090] 10 magnet housings

[0091] 11 Pole plate

[0092] 12 inner pole

[0093] 13 Pole face

[0094] 14 Cavity

[0095] 15 ring groove

[0096] 16 Hole

[0097] 17 clamping sleeves

[0098] 18 threaded holes

[0099] 19 Recess

[0100] 20 coil

[0101] 21 Coil connection

[0102] 25 Insulator

[0103] 26 inner surface

[0104] 30 flange

[0105] 31 compression sleeve

[0106] 32 countersunk screws

[0107] 33 bulge

[0108] 34 Hole

[0109] 35 countersunk screw head

[0110] 36 countersunk screw end

[0111] 40 Anchor 41 Ground

[0112] 42 exterior wall

[0113] 44 bulge

[0114] 45 bulge

[0115] 50 friction disc

[0116] 51 Base plate

[0117] 52 Interior wall

[0118] 54 grooves

[0119] 60 compression spring

[0120] 70 carriers

[0121] 71 tooth

[0122] 100 braking device

[0123] 102 Spring-applied brake

[0124] 110 magnet housing

[0125] 115 base housing

[0126] 116 Base plate

[0127] 117 Base housing pole

[0128] 118 Distal end

[0129] 120 pole housings

[0130] 200 braking device

[0131] 202 spring-applied brake

[0132] 210 Magnet housing 215 Base housing

[0133] 216 base plate

[0134] 217 Base housing pole

[0135] 218 Distal end

[0136] 220 pole housing

[0137] L Longitudinal axis

Claims

Patent claims 1. Method for producing an excitation system (3), in particular an excitation system (3) of a braking device (1; 100; 200), comprising the following method steps: - providing a ferromagnetic magnet housing (10; 110; 210), - forming a circumferential annular groove (15) on an outer side of the magnet housing (10; 110; 210), - Inserting an insulator (25) into the annular groove (15), - Winding a coil (20), in particular a coil wire, onto the insulator (25) in the annular groove (15).

2. Method according to claim 1, characterized in that the insulator (25) is applied, in particular sprayed, onto an inner surface (26) of the radial annular groove (15).

3. Method according to claim 1 or 2, characterized in that the insulator (25) is applied to the inner surface (26) of the radial annular groove (15) by means of an injection molding process.

4. Method according to claim 1 or 2, characterized in that the insulator (25) is applied to the inner surface (26) of the radial annular groove (15) by means of a coating process, in particular by means of a painting process, wherein the protective lacquer is applied by spraying, painting, dipping, vapor deposition, deposition or flooding.

5. Method according to claim 1 or 2, characterized in that an at least two-part coil body is inserted into the radial groove (15), wherein the coil body is preferably made of an electrically insulating material.

6. Method according to claim 4, characterized in that during the coating process, in particular during the painting process, an insulator (25) is at least partially applied to the outer surface of the magnet housing (10; 110; 210).

7. Braking device (1; 100; 200), in particular spring-loaded brake (2; 102; 202), comprising: - an excitation system (3), in particular manufactured according to one of claims 1 to 6, - the excitation system (3) has a magnet housing and a coil, - an electromagnetic actuating device with the coil (20) and an armature (40) movable along a longitudinal axis (L) against a force of a compression spring (60), - a friction disc (50), wherein the armature (40) can come into operative contact with the friction disc (50) to generate a braking force, characterized in that - the coil (20) is arranged in a radial groove (15) of the magnet housing (10; 110; 210) which runs around the longitudinal axis (L) and that between the magnet housing (10; 110; 210) and the coil (20) an insulator (25) is arranged.

8. Braking device (1; 100; 200) according to claim 7, characterized in that the magnet housing (10; 110; 210) has an inner pole (12) and a pole plate (11) projecting from the inner pole (12) in a flange-like manner, and in that the inner pole (12) comprises the radial annular groove (15).

9. Braking device (1; 100; 200) according to claim 7 or 8, characterized in that the magnet housing (10; 110; 210) is rotationally symmetrical about the longitudinal axis (L).

10. Braking device (1; 100; 200) according to one of claims 7 to 9, characterized in that the armature (40) is pot-shaped with a base (41) and an outer wall (42) projecting from the base (41) in the longitudinal axis (L), and in that the armature (40) can engage over the magnet housing (10; 110; 210) in such a way that a free end can touch the pole plate (11) of the magnet housing (10; 110; 210).

11. Braking device (1; 100; 200) according to one of claims 7 to 10, characterized in that the armature (40) encloses a cavity (14) between the pole plate (11) and the inner pole (12) of the magnet housing (10; 110; 210).

12. Braking device (1; 100; 200) according to one of claims 7 to 11, characterized in that compression springs (60) arranged at a radial distance from the longitudinal axis (L) or permanent magnets arranged at a radial distance from the longitudinal axis (L) are arranged in the cavity (14).

13. Braking device (1; 100; 200) according to one of claims 7 to 12, characterized in that the compression springs (60) arranged at a radial distance from the longitudinal axis (L) are guided in the cavity (14) on a bolt-shaped spring guide, in particular clamping sleeves (17).

14. Braking device (1; 100; 200) according to one of claims 7 to 13, characterized in that the braking pressure between the armature (40), flange (30) and friction disc (50) can be provided by the compression spring (60) or by a permanent magnet when the electromagnetic coil (20) is not energized.

15. Braking device (1; 100; 200) according to one of claims 7 to 14, characterized in that the inner pole (12) forms a pole face (13) parallel to the bottom (41) of the armature (40).

16. Braking device (1; 100; 200) according to one of claims 7 to 15, characterized in that the flange (30) can preferably be fastened to the magnet housing (10; 110; 210) with countersunk screws (32).

17. Braking device (1; 100; 200) according to one of claims 7 to 16, characterized in that the insulator (25) applied in the radial annular groove (15) has an insulator thickness of preferably less than or equal to 0.6 mm, particularly preferably less than or equal to 0.4 mm.

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