Brake assembly, in particular for an electric motor, for braking a shaft

Abstract

Proposed is a brake assembly for braking a shaft, wherein: the brake assembly comprises • - a magnet body (9), • - an armature disk (2) and • - an electrically energizable coil winding (8); the coil winding (8) is received in the magnet body (9); the armature disk (2) is rotationally coupled to the magnet body (9) and is movable in the axial direction; a permanent magnet (10) is arranged in a recess of the magnet body (9); bolts (3) which are mutually spaced in the circumferential direction project in the axial direction through respective recesses in the magnet body (9); and the bolts (3) are connected at one end to the armature disk (2) and at the other end to a magnetic return disk (4).

Description

[0001] Brake arrangement, in particular for an electric motor, for braking a shaft

[0002] Description:

[0003] The invention relates to a brake arrangement, in particular for an electric motor, for braking a shaft.

[0004] It is well known that a brake arrangement slows down a rotatably mounted shaft.

[0005] From DE 10 2010 049 744 A1, a brake is known as the closest state of the art.

[0006] From DE 10 2010 049 747 A1 a kit for the production of different electric motors of a series of electric motors is known.

[0007] An electric motor is known from DE 10 2010 049 748 A1.

[0008] The invention is therefore based on the object of developing a brake arrangement, whereby energy-saving operation is to be achieved.

[0009] According to the invention, the object is achieved in the brake arrangement according to the features specified in claim 1.

[0010] Important features of the invention in the brake assembly, in particular for an electric motor, for braking a shaft are that the brake assembly comprises a magnetic body, in particular made of ferromagnetic material, an armature disk, in particular made of ferromagnetic material, and an electrically energizable coil winding, wherein the coil winding is received in the magnetic body, in particular in an annular recess of the magnetic body, wherein the armature disk is rotationally connected to the magnetic body and arranged to be movable in the axial direction, in particular wherein the axial direction is aligned parallel to the axis of rotation of the shaft, in particular wherein the coil winding is designed as a ring winding, the ring axis of which is aligned coaxially to the axis of rotation of the shaft, wherein a permanent magnet is arranged in a recess of the magnetic body,wherein circumferentially spaced bolts protrude through respective recesses of the magnetic body in the axial direction, wherein the bolts are connected on the one hand to the armature disk and on the other hand to a return disk, in particular wherein the bolts are connected to the return disk at their end region axially remote from the armature disk and are connected to the armature disk at their end region remote from the return disk, in particular wherein the return disk is made of ferromagnetic material.

[0011] The advantage here is that the electrical power required for release can be reduced. By feeding the magnetic field generated by the permanent magnet back through the armature disk, the armature disk is held in the release position not only by the coil winding but also by the permanent magnet. This reduces the holding current required in the coil winding, and thus reduces the electrical power required.

[0012] However, when the coil winding is not energized, the spring force generated by the spring elements exceeds the holding force generated by the permanent magnet. This then moves the armature disk away from the magnetic body, in particular into the applied position, i.e. the position the armature disk assumes when the brake is applied. When the brake is applied, the magnetic field generated by the permanent magnet is fed back into the magnetic body via the return disk. This means that essentially no force from the permanent magnet acts on the armature disk. When the brake is applied, the undiminished spring force generated by the spring elements acts on the armature disk and presses it onto the brake pad carrier, which is then pressed by the armature disk onto the braking surface, in particular onto the braking surface formed on the braking part.

[0013] In an advantageous embodiment, the permanent magnet is radially magnetized, in particular with the magnetization direction of the permanent magnet being radially aligned. Advantageously, the magnetic field generated by the first pole of the permanent magnet passes through a first part of the magnetic body and from there via the return disc, i.e., the armature disc or return disc, from where the magnetic field enters a second part of the magnetic body and then reaches the other pole of the permanent magnet. The first part can be arranged radially outside the second part—at least in the axial region covered by the second part—because the magnetization direction is radially aligned.

[0014] In an advantageous embodiment, the recess is formed axially through the magnetic body. This is advantageous because the recess separates the first part from the second part. Thus, the magnetic body can be constructed in two parts if the recess is also completely continuous in the circumferential direction, in particular, if it runs continuously. If the recess is interrupted in the circumferential direction, the magnetic body can be constructed in one part, and thus the first part is constructed only as the first partial area of ​​the magnetic body, and the second part as the second partial area of ​​the magnetic body.

[0015] In an advantageous embodiment, the recess is formed continuously through the magnetic body in the circumferential direction, in particular so that the magnetic body consists of at least two parts, wherein the first part of the magnetic body is arranged radially outside the permanent magnet and accommodates the coil winding and the second part of the magnetic body functions as a guide ring, in particular wherein the bolts are guided in the guide ring in particular by means of a clearance fit, in particular wherein the guide ring is placed on a bearing receiving part in which a bearing, in particular a rolling bearing, is accommodated for the rotatable mounting of the shaft. The advantage here is that the two-part design of the magnetic body enables simple, cost-effective production and the magnetic field of the permanent magnet can be efficiently utilized.

[0016] In an advantageous embodiment, the radial distance area covered by the armature disk relative to the shaft's rotational axis includes the radial distance area covered by the recess. Advantageously, the armature disk transmits the magnetic field emerging from the first part or sub-area of ​​the magnetic body to the second part or sub-area of ​​the magnetic body.

[0017] In an advantageous embodiment, the radial distance area covered by the return plate relative to the rotational axis of the shaft comprises the radial distance area covered by the recess. Advantageously, the return plate transmits the magnetic field emerging from the first part or sub-region of the magnetic body to the second part or sub-region of the magnetic body.

[0018] In an advantageous embodiment, the permanent magnet is designed as a ring magnet whose ring axis is aligned coaxially with the rotational axis of the shaft. This allows for simple manufacturing by simply inserting the permanent magnet into the recess. Furthermore, the permanent magnet is constructed in a single piece.

[0019] In an advantageous embodiment, the magnetic body, in particular the guide ring of the magnetic body, is placed onto a surface area of ​​a bearing receiving part designed as a cylindrical jacket surface, which receives a bearing, in particular a rolling bearing, for rotatably supporting the shaft. The advantage here is that the magnetic body and thus the coil winding received therein as well as the bolt-guiding recesses of the magnetic body are centered and aligned with the shaft. In an advantageous embodiment, in a first axial position, in particular displacement position, of the armature disk, the return disk is spaced from the magnetic body and the armature disk rests on the magnetic body, and in a second axial position, in particular displacement position, of the armature disk, the armature disk is spaced from the magnetic body and the return disk rests on the magnetic body, in particular on the first and second part of the magnetic body.The advantage here is that the magnetic field generated by the permanent magnet and introduced into and discharged from the magnetic body is returned either through a return plate or alternatively through the armature plate, depending on the position of the armature plate.

[0020] In an advantageous embodiment, a sealing plate, particularly made of metal, is connected to the magnet body and to the bearing support part. Advantageously, the bearing support part is connected to the magnet body by means of the sealing plate.

[0021] In an advantageous embodiment, an annular driver having external teeth is connected to the shaft in a rotationally fixed manner, in particular by means of a keyway connection, wherein a lining carrier having internal teeth, in particular a lining carrier having brake pads axially on both sides, is pushed onto the driver, wherein the lining carrier is connected to the driver in a rotationally fixed manner, wherein the internal teeth engage with the external teeth, wherein the lining carrier is displaceable in the axial direction relative to the driver, wherein the armature disk is arranged in the axial direction between the lining carrier and the magnetic body, wherein spring elements supported on the magnetic body and spaced apart from one another in the circumferential direction press onto the armature disk. The advantage here is that in the event of a power failure, the brake applies automatically and the required electrical power is reduced when the coil winding is energized.In an advantageous embodiment, when the coil winding is energized, the armature disk is or will be drawn toward the magnetic body against the spring force generated by the spring elements, whereby the magnetic field generated by the permanent magnet is induced via the armature disk, and the armature disk is or will be spaced apart from the magnetic body. The advantage here is that when the coil winding is energized, the armature disk creates an additional magnetic holding force, so that the coil winding can be subjected to a lower current than without the permanent magnet. This reduces power loss.

[0022] In an advantageous embodiment, when the coil winding is de-energized, the armature disk is pressed by the spring elements away from the magnet body towards the lining carrier and this towards a braking part having a braking surface, whereby the magnetic field generated by the permanent magnet is returned via the return disk and the armature disk is or will be separated from the magnet body. The advantage here is that by means of the return of the magnetic field generated by the permanent magnet via the

[0023] Return disc the spring force of the spring elements is transferred undisturbed into the armature disc.

[0024] In an advantageous embodiment, the wall thickness of the armature disk is thinned radially between the coil winding and the permanent magnet. This is advantageous because the thinned area can be saturated, thus increasing the magnetic resistance between the radially outer and inner regions of the armature disk.

[0025] In an advantageous embodiment, the armature disk has a region with a narrowed wall thickness in a radial spacing region, which is arranged radially outside the radial spacing region covered by the permanent magnet, in particular radially between the radial spacing region covered by the coil winding and the radial spacing region covered by the permanent magnet, in particular wherein the narrowed region runs continuously in the circumferential direction, in particular wherein the narrowed region is designed as an annular groove running circumferentially. The advantage here is that, by means of the narrowed region, the magnetic circuit of the permanent magnet is separated from the magnetic circuit of the coil winding by means of a high magnetic resistance, since the narrowed region is brought into saturation and thus acts as an air gap for the excessive magnetic field.

[0026] In an advantageous embodiment, the shaft is a rotor shaft of the electric motor, in particular wherein the magnetic body is connected in a rotationally fixed manner to the stator housing of the electric motor and / or wherein the braking part is connected in a rotationally fixed manner to the magnetic body.

[0027] The advantage here is that the brake assembly can be used in a brake motor. Overall, the brake motor can be operated with less power.

[0028] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0029] The invention will now be explained in more detail using schematic illustrations:

[0030] Figure 1 shows a schematic representation of a brake arrangement according to the invention.

[0031] Figure 2 shows a further brake arrangement according to the invention schematically.

[0032] Figure 3 shows a third brake arrangement according to the invention in an oblique view.

[0033] As shown in Figure 1, the brake arrangement has a magnetic body 9 which is made of a ferromagnetic material, in particular a GGG cast or other cast steel.

[0034] The magnetic body 9 has an annular recess in which a coil winding 8 is accommodated. The ring axis of the annular recess is aligned coaxially with the rotational axis 1 of a rotor shaft 32 (not shown in Figure 1).

[0035] An armature disk 2 which is movable in the axial direction relative to the magnetic body 9 is connected in a rotationally fixed manner to the magnetic body 9 and is arranged axially next to the magnetic body 9.

[0036] The axial direction is aligned parallel to the rotor shaft's rotational axis 1. The radial direction is related to the rotational axis 1, as is the circumferential direction.

[0037] When the winding is energized, the armature disk 2 is attracted to the magnet body 9 against the spring elements supported on the magnet body 9.

[0038] A bolt 3 connected to the armature disk 2 projects through an axially continuous recess of the magnetic body 9 and is connected on its side facing away from the armature disk 2 to a particularly annular return disk 4, in particular the annular axis of which is aligned coaxially to the axis of rotation of the rotor shaft.

[0039] The bolt 3 preferably projects through the recess with a clearance fit and is thus guided in the magnet body 9. The return plate 4 is made of a ferromagnetic material, in particular, for example, of steel.

[0040] The armature disk 2 is made of a ferromagnetic material, in particular, for example, of steel.

[0041] The bolts 3 are made of a ferromagnetic or diamagnetic material.

[0042] Due to the rigid coupling of the return plate 4 to the armature plate 2 by means of the bolts 3, the return plate 4 is moved along with the armature plate 2 when the armature plate 2 is moved back and forth in the axial direction.

[0043] A permanent magnet 10, which is preferably magnetized in the radial direction, is arranged in a further recess of the magnetic body 9. The further recess is axially continuous, so that the magnetic body 9 is designed in two parts.

[0044] When the armature disk 2 is pressed away from the magnetic body 9 by the spring elements when the coil winding 8 is not energized, the return disk 4 comes into contact with the magnetic body 9. As a result, the magnetic circuit 5 generated by the permanent magnet 10 is closed via the return disk 4.

[0045] When the coil winding 8 is energized, the armature disk 2 is attracted to the magnetic body 9 against the spring force generated by the spring elements supported on the magnetic body 9, and the return disk 4 previously effective for the permanent magnet 10 is removed from the magnetic body 9.

[0046] The magnetic circuit 5 thus receives an air gap and thus an increased magnetic resistance.

[0047] Instead of the return plate 4, the magnetic return of the magnetic field generated by the permanent magnet 10 is now carried out via the armature plate 2, with the associated second magnetic circuit 6 also symbolically shown in Figure 1. The magnetic circuit 7 created when the coil winding 8 is energized is closed by the armature plate 2, which then rests against the magnet body 9.

[0048] The two-part or multi-part design of the magnetic body 9 particularly provides for a magnetic separation of the third magnetic circuit 7 from the other two magnetic circuits (5, 6). This enables a compact design, with at least a radial air gap being provided between the two parts of the magnetic body 9.

[0049] In a further embodiment, a one-piece design of the magnetic body 9 is also possible, in particular so that all three magnetic circuits (5, 6, 7) pass through the magnetic body 9 at least in sections. For this purpose, instead of a permanent magnet 10 designed as a large magnetic ring, an arrangement of several individual magnets, in particular bar magnets or round magnets, spaced apart from one another in the circumferential direction is used, which are then arranged only in corresponding recesses of the magnetic body 9 and do not have to be spaced apart from one another in the circumferential direction only by air.

[0050] As shown in Figure 2, in a further brake arrangement according to the invention, in contrast to the embodiment according to Figure 1, the magnetic body 9 is accommodated in a housing or connected to a housing. The housing is formed from housing parts (20, 21). Preferably, a guide for the return plate 4 during its axial movement, in particular reciprocating movement, can be provided on a housing part 20.

[0051] As shown in Figure 3, in a further brake arrangement according to the invention, in contrast to the embodiment according to Figures 1 or 2, a rotor shaft 32 is rotatably mounted via a bearing 31, which is accommodated in the bearing receiving part 30. Alternatively, however, the bearing can also be accommodated and / or arranged in a bearing flange connected to the magnetic body 9.

[0052] An annular driver 36 is mounted on the rotor shaft 32. The driver 36 is preferably connected to the rotor shaft 32 in a rotationally fixed manner by means of a keyway.

[0053] A disc-like lining carrier 35 has internal teeth and is mounted on the driver 36, with the internal teeth engaging with external teeth of the driver 36. Thus, the lining carrier 35 is axially displaceable relative to the driver 36, but is rotationally fixedly connected to the driver 36 and thus also to the rotor shaft 32.

[0054] The lining carrier 34 has a brake pad 34 axially on each side. The respective brake pad 34 is arranged radially outside the internal toothing of the lining carrier 35.

[0055] When the coil winding 8 is de-energized, the spring elements 33 press the armature disk 2 onto the brake pad 34 of the pad carrier 35, which is thus pressed with its other brake pad 34 in the axial direction onto a braking surface of a braking part 37.

[0056] The braking part 37 is firmly connected to the magnetic body 9 directly or indirectly.

[0057] The brake pads 34 are fastened and / or connected to a disc-like base body of the pad carrier 35, which is composed of sheet metal and is connected in particular by means of rivets.

[0058] The spring elements 33 are spaced apart from one another in the circumferential direction, in particular evenly spaced apart from one another in the circumferential direction.

[0059] The permanent magnet 10 is designed to be continuous in particular in the circumferential direction, in particular as a magnetic ring whose ring axis is aligned coaxially with the axis of rotation of the rotor shaft, or as individual magnets, in particular bar magnets and / or round magnets, which are spaced apart from one another in the circumferential direction, in particular evenly spaced apart from one another.

[0060] As shown in Figure 3, the coil winding 8 is arranged radially outside the permanent magnet 10. In particular, the area covered by the coil winding 8 in the axial direction overlaps the area covered by the permanent magnet 10 in the axial direction.

[0061] The permanent magnet 10 is mounted on a guide ring 39 and preferably adhesively bonded to the guide ring 39, which is mounted on a bearing support part 30 that accommodates the bearing 31 of the rotor shaft 32. The bearing support part 30 is preferably made of a non-magnetic material, in particular aluminum, and is attached to a sealing plate 38, which bears against a particularly axial end face of the magnet body 9. The sealing plate 38 thus covers the brake assembly at its axial end. The sealing plate 38 is preferably made of a ferromagnetic material.

[0062] The bearing receiving part 30 is arranged radially inside the magnetic body 9. The radial distance area covered by the sealing plate 38 overlaps with the radial distance area covered by the magnetic body 9 and with the radial distance area covered by the bearing receiving part 30.

[0063] The sheets of the base body of the lining carrier 35 are connected to each other by rivets.

[0064] The spring elements 33 are supported on the magnet body 9, spaced from one another in the circumferential direction, and press on the armature disk 2, so that when the coil winding 8 is de-energized, the armature disk 2 is pushed away from the magnet body 9. The armature disk is connected to the magnet body 9 in a rotationally fixed manner and arranged to be movable in the axial direction, in particular guided by the bolts 3 or, in particular, by further bolts that are connected to the magnet body 9 and protrude through respective axially continuous recesses through the armature disk 2.

[0065] When the coil winding 8 is de-energized, the lining carrier 35 is pressed onto the braking surface part 37 by the armature plate 2, which is spring-loaded by the spring elements 33. Thus, the lining carrier 35 is then force-fitted between the armature plate 2 and the braking surface part 37. The resulting frictional heat is dissipated to the surrounding environment via the braking surface part 37 and dissipated via the armature plate 2.

[0066] The magnetic field generated by the radially magnetized permanent magnet 10 and emerging from the magnetic body 9 on the side of the magnetic body 9 axially remote from the armature disk 2 is guided back into the magnetic body 9 via the return disk 4, with the air gap accommodating the permanent magnet 10 being radially bridged by the return disk 4. When the coil winding 8 is energized, however, the armature disk 2 is drawn toward the magnetic body 9, thus pushing the return disk 4 away from the magnetic body 9. Thus, the return of the magnetic field generated by the permanent magnet 10 is then effected via the armature disk 2, which, however, also forms the return for the magnetic field generated by the coil winding 8.

[0067] In further embodiments according to the invention, the armature disk 2 has a narrowed wall thickness in a radial distance region located radially outside the radial distance region covered by the permanent magnet 10, in particular radially between the radial distance region covered by the coil winding 8 and the radial distance region covered by the permanent magnet 10. In this way, the narrowed region is saturated when the armature disk 2 forms the return path for the two magnetic fields, and thus a high magnetic resistance separates the two magnetic circuits 5 and 6.

[0068] The constricted area runs continuously in the circumferential direction. In particular, the constricted area can be designed as an annular groove running circumferentially.

[0069] The return plate 4 is shaped like a perforated plate, with an additional hollow-cylindrical extension extending axially from its radially inner edge region, which protrudes radially between the guide ring 39 and the bearing support part 30 and is thus guided there. The guide ring 39 is pushed onto the bearing support part and rests against a step of the bearing support part 30. The bolts 3 protrude axially through the guide part 39 and are connected on the one hand to the return plate 4 and on the other hand to the armature plate 2.

[0070] The bolts 3 are guided in the guide ring 39 by means of a clearance fit.

[0071] The brake part 37 is connected by means of screws to a housing part 20, which

[0072] Radially surrounds the brake assembly and is connected to the sealing plate 38, which covers the brake assembly at its axial end region facing away from the lining carrier 34 and the brake part 37.

[0073] In further embodiments according to the invention, the lining carrier 34 together with its brake linings is made of a single material, in particular as a monoblock, or of a metallic base ring, the internal toothing of which is placed on the external toothing of the driver 36 and which is radially surrounded by the material of the brake lining, which is materially connected to the base ring and is thus designed as a composite part with the base ring.

[0074] List of reference symbols

[0075] 1 axis of rotation

[0076] 2 anchor disc

[0077] 3 bolts

[0078] 4 Return disc

[0079] 5 first magnetic circuit

[0080] 6 second magnetic circuit

[0081] 7 third magnetic circuit

[0082] 8 coil windings

[0083] 9 magnetic bodies, ferromagnetic

[0084] 10 Permanent magnet, radially magnetized

[0085] 20 Housing part

[0086] 21 Housing part

[0087] 30 bearing support part

[0088] 31 warehouses

[0089] 32 Rotor shaft

[0090] 33 spring element

[0091] 34 brake pad

[0092] 35 lining carriers

[0093] 36 drivers

[0094] 37 Brake part, having a braking surface

[0095] 38 Sealing plate

[0096] 39 Guide ring

Claims

Patent claims:

1. A brake assembly, in particular for an electric motor, for braking a shaft, wherein the brake assembly comprises a magnetic body, in particular made of ferromagnetic material, an armature disk, in particular made of ferromagnetic material, and an electrically energizable coil winding, wherein the coil winding is received in the magnetic body, in particular in an annular recess of the magnetic body, wherein the armature disk is connected to the magnetic body in a rotationally fixed manner and is arranged to be movable in the axial direction, in particular wherein the axial direction is aligned parallel to the axis of rotation of the shaft, in particular wherein the coil winding is designed as a ring winding, the ring axis of which is aligned coaxially to the axis of rotation of the shaft, characterized in that a permanent magnet is arranged in a recess of the magnetic body,wherein circumferentially spaced bolts protrude through respective recesses of the magnet body in the axial direction, wherein the bolts are connected on the one hand to the armature disk and on the other hand to a return disk, in particular wherein the bolts are connected to the return plate at their end region axially remote from the armature plate and are connected to the armature plate at their end region remote from the return plate, in particular wherein the return plate is made of ferromagnetic material.

2. Brake arrangement according to claim 1, characterized in that the permanent magnet is magnetized radially, in particular wherein the magnetization direction of the permanent magnet is aligned radially.

3. Brake arrangement according to one of the preceding claims, characterized in that the recess is formed continuously in the axial direction through the magnetic body.

4. Brake arrangement according to one of the preceding claims, characterized in that the recess is formed continuously through the magnetic body in the circumferential direction, in particular so that the magnetic body consists of at least two parts, wherein the first part of the magnetic body is arranged radially outside the permanent magnet and receives the coil winding and the second part of the magnetic body functions as a guide ring, in particular wherein the bolts are guided in the guide ring in particular by means of a clearance fit, in particular wherein the guide ring is placed on a bearing receiving part in which a bearing, in particular a rolling bearing, is received for the rotatable mounting of the shaft.

5. Brake arrangement according to one of the preceding claims, characterized in that the radial distance area covered by the armature disk with respect to the axis of rotation of the shaft comprises the radial distance area covered by the recess.

6. Brake arrangement according to one of the preceding claims, characterized in that the radial distance area covered by the return disc with respect to the axis of rotation of the shaft comprises the radial distance area covered by the recess.

7. Brake arrangement according to one of the preceding claims, characterized in that the permanent magnet is designed as a ring magnet whose ring axis is aligned coaxially with the axis of rotation of the shaft.

8. Brake arrangement according to one of the preceding claims, characterized in that the magnetic body, in particular the guide ring of the magnetic body, is placed on a surface area of ​​a bearing receiving part designed as a cylindrical surface, which receives a bearing, in particular a rolling bearing, for the rotatable mounting of the shaft.

9. Brake arrangement according to one of the preceding claims, characterized in that in a first axial position, in particular displacement position, of the armature disk, the return disk is spaced from the magnetic body and the armature disk bears against the magnetic body and that in a second axial position, in particular displacement position, of the armature disk, the armature disk is spaced from the magnetic body and the return disk bears against the magnetic body, in particular against the first and second part of the magnetic body.

10. Brake arrangement according to one of the preceding claims, characterized in that a sealing plate, in particular made of metal, is connected to the magnetic body and to the bearing receiving part.

11. Brake arrangement according to one of the preceding claims, characterized in that an annular driver having external teeth is connected to the shaft in a rotationally fixed manner, in particular by means of a keyway connection, wherein a lining carrier having internal teeth, in particular a lining carrier having brake pads axially on both sides, is pushed onto the driver, wherein the lining carrier is connected to the driver in a rotationally fixed manner, wherein the internal teeth are in engagement with the external teeth, wherein the lining carrier is displaceable in the axial direction relative to the driver, wherein the armature disk is arranged in the axial direction between the lining carrier and the magnetic body, wherein spring elements supported on the magnetic body and spaced apart from one another in the circumferential direction press on the armature disk.

12. Brake arrangement according to one of the preceding claims, characterized in that when the coil winding is energized, the armature disk is or becomes attracted to the magnetic body against the spring force generated by the spring elements, wherein the return of the magnetic field generated by the permanent magnet is effected via the armature disk and the return disk is or becomes spaced from the magnetic body.

13. Brake arrangement according to one of the preceding claims, characterized in that when the coil winding is de-energized, the armature disk is pressed by the spring elements away from the magnetic body towards the lining carrier and this is pressed onto a braking part having a braking surface, wherein the return of the magnetic field generated by the permanent magnet is effected via the return disk and the armature disk is or is spaced from the magnetic body.

14. Brake arrangement according to one of the preceding claims, characterized in that the wall thickness of the armature disk is thinned radially between the coil winding and the permanent magnet and / or that the armature disk has a region with a narrowed wall thickness in a radial distance region which is arranged radially outside the radial distance region covered by the permanent magnet 10, in particular radially between the radial distance region covered by the coil winding 8 and the radial distance region covered by the permanent magnet 10, in particular wherein the narrowed region runs continuously in the circumferential direction, in particular wherein the narrowed region is designed as an annular groove running in the circumferential direction.

15. Electric motor with a brake arrangement according to one of the preceding claims, characterized in that the shaft is a rotor shaft of the electric motor, in particular wherein the magnetic body is connected in a rotationally fixed manner to the stator housing of the electric motor and / or wherein the brake part is connected in a rotationally fixed manner to the magnetic body.

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