Braking device for an electric machine

Abstract

The invention relates to a brake device for an electric machine, wherein the brake device has: - a brake lining carrier (3), - a belt drive and - a shaft (2), wherein the belt drive has an inner belt drive component (41) and an outer belt drive component (43) which are connected to one another by means of an intermediate layer (42), wherein the brake lining carrier (3) has an inner toothing which engages with an outer toothing of the outer belt drive component, so that the brake lining carrier (3) is connected to the belt drive in a rotationally fixed but axially movable manner, wherein the inner belt drive component is connected to the shaft (2) in a rotationally fixed manner.

Description

Technical Field

[0001] This invention relates to a braking device for an electric motor. Background Technology

[0002] It is generally known that a brake motor is a motor with a brake.

[0003] As the closest prior art, a spring-pressure brake with a brake disc having friction surfaces on opposite sides is known from patent document DE 10 2006 010 656 B3.

[0004] A friction clutch is known from patent document DE 38 44 476 C1.

[0005] A clutch assembly is known from patent document DE 10 2011 102 077 A1.

[0006] An electric motor with a brake is known from patent document DE 198 38 171 A1.

[0007] An electromagnetic brake having a brake disc that can move axially on a shaft is known from patent document DE 19 32 932 U.

[0008] A braking system with a movable brake disc is known from patent document DE 601 11 429 T2. Summary of the Invention

[0009] Therefore, the object of the present invention is to improve the braking device for an electric motor, wherein the angle of the motor rotor shaft should be detected with high precision.

[0010] According to the present invention, this objective is achieved in a braking device for an electric motor with the features given in claim 1.

[0011] An important feature of this invention in braking devices for electric motors is that the braking device has...

[0012] - Brake pad carrier

[0013] -Driver components, and

[0014] -axis,

[0015] The driving component has internal driving parts and external driving parts interconnected by an intermediate layer, thereby enabling the driving component to be constructed as a metal-plastic composite.

[0016] The brake pad carrier has internal teeth that mesh with the external teeth of an external drive component, thereby connecting the brake pad carrier to the drive component, particularly the external drive component and / or the shaft, in a manner that prevents relative rotation but allows axial movement.

[0017] The internal driving components are connected to the shaft in a manner that prevents relative rotation, especially by means of a key connection, and particularly by means of a gapless connection.

[0018] In particular, the internal driving components, the external driving components, the intermediate layer and / or the driving parts are each implemented as ring components.

[0019] In particular, the external drive component has teeth, especially external teeth, on its radial outer surface that mesh with the internal teeth of the brake pad carrier.

[0020] In particular, the axial direction is parallel to the axis of rotation.

[0021] The advantage here is that torque mutations are introduced into the shaft only in a reduced manner, and thus angle detection can be performed without interference.

[0022] In one advantageous design, the drive component has an inner drive element and an outer drive element, as well as an intermediate layer arranged radially between the inner and outer drive elements.

[0023] In particular, the internal and external driving components are spaced apart from each other, and / or the internal and external driving components are each constructed in a ring shape, and / or the internal driving component is arranged radially inside the external driving component. The advantage here is that it can reduce torque abrupt changes and / or the torque flow transmitted through the driving components. Combined with the reduction of impacts introduced circumferentially from the armature disk to the housing component and / or the magnet body, it achieves a high degree of protection for the angle sensor arranged on the motor, especially the sensor shaft that is not rotatably connected to the rotor shaft. That is, angle detection can be robustly performed without being affected by interference generated during the operation of the electromagnetically operable brake.

[0024] In an advantageous design, the internal driving component has radially outward-projecting ribbed areas, particularly protruding into the intermediate layer. The advantage here is that the intermediate layer can be made more flexible and / or softer than the two driving components. This reduces the flow of force and / or torque transmitted through the intermediate layer.

[0025] In an advantageous design, the external drive component has radially inwardly projecting rib regions, particularly protruding into the intermediate layer. The advantage here is that the intermediate layer can be made softer than the external and / or internal drive components. This reduces the force and / or torque flow transmitted through the intermediate layer.

[0026] In an advantageous design, the intermediate layer is made of plastic, especially polymer and / or elastomer, and / or the two driving components are made of metal, especially steel. The advantage here is that cost-effective and simple vibration damping can be implemented.

[0027] In an advantageous design, the radial distance region covered by the outer driving component, especially the rib region of the outer driving component, overlaps with the radial distance region covered by the inner driving component, especially the rib region of the inner driving component. The advantage here is that, in the event of interlayer failure, the circumferentially gapped form-locking between the two driving components will function. Thus, when the braking device changes state, especially when the braking device disengages or engages, noise, i.e., an acoustic alarm signal, is generated due to the sides of the rib regions colliding with each other.

[0028] In an advantageous design, the external drive component has teeth, particularly external teeth, on its radially outer surface that mesh with the internal teeth of the brake pad carrier. The advantage here is that the drive component is implemented as a multi-piece assembly, especially a composite component. However, the external dimensions are made the same as those of a one-piece drive component. Therefore, known one-piece drive components can be easily replaced with a multi-piece drive component, thereby achieving improved vibration reduction.

[0029] In an advantageous design, the shaft is supported by a bearing housed in a flange and another bearing housed in another flange, wherein the flanges are connected to the stator housing of the motor.

[0030] In particular, the shaft is the rotor shaft of the motor.

[0031] The advantage here is that although the shaft is arranged to be rotatably supported, when the brake is disengaged or engaged, an impact can be introduced into the shaft. Thus, when the present invention does not mitigate the impact by means of a first bushing that is softer than the second bushing, the angle sensor may be disturbed when detecting the angular position of the rotor shaft on the B side, that is, on the side of the brake away from the stator.

[0032] In an advantageous design, the braking device additionally has

[0033] -Magnet body

[0034] - Winding

[0035] - at least one plug

[0036] - Housing components with braking surfaces

[0037] - Armature plate

[0038] -At least one spring component, especially a mating spring.

[0039] -At least one first bushing

[0040] The housing component is connected to the magnet body by means of bolts—especially in a locking manner at least in the circumferential direction.

[0041] The first bushing is housed within the second bushing, or more specifically, pressed into the second bushing.

[0042] The spring member supported on the housing component presses the first bushing and / or the second bushing against the magnet body.

[0043] The radial distance region covered by the armature disk includes, in particular, the radial distance region covered by the second bushing.

[0044] The axial region covered by the armature disk includes, in particular, the axial region covered by the second bushing, or overlaps with it.

[0045] The advantage here is that by stopping the armature disk circumferentially on the second bushing, the armature disk is connected to the magnet body without relative rotation in the circumferential direction. The second bushing transmits the impact to the bolt via the first bushing, and the bolt transmits the impact to the magnet body and the housing components. Thus, the impact can be mitigated by means of the elasticity of the first bushing. At the same time, the first bushing serves as an axial sliding support for the bushing assembly, i.e., the two press-fitted bushings, i.e., the first and second bushings.

[0046] In an advantageous design, the first bushing is made of a softer and / or more elastic material than the second bushing. This has the advantage of reducing impact and providing a sliding support in the axial direction, resulting in minimal static friction and preventing corrosion during nut readjustment due to wear of the brake pads. This is because the bolt is made of metal, while the first bushing is made of plastic.

[0047] In an advantageous design, the first bushing is made of rubber, a rubber-coated material, or plastic, especially a polymer, and the second bushing is made of metal, especially steel. The advantage here is that it reduces the impact of the armature disc on the second bushing.

[0048] In one advantageous design, the first bushing is pressed into the second bushing.

[0049] In particular, the first bushing is an O-ring. The advantage of this is that a fixed connection is achieved. Furthermore, the bushing assembly allows for multiple functions, such as sliding support, impact mitigation, and a stable outer surface.

[0050] In an advantageous design, the first bushing is slidably supported on the bolt, specifically fitted precisely onto the bolt. This provides an advantage in terms of impact reduction and the slidable support of the bushing assembly. Furthermore, the armature disc impacts the second bushing, which can be made of a stable material that does not cause significant vibration damping but achieves a long service life. Impact reduction is achieved by the first bushing being housed in and / or pressed into the second bushing.

[0051] In an advantageous design, the armature disc is circumferentially and form-locked to the second bushing and / or bolt with a gap. The advantage here is that the armature disc extends radially longer than the brake pad carrier and the bolt is arranged in the radially extended radial distance region. Thus, the bolt can pass through a notch axially penetrating the armature disc. In this way, the brake pad carrier is arranged to rotate freely with the shaft in the circumferential direction, and the armature disc is circumferentially and form-locked.

[0052] In an advantageous design, the bolt is threaded to the housing component and passes through a notch that axially penetrates the magnet body.

[0053] In particular, the nut is screwed onto the threaded area located on the side of the magnet body facing away from the housing component.

[0054] In particular, the bolt has a stepped portion, which rests against the stepped portion of the stepped hole in the housing component. An advantage here is that the braking device can be readjusted / calibrated when the brake pads wear, i.e., the axial distance between the magnet body and the housing component can be adapted, wherein the readjustment part, i.e., the nut, can be operated from side B.

[0055] In one advantageous design, the bolt is threaded to the magnet body and passes through a notch that axially penetrates the housing component.

[0056] In particular, the nut is screwed onto the threaded area located on the side of the housing component opposite to the magnet body.

[0057] In particular, the bolt has a stepped portion, which abuts against the stepped portion of the stepped hole in the magnet body. An advantage here is that the braking device can be readjusted when the brake pads wear out; that is, the axial distance between the magnet body and the housing component can be adapted. The readjustment part, i.e., the nut, can be operated from side B.

[0058] In an advantageous design, the winding is housed in a recess in the magnet body and / or the armature disk is axially movably, with a gap, but not relatively rotatably connected to the magnet body, especially to the bolt. The advantage here is that the loss of field lines is minimized.

[0059] In an advantageous design, a brake pad carrier, axially movable on a shaft but not rotatably connected to it, is arranged between the housing component and the armature disc. The advantage here is that the brake pad carrier can be braked from both sides; that is, a first brake pad can be loaded by the armature disc, and a second brake pad can be pressed against the brake surface of the housing component. Here, the brake surface, like the armature disc, is precision-machined, and in particular, ground.

[0060] In an advantageous design, the brake pad carrier has internal teeth that mesh with external teeth introduced into a shaft or a drive element, which is connected to the shaft in a way that prevents relative rotation—especially by means of a key connection.

[0061] In particular, the drive component is implemented as a ring. The advantage here is that, by means of teeth, high braking torque can be transferred from the brake pad carrier through the drive component or directly into the shaft.

[0062] In an advantageous design, a spring supported on the magnet body presses the armature disk away from the magnet body, specifically pressing it against the brake pad carrier in the axial direction.

[0063] When the toroidal winding is energized, the armature disk is attracted toward the magnet body while overcoming the spring force generated by the spring.

[0064] Furthermore, when no power is applied, the armature disc is pressed by the spring onto the brake pad carrier, particularly onto the brake pads located on the side of the brake pad carrier facing the armature disc.

[0065] In particular, this causes the brake pad carrier, especially its other brake pad, to press against the housing component, especially the brake surface constructed on the housing component. The advantage here is that, when not energized, the electromagnetically operable braking device is engaged. However, when energized, the braking device disengages.

[0066] In an advantageous design, the housing component is sealed and detachably connected to a flange that houses a bearing for supporting the shaft. An advantage here is that the electromagnetically operable brake can be stored as a pre-assembled unit and subsequently connected to a motor.

[0067] In an advantageous design, the sealing strip covers and / or seals the space containing the armature disc and brake pad carrier relative to the environment. This has the advantage of preventing contaminants from seeping into the friction area.

[0068] In an advantageous design, the axial area covered by the second bushing is smaller than the axial area covered by the first bushing, and a spring presses the first bushing against the magnet body. The advantage here is that the impact transmitted by the armature disk can be absorbed in the circumferential direction by a harder material, thus achieving a longer lifespan. Furthermore, the spring pressing against the first bushing prevents the component impacted by the armature disk, i.e., the second bushing, from being additionally restricted and / or loaded.

[0069] In an advantageous design, the axial region covered by the second bushing is equal to or larger than the axial region covered by the first bushing, and the spring presses the second bushing against the magnet body. The advantage here is that the functions of sliding support and impact damping are achieved by the first bushing, while the second bushing is pressed against the magnet body. Thus, the impact introduced into the second bushing in the circumferential direction is at least partially mitigated by the static friction acting in the circumferential direction during relative movement of the first bushing and the sliding friction of the frictional contact between the second bushing and the magnet body or the spring. Therefore, the first bushing only needs to dampen the remaining impact energy.

[0070] In an advantageous design, the braking device has

[0071] -Magnet body

[0072] - Winding

[0073] - Housing components with braking surfaces, and

[0074] - Armature plate

[0075] The brake pad carrier and armature disk are arranged axially between the housing component and the magnet body.

[0076] The sealing strip is connected to the housing component in the first axial region, and is particularly force-locked and pressed together, and is connected to the magnet body in the second axial region, and is particularly force-locked and pressed together.

[0077] The sealing strip radially surrounds the armature disc and brake pad carrier, especially covering and / or sealing the space containing the armature disc and brake pad carrier relative to the environment.

[0078] The sealing strip has a radially inwardly extending protruding area that restricts the armature disc in the axial direction.

[0079] The advantage here is that the sealing strip serves both as a seal to prevent contaminants from seeping in and as a component to reduce the movement of the armature disc, especially the impact of the armature disc on the brake pad carrier. Here, the raised area is integrally formed, i.e., one-piece, on the sealing strip made of plastic or rubber. The sealing strip is formed in a ring shape, and the raised area is also formed in a ring shape.

[0080] In one advantageous design, a sealing ring is arranged on the magnet body, the sealing ring restricting the armature disk in the opposite direction to the axial direction.

[0081] In particular, the sealing ring is housed in an annular groove introduced into the magnet body.

[0082] In particular, the ring axis is the axis of rotation of the shaft. An advantage here is that elements that reduce the movement of the armature disk are also arranged on the side of the armature disk away from the raised area.

[0083] In an advantageous design, the elastic force acting on the armature disc generated by the sealing ring is numerically greater than the elastic force acting on the armature disc generated by the elastically tensioned, especially pre-tensioned, raised area, particularly when the brake is disengaged, especially when the winding is energized. The advantage here is that the spring's restoring effect is not diminished, and thus the braking mechanism is kept slow if necessary.

[0084] In an advantageous design, the radial distance region covered by the sealing strip, particularly the raised area of ​​the sealing strip, overlaps with the radial distance region covered by the armature disc. The advantage here is that the armature disc rests against the raised area, thereby introducing a resilient force into the armature disc.

[0085] In an advantageous design, the axial region covered by the sealing strip, particularly the raised area of ​​the sealing strip, overlaps with the axial region covered by the brake lining carrier, and / or, especially in the absence of overlap, adjoins the axial region covered by the armature disc. The advantage here is that a compact arrangement can be achieved. Here, the radial extension of the brake lining carrier is smaller than that of the armature disc. Therefore, the raised area can be arranged in free space radially outside the brake lining carrier. This results in an implementation scheme that is as compact as possible.

[0086] In an advantageous design, the ring axis of the sealing ring is the axis of rotation of the shaft. This has the advantage of allowing for uniform contact between the armature disc and the sealing ring, particularly the O-ring, arranged parallel to the end face of the armature disc.

[0087] In an advantageous design, the raised region is configured as annular and / or circumferentially surrounding the shaft, particularly wherein the annular axis of the raised region is the axis of rotation of the shaft, and / or particularly wherein the axis of symmetry of the raised region is the axis of rotation of the shaft. The advantage here is that the sealing strip and the raised region are configured to circumferentially surround the shaft, thereby achieving simple manufacturing, particularly for producing continuous profiles.

[0088] In an advantageous design, the ring is arranged at a radial distance, particularly at the maximum radial distance, within the radial distance region covered by the armature disk. The advantage here is that vibration reduction can be achieved as effectively as possible.

[0089] Other advantages are derived from the dependent claims. The invention is not limited to the combination of features in the claims. For those skilled in the art, in particular from the objective setting and / or by means of objectives set in comparison with the prior art, other reasonable combinations of claims and / or individual claim features and / or specification features and / or drawing features are derived. Attached Figure Description

[0090] The invention will now be explained in detail with reference to the schematic diagram:

[0091] exist Figure 1 The electromagnetically operable braking device of the motor according to the invention is shown in a sectional view at an angle.

[0092] exist Figure 2 It shows Figure 1 A magnified view of a local area.

[0093] exist Figure 3 The image shows the corresponding oblique view without being cut open.

[0094] exist Figure 4 Another electromagnetically operable braking device of the motor according to the invention is shown in oblique view with a cross-section, wherein the driving elements (41, 42, 43) are implemented as multiple pieces.

[0095] exist Figure 5 The drive components (41, 42, 43) are shown in a slanted view. Detailed Implementation

[0096] As shown in the figure, the braking device has a shaft, in particular the rotor shaft 2 of the motor, wherein an annular drive element 1 is pushed onto the shaft and connected by means of a key connection in a manner that prevents relative rotation.

[0097] The drive element 1 has teeth / engaging portions, particularly external teeth, on its outer periphery. Preferably, the external teeth do not have an inclination angle, that is, they are straight teeth, so that the teeth extend in the axial direction.

[0098] The brake pad carrier 3 is pushed onto the drive member 1, and the brake pad carrier has internal teeth that mesh with the external teeth. Thus, the brake pad carrier 3 is connected to the drive member 1 in a manner that prevents relative rotation but allows axial movement.

[0099] The brake pad carrier 3 has brake pads on both sides of the axial direction.

[0100] In particular, the magnet body 4, made of cast steel, has an annular notch into which the annular winding 5 is placed.

[0101] Each axially oriented bolt 6, especially the threaded bolt, is guided through the notch that axially penetrates the magnet body 4, and screwed into the threaded hole of the housing component 11 using its threaded area.

[0102] On the side of the magnet body 4 facing away from the housing component 11, nuts 6 are screwed onto the other threaded area of ​​each bolt 6, thereby restricting the magnet body to the maximum distance relative to the housing component 11.

[0103] The corresponding supporting spring, especially the helical spring, which is supported on the housing component 11, is fitted onto the bolt 6 and pressed against the first bushing 7, especially the plastic bushing.

[0104] The first bushing is pressed into a slightly larger second bushing 8, which is made of a different material than the first bushing.

[0105] Here, the second bushing 8 is preferably made of metal, especially steel.

[0106] Therefore, the spring 10 presses the first bushing 7 onto the housing component 4.

[0107] The armature disk 9 is arranged axially between the brake pad carrier 3 and the magnet body 4.

[0108] The radial distance covered by the armature disc includes the radial distance area covered by the bolt 6 together with the first bushing 7 and the second bushing 8 fitted onto the bolt.

[0109] Therefore, the bolt 6, together with the first bushing 7 fitted onto the bolt 6 and the second bushing 8 that accommodates the first bushing 7, axially passes through the notch that penetrates the armature disk 4.

[0110] In this way, the armature disk 9 is arranged to be connected to the magnet body with a gap so that it cannot rotate relative to it, but it can move axially.

[0111] The spring, which is not shown in the figure and is supported on the magnet body, presses the armature disk 9 away from the magnet body 4, especially pressing it against the brake pad carrier 3 in the axial direction.

[0112] When the toroidal winding 5 is energized, the armature disk 9 is attracted toward the magnet body 4, wherein the armature disk 9 overcomes the spring force generated by the spring.

[0113] When no power is applied, the armature disc 9 is pressed by a spring onto the brake pad carrier 3, particularly onto the brake pad arranged on the side of the brake pad carrier 3 facing the armature disc 9, thereby pressing the brake pad carrier 3, particularly with its other brake pad, onto the housing component 11, particularly onto the brake surface constructed on the housing component 11.

[0114] The radial distance region covered by the brake pad carrier 3 is separated from the radial distance region covered by the bolt 6.

[0115] Preferably, the bolts 6 are regularly spaced apart from each other in the circumferential direction and are arranged at the same radial distance.

[0116] The sealing strip, not shown in the figure, and particularly made of rubber, covers the area between the magnet body 4 and the housing component 11 relative to the environment. Here, the sealing strip surrounds the armature disk 8 radially outward, that is, it is arranged at a greater radial distance than the armature disk 9 in the axial region covered by the armature disk 9, and is particularly radially spaced from the armature disk 9.

[0117] Because the first bushing 7 is made of a softer material than the second bushing 8, when the brake is engaged or disengaged, the armature disc 9 impacts the second bushing 8, and this impact is then directed to the first bushing 7 and dampened by it. Furthermore, the first bushing is arranged and thus slidably supported on a metal pin 6. Therefore, a polymer or elastomer is preferably chosen as the material for the first bushing 7.

[0118] exist Figure 1 and Figure 2 In the embodiment shown, the first bushing 7 is shorter in the axial direction than the second bushing 8.

[0119] As the brake pads wear down, the distance between the magnet body 4 and the housing component 11 can be adjusted by rotating the nut 14. This is because the bolt 6 has a stepped portion, which allows it to rest against the housing component 11 when it is screwed into it.

[0120] Here, in particular, the axial direction is always parallel to the axis of rotation of the shaft, the circumferential direction relates to the rotation angle of the shaft, and the corresponding radial distance relates to the distance from the axis of rotation of the shaft.

[0121] The housing component 11 is preferably detachably connected to the flange 12 of the motor, particularly the support flange, but this connection is implemented with a high level of protection, i.e., sealing. Here, the flange 12 houses the bearing 13, which rotatably supports the shaft, particularly the rotor shaft 2, and is connected to the stator housing of the motor. The stator housing is connected to another flange that houses another bearing of the rotor shaft.

[0122] In another embodiment, the first bushing 7 extends axially in the same or greater manner as the second bushing 8. Preferably, a cooperating spring 10 presses against the second bushing 8, thus pressing the second bushing against the magnet body 4. Thus, in this embodiment, as according to... Figure 1 and 2Compared to the previous implementation, the spring force of the spring 10 is guided through the second bushing 8 instead of the first bushing 7. Therefore, the first bushing 7 only functions to provide sliding support on the bolt 6 and to reduce the impact transmitted from the armature disc 9 into the second bushing 7.

[0123] In another embodiment according to the invention, the first bushing is implemented as a ring made of polymer, particularly an O-ring, especially an O-ring made of rubber. Here, this ring is pressed into a second bushing 8 made of steel.

[0124] Therefore, in another embodiment of the invention, in an electromagnetically operable braking device for an electric motor, the armature disc is arranged such that it cannot rotate relative to the bolt but can move axially, and a plastic bushing pressed into a metal bushing is fitted onto the bolt.

[0125] As in Figure 4 and Figure 5 As shown in the figure, the only difference from the above embodiment is that the drive component is implemented as a multi-piece.

[0126] In addition, a sealing strip 40 is shown, which is connected to the magnet body 4 in a first axial end region and to the housing component 11 in another axial end region.

[0127] The internal drive component 41 is connected to the shaft 2 by means of a key connection and has radially outwardly projecting, axially extending rib regions, which are preferably regularly spaced apart from each other in the circumferential direction.

[0128] The external drive component 43 has radially inwardly projecting, axially extending rib regions that are preferably regularly spaced apart from each other in the circumferential direction and are also spaced apart from the rib regions of the internal drive component 41 in the circumferential direction but overlap in the radial direction.

[0129] The radial distance region covered by the rib region of the external driving component 43 overlaps with the radial distance region covered by the rib region of the internal driving component 41.

[0130] An intermediate layer 42 is arranged radially between the inner driving component 41 and the outer driving component 43. The intermediate layer is composed of plastic, especially polymer and / or elastomer.

[0131] In this way, rotational shocks, i.e., sudden torque changes, can be reduced. This is because, for example, when the brake is disengaged or engaged, braking torque is introduced into the shaft, particularly the rotor shaft 2. Here, the torque flows through the intermediate layer 42, causing the intermediate layer to deflect elastically and also absorb energy. Therefore, shocks can be avoided.

[0132] The rib regions preferably have a rectangular outline. The rib regions preferably extend in the axial direction without any tilt angle.

[0133] In the event of failure of the intermediate layer 42, the form-locking mechanism, which has a circumferential gap between the rib areas of the internal and external driving components (41, 43), becomes effective. This improves safety. Because braking function is still guaranteed even in the event of failure of the intermediate layer 42, higher noise emissions occur due to the impact of the rib areas against each other, thus generating an acoustic alarm signal.

[0134] The external driving component 43 has teeth on its radially outer side, especially according to Figures 1 to 3 The toothed portion of the drive member 1 in the embodiments described above is the same as the toothed portion, especially the external toothed portion.

[0135] As in Figure 6 and Figure 7 As shown, instead of the sealing strip 40, a sealing strip 60 is provided to cover the working area of ​​the armature disk 9 and the working area of ​​the brake pad carrier 3. Here, the sealing strip 60 has a radially inwardly projecting protruding area 61, which elastically restricts the armature disk 9 in the axial direction. Therefore, when the winding 5, especially the coil 5, is not energized, the armature disk 9 is pressed against the protruding area 61.

[0136] When the armature disk 9 is pressed away from the magnet body 4 by the spring supporting it on the magnet body, especially when it is pressed against the brake pad carrier 3 in the axial direction, the raised area 61 acts in the opposite direction and thus reduces the impact of the armature disk 9 on the brake pad carrier 3.

[0137] Therefore, the impact of the armature disc 9 on the brake pad carrier 3 is reduced by means of the elastically deflectable protrusion 61.

[0138] The radial distance area covered by the sealing strip 60 together with the raised area 61 overlaps with the radial distance area covered by the armature plate 9.

[0139] A clamp may be fixed in the first recess 63 of the sealing strip 60, particularly in the annular first recess that surrounds in the circumferential direction. When operated, the clamp retracts the sealing strip 60 and thus forcefully / frictionally presses it against the housing component 11.

[0140] Similarly, a clamp can be fixed in the second recess 64 of the sealing strip 60, especially in the annular second recess that surrounds in the circumferential direction. When operated, the clamp will retract the sealing strip 60 and thereby forcefully lock it against the magnet body 4.

[0141] On the magnet body 4, a sealing ring 62, particularly an O-ring, and especially a plastic or rubber ring, is arranged in an annular groove surrounding the magnet body 4 in the circumferential direction. Here, the sealing ring 62 protrudes axially toward the armature disk 9, thereby also reducing the impact of the armature disk 9 on the magnet body 4.

[0142] The sealing ring 62 is preferably arranged over the largest possible radial distance, wherein the radial distance is arranged in the radial distance region covered by the armature disk 9.

[0143] Preferably, the sealing ring 62 and the raised region 61 are implemented to extend so far along the axial direction that the armature disc 9 contacts not only the sealing ring 62 but also the raised region 61 throughout its entire working stroke (i.e., without interruption). In this way, the effects of unevenness are reduced.

[0144] The preload, especially the elastic force, of the sealing ring 62 is higher than the elastic force caused by the raised area 61 at least when the brake is engaged.

[0145] Thus, the elastic force generated by the sealing ring 62 enhances the spring force. Conversely, the elastic force introduced by the protruding region 61 on the armature plate acts in the opposite direction.

[0146] List of reference numerals in the attached diagram:

[0147] 1. Drive components

[0148] 2. Rotor shaft

[0149] 3 Brake pad carrier

[0150] 4. Magnet body

[0151] 5 coils

[0152] 6. Bolts, especially threaded bolts

[0153] 7. First bushing, especially plastic bushing

[0154] 8. Second bushings, especially metal bushings

[0155] 9. Armature plate

[0156] 10 Spring components

[0157] 11. Housing components

[0158] 12. Flanges, especially support flanges

[0159] 13 bearings

[0160] 14 Nuts

[0161] 40 Sealing tape

[0162] 41 Internal driving components

[0163] 42 Intermediate Layer

[0164] 43 External driving components

[0165] 60 Sealing tape

[0166] 61. Raised area

[0167] 62 Sealing ring

[0168] 63. Concave areas, especially those in a ring-shaped depression that encircles the perimeter.

[0169] 64. Recesses, especially those in a ring shape that encircles the perimeter.

Claims

1. A braking device for an electric motor, wherein, The braking device has: - Brake pad carrier, - Drive components, and - axis, Its features are, The drive component has internal drive parts and external drive parts interconnected by means of an intermediate layer, thereby making the drive component a metal-plastic composite; The brake pad carrier has internal teeth that mesh with the external teeth of the external driving component, thereby connecting the brake pad carrier to the driving component and / or the shaft in a manner that prevents relative rotation but allows axial movement. The internal driving components are connected to the shaft in a manner that prevents relative rotation.

2. The braking device according to claim 1, characterized in that, The brake pad carrier is connected to the external drive component in a manner that prevents relative rotation but allows axial movement.

3. The braking device according to claim 1, characterized in that, The internal driving components are connected to the shaft by means of a key connection in a manner that prevents relative rotation.

4. The braking device according to claim 1, characterized in that, The internal driving components are connected to the shaft without clearance in a manner that prevents relative rotation.

5. The braking device according to claim 1, characterized in that, The internal driving components, external driving components, intermediate layers and / or driving elements are respectively implemented as ring components.

6. The braking device according to claim 1, characterized in that, The external drive component has teeth on its radially outer surface that mesh with the internal teeth of the brake pad carrier.

7. The braking device according to claim 6, characterized in that, The external drive component has external teeth on its radial outer surface that mesh with the internal teeth of the brake pad carrier.

8. The braking device according to claim 1, characterized in that, The drive component has an inner drive component and an outer drive component, as well as an intermediate layer arranged radially between the inner drive component and the outer drive component.

9. The braking device according to claim 8, characterized in that, The internal driving components and the external driving components are spaced apart from each other, and / or therein, The internal driving component and the external driving component are respectively constructed in a ring shape, and / or wherein the internal driving component is arranged radially inside the external driving component.

10. The braking device according to any one of claims 1 to 9, characterized in that, The internal driving components have radially outward-protruding rib areas. and / or The external drive components have radially inward protruding rib areas.

11. The braking device according to claim 10, characterized in that, The rib region of the internal driving component and the rib region of the external driving component protrude into the intermediate layer.

12. The braking device according to any one of claims 1 to 9, characterized in that, The middle layer is made of plastic, and / or the two drive components are made of metal. and / or The radial distance area covered by the external driving component overlaps with the radial distance area covered by the internal driving component.

13. The braking device according to claim 12, characterized in that, The intermediate layer is made of filler, adhesive, polymer and / or elastomer; the two drive components are made of steel.

14. The braking device according to claim 12, characterized in that, The radial distance region covered by the rib region of the external driving component overlaps with the radial distance region covered by the rib region of the internal driving component.

15. The braking device according to any one of claims 1 to 9, characterized in that, The first bushing is housed within the second bushing. The spring member supported on the housing component presses the first bushing and / or the second bushing against the magnet body. The radial distance region covered by the armature disk includes the radial distance region covered by the second bushing. The axial region covered by the armature disk includes the axial region covered by the second bushing, or overlaps with the axial region covered by the second bushing.

16. The braking device according to any one of claims 1 to 9, characterized in that, The braking device has: - Magnet body, - Winding, - At least one plug, - Housing components with braking surfaces, - Handle plate, - At least one spring element, - At least one first bushing, The housing component is connected to the magnet body by means of a bolt. The first bushing is housed within the second bushing. The spring member supported on the housing component presses the first bushing and / or the second bushing against the magnet body. The radial distance region covered by the armature disk includes the radial distance region covered by the second bushing. The axial region covered by the armature disk includes the axial region covered by the second bushing, or overlaps with the axial region covered by the second bushing.

17. The braking device according to claim 16, characterized in that, The spring component is a mating spring.

18. The braking device according to claim 16, characterized in that, The housing component is connected to the magnet body in a form-locking manner, at least in the circumferential direction, by means of a bolt.

19. The braking device according to claim 16, characterized in that, The first bushing is pressed into the second bushing.

20. The braking device according to claim 16, characterized in that, The first bushing is made of a softer and / or more flexible material than the second bushing. and / or The first bushing is made of rubber, a rubber-coated material, or plastic, while the second bushing is made of metal. and / or The first bushing is pressed into the second bushing.

21. The braking device according to claim 20, characterized in that, The first bushing is an O-ring.

22. The braking device according to claim 16, characterized in that, The first bushing is slidably supported on the bolt. and / or The armature disc is connected to the second bushing and / or bolt in a form-locking manner with a gap in the circumferential direction.

23. The braking device according to claim 22, characterized in that, The first bushing was precisely fitted onto the bolt.

24. The braking device according to claim 16, characterized in that, The bolt is threaded to the housing component and passes through a notch that axially penetrates the magnet body.

25. The braking device according to claim 24, characterized in that, The nut is screwed onto the threaded area located on the side of the magnet body opposite to the housing component.

26. The braking device according to claim 24, characterized in that, The bolt has a stepped portion, which allows it to abut against the stepped portion of a stepped hole in the housing component. and / or The bolt is threaded to the magnet body and passes through a notch that axially penetrates the housing component. The nut is screwed onto a threaded area located on the side of the housing component opposite to the magnet body.

27. The braking device according to claim 24, characterized in that, The bolt has a stepped portion, which is used to abut against the stepped portion of the stepped hole in the magnet body.

28. The braking device according to claim 16, characterized in that, The winding is accommodated in a recess in the magnet body. And / or wherein the armature disk is connected to the magnet body in a manner that allows axial movement, has a gap, and cannot rotate relative to it. and / or A brake pad carrier that can move axially on the shaft and is connected to the shaft in a manner that prevents relative rotation is arranged between the housing component and the armature disk.

29. The braking device according to claim 28, characterized in that, The armature disc is connected to the bolt in a manner that allows axial movement, has gaps, and cannot rotate relative to it.

30. The braking device according to claim 16, characterized in that, The spring supporting the magnet body pushes the armature disk away from the magnet body. When the toroidal winding is energized, the armature disk is attracted toward the magnet body while overcoming the spring force generated by the spring. When no power is applied, the armature disc is pressed against the brake pad carrier by the spring. This causes the brake pad carrier to press its other brake pad against the housing component.

31. The braking device according to claim 30, characterized in that, The spring supported on the magnet body presses the armature disk against the brake pad carrier (3) in the axial direction.

32. The braking device according to claim 30, characterized in that, The armature disc is pressed by a spring onto the brake pads located on the side of the brake pad carrier facing the armature disc.

33. The braking device according to claim 30, characterized in that, The brake pad carrier presses its other brake pad against the brake surface constructed on the housing component.

34. The braking device according to claim 16, characterized in that, The housing component is sealed and detachably connected to a flange, the flange housing a bearing for supporting the shaft. and / or The sealing strip covers and / or seals the space containing the armature disc and brake pad carrier relative to the environment.

35. The braking device according to claim 16, characterized in that, The axial area covered by the second bushing is smaller than the axial area covered by the first bushing, and the spring presses the first bushing against the magnet body. or The axial area covered by the second bushing is equal to or greater than the axial area covered by the first bushing, and the spring presses the second bushing onto the magnet body.

36. The braking device according to any one of claims 1 to 9, characterized in that, The braking device has: - Magnet body, - Winding, - Housing components with braking surfaces, and - Handle plate, The brake pad carrier and armature disk are arranged axially between the housing component and the magnet body. The sealing strip is connected to the housing component in the first axial region and to the magnet body in the second axial region. The sealing strip radially surrounds the armature disc and brake pad carrier. The sealing strip has a radially inwardly extending protruding area, which restricts the armature disc in the axial direction.

37. The braking device according to claim 36, characterized in that, The sealing strip is forcefully pressed against the housing component in the first axial region and forcefully pressed against the magnet body in the second axial region.

38. The braking device according to claim 36, characterized in that, The sealing strip covers and / or seals the space containing the armature disc and brake pad carrier relative to the environment.

39. The braking device according to claim 36, characterized in that, A sealing ring is arranged on the magnet body, which restricts the armature disk in the opposite direction to the axial direction. and / or The elastic force generated by the sealing ring and acting on the armature disc is numerically greater than the elastic force generated by the elastically tensioned, pre-tightened protrusion area and acting on the armature disc. This is especially true when the braking device is disengaged, i.e., when the winding is energized. and / or The radial distance area covered by the sealing strip overlaps with the radial distance area covered by the armature disc. and / or The axial region covered by the sealing strip overlaps with the axial region covered by the brake pad carrier, and / or, in the absence of overlap, is adjacent to the axial region covered by the armature disc. and / or The axis of the sealing ring is the axis of rotation of the shaft. and / or The raised region is configured as annular and / or configured to surround in the circumferential direction, wherein the annular axis of the raised region is the axis of rotation of the axis, and / or wherein the axis of symmetry of the raised region is the axis of rotation of the axis. and / or The ring is arranged at a radial distance within the radial distance region covered by the armature disk.

40. The braking device according to claim 39, characterized in that, The sealing ring is housed in an annular groove introduced into the magnet body.

41. The braking device according to claim 39, characterized in that, The radial distance region is covered by the raised area of ​​the sealing strip, and the axial region is covered by the raised area of ​​the sealing strip.

42. The braking device according to claim 39, characterized in that, The ring is arranged at the maximum radial distance within the radial distance region covered by the armature disk.

43. A motor having a braking device according to any one of claims 1 to 42, characterized in that, The shaft is supported in a bearing housed in a flange and in another bearing housed in another flange, wherein the flange is connected to the stator housing of the motor.

44. The motor according to claim 43, characterized in that, The shaft is the rotor shaft of the motor.

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