Brake arrangement

Abstract

Brake assembly comprising a brake pad carrier (2), a drive lug (7), a stop ring (9) and a spring, wherein the driver (7) is non-rotatably connected to a shaft (10), in particular by means of a keyway connection, wherein the brake pad carrier (2) is connected to the driver (7) in a rotationally fixed but axially displaceable manner, in particular wherein the axial direction is aligned parallel to the axis of the shaft (10), wherein the spring is arranged axially between the stop ring (9) and the brake pad carrier (2), the spring is supported on the stop ring (9), wherein the spring is arranged in an annular groove of the stop ring (9) such that the spring force generated by the spring is directed to push the brake pad carrier (2) away from the counter braking surface in order to overcome a static friction force acting on the brake pad carrier (2), wherein the working range of the spring (8) corresponds to the axial width of the annular groove.

Description

[0001] The invention relates to a brake arrangement.

[0002] It is generally known that a brake arrangement has a brake pad carrier which can be pressed against a counter braking surface, so that braking force or braking torque can be generated by means of friction.

[0003] From DE 833 070 B, an electromagnetic brake release device attached to an electric machine is known as the closest prior art.

[0004] A brake motor is known from DE 13 03 888 A.

[0005] The invention is therefore based on the objective of further developing a braking arrangement, whereby the highest possible dynamics should be achievable.

[0006] According to the invention, the problem is solved in the brake arrangement according to the features specified in claim 1.

[0007] Important features of the invention in the brake arrangement are that the brake arrangement can be provided with a brake pad carrier, with a driver, with a stop ring and with a spring, wherein the driver is non-rotatably connected to a shaft, in particular by means of a keyway connection, wherein the brake pad carrier is connected to the driver in a rotationally fixed but axially displaceable manner, in particular wherein the axial direction is aligned parallel to the axis of the shaft, wherein the spring is arranged axially between the stop ring and the brake pad carrier, the spring is supported on the stop ring.

[0008] An advantage of this design is that the spring force generated by the spring can be used to overcome the static friction between the brake pad carrier and the stop ring, thus enabling higher dynamics of the brake assembly. While the spring can be designed as any spring element, it is preferably designed as a metallic spring element which, according to the invention, operates in the elastic range, thus preventing deflections of the spring element that would lead to inelastic deformation.

[0009] In an advantageous embodiment, the spring is arranged in an annular groove. The advantage here is that the working range of the spring can be defined by the width of the annular groove.

[0010] In an advantageous embodiment, the brake pad carrier has an internal toothing which is mounted on an external toothing of the drive lug, In particular, the internal and external teeth are straight-cut, meaning they have a negligible helix angle. An advantage of this design is that the brake pad carrier is axially displaceable relative to the drive pin.

[0011] In an advantageous embodiment, the radial spacing area covered by the stop ring overlaps with the radial spacing area covered by the brake pad carrier, particularly wherein the radial spacing area covered by the stop ring overlaps and / or encompasses the radial spacing area covered by the spring. It is advantageous that the stop ring extends radially further outwards than the brake pad carrier extends radially inwards. This overlap allows the stop ring to function as an axial stop.

[0012] In an advantageous embodiment, an anchor disc is arranged on the side of the brake pad carrier facing away from the spring. wherein a coil core is arranged on the side of the armature disc facing away from the brake pad carrier, wherein the armature disk is arranged in a rotationally fixed but axially displaceable manner relative to the coil core, In particular, wherein the coil core has a coil winding, and especially wherein the coil winding is received in an annular groove of the coil core, the axis of which corresponds to the axis of the shaft. It is advantageous that the brake arrangement is electromagnetically actuated.

[0013] In an advantageous embodiment, a spring element supported on the coil core presses on the armature disk, in particular so that when the coil winding is energized, the armature disk is pressed by the spring element towards the brake pad carrier and thus this brake pad carrier is pressed against a counter-braking surface arranged on a part, In particular, the part is firmly connected to the stop ring, especially being manufactured in one piece and integrated with it. An advantage of this is that in the event of a power failure, the brake engages and can only be released by energizing the coil winding.

[0014] In a preferred embodiment, the spring is a disc spring. The advantages here are that it allows for simple assembly and the working range of the disc spring can be defined by arranging the disc spring in an annular groove.

[0015] In an advantageous embodiment, the spring is slotted, in particular so that during manufacturing it is pushed onto the annular groove from a radial direction and / or snapped into place. The advantage here is that simple assembly is possible.

[0016] In an advantageous embodiment, the annular groove limits the working range of the spring. The advantage here is that the axial width of the annular groove allows the working range, and thus the part of the spring characteristic curve relevant for the operation of the brake assembly, to be predetermined.

[0017] In an advantageous embodiment, the spring constant of the spring is at least five times smaller than the spring constant of the spring element. It is advantageous that the spring, in order to overcome static friction, works in conjunction with the magnetic force generated by the coil winding, with both forces acting in the opposite direction to the force generated by the spring element.

[0018] In an advantageous embodiment, the annular groove is axially limited by the external teeth of the drive pin and at its other axial end by the stop ring. An advantage of this design is that the spring provided in the annular groove can be positioned directly between the stop ring and the drive pin, thus limiting its working range. Therefore, when the brake pad carrier penetrates the axial area covered by the annular groove, the spring generates a counterforce that pushes the brake pad carrier out of the annular groove.

[0019] Key features of the electric motor are that it is equipped with a brake arrangement, with the shaft being the rotor shaft of the electric motor.

[0020] An advantage of this is that the motor, together with the brake assembly, can be designed as a brake motor, and thus the rotor shaft can be braked by the brake assembly.

[0021] In an advantageous embodiment, the part with the counter-braking surface is a bearing shield or housing part of the motor. The advantage here is that a separate brake disc is unnecessary if a surface on the bearing shield or housing part is machined accordingly.

[0022] Further advantages arise from the dependent claims. The invention is not limited to the combination of features of the claims. For those skilled in the art, further meaningful combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent, in particular from the problem statement and / or the problem arising from a comparison with the prior art.

[0023] The invention will now be explained in more detail with the help of illustrations: In the Fig. Figure 1 shows a brake arrangement according to the invention in section and in oblique view. In the Fig. Figure 2 shows this brake arrangement in a sectional view. In the Fig. Figure 3 shows a partial section of this brake arrangement in side view.

[0024] As shown in the figures, the brake arrangement has a driver 7 which is non-rotatably connected to a shaft (10), in particular by means of a keyway connection.

[0025] The drive pin 7 is ring-shaped and mounted on the shaft (10). It has external teeth onto which a brake pad carrier with its internal teeth is mounted. The teeth extend in the axial direction, i.e., parallel to the axis of the shaft (10). Thus, the brake pad carrier 2 is rotationally fixed but axially displaceable with the drive pin 7 and surrounds it radially.

[0026] A coil core 5 is arranged axially spaced from the brake pad carrier 2, and has an annular groove on its side facing the brake pad carrier 2, into which a coil winding 4 is received and / or inserted.

[0027] An armature disk 6 is arranged axially between the brake pad carrier 2 and the coil core 5. It is rotationally fixed to the coil core 5 but axially displaceable. This is achieved by guide elements, such as bolts or the like, which are detachably connected to the coil core 5, in particular by screws. The armature disk 6 has recesses through which the guide elements protrude, thus axially guiding the armature disk 6 and preventing rotational movement of the armature disk 6.

[0028] The armature disc is made of metal, preferably a ferromagnetic material.

[0029] When current is applied to the coil winding 4, the armature disk 6 is pulled towards the coil core 5 against the spring force generated by the spring elements 3. The spring elements 3 press against the armature disk 6 with their respective first ends and are supported against the coil core 5 with their respective other ends.

[0030] When the coil winding 4 is not energized, the spring elements 3 press the armature disc 6 onto the brake pad carrier 2, which is thus pressed onto the counter-braking surface on part 1.

[0031] Part 1 is designed as a brake disc.

[0032] On the side of the brake pad carrier 2 facing away from the anchor disk 6, the brake pad carrier 2 is axially limited by a stop ring 9, which extends radially further than the driver 7. For this purpose, the radial clearance area covered by the brake pad carrier 2 and the radial clearance area covered by the stop ring 9 overlap. The stop ring 9 is firmly connected, preferably by frictional connection, to the driver 7.

[0033] A spring 8, preferably a disc spring, is arranged axially between the stop ring 9 and the brake pad carrier 2. For this purpose, an annular groove is provided between the toothing 30 of the driver 7 and the stop disc 9, with the spring 8 being received in the annular groove.

[0034] The annular groove thus limits the axial working range of the spring 8. Although the annular groove projects radially beyond the toothing 30 of the driver 7, it only presses on the brake pad carrier 2 when its axial position reaches or exceeds the axial end position of the toothing 30 of the driver.

[0035] The working range of the spring 8 therefore corresponds to the axial width of the annular groove. The spring 8 is supported on the stop ring 9.

[0036] The spring 8 thus pushes the brake pad carrier 2 away from the opposing braking surface.

[0037] However, the spring force generated by springs 3 is much stronger. When coil winding 4 is energized, spring 8 assists in overcoming the static friction force. This prevents the brake pad carrier 2 from adhering to the opposing braking surface of part 1 for too long. When coil winding 4 is energized, the spring force generated by spring 8 is added to the magnetic force, so that static friction is overcome even at low currents. The brake can therefore be operated with very high dynamics.

[0038] The spring 8 is preferably designed as a disc spring and thus extends in the circumferential direction essentially over the entire annular groove.

[0039] The disc spring is preferably slotted so that it can be placed onto the ring groove from a radial direction during manufacturing.

[0040] The external toothing 30 of the drive pin 7 is straight-cut, i.e., without helical teeth. The internal toothing of the brake pad carrier 2 is also straight-cut.

[0041] In another embodiment according to the invention, part 1 is designed as a bearing shield of an electric motor and thus accommodates a bearing for the shaft (10), in particular rotor shaft (10), of the electric motor.

[0042] In a further embodiment of the invention, the stop ring 9 and the driver 7 are formed in one piece. The annular groove, which receives the spring 8, is then provided at the axial end region of the toothing of the driver 7. Reference symbol list 1 part with counter-braking surface 2 brake pad carriers 3 Spring element 4 coil windings 5 coil core 6 Anchor disc 7 drivers 8 Spring, in particular disc spring 9 Stop ring 10 wave 30 External teeth

Claims

[1] Brake assembly comprising a brake pad carrier (2), a driver (7), a stop ring (9) and a spring, wherein the driver (7) is non-rotatably connected to a shaft (10), in particular by means of a keyway connection, wherein the brake pad carrier (2) is connected to the driver (7) in a rotationally fixed but axially displaceable manner, in particular wherein the axial direction is aligned parallel to the axis of the shaft (10), wherein the spring is arranged axially between the stop ring (9) and the brake pad carrier (2), the spring is supported on the stop ring (9), wherein the spring is arranged in an annular groove of the stop ring (9) such that the spring force generated by the spring is directed to push the brake pad carrier (2) away from the counter braking surface in order to overcome a static friction force acting on the brake pad carrier (2), wherein the working range of the spring (8) corresponds to the axial width of the annular groove. [2] Brake arrangement according to claim 1, characterized by , that the brake pad carrier (2) has an internal toothing which is fitted onto an external toothing (30) of the driver (7), in particular wherein the internal teeth and the external teeth (30) are straight-cut, i.e. have a vanishing helix angle. [3] Brake arrangement according to at least one of the preceding claims, characterized by , that the radial clearance area covered by the stop ring (9) overlaps with the radial clearance area covered by the brake pad carrier (2), in particular wherein the radial clearance area covered by the stop ring (9) covers and / or includes the radial clearance area covered by the spring. [4] Brake arrangement according to at least one of the preceding claims, characterized by , that an anchor disc (6) is arranged on the side of the brake pad carrier (2) facing away from the spring, wherein a coil core (5) is arranged on the side of the armature disk (6) facing away from the brake pad carrier (2), wherein the armature disk (6) is arranged in a rotationally fixed but axially displaceable manner relative to the coil core (5), in particular wherein the coil core (5) has a coil winding (4), in particular wherein the coil winding (4) is received in an annular groove of the coil core (5), the annular axis of which corresponds to the axis of the shaft (10). [5] Brake arrangement according to at least one of the preceding claims, characterized by , that a spring element (3) supported on the coil core (5) presses on the armature disk (6), in particular so that when the coil winding (4) is energized the armature disk (6) is pressed by the spring element (3) towards the brake pad carrier (2) and thus this brake pad carrier (2) is pressed onto a counter braking surface arranged on a part, in particular wherein the part is firmly connected to the stop ring (9), in particular is made in one piece and is manufactured in one piece with it. [6] Brake arrangement according to at least one of the preceding claims, characterized by that the spring is a disc spring. [7] Brake arrangement according to at least one of the preceding claims, characterized by that the spring is slotted, in particular so that during manufacturing it is pushed onto the annular groove from a radial direction and / or snapped on. [8] Brake arrangement according to at least one of the preceding claims, characterized by that the ring groove limits the working range of the spring. [9] Brake arrangement according to at least one of the preceding claims, characterized by , that the spring constant of the spring is at least five times smaller than the spring constant of the spring element (3). [10] Brake arrangement according to at least one of the preceding claims, characterized by , that the axial area covered by the annular groove borders the axial area covered by the external toothing (30) of the driver (7) and at its other axial end the annular groove is axially limited by the stop ring (9). [11] Electric motor with brake arrangement according to at least one of the preceding claims, characterized by , that the shaft (10) is the rotor shaft of the electric motor, where the part with the counter-braking surface is a bearing shield or housing part of the motor.

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