Brake arrangement

Abstract

Brake arrangement wherein the brake arrangement has an output shaft (9) on which a brake pad carrier (7) is fixedly connected and axially movable, wherein a disc (3) having a braking surface is rigidly connected to a housing part (25, 27) of the brake, wherein at least one ball (5) is arranged between a driving shaft (1) and the pad carrier (7), which is movable in the circumferential direction in a circumferential angle section provided relative to the pad carrier (7) against a spring force generated by spring elements (20), wherein, depending on the respective circumferential angle position of the ball (5), the ball (5) pushes the pad carrier (7) to a respective corresponding axial position, the spring force depends on the respective circumferential angle, wherein the distance between the pad carrier (7) and the disc (3) having the braking surface depends in the axial direction on the respective circumferential angle position, i.e. is not constant, wherein a further brake pad carrier (2) is arranged to be axially movable on the driving shaft (1) and / or on the side of the disc (3) facing away from the first pad carrier (7), wherein the first lining carrier (7) and the further lining carrier (2) are pressed towards each other by the spring elements (20), wherein the disc (3) has a further braking surface against which the further brake pad carrier (2) can be pressed, at the corresponding circumferential angle position of the ball (5), wherein the driven shaft (9) and the driving shaft (1) are each supported by means of at least one bearing (12, 24) on the housing part (25, 27) or a housing part (25, 27) rigidly connected to it, wherein the first and second pad carriers (2, 7) are connected by means of axially extending bolts via discs (6, 10) connected to the pad carriers (2, 7) and spring elements (20) pressing on the pad carrier (7) are supported on the bolts or on nuts connected to the bolts in such a way that the balls (5) are held in the local extremum as long as no torque is transmitted from the driving shaft (1) through the balls (5) towards the first brake pad carrier (7), wherein in the circumferential direction the balls (5) are held at regular intervals from each other by means of a ball guide part (4), wherein the ball guide part (4) is connected to the driving shaft (1) in a rotationally fixed manner, wherein the first lining carrier (2) sits on an externally cylindrically shaped shaft section of the ball guide part (4) and a sliding bearing (11) of a first of the disks (10) is arranged on this shaft section, which is connected to the first lining carrier (2) in a rotationally fixed and axially fixed manner, wherein the first pad carrier (2) is guided in the axial direction by means of the first disk (10), wherein the second pad carrier (7) is connected to the second disk (6), wherein the second disk (6) is touched by the balls (5) and is non-rotatably connected to the driving shaft (9), wherein the contact surface of the second disk (6) has a circumferentially extending chamfer associated with a respective sphere (5), which is axially increased with increasing circumferential direction.

Description

[0001] The invention relates to a brake arrangement.

[0002] It is generally known that in electromagnetically actuated brakes, a magnetic field is generated by energizing a coil winding, i.e., the brake coil. This magnetic field attracts an armature disk in the axial direction against the spring force generated by spring elements, thus releasing the brake. When de-energized, the spring elements press the armature disk against a brake pad carrier, which is mounted to a brake shaft so that it is rotationally fixed but axially displaceable. This causes the brake pad carrier to contact both a braking surface and the armature disk on both sides, generating braking force.

[0003] From EP 0 330 133 A2, a device for transmitting torque for elevator systems is known as the closest prior art.

[0004] The invention is therefore based on the objective of further developing a braking arrangement in such a way that a holding brake property should be achievable.

[0005] According to the invention, the problem is solved in the brake arrangement according to the features specified in claim 1 or 2.

[0006] Important features of the invention in the brake arrangement according to claim 1 are that the brake arrangement has a driven shaft on which a brake pad carrier is non-rotatably connected and axially movable, in particular in the direction of the shaft axis, wherein a disc having a braking surface, in particular an anchor disc, is connected to a housing part of the brake, in particular firmly connected, wherein at least one ball is arranged between a driving shaft and the pad carrier, which is movable in the circumferential direction in a circumferential angle section provided relative to the pad carrier, in particular against a spring force generated by spring elements, wherein, depending on the respective circumferential angle position of the ball, the ball pushes the pad carrier (7) to a respective corresponding axial position, in particular where the spring force depends on the respective circumferential angle, in particular where the distance between the pad carrier and the disc having the braking surface in the axial direction depends on the respective circumferential angle position, and is in particular not constant,

[0007] An advantage of this design is that the braking arrangement can be implemented as a brake or integrated into another device, such as an electric motor, gearbox, or clutch. When an electric motor is used with a brake, this braking arrangement is referred to as a brake motor.

[0008] An advantage of the invention is that the brake assembly has a driving shaft to which torque can be applied by an electric motor. The torque is thus transmitted from the driving shaft via the balls to the first brake pad carrier and from there via a drive gear to a driven shaft, on which a load is applied. When the motor is switched off, i.e., when the torque applied by the motor falls below the amount of torque applied to the load, the brake engages. In this case, the brake pad carrier with its brake pad is pressed against a braking surface of a disc, in particular an armature disc. The disc is rigidly connected to the housing of the brake assembly, with the driving and driven shafts each being supported by bearings in this housing.The housing is made up of several parts, with the disc at least partially taking on a housing-forming function, as it can be arranged between two housing parts and thus contributes to the formation of the outer surface of the brake assembly.

[0009] A further advantage of the invention is that the driving shaft transmits torque via the balls or similarly acting release elements. If the torque introduced by the motor significantly exceeds the torque applied on the load side, the release elements, in particular the balls, are disengaged from their rest position in the circumferential direction against a restoring spring force. The rest position represents a local extremum for both the magnitude of the spring force and the functional dependence of the axial position of the first brake pad carrier on the circumferential angle. The circumferential angle is understood here to be the circumferential angle measured relative to the first brake pad carrier. This is because the first brake pad carrier and the release elements are set into rotational motion by the driving shaft, and the release elements can only move within a limited circumferential angle range relative to the first brake pad carrier.During this movement, which occurs against the spring force from the rest position, the axial position of the first brake pad carrier is affected. In particular, the distance between the first brake pad carrier and the disc is changed.

[0010] In this way, automatic release of the brake when the motor is running and automatic engagement of the brake when the motor is not powered are achieved. This holding brake function operates without electromagnetic or other control. The holding brake function is therefore purely mechanical and thus offers increased safety.

[0011] Important features of the invention in the brake arrangement according to claim 2 are that the brake arrangement has a driven shaft on which a brake pad carrier is fixedly connected and axially movable, in particular in the direction of the shaft axis, wherein a disc having a braking surface, in particular an anchor disc, is connected to a housing part of the brake, in particular firmly connected, wherein at least one ball is arranged between a driving shaft and the lining carrier, which is arranged in a groove section of the lining carrier extending in the circumferential direction and having a groove depth that varies in the circumferential direction, that a brake pad of the pad carrier is pressed onto a braking surface of the disc when the ball is located in a first area of ​​the groove section, in particular against a spring force generated by spring elements, and in particular that the brake pad of the pad carrier is axially removed from the braking surface of the disc when the ball is located in another area of ​​the groove section, in particular against a spring force generated by spring elements.

[0012] The advantages correspond to those mentioned above for the embodiment according to claim 1. In addition, it is advantageous that the simple formation of a corresponding groove contour allows the function of the holding brake to be implemented in a straightforward manner. This is because the groove contour can be incorporated as a post-processing step on the end face of the first lining carrier and can therefore be executed without any special effort.

[0013] In an advantageous embodiment, the torque transmitted from the driving shaft to the driven shaft is at least partially transmitted via the at least one ball. An advantage of this is that the ball can be used as a release element, and the torque transmission through the release element can be used to control the braking function. Using balls as the release element results in particularly low friction, thus enabling a particularly low critical minimum torque from the driving motor required to release the brake.

[0014] In an advantageous embodiment, the axial position corresponding to the circumferential angle position, as a function of the circumferential angle position, has a local extremum, in particular a single maximum or minimum, in the circumferential angle section. in particular where the magnitude of the spring force also has a local extremum, in particular a single maximum or minimum, as a function of the circumferential angle position in the circumferential angle section, This applies particularly to the same circumferential angle as the local extremum of the axial position's function curve. An advantage of this is that the same function can be implemented for both directions of rotation. Specifically, if the function curve, and in particular the groove depth curve in the circumferential direction, is symmetrical about a mean circumferential angle position, the behavior is identical in both directions. Thus, the brake release is achieved in both directions of rotation with the same torque.

[0015] In an advantageous embodiment, the driven shaft and the driving shaft are each supported by at least one bearing on the housing part or on a housing part rigidly connected to it. It is advantageous that the brake assembly has a housing, so that the release elements are protected and therefore no interfering dirt particles can impede their disengagement. Furthermore, the disc with the braking surface can be fixed to the housing, thus allowing the braking torque to be transferred from the pad carrier to the disc or to the housing.

[0016] In an advantageous embodiment, a further brake pad carrier is arranged to be axially movable on the driving shaft and / or on the side of the disc facing away from the first pad carrier. in particular, wherein the minimum axial distance between the first pad support and the next pad support is specified by means of the ball. In particular, the disc has an additional braking surface against which the additional brake pad carrier can be pressed, depending on the corresponding circumferential angle position of the ball. An advantage of this is that, depending on the torque introduced via the drive shaft, the ball is deflected against the spring force by a circumferential angle relative to the brake pad carrier, and the distance between the brake pad carrier and the disc is determined by this deflection.

[0017] According to the invention, the balls are held at essentially regular intervals from one another in the circumferential direction by means of a ball guide part. The ball guide element is rotationally fixed to the driving shaft. An advantage of this design is that it allows for simple assembly and secure retention of each ball in the groove of the first pad carrier.

[0018] In an advantageous embodiment, the driven shaft has a drive tooth that engages with an internal toothing of the first brake pad carrier. It is advantageous that the first brake pad carrier is arranged to be axially displaceable and yet is rotationally fixed to the driven shaft. In this way, the torque introduced by the driving shaft via the release elements to the first brake pad carrier is transferred to the driven shaft.

[0019] In an advantageous embodiment, the first and / or subsequent brake pad carriers are connected to, or integrally formed with, the respective first and second discs. This offers the advantage of increased mechanical strength and allows certain components, such as brake pad carriers, to be used in other brake configurations. Thus, a high variety of brakes can be manufactured using a modular system with a small number of parts.

[0020] According to the invention, the first and second brake pad carriers are connected by axially extending bolts via discs connected to the respective pad carriers. Spring elements pressing against the pad carriers are supported on the bolts or on nuts connected to the bolts in such a way that the balls are held in their local extremum as long as no significant torque is transmitted from the driving shaft through the balls to the first brake pad carrier. It is advantageous that the bolts protrude through one of the pad carriers, so that the spring elements are supported between the side of the pad carrier facing away from the other pad carrier and the bolt. Thus, the spring elements effectively press the pad carriers towards each other and therefore against the anchor disc on both sides.

[0021] In an advantageous embodiment, the groove section, and in particular the groove depth, extends circumferentially in a substantially U- or V-shape. It is advantageous that a simple and / or symmetrical shape is sufficient.

[0022] In a preferred embodiment, a different release element is used instead of the ball. The advantage here is that, instead of point contact between the ball and a contact surface, line contact or even area contact between the release element and the contact surface can be achieved.

[0023] Further advantages arise from the sub-claims.

[0024] The invention will now be explained in more detail with the help of illustrations: In the Fig. Figure 1 shows an embodiment of the invention in exploded view, with the counter-braking surfaces not shown. In Fig. Figure 2 shows a corresponding sectional view. In the Fig. Figure 3 shows an external view of the brake assembly.

[0025] As shown in the figures, the brake arrangement has a driving shaft 1 with which a lining carrier 2 is arranged to be rotationally fixed but axially displaceable, i.e. in the direction of the shaft axis.

[0026] As in Fig. As shown in Figure 1, the lining carrier 2 sits on an externally cylindrical shaft section of the ball guide part 4. A sliding bearing 11 of the disk 10 is also arranged on this shaft section and is rigidly connected to the lining carrier 2, in particular rotationally fixed and axially fixed. Thus, the lining carrier 2 is guided in the axial direction.

[0027] When the brake is applied, the brake pad carrier 2 is pressed against the side of an anchor disc 3 facing it. This causes the brake pad carrier 2 to be axially displaced. The anchor disc 3, however, is connected to the housing and is therefore fixed and immovable to it. The anchor disc 3 can be made of perforated steel. The anchor disc 3 therefore does not rotate with the driving shaft 1.

[0028] Likewise, a further lining carrier 7 is connected to a driving shaft 9, which is supported in the housing via a bearing 12, in a rotationally fixed but axially displaceable manner. For this purpose, this lining carrier 7 has a drive toothing which engages with an external toothing formed on the shaft 9.

[0029] This additional lining carrier 7 is also pressed against the anchor disc 3 when the brake is applied, with the associated braking surface being arranged on the axial side of the anchor disc facing away from the lining carrier 2.

[0030] The driving shaft 1 has a square-shaped end area facing the driving shaft 9, so that a ball guide part 4 with an internal square can be attached and axially moved under correspondingly high forces when acted upon.

[0031] Balls 5 are arranged on the ball guide part 4, each located in a recess of the ball guide part 4. The ball guide part 4 thus spaces the balls 5 apart from each other in the circumferential direction. The disk 6 is contacted by the balls 5 and is rotationally fixed to the driven shaft 9.

[0032] Since the contact surface of the disk 6 has a circumferentially extending chamfer associated with each ball 5, which increases axially with increasing circumferential direction, the balls 5 move outwards in the axial direction when torque is applied from the motor, thus pushing the two disks 4, 6, and 10 apart in the axial direction. Therefore, if the torque applied by the motor to the driving shaft 1 is higher than the load torque applied to the driven shaft 9, the brake is released. If the torque applied by the motor to the driving shaft 1 is less than the load torque, the brake engages. In particular, the brake engages when the motor is switched off.

[0033] Therefore, the brake can be used as a holding brake.

[0034] The balls 5 are disengaged against the action of spring elements 20.

[0035] The disengagement movement is limited by axial stops, in particular corresponding shaft flanges, on the driving shaft 1 and the driving shaft 9, wherein the lining carrier 7 abuts a corresponding shaft flange of the driving shaft 9 and the lining carrier 2 abuts a corresponding shaft flange of the driving shaft 1.

[0036] The driving shaft 1 is supported in the housing part 25 via bearing 24, the anchor disk 3 being fixed between the housing part 25 and the housing part 27 by means of a connecting screw 26 passing through the anchor disks 3, which screws the two housing parts (25, 27) together.

[0037] A bolt 21 is screwed to the disc 10 by means of the screw 28 and thus also connected to the pad carrier 2. The axially extending bolt projects through recesses in the pad carrier 7 and also in the disc 6. At its axial end, the bolt has an external threaded section onto which a nut is screwed. A spring element 20 is supported against this nut, which is also supported against the pad carrier 7 and / or the disc 6.

[0038] Thus, the brake lining carriers 2 and 7 are pressed towards each other by the spring elements 20. If the balls 5 do not disengage, the brake lining carriers 2 and 7 are pressed against the anchor disc 3 from axially opposite directions, and the brake is therefore in the engaged state and generates braking force.

[0039] Only when the torque generated by the motor is greater than the torque applied to the load, i.e., when the torque from the motor is transmitted to the load via the drive teeth 8, does the brake release, by pushing the pads 2 and 7 apart against the spring force of the spring elements 20 by the balls 5 disengaging from their axially arranged lowest point.

[0040] As a result of the aforementioned axial limitation of the lining carriers 2 and 7, in particular the aforementioned stops or wave collars, the axial stroke of the balls 5 is limited.

[0041] The spheres 5 contact the disks 6 and 10. To facilitate disengagement from the lowest point, the disks 6 and 10 each have the aforementioned chamfer. For this purpose, a groove section is provided on the side of each disk 6 and 10 facing the sphere, extending circumferentially over a finite angular range, in particular between 5° and 25°. Thus, several spaced-apart groove sections can be arranged at the same radial distance circumferentially, and consequently, several spheres 5 can also be accommodated.

[0042] The groove bottom of the groove section is not machined to a constant depth, but rather exhibits a depth gradient that increases circumferentially. Thus, the ball moves axially as it traverses the groove section. Since the distance between disks 6 and 10 is determined by the position of ball 5, this distance is changed by ball 5 as it traverses the groove section. The axial distance between disks 6 and 10 increases as ball 5 moves out of the lowest point in the axial direction.

[0043] Preferably, the drive teeth of the pad carriers (2, 7) are each designed as involute teeth.

[0044] In a further embodiment according to the invention, the lining carriers 2 and 7 are formed in one piece with the disks 10 and 6 respectively associated with them.

[0045] In another embodiment according to the invention, the ball guide part 4 and the driving shaft 1 are formed in one piece.

[0046] In an alternative embodiment, the ball guide part 4 is pressed onto the square-shaped end area of ​​the driving shaft 1.

[0047] In another alternative embodiment, the ball guide part 4 is connected to the end region of the driving shaft 1 facing the driving shaft 9 in a rotationally fixed manner without a square, in particular by friction locking, form locking and / or material locking.

[0048] In a further embodiment of the invention, there is not two, but only a single pad carrier 7. The pad carrier 2 is therefore not present, but only the disc 10, which is then fixedly connected to the driving shaft 1, i.e., essentially not axially displaceable. Alternatively, instead of the disc 10, a shaft collar can be formed on the driving shaft 1, on which the spring elements are supported directly or indirectly via bolts. These spring elements press against the single pad carrier 7, which in turn is connected to the driven shaft in a rotationally fixed but axially movable manner. The disc 3, which has the braking surface, is again fixedly connected to the housing, in which the driving (i.e., motor-side) and driven (i.e., load-side) shafts are supported by respective bearings, in particular ball bearings. Reference symbol list 1 driving shaft 2 decking carriers 3 Anchor disc 4 ball guide part 5 balls 6 Disc, in particular connectable to the pad carrier 7 7 decking carriers 8 Drive teeth 9 outgoing wave 10 Disc, in particular connectable to the pad carrier 2 11 plain bearings 12 bearings for driven shaft 9 20 spring elements 21 bolts 22 Mother 23 plate 24 bearings of the driving shaft 1 25 Housing part 26 Connecting screw 27 Housing part

Claims

[1] Brake arrangement, wherein the brake arrangement has an output shaft (9) on which a brake pad carrier (7) is fixedly connected and axially movable, wherein a disc (3) having a braking surface is rigidly connected to a housing part (25, 27) of the brake, wherein at least one ball (5) is arranged between a driving shaft (1) and the pad carrier (7), which is movable in the circumferential direction in a circumferential angle section provided relative to the pad carrier (7) against a spring force generated by spring elements (20), wherein, depending on the respective circumferential angle position of the ball (5), the ball (5) pushes the pad carrier (7) to a respective corresponding axial position, the spring force depends on the respective circumferential angle, wherein the distance between the pad carrier (7) and the disc (3) having the braking surface depends in the axial direction on the respective circumferential angle position, i.e. is not constant, wherein a further brake pad carrier (2) is arranged to be axially movable on the driving shaft (1) and / or on the side of the disc (3) facing away from the first pad carrier (7), wherein the first lining carrier (7) and the further lining carrier (2) are pressed towards each other by the spring elements (20), wherein the disc (3) has a further braking surface against which the further brake pad carrier (2) can be pressed, at the corresponding circumferential angle position of the ball (5), wherein the driven shaft (9) and the driving shaft (1) are each supported by means of at least one bearing (12, 24) on the housing part (25, 27) or a housing part (25, 27) rigidly connected to it, wherein the first and second pad carriers (2, 7) are connected by means of axially extending bolts via discs (6, 10) connected to the pad carriers (2, 7) and spring elements (20) pressing on the pad carrier (7) are supported on the bolts or on nuts connected to the bolts in such a way that the balls (5) are held in the local extremum as long as no torque is transmitted from the driving shaft (1) through the balls (5) towards the first brake pad carrier (7), wherein in the circumferential direction the balls (5) are held at regular intervals from each other by means of a ball guide part (4), wherein the ball guide part (4) is connected to the driving shaft (1) in a rotationally fixed manner, wherein the first lining carrier (2) sits on an externally cylindrically shaped shaft section of the ball guide part (4) and a sliding bearing (11) of a first of the disks (10) is arranged on this shaft section, which is connected to the first lining carrier (2) in a rotationally fixed manner and in the axial direction, wherein the first pad carrier (2) is guided in the axial direction by means of the first disk (10), wherein the second pad carrier (7) is connected to the second disk (6), wherein the second disk (6) is touched by the balls (5) and is non-rotatably connected to the driving shaft (9), wherein the contact surface of the second disk (6) has a circumferentially extending chamfer associated with a respective sphere (5), which is axially increased with increasing circumferential direction. [2] Brake arrangement, wherein the brake arrangement has an output shaft (9) on which a brake pad carrier (7) is fixedly connected and axially movable, wherein a disc (3) having a braking surface is rigidly connected to a housing part (25, 27) of the brake, wherein at least one ball (5) is arranged between a driving shaft (1) and the lining carrier (7), which is arranged in a groove section of the lining carrier (7) extending in the circumferential direction and having a groove depth that varies in the circumferential direction, wherein a brake pad of the pad carrier is pressed onto a braking surface of the disc (3) when the ball (5) is located in a first area of ​​the groove section against a spring force generated by spring elements (20), wherein the brake pad of the pad carrier is axially removed from the braking surface of the disc (3) when the ball (5) is located in a different area of ​​the groove section against the spring force generated by the spring elements (20), wherein a further brake pad carrier (2) is arranged to be axially movable on the driving shaft (1) and / or on the side of the disc (3) facing away from the first pad carrier (7), wherein the first lining carrier (7) and the further lining carrier (2) are pressed towards each other by the spring elements (20), wherein the disc (3) has a further braking surface against which the further brake pad carrier (2) can be pressed, at the corresponding circumferential angle position of the ball (5), wherein the driven shaft (9) and the driving shaft (1) are each supported by means of at least one bearing (12, 24) on the housing part (25, 27) or a housing part (25, 27) rigidly connected to it, wherein the first and second pad carriers (2, 7) are connected by means of axially extending bolts via discs (6, 10) connected to the pad carriers (2, 7) and spring elements (20) pressing on the pad carrier (7) are supported on the bolts or on nuts connected to the bolts in such a way that the balls (5) are held in the local extremum as long as no torque is transmitted from the driving shaft (1) through the balls (5) towards the first brake pad carrier (7), wherein in the circumferential direction the balls (5) are held at regular intervals from each other by means of a ball guide part (4), wherein the ball guide part (4) is connected to the driving shaft (1) in a rotationally fixed manner, wherein the first lining carrier (2) sits on an externally cylindrically shaped shaft section of the ball guide part (4) and a sliding bearing (11) of a first of the disks (10) is arranged on this shaft section, which is connected to the first lining carrier (2) in a rotationally fixed manner and in the axial direction, wherein the first pad carrier (2) is guided in the axial direction by means of the first disk (10), wherein the second pad carrier (7) is connected to the second disk (6), wherein the second disk (6) is touched by the balls (5) and is non-rotatably connected to the driving shaft (9), wherein the contact surface of the second disk (6) has a circumferentially extending chamfer associated with a respective sphere (5), which is axially increased with increasing circumferential direction. [3] Brake arrangement according to claim 1 or 2, characterized by, that the torque transmitted from the driving shaft (1) to the driven shaft (9) is transmitted at least partially via the at least one sphere (5). [4] Brake arrangement according to at least one of the preceding claims, characterized by , that the axial position corresponding to the circumferential angle position, as a function of the circumferential angle position in the circumferential angle section, exhibits a local extremum, in particular a single maximum or minimum, in particular where the magnitude of the spring force also has a local extremum, in particular a single maximum or minimum, as a function of the circumferential angle position in the circumferential angle section, especially at the same circumferential angle as the local extremum of the functional curve of the axial position. [5] Brake arrangement according to at least one of the preceding claims, characterized by, that the minimum axial distance between the first lining support (7) and the further lining support (2) is specified by means of the ball (5). [6] Brake arrangement according to at least one of the preceding claims, characterized by , that the driving shaft (9) has a drive toothing which engages with an internal toothing of the first pad carrier (7). [7] Brake arrangement according to at least one of the preceding claims, characterized by , that the first and / or the further lining carrier (2, 7) are connected to a respective first or second disc or are integrally formed with it. [8] Brake arrangement according to at least one of the preceding claims, characterized by that the groove section, in particular the groove depth, runs in a U- or V-shape in the circumferential direction. [9] Brake arrangement according to at least one of the preceding claims, characterized by, that instead of the ball (5) a different release element is used.

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