Brake device having shaft and brake pad carrier

Abstract

The invention relates to a brake device having a shaft and a brake pad carrier, an annular driver being connected to the shaft in a rotationally fixed manner, the brake pad carrier having an internal toothing which engages with an external toothing of the driver, an elastic element being elastically clamped in an annular groove, an elastic force generated by an elastic part supported on the driver has a first force component which presses against the brake pad carrier in the radial direction and a second force component of the elastic force which acts on the brake pad carrier and is directed in the axial direction.

Description

Technical Field

[0001] The invention relates to a brake device having a shaft and a brake pad carrier. Background Art

[0002] As is known, shafts can be braked by means of friction brakes.

[0003] As the latest prior art, a brake device having a shaft-hub connection is known from DE 10 2022 001 345 A1.

[0004] A joining device having a spring element is known from DE 10 2011 121 790 A1.

[0005] A centering device for a gear train is known from DE 78 25 113 U1.

[0006] A shaft-hub connection with a vibration protection device is known from US Pat. No. 2,800,800 A. Summary of the invention

[0007] It is therefore an object of the present invention to improve a brake in which an operation which is as dynamic and / or as safe as possible should be possible.

[0008] According to the invention, this object is achieved by the features specified in claim 1 .

[0009] In a brake device with a shaft and a brake pad carrier, an essential feature of the invention is that the annular carrier is connected to the shaft in a rotationally fixed manner, in particular in a form-fitting manner, in particular by means of a key connection.

[0010] In particular, the brake pad carrier is mounted on the driver.

[0011] The brake pad carrier has an internal toothing which meshes with an external toothing of the driver, in particular such that the brake pad carrier is arranged to be movable relative to the driver in an axial direction, i.e. in particular parallel to the axis of rotation of the shaft,

[0012] The elastic element is received and / or elastically clamped in an annular groove, in particular an annular inner groove.

[0013] The elastic force generated by the elastic component supported on the driving member includes a first force component and a second force component of the elastic force, the first force component presses on the brake pad carrier in the radial direction, and the second force component acts on the brake pad carrier in the axial direction.

[0014] The advantage here is that the elastic element provides an axial restoring force which pulls the brake pad carrier back from the friction surface without the action of other forces. In particular, when the winding of the electromagnetically actuable brake, which has a brake pad carrier, is energized, the armature disk is pulled toward the magnet, in particular against the spring force generated by the spring element supported on the magnet and pressing against the armature disk. The brake pad carrier then does not have to be released automatically / autonomously, but is actively pulled back, i.e. away from the friction surface - both when the shaft is rotating and when the shaft is stationary - by the axial force component provided in the axial direction by the elastic element and introduced into the brake pad carrier.

[0015] According to the present invention, the restoring force is generated by the elastic bending of the elastic component. Preferably, the elastic component has an axial bend and can be elastically deflected in the axial direction, or the elastic component is clamped in the annular groove and is driven by the brake pad carrier in the axial direction and thus elastically deflected.

[0016] The restoring force thus improves, in particular accelerates and / or ensures that the brake pad carrier is separated from the friction surface as soon as the winding is energized and the armature disk is thereby pulled toward the magnet.

[0017] In an advantageous embodiment, the brake pad carrier has an annular part, which has an internal toothing and to which at least one carrier disk is fastened, on which a friction pad is respectively mounted.

[0018] In particular, the minimum radial distance of the annular element is radially spaced and arranged radially in the radial distance region covered by the carrier disk. The advantage here is that the elastic element generates a radially directed force between the annular element and the entraining element, so that the annular element entrains the elastic element during the axial movement of the brake pad carrier and thus axially elastically preloads the elastic element.

[0019] In an advantageous embodiment, the ring has an annular groove, in particular an annular inner groove.

[0020] In particular, the annular groove is arranged axially next to the internal toothing. The advantage here is that the restoring force can be introduced as close to the friction surface as possible and thus stable operation can be achieved.

[0021] In an advantageous embodiment, the spring element is a bent piece made of a round wire. The advantage here is that it can be manufactured simply and cost-effectively. In addition, the round wire can be bent in a defined and simple manner.

[0022] In an advantageous embodiment, the spring element has radially directed bends, in particular five bends. This has the advantage that the bends can be produced simply and cost-effectively.

[0023] In an advantageous embodiment, the spring element is formed so as to rise in a spiral in the axial direction, in particular when no second axial force component is provided. The advantage here is that the spring element is formed in a spiral shape so that as the spiral angle (i.e. the circumferential angle about the axis of rotation of the shaft) increases, the spring element rises monotonically, in particular strictly monotonically, in the axial direction. This applies in particular when the brake pad carrier is not pressed against the friction surface and the spring element is therefore relaxed in the axial direction, i.e. the brake pad carrier is arranged without contact with the friction surface and the armature disk.

[0024] In this way, the spring element is clamped or clamped in the groove base of the annular groove without play even if the annular groove has a groove width at the groove base that is greater than the diameter of the round wire of the spring element.

[0025] In an advantageous embodiment, the elastic element is shaped so as to increase monotonically, in particular strictly monotonically, in the axial direction with increasing circumferential angle.

[0026] In particular, if no second axial force component is provided, it is advantageous here that the spring element is formed in a spiral shape so that as the spiral angle (i.e. the circumferential angle about the axis of rotation of the shaft) increases, the spring element rises monotonically, in particular strictly monotonically, in the axial direction. This applies in particular to the case where the brake pad carrier is not pressed against the friction surface and the spring element is therefore relaxed in the axial direction, i.e. the brake pad carrier is arranged without contact with the friction surface and the armature disk.

[0027] In this way, the spring element is clamped or clamped in the groove base of the annular groove without play even if the annular groove has a groove width at the groove base that is greater than the diameter of the round wire of the spring element.

[0028] In an advantageous embodiment, the spring element has an axial bend, in particular one or two bends. The advantage here is that the bend can be produced simply and cost-effectively.

[0029] In an advantageous embodiment, the circumferential angular area covered by the elastic component in the circumferential direction extends over less than 270°, in particular, the circumferential angular area extends over more than 180°. The advantage here is that the elastic component introduces radially directed forces and is stably arranged and supported at the same time.

[0030] In an advantageous embodiment, the driver has one or more annular grooves.

[0031] In particular, the annular groove interrupts the external toothing in the axial direction and / or the annular groove is arranged in a region covered by the external toothing in the axial direction. The advantage here is that the elastic element is supported both in the driver and in the annular element of the brake pad carrier and that the elastic element generates a force in the radial direction, thereby pushing the brake pad carrier away from the driver in the radial direction.

[0032] In an advantageous embodiment, the ring axis is coaxial with the axis of rotation of the shaft. It is advantageous here that the entrainment element, the external toothing, the internal toothing and / or the ring element of the brake pad carrier are arranged coaxially with respect to one another.

[0033] In an advantageous embodiment, the groove width of the annular groove measured in the axial direction decreases monotonically with increasing groove depth. The advantage here is that the groove narrows with decreasing radial distance and thus the round wire of the spring element is clamped at one point when the spring element is pushed in.

[0034] In an advantageous embodiment, at least one of the groove walls of the annular groove is designed to be inclined at an angle of 20° to 40°. The advantage here is that when pushed in, the elastic element is clamped after reaching a critical depth value.

[0035] In an advantageous embodiment, at each angular position of the annular groove, the normal vector of at least one of the groove walls has an angle value of between 50° and 70° relative to the radial direction, in particular relative to the radial direction associated with the respective angular position of the annular groove. The advantage here is that when the spring element is inserted, the spring element is clamped with a section of its round wire from the critical groove depth, so that the remaining spring element can be elastically deflected relative to the clamped section.

[0036] In an advantageous embodiment, at least one of the groove walls of the annular groove has a circular section. This has the advantage that simple production can be achieved and that the spring element can be clamped in a well-defined groove depth.

[0037] In an advantageous embodiment, the shaft is mounted rotatably relative to the magnet, which is in particular made of ferromagnetic material.

[0038] In this case, a winding that can be energized is accommodated in an annular recess of the magnet.

[0039] In this case, the armature disk, which is made of ferromagnetic material in particular, is arranged axially between the magnet and the brake pad carrier.

[0040] wherein the armature disk is connected to the magnet in a rotationally fixed manner, in particular wherein a pin fastened to the magnet passes through a recess of the armature disk,

[0041] The brake pad carrier is arranged axially between the armature disc and the friction surface.

[0042] In particular, the friction surface is designed on a plate or a support flange which is connected to the magnet in a non-rotatable but detachable manner.

[0043] In this case, a spring element, in particular an annular spring element, supported on the magnet presses onto the armature disk, in particular so that

[0044] - when the winding is energized, the armature disk is pulled toward the magnet against the spring force generated by the spring element and the brake pad carrier is moved away from the friction surface by means of a second force component,

[0045] - and when the winding is not energized, the spring element presses the armature disk onto the brake pad carrier and thereby the brake pad carrier onto the friction surface, in particular with one of its friction pads.

[0046] The advantage here is that the brake automatically applies when the current is interrupted, because the spring element presses the armature disk against the brake pad carrier and thus presses the brake pad carrier on its side facing away from the armature disk against the friction surface. When the current is (not) applied, the brake pad carrier is then separated from the friction surface, because the elastic element generates an axially directed restoring force, which pulls the brake pad carrier back from the friction surface.

[0047] In an advantageous embodiment, the diameter of the round wire of the spring element is greater than the minimum groove depth of the annular groove in the axial direction, in particular so that the round wire is pressed into the annular groove. The advantage here is that the spring element is stuck in a defined position when pressed into the annular groove.

[0048] In an advantageous embodiment, the shaft is a rotor shaft of an electric motor. The advantage here is that the rotor shaft of the electric motor can be braked. Here, the stator of the electric motor is connected to the friction surface and the magnet in a rotationally fixed manner.

[0049] Further advantages are derived from the dependent claims. The invention is not limited to the feature combinations described in the claims. Other reasonable combinations of the claims and / or the features of the individual claims and / or the features of the description and / or the drawings are apparent to a person skilled in the art, especially from the purpose setting and / or the purpose proposed by comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] The present invention will now be explained in detail according to the schematic diagram:

[0051] exist Figure 1 ] A longitudinal section through a brake pad carrier of an electromagnetically actuable brake is shown in FIG.

[0052] exist Figure 2 The enlarged view shows Figure 1 , in which a prestressed elastic element 20 arranged in an annular inner groove, in particular pressed radially outwardly, can be seen.

[0053] exist Figure 3 A top view looking toward the brake pad carrier is shown in FIG.

[0054] exist Figure 4 The entrainment member 30 is shown in an oblique view.

[0055] exist Figure 5 2 shows a cross section through the entrainment member 30 .

[0056] exist Figure 6 , the spring element 20 is shown in a top view, so that the radially oriented curvature of the spring element 20 can be seen.

[0057] exist Figure 7 The entrainment member 30 is shown in a side view.

[0058] exist Figure 8 , the spring element 20 is shown in a side view, so that the axially directed curvature of the spring element 20 can be seen.

[0059] exist Fig. 9 2 shows a longitudinal section through a driver 30 of a second electromagnetically actuable brake according to the invention.

[0060] exist Fig.10 The enlarged view shows Fig. 9 The annular groove 100 of the driving member 30.

[0061] exist Fig.11 The figure shows the Fig. 9 and Fig.10 Optional annular groove 110 .

[0062] exist Fig.12 The elastic member 20 is shown in a side view, wherein Figure 8 In contrast, the spring element 20 has a helical rise, ie, an axial rise which increases monotonically, in particular strictly monotonically, with increasing circumferential angle. DETAILED DESCRIPTION

[0063] As in Figures 1 to 8 As shown in FIG. 1 , the brake pad carrier has an annular part 1 which is provided with an internal toothing 2. Two carrier disks 4, in particular two carrier disks 4 designed as perforated disks, are provided with friction linings 3 at the axial end sides facing away from the respective other carrier disk.

[0064] At the carrier discs 4 where no friction lining 3 is provided, two carrier discs 4 are arranged in contact with each other in an abutting manner. The carrier discs are connected to the ring 1 by means of axially oriented bolts. For this purpose, the bolts are screwed into axially oriented threaded holes, wherein the bolt heads of the bolts press the first of the carrier discs 4 against the other carrier disc 4, thereby pressing the other carrier disc onto the ring 1.

[0065] An annular inner groove, ie in particular an annular groove, is formed on the ring part 1 axially beside the inner toothing 2, in which the elastic element 20 is received. The ring (elastic element) 20 is preferably elastically preloaded and thereby pressed radially outwards.

[0066] The carrier plates 3 are coaxial with respect to one another and also with respect to the ring 1 .

[0067] In particular, the annular (elastic component) 20 can be referred to as an elastic ring, wherein the elastic ring is interrupted in the circumferential direction.

[0068] The annular (elastic portion) member 20 is preferably made of a bent round wire.

[0069] The annular (elastic part) part 20 has radially directed curvatures, so that the annular (elastic part) part 20 is pressed radially outwards against the annular part 1, in particular against the groove bottom of the annular inner groove of the annular part 1, by means of the first curvature. The second curvature is directed radially inwards.

[0070] The brake pad carrier is sleeved onto an annular entraining member 40 with an external toothing, and the entraining member is connected to the shaft in a non-rotatable manner, especially by means of a key connection in a non-rotatable manner. At this time, the internal toothing 2 is sleeved onto the external toothing of the entraining member.

[0071] In particular, the outer toothing of the entrainment member 40 meshes with the brake pad carrier, in particular the inner toothing 2 of the ring member 1. Thus, the entrainment member 40 and the ring member 1 are connected in a rotationally fixed manner.

[0072] The outer tooth portion and the inner tooth portion are arranged coaxially with each other.

[0073] The brake pad carrier is arranged on the driver 40 so as to be displaceable in the axial direction.

[0074] The brake has a magnet (not shown in the figures), wherein a winding which can be energized is received in an annular recess of the magnet, in particular wherein the ring axis or the winding axis is oriented parallel to the axial direction.

[0075] The armature disk, in particular a disk made of ferromagnetic material, is connected to the magnet in a rotationally fixed manner and is arranged so as to be axially displaceable. For example, for this purpose, a pin extending through a recess in the armature disk is connected to the magnet, in particular so that the armature disk is arranged so as to be movable in the axial direction and is nevertheless connected to the armature disk in a rotationally fixed manner.

[0076] The armature disk is arranged axially between the brake pad carrier and the magnet. The brake pad carrier is arranged axially between the armature disk and the friction surface, which is provided either by means of a friction plate or by means of a correspondingly finely machined flange, in particular of the electric motor.

[0077] A spring element, in particular a compression spring, supported on the magnet presses against the armature disk, in particular so that when the winding is not energized, the armature disk is pressed away from the magnet toward the brake pad carrier, so that the brake pad carrier is pressed against the friction surface on its side axially facing away from the armature disk.

[0078] However, when the winding is energized, the spring force generated by the spring element is overcome to pull the armature disc toward the magnet and thereby release the brake pad carrier. However, in order to assist and / or reliably ensure that the brake pad carrier is separated from the friction surface, the elastic deflection of the elastic component 20 acts as a restoring force for the brake pad carrier. Because the elastic component 20 is arranged between the ring 1 and the driving member 40 in an elastically preloaded manner, and when the brake pad carrier moves toward the friction surface, it is correspondingly axially driven by the ring 1 and thereby elastically deflected.

[0079] Furthermore, the annular inner groove has a groove bottom whose width exceeds the diameter of the round wire material of the elastic member 20 .

[0080] However, since the elastic member has both radial curvature and axial curvature, the elastic member 20 is elastically tightened at the groove bottom. In particular, it can be said that the elastic member 20 is fixed at the groove bottom.

[0081] As in Figure 3 As shown in , the elastic component 20 protrudes radially inward from the annular inner groove of the ring 1 in several circumferential angle regions, so that when the driver 40 is pushed in axially, these radially inwardly protruding regions are slightly pulled in the axial direction, and the elastic component 20 is thereby preloaded in the axial direction. In addition, the radial preload of the elastic component 20 is achieved in the following manner, that is, when the outer toothing of the driver 40 is pushed into the inner toothing of the ring 1, the elastic component 20 is radially pressed.

[0082] Preferably, the outer toothing of the entrainment member 40 has a chamfer at its end face end region, in particular in such a way that the maximum outer diameter of the outer toothing of the entrainment member 40 increases monotonically in the axial direction, in particular with increasing distance from the end face of the entrainment member 40 .

[0083] As in Figure 3 As shown in , the friction plate 3 is composed of a plurality of segments, in particular 12 segments, which are evenly spaced from each other in the circumferential direction and / or are all arranged at the same radial distance. Alternatively, the friction plate 3 is implemented in one piece, that is, in one piece.

[0084] As in Figure 8 As shown in , the axial curvature is designed in such a way that the elastic element 20 is sinusoidal in a side view, that is, in particular, the vertical projection of the elastic element 20 in a plane having the radial direction and the axial direction as Cartesian coordinate axes is sinusoidal and / or similar to a sine arc.

[0085] As in Figure 6 As shown in , the elastic element has a radial bend. Preferably, five bends are implemented here, wherein these bends extend over a circumferential angle range of greater than 180° but in particular less than 270°.

[0086] As in Fig. 9 and Fig.10 As shown in the figure, unlike the driver 40 of the first brake, the driver 40 in the second brake has an inclined groove wall in the annular groove 100 of the driver 40, the annular groove is arranged in the area covered by the external tooth portion of the driver 40 in the axial direction, and the elastic component 20 is elastically clamped in the annular groove.

[0087] That is, the elastic member 20 is elastically pretensioned radially inwards. Preferably, the elastic member 20 is thus fixedly clamped in the annular groove of the entrainment member 20 .

[0088] The ring axis of the annular groove 100 is coaxial with the rotation axis of the brake pad carrier and / or the shaft to be braked, onto which the driver is mounted and connected in a form-fitting manner, in particular by means of a key connection.

[0089] The annular groove is designed to be narrow at the groove bottom, so that the elastic element 20 has no play or no significant play.

[0090] The annular inner groove on the annular part 1 of the brake pad carrier can be omitted.

[0091] The groove wall of the groove 100 is designed to be inclined at an angle of preferably 30° or 20° to 40° relative to a plane which is oriented normal to the axial direction parallel to the axial direction.

[0092] However, in a further development, both groove walls can also be designed to be inclined, in which case the values ​​of the inclination angles of the two groove walls are then equally large.

[0093] As a result, when the entrainment element 40 is pushed into the ring part 1 , the spring element 20 is preferably deflected by the angle of inclination and thus provides a corresponding restoring force for the brake pad carrier.

[0094] However, instead of a straight groove wall in longitudinal section, it is also possible to realize Fig.11 In the embodiment of the bending shown in . In particular, the groove wall has a circular section in the longitudinal section. In an improved solution, the two groove walls are implemented to be symmetrical to each other.

[0095] In other embodiments according to the present invention, groove walls that are curved in other ways may also be used.

[0096] In other embodiments according to the present invention, a tooth number greater than 10 (ie, in particular, an internal toothing and an external toothing) may also be replaced by a tooth number of 10 or less, ie, 1 to 10. The toothing may be implemented as an involute toothing or a trochoid toothing.

[0097] Reference numerals list

[0098] 1 Ring

[0099] 2Inner teeth

[0100] 3 Friction plate

[0101] 4 Carrying tray

[0102] 20 Elastic components

[0103] 40 driving parts

Claims

1. A brake device having a shaft and a brake pad carrier, in, The annular entrainment element is connected to the shaft in a rotationally fixed manner, in particular in a form-fitting manner, in particular by means of a key connection. In particular, the brake pad carrier is mounted on the driver. The brake pad carrier has an internal toothing which meshes with an external toothing of the driver, in particular with play and / or displaceably in the axial direction, in particular such that the brake pad carrier is arranged displaceably relative to the driver in the axial direction, i.e. in particular parallel to the axis of rotation of the shaft, It is characterized in that The elastic component, in particular an elastic ring, in particular an elastic ring made of a bent round wire, is received and / or elastically clamped in an annular groove, in particular an annular inner groove, The elastic force generated by the elastic component supported on the driving member includes a first force component and a second force component of the elastic force, the first force component presses on the brake pad carrier in the radial direction, and the second force component acts on the brake pad carrier in the axial direction.

2. The braking device according to claim 1, characterized in that: The brake pad carrier has an annular part, the annular part has an internal tooth portion and at least one carrier disk is fastened to the annular part, and friction pads are respectively mounted on the carrier disks. Especially among them, The smallest radial distances of the rings are radially spaced apart and are arranged radially in a radial distance region covered by the carrier disc.

3. The braking device according to any one of the preceding claims, characterized in that The ring has an annular groove, in particular an annular inner groove. Especially among them, The annular groove is arranged axially next to the internal toothing.

4. The braking device according to any one of the preceding claims, characterized in that The elastic part is a bent part made of round wire, and / or The spring element has radially directed bends, in particular five bends.

5. The braking device according to any one of the preceding claims, characterized in that Especially when the second axial force component is not designed, The elastic member is formed to rise spirally in the axial direction. and / or The elastic component is shaped so as to increase monotonically, in particular strictly monotonically, in the axial direction as the circumferential angle increases. This is especially true if no second axial force component is provided.

6. The braking device according to any one of the preceding claims, characterized in that The elastic element has an axial bend, in particular one or two bends.

7. The braking device according to any one of the preceding claims, characterized in that The extension of the circumferential angular area covered by the elastic component in the circumferential direction is less than 270°, in particular, the extension of the circumferential angular area is greater than 180°.

8. The braking device according to any one of the preceding claims, characterized in that The driving member has one or more annular grooves. In particular, the annular groove interrupts the external toothing in the axial direction and / or the annular groove is arranged in a region which is covered by the external toothing in the axial direction.

9. The braking device according to any one of the preceding claims, characterized in that The ring axis is coaxial with the axis of rotation of the shaft.

10. The braking device according to any one of the preceding claims, characterized in that The groove width of the annular groove measured in the axial direction decreases monotonically with the increase of the groove depth.

11. The braking device according to any one of the preceding claims, characterized in that At least one of the groove walls of the annular groove is designed to be inclined at an angle of 20° to 40°. and / or At each circumferential angular position, a normal vector of at least one of the groove walls of the annular groove has an angle value between 50° and 70° relative to a radial direction, in particular relative to the radial direction associated with the respective circumferential angular position.

12. The braking device according to any one of the preceding claims, characterized in that At least one of the groove walls of the annular groove has a circular section.

13. The braking device according to any one of the preceding claims, characterized in that The shaft is mounted rotatably relative to a magnet, in particular made of ferromagnetic material, In this case, a winding capable of being energized is accommodated in an annular recess of the magnet. In this case, the armature disk, which is made of ferromagnetic material in particular, is arranged axially between the magnet and the brake pad carrier. wherein the armature disk is connected to the magnet in a rotationally fixed manner, in particular wherein a pin fastened to the magnet passes through a recess of the armature disk, The brake pad carrier is arranged axially between the armature disc and the friction surface. In particular, the friction surface is designed on a plate or a support flange which is connected to the magnet in a non-rotatable but detachable manner. In this case, a spring element, in particular an annular spring element, supported on the magnet is pressed onto the armature disk. In particular, - when the winding is energized, the armature disk is pulled toward the magnet against the spring force generated by the spring element and the brake pad carrier is moved away from the friction surface by means of a second force component, - and when the winding is not energized, the spring element presses the armature disk onto the brake pad carrier and thereby the brake pad carrier onto the friction surface, in particular with one of its friction pads.

14. The braking device according to any one of the preceding claims, characterized in that The diameter of the round wire of the spring element is greater than the minimum groove depth of the annular groove in the axial direction, in particular so that the round wire is pressed into the annular groove.

15. An electric machine having a brake device according to any one of the preceding claims, characterized in that The shaft is the rotor axis of the motor.

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