BRAKING DEVICE

Abstract

A brake device for a drivable part, in particular for use for a vehicle flap, in particular in an automobile, includes a drivable load device (11) which can be radially brought into contact with a disc (90) of the drivable part, with a first holding position and a second release position. At least one brake element rests against the periphery (92) of the disc (90) in a frictional manner in the holding position and secures the disc (90) from rotating using a specifiable force. In the release position, the at least one brake element is arranged at a distance from the periphery of the disc (90) and allows a free run of the disc (90), and the load device (11) can be adjusted between the holding position and the release position, preferably by a motor (12). A brake device or a rotating drive with which a drivable part of the drive is secured against a displacement on the basis of the mass of the component to be displaced even when the motor is not being provided with power or is deactivated is achieved in that the first holding position and the second release position are each designed as a metastable holding position.

Claims

1-30. (canceled)

31. A braking device for a drivable part, the drivable part being a vehicle flap in an automobile, the braking device comprising: a drivable loading device having a first holding position and a second release position, the drivable loading device being configured for being brought into radial contact with a cylindrical disc portion of the drivable part, the cylindrical disc portion having a rotational axis; the drivable loading device including: at least one braking member frictionally abutting a circumference of the cylindrical disc portion and securing the cylindrical disc portion against a rotation with a pre-settable force in the first holding position, the at least one braking member being spaced from the circumference of the cylindrical disc portion and allowing the cylindrical disc portion to run freely in the second release position; a motor configured for adjusting the drivable loading device between the first holding position and the second release position; a guiding member assigned to the braking member, the guiding member being out of contact with the cylindrical disc portion; and an eccentric disc cooperating with the guiding member, the eccentric disc having a bearing axis which is coaxial with the rotational axis of the cylindrical disc portion.

32. The braking device according to claim 31, wherein the guiding member is a rotatable roller attached to the at least one braking member.

33. The braking device according to claim 31, wherein the eccentric disc comprises a first circumferential portion in which the guiding member is arranged in the first holding position, and wherein the eccentric disc comprises a second circumferential portion in which the guiding member is arranged in the second release position.

34. The braking device according to claim 31, wherein the eccentric disc comprises a drive portion, and wherein the drive portion is coupled to the motor to impart a rotation of the eccentric disc about the bearing axis.

35. The braking device according to claim 34, wherein the drive portion comprises an externally toothed disc segment.

36. The braking device according to claim 31, wherein the eccentric disc comprises a radial projection which forms a stop for the guiding member.

37. The braking device according to claim 34, wherein the eccentric disc comprises a constricted portion, wherein the drive portion is provided on one side of the constricted portion, and wherein the first circumferential portion is provided on the other side of the constricted portion.

38. The braking device according to claim 34, wherein the drive portion is drivable by a gear driven by the motor.

39. A braking device for a drivable part, the drivable part being a vehicle flap in an automobile, the braking device comprising: a drivable loading device having a first holding position and a second release position, the drivable loading device being configured for being brought into radial contact with a disc of the drivable part, the disc having a rotational axis; the drivable loading device including: at least one braking member frictionally abutting a circumference of the disc and securing the disc against a rotation with a pre-settable force in the first holding position, the at least one braking member being spaced from the circumference of the disc and allowing the disc to run freely in the second release position; a motor configured for adjusting the drivable loading device between the first holding position and the second release position; and spring member loading the braking member towards the disc, the spring member comprising a first loading leg, the first loading leg loading the braking member against the disc, the first loading leg moving a first lever, and the braking member being arranged on the first lever.

40. The braking device according to claim 39, wherein the first lever is pivotably articulated about a first pivot joint.

41. The braking device according to claim 39, wherein the first lever comprises an abutment for the first loading leg.

42. The braking device according to claim 39, wherein the braking member comprises a braking surface of the first lever.

43. The braking device according to claim 39, wherein a distance between an articulation of the lever and the braking member is smaller than a diameter of the disc.

44. A braking device for a drivable part, the drivable part being a vehicle flap in an automobile, the braking device comprising: a drivable loading device having a first holding position and a second release position, the drivable part comprising a cylindrical disc portion; the drivable loading device including: a first braking member pivotally attached to a first pivot joint and a second braking member pivotally attached to a second pivot joint distant from the first pivot joint; a rotative actuator being in operative contact with the first braking member and the second braking member; wherein the first braking member radially abuts a first circumference portion of the cylindrical disc portion in the first holding position to arrest the cylindrical disc portion against a rotation and wherein the first braking member is spaced from the first circumference portion of the cylindrical disc portion in the second release position to allow the cylindrical disc portion to run freely, wherein the second braking member radially abuts a second circumference portion of the cylindrical disc portion in the first holding position to arrest the cylindrical disc portion against a rotation and wherein the second braking member is spaced from the second circumference portion of the cylindrical disc portion in the second release position to allow the cylindrical disc portion to run freely, wherein the rotative actuator device is adjustable between the first holding position and the second release position by a rotational movement, wherein the rotative actuator comprises a radial projection protruding between the first pivot joint and the second pivot joint, and wherein the radial projection comprises a coupling arrangement for an external motor.

45. The braking device according to claim 44, wherein at least one spring member loads at least one of the first and second braking members towards the respective first and second circumference portions of the cylindrical disc portion, and wherein the at least one spring member comprises at least one deflectable loading leg for urging said one of the first and second braking members toward one of said respective first and second circumference portions.

46. The braking device according to claim 45, wherein the drivable loading device includes a first lever comprising the first braking member and a second lever comprising the second braking member, wherein the first lever is pivotally attached to the first pivot joint. wherein the second lever is pivotally attached to the second pivot joint, wherein the first lever comprises a first recess for receiving a distal portion of the at least one deflectable loading leg, and wherein the second lever comprises a second recess for receiving a distal portion of the at least one deflectable loading leg.

47. The braking device according to claim 46, wherein the first lever comprises a first guiding member protruding to cooperate with the rotative actuator, wherein the second lever comprises a second guiding member protruding to cooperate with the rotative actuator, such that upon a rotation of the rotative actuator responsive to a driving movement of the motor, the first and second guiding members together with the first and second levers are simultaneously radially displaced depending upon a radial bulge of the rotative actuator to engage the first and second braking members with the first and second circumference portions of the cylindrical disc portion under a load of the at least one deflectable loading leg in the first holding position and the first and second guiding members together with the first and second levers are simultaneously radially displaced depending upon the radial bulge of the rotative actuator to disengage the first and second braking members from the first and second circumference portions of the cylindrical disc portion against a load of the at least one deflectable loading leg in the second release position.

48. The braking device according to claim 44, wherein the radial projection of the rotative actuator comprises a constricted portion having a first concave surface oriented toward the first pivot joint and a second concave surface opposite the first concave surface and oriented toward the second pivot joint, wherein the coupling arrangement of the radial projection comprises a toothed segment for meshing engagement with a gear of the external motor, and wherein a gear axis of the gear of the external motor is parallel to a rotational axis of the cylindrical disc portion.

49. The braking device according to claim 44, wherein the rotative actuator comprises an eccentric flat body comprising a first protruding circumferential edge and a first retracted circumferential edge for engagement with a first guiding member assigned to the first braking member, wherein the eccentric flat body comprises a second protruding circumferential edge and a second retracted circumferential edge for engagement with a second guiding member, assigned to the second braking member, such that upon a rotation of the rotative actuator responsive to a driving movement of the motor, the first and second guiding members together with the first and second braking members are simultaneously radially displaced depending upon a rotational orientation of the rotative actuator to engage the first and second braking members with the first and second circumference portions of the cylindrical disc portion in the first holding position and the first and second guiding members together with the first and second braking members are simultaneously radially displaced depending upon the radial bulge of the rotative actuator to disengage the first and second braking members from the first and second circumference portions of the cylindrical disc portion in the second release position.

50. The braking device according to claim 44, wherein the rotative actuator comprises a flat body comprising a first protruding contact surface and a first retracted contact surface assigned to deflect the first braking member, wherein the flat body comprises a second protruding contact surface and a second retracted contact surface assigned to deflect the second braking member, wherein the flat body is rotatable about a rotational axis of the cylindrical disc portion, and wherein the flat body radially protrudes over the cylindrical disc portion.

Description

BRIEF SUMMARY OF THE DRAWINGS

[0043] The present disclosure is explained below with reference to the accompanying drawings using a preferred embodiment.

[0044] FIG. 1 is a perspective view of a preferred embodiment of a braking device according to the present disclosure.

[0045] FIG. 2 is an exploded view of the braking device from FIG. 1.

[0046] FIG. 3 is a plan view of the braking device from FIGS. 1 and 2 in the release position.

[0047] FIG. 4 is a section through the braking device of FIG. 3 along the line IV-IV.

[0048] FIG. 5 is a plan view of the braking device from FIGS. 1 to 3 in the holding position.

[0049] FIG. 6 is a section through the braking device of FIG. 5 along the line VI-VI.

DETAILED DESCRIPTION

[0050] FIG. 1 shows the overall braking device, designated 10, in a perspective view. The embodiment of the individual parts of the braking device can be seen more clearly in the exploded view according to FIG. 2. The braking device 10 has a loading device 11, which can optionally be brought into contact with a disc 90 that does not belong to the loading device 11 and that is part of a drive or a drivable part. The disc 90 has a central bore 91 with which the disc 90 can be connected to a rotatable rod. Furthermore, the disc 90 has a completely circular outer circumference 92, via which the disc 90 which rotates or allows a rotation is intended to be braked respectively locked in place by the loading device 11.

[0051] The loading device 11 has a motor 12, which is a conventional electric motor with two directions of rotation and the output shaft 13 of which has a pinion or gear 14, which allows the loading device 11 to be adjusted from a holding position to a release position and vice versa. The motor 12 thus serves to adjust or switch the loading device 11 between the holding position and the release position and vice versa.

[0052] The loading device 11 also has a first lever 21 and a second lever 22, which are designed as plastics injection molded parts and which each have inner sides 21i, 22i facing one another and outer sides 21a, 22a facing away from one another. The levers 21, 22 are each designed to be pivotable about a pivot axis 21b, 22b, the pivot axis in the present embodiment being embodied as a pin. The pin can for example be connected to a housing part of the drivable part. The height of the levers 21, 22 is somewhat larger than the height of the disc 90, so that in the installed state the levers 21, 22, which lie in the plane of the disc 90, exceed the disc 90 in at least one axial direction, preferably in both axial directions, as can be seen in particular in FIGS. 4 and 6.

[0053] The levers 21, 22 each have on their inner side 21i, 22i a braking member 31, 32 designed as a braking surface, which is intended to come into contact with the circumference 92 of the disc 90 and to lock the disc 90. The braking surface 31, 32 is slightly concave with the radius of the circumference 92.

[0054] At its end facing away from the bearing 21b, 22b, each lever 21, 22 has a receptacle 21z, 22z in which the end of a spring member 40 described below can be inserted.

[0055] The spring member 40 has a first loading leg 41 and a second loading leg 42, the ends of which have an S-shaped configuration in order to be able to be received in the protruding receptacles 21z, 22z. The spring member 40 is designed in the manner of a torsion spring with two loading legs 41, 42, which connect on both sides of a base 43 of the spring member 40 and the windings connected to it. The base 43, like the journals of the bearings 21b, 22b, is connected to the housing of the part. The loading leg 41, 42 biases the levers 21, 22 in the direction of the circumference 92 of the disc 90, and the bias of the spring member 40 or the loading limb 41, 42 must be overcome in order to move the levers 21, 22 and thus to push the braking members 31, 32 away from circumference 92 of the disc 90. The spring force of the spring member 40 defines the holding force for the drivable part respectively its disc 90 and is selected by design so that the holding force is able to hold the mass of a component moved by the drivable part when the drive is de-energized, but can be overcome when the component is actuated by hand. This can be adjusted by simple experimentation.

[0056] On an upper side of each lever 21, 22, a guiding member 51, 52 designed as a plastics roller and mounted on the lever 21, 22 is connected, which can be brought into contact with the circumference of an eccentric disc 60 described below in order to pivot the braking members 31,32 via the lever 21, 22 away from the circumference 92 of the disc 90 against the bias of the two loading legs 41, 42. It can be seen that the guiding members 51, 52 lie in a common plane in which the eccentric disc 60 to be described below is also arranged.

[0057] The eccentric plate 60 is arranged concentrically and axially spaced from the disc 90 and has a central, in the present case circular opening 60a through which a shaft connected to the disc 90 can be passed at a distance from the opening 60a. The eccentric disc 60 can be pivotably guided via the opening 60a on a housing part, but the eccentric plate 60 is preferably circumferentially around an outer collar 60b which extends the opening 60a and protrudes axially from the side of the eccentric disc 60 facing away from the disc 90 out of the housing of the drive.

[0058] At its end spaced from the opening 60a, the eccentric disc 60 has an externally toothed disc segment 61 with a plurality of teeth, of which the first tooth 61a forms an end stop for the gear 14. It is possible to also equip the other end of the toothed segment 61 with a corresponding stop. The toothed segment 61 and the gear 14 mesh with one another, so that when the motor respectively the shaft 13 is actuated, the eccentric disc 60 is pivoted in the corresponding direction about the common axis A of disc 90 and eccentric disc 60. A constricted portion 62 is provided between the opening 60a and the disc segment 61, which allows the pivoting between the two axes 21b, 22b.

[0059] The eccentric disc 60 has two first circumferential portions 71 which are arranged on the outer circumference 60u of the eccentric plate in opposite positions such that the two guiding members 51, 52 simultaneously overlap the corresponding first circumferential portion 71 and correspond to the holding position. The circumference 60u of the eccentric disc 60 also has two second circumferential portions 72 which correspond to a release position.

[0060] In particular in FIGS. 3 and 4, it can be seen that at the maximum distance of the tooth 61a from the gear 14, the two guiding members 51, 52 each rest against the second circumferential portion biased by the spring member 40, wherein projections 79 on the circumference 60u of the eccentric disc 60 prevent the eccentric disc 60 from being significantly moved beyond the release position. It can be seen that the distance between the second circumferential portion 72 and the axis A of the eccentric disc 60 is greater than the distance between the first circumferential portion 71 of the eccentric disc 60.

[0061] In FIGS. 5 and 6 the guiding members 51, 52 lie in the region of the first circumferential portion 71, wherein the levers 21, 22 being moved in the direction of the outer circumference 92 of the disc 90 under the bias of the loading legs 41, 42. It can be seen that the guiding members 51, 52 no longer rest on the outer circumference 60u of the eccentric disc 60, but are slightly spaced therefrom, since the braking members 31, 32 now frictionally abut the outer circumference 92 of the disc 90 and under the bias of the spring member 40. The disc 90 is braked on both sides by the spring member 40 and the guiding members 51, 52 are accordingly positioned at a distance from the first circumferential portion 71, 72. It can be seen that the outer circumference 60u has a third circumferential portion 73 which is at a greater distance from the axis A of the eccentric disc 60 than the first circumferential portion 71 and/or the second circumferential portion 72, so that for transferring the guiding members from the one circumferential portion 71 to the other circumferential portion 72 an increased resistance of the spring member 40 must be overcome. The first circumferential portion 71 and the second circumferential portion 72 form metastable positions that do not allow the transition from one to the other without increased expenditure of force. It can also be seen that two stops 79 protrude radially on the outer circumference 60u of the eccentric disc 60 and prevent pivoting beyond the desired pivoting range.

[0062] The present disclosure then works as follows: If the shaft of the drivable part, which is non-rotatably connected to the disc 90, is in an energized state, the motor 12 is controlled in such a way that it assumes the release position shown in FIGS. 3 and 4. In this case, the guiding members 51, 52 are in contact with the relevant second circumferential portion 72 of the eccentric disc 60. If the drive is switched off, the motor 12 causes the eccentric disc 60 to pivot over the toothed portion 61 until the eccentric disc 60 has assumed the position shown in FIGS. 5 and 6. The guiding members 51, 52 are then preferably at a distance in the region of the first circumferential portions 71, and the braking members 31, 32 enclose the circumference 92 of the disc 90 in a frictional manner. As a result, a holding force corresponding to the spring force of the two loading legs 41, 42 is exerted on the disc 90, which means that even when the drive is switched off, it no longer allows any rotation.

[0063] The present disclosure has been explained above on the basis of an embodiment in which the levers 21, 22, the loading legs 41, 42, the braking members 31, 32 and the guiding members 51, 51 are each provided in mirror image and thus twice. This increases the overall operational safety. It has to be understood, however, that merely a single configuration of all the parts can also suffice to hold the disc 90.

[0064] The present disclosure has been described above using an embodiment in which a spring member 40 loads both levers 21, 22. It has to be understood that a dedicated spring member, that is to say a first spring member and a second spring member, can also be provided for each lever.

[0065] The present disclosure has been explained above on the basis of an embodiment in which a rotary motor 12 effects the adjustment of the eccentric disc 60 and thus the tensioning of the loading legs 41, 42. It has to be understood that, as an alternative, the loading legs 41, 42 can also be loaded and relieved in a different manner, for example by an axial actuator which moves the corresponding base 43 of the spring member 40.

[0066] The present disclosure has been explained above on the basis of an embodiment in which levers 21, 22 are used in order to achieve reproducible contact between the outer circumference 92 of the disc 90 and the braking members 31, 32. It has to be understood that the levers 21, 22 are not absolutely necessary for this if, for example, the braking members 31, 32 are provided on the loading legs 41, 42, and further expediently the guiding members 51, 52 are also arranged on the loading legs 41, 42.

[0067] The present disclosure has been described above on the basis of an embodiment in which a frictional connection between the braking members 31, 32 and the disc 90 is achieved. It has to be understood that, alternatively and/or cumulatively, the provision of engaging noses, teeth or flanks can produce a form-fitting contact which, however, is more difficult to overcome when operated manually.

[0068] The present disclosure has been explained above on the basis of an embodiment in which the spring member 40 is a double-legged torsion spring which provides a high spring force in a favorable manner in terms of installation space. It has to be understood that the spring member can also be provided in another way, for example as a torsion spring.

[0069] The present disclosure has been explained above using an embodiment in which the disc 90 can be connected in a rotationally fixed manner to a shaft of a drive. It has to be understood that the disc 90 can also be connected to another moving part, for example a hinge pin or the like, in a hinge or an articulated connection for blocking the pivoting.