DE102014215257A1 - Ramp system for converting a rotational movement into a linear movement for the operation of a disc brake - Google Patents

Abstract

It is a ramp system for converting a rotational movement into a linear movement for the operation of a disc brake, in particular for braking a ring gear of a connected between a pulley for driving ancillary components of a motor vehicle and a drive shaft of a drive motor of a motor vehicle planetary gear provided with a ramp seat, wherein the ramp seat each having an intermediate surface in the circumferential direction interconnected ramp tracks, a relative to the ramp seat between a short position and an elongated position for changing the axial extent of the ramp system rotatable about a rotation Gegenrampensitz, the Gegenrampensitz each having a counter-surface in the circumferential direction interconnected Gegenrampenbahnen, one each in the ramp path and the counter-ramp track guided ramp ball, the ramp track at its pointing to the counter ramp seat ramp edge opposite a perpendicular z ur axis of rotation extending radial plane has a lower slope than at its facing away from the Gegenrampensitz ramp base and / or the Gegenrampenbahn at its pointing to the ramp seat Gegenrampenrand relative to the radial plane has a lower slope than at its facing away from the ramp seat Gegenrampengrund, wherein the ramp edge and / or the counter ramp edge against the radial plane are bevelled by an angle. Due to the fact that the ramp edge and counter ramp edge are chamfered against the radial plane, it is possible for the material forming the ramp track and the counter-ramp track to partly follow the ramp gradient of the ramp base or counter ramp base, so that at the same ramp pitch and the same translation in the long position greater immersion depth of the ramp ball in the ramp path and the Gegenrampenbahn can result, allowing a secure support of higher forces in the closed position of the disc brake with low space requirement.

Description

The invention relates to a ramp system for converting a rotational movement into a linear movement for the operation of a disc brake, with the aid of which in particular a pivoting movement of a brake lever can be converted into a linear movement of a brake shoe, in particular a ring gear between a pulley for driving ancillaries of a motor vehicle and To brake a drive shaft of a drive motor of a motor vehicle connected planetary gear.

From the DE 10 2012 215 278 A1 is known a disc brake for a belt drive with a pulley for driving ancillaries, with the aid of a ring gear of a provided between the pulley and a crankshaft of the internal combustion engine of a motor vehicle planetary gear can be braked to selectively change a gear ratio between the crankshaft and the pulley. The disc brake has a friction pad provided with a brake shoe and provided with a friction pad brake caliper, which can be displaced by means of Betätigungsaktorik each other in the axial direction to close the disc brake and braking a brake disc of the ring gear, the caliper and the brake shoe against the brake disc to squeeze. The Betätigungsaktorik has a pivotable by an actuating actuator brake lever, which converts the pivotal movement of the brake lever in an axial displacement of the brake shoe and the caliper via a ramp system.

There is a constant need for a small space requirement in the closed state of the disc brake to provide a secure support.

It is the object of the invention to show measures that enable safe support with low space requirement in the closed state of the disc brake.

The object is achieved according to the invention by a ramp system having the features of claim 1. Preferred embodiments of the invention are specified in the subclaims, which individually or in combination may represent an aspect of the invention.

According to the invention, a ramp system for converting a rotational movement into a linear movement for the operation of a disc brake, in particular for braking a ring gear of a connected between a pulley for driving ancillary components of a motor vehicle and a drive shaft of a drive motor of a motor vehicle planetary gear provided with a ramp seat, wherein the ramp seat each having an intermediate surface in the circumferential direction interconnected ramp tracks, a relative to the ramp seat between a short position and an elongated position for changing the axial extent of the ramp system rotatable about a rotation Gegenrampensitz, the Gegenrampensitz each having a counter-surface in the circumferential direction interconnected Gegenrampenbahnen, one each in the ramp track and the Gegenrampenbahn guided ramp ball, the ramp track at her facing the counter ramp seat ramp edge opposite egg ner perpendicular to the axis of rotation extending radial plane has a lower slope than at its pointing away from the Gegenrampensitz ramp base and / or the Gegenrampenbahn at its pointing to the ramp seat Gegenrampenrand relative to the radial plane has a lower slope than at their facing away from the ramp seat Gegenrampengrund, wherein the ramp edge and / or the counter ramp edge are bevelled against the radial plane by an angle.

Here, the knowledge is exploited that at a running in the radial plane ramp edge and counter ramp edge at a predetermined slope of the Rampengrunds or the Gegenrampengrunds the extent of the ramp track and the Gegenrampenbahn is greatly limited in the circumferential direction. The maximum immersion depth of the ramp ball in the ramp path and in the counter-ramp path in the short position corresponds to half the diameter of the ramp ball or even less, if preferably a striking contact of the ramp seat to the counter ramp seat should be avoided. In order to achieve a sufficient translation of the ramp system between the short position and the long position with a small space-saving diameter of the ramp seat and / or Gegenrampensitz, it would be necessary that the ramp ball to the end of the ramp track and the Gegenrampenbahn in the circumferential direction of the slope of the Rampengrunds and Gegenrampengrunds follows, so that the ramp ball in the long position barely guided laterally by the ramp track and the Gegenrampenbahn. As a result, the ramp system would have a particularly low support capability in the long position, in which in particular the disc brake is closed and the highest forces to be supported occur. Due to the fact that the ramp edge and counter ramp edge are chamfered against the radial plane, it is possible for the material forming the ramp track and the counter-ramp track to partly follow the ramp gradient of the ramp base or the counter ramp base, so that the same Ramp pitch and the same translation in the long position may result in a greater immersion depth of the ramp ball in the ramp path and the Gegenrampenbahn, whereby a secure support of higher forces in the closed position of the disc brake is made possible with low space requirements.

Because the ramp edge and the counter ramp edge do not have the same pitch as the ramp base or the counter ramp base, the ramp edge and the counter ramp edge do not run parallel to the ramp base or to the counter ramp base. This avoids a constant immersion depth of the ramp ball into the ramp track and into the counter-ramp track, which otherwise would have required positioning the ramp track and the counter-ramp track at a greater radius to avoid striking the intermediate section at the intermediate section before reaching the short position. Instead, by the different slopes of the ramp edge and the Gegenrampenrands Rampengrund or Gegenrampengrund the slopes are adjusted so that on a given radius, a predetermined slope of the Rampengrunds and Gegenrampengrunds and a predetermined between the short position and the long position to be achieved translation of in Circumferential direction available space for the ramp track and the Gegenrampenbahn can be used to maximum in the long position to achieve the greatest possible immersion depth for the ramp ball. Additionally or alternatively, the extension of the ramp track and the Gegenrampenbahn can be extended without additional space requirements in the circumferential direction, so that, for example, a larger ratio between the short position and the long position and / or a lower pitch for the ramp base and / or the Gegenrampengrund to reduce the operation the disc brake required actuation forces can be achieved.

The slopes of the Rampengrunds, the Gegenrampengrunds, the ramp edge and the Gegenrampenrads be determined, for example, as the angle of the developments of the Rampengrunds, the Gegenrampengrunds, the ramp edge and the Gegenrampenrads against the radial plane, wherein the enclosed between the radial plane and the settlement of the Rampengrunds and Gegenrampengrunds angle is greater than the included between the radial plane and the development of the ramp edge and the Gegenrampenrads angle. For example, an angle α between the radial plane and the development of the Rampengrunds or the Gegenrampengrunds 15 ° ≤ α ≤ 40 °, in particular 20 ° ≤ α ≤ 30 ° and preferably α = 23 ° ± 3 °. For example, an angle β between the radial plane and the development of the Rampengrunds or the Gegenrampengrunds 5 ° ≤ β ≤ 30 °, in particular 10 ° ≤ β ≤ 20 °, and preferably β = 15 ° ± 3 °.

In particular, it is provided that the intermediate surface and the counter-intermediate surface are chamfered at least in a partial region against the radial plane by an angle and extend in the tapered region substantially parallel to each other. Characterized in that the intermediate surface and the counter-intermediate surface are not parallel to the radial plane, the intermediate surface and the counter-interface in the circumferential direction can be designed to be particularly short without fear of striking the intermediate surface against the counter-surface before reaching the short position.

The ramp path preferably has a ramp outlet area for braking the ramp ball in the circumferential direction in the longitudinal position and / or the counter-ramp path has a counter-ramp outlet area for braking the ramp ball in the circumferential direction in the longitudinal position. The ramp outlet area and / or the counter-ramp outlet area can cling to the ramp ball in the long position, so that a high ramp gradient for the ramp ball is formed by the respective outlet area, which slows down the ramp ball and can not move beyond the long position. As a result, the respective outlet region can form a gentle end stop of the ramp track or the counter-ramp track. Jumping out of the ramp ball from the ramp track and / or from the Gegenrampenbahn can be avoided. An over-rotation beyond the long position with sudden force peaks can be avoided.

Particularly preferably, the ramp ball has a diameter D and, in the long position, a maximum insertion depth t _L in the ramp track and / or in the counter-ramp track, where 0.05 ≦ t _L / D ≦ 0.40, in particular 0.10 ≦ t _L / D ≦ 0.30, preferably 0.15 ≦ t _L / D ≦ 0.20, and more preferably t _L / D = 0.17 ± 0.02 applies. With such a depth of immersion, a secure support of forces can be achieved in the long position with closed disc brake.

In particular, the ramp ball has a diameter D and, in the short position, has a maximum insertion depth t _K in the ramp track and / or in the counter-ramp track, where 0.25 ≦ t _K / D ≦ 0.40, in particular 0.27 ≦ t _K / D ≦ 0.35, preferably 0.29 ≦ t _K / D ≦ 0.30, and more preferably t _K / D = 0.27 ± 0.02. The immersion depth in the short position is in particular significantly lower than that half diameter of the ramp ball. The extension of the ramp path and / or the counter-ramp path in the circumferential direction can thereby be reduced and / or used for a greater immersion depth in the long position. Here, the knowledge is exploited that in the short position, which corresponds in particular to the open position of the disc brake, hardly supported forces occur and a correspondingly low insertion depth can be provided in the short position in favor of increased immersion depth in the long position.

Preferably, it is provided that the ramp ball has a diameter D and in the short position, the intermediate surface and the counter-interface are spaced by a minimum distance a, wherein 0.0005 ≤ a / D ≤ 0.0050, in particular 0.0010 ≤ a / D ≤ 0.0045, preferably 0.0015 ≤ a / D ≤ 0.0040, and more preferably 0.0020 ≤ a / D ≤ 0.0035. A striking of the ramp seat on the counter ramp seat on the intermediate surface and the counter-intermediate surface in the short position can be safely avoided.

The invention further relates to a disc brake, in particular for braking a ring gear of a provided between a drive shaft of an automotive engine and a pulley for driving ancillaries planetary gear, with at least one brake shoe for braking a brake disc, an electrically operable Betätigungsaktor for pivoting a brake lever and a ramp system, the As described above and can be developed further, for converting the pivotal movement of the brake lever in an axial displacement of the at least one brake shoe. Due to the fact that the ramp edge and counter ramp edge are chamfered against the radial plane, it is possible for the material forming the ramp track and the counter-ramp track to partly follow the ramp gradient of the ramp base or counter ramp base, so that at the same ramp pitch and the same translation in the long position greater immersion depth of the ramp ball in the ramp path and the Gegenrampenbahn can result, allowing a secure support of higher forces in the closed position of the disc brake with low space requirement.

The invention further relates to a pulley arrangement, in particular for connection to a crankshaft of an internal combustion engine of a motor vehicle, with a pulley for driving ancillaries, a ring gear having a ring gear for transmitting torque from a drive shaft, in particular crankshaft of an internal combustion engine of a motor vehicle, to the pulley, and a disc brake, which may be formed and further developed as described above, for braking the ring gear via a brake disc connected to the ring gear. Due to the fact that the ramp edge and counter ramp edge are chamfered against the radial plane, it is possible for the material forming the ramp track and the counter-ramp track to partly follow the ramp gradient of the ramp base or counter ramp base, so that at the same ramp pitch and the same translation in the long position greater immersion depth of the ramp ball in the ramp path and the Gegenrampenbahn can result, allowing a secure support of higher forces of the pulley assembly in the closed position of the disc brake with low space requirement.

The invention will now be described by way of example with reference to the accompanying drawings, in which the features shown below may represent an aspect of the invention both individually and in combination. Show it:

1 : a schematic perspective view of a disc brake,

2 : A sectional side view of a ramp system for the disc brake off 1 in a short position,

3 : a sectioned side view of the ramp system 2 in a long position,

4 : a schematic developed view of the ramp system 2 .

5 : a schematic developed view of the ramp system 3 and

6 : a schematic perspective view of a part of the ramp system from 2 ,

As in 1 the disc brake can be shown 10 a first brake shoe 12 have, over several first spring elements 14 on a support piece 16 is relatively movably supported in the axial direction. In addition, a second brake shoe 18 provided, which has several second spring elements 20 on the support piece 16 is relatively movably supported in the axial direction. The brake shoes 12 . 18 each have a wear-affected friction lining 22 on to between the brake shoes 12 . 18 to brake a brake disc, not shown frictionally. With the help of an actuatable by a Betätigungsaktor brake lever 24 can use a ramp system 26 the first brake shoe 12 against the spring force of the first spring elements 14 and the second brake shoe 18 against the Spring force of the second spring elements 20 be moved towards each other in the axial direction to the disc brake 10 close.

This in 2 illustrated ramp system has a via an axial ball bearing 28 supported ramp seat 30 on top of the ramp balls 32 with a diameter D about an axis of rotation 34 relative to a counter ramp seat 36 is rotatable. The brake lever 24 is this with the ramp seat 30 rotatably coupled. The ramp ball 32 is in one of the ramp seat 30 trained ramp track 38 and in one of the counter ramp seat 36 trained counter ramp train 40 guided. In the in 2 shown short position of the ramp system 26 is the ramp ball 32 as far as possible into the ramp track 38 and in the opposite ramp path 40 immersed so that itself for the ramp system 26 a short axial extent in the direction of the axis of rotation 34 results. In the in 3 shown elongated position of the ramp system 26 is the ramp ball 32 as far as possible the ramp slope of the ramp track 38 and the counter ramp train 40 followed and out of the ramp 38 and the counter ramp train 40 Something emerged, leaving for the ramp system 26 a long axial extent in the direction of the axis of rotation 34 results. The ramp seat 30 and the counter ramp seat 36 are designed symmetrically on the sides facing each other in particular symmetrical.

As in 4 shown has the ramp track 38 one to the counter ramp seat 36 pointing ramp edge 42 on. Max far away from the counter ramp seat 36 forms the ramp track 38 a ramp ground 44 out. Accordingly, the Gegenrampenbahn 40 one to the ramp seat 30 pointing counter ramp edge 46 on. At maximum distance from the ramp seat 30 forms the counter ramp path 40 a counter ramp ground 48 out. The ramp ball 32 dives in the illustrated short position with an immersion depth t _K in the ramp path 38 and in the opposite ramp path 40 one. The immersion depth t _K is from the edge of the ramp 46 to the bottom of the ramp 44 or from the counter ramp edge 46 to the counter ramp ground 48 measured substantially perpendicular to a ramp plane surface, that of the ramp track 38 or the Gegenrampenbahn 40 forming material is formed. Subsequent ramp tracks 38 are over an interface 50 connected while subsequent counter ramp paths 40 over a counter-surface 52 connected to each other. The slope and arrangement of the interface 50 and the counter-interface 52 are chosen such that the interface 50 and the counter-interface 52 are arranged at least in a predominant portion substantially parallel to each other and in the illustrated short position have a minimum distance a to each other.

In the In 5 shown elongated position of the ramp system 26 the ramp ball arrives 32 at a circumferential end of the ramp track 38 or the counter ramp path 40 in contact with a ramp outlet area 54 the ramp track 38 and a counter ramp exit area 56 the counter ramp train 40 , This leaves for the ramp ball 32 in the long position an immersion depth t _L , the safe support when closing the disc brake 10 allows occurring forces. For this purpose, the ramp ground 44 and the counter ramp ground 48 opposite to a perpendicular to the axis of rotation 34 extending radial plane a slope of approximately α = 23 °, while the ramp edge 42 and the counter ramp edge 46 relative to the radial plane has a slope of about β = 17 °.

In 6 is an example of the ramp seat 36 shown in perspective. Through the course of the ramp track 38 in the circumferential direction can affect the interface 50 give a substantially trapezoidal or triangular design.

LIST OF REFERENCE NUMBERS

10

 disc brake

12

 first brake shoe

14

 first spring element

16

 support piece

18

 second brake shoe

20

 second spring element

22

 friction lining

24

 brake lever

26

 ramp system

28

 Axialkugellager

30

 ramp seat

32

 ramp ball

34

 axis of rotation

36

 Counter-ramp seat

38

 ramp rides

40

 Counter-ramp rail

42

 ramp edge

44

 ramp reason

46

 Counter-ramp edge

48

 Counter-ramp base

50

 interface

52

 Against interface

54

 Ramp-down area

56

 Against ramp-down area

t _K

 Immersion depth short position

t _L

 Immersion depth

a

 minimum distance

D

 Diameter ramp ball

α

 Slope Rampengrund / Gegenrampengrund

β

 Gradient ramp edge / counter ramp edge

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012215278 A1 [0002]

Claims (8)

Ramp system for converting a rotational movement into a linear movement for the operation of a disc brake ( 10 ), in particular for braking a ring gear of a connected between a pulley for driving ancillary components of a motor vehicle and a drive shaft of a drive motor of a motor vehicle planetary gear, with a ramp seat ( 30 ), whereby the ramp seat ( 30 ) via in each case an intermediate surface ( 50 ) circumferentially interconnected ramp tracks ( 38 ), one to the ramp seat ( 30 ) between a short position and a longitudinal position for changing the axial extension of the ramp system ( 26 ) relative to a rotation axis ( 34 ) rotatable counter-ramp seat ( 36 ), whereby the counter ramp seat ( 36 ) via a respective counter-interface ( 52 ) in the circumferential direction interconnected Gegenrampenbahnen ( 40 ), one each in the ramp path ( 38 ) and the counter ramp path ( 40 ) guided ramp ball ( 32 ), whereby the ramp track ( 38 ) on her to the counter ramp seat ( 36 ) pointing ramp edge ( 42 ) with respect to a perpendicular to the axis of rotation ( 34 ) extending radial plane a smaller slope than at its from the Gegenrampensitz ( 36 ) pointing away ramp ground ( 44 ) and / or the counter-ramp path ( 40 ) at her to the ramp seat ( 30 ) pointing counter ramp edge ( 46 ) relative to the radial plane, a smaller pitch than at its from the ramp seat ( 30 ) pointing away counter ramp ground ( 48 ), wherein the ramp edge ( 42 ) and / or the counter ramp edge ( 46 ) are bevelled against the radial plane by an angle. Ramp system according to claim 1, characterized in that the intermediate surface ( 50 ) and the counter-interface ( 52 ) are beveled at an angle in at least a partial region against the radial plane and extend in the tapered region substantially parallel to each other. Ramp system according to claim 1 or 2, characterized in that the ramp track ( 38 ) a ramp exit area ( 54 ) for braking the ramp ball ( 32 ) in the circumferential direction in the longitudinal position and / or the Gegenrampenbahn ( 40 ) a Gegenrampenauslaufbereich ( 56 ) for braking the ramp ball ( 32 ) in the circumferential direction in the elongated position. Ramp system according to one of claims 1 to 3, characterized in that the ramp ball ( 32 ) a diameter D and in the long position a maximum immersion depth t _L in the ramp track ( 38 ) and / or in the Gegenrampenbahn ( 40 ), wherein 0.05 ≦ t _L / D ≦ 0.40, in particular 0.10 ≦ t _L / D ≦ 0.30, preferably 0.15 ≦ t _L / D ≦ 0.20 and more preferably t _L / D = 0.17 ± 0.02 applies. Ramp system according to one of claims 1 to 4, characterized in that the ramp ball ( 32 ) a diameter D and in the short position a maximum immersion depth t _K in the ramp track ( 38 ) and / or in the Gegenrampenbahn ( 40 ), wherein 0.25 ≦ t _K / D ≦ 0.40, in particular 0.27 ≦ t _K / D ≦ 0.35, preferably 0.29 ≦ t _K / D ≦ 0.30 and particularly preferably t _K / D = 0.27 ± 0.02 applies. Ramp system according to one of claims 1 to 5, characterized in that the ramp ball ( 32 ) has a diameter D and in the short position, the intermediate surface ( 50 ) and the counter-interface ( 52 ) are spaced apart by a minimum distance a, where 0.0005 ≦ a / D ≦ 0.0050, more preferably 0.0010 ≦ a / D ≦ 0.0045, preferably 0.0015 ≦ a / D ≦ 0.0040, and especially preferably 0.0020 ≤ a / D ≤ 0.0035 applies. Disc brake, in particular for braking a ring gear of a provided between a drive shaft of an automotive engine and a pulley for driving ancillaries planetary gear, with at least one brake shoe ( 12 . 18 ) for braking a brake disc, an electrically operable Betätigungsaktor for pivoting a brake lever ( 24 ) and a ramp system ( 26 ) according to one of claims 1 to 6 for the conversion of the pivoting movement of the brake lever ( 24 ) in an axial displacement of the at least one brake shoe ( 12 . 18 ). Pulley arrangement, in particular for connection to a crankshaft of an internal combustion engine of a motor vehicle, with a pulley for driving ancillaries, a ring gear having a ring gear for transmitting torque from a drive shaft, in particular crankshaft of an internal combustion engine of a motor vehicle, to the pulley, and a disc brake ( 10 ) according to claim 7 for braking the ring gear via a brake disc connected to the ring gear.

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