|Title of Invention||
AN ADJUSTING DEVICE FOR ADJUSTING THE FRICTION FACE WEAR ON THE BRAKE LINING AND BRAKE DISK OF A PNEUMATICALLY ACTUATED DISK BRAKE
|Abstract||The invention relates to an adjusting device for adjusting the wear of the friction surface on the brake lining and brake disc of a pneumatic disc brake, which has a clamping device that is actuated by a rotary lever and that can be preferably inserted into a rotary spindle of the disc brake. According to the invention, a respective anti-friction body is positioned on both axial sides of a drive element such as a control fork, one of said bodies being configured as a ramp coupling (9) with a freewheeling function. The ramp coupling has coupling bushes (10, 11) and clamping balls (12) and the coupling bush (11) on the driven side is supported on a sprung sleeve (14) for a pretensioning spring (15). A coupling-type conical seat (23, 24) is configured between the coupling bush (11) and the sprung sleeve (14).|
|Full Text||WO 2006/015782 PCT/EP2005/008403
Adjusting device for a pneumatically actuated disk
The invention relates to an adjusting device for a pneumatically actuated disk brake, according to the preamble of claim 1.
A first adjusting device is known from DE 40 34 165, reference being made to the full contents of this document. In particular, the adjusting device of the invention is likewise suitable for a disk brake which is actuated by compressed air, in particular in a sliding caliper design, as is shown in this document. Moreover, they can also be used, however, in fixed caliper or pivoting caliper disk brakes which are actuated by compressed air.
Pneumatically actuated disk brakes of this type now belong to the standard equipment of heavy commercial vehicles, where they replace the previously customary drum brakes more and more.
Disk brakes of this type require a mechanical transmission means in order to generate the required brake application of force, as the force of the pneumatically loaded brake cylinders is limited on account of the pressure level (currently approximately 10 bar) and the limited overall size of the brake cylinders. In the pneumatically actuated disk brakes which are known at present, transmission ratios are found between 10:1 and 20:1 which are realized by means of an eccentrically mounted rotary lever in the generic prior art.
The piston strokes of the brake cylinders are between 50 and 75 mm, and this results in brake application paths for pressing the brake linings against the brake disk of approximately 4 mm.
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The friction material thickness of the brake linings lies in the region of 20 mm. As two linings are installed, the result is therefore a wear travel of approximately 40 mm, without taking the disk wear into consideration. This travel is greater by a multiple than the abovementioned brake application travel. There is therefore the necessity to adjust the brake by means of a device, in a manner which corresponds to the lining wear.
DE 40 34 165 Al achieves this by means of an automatically operating wear adjusting means having a freewheel and an overload coupling (see, for example, fig. 5 of this document) . This achieves a situation where what is known as the air play (this means the gap between the brake linings and the brake disk in the non-actuated state) is kept constant independently of the wear state and wear behavior of the brake linings.
Furthermore, DE 40 34 165 Al proposes to arrange the adjusting device concentrically in the hollow space of a threaded ram (a threaded spindle) and to drive it from the brake lever eccentrically via a drive element (switching finger).
During braking, the brake lever which is coupled to the piston rod of the brake cylinder performs a rotary movement. Before the rotary movement of the rotary lever is introduced into the adjusting device via the coupling mechanism of the adjusting means (for example, switching fork and switching finger), what is known as an idle travel has to be overcome. This travel is critical for the magnitude of the air play, as the adjusting means is not activated during this movement and the travel of the pressure pistons therefore represents the air play. After this idle travel is overcome, the adjusting device is set into a rotary movement and an adjusting process is initiated by the coupling to the threaded tube.
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However, this is only the case when the air play is too great. If the air play has the correct size, the brake linings come into contact with the brake disk at the same time as the switching fingers come into contact with the switching fork of the adjusting device, and a rotation of the threaded tube is no longer possible on account of the high frictional force which is caused by this in the thread.
Nevertheless, the brake lever is rotated further, as a result of the deformation of the component (linings, caliper, mechanical means) which is situated in the force flow, and a rotary movement is also initiated at the adjusting device, furthermore, on account of the direct coupling of the switching fork to the brake lever.
In order that the adjusting device is not damaged, it has to be equipped with what is known as the overload coupling. In the case of the generic prior art (fig. 5 of the generic document) , this is ensured by a ball ramp coupling which unlatches if a defined torque is exceeded.
A further basic component of the adjusting device is the directional coupling, what is known as a clamping roller freewheel in the case of the adjusting device which is described in the above text. This freewheel achieves a situation where the adjusting device can be rotated by the brake lever only in the brake application direction.
During a lining change, the wear adjusting means has to be rotated back into the initial position again. During resetting, the adjusting device has to be rotated counter to the locking direction of the freewheel, which is made possible by the overload coupling which unlatches at a defined torque. An unlimited return
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rotational angle is possible as a result of the "overrolling function".
In addition to other components, the adjusting device which has been described in the above text therefore necessarily has a clamping roller freewheel and an overload coupling. In order to function reliably, the clamping roller freewheel requires a very accurately manufactured mating running face and a precisely manufactured press fit.
It has therefore been proposed in generic DE 197 29 024 Cl to combine the unidirectional rotational coupling and the overload coupling to form a combined unidirectional rotary and overload coupling system. Nevertheless, there is also a requirement for a further reduction in the manufacturing costs of this solution.
Against this background, it is the object of the invention to develop the generic adjusting device in such a way that it can be manufactured with as few components as possible and inexpensively with a low processing expenditure. In addition, optimization of the function and service life is preferably also aimed for.
The invention achieves this object by way of the subject matter of claim 1.
Advantageous refinements of the invention are specified in the subclaims.
A basic principle of the adjusting device is again a combination of the freewheel and the overload coupling in one functional unit which is configured here, however, to be particularly inexpensive, robust and functionally reliable, in particular by means of a conical seat as an inexpensive failsafe functional element.
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In the following text, the invention will be described in greater detail using one preferred exemplary embodiment with reference to the drawing, in which:
fig. 1 shows a section through an adjusting device according to the invention.
Fig. 1 shows an adjusting device which, like the adjusting devices of DE 197 29 024 Cl, can be introduced into a surrounding hollow rotary spindle, relative to which it can be displaced axially but cannot be rotated.
The adjusting device has a central spindle 1 which serves as an axle and extends over the entire length of the adjusting device. Said spindle 1 ends, in its region which protrudes outward out of the rotary spindle and the brake caliper, in a drive journal 2 having a profiling 3, which drive journal 2 allows the spindle 1 to be rotated back during a lining change, in order to reset the rotary spindle for a lining change by the amount of wear of the brake linings.
A star-shaped driver 4 is arranged at the opposite end of the spindle 1, which star-shaped driver 4 is designed for engaging into an axially extending internal profiling (at least one groove) of the surrounding rotary spindle (not shown here), with the result that, during revolutions of the spindle 1 and the star-shaped driver 4 which is fastened to the latter, the surrounding internally hollow rotary spindle which is screwed into a further element such as a bridge is also rotated, with the result that it moves axially parallel to the brake disk axis and advances a brake lining axially in the direction of the brake disk for adjusting brake lining wear.
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The drive journal 2 is adjoined by a collar 27 of the spindle, on which a bearing bush 5 is supported which is shaped concavely on its side which faces away from the collar 27 and carries a cardanic bearing plate 7.
The bearing plate serves as one bearing bush of a first roller bearing arrangement 22, of a roller bearing, in particular a ball bearing, having bearing elements, in particular balls 6, the further bearing bush of which is configured as a spacer sleeve 8 having a collar 21 and a cylindrical projection 17 with a relatively smaller diameter with respect to the collar 21.
By way of its projection 17, the spacer sleeve 8 reaches through a further roller bearing arrangement, a combined freewheel and overload coupling device 9 which has two coupling bushes 10, 11 which serve as coupling bushes of a ball ramp coupling having bearing elements, in particular having balls 12, a torsion spring 13 being seated here between the two coupling bushes 10, 11 and connecting the latter, concentrically on the inside with respect to the ball ramp coupling and the balls and concentrically on the outside with respect to a cylindrical projection 17 of the spacer sleeve 8.
The drive-side coupling bush 10 carries a drive projection 20, for example in the manner of a switching fork, in which, for example, a projection of the rotary lever of the disk brake acts, in order to realize a drive of the adjusting device during brake operations.
In contrast, the output-side coupling bush 11 is supported via an internal conical seat 23 on an external cone 24 of a spring sleeve 14 which accommodates a prestressing spring 15 which is supported with one end on the star-shaped driver 4 and with its other end in an axial end region 16 of the spring sleeve 14.
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The freewheel function and the overload coupling are thus combined in a manner which is optimized in terms of installation space, the complete function of the freewheel and the overload coupling being preserved satisfactorily, however.
In its region which faces the star-shaped driver, the spring sleeve 14 has an external profiling 18 which is shaped like the external profiling 19 of the star-shaped driver 4 and likewise engages in the inner grooves of the surrounding rotary spindle.
In the following text, the function of this adjusting device will be described in greater detail.
The prestressed pre-stressing spring 15 presses the spring sleeve 14 with its end side against the spacer sleeve 8.
The length of the spacer sleeve 8 is defined in such a way that the balls 6 and the coupling bushes 10, 11 are not loaded by the spring force in the rest state of the adjusting device.
The play in the coupling is compensated for by the torsion spring 13 which rotates the two coupling halves or coupling bushes 10, 11 in the locking direction. This achieves a situation where manufacturing tolerances have no influence on the response behavior of the overload coupling and an exact, delay-free response of the adjusting device is ensured.
In the rest state, the force of the prestressing spring 15 is guided by the spring sleeve 14 on the end side into the spacer sleeve 8 and from the latter via the first roller bearing 22, preferably an axial ball bearing, into the cardanically shaped bearing plate 7. The force flow is finally guided via the convexly shaped bearing bush 5 into the adjusting device axle
and is closed via the star-shaped driver 4 at the other end of the axle or spindle 1.
After the above-described idle travel has been overcome, the rotary movement of the lever of the disk brake at the drive element 20 (for example, a switching fork which is driven by a journal of the rotary lever) is introduced into the adjusting device.
The movement is transmitted by the drive element 20 to the drive-side coupling bush 10 which is integrally formed in one piece here.
The latter transmits the movement to the balls 12 which are mounted in each case on the drive side and output side in ramp-shaped raceways 25, 26.
As the two coupling halves 10, 11 are pre-stressed with respect to one another via the torsion spring 13, they are pressed axially apart from one another.
Here, the output-side coupling bush 11 is pressed with the integrally formed internal conical seat 23 against the external cone 24 of the spring sleeve 14, and the drive-side coupling bush 10 is pressed with the end side against the collar 21 of the spacer sleeve 8.
The frictional moment of this conical coupling is
adapted in such a way that there is a self-locking
action in interaction with the ball ramp geometry of
the two coupling bushes.
This ensures that the rotary movement is introduced by the drive element via the two coupling bushes 10, 11, the conical seat (elements 23, 24) and the spring sleeve 14 into the threaded tube or the surrounding threaded spindles, and an adjusting operation is carried out.
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Furthermore, it is ensured that, during locking of the threaded tube when the linings come into contact with the brake disk, the two coupling bushes 10, 11 can be pressed apart from one another counter to the force of the prestressing spring 15 and the overload protective function or overload coupling function is ensured.
The response moment of the overload function can be set in an accurate and simple manner via the magnitude of the prestressing spring force and the pitch angle of the ball ramp raceways 25, 26.
It is necessary for correct functioning that the response moment of the overload function has a defined magnitude. In order to protect the drive elements, it is favorable if the further rolling moment decreases after the response of the overload function. This can be implemented very simply and clearly by different pitch angles of the ball ramp raceways 24, 25.
The freewheel function which is necessary in order to compensate for the lining wear is ensured by the fact that, during reversing, the balls are moved on the ramp contour of the raceways 24, 25 so as to run down the latter and no locking of the coupling bushes 10, 11 in conjunction with the conical seat is possible.
As a result of the prestressing with the torsion spring 13, the two coupling halves 10, 11 are opened only until the force flow in the conical seat is smaller than the force of the torsion spring 13 which counteracts it, as it were.
This achieves a situation where the freewheel function is practically without play, and therefore a very direct and exact response is achieved.
A further requirement of the adjusting device is the possibility of reversing counter to the locking action
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of the freewheel during the lining change. This function is brought about in the following manner:
During reversing, the coupling halves 10, 11 are pressed apart until the balls 12 reach the end of the ball ramp raceway. Here, the pitch angle of the ball ramp raceways 25, 26 changes in such a way and to such an extent that there is no self-locking action of the ball ramp coupling in conjunction with the conical seat in this case.
As a result, the spring sleeve 14 rotates when the
frictional moment in the conical seat is overcome, and
the threaded tube therefore rotates counter to the
locking direction of the freewheel.
In comparison with the prior art, this arrangement leads to some noticeable advantages.
First of all, a very small number of individual parts are required, which leads to low costs and relatively simple assembly.
In addition, the individual parts which are used are configured in such a way that they can be manufactured inexpensively, substantially by shaping without cutting. In addition, they are of entirely robust configuration and are therefore particularly functionally reliable.
As the balls 12 move on defined ball raceways 24, 25, clear functional behavior is ensured.
In addition, the adjusting device ensures a low hysteresis in the functional behavior, as all the moving parts are mounted on ball bearings.
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In addition, on account of the great rolling angle of the balls 12, uncontrolled overrolling of the balls cannot occur in the overload coupling.
The constant functional behavior which can be achieved during the entire service life is also advantageous, as possible wear has scarcely no effect on the force conditions .
Finally, the great adaptability as a result of many individual parameter setting possibilities is also to be mentioned as advantageous.
WO 2006/015782 PCT/EP2005/008403
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List of Designations
2 Drive journal
4 Star-shaped driver
5 Bearing bush
6 Ball bearing
7 Bearing plate
8 Spacer sleeve
9 Freewheeling and overload coupling device
10, 11 Coupling bushes
13 Torsion spring
14 Spring sleeve
15 Prestressing spring
16 End region
17, 20 Proj ection
18, 19 External profiling
22 First roller bearing
23 Conical seat
24 External cone
25, 26 Raceways
WO 2006/015782 PCT/EP2005/008403
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1. An adjusting device for adjusting the friction
face wear on the brake lining and brake disk of a
pneumatically actuated disk brake which has a brake
application device which is actuated by a rotary lever
and can be introduced preferably into a rotary spindle
of the disk brake,
a) in each case one rolling body arrangement being
arranged axially on both sides of a drive element
such as a switching fork (20), of which rolling
body arrangements one is configured as a roller
bearing (22) and one is configured as a ball ramp
coupling (9) with a freewheeling function,
b) the ball ramp coupling (9) having a drive-side
coupling bush (10) which is arranged axially
between the rolling body arrangements and an
output-side coupling bush (11), and wedging balls
characterized in that
c) the output-side coupling bush (11) is supported on
a spring sleeve (14) for a prestressing spring
d) a coupling-like conical seat (23, 24) is formed
between the output-side coupling bush (11) and the
spring sleeve (14).
2. The adjusting device as claimed in claim 1,
characterized in that the drive bush (10) and the
output bush (11) are stressed with respect to one
another by way of a torsion spring (13).
3. The adjusting device as claimed in one of the
preceding claims, characterized in that the torsion
spring (13) is arranged concentrically with respect to
the drive bush (10) and with respect to the output bush
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4. The adjusting device as claimed in one of the
preceding claims, characterized in that the two
coupling bushes (10, 11) are held without load by a
spacer sleeve (8) in the rest position.
5. The adjusting device as claimed in one of the
preceding claims, characterized in that the length of
the spacer sleeve (8) is defined in such a way that the
balls (6) of the first rolling body arrangements (22)
and the coupling bushes (10, 11) are not loaded by the
spring force of the prestressing spring (15) in the
rest state of the adjusting device.
6. The adjusting device as claimed in one of the
preceding claims, characterized in that a predefined
response force of the coupling bushes (10, 11) is
generated by the prestressing spring (14) .
7. The adjusting device as claimed in one of the
preceding claims, characterized in that the adjusting
device is mounted by means of a bearing plate (7) of
8. The adjusting device as claimed in one of the
preceding claims, characterized in that the frictional
moment of the conical seat (23, 24) is selected in such
a way that there is a self-locking action in
interaction with the ball ramp geometry of the two
9. The adjusting device as claimed in one of the
preceding claims, characterized in that the free
wheeling function which is necessary in order to
compensate for the lining wear is realized by the fact
that, during reversing, the balls are moved on the ramp
contour of the raceways (24, 25) so as to run down the
latter and no locking of the coupling bushes (10, 11)
in conjunction with the conical seat is possible.
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10. The adjusting device as claimed in one of the preceding claims, characterized in that the conical seat is configured in such a way, and is adapted to the raceways (25, 26) of the ball ramp coupling, that, during reversing, there is no self-locking of the ball ramp coupling in conjunction with the conical seat.
The invention relates to an adjusting device for adjusting the wear of the friction surface on the brake lining and brake disc of a pneumatic disc brake, which has a clamping device that is actuated by a rotary lever and that can be preferably inserted into a rotary spindle of the disc brake. According to the invention, a respective anti-friction body is positioned on both axial sides of a drive element such as a control fork, one of said bodies being configured as a ramp coupling (9) with a freewheeling function. The ramp coupling has coupling bushes (10, 11) and clamping balls (12) and the coupling bush (11) on the driven side is supported on a sprung sleeve (14) for a pretensioning spring (15). A coupling-type conical seat (23, 24) is configured between the coupling bush (11) and the sprung sleeve (14).
00442-kolnp-2007-international search authority-1.1.pdf
0442-kolnp-2007 correspondence others.pdf
0442-kolnp-2007 international publication.pdf
0442-kolnp-2007 international search authority report.pdf
0442-kolnp-2007 priority document.pdf
442-kolnp-2007-granted-reply to examination report.pdf
442-kolnp-2007-granted-translated copy of priority document.pdf
442-KOLNP-2007-PETITION UNDER SECTION 8(1).pdf
442-KOLNP-2007-REPLY EXAMINATION REPORT 1.1.pdf
442-KOLNP-2007-REPLY TO EXAMINATION REPORT-1.1.pdf
442-KOLNP-2007-REPLY TO EXAMINATION REPORT.pdf
|Indian Patent Application Number||442/KOLNP/2007|
|PG Journal Number||18/2010|
|Date of Filing||07-Feb-2007|
|Name of Patentee||KNORR-BREMSE SYSTEME FUR NUTZFAHRZEUGE GMBH|
|Applicant Address||MOOSACHER STR. 80, 80809 MUNCHEN|
|PCT International Classification Number||F16D 65/38|
|PCT International Application Number||PCT/EP2005/008403|
|PCT International Filing date||2005-08-03|