CA2578982A1 - Disc brake, especially for a utility vehicle - Google Patents
Disc brake, especially for a utility vehicle Download PDFInfo
- Publication number
- CA2578982A1 CA2578982A1 CA002578982A CA2578982A CA2578982A1 CA 2578982 A1 CA2578982 A1 CA 2578982A1 CA 002578982 A CA002578982 A CA 002578982A CA 2578982 A CA2578982 A CA 2578982A CA 2578982 A1 CA2578982 A1 CA 2578982A1
- Authority
- CA
- Canada
- Prior art keywords
- brake
- lugs
- spring
- disk
- sliding ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 229910000639 Spring steel Inorganic materials 0.000 claims description 2
- 238000004080 punching Methods 0.000 claims 1
- 238000013016 damping Methods 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
- F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
- F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/22655—Constructional details of guide pins
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The invention relates to a disc brake, especially for a utility vehicle, said disc brake comprising a caliper (2) which is provided with a brake disc (1) and is fixed to a brake carrier (7) by means of two fixing elements (5, 6) in such a way that it can be axially displaced in relation to the brake disc (1).
One fixing element (6) is embodied as a fixed bearing and the other (5) as a movable bearing that comprises a guiding sleeve (8) fixed in the caliper (2).
A guiding bar (10) which is connected to the brake carrier (7) in a fixed manner can be axially displaced inside said guiding sleeve, and at least one partial region of the guiding sleeve (8) is formed by a sliding ring (11) surrounding the guiding bar (10). A spring (12) is applied to the outer periphery of the sliding ring, said spring being supported on a component of the caliper (2). The inventive disk brake is embodied in such a way that the spring (12) consists of a bow (18) at least partially surrounding the sliding ring (11), and adjacent fishplates (19) which extend in the direction of the longitudinal axis of the sliding ring and are applied to certain regions of the sliding ring (11) and of the component of the caliper (2).
One fixing element (6) is embodied as a fixed bearing and the other (5) as a movable bearing that comprises a guiding sleeve (8) fixed in the caliper (2).
A guiding bar (10) which is connected to the brake carrier (7) in a fixed manner can be axially displaced inside said guiding sleeve, and at least one partial region of the guiding sleeve (8) is formed by a sliding ring (11) surrounding the guiding bar (10). A spring (12) is applied to the outer periphery of the sliding ring, said spring being supported on a component of the caliper (2). The inventive disk brake is embodied in such a way that the spring (12) consists of a bow (18) at least partially surrounding the sliding ring (11), and adjacent fishplates (19) which extend in the direction of the longitudinal axis of the sliding ring and are applied to certain regions of the sliding ring (11) and of the component of the caliper (2).
Description
Disc brake, especially for a utility vehicle The present invention relates to a disk brake, in particular for a utility vehicle, as per the preamble of claim 1.
In disk brakes of said type, the brake caliper, also referred to as a sliding caliper, is connected by means of fastening elements to the brake carrier which is attached to the vehicle. Here, guide bars engage into the brake carrier, which guide bars are guided at the other side in sliding bearings of the brake caliper in such a way as to permit an axial displacement of the brake caliper relative to the positionally fixed brake carrier. Of the sliding bearings, one is embodied as a fixed bearing with little sliding play, while the other functions as a floating bearing, as a result of which in particular production tolerances are compensated.
It is known from DE 102 48 948 Al to arrange a spring between the brake caliper, or a component which is fixed therein, and the sliding ring of the floating bearing, which spring serves to improve the wear resistance and rattle-resistance of the floating bearing. The spring in particular provides damping in the case of vibrations as they usually occur during driving operation. Here, the sliding ring and, with the latter, the guide bar are held under load in a specified position, so that disturbing rattling noises are avoided.
In the known disk brake, the spring is preferably of a meandering design and engages fully in terms of its width around the sliding ring, with the individual spring limbs also bearing against the sliding ring in regions in which axial compensation takes place, such as is necessary for compensating production tolerances or else for compensating changes in position of the guide bar relative to the guide sleeve transversely with respect to the axial movement direction of the guide bar. The axial compensating travel is however restricted to a certain extent as a result of the adjoining resilient limbs.
The present invention is therefore based on the object of further developing a disk brake of the generic type in such a way that the functioning of the floating bearing is improved.
Said object is achieved by means of a disk brake which has the features of claim 1.
As a result of said design embodiment, the travel of the required axial compensation is practically unhindered, since it is now possible to permit damping, that is to say .to position the lugs which assume the spring action, only at the point where no axial compensation takes place, that is to say perpendicularly with respect to the direction of the axial compensation.
The lugs are advantageously shaped such that the spring action is also incorporated in the axial compensation.
Here, the corresponding travel movement is damped by limbs of the lugs which are preferably of trapezoidal cross-sectional contour, with the result that the rattling mentioned in the introductory part of the description is effectively prevented.
According to an advantageous refinement of the invention, the lugs are fixedly arranged on opposite sides of the sliding ring or of the component which is fixedly connected to the brake caliper and is expediently in the form of a retaining ring.
Here, the spring can be composed of two approximately identical parts, each of which has a strap and two lugs which are attached at the end sides and, in the assembled state, bear against one another, that is to say overlap.
This permits a small initial thickness of the two spring parts which are produced from a spring steel sheet, preferably as punched parts.
Said production of the spring offers the advantage of extremely cost-effective production, it being possible in principle for the spring to initially be produced in one piece and then divided in a further production step in such a way as to produce two substantially identical half-parts.
In order to fix the spring, in particular to rotationally lock and axially secure the latter, the receptacle of the brake caliper or of the component which is fastened therein can be provided with a corresponding locking means. The latter is composed, according to a preferred refinement of the invention, of a plastic cage which is vulcanized into the component and has cut-outs for receiving the resilient lugs. The receptacles correspond in shape and dimensions to the associated lugs.
In addition to said axial compensation which is unimpeded in this respect on account of the new configuration of the spring, it is also possible in this context to provide inclination compensation without any problem when the longitudinal axis of the receptacle in the brake caliper deviates from the functional profile of the longitudinal axis of the guide bar or of the sliding ring, with both axes then being aligned at a certain angle to one another.
The spring therefore serves to provide a so-called floating bearing which, in addition to the stated damping, also permits precise, misalignment-free guidance of the guide bar in the sliding ring.
Further advantageous embodiments of the invention are characterized in the subclaims.
One exemplary embodiment of the invention is described in the following on the basis of the appended drawings, in which:
Figure 1 shows a partial longitudinal section through a disk brake according to the invention, Figure 2 shows a detail of the disk brake in a longitudinal section, Figure 3 shows a further detail of the disk brake in a plan view, Figure 4 shows a part of the detail according to figure 3 in a perspective view, Figure 5 shows a detail according to figure 2 in a perspective view, and Figure 6 shows an exemplary embodiment of a spring of the disk brake in an exploded illustration.
In disk brakes of said type, the brake caliper, also referred to as a sliding caliper, is connected by means of fastening elements to the brake carrier which is attached to the vehicle. Here, guide bars engage into the brake carrier, which guide bars are guided at the other side in sliding bearings of the brake caliper in such a way as to permit an axial displacement of the brake caliper relative to the positionally fixed brake carrier. Of the sliding bearings, one is embodied as a fixed bearing with little sliding play, while the other functions as a floating bearing, as a result of which in particular production tolerances are compensated.
It is known from DE 102 48 948 Al to arrange a spring between the brake caliper, or a component which is fixed therein, and the sliding ring of the floating bearing, which spring serves to improve the wear resistance and rattle-resistance of the floating bearing. The spring in particular provides damping in the case of vibrations as they usually occur during driving operation. Here, the sliding ring and, with the latter, the guide bar are held under load in a specified position, so that disturbing rattling noises are avoided.
In the known disk brake, the spring is preferably of a meandering design and engages fully in terms of its width around the sliding ring, with the individual spring limbs also bearing against the sliding ring in regions in which axial compensation takes place, such as is necessary for compensating production tolerances or else for compensating changes in position of the guide bar relative to the guide sleeve transversely with respect to the axial movement direction of the guide bar. The axial compensating travel is however restricted to a certain extent as a result of the adjoining resilient limbs.
The present invention is therefore based on the object of further developing a disk brake of the generic type in such a way that the functioning of the floating bearing is improved.
Said object is achieved by means of a disk brake which has the features of claim 1.
As a result of said design embodiment, the travel of the required axial compensation is practically unhindered, since it is now possible to permit damping, that is to say .to position the lugs which assume the spring action, only at the point where no axial compensation takes place, that is to say perpendicularly with respect to the direction of the axial compensation.
The lugs are advantageously shaped such that the spring action is also incorporated in the axial compensation.
Here, the corresponding travel movement is damped by limbs of the lugs which are preferably of trapezoidal cross-sectional contour, with the result that the rattling mentioned in the introductory part of the description is effectively prevented.
According to an advantageous refinement of the invention, the lugs are fixedly arranged on opposite sides of the sliding ring or of the component which is fixedly connected to the brake caliper and is expediently in the form of a retaining ring.
Here, the spring can be composed of two approximately identical parts, each of which has a strap and two lugs which are attached at the end sides and, in the assembled state, bear against one another, that is to say overlap.
This permits a small initial thickness of the two spring parts which are produced from a spring steel sheet, preferably as punched parts.
Said production of the spring offers the advantage of extremely cost-effective production, it being possible in principle for the spring to initially be produced in one piece and then divided in a further production step in such a way as to produce two substantially identical half-parts.
In order to fix the spring, in particular to rotationally lock and axially secure the latter, the receptacle of the brake caliper or of the component which is fastened therein can be provided with a corresponding locking means. The latter is composed, according to a preferred refinement of the invention, of a plastic cage which is vulcanized into the component and has cut-outs for receiving the resilient lugs. The receptacles correspond in shape and dimensions to the associated lugs.
In addition to said axial compensation which is unimpeded in this respect on account of the new configuration of the spring, it is also possible in this context to provide inclination compensation without any problem when the longitudinal axis of the receptacle in the brake caliper deviates from the functional profile of the longitudinal axis of the guide bar or of the sliding ring, with both axes then being aligned at a certain angle to one another.
The spring therefore serves to provide a so-called floating bearing which, in addition to the stated damping, also permits precise, misalignment-free guidance of the guide bar in the sliding ring.
Further advantageous embodiments of the invention are characterized in the subclaims.
One exemplary embodiment of the invention is described in the following on the basis of the appended drawings, in which:
Figure 1 shows a partial longitudinal section through a disk brake according to the invention, Figure 2 shows a detail of the disk brake in a longitudinal section, Figure 3 shows a further detail of the disk brake in a plan view, Figure 4 shows a part of the detail according to figure 3 in a perspective view, Figure 5 shows a detail according to figure 2 in a perspective view, and Figure 6 shows an exemplary embodiment of a spring of the disk brake in an exploded illustration.
Figure 1 illustrates a disk brake, in particular for a utility vehicle, which in terms of its basic construction has a brake caliper 2 which surrounds an internally-ventilated brake disk 1 which is fastened to an axle (not illustrated) of the utility vehicle.
The brake caliper 2 is connected to a brake carrier 7 of the utility vehicle so as to be axially displaceable relative to the brake disk 1.
For this purpose, two fastening elements 5, 6 are provided, of which the fastening element 5 is embodied as a floating bearing and the fastening element 6 is embodied as a fixed bearing.
The two fastening elements 5, 6 have in each case one guide sleeve 8, 9 and a guide bar 10 guided therein, with the guide sleeves 8, 9 being fixed in bores 3 of the brake caliper 2.
The guide bars 10 are screwed into the brake carrier 7 and are therefore positionally fixed relative the brake caliper 2, while the guide sleeves 8, 9 are fixedly connected to the brake caliper 2 and are therefore mounted so as to be axially displaceable on the guide bar 10 together with the brake caliper 2.
Figure 2 illustrates the guide sleeve 8 of the floating bearing 5, with the guide sleeve 8 having a sliding ring 11 which surrounds the guide bar 10.
At one end, the sliding ring 11 is surrounded by a shank guide 14 which is of sleeve-shaped form and is supported laterally against a shank 16 of the guide bar 10. Arranged at the end region situated opposite the shank guide 14 is a support ring 17 which encloses the sliding ring 11 in said end region and at the other side bears with a lip against the guide bar 10.
The floating bearing permits, for example for tolerance compensation, an axial displacement of the guide bar 10 transversely with respect to the axial displacement direction corresponding to the arrow.
In order to provide the greatest possible degree of damping of transverse movements for example in the case of vibrations, a spring 12 is provided which bears in regions against the outer face of the sliding ring 11 and, at the opposite side, against the inner wall of a retaining ring 13 which concentrically surrounds the sliding ring 11 and is placed in the bore 3 of the brake caliper 2.
According to the invention, the spring is composed of a strap which at least partially surrounds the sliding ring 11 and lugs 19 which are attached to said strap, extend in the longitudinal direction of the sliding ring 11 and bear in regions against the sliding ring 11 and against a retaining ring 13 which constitutes a component of the brake caliper 2.
Figure 3 shows the contoured spring 12 in a plan view.
It can also be seen in said figure that the spring is composed of two half-parts as illustrated individually in figure 6.
Here, each half-part has a circular-segment-shaped strap 18 whose respective ends are each adjoined by a lug 19, with the associated strap 18 forming an upper delimitation of the lugs 19.
The half-parts are dimensioned such that, in the assembled state, two lugs 19 always bear against one another, with said lugs 19 being trapezoidal in cross section, so that two edges of the outer lugs bear against the inner wall of the retaining ring 13, while the inner lugs 19 are tangent to the sliding ring 11.
The damping travel in said region is smaller than the axial compensation which takes place in one direction which is 90 offset in relation to the lugs 19.
Nevertheless, as a result of the shaping of the lugs 19, damping is also provided by the resilient lugs 19 during axial compensation.
Figure 5 illustrates an axial compensation caused by an angular misalignment, with the shank 16 deviating from an axially parallel arrangement with the retaining ring 13 which is fixed in the brake caliper 2. It can be very clearly seen here that even relatively large angular misalignments can be compensated by the spring 12 embodied according to the invention.
In order to lock the spring 12, a cage 20 which is preferably composed of plastic is provided in the retaining ring 13, which cage 20 is fixedly connected to the retaining ring 13 and has two opposing receptacles 21 in which in each case the lugs 19 of the spring 12 rest so as to be rotationally locked. Said cage 20 is preferably vulcanized in.
The brake caliper 2 is connected to a brake carrier 7 of the utility vehicle so as to be axially displaceable relative to the brake disk 1.
For this purpose, two fastening elements 5, 6 are provided, of which the fastening element 5 is embodied as a floating bearing and the fastening element 6 is embodied as a fixed bearing.
The two fastening elements 5, 6 have in each case one guide sleeve 8, 9 and a guide bar 10 guided therein, with the guide sleeves 8, 9 being fixed in bores 3 of the brake caliper 2.
The guide bars 10 are screwed into the brake carrier 7 and are therefore positionally fixed relative the brake caliper 2, while the guide sleeves 8, 9 are fixedly connected to the brake caliper 2 and are therefore mounted so as to be axially displaceable on the guide bar 10 together with the brake caliper 2.
Figure 2 illustrates the guide sleeve 8 of the floating bearing 5, with the guide sleeve 8 having a sliding ring 11 which surrounds the guide bar 10.
At one end, the sliding ring 11 is surrounded by a shank guide 14 which is of sleeve-shaped form and is supported laterally against a shank 16 of the guide bar 10. Arranged at the end region situated opposite the shank guide 14 is a support ring 17 which encloses the sliding ring 11 in said end region and at the other side bears with a lip against the guide bar 10.
The floating bearing permits, for example for tolerance compensation, an axial displacement of the guide bar 10 transversely with respect to the axial displacement direction corresponding to the arrow.
In order to provide the greatest possible degree of damping of transverse movements for example in the case of vibrations, a spring 12 is provided which bears in regions against the outer face of the sliding ring 11 and, at the opposite side, against the inner wall of a retaining ring 13 which concentrically surrounds the sliding ring 11 and is placed in the bore 3 of the brake caliper 2.
According to the invention, the spring is composed of a strap which at least partially surrounds the sliding ring 11 and lugs 19 which are attached to said strap, extend in the longitudinal direction of the sliding ring 11 and bear in regions against the sliding ring 11 and against a retaining ring 13 which constitutes a component of the brake caliper 2.
Figure 3 shows the contoured spring 12 in a plan view.
It can also be seen in said figure that the spring is composed of two half-parts as illustrated individually in figure 6.
Here, each half-part has a circular-segment-shaped strap 18 whose respective ends are each adjoined by a lug 19, with the associated strap 18 forming an upper delimitation of the lugs 19.
The half-parts are dimensioned such that, in the assembled state, two lugs 19 always bear against one another, with said lugs 19 being trapezoidal in cross section, so that two edges of the outer lugs bear against the inner wall of the retaining ring 13, while the inner lugs 19 are tangent to the sliding ring 11.
The damping travel in said region is smaller than the axial compensation which takes place in one direction which is 90 offset in relation to the lugs 19.
Nevertheless, as a result of the shaping of the lugs 19, damping is also provided by the resilient lugs 19 during axial compensation.
Figure 5 illustrates an axial compensation caused by an angular misalignment, with the shank 16 deviating from an axially parallel arrangement with the retaining ring 13 which is fixed in the brake caliper 2. It can be very clearly seen here that even relatively large angular misalignments can be compensated by the spring 12 embodied according to the invention.
In order to lock the spring 12, a cage 20 which is preferably composed of plastic is provided in the retaining ring 13, which cage 20 is fixedly connected to the retaining ring 13 and has two opposing receptacles 21 in which in each case the lugs 19 of the spring 12 rest so as to be rotationally locked. Said cage 20 is preferably vulcanized in.
List of reference symbols 1 Brake disk 2 Brake caliper 3 Bore Fastening element 6 Fastening element 7 Brake carrier 8 Guide sleeve 9 Guide sleeve Guide bar 11 Sliding ring 12 Spring 13 Retaining ring 14 Shank guide 16 Shank 17 Support ring 18 Strap 19 Lug Cage 21 Receptacle
Claims (14)
1. A disk brake, in particular for a utility vehicle, having a brake caliper which surrounds a brake disk and is fastened by means of two fastening elements to a brake carrier so as to be axially displaceable relative to the brake disk, with one fastening element being embodied as a fixed bearing and the other being embodied as a floating bearing which has a guide sleeve which is fixed in the brake caliper, with a guide bar which is fixedly connected to the brake carrier being axially moveable in said guide sleeve, and with at least a partial region of the guide sleeve being formed by a sliding ring which surrounds the guide bar, against the periphery of which sliding ring bears a spring which is supported on the other side on a component of the brake caliper, characterized in that the spring is composed of a strap which at least partially surrounds the sliding ring and of lugs which adjoin said strap, extend in the direction of the longitudinal axis of the sliding ring and bear in regions against the sliding ring and against the component of the brake caliper.
2. The disk brake as claimed in claim 1, characterized in that the strap delimits the lugs at the top.
3. The disk brake as claimed in claim 1 or 2, characterized in that the lugs are contoured so as to deviate from the shape of a circular arc in cross section.
4. The disk brake as claimed in one of the preceding claims, characterized in that the lugs are contoured so as to be trapezoidal in cross section.
5. The disk brake as claimed in one of the preceding claims, characterized in that the spring is composed of two half-parts, each of which has a strap and in each case one lug at the end sides.
6. The disk brake as claimed in one of the preceding claims, characterized in that the straps are of circular-arc-shaped form.
7. The disk brake as claimed in one of the preceding claims, characterized in that the two lugs, which face toward one another, of the two half-parts are arranged so as to bear against one another.
8. The disk brake as claimed in one of the preceding claims, characterized in that, proceeding from the strap, the lugs extend in the direction of the brake disk.
9. The disk brake as claimed in one of the preceding claims, characterized in that the spring is produced by means of punching.
10. The disk brake as claimed in one of the preceding claims, characterized in that the spring is formed from a spring steel sheet.
11. The disk brake as claimed in one of the preceding claims, characterized in that the component, against the inside of which the lugs are supported, of the brake caliper is embodied as a retaining ring which has, at the inside, a cage which is provided with receptacles for positioning the lugs.
12. The disk brake as claimed in one of the preceding claims, characterized in that the cage is composed of plastic.
13. The disk brake as claimed in one of the preceding claims, characterized in that the receptacles correspond approximately in their dimensions to the dimensions of the lugs which are placed therein.
14. The disk brake as claimed in one of the preceding claims, characterized in that the cage is vulcanized onto the inside of the retaining ring.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004042575.2 | 2004-09-02 | ||
| DE200410042575 DE102004042575B3 (en) | 2004-09-02 | 2004-09-02 | Disc brake, in particular for a commercial vehicle |
| PCT/EP2005/009371 WO2006024513A1 (en) | 2004-09-02 | 2005-08-31 | Disc brake, especially for a utility vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2578982A1 true CA2578982A1 (en) | 2006-03-09 |
Family
ID=35529577
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002578982A Abandoned CA2578982A1 (en) | 2004-09-02 | 2005-08-31 | Disc brake, especially for a utility vehicle |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP1789692A1 (en) |
| AU (1) | AU2005279274A1 (en) |
| CA (1) | CA2578982A1 (en) |
| DE (1) | DE102004042575B3 (en) |
| MX (1) | MX2007002496A (en) |
| WO (1) | WO2006024513A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8037976B2 (en) | 2006-10-24 | 2011-10-18 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Disc brake, in particular for a utility vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012006133A1 (en) * | 2012-03-26 | 2013-09-26 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake, in particular for a commercial vehicle |
| DE102015114437A1 (en) * | 2015-08-31 | 2017-03-02 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake for a commercial vehicle |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2414174C2 (en) * | 1974-03-23 | 1983-10-27 | Alfred Teves Gmbh, 6000 Frankfurt | Brake caliper guide for a partially lined disc brake |
| IT1261610B (en) * | 1993-10-14 | 1996-05-23 | Alliedsignal Freni Spa | DISC BRAKE WITH FLOATING BRACKET, AND COLUMN FOR SUCH DISC BRAKE. |
| DE10248948C5 (en) * | 2002-10-21 | 2008-07-24 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake, in particular for a commercial vehicle |
-
2004
- 2004-09-02 DE DE200410042575 patent/DE102004042575B3/en not_active Expired - Fee Related
-
2005
- 2005-08-31 MX MX2007002496A patent/MX2007002496A/en not_active Application Discontinuation
- 2005-08-31 EP EP05786277A patent/EP1789692A1/en not_active Withdrawn
- 2005-08-31 CA CA002578982A patent/CA2578982A1/en not_active Abandoned
- 2005-08-31 WO PCT/EP2005/009371 patent/WO2006024513A1/en not_active Application Discontinuation
- 2005-08-31 AU AU2005279274A patent/AU2005279274A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8037976B2 (en) | 2006-10-24 | 2011-10-18 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Disc brake, in particular for a utility vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102004042575B3 (en) | 2006-04-20 |
| EP1789692A1 (en) | 2007-05-30 |
| WO2006024513A1 (en) | 2006-03-09 |
| AU2005279274A1 (en) | 2006-03-09 |
| MX2007002496A (en) | 2007-05-11 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |