Internally ventilated brake disk

Abstract

An internally ventilated brake disk for a disk brake, includes two friction disks, which are arranged adjacent to each other and which are connected to each other by radially extending, regularly arranged webs. The webs extend from an outer peripheral edge to an inner peripheral edge of the friction disks and the friction disks are connected by the webs in such a way that intermediate spaces thereof form cooling channels of equal size, through which cooling air can flow and which are divided by further, shorter webs in such a way that at least one shorter web is located centrally between the webs in a radial region closer to the inner peripheral edge of the friction disks. Outward from the shorter web in the radial direction, the cooling channels are divided into at least three flow channels in that, in each cooling channel, two first further shorter webs are arranged at an offset to each shorter web radially outwardly and in the peripheral direction. The friction disk directed toward a brake disk hub is extended radially inward from each of the shorter webs and is provided with a bore in the axial direction at the height of a collar of the brake disk hub, which bore is used to hold a rivet, which fastens the friction disk to the brake disk hub.

Claims

1. An internally ventilated brake disk for a disk brake, comprising: two adjacent friction disks, which are connected to one another by radially running, regularly arranged webs, wherein the webs run from an outer-circumference periphery to an inner-circumference periphery of the friction disks, the friction disks are connected by the webs such that interspaces thereof form identically sized cooling channels through which cooling air is flowable, the cooling channels are subdivided by further, relatively shorter webs such that, in a radial region relatively close to the inner-circumference periphery of the friction disks, at least one relatively shorter web is located centrally between the webs, wherein, directed radially outward from the relatively shorter web, the cooling channels divide up into at least three flow channels, two first further relatively shorter webs being arranged in each cooling channel, in a state in which they are offset radially outward in relation to each relatively shorter web in the circumferential direction, starting from each of the relatively shorter webs and directed radially inward, the friction disk, which is directed toward a brake-disk hub, is extended and, level with a collar of the brake-disk hub, is provided in the axial direction with a bore, the bore serves to accommodate a rivet, which fastens the friction disk on the brake-disk hub, the friction disk, which is directed toward the brake-disk hub, has an axially directed depression for supporting the collar of the brake-disk hub, and the internal diameter of the depression is greater than an external diameter of the collar, and therefore the friction disk and the brake-disk hub are centered in relation to one another exclusively by way of the rivets.

2. The internally ventilated brake disk as claimed in claim 1, further comprising: a bore in the collar of the brake-disk hub for accommodating the rivet, said bore corresponding to the bore for accommodating the rivet, has a planar depression at its end which is directed away from the friction disk, said planar depression serving to accommodate a manufactured head of the rivet at least to some extent.

3. The internally ventilated brake disk as claimed in claim 2, wherein the radial distances between the relatively shorter webs and the two first further relatively shorter webs within the cooling channels give rise to a circular-ring band which is free of relatively shorter webs, has a circle center point in the center of the brake disk and is interrupted exclusively by the webs.

4. The internally ventilated brake disk as claimed in claim 1, wherein the depression fully accommodates the collar of the brake-disk hub.

5. The internally ventilated brake disk as claimed in claim 1, wherein the planar depression of the collar of the brake-disk hub fully accommodates the manufactured head of the rivet.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a three-dimensional illustration of a brake disk according to an embodiment of the invention, with a view of the brake-disk hub.

(2) FIG. 2 shows the brake disk according to FIG. 1 in an enlarged partial section (the section plane contains the axis of rotation), in a state in which it has been rotated in relation to FIG. 1 about a vertical axis located in the drawing plane, in the region where the friction disk is fastened on the brake-disk hub.

(3) FIG. 3 shows a yet further-enlarged partial view of a rivet from FIG. 2 rotated through 180 degrees.

(4) FIG. 4 is a plan view of the hub side of the brake disk.

(5) FIG. 5 is a plan view of part of the rear side of the brake disk rotated through 180 degrees in relation to FIG. 4, the connection between two friction disks via webs being illustrated by virtue of part of the friction disk being cut away.

DETAILED DESCRIPTION OF THE DRAWINGS

(6) The brake disk 1 illustrated in the figures has a brake-disk hub 3 and a friction ring 2 and is provided for installation on a wheel hub (not shown) in order to rotate therewith, during operation, about the axis of rotation D. The single-piece, internally cooled friction ring 2, which is produced from gray cast iron, includes two friction disks 2a, 2b with webs 2c which are located therebetween, and connect the friction disks to one another, for cooling-air guidance. The annular friction disk 2a, which is located closer to the brake-disk hub 3 in the axial direction, i.e. as seen in the direction of the axis of rotation D, extends radially R (as seen in relation to the axis of rotation D), by way of a so-called fastening extension 9, a certain amount further in the direction of the axis of rotation D than the other friction disk 2b, which is further away from the brake-disk hub 3 in the axial direction.

(7) In the region of overlap between the aforementioned fastening extension 9 of the friction disk 2a and a collar 3b, which projects outward in the radial direction R from the free end of the lateral surface 3a of the brake-disk hub 3, said lateral surface being circular-cylindrical in relation to the axis of rotation D, the brake-disk hub 3 is connected to the friction disk 2a and thus to the friction ring 2, via axially extending rivets 5. In this regard, the text here (and in particular in the introductory part of the description) refers to a connection between the brake-disk hub 3 and the friction ring 2.

(8) In the lateral surface 3a of the brake-disk hub 3, and to some extent also in the base 3c of the brake-disk hub 3, cutouts 7 are distributed uniformly over the circumference of the brake-disk hub 3. The rivets 5 project into the cutouts, i.e. the rivets 5 are placed at least to some extent therein. Each of these cutouts 7, which also form reduced-wall-thickness portions 7, extends in the axial direction around the respectively associated, likewise oriented rivet 5 and serves to accommodate the latter to some extent and/or to accommodate the set rivet 5 during installation, i.e. the connection of the brake-disk hub 3 to the friction ring 2, as can be seen in the axial direction. The cutouts 7 here are essentially in the form of a semicircular cylinder and are formed in the lateral surface 3a of the brake-disk hub 3 during casting or forging, and therefore, although said lateral surface 3a is weakened in the region of the cutouts 7, it still forms a closed wall on the inside, i.e. as seen from the axis of rotation D. Of course, through-passages in the form of bores are also provided, pretty much as an extension to the cutouts 7, in the collar 3b of the brake-disk hub 3, and the rivets 5 are fitted through these. These cutouts 7 therefore allow the rivets 5 to be arranged closer to the axis of rotation D.

(9) FIG. 5 shows, on the inside of the friction disk 2a of the brake disk 1, a combination of webs 1a and relatively shorter webs 1b, 1c of the internally ventilated brake disk 1 which is repeated in a geometrically regular manner in the circumferential direction over the circular-ring surface of said friction disk. The friction disks 2a, 2b of the friction ring 2 are connected to one another via the webs 1a and the relatively shorter webs 1b, 1c, wherein the webs 1a, at the same time, bound cooling channels 20, which are repeated in a likewise geometrically regular manner in the circumferential direction over the circular-ring surfaces of the friction disks 2a, 2b. The cooling channels 20 each extend from an inner-circumference periphery 14 of the friction disks 2a, 2b at the beginning of the webs 1a as far as an outer-circumference periphery 15 of the friction disks 2a, 2b of the brake disk 1.

(10) As seen in the circumferential direction, centrally in each cooling channel 20 between the respectively equal-length webs 1a within the friction disks 2a, 2b, the shorter web 1b extends in each case from the vicinity of the inner-circumference periphery 14 of the friction disks 2a, 2b, in the direction of the outer-circumference periphery 15 of the latter, as far as a first diameter 12 of the friction disks 2a, 2b. Proceeding therefrom, two first further shorter webs 1c, which are offset in the circumferential direction in relation to the shorter web 1b within the cooling channel 20, extend further outward in the radial direction as far as the outer-circumference periphery 15, one offset to the left, and the other offset to the right. The first further shorter webs 1c divide up the cooling channels 20, in the radially outward direction from the relatively shorter web 1b, into three flow channels 1ca, 1cb, 1cc. All the webs 1a, 1b, 1c have essentially the same web width and are rounded at the front and rear. The radially outer ends of the respective webs 1a, 1c here are located on the same circle circumference in the vicinity of the outer-circumference periphery 15, and the radially inner ends of the respective webs 1a are located on the same circle circumference in the vicinity of the inner-circumference periphery 14, of the brake disk 1. Moreover, starting from each of the relatively shorter webs 1b, the friction disk 2a, which is directed toward the brake-disk hub 3, is extended in the radially inward direction and, level with the collar 3b of the brake-disk hub 3, is provided in the axial direction with a bore 21 which serves to accommodate the rivet 5, which fastens the friction disk 2a on the brake-disk hub 3. Closing heads 5d of all the rivets 5 are located on the visible side of the fastening extension 9 of the friction disk 2a, whereas the manufactured heads 5b of the rivets 5 are fully recessed in a planar depression 23 of the collar 3b of the brake-disk hub 3, as illustrated in FIG. 2. The friction disk 2a, which is directed toward the brake-disk hub 3, likewise has an axially directed depression 27, which is intended for supporting the collar 3b of the brake-disk hub 3 and of which the internal diameter is greater than an external diameter of the collar 3b. Therefore, the friction disk 2a and the brake-disk hub 3, on account of an amount of radial play 25, are centered in relation to one another exclusively by way of the rivets 5.

(11) FIG. 3 shows a view of part of a rivet 5 designed in the form of semitubular rivets, measuring 5 mm13 mm, with a manufactured head 5b and a stem 5a. In the direction of the manufactured head 5b, the rivet stem 5a is designed to be conical with an increasing diameter. In the direction of the rivet stem 5a, the manufactured head 5b has an undercut, and therefore the angle designated by a double arrow F measures essentially 88 degrees. The extent of a radius R between the cone 5c of the rivet stem 5a and the undercut of the manufactured head 5b is not defined and is established by manufacturing. The cone 5c has a length of at least 1.5 mm and at most 4 mm, the diameter of the cone 5c at the manufactured head 5b being 5.33 mm. Tests have found that this rivet geometry, along with self-centering of the rivet during the operation of setting the rivet 5, results in an advantageous contact pattern with a 100% amount of contact, which gives rise to optimum centering and force transmission. In addition, the conical rivet stem 5a and the undercut F of the manufactured head 5b provide for perfect sealing of the rivet connection and, consequently, protection against corrosive media.

(12) The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.