WO2010108671A1

WO2010108671A1 - Brake disk

Info

Publication number: WO2010108671A1
Application number: PCT/EP2010/001858
Authority: WO
Inventors: Heinz Aab; Tobias Braecker; Philipp Imhof; Klaus Knaup; Henrik Krause; Andreas Mehlan; Helmut Ruppert
Original assignee: Faiveley Transport Witten Gmbh
Priority date: 2009-03-27
Filing date: 2010-03-25
Publication date: 2010-09-30

Abstract

In order to create a brake disk (1), which is composed of a plurality of segments (7, 9), wherein the segments (7, 9) are disposed opposite of each other on both sides of a wheel (2) or a fastening disk and are fastened to each other by way of at least one fastening means (6) in a fastening region (15, 16) and to the wheel (2) or to the fastening disk, which has improved properties with respect to the thermal expansion, it is proposed that at least one fixed bearing (17) and at least one floating bearing (18) are provided for centering and fastening each segment (7, 9), said floating bearing being provided in the region of a fastening region (15, 16), and that the floating bearing (18) is designed and disposed so as to allow for a non-radial expansion of the segment (7, 9).

Description

description

brake disc

Technical area

The invention relates to a brake disk, in particular for disk brakes, in particular for wheels, according to the preamble of claim 1.

State of the art

Brake discs of wheels are well known in the art. The brake discs are exposed to different influences during a braking process. Basically, they are subject to the centrifugal force due to the rotation, for example, of the wheel to which the brake disc is attached and which is to be braked by means of the brake disc. In addition, the brake disc is bremsmomentbeaufschiagt during braking and it is under the influence of shocks by the frictional engagement between the brake pads and the brake disc, which are transmitted through the brake disc segments. Furthermore, the brake disc is under the influence of Zustellkräften which act during braking substantially axially on the brake disc. Furthermore, it is known that due to the friction between the brake disc unα Bremsbeiäycn a niCiY. ür.crhcbüchc friction is caused, which leads to a sometimes very significant thermal load on the brake disc.

Due to the thermal load on the brake disc, the brake disc is heated to considerable temperatures, which can lead to red hot the brake disc. Due to this significant energy input and the associated increase in temperature, the brake disc itself also experiences a significant thermal expansion. The particularly stressed friction rings or friction ring segments usually deform from a metallic material due to this heating stronger than their contact partners and can thereby cause undesirable constraining forces, which can lead to crack damage due to locally increased voltage spikes. Therefore, some solutions already exist in the prior art for allowing the friction rings to expand. However, these solutions are either expensive or they can not be transferred to segmented friction rings.

EP 1 682 791 B1 discloses a brake disk in which a friction ring can be fastened by means of clamping screws to a hub or a fastening disk, sliding elements being guided in radial grooves for preventing rotation and for centering. This allows to allow the thermal expansion occurring in operation in the radial direction.

DE 38 14 614 A1 discloses a shaft brake disk for rail vehicles with a friction ring, which are connected by means of through-bolts with the hub, wherein the through-bolts extend through bores on the outer circumference of the hub and through bores located on the inner circumference of the friction ring retaining tabs. Furthermore, sliding blocks are provided, which are arranged radially movable. This should cause a centering of the friction ring at every thermal load.

WO 01/96758 A1 discloses a brake disc for a disc brake, h ^p i wfiir.hfim a Bremsrinα is connected to a hub flange with screws. In this case, thermal expansions also occur between the brake ring and the hub body, because the brake ring is strongly heated during braking, while the hub body is heated less. In order to ensure an axial parallelism of screws at a thermal expansion, it is proposed that a holding element is arranged, which is fixed to the hub body and through which the end of the screws can be held after their passage through the brake ring flange. In this case, the holding element is designed as an angle element. DE 2 133 235 A describes a brake disk for rail vehicles, which is composed of two segments in the form of half rings. The half rings are arranged opposite each other on both sides of the wheel disc and are connected to each other on the side surfaces of the wheel disc via two through-bolts and two screws which pass through a clamping sleeve. The half rings are held almost rigidly to the wheel disc only at the local bearings of the clamping sleeves and afford the centering of the half rings in that the concentric position of the half rings is maintained by the at least two clamping sleeves. In this case, the remaining through bolts are located away from the defined by the clamping sleeves location of the fixtures and have radial play.

In DE 38 39 073 AI the centering of the ring segment to the wheel disc is formed by the combination of three fitting screws, which are guided without play in U-shaped slide bushings. Due to the radial orientation of the three U-shaped sliding bushes they form a fixed bearing in the composite; The floating bearings are formed by the remaining through bolts, which are provided with a certain play and allow specifically targeted expansion movements of the ring segments. Thus, they represent multiple floating bearings. Again, a radial expansion is allowed.

DESCRIPTION OF THE INVENTION: Problem, Solution. advantages

It is the object of the invention to provide a brake disk which has improved properties in terms of thermal expansion. Another object of the invention is to make the fixed bearing of a segmented brake disc such that the tolerance chain and the number of components is minimized and incorrect assembly is excluded.

This is achieved with the features of claim 1, wherein a brake disc is provided, which is composed of a plurality of segments, wherein the segments on both sides of a wheel or a mounting plate are arranged opposite one another and with each other at least one fixed bearing and at least one floating bearing is provided for centering and fastening of the segment, which is preferably provided in the region of a mounting portion and that the movable bearing is formed so and arranged to allow non-radial expansion of the segment.

Under a fixed bearing is to be understood as a storage that leads to the fixation in two translational degrees of freedom, with a rotation is allowed, so that no force counteracts when the bearing is rotated.

In contrast, the floating bearing only fixes a translational degree of freedom. The combination of a non-locating bearing and a fixed bearing is particularly suitable for compensating for expansion due to temperature changes.

A key idea of the invention consists in the fact that the floating bearing is designed so that the expansion of the individual segments on the fixed-floating bearing attachment is designed so that now the stretching direction is no longer radial. Thus, the storage of the segments differs from the previous storage and mounting. Because the movable bearing is designed with one degree of freedom, a targeted direction of expansion can be specified

Preferably, it is provided that the movable bearing is designed so that a tangential expansion of the segment is allowed. Under tangential expansion direction is understood to mean the direction that results when a tangent with respect to the imaginary circle center of the annular segments formed in the center of the floating bearing.

According to the invention it is expedient if the at least one floating bearing and / or the fixed bearing is designed by means of a sliding block, which in an opening of the wheel or in the wheel disc is preferably received in an opening.

It is also expedient if the sliding block of the fixed bearing is a substantially cylindrical sliding block, which does not allow any relative movement between the segment and the wheel or wheel disk and fixes and centers the segment relative to the wheel or wheel disk.

It is also advantageous that the sliding block of the movable bearing is a sliding block with a groove with two parallel opposite flanks, in which an element of the wheel or the wheel engages, which allows a relative movement between the segment and the wheel or wheel in the direction of the parallel edges ,

Furthermore, it is expedient if the fastening means passes through the sliding block in a respective opening. According to a further advantageous embodiment, it is provided that a centering of the brake disk element on the fixed bearing side and a dowel screw is provided. Advantageously, can be dispensed with an additional sliding block. The dowel screw centers the brake disc segments directly with the hole in the wheel. This ensures the shortest possible tolerance chain. A confusion with the KLJÜcccnεteiriep c ¹⁰ "'<~> ^Q iaπ ^p rs is prevented.

It is particularly advantageous if the fastening means is a screw.

It is also expedient if the segment has cooling ribs on its side facing the wheel or the wheel disk.

It is also expedient if the cooling ribs protrude in their radially inner and / or radially outer region relative to a central region in the axial direction. Brief description of the drawings

The invention will be explained in more detail on the basis of an embodiment with reference to the drawings. In a purely schematic representation:

1 is a partial sectional view of a brake disc,

2 is a side view of a segment of a brake disc,

3 is a perspective view of a movable bearing,

Fig. 4 is a perspective view of another embodiment of a movable bearing, and

Fig. 5 is a partial view of another embodiment of a

Brake disc.

Preferred embodiment of the invention

1 shows a brake disc 1, as it is attached to a wheel 2 or on a mounting plate, for example, a rail vehicle. The Ercrr.εεcheibe ^Λ hest ^p ht case of segmented brake rings so that it is composed of a disc in directly opposite or arranged on both sides of the disk segments.

The wheel 2 or the fastening disc preferably consists of a wheel hub 3 and a radially extending and preferably also axially narrow central region 4 and a radially outwardly adjoining region 5 which is also extended in the axial direction. The brake disc 1 is preferably in the region of the axially narrow central region 4 connected to the wheel 2 and the mounting plate. The segments of the brake disc 1 are by means of screws 6 or other connecting means to the wheel 2 and with the Fastening disc or connected to the respective opposite segment. In this case, the screw 6 is carried out in the axial direction from one side through an opening 8 in the segment 7 of the brake disk 1 and on the other side of the middle central region 4 also by the segment 9 arranged there and by an opening 10 provided in this respect and by means of a Nut 11 bolted and secured.

In this case, the central region 4 of the wheel 2 and the mounting plate has an opening 12 in which a sliding block 13 can be accommodated. The sliding block shown in Figure 1 is one of two sliding blocks of the brake disk segment 7, as shown in Figure 2 and shows in Figure 1 the sliding block 13 of the fixed bearing.

The opening 12 thus serves to center the brake disk segment 7, 9 of the brake disk 1.

On the back of the brake disc segments 7.9 cooling fins 14 are provided, which serve to improve the cooling of the brake disc by 7,9 air can flow past the back of the segments.

FIG. 2 shows a segment 7 of the brake disk 1, in which the rear side is seen, the cooling ribs 14 being recognized, which are in the radial direction. The reinforcement 7 has two fastening or screwing areas 15, 16 in which screws 6 are made through openings in order to connect the segment of the brake disk to the wheel 2 or to the fastening disk.

The at least one screw 6 and the screws 6 serve to tension the segment 7 of the brake disk 1 with the segment of the brake disk 1 which is opposite the segment 7 on the other side of the wheel 2 or the mounting disk.

The Verschraubungsbereiche or points of the segment 7 of the Figure 2 is a fixed bearing 17 and a movable bearing 18, wherein at more than two Verschraubungsbereichen or -punkien a fixed bearing and at least two movable bearings are formed.

The centering of the segment 7 takes place in the case of the invention on the fixed bearing 17 and the floating bearing 18. For this purpose, sliding blocks 19,20 are provided, which serve for centering.

The centering on the non-locating side 18 is characterized in that a cylindrical sliding block 20 sits on one side in a bore or opening in the wheel 2 or in a mounting plate and by two plane-parallel flattened flanks 21 in the cylindrical portion of the sliding block 20, the thermal expansion of the segment 7 of Brake disc 1 passes through a matching groove in the brake disc 1. This means that the sliding block 20 of the segment 7 can slide along a groove in the region of the wheel 2 or the fastening disk and thus, when the thermal expansion of the segment 7 causes no tension of the segment, but this can expand freely.

FIG. 2 indicates the preferred idea of the invention, which consists in that the floating bearing is designed such that a tangential formation of the segment (7, 9) is permitted. "; The strain ^nt • ■ Chil -.- g."Understood> tangential direction, said tangent should be seen as perpendicular to the radius R about an imaginary center point M of the segment 7 in the tangential direction it is the. As will be apparent to those skilled in the art, the non-locating bearing 18 is designed so that specifically this elongation is permitted as a degree of freedom of the movable bearing and then the special design of the movable bearing 18 is aligned.

The centering on the fixed bearing side 17 is characterized in that a cylindrical sliding block 19 is seated on one side in a bore or opening in the wheel 2 or in a mounting plate, and by the fit of the cylindrical sliding block in the cylindrical bore all Degrees of freedom of movement are blocked.

The segment 7 is thus around the sliding block 19 of the fixed bearing 17 in a position to expand freely around the fixed bearing 17 around. The movable bearing 18 prevents a torsion of the segment 7 to the fixed bearing 17, without hindering the thermally induced strain.

It can also be seen in FIG. 2 that the cooling ribs 14 have a greater axial formation at their radially inner and radially outer edges 31, 32 and protrude from the remaining central region 33 of the cooling rib 14, so that when they contact the wheel 2 or the fastening disk these projecting radially inner or radially outer portions 31, 32 abut the wheel 2.

The movable bearing 18 is shown again separately in FIG. As can be seen there well, the sliding block 20 is penetrated by the screw 6 The sliding block 20 is arranged in a screw dome 21 having a groove 22, the flanks 23 are formed parallel opposite one another. The sliding block 20 consists of the sections 24 and 25, wherein the base diameter of the section 24 is smaller than the basic diameter of the section 25. The section 25 is provided with two corresponding flat sections, the flanks 26 cucbüdcn, the rp.it the piankon 93 H ^p »r groove 92 correspond and thus prevent rotation of the sliding block 20 in Schraubdom 21, which is fixedly connected to the segment 7, prevent. A translational movement of the sliding block 20 is in contrast allowed by this design.

In the alternative embodiment of the sliding block 20a shown in FIG. 4, a projection 27 in the manner of a spring of a tongue and groove connection is provided on the screw dome 21 instead of a groove, which has corresponding parallel opposite side surfaces as flanks 28.

The section 25 of the sliding block 20a points in this embodiment a groove 29, whose flanks 30 are formed parallel opposite and correspond to the flanks 28 of the projection 27. Also in this embodiment, there are the advantages of a floating bearing, which allows a corresponding movement due to thermal expansion.

In the case of the further embodiment of a brake disk shown in FIG. 5, the construction essentially corresponds to the embodiment shown in FIG. 1 with the essential difference according to the invention that the sliding block provided in FIG. 1 is dispensed with and the fastening means is designed as a fitting screw 34. The Passdehnschraube 34 centers the brake disc segments directly with the hole in the wheel. Thus, the shortest possible tolerance chain (segment 7, Passdehnschraube 34, nut 11, segment 9) is guaranteed.

LIST OF REFERENCE NUMBERS

1 brake disc

2 wheel

3 wheel hub

4 middle area

5 Radially outboard area

6 fasteners, screw

7 segment

8 opening

9 segment

10 opening

11 mother

12 opening

13 sliding stone

14 cooling fin

15 mounting or bolting area

16 mounting or bolting area

17 fixed camps

18 loose bearings

19 sliding stone

20, 20a Kulissenstein

21 screw dome

Σέ. I N Ul

23 flanks

24 subsection

25 -

26 flanks

27 advantage

28 flanks

M fictitious center

R radius

Dt tangential strain

Claims

claims

1. brake disc (1), which is composed of a plurality of segments (7, 9), wherein the segments (7, 9) on either side of a wheel (2) or a fixing disc are arranged opposite each other and by means of at least one fastening means (6) in a fastening region (15, 16) with one another and with the wheel (2) or with the fastening disk, characterized in that for centering and fastening each segment (7, 9) at least one fixed bearing (17) and at least one floating bearing (18 ) is provided, which is provided in the region of a fastening region (15, 16), and that the movable bearing (18) is formed and arranged so that a non-radial expansion of the segment (7, 9) is allowed.

2. Brake disc according to claim 1, characterized in that the floating bearing (18) is formed so that a tangential expansion of the segment (7, 9) is allowed.

3. Brake disc according to one of the preceding claims, characterized in that the sliding block (19) of the fixed bearing (17) a

Kuiiaaei iaieiii isi, weiuiiei no Reiciiivueweyuπy between Segmeni (/, yj and wheel or mounting plate permits and the segment (7) relative to the wheel (2) or fixing disc determines and centers.

4. Brake disc according to one of the preceding claims 1 to 3, characterized in that the sliding block (20) of the floating bearing (18) has a partial section (25) with two parallel opposite flanks (26), which with flanks (23) of a Groove (22) in a screw dome (21) of the segment (27) correspond so that a relative movement between the segment and the wheel or mounting plate is allowed.

5. Brake disc according to one of the preceding claims 1 to 3, characterized in that the sliding block (20a) of the floating bearing (18) has a portion (25) having a groove (29) with two parallel opposite flanks (30), which with two parallel opposite flanks (28) of a projection (27), in particular in the manner of a tongue and groove connection, on a, screw dome (21) of the segment (7) so correspond that a relative movement between the segment and the wheel or mounting plate is allowed.

6. Brake disc according to one of the preceding claims, characterized in that the fastening means, the opposing segments (7, 9) and the sliding block (19, 20, 20a) passes through.

7. Brake disc according to one of the preceding claims, characterized in that the fastening means engages through the opposing segments (7, 9) and the wheel hub (3).

8. Brake disc according to one of the preceding claims, characterized in that the fastening means is a screw (6).

9. Brake disc according to one of the preceding claims, characterized in that the fixed bearing 17 comprises a dowel screw or a Passdehnschraube (34).