WO2007135044A1

WO2007135044A1 - Floating caliper disk brake with biasing spring

Info

Publication number: WO2007135044A1
Application number: PCT/EP2007/054740
Authority: WO
Inventors: Rudolf Platzer; Michael Kollers
Original assignee: Continental Teves Ag & Co. Ohg
Priority date: 2006-05-24
Filing date: 2007-05-16
Publication date: 2007-11-29
Also published as: EP2029909A1; DE102007022905A1

Abstract

The invention relates to a disk brake (1) with a brake caliper (22) comprising a support (3) attached to the vehicle, a caliper housing (2) and at least one brake pad (8). The support and the caliper housing axially encompass at least one brake disk (23). Furthermore, the caliper housing and the brake pad on the support are mounted to be axially movable, wherein there is at least one spring assembly (9) acting between the caliper housing and support that produces an elastic, resultant biasing force (Fv) between the caliper housing and support. A braking peripheral force (Fu) caused by the braking procedure is diverted through the support. Because of the favorable shape and attachment of the spring assembly to the disk brake, the biasing force of the spring assembly, with regard to the brake disk, has a tangential force (Fvu) acting in the peripheral direction and a radial force (Fvr), and means are provided for receiving or supporting the spring assembly on the caliper housing and support that are able to accept the tangential and radial force. Because of this, an angle enclosed by the resultant peripheral braking force and the resultant bias force during braking is not equal to 90 degrees.

Description

SWIM SADDLE DISK BRAKE WITH SPRING SPRING

The invention relates to a disc brake with a brake caliper comprising a vehicle-fixed holder, a caliper housing and at least one brake pad. The holder and the caliper housing surround axially at least one brake disc. Furthermore, the caliper housing and the brake pad are mounted axially displaceably on the holder, wherein at least one spring arrangement is effectively provided between the caliper housing and the holder, which produces a resilient, resulting biasing force between caliper housing and holder. A brake circumferential force caused by a braking operation is dissipated through the holder.

Such a disc brake is known from DE 41 10 850 Al. In it, a spring assembly braces a caliper housing a caliper each against a holder and thus prevents a possible rattling of brake pads in the disc brake. Such spring assemblies typically engage the outer surface of the outer saddle leg and extend under the arms of the holder. Since the caliper housing is mounted on the brake pads on the holder, he is subject to the game-afflicted leadership of the brake pads in the receiving slots of the holder. This results in a braking operation that the brake pads and the caliper housing undergo a shift in the circumferential direction. This displacement is on the order of magnitude of the tangential clearance of the brake pad and caliper guide and is, especially because of the associated noise, to avoid. In addition, the tangential displacement disadvantageously promotes an inclined position of the brake pads on the brake disc, whereby a non-uniform wear pattern is caused, and losses in terms of ride comfort must be accepted.

It is an object of the invention to provide a disc brake, which avoids the disadvantages of the prior art and provides an improved alternative, in particular by a favorable expression and attachment of the spring assembly to the disc brake.

The object is achieved with the features of claim 1, characterized in that the biasing force of the spring assembly with respect to the brake disc, acting in a circumferential direction, tangential force and a radial force, and provided by the saddle housing and the holder means for receiving or supporting the spring assembly which are able to absorb the tangential force and the radial force. This causes that during braking, an angle subtended by the resulting brake circumferential force and the resulting biasing force is not equal to 90 degrees. The tangential component of the biasing force of the spring assembly causes the caliper housing and the brake pads occupy a defined position in the circumferential direction in the bearing shafts of the holder and abut against a tangential stop the storage shafts at any time. Thus, it is prevented that the caliper housing and the brake pads perform a relative movement to the holder in the context of the tangential clearance of the pad and saddle housing guide. A favorable embodiment of the invention includes that the means in cooperation with the spring arrangement are so pronounced that the tangential force has substantially the same orientation as the brake circumferential force when braking the brake disc rotating in the main direction of rotation. This has the consequence that the caliper housing and the brake pads abut at any time on an effective in the main direction of rotation stop. This prevents a braking operation during forward travel, ie when the brake disc in

Rotates main direction of rotation, the caliper and / or the brake pads by the brake circumferential force in the context of the bearing clearance, move to the stop. This would lead to noise and uneven wear of the brake pads. Especially when the disc brake on the main driving direction facing away from the axis of rotation of a wheel is mounted on the vehicle, the advantages of the invention described are particularly pronounced: In such a position, the caliper housing and / or the brake pads are raised during each braking operation within the storage game and fall after the braking process due to gravity back again. It comes easily to an oblique position of the brake pads on the brake disc, which leads to an irregular Verscheiß. The tangential force component of the biasing force now keeps the caliper housing and / or the brake pads always in the raised position, whereby the above-mentioned disadvantages are effectively avoided.

An embodiment of the invention discloses that the means are at least partially formed as a ramp arrangement with at least one ramp, wherein the ramp, projected onto a plane of rotation of the brake disc, runs anti-parallel to the brake circumferential force. In particular, this ramp can be so pronounced that the ramp, projected onto the plane of rotation, with the brake circumferential force at a braking of the rotating in a main direction of rotation brake disc includes a ramp angle of greater than 10 °. It may be useful that the ramp is disposed on a holder arm of the holder, and that the means are at least partially formed as a receptacle for the spring assembly. If the spring arrangement can be fastened in the seat in the saddle housing by means of a fastening hook, and optionally a spring head is provided at one end of a spring arm of the spring arrangement, which spring can be applied to the ramps in an axially displaceable manner, the advantages of the invention are particularly pronounced.

In the context of a further embodiment of the invention, two ramps are provided on the holder arm. In the assembled state, the spring arrangement can be supported exclusively on either one ramp or exclusively on the other ramp on a holder arm. In the installed state of the disc brake, the spring assembly rests exclusively on the inlet-side ramp on the respective holder arm. The two ramps on a holder arm have an opposite inclination, but which in each case enclose the same angle with the brake circumferential force which arises during a rotation of the brake disc in a main direction of rotation. As a result, the same shape of the holder of the disc brake can be used for both sides of the vehicle, whereby the manufacturing costs are reduced. The above-mentioned main direction of rotation of the brake discs, based on the installed holder on the different sides of the vehicle in an opposite direction. To fully exploit the stated advantage, the spring assembly can be secured by means of the receptacles at two different positions in the caliper housing. Thus, the same spring arrangement can be supported at both ramps on a support arm depending on the obstruction of the disc brake on the different sides of the vehicle by each of the inlet-side mounting position is selected for the spring assembly. In this case, an offset of the two receptacles in the circumferential direction is substantially the same size as an offset between the two support points on the inlet side and the outlet side ramp.

Further details of the invention will become apparent from the drawings with reference to the description.

In the drawings shows

Fig. 1 is an axial view of a disc brake with a spring arrangement, which is effective between the caliper housing and holder, and

Fig. 2 is an enlarged axial view of an alternative embodiment of a disc brake with an advanced caliper.

Fig. 1 shows an axial view of a caliper 22 of a disc brake 1 with a caliper housing 2 and a vehicle-fixed holder 3. The caliper housing 2 includes an axially inner housing leg, which includes, among other things, an actuator and in the installed state facing the vehicle. In addition, the caliper housing 2 comprises a housing bridge 5, which has an axially outer housing leg 6 with the inner housing leg combines. The caliper housing 2 engages around the dashed lines, rotatably mounted about the axis of rotation 24 brake disk 23 and is mounted axially displaceable on brake pads 8 on the holder 3. Between the holder 3 and the caliper housing 2, the brake pads 8 are provided axially displaceable. A spring assembly 9 braces the caliper housing 2 via the brake pads 8 with the holder 3. The spring assembly 9 is made of a metallic material, in particular it is punched out of a sheet metal and bent, and can roughly in a mounting portion 10 and in two spring arms 11,11 be divided. Also conceivable is an embodiment of the spring arrangement of bent spring wire. The attachment portion 10 of the spring assembly 9 is perpendicular to the spring arms 11,11 'and nestles parallel to an outer surface of the outer housing leg 6 at. In the housing leg 6 receptacles 13,13 'are provided, which are engaged behind by fastening hooks 14,14' of the spring assembly 9, whereby the spring assembly 9 is fixed to the caliper housing 2. The spring arms 11,11 'terminate in crowned spring heads 12,12' which press against holder arms 4,4 'of the holder 3. Thus, a bias voltage F _{v is} generated between the caliper housing 2 and the holder 3, which is composed of an inlet and outlet side biasing force F _v _ _a , F _v _ _a usus of the respective spring arm 11,11 'composed.

The contact surfaces of the holder arms 4,4 'for the spring arms 11,11' are each provided with a ramp assembly 15,15 ', which in turn each include an inlet-side ramp 16,16' and an outlet-side ramp 17,17 '. An inlet side 18 'and an outlet side 18 are defined in a main direction of rotation 20 of the brake disc 23. As shown in FIG. 1, the inlet-side ramps 16, 16' and the resulting resultant during the braking process close Peripheral force F _11, the ramp angle δ and the ramp angle ß. Due to this inclination of the ramps 16, 16 ', the inlet and outlet side biasing forces F _{ve ± n} , F _{v from} the respective spring arm 11, 11' according to the ramp angles β and δ each share in an inlet-side tangential and radial force F _Vu _a, Fvr_em and in an outlet side tangential and radial force Fvu_off, F _Vr _off on. Vectorially added, these partial forces give the resulting biasing force F _v , which due to the

Ramp angle ß and δ not perpendicular to the resulting

Braking circumferential force F ₁₁ is, and with this an angle φ includes.

In experiments it has been shown that even at an angle ß and δ of 15 degrees, and thus from an angle φ of 75 degrees, the undesirable freedom of movement of the caliper 2 in the circumferential direction 21 is significantly limited, and thus the brake pads 8 after the Braking, in particular the outer brake pad, no longer rest against the brake disc 23. This phenomenon increases continuously with an increase in the ramp angles β and δ, that is, the steeper the ramps 16, 16 'are pronounced, the larger the tangential force components F _Vu _in and F _Vu _ become from the preload forces F _ve m and F _v • At a ramp angle of 25 ° C, there is hardly any unwanted contact of the brake pads 8.

Furthermore, it is also conceivable that the ramp angles ß and δ are formed differently large, and in this way further positive effects can be displayed. For example, an axial tilting moment, which acts on the brake pad 8 and the caliper housing 2 during braking, can be compensated by providing only the outlet-side retainer arm 4 with a ramp arrangement 15. Furthermore, on the holder 2 outlet ramps 17,17 'are provided on the ramp assemblies 15,15', which have a slope with the ramp angles CC and γ. These meet in the present example, however, no function, but only serve that in a reverse main direction of rotation same caliper design can be used, and only the position of the spring assembly 10 in the circumferential direction 21 must be changed. In this case, particularly when the disc brake 1 is installed on the opposite side of the vehicle, the spring heads 12,12 'abut against the ramps 17,17' of the ramp assemblies 15,15 ', and produce a tangential component of the biasing force F _Vu corresponding to the reverse one Main direction of rotation of the brake disc 23. The holder 2 is thus designed symmetrically to a line of symmetry 7, and the ramp angle OC and γ correspond to the ramp angles ß and δ. Since the spring assembly 9 is symmetrical to a symmetry line 19, determines the position of the spring assembly 9 in the circumferential direction, which ramps 16,16 'or 17,17' the spring heads 12,12 'bear, and in which direction the tangential force component F _Vu acts. In Fig. 1, the receptacles 13,13 'are mounted asymmetrically in the caliper housing 2, so that the spring assembly 9 is displaced by a distance A to the symmetry line 7 of the caliper housing 2. Thus, the caliper housing 2 and the receptacles 13,13 'each have to be adjusted according to a provided main rotational direction of a brake disc 23.

Fig. 2 leads an embodiment of a disc brake 31, wherein analogous to FIG. 1, a spring assembly 39 is provided such that corresponding to a main direction of rotation 20 of a brake disc, a biasing force F _{v has} a tangential F _Vu and a radial force component F _Vr . In contrast 1, this holder 33, spring assembly 39 and the Satteigehause 32 are symmetrical, so that all components for each main direction of rotation can be used, and no adjustment of the recordings 43 must be made. For this, the receptacles 43 are provided for the spring assembly 39 with two Einhangepunkten 50,51, in which the fastening hooks 44 spring assembly 39 depending on the main direction of rotation of the brake disc, or depending on the desired orientation of the tangential component F _{Vu of} the biasing force F _v , is mounted. The offset V of the two Einhangepunkte 50,51 corresponds to twice the distance A between the line of symmetry 37 of the Satteigehauses 32 and the line of symmetry 49 of the spring assembly 39th

In the exemplary embodiments from FIG. 1 and FIG. 2, the spring arrangement 9, 39 is respectively fixed on the foodstuff home 2, 32, and the spring arms 11, 11 ', 41 print against the holder arms 4, 4', 34 of the holder 3, 33. Equivalent thereto, other embodiments are conceivable in which a spring arrangement is fixed to a holder and prints over at least one spring arm in a suitable manner against a ramp on a brake caliper, and thus generates the biasing force F _v with tangential and radial component.

The features shown in the figures can also be combined with each other and not limited to the individual exemplary embodiments. Reference sign list

1 disc brake 21 Umfangsriehtung

2 caliper housing 22 caliper

3 holder 23 brake disc

4 holder arm 24 axis of rotation

4 'holder arm 31 disc brake

5 housing bridge 32 saddle housing

6 housing legs 33 holders

7 Symmetrical line 34 Holder arm

8 Brake lining 35 Housing bridge

9 spring arrangement 36 housing legs

10 fixing section 37 symmetry line

11 Spring arm 38 Brake lining

11 'spring arm 39 spring arrangement

12 spring head 40 fixing section

12 'spring head 41 spring arm

13 Recording 42 Spring head

13 'recording 43 recording

14 fixing hooks 44 fixing hooks

14 'mounting hook 45 ramp arrangement

15 ramp arrangement 46 ramp

15 'ramp arrangement 47 ramp

16 ramp 48 outlet side

16 'ramp 48' inlet side

17 Ramp 49 Symmetry line

17 'ramp 50 mount point

18 outlet side 51 suspension point

18 'inlet side 52 caliper

19 symmetry line

20 main direction of rotation A distance

Fu resulting brake circumferential force

F _v resulting preload force

F _Vu tangential force

F _Vr radial force

F _v _em preload force (inlet side)

Fvu_emTangential Force (inlet side)

Fvr_em radial force (inlet side)

F _v _aus Vorspannkraft (outlet side)

F _Vu eme tangential force (downstream)

^■ f For a radial force (outlet side)

V Offset α Ramp angle ß Ramp angle γ Ramp angle δ Ramp angle φ Angle

Claims

claims

1. Disc brake with a caliper comprising a vehicle-fixed holder, a caliper housing and at least one brake pad,

- Wherein the holder and the caliper housing axially surround at least one brake disc,

the saddle housing and the brake lining are mounted so as to be axially displaceable on the holder,

and wherein at least one spring arrangement is effectively provided between the caliper housing and the holder, which produces an elastic, resulting pretensioning force between the caliper housing and the retainer,

and a brake circumferential force caused by a braking process is dissipated via the holder, characterized in that the biasing force (F _v ) has a tangential force (F _Vu ) acting in a circumferential direction (21) and a radial force (F _Vr ),

- And that on the caliper housing (2, 32) and on the holder (3, 33) means (13, 13 ', 15, 15', -45, 50, 51) for receiving or supporting the spring assembly (9, 39) are provided which are capable of receiving the tangential force (F _Vu ) and the radial force (F _Vr ) such that an angle (φ) subtended by the resulting brake circumferential force (F ₁₁ ) and the resulting biasing force (F _v ) is not equal to 90 ° degrees ,

2. Disc brake according to claim 1, characterized in that the means (13, 13 ', 15, 15', 45, 50, 51) in cooperation with the spring arrangement (9, 39) are so pronounced that the tangential force (F _Vu ) has substantially the same orientation as the brake circumferential force (F ₁₁ ), in a braking of the brake disc rotating in the main direction of rotation (20).

3. Disc brake according to claim 1 or 2, characterized in that the means (15, 15 ', 45) at least partially as a ramp arrangement (15, 15', 45) with a ramp (16, 16 ', 17, 17'; 45 , 46) are formed, wherein the ramp (16, 16 ', 17, 17', 45, 46) projected onto a plane of rotation of the brake disc antiparallel to

Brake circumferential force (F ₁₁ ) runs.

4. Disc brake according to claim 3, characterized in that a ramp (16, 16 ', 46) or a ramp (17, 17'; 47) projected onto the plane of rotation with the brake circumferential force (F ₁₁ ), with a braking in one Main rotational direction of rotating brake disc, each including a ramp angle (α, ß, γ, δ) greater than 10 °.

5. Disc brake according to claim 4, characterized in that the ramp (16, 16 ', 17, 17', 46, 47) on a holder arm (4,4 '; 34) of the holder (3; 33) is arranged, and in that the means (13, 13 ', 50, 51) are formed at least partially as a receptacle (13, 13', 50, 51) for the spring arrangement (9, 39).

6. Disc brake according to claim 5, characterized in that the spring arrangement (9, 39) by means of a Fixing hook (14, 14 ', 44) in the receptacles (13, 13', 50,51) in the caliper housing (2, 32) can be fastened.

7. Disc brake according to claim 5 or 6, characterized in that at one end of a spring arm (11, 11 ', 41) of the spring arrangement (9, 39) a spring head (12, 12', 42) is provided, which axially displaceably the ramps (16, 16 ', 17, 17', 46, 47) can be applied.

8. Disc brake according to one or more of the preceding claims, characterized in that on the holder arm (4, 4 ', 34) two ramps (16, 16', 17, 17 ', 46, 47) are provided, wherein the spring arrangement (9; 39) in the assembled state can be supported exclusively either on the ramp (16, 16 '; 46) or exclusively on the ramp (17, 17'; 47).

9. Disc brake according to claim 8, characterized in that the spring arrangement (9, 39) by means of the receptacles (50,51) in two different positions in the caliper housing (32) can be attached.

10. Disc brake according to claim 8, characterized in that an offset (V) of the receptacles (50) and (51) in the circumferential direction (21) is substantially equal to an offset (V) between two support points on the ramp (46). and (47).