巴西专利BR112014005830B1 automobile disc brake and brake pad

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专利摘要:
DISC BRAKE OF A CAR AND BRAKE CANVAS. The present invention relates to a disc brake on an automobile, particularly a utility vehicle, with a brake caliper covering the brake disc, on which at least one brake liner is provided, provided with a support plate lining (42) and a friction lining attached to it and a brake bracket (1) stationary on the side of the vehicle, with two support horns that support the lining support plate (42) on the intake side and on the side of the outlet, with the support horn (3) on the side of the brake support inlet (1) and the support surface (422) adjacent to it, engage with each other positively, and the support horn ( 2) on the outlet side and a corresponding abutment contour of the cladding support plate (42) have a support surface (21. 423) slanted in total, in areas or at least in the highest radial region of the cladding support in the brake support by an angle of inclination to the Y axis. write a brake liner (4).
公开号:BR112014005830B1
申请号:R112014005830-0
申请日:2012-09-13
公开日:2021-03-09
发明作者:Johann Iraschko
申请人:Knorr-Bremse Systeme für Nutzfahrzeuge GmbH；
IPC主号:

专利说明:

[001] The present invention relates to an automobile disc brake according to the preamble of claim 1, as well as to a brake pad according to the preamble of claim 11.
[002] Disc brakes according to species consist, substantially, of a rotating brake disc with a vehicle axle in operation, at least one or more brake pads arranged on one or, preferably, on both sides of the disc brake caliper, and preferably a brake caliper 4, which extends, preferably on one or both sides of the brake disc. The disc brake, which has the brake supports, preferably has a movable sliding caliper in relation to the brake support or a rotating caliper.
[003] To ensure a safe function of the disc brake, it is necessary to drive and support the brake pads securely on the brake caliper or on the brake support.
[004] The brake support according to the known species (and also according to the invention) preferably has, for this purpose, on each side of the brake disc, preferably two support horns, connected to each other another by means of a crosspiece, as well as radially projected from a frame, which limit a coating pit for receiving a brake pad. The casing pit is formed open, in this case, according to the state of the art, preferably farther away radially, so that the brake pads can be inserted into it radially from the outside. After insertion, the brake pads are fixed radially by a clamp. Optionally, a coating retaining spring can be provided, particularly one that is arranged and acts elasticly between the coating retaining clamp and the brake pad.
[005] The brake pads are subject, in operation, to a plurality of requests. Thus, the brake pads are ordered thermally high and loaded mechanically. For the two operating states a) activated brake and b) non-activated brake, different load states are shown.
[006] On a brake activation, the brake pad is exposed to high pressure and transverse forces, the brake pad having to fulfill the task of introducing the transverse forces generated on the friction surface of the brake pad through the mass friction plate on a lining support plate and, from there, on the brake caliper or the brake support. The transverse forces acting on the brake pad are, in this case, received mainly by the support horn on the outlet side, therefore, by the anterior support horn in the direction of rotation of the brake disc.
[007] In addition, the brake pad needs to transform the clamping force generated by the brake caliper into a pressure force distributed as evenly as possible on the friction surface. For this purpose, the clamping force generated by the brake caliper needs to be transformed with the help of the rigid lining support plate into a surface load.
[008] The problem is that due to the limited construction space conditions, that the narrow sides of the front side or support surfaces of the cladding support plate against the brake pad of the known brake pad, in a braking process are unable to prevent rotation of the brake pad. This pivoting movement can have a negative effect on the ventilation gap, that is, the free space between the friction lining and the brake disc, as well as on the wear behavior of the brake pads, particularly in the form of an oblique wear. and the clearance of the linings.
[009] DE 29 26 818 A1 is mentioned on the state of the art.
[0010] It is the task of the present invention to further develop a disc brake according to the species, in such a way that the negative effects described above are extensively avoided on service behavior.
[0011] This task is solved by a disc brake with the characteristics of claim 1, as well as by a brake pad with the characteristics of claim 12.
[0012] As the support horn on the inlet side, in this case, the rear support horn in a main direction of rotation of the brake disk, therefore, the direction of rotation of the brake disk during a drive ahead of the car.
[0013] Correspondingly, as the support horn on the output side, the anterior support horn is designated in a main direction of rotation of the brake disc, therefore, the direction of rotation of the brake disc during a forward drive. .
[0014] In this case, the support horn on the outlet side and the associated contour of the cladding support plate have, in each case, at least at the highest point of support in a radial direction an inclined support surface in relation to the axis Y by an angle of inclination α> 0o, and these support surfaces are designed to rest against each other when braking in the main travel direction.
[0015] To prevent tangential slipping of the brake pad, caused by the oblique position of the highest fulcrum A, the angle of inclination and, in this case, preferably less than the sum of an angle of introduction of force and Arcus Tangens of a friction value μa at the support point on the support horn on the outlet side. As particularly advantageous, the inclination angles α between 8 ° and 30 ° were shown. Also to ensure that the coating does not slide tangentially on the support of the support horn, values for angle α are preferably given between min. 8 ° and max. 30th.
[0016] In the disc brake according to the invention, in which the support horn on the side of the brake support inlet and the support surface adjacent to it of the cladding plate interlock with each other, the pad brake is supported on a support point on the support horn on the outlet side, which in the Y direction is below a force action line that represents the total frictional force.
[0017] The distribution of force on the two support horns that can be obtained in this way, has an advantageous effect on the braking behavior.
[0018] On the one hand, the brake pad shows a defined torque around a Z axis parallel to the axis of rotation of the brake disc. By this torque, a support force is also generated on the support horn, advantageously, and therefore this side of the brake support is also included in the force flow during a braking process, which means that, for example, in turn, a more advantageous distribution or introduction of force is obtained in the brake support. On conventional brake supports, without support on the inlet side of the brake pad, there is, on the other hand, a proportionally high support of the lining on the support horn on the outlet side.
[0019] Advantageously, it is then the distribution of force more uniform compared to the state of the art on the two support horns in a braking process, to which also the higher low point (in the Y direction) contributes considerably.
[0020] This is explained through a first model observation. Simply put, for the description of the coating, a model of a short annular segment in the peripheral direction can be assumed (that is, the angle of overlap Φ in the peripheral direction is, simply, assumed to be relatively small), for which there is a line of action of force or a force action vector, which by the center of gravity of the brake pad in the X direction (perpendicular to the axis of rotation of the brake disc). In Figures 2ff, this force action vector, in the variants shown in the figures, is located radially exactly or approximately in the center and, in a circumferential direction, in the center or approximately in the center of the brake pad. The support on the outlet side of the brake support occurs, on the other hand - see also Figs. 3 and 4 and the other existing representations besides Fig. 1 - in the direction perpendicular to the axis of the brake disc in relation to the force action vector to be applied in the center of gravity, preferably and advantageously, further in, towards to the axis of rotation. This is also true for figures, which do not include a brake support.
[0021] The highest support point A of the brake pad on the support horn on the outlet side in the Y direction is particularly preferred at a distance h from the force action line, which is at least 0.1 times the length of the brake pad in the direction of the force action line of the total friction force and / or between 0.1 and 0.25 times the width of the brake pad, perpendicular to the direction of the force action line of the force of friction total friction. Thus, the introduction and distribution of force is also advantageous on the inlet side, which is explained in more detail below.
[0022] According to an improvement of claim 1, but which can also be seen as an independent invention, it is also particularly advantageous when the support horn on the outlet side and the respective contour of the cladding support plate have, in in each case, a support surface inclined in relation to the Y axis, a support surface inclined in relation to the Y axis by an angle of inclination α> 0 °, these support surfaces being determined to abut each other when braking in the direction main gear.
[0023] To prevent tangential slipping of the brake pad, due to the oblique position of the highest fulcrum A, the angle of inclination is, in this case, preferably less than the sum of an angle of introduction of force and the Arcus Tangens of a friction value μa at the point of support on the support horn on the outlet side. Inclination angles α between 8 ° and 30 ° have proved to be particularly advantageous. Also to ensure that the coating does not slide tangentially on the support of the support horn, values for min. 8th and max. 30th.
[0024] The observations described above apply to braking processes in the forward direction. But in order for braking processes to be possible in the backward direction as well, without prejudice to the function, the oriented brake support horn entering the forward direction must have a minimum height. An advantageous rule is, in this case, that the height of the brake support horn must be greater than the height of the line of action oriented in the circumferential direction of the frictional forces of the coating. This ensures that no outward torque is generated by the brake pad support.
[0025] Advantageous modality variants of the invention are the subject of the other secondary claims.
[0026] According to a variant of advantageous modality, which, on the one hand can be seen as an improvement on the object of claim 1, but on the other hand, also as an independent invention - the support horn on the outlet side of the support of the brake is formed recessed in relation to the support horn on the inlet side of the brake support. This even refers to the radial distance of the axis of rotation (Z axis) of the brake disc. The support horn on the inlet side, which is formed radially high in relation to the support horn on the outlet side, guarantees particularly secure retention and prevents outward rotation on the inlet side of the brake pad of the brake support.
[0027] In particular, the support horn on the inlet side is higher than a point of intersection of the line of action and force with the support horn on the inlet side, which improves brake pad retention, even in a reverse gear.
[0028] According to another variant of the modality, the support horn on the outlet side of the brake support and the support surface of the cladding support plate adjacent to it are formed in such a way that the cladding support plate on the outlet side, it can be rotated out of the brake support, radially away from the axis of rotation of the brake disc. Because of this, at the same time, in the constructive configuration of the brake support and brake support plate, to prevent the brake pad from rotating, simple assembly and disassembly of the brake pad is possible. The mounting and dismounting of the brake pad on the brake bracket can be carried out here simply by a rotating movement.
[0029] The support surface of the cladding support plate, adjacent to the support horn on the side of the brake support entrance, presents, according to a variant of advantageous modality, a displacement, which is inserted in a lowering corresponding to the displacement in the support horn on the entry side. Because of this, the impediment of removal on the inlet side of the brake pad is caused not only by the presence of sufficient frictional forces, but by the configuration of the liner support plate and the support horn on the inlet side, with the that it is also possible to redistribute larger support forces on the entry side. Particularly advantageous here is a positive fit engagement of the displacement in the lowering on the support horn on the entrance side, for example, due to the fact that the support horn on the entrance side has a head part, which covers the displacement on the surface of support of the cladding support plate, adjacent to the support horn on the inlet side.
[0030] According to another preferred mode variant, the cladding support plate is formed by the formation of the respective displacements asymmetrically to an axis of symmetry, which cuts through the center and is extended by the axis of rotation of the brake disc . Also due to this, there are several advantages. Thus, a brake pad guide on the inlet side, which acts in a radial direction, prevents the brake pad from rotating during a braking process. In addition, due to the asymmetry, there is the possibility of an asymmetric arrangement of the friction mass of the brake pad, for example, by compensating for the oblique wear of the friction mass. In addition, due to the asymmetric configuration, incorrect mounting of the brake pad on the brake support is almost excluded. Thus, the lowering preferably extends as a protrusion in the direction of the main rotation direction of the brake disc and is supported from below on the inlet side by the cover plate, such that the brake pad cannot be taken directly, radially in relation to the center of the brake disc of the brake support.
[0031] In the following, examples of the modality of the invention are explained in more detail by means of the attached drawings.
[0032] Show: Figure 1 a side top view over a brake pad retained in a brake support according to the state of the art, Figure 2 a side view of a first variant of a brake support according to the invention, with brake pad installed in it, Figure 3 a side view of the brake pad and the brake pad of Figure 2 with brake pad shifted for assembly or disassembly, Figures 4a-4d a side view of the brake pad and of the brake pad of Figure 2 with schematic representation of the brake disc and forces acting on various points of the brake pad or brake pad, Figure 5 a top view of the brake pad and the brake pad of Figure 2 with reception of forces acting at different points, Figure 6 a-6 and modality variants different from the configuration of a brake pad according to the invention, Figure 7 a perspective view of a second variant of modality a disc brake according to the invention, Figure 8 a perspective view of the brake support of the modality variant shown in Figure 7 of the disc brake, Figure 9 a perspective view of the brake pad of the modality variant shown in Figure 7 of the disc brake, Figures 10a-10c modality variants different from the brake pad configuration of a brake pad according to the invention, Figure 11-12 other side views of the modifications of a brake support according to the invention, on the brake pad installed on it.
[0033] In the description of the subsequent figures, the terms, such as top, bottom, left, right, front, back etc. they refer, substantially, to the representation and exemplified position of the disc brake, selected in the respective figures, the cladding support plate and the brake support according to the figures. In another mounting position, the coordinate system used for the description moves together.
[0034] In a Cartesian coordinate system, the Z axis is parallel to the axis of rotation of the brake disk (in C, see Fig. 4aa and 5), the X axis extends perpendicular to the axis of rotation of the brake disk (in C, see Fig. 4a), along the axis of rotation of the brake disc or parallel to that line and the Y axis extends parallel to the X axis and the Z axis, The Y axis extends, still, preferably , by the center of gravity of the brake pad, approximately in the center of the casing pit (in the circumferential direction).
[0035] In Figure 2 a detail of a brake disc is shown in a schematic representation. In this case, with the reference sign 42, a lining support for a brake pad 4 is designated, on whose rear side, which is not seen in Figure 2, a brake pad 41 (which can be identified in the Figures 5, 7 or 10). The liner bracket 42 of the brake pad 4 is stationarily mounted on the side of the vehicle on a brake bracket 1 and is retained on the side of the brake caliper with the aid of a liner clamp 6 on the brake bracket 1.
[0036] The brake support 1 can, in this case, be formed as a separate component, as shown here, or be formed as an integral part of the brake caliper 8. For fixing the brake support 1 on a vehicle axle, it is usually provided with holes 7, into which screws or pins can be inserted and which retain the brake support on the vehicle axle. Another support element for support and / or support of the brake pad 4 is also conceivable.
[0037] The brake support 1 covers or covers, as shown in Figures 4a, b and 7, in the form of a frame a radially external section of the brake disc 5 and consists, substantially, of two support horns 2, 3 , connected to each other by bridge parts 11 and arranged one behind the other in a plane parallel to the braking surface of the brake disc 5, which support the brake support plate 42 of the brake pad 4 laterally, that is, in the side of the entrance and side of the exit.
[0038] The brake support 1 shown in Figure 7 covers the brake disc both on the side of the action and also on the side of the reaction. A variant of the brake support modality for supporting the brake pad is also conceivable only on the action side or only on the reaction side. The brake pad 4 located on the other side of the brake disc 5, in this alternative mode variant, is preferably retained directly in the brake caliper 8. The brake caliper 8 is preferably a brake caliper arranged in a movable mode on the brake bracket.
[0039] The liner support plate 42 of the brake pad 4 is located, in this case, in the inserted state, without play or practically without play, in the liner well of the brake support 1, formed by the support horns 2, 3 and the bridge part11 that connects them, partially open radially outward,
[0040] In this case, the support horn 3 on the entry side of the brake support 1 contrary to the disc brakes according to the state of the art, as shown in an example in Figure 1, is not formed as support 102 , with a straight support surface 104 facing the brake pad, but has a recess 32, which receives an offset 424 on the support surface 422 of the liner support plate 42, adjacent to the support horn 3 on the inlet side. brake support 1.
[0041] The recess 32 and the offset 424 on the support surface 422 of the cladding support plate 42 adjacent the support horn 3 of the brake support 1, in this case, are formed in such a way that the brake pad 4 is displaceable around a rotary axis parallel to the rotation axis C of the brake disk 5 (shown in Figure 4a), in the opposite direction to a main rotation direction HDR of the brake disk 5. The undercut 32 extends, in this case, as a projection in the direction of the main rotation direction HDR of the brake disc 5 and is engaged underneath by the liner support plate 42, particularly by the displacement 424 mentioned above on the inlet side, that the brake pad 4 cannot be removed directly radially in relation to the center point of the brake disc C of the brake support 1.
[0042] The support horn 2 on the outlet side of the brake support 1 and the support surface 41 of the liner support plate 42 adjacent to it are correspondingly formed in such a way that the brake pad 4 can be moved around of the rotary axis parallel to the rotation axis C of the brake disk 5, in the opposite direction to the main rotation direction HDR of the brake disk 5. Consequently, the brake pad 4 is retained in such a way in the brake support 1 that in the assembly and disassembly, a pivoting movement or a combined pivoting and radial movement is required, and the radial movement, when disassembling the brake pad 4, takes place after the brake pad 4 outflow of the recess 3 or, in the assembly of the brake pad, before the brake pad inlet turn 4 on the groove 32 of the support horn 3 on the inlet side. This ensures simple assembly and disassembly of the brake pad 4 on or on the brake support 1.
[0043] As can be seen in Figure 2, the support surface 4 of the liner support plate 42, adjacent to the support horn 2 on the outlet side of the brake support 1, presents, for this purpose, a displacement 43 which covers, at least partially, the support horn 2. The arrangement and configuration of the displacements 43, 44 of the liner support plate 42 with the friction liner 41 disposed therein, as well as of the lowering 32 of the brake support 1, they are, in such a case, that both the liner support plate 42 and the brake support 1 preferably take on an asymmetrical configuration, which is advantageous both for the assembly and disassembly of the brake pad, as well as for the improved support of the brake pad or liner support plate 42 on the brake support 1.
[0044] The rotating shaft, by which the brake pad 4 is movable, is preferably located on the support surface 422 of the liner support plate 42 adjacent to the support horn 3 on the inlet side of the brake support 1 , next to a head 33 of the support horn 3 on the inlet side, preferably within 20 mm (<= 20 mm), next to head 33 of the support horn 3 on the inlet side.
[0045] In the brake supports and cladding support plates according to the state of the art, the brake support 100 (shown in Figure 1) is formed with, in each case, support horns 101, 102 on the entrance side and on the outlet side, which support the lining support plate 105. For mounting or dismounting the lining support plate 42 105, it is already inserted vertically into the gap between the two support horns 101, 102, the horns being support struts 101, 102 extend to the edge located radially outward or approximately to the edge of the cladding retainer support 105. In that case, both the inner surfaces of the support horns 101, 102 as well as the support surfaces 103, 104 adjacent to support plate 105 are formed as flat surfaces. In particular, the support horn 101 on the outlet side must, in this case, overcome a high concentration at the upper end, which is associated with a very high load and deformation of the support horn, as well as with an unfavorable force distribution in the support. brake pad 100 and the liner retaining bracket 105 of the brake pad.
[0046] On the other hand, as shown in Figures 2, 3, and 4a through 4d, particularly the support horn 2 on the outlet side is formed in a lowered or flatter way, so that an upper support point A of the cladding retaining bracket 42 on the support horn 2 on the steel side is not located at the upper end of the support surface 421, but radially below a force action line FRxge, which represents the total frictional force acting on the brake pad 4, as shown, particularly, in Figure 4b. This force action line FRxge is located, in this case, radially at the height of the brake pad's center of gravity. In this case, the contact point on the brake pad is approximately in the center or below the center of the support surface 421. As a result, in a braking process, a defined torque around the Z axis acts on the retaining bracket. coating 42 of the brake pad 4. By this torque, also in the support horn 3 on the inlet side it generates a supporting force on the lowering 32 and the displacement 424 and therefore also the inlet side of the substantially brake 1 it is included in the force flow during a braking process.
[0047] The support horn 2 on the outlet side and the support horn 3 on the inlet side have at the foot of the respective support horn a support surface 21, 31, which extend parallel to each other or, preferably, as shown in Figure 2, they move away from each other, at an acute angle to a straight line parallel to the y-axis of the coordinate system defined below.
[0048] The length of these support surfaces 21, 31, which partially surround, laterally, the coating retaining support 4, preferably makes up approximately half or less than the height hg of the support support plate in that cos. cladding 42, in order, on the one hand, to allow the entry or exit of the cladding support plate 42 in or of the brake support 1 and, on the other hand, to keep as little as possible the torque acting during the support horn on the side of the output during a braking process.
[0049] Above the support surface 21 documents 2 on the outlet side, the support surface 21 falls off the cladding support plate 42 towards an oblique surface 22, according to the configuration of offset 43 on the support 4 of the liner support plate 4.
[0050] Above the support surface 31 of the support horn 3 on the entry side, the support surface tumbles from the cladding support plate 42 inward, under the formation of the undercut 32, according to the configuration of the displacement 44 on the surface support 42 on the inlet side of the liner support plate 4.
[0051] In Figure 3 it is shown, in particular, the assembly or disassembly of the cladding with that of the cladding support plate 42 in or of the brake support 1. As can be clearly seen here, by a simple rotating movement, the plate casing support 42 is taken out of engagement with the recess 3 in the head 33 of the support horn 3 on the inlet side.
[0052] In Figures 4a to 4d, in addition to the components, arrows are represented that represent forces of the forces that act in different points of the components. With C, the axis of rotation of the clamping device 5 is designated here, which at the same time is defined as the Z axis of a Cartesian coordinate system. The X and Y axes of this coordinate system serve as the horizontal dashed line (X axis) and the vertical dashed line (Y axis), which intersect orthogonally in C.
[0053] Looking more closely at the forces on the brake pad 4 in the plane and assuming, in particular, not more simply a short angle, but a covering angle Φ of the coating in the circumferential direction, which is slightly larger (and which, preferably, seen in the radial center, is greater than 25 °, particularly preferably greater than 35 °) then it is valid (see Fig. 4a): For the half of the coating on the inlet side:
[0054] In the x direction (observed in a Cartesian coordinate system with a) the axis of rotation of the disk as the Z axis, b) a vertical Y axis at the same, which crosses the Z axis: and c) with an X axis, which crosses the Y axis, but does not cross the Z axis):
where: p: brake pad surface compression b: lining width rm: friction radius μ: lining friction value <p: angle formed in the direction and inlet or outlet K: angle formed in the direction of inlet or outlet at the contact point of the support horn on the inlet or outlet side FRx: frictional component of the liner on the liner side entering the x direction
[0055] The friction radius rm is assumed to be located radially in the center of the brake disc or brake pad.
[0056] Coating frictional forces acting in the x direction must be received by the brake support horn 2 on the outlet side.
[0057] In the y direction:
With
[0058] FRye: frictional component of the coating on the side of the coating entering the y direction
[0059] The frictional forces of the coating cause the brake pad to be removed from the brake support shaft.
[0060] For half of the coating on the outlet side, it is worth:
[0061] In the x direction, the relationship, due to the direction of action of identical force, can be assumed without modification by the half coating on the entrance side.
[0062] In the y direction, the relation is valid as above, but with a changed sign. The forces here cause the brake pad to compress into the brake support shaft.
with
[0063] FEya: friction force component of the coating on the side of the coating exiting in the y direction
[0064] Due to these facts, an asymmetric force action results in the brake pad in the y direction.
[0065] All the frictional force of the coating acting in the x direction is:

[0066] FRx: friction component of the liner on the liner side exiting in the x direction
[0067] FRxges: total coating frictional force in the x direction.
[0068] This force needs to be received by the support horn 2 on the side of the outlet alone.
[0069] Now, observing the balance of forces and moments around the Z axis at a point A at the contact point of the support horn on the outlet side (Fig. 4b) with the inclusion of the previously determined relations, result the following equations:

[0070] Fcy: support force on the support horn that is entering the y direction
[0071] Fay; support force on the support horn that is coming out in the y direction
[0072] l: brake pad lining length 4
[0073] h: distance from the line of action and force to the support point (A) on the support horn 2 on the outlet side
[0074] From this equation, it is surprisingly evident that by a corresponding configuration of the brake support 1, a supporting force can also be generated on the input side.
[0075] To achieve this, it is advantageously foreseen to prevent the brake pad 4 on the brake support 1 from being withdrawn on the inlet side. This can be achieved, for example, by a projection on the brake pad 4 (see Fig. 2 ), which is inserted in the brake support 1.
[0076] This equation containing the h / l ratio also shows that, surprisingly and advantageously, by a radial support point A, relatively low radially on the outlet side, can be performed particularly easily by lowering the support horn 2 in relation to the inlet support horn, increase the support force in the inlet support horn 3. (h should be as large as possible; support point A is, in particular, the outermost / highest support point A in radial direction).
[0077] By the measures described, a more favorable force distribution is obtained on the brake support 1. Conventional brake supports, without support on the inlet side of the brake pad, have a high concentration of the coating support forces on the brake horn. support on the outlet side.
[0078] The frictional force component on the inlet side of the liner, which acts in the y direction, on conventional brake supports needs to be introduced in the caliper support, mainly through the friction contact between the liner support plate 42 and the brake caliper or the pressure parts. The frictional force components on the side of the liner lead to a high load on the clamp support. In order to avoid premature wear or failure, therefore, a relatively large dimension is required and, therefore, demanding in construction space.
[0079] There is also the possibility that in a friction connection that is too small between the brake pad and the brake caliper or the pressure parts (such as, for example, in the presence of grease or oil), the removal of the pads may occur brake and thus lead to malfunction of the brake.
[0080] As described above, the brake pad 4 must be suspended on the side of the entrance in the brake support 1. To ensure simple assembly and disassembly, the assembly and disassembly must therefore take place by a movement rotating brake pad 4. To make this possible, the support horn 2 on the outlet side and the contour of the liner support 42 have an inclined support surface, as shown in Figures 3 and 6.
[0081] The angle of inclination α of the support horn 2 on the side of the output to the axis, however, cannot be freely selected. On the one hand, the minimum oblique position is determined by the conditions of assembly and disassembly. On the other hand, the maximum permissible oblique position is predetermined by observing the self-inhibition limit. If the autoinhibition limit is exceeded, a tangential sliding of the brake pad 4 could occur. The autoinhibition limit depends decisively on the geometry of the liner, the conditions of friction in the liner support and the direction of force introduction between brake pad 4 and brake support 1.
[0082] The physical relationships are represented in Fig. 4c and determined by the following equations. By the angle of action of force y valley:
and FaR = FaT (condition for autoinhibition) follows: α = y + arctanμa With:
[0083] Y: force actuation angle on the support horn on the side of the outlet 2
[0084] α: angle of inclination of the support surface on the support horn 2 on the outlet side
[0085] Fa: full support force on the output support horn
[0086] FaN: normal force on the exit support horn (perpendicularly to the support surface)
[0087] FaT: tangential force in the exit support horn (parallel to the support surface)
[0088] μa: friction value on the lining support on the outlet support horn
[0089] The above equation defines the autoinhibition condition for the inclination angle α of the support horn 2 on the outlet side, depending on the angle of force introduction y and the friction μa at the support point.
[0090] To ensure that the coating 4 does not slide tangentially on the support of the support horn 2, the angle α needs to be selected significantly less than calculated with the help of the above ratio.
[0091] Taking into account realistic friction conditions (μa = 0.1 to 0.2) in the support horn of the usual measures for brake pads in heavy utility vehicles, the angle α values between min. 8th and max. 30 °.
[0092] The considerations made above apply to the braking process in the forward direction. However, in order for braking processes to be possible in the back direction without impairing function, the brake support horn 3 oriented at the entrance in the forward direction must have a minimum height. Here, the conditions as usual in conventional brake supports apply. It is advantageous when the brake caliper height must be greater than the radial height position of the line of action oriented in the circumferential direction of the frictional forces of the coating. This ensures that no withdrawal torque is generated by the brake pad support in the brake pad. The measure of displacement v of the two lines of action is visible in Fig. 4d.
[0093] As reversing brakes in traffic vehicles on the road are, in general, significantly more frequent and with less force, the driving of the lining for reversing brakes can be carried out therefore, in a simplified way compared to forward braking.
[0094] Due to the requirements described above for braking in forward gear and the requirements regarding the assembly and disassembly of the coating, as well as the requirements regarding the support of the coating in braking in reverse, it results in system reason, an asymmetric geometry for the brake pad 4.
[0095] Typically for asymmetric lining and brake support geometry, a relatively low support horn on the side of the exit-oriented brake support, an oblique position of the support horn lining support on the exit side, the angle of the oblique position is preferably 8o <= α <= 30 °, a mesh between brake pad 4 and brake support horn 3 on one side of the brake support 1 (for example, by a protrusion on the brake pad and a corresponding notch on the support horn 3), as well as a relatively high support horn 3 on the side of the brake support oriented towards the outlet.
[0096] The following variables are still defined in Fig. 4b: Fey: reaction force on the inlet side, l: lining length, FR: friction force of the brake pad, h: distance from the action line and force for the support of the coating; fax: backing force of the coating: Fay: reaction force on the output side.
[0097] It is important that due to the formation according to the invention of the support horns 2, 3 and the support surface 41, 42 of the cladding support plate 42, not only the support horn 2 on the outlet side, but also the support horn 3 on the inlet side 3 contributes to support the cladding support plate 42 in a braking process.
[0098] With reference to the forces and moments in the brake pad around the vertical axis (y axis), in the displacement of the brake pad, under the action of the force in the x direction, represented in Figure 5, the following equations are valid:

[0099] FZ :: clamping force
[00100] FP compression force of the coating on the brake disc
[00101] FRa; frictional force on the output side
[00102] FRe; frictional force on the input side
[00103] d: coating thickness
[00104] x: distance from the action line and clamping force
[00105] For asymmetry of the action of the force on the brake pad or on the cladding support plate 42, therefore, it is worth:

[00106] For FRe = 0 (incoming frictional force) and FRa = 0 (outgoing frictional force), as well as d = 0 (coating frictional force and supporting force on the same plane) is worth:
(ideal state, since there is uniform force distribution in the coating)
[00107] For a conventional brake pad, without friction force on the brake pad support horn on the inlet side, it is worth:

[00108] For a brake pad 4 with frictional force on the brake support horn 3 on the inlet side, the relationship derived previously applies:

[00109] A brake support 1 with frictional force on the brake support horn 3 on the inlet side therefore has a more favorable force distribution over the term (FRel) than a brake pad without frictional force on the side of the entrance.
[00110] By the displacements 423, 424 on the support surfaces 421, 422 of the cladding support plate 42 and the recess 32 in the support horn 3 on the inlet side, the cladding support plate 42 can be inserted loosely or practically loosens on the liner support 1.
[00111] Other modality variants shown in Figures 6a to 6e of the cladding support plate 42 and corresponding configurations of the support horns 2,3 of the brake support 1 are also conceivable.
[00112] Thus, in Figure 6a, a rectangular displacement projection with support surfaces 423, 424 extending parallel to the X axis is molded on the inlet and outlet side in each case. that the surface 4241 on the inlet side of the displacement 424 rests on a recess 32 of the support horn 3 on the inlet side, correspondingly aligned, and the support surface 423 on the outlet side rests on the support 2 on the outlet side.
[00113] In the modality of modality shown in Figure 6b, the displacement projections 423, 423 are formed as roundings, which rest on recesses formed correspondingly to the support horn 3 on the entrance side and a support surface 22 formed by corresponding mode 22 of the support horn 2 on the outlet side.
[00114] In the modality of modality shown in Figure 6c, the displacement 424 on the input side 422 is formed as a semicircle-shaped cavity. The inlet side 421 of the liner support plate 42 is shaped in the form of two straight surfaces extending annularly to each other, for support on the support horn 2 on the outlet side.
[00115] The cladding support plate 4 shown in Figures 6d, 6e and 9, is distinguished by the fact that on the entrance side a rectangular projection 424 is arranged on a lateral surface 422 projected outwards at an acute angle β, which can be inserted into a recess 32 correspondingly formed from the support horn 3 on the entrance side. In this case, the height hv of offset 424 of Figure 6d is less than the height hv of offset 424 of Figure 6e. On the outlet side, the side surface 421 of the liner support plate 4 is formed centrally as a side surface 423 projecting outward at an acute angle a.
[00116] Preferably, for better ability to insert the cladding support plate 4 into the groove 32 of the support horn 3 on the entry side, the edge region 430 adjacent to the upper side 428 and the edge region 432 adjacent to the side bottom 427 of the liner support plate 4 are formed in a slightly flattened manner.
[00117] Likewise, a partial surface 4242 of the rectangular displacement or displacement projection 424, pointed in the direction of the rotation axis of the brake disc 5, is provided with a flattening 4243, to facilitate the pivoting movement of the brake pad 4 outwards of the coupling with the brake bracket 1.
[00118] The offset 424 is molded, in this case, according to a variant of preferred modality, in one piece on the liner support plate 42. Alternatively, it is also conceivable to fix the offset 424 on the liner support plate 42 as a component separate.
[00119] Figure 7 shows a fashion variant of the brake support 1, which is suitable for the brake pads 4 shown in Figures 6d and 6e, with two brake pads 4 inserted in the brake support 1. The brake support 1 without the brake pads is shown in Figure 8. It can be clearly seen that the asymmetric construction of the brake pads and the configuration of the brake support components 1, which receive the brake pads 4, particularly the head 33 of the brake pad. support horn 3 on the inlet side, as well as the v-shaped spacing of each other from the brake lining well of the brake support, formed by the support horns 2,3.
[00120] The brake pad 41 disposed on the brake pads 4 is shaped, preferably according to the asymmetric configuration of the liner support plate 42, as shown in Figures 10a and 10c. Partial part 413 covering the displacement 424 of the liner support plate 42 of the brake pad 41, preferably divided into two partial parts 411, 412, is formed, in this case, preferably, in a part with one of the two partial parts 412, but can also be mounted, in a variant of the brake pad modality, with an offset 424 formed separately, together with the offset 424 in the brake pad. It is also conceivable not to mount any friction linings at offset 424, as shown in Figure 10b.
[00121] Figures 11 and 12 show side top views of the brake support shown in Figure 7 and the brake pad 4, once with representation of the brake pad lining support plate 42 (Figure 11) and, in the another case, with a representation of the friction lining 41 of the brake pad (Figure 12). It can be seen clearly, also here, that the support horn 2 on the outlet side is formed asymmetrically in relation to the support horn 3 on the inlet side of the brake support 1, in relation to a symmetry axis, which cuts the insert brake 4 in half and extending through the rotation axis C of the brake disc 5.
[00122] With the cladding support plates 4 and brake supports 1 molded according to the invention, therefore, an improvement in the force distribution is achieved by a friction connection support on both the inlet and outlet side. In addition, there is a more uniform introduction of the forces transmitted in a braking process by the brake pad 4 to the brake support 1, which is associated with a more uniform demand of the brake support 1 or the brake caliper and the brake elements. fixing the brake on the axle supporting the brake support 1. In addition, a reduction in crashing noise is also achieved by radially conducting the brake pad 4 on the brake support 1. REFERENCE LISTING I brake support II part of bridge 2 support horn 21 support surfaces 22 support surface 23 upper side 24 support surface 25 support horn 32 support surfaces 32 recess 33 head 34 support surface 35 brake pad 41 friction coating 42 coating support plate 421 support surfaces 422 support surfaces 423 offset 424 offset 4241 top side 4242 bottom side 4243 flattening 4244 side surface 425 support surfaces 426 surface support ies 427 bottom edge 428 top edge 429 attachment for liner retention spring 430 edge region 431 support surfaces 432 support surfaces 43 brake disc 44 liner retention clamp 45 hole 8 brake caliper 100 brake support 101 support horn 102 support horn 103 support surfaces 104 support surfaces 105 cladding support plate C axis of rotation, coordinate center The point of application of HDR force main direction of rotation of the brake disc hB height of the plate liner retention hTe height of the support horn on the inlet side hTa height of the support horn on the outflow side v: displacement of the action lines braking force in reverse gear x: distance from the compression force of the liner to the FR coating support point: total coating friction force FRw: coating friction force when reversing braking Farw: coating support force when braking ma rear-end FZ: clamping force FP: compression force of the coating FRa: frictional force on the support surface of the support horn on the outlet side FRe: frictional force on the support surface of the support horn on the side Entrance

权利要求:
Claims (18)
[0001]
1. Disc brake of an automobile, particularly of a utility vehicle, which has a brake caliper (8), which covers a brake disc (5), which has a brake support (1), which can be fixed a vehicle stationary mode, in which at least one brake pad (4) is provided, provided with a liner support plate (42) and a friction liner (41) attached to it, the brake support ( 1) features in a main direction of rotation (HDR) of the brake disc (5) on the inlet side and on the outlet side of the liner support plate (42) of the brake pad (4) support horns (2, 3) support, the support horn (3) on the entrance side of the brake support (1) and the support surface (422), which is located adjacent to it, of the cover support plate ( 42) engage with each other, characterized by the fact that the support horn (2) on the outlet side and a corresponding abutment contour of the plate liner support (42) have a support surface (21,423) slanted in total, in areas or at least in the radially higher region of the liner support on the brake support by an angle of inclination (α) to the Y axis, being that the angle facilitates the removal and installation of the brake pad (4) through a rotating movement around an axis parallel to the axis of rotation of the brake disc (5), the Y axis being an axis of a brake system coordinates, in which the axis of rotation of the brake disc (5) forms the Z axis, with the Y axis extending through the center of gravity of the brake pad (4) in the circumferential direction at the center of a casing pit, as well as it extends perpendicularly to the axis of rotation of the brake disc (5) and crosses it, and the X axis perpendicularly to the Z axis and the Y axis.
[0002]
2. Disc brake, according to claim 1, characterized by the fact that the angle of inclination (α) is less than the sum of an angle of introduction of force (y) and the Arcus T angens of a value of friction μa, at the support point (A) on the support horn (2) on the outlet side.
[0003]
3. Disc brake, according to claim 1 or 2, characterized by the fact that for the angle of inclination (α) it is valid: 8o <α <30o.
[0004]
Disc brake according to one of the preceding claims, characterized by the fact that the brake pad (4) is supported by a support point (A) on the support horn (2) on the outlet side, which it is located below a force action line (FRxges) that represents the total frictional force, which acts on the brake pad (4).
[0005]
Disc brake according to any one of the preceding claims, characterized by the fact that the support horn (2) on the outlet side is formed in a lowered way in relation to the support horn (3) on the inlet side.
[0006]
6. Disc brake according to any of the preceding claims, characterized by the fact that - as seen in the X direction - the highest support point (A) on the support horn (2) on the outlet side is at a distance (H)> 0 to the force action line (FRxges) and is below the force action line.
[0007]
Disc brake according to claim 6, characterized by the fact that the distance (h) from the support point (A) on the support horn (2) on the output side of the force action line (FRxges) makes at least 0.1 times the length (1) of the brake pad (4) in the direction of the force action line (FRxgds).
[0008]
Disc brake according to any one of the preceding claims, characterized by the fact that the support horn (3) on the entry side is higher than a point of intersection of the force action line (FRxges) with the support horn (3) on the entry side.
[0009]
Disc brake according to any one of the preceding claims, characterized by the fact that the support surface (422) of the cladding support plate (42), adjacent to the support horn (3) on the inlet side of the brake support (1), presents a displacement (424), which engages in a recess (32) in the support horn (3) on the entrance side, corresponding to the displacement (424).
[0010]
Disc brake according to any one of the preceding claims, characterized by the fact that the support horn (3) on the side of the brake support inlet (1) and the support surface (422) adjacent to it cladding support plate (42) interlock with each other with a positive fit.
[0011]
11. Brake pad (4) for a disc brake, according to any one of the preceding claims, with a cladding support plate (42) and a friction lining (41) attached to it, the plate being cladding support (42) has side surfaces (421, 422) for support on the internal side walls of support horns (3) of a brake support (1) or of another support element, being that in at least one of the lateral support surfaces (421, 422) a displacement (423, 424) is provided for fixing by positive fitting in one of the internal walls of the support horns (3) of the brake support (1) or of the other support element, characterized by the fact that the covering support plate has, in the circumferential direction, a support contour on the side of the outlet to rest on a brake support (1) and the support contour on the outlet side of the support plate of cover (42) has a supporting surface (21, 423) inc aligned to a Y axis by an angle of inclination (α), the angle facilitating the removal and installation of the brake pad (4) through a rotary movement around an axis parallel to the axis of rotation of the brake disc ( 5), the Y axis being an axis of a coordinate system, in which the axis of rotation of the brake disc (5) forms the Z axis, with the Y axis extending through the center of gravity of the brake pad. brake (4) in a circumferential direction in the center of a casing pit, as well as extending perpendicularly to the axis of rotation of the brake disc (5) and crossing it, and the X axis perpendicular to the Z axis and the Y axis.
[0012]
12. Brake pad according to claim 11, characterized in that the angle of inclination (α) is less than the sum of an angle of introduction of force (y) and the tangent arc of a friction value μa at the support point (A) on the support horn (2) on the outlet side.
[0013]
13. Brake pad according to claim 12, characterized by the fact that the angle of inclination (α) is between 8 ° and 30 °.
[0014]
14. Brake pad according to any one of the preceding claims, characterized by the fact that, on the entrance side, a rectangular displacement (424) is formed on a side surface (422) of the cladding plate and in which the offset (424) on the inlet side is formed close to a lower side (427) of the liner support plate (42).
[0015]
15. Brake pad according to claim 14, characterized in that the displacement (423, 424) is formed as an attached part that protrudes from the lateral support surface (421, 422).
[0016]
16. Brake pad according to claim 15, characterized in that the offset (424) is formed as a trapezoidal protrusion, particularly rectangular.
[0017]
17. Brake pad according to any of the preceding claims related to the brake pad, characterized by the fact that the liner support plate (42) is formed asymmetrically as a result of the displacements (423, 424).
[0018]
18. Disc brake according to any of the preceding claims, characterized by the fact that the angle (Φ) covered by the friction surface of the brake liner in the circumferential direction is greater than 25 °, particularly greater than 30 ° °.

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法律状态:
2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

2020-06-16| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

2021-01-26| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

2021-03-09| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 13/09/2012, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

申请号 | 申请日 | 专利标题

EP11181212.9|2011-09-14|

EP11181212.9A|EP2570689B2|2011-09-14|2011-09-14|Disc brake of a motor vehicle and brake lining|

PCT/EP2012/067926|WO2013037876A1|2011-09-14|2012-09-13|Disc brake for a motor vehicle and brake lining|

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