Motor vehicle disc brake friction pad with wire coil spring clamped in place across saddle projection

Abstract

This invention relates to a friction lining (1) for a motor vehicle disc brake, preferably having a hammer-shaped design and a wire coil spring (5) in the form of a compression spring, which is mounted in a clamping fit and radially fixed to a spring saddle (6) from the outside in a straddle manner. The object of this invention is to provide a friction lining spring mounting system with further improved air gap behavior and improved radial spring mounting characteristics, so that the associated wheel braking system can operate appropriately and advantageously as required in terms of life cycle assessment. This objective is essentially achieved by the fact that the wire coil spring (5) is formed of a rust-free alloy steel wire material; formed of a rust-resistant steel wire material (surface-treated steel wire material, especially sheathed, painted, coated, etc.), and the support arm (10, 10') engages with the shaped profile above the higher level central protrusion (4) of the support plate (2), such that the support portion is arranged substantially centrally relative to the longitudinal axis C, BPCL passing through the support plate and aligned with the longitudinal axis, and wherein, at the same time, the height level of the support portion is reduced by the fact that the height level is arranged substantially radially below the height level of the protrusion (4) relative to the radial axis R (vertical axis).

Description

Technical Field

[0001] This invention relates to a hammer-shaped friction pad 1 for a motor vehicle disc brake, comprising a wire coil spring 5 in the form of a compression spring, which can be mounted in a clamping fit and radially fixed to a saddle protrusion from the outside in a straddle manner. The spring mounting arrangement serves to apply a substantially radially inwardly oriented spring preload to the friction pad 1 on which the spring is mounted, such that the friction pad 1 is mounted with a certain elastic preload on and within a receiver in a retaining component (i.e., the combined spring preload is oriented radially inward toward the hypothetical wheel axis of rotation). This spring force preload on the friction pad, for example, helps to suppress unwanted rattling noise caused by vibrations due to, for example, uneven road surfaces. Background Technology

[0002] DE 103 51 477 B4 describes a known disc brake pad with a hammer-shaped backplate. Here, a central spring saddle protrusion allows for a relatively large volume of friction material and allows for the radial mounting of a compression spring, which in its embodiment is inserted as a wire helical spring type compression spring for straddle-mounting within the spring saddle protrusion. The spring saddle is distributed within a chamber of the protrusion and is integrated in a stepped configuration axially inward and rearward relative to the longitudinal axis of the backplate. The spring saddle includes a narrowed retaining edge that engages and clamps between helical coils in a form-locking manner, and this narrowed retaining edge defines the chamber. One or more right-handed helical spring coils are centrally arranged between two spring arms, which, as seen in the front view, are curved to extend horizontally to the sides. A particular advantage of this known construction is that, because the friction pads can be displaced with exceptional precision during operation, uneven loading of the friction pad assembly during operation is avoided. To further enhance spring elasticity, it is recommended that the wire helical spring be provided with multiple additional circular winding portions.

[0003] Recent practical experiments are driving further development, as the latest specifications from automotive customers define further improvements in air gap behavior, including, for example, the requirement for more agile exhaustion of remaining braking torque (as a response to confirmation of brake release requirements). Based on this, the objective of this invention is to provide, relative to the prior art, a friction liner spring mounting system with further improved air gap behavior and improved radial spring mounting characteristics, so that the associated wheel braking system can continue to operate as needed. Summary of the Invention

[0004] For the purpose of solving the problem for the first time (i.e. in a novel way), a special type of wire helical spring is first proposed, followed by a system of friction linings for motor vehicle disc brakes with wire helical springs, and a special type of motor vehicle wheel brake of the disc brake type is proposed. Based on the characteristics of one or more of the two solutions mentioned above, the above solutions are, in principle, very independent of each other and are separate.

[0005] Accordingly, the present invention is entirely different from the prior art. According to the present invention, to address existing problems, the characteristic features of motor vehicle disc brake pads are illustrated by way of example. Separately coordinated solutions arise from separately coordinated features, including individual wire coil springs or motor vehicle wheel brakes. Accordingly, the present invention allows for a novel radial spring mounting arrangement that allows for improved air gap behavior through a practically operable curved shape with a particularly space-saving compact design. Simultaneously, this novel radial spring mounting arrangement can be assembled in a fault-proof manner (reversibly, i.e., without directional dependence relative to the vertical axis) and with reduced tilting tendency. Here, the present invention is associated with the specific advantage that not only new vehicles but also existing wheel brake systems in existing older vehicles can, in principle, be enhanced by adapting friction pads to the required improvements of the wire coil springs according to the present invention. Attached Figure Description

[0006] The present invention will now be described in detail with reference to the accompanying drawings.

[0007] Figure 1a A perspective view of a conventional brake pad retaining spring is shown for illustration purposes;

[0008] Figure 1b To illustrate, a conventional spring is shown that integrates a hammer-mounted brake disc, brake bracket, and brake and caliper system.

[0009] Figure 1c To illustrate this, a graph showing the interaction and tension characteristics of a conventional brake disc spring under different braking pressure levels and temperatures during use and release is presented, demonstrating a significant overall delay under rigid resistance effects.

[0010] Figure 2a A perspective view of one embodiment of the wire spiral retaining spring according to the invention is shown;

[0011] Figure 2b A wire spiral retaining spring according to the invention is shown, integrating a hammer-shaped brake disc brake bracket and a brake caliper system;

[0012] Figure 2c A graph showing the interaction between the brake disc spring and the braking system according to the invention is presented under different braking pressure levels and temperatures during use and release of the disc brake, exhibiting negligible delay and low drag effect.

[0013] Figure 3 yes Figure 2a The cross-sectional view of the spring shown is shown.

[0014] Figure 4 yes Figure 2a The side view of the spring shown;

[0015] Figure 5 yes Figure 2a Top view of the spring shown;

[0016] Figure 6 yes Figure 2b Another perspective view of the spring according to the present invention is shown;

[0017] Figure 7 For ease of understanding and clarity, the following is shown: Figure 2b Enlarged image;

[0018] Figure 8 This is an embodiment of a single-spring calibration step, which is a suitable example of press-fitting in a series of multiple processing steps;

[0019] Figure 9 yes Figure 7 A cross-sectional view of an embodiment of the assembled brake components shown;

[0020] Figure 10 This is a top view of a preferred embodiment of a brake pad system having a spring seat and a mounted retaining spring. Detailed Implementation

[0021] This friction lining invention enables a significant and correct technical contribution to reducing CO2 emissions from vehicle fleets by: the wire coil spring being formed from a rust-free alloy steel wire material; or from a rust-resistant steel wire material (surface-treated steel wire material, particularly sheathed, painted, coated, etc.), which allows for sustainable raw material recycling; and the arms 10, 10' engaging with the protrusion 4 by means of a shaped profile, such that the support portion is arranged substantially centrally relative to the longitudinal axis passing through the friction bearing plate 2 and aligned with that longitudinal axis, and wherein, simultaneously, the height level of the same support portion is lowered relative to the periphery by the support portion being arranged substantially radially below the height level of the protrusion relative to the radial axis (vertical axis).

[0022] This invention achieves extremely high precision while also being suitable for mass production. It can be flexibly, energy-efficiently, and sustainably manufactured by incorporating a wire forming machining center, where each wire helical spring 5 is formed from a single wire section through cold working by bending and winding. The required manufacturing step planning and sequence in the progressive system are advantageously based on the fact that at the start of the manufacturing process, the wire forming machining center unravels the desired wire blank section from the semi-finished part spool / endless wire coil to the required length, then trims and cuts the wire blank section, wherein the subsequently calibrated wire blank undergoes the manufacturing step sequence at the machining center.

[0023] The flexural fatigue strength of the wire coil spring 5 according to the invention is improved by providing specific surface treatments to the finished spring parts or spring blanks. Surface treatments may include mechanical surface treatments, such as introducing surface or internal compressive stresses. For this purpose, a particle blasting (especially shot peening) surface treatment process is advantageously recommended. Alternatively or additionally, a surface coating may be provided so that all microcracks are sealed, particularly by means of paint, coatings, etc.

[0024] Each wire coil spring 5 has two defined support contact points K1, K2 at its support portion. These support portions are substantially centered relative to each other, aligned with the longitudinal axis T, and have no axial offset D relative to each other or otherwise. Moreover, these support portions are bent into the shape of a metal ring, so that improper mating can be prevented through structural design. Here, an additional shape is chosen such that the longitudinal axis T passing through the two support contact points K1, K2 is oriented parallel to the central longitudinal axis M, which extends perpendicularly to the winding axis B of the wire coil spring 5.

[0025] The wire coil spring 5 according to the invention also allows for precisely fitted radial spring mounting and prevents damage or injury, providing exceptionally high safety. This is because each support contact point K1, K2 is defined by the end of a wire in the form of a very special, rather uniquely constructed metal ring 12, 12'. The metal rings 12, 12' are closed at the end member side by closed arms 13, 13', each associated closed arm 13, 13' extending from the metal ring 12, 12' and respectively bent at an angle or curve towards the corresponding arm 10, 10' of the wire coil spring. The metal rings 12, 12' are arranged asymmetrically relative to each other on their respective associated arms 10, 10', i.e., bent alternately relative to each other. Furthermore, the shape of the metal rings is chosen such that each preferentially presents half of a so-called "German-style metal ring". In order to prevent damage caused by displacement, incorrect disassembly or other separation of the wire coil spring, the end caps 14 and 14' of the closed arms 13 and 13' of the metal rings 12 and 12' are formed with bevels, rounded corners or other non-sharp edges to prevent cutting.

[0026] For the purpose of utilizing the material’s advantages (safety and durability under load, closed metal-based recycling cycle, strain hardening properties, elastic modulus, ability to be coated, and installation capability), the friction lining bearing plate 2 (back plate) is advantageously configured as a cold-worked steel sheet back plate, which is cut from a thin and flat (i.e., uniformly thick) steel sheet semi-finished material (panel product or coil product).

[0027] The proportions of the components involved are advantageously adapted such that the design thickness d of the support plate 2 is at least approximately equal to or greater than the maximum design width of the wire coil spring 5, such that, as can be seen in the plan view, the wire coil spring 5 does not protrude beyond the side of the support plate or only slightly protrudes beyond the side of the support plate. This advantageous proportional allocation is achieved by the following assistance: at least as can be seen in the projection in one spatial direction, the outlines of all longitudinal axes T, M coincide with and are congruent to the overall center of the support plate 2, and in particular coincide with the overall center.

[0028] Particularly advantageously, if the height levels of the two lowered support contact points K1, K2 of the two support portions are reduced in the peripheral region, and wherein the peripheral region extends at most to the upper edge of the protrusion 4 of the bearing plate 2, but is advantageously located below this upper edge, a tight fit between the components involved can be achieved, and additionally, the radial spring is mounted without lateral and tilting moments. The radially inward boundary of the peripheral region is advantageously chosen such that the height levels of the two lowered support contact points K1, K2 of the two support portions are reduced in the region defined by the friction material coating portion of the bearing plate 2 radially downward (radially inward relative to the hypothetical wheel rotation axis). Recommended, or as an average evaluation, it can be recommended that the height levels of the two support contact points K1, K2 of the two support portions coincide with or are approximately the same as the height level of the winding axis B of the wire coil spring 5.

[0029] Springs produced by deformation and / or stamping according to the present invention may include one or more regions comprising strain-hardened metal. Strain hardening may be provided in the spring in a gradually varying and position-dependent alternating manner. Here, each spring may have arms 10, 10' having one or more regions that, through strain hardening, integrally form peripheral portions 11, 11' and introduce flexural stiffness. In particular, springs designed according to the present invention may have regions with different degrees of strain hardening and / or alternating regions with different degrees of strain hardening.

[0030] Preferably, the peripheral portions 11, 11' are respectively introduced between the winding half and the support portion. Each peripheral portion 11, 11' may be defined by two deformation zones including two bending axes for strain hardening and flexural strengthening purposes. Each peripheral portion 11, 11' may be angled in a non-linear manner and / or be crank-shaped relative to the horizontal direction, particularly inclined obliquely relative to the horizontal direction.

[0031] The support contact points K1 and K2 are offset relative to each other by a certain distance via the lever arm, such that the combined total preload transmitted to the friction lining via the wire coil spring 5 is limited to a maximum of about 70 N or less. The recommended lower limit of the force range is a combined total preload of at least about 5 N. A particularly preferred preload range is concentrated between a maximum of about 40 N-60 N and a minimum of about 10 N. Furthermore, if the conformal clamping fixation between the bearing plate 2 / spring saddle and the wire coil spring 5 is defined based on a determined average clamping force, then as a result, a specific predetermined tension must be applied to release this clamping fixation, wherein the tension is substantially in the range of about 2 N to 20 N in magnitude. For the purpose of simplifying maintenance, it is advantageous to concentrate the tension in a range where the average tension is substantially preferably about 5 N + / - 3 N.

[0032] A particularly robust and corrosion-insensitive design can be obtained by meeting the following conditions: the wire coil spring 5 is made of rust-free alloy stainless steel; or it is made of rust-resistant stainless steel in a bent form (surface-treated stainless steel, especially sheathed, painted, coated, etc.).

[0033] Here, a space-saving design can be provided, specifically a design that encompasses the surrounding support arm. Furthermore, as can be seen at least in a spatial projection, the wire coil spring 5 can be bent into an angled profile in the shape of a bicycle handlebar.

[0034] Each wire coil spring 5 is fixed only to the disc brake pad 1 of the vehicle wheel brake 17, which is directly actuated by means of an actuating element (hydraulic or mechanical). The oppositely positioned disc brake pad 1' is not equipped with a wire coil spring 5 and is indirectly actuated by a reaction force, particularly by means of the brake caliper housing 18.

[0035] The wire coil spring 5 is preferably configured in a space-saving peripheral support configuration for constructing compact hydraulically or electromechanically actuated sliding caliper disc brakes, and is also particularly suitable for and specifically suited for hydraulically sliding caliper disc brakes that can be actuated in combination, wherein the hydraulically sliding caliper disc brake may additionally have an electromechanically actuated parking brake device. Furthermore, it is advantageous if the motor vehicle disc brake friction pad 1 according to the invention is suitable for and specifically suited for motor vehicle wheel brakes 17 at or within the driven passenger vehicle axle, particularly suitable for and specifically suited for special rear axle brakes.

[0036] The bearing plate 2 of the friction lining 1 (which is particularly advantageously made of steel sheet material) is provided with a hooked profile configuration, which is achieved by having two hammer-shaped retaining protrusions laterally on the side for the purpose of engaging with the brake retainer when braking force is introduced. These two hammer-shaped retaining protrusions are formed substantially mirror-symmetrically and opposite in diameter to each other, and wherein the two hammer-shaped retaining protrusions are horizontally aligned below the protrusion 4, such that engagement with the brake retainer when braking force is introduced is at the same level as the brake piston axis or at a lower level below the brake piston axis, or alternatively substantially coincident with the center of the brake lining, and / or distributed in a mixed manner at one or more of the above positions.

[0037] Further details or advantageous features (including any combination of features of the invention) will be embodied in the description based on the accompanying drawings. Here, the drawings systematically illustrate, in some cases, the interaction with other features, parts or components in various views, and schematically illustrate a) the isolation spring 5 as a separate part, b) the friction liner spring assembly, and c) a motor vehicle point-type disc brake 17 including the brake caliper housing 18 and having the friction liner spring assembly.

[0038] The motor vehicle (point-type) disc brake 17 includes disc brake friction pads 1 and 1' as critical wear and replaceable components of the system. Each disc brake friction pad has a support plate 2 partially coated with friction material on at least one side. A wire coil spring 5 is mounted in a clamping fit and straddle-mounted to a protrusion 4 without friction material; this wire coil spring acts as a friction pad compression spring. This is because, when the disc brake wheel brake system is fully assembled, each associated friction pad 1 is received in a stator (typically a so-called brake retainer) and fixed in a non-rotatable manner, and is axially displaceable along a guide, such that the friction pad is pressed against the brake rotor (so-called brake disc) to achieve friction braking requirements. Because the friction pad can impact any component of the brake caliper housing 18 (e.g., the so-called brake housing bridge) via the wire coil spring 5, which is elastically preloaded and supported in the force flow between the housing (bridge) - disc brake pad - stator (brake retainer), the friction pad 1 is permanently and elastically pushed radially inward (i.e., "inward" in the direction of the imaginary wheel axis of rotation), thus preventing the friction pad 1 from moving / passing in the radial direction and disengaging from its (longitudinal) guide, and preventing the friction pad from making any rattling noise on rough roads.

[0039] For directional purposes, in this context, except with reference to a hypothetical wheel rotation axis, the specifications of all directions and axes are, in principle, related to the wire coil spring 5, which is supplied separately as a single part. This is because the specifications are, in principle, defined in relation to the spring winding axis (multiple spring winding axes) which is the basic and manufacturing-related spring axial axis (related to the wire winding machine), and wherein the spring longitudinal axis SCL, M, or the spring vertical axis (i.e., the radial axis) may nominally extend in directions orthogonally offset relative to the spring winding axis, respectively. However, when the system and / or functional coordination of the friction lining 1 and / or the wire coil spring 5 in the wheel brake 17 is relevant or defined, in this context, the specifications of all axes and / or directions should, in principle, be understood as defined in relation to the wheel rotation axis of the motor vehicle.

[0040] The wire coil spring (compression spring) 5 is substantially symmetrical with respect to the radial axis (vertical axis) R and asymmetrical with respect to the longitudinal axes SCL, M and the axial axis. The friction liner support plate (so-called back plate) 2 defines a protrusion 4 with an integrated spring saddle 6 above a friction material coating 3 applied to one side. This spring saddle is also configured as a chamber 7 with respect to the longitudinal axes C, BPCL of the support plate. The spring saddle also has a stepped descending profile and a narrowed retaining edge 8 projecting in a direction toward the center of the chamber 7, wherein the retaining edge 8 defines the chamber 7. Under force-fit and / or conformal extension action, two diameter-displaced and spaced-apart coiled portion regions 9, 9' of the coil springs engage the described spring saddle 6 elastically and resiliently, while simultaneously having a matching retaining function that interacts with the spring saddle. The wire coil spring 5 is fixed to the spring saddle 6 in a form-locking manner with the winding gradient of the wire coil spring limited to right-hand rotation in the forward direction, and is also fixed to the support plate 2 in a manner that prevents relative rotation. In addition, the wire coil spring 5 includes two arms 10, 10', which are oriented substantially in the tangential direction to extend laterally, and these two arms are used for limited elastic abutment when placed on the brake caliper housing 18 by support portions defined at the ends.

[0041] Based on these principles, the wire coil spring 5 according to the invention is formed of rust-free alloy steel wire; or of rust-resistant steel wire (surface-treated steel wire, particularly sheathed, painted, coated, etc.). Particularly preferably, the wire coil spring 5 is formed of rust-free alloy stainless steel; or of rust-resistant stainless steel (surface-treated stainless steel, particularly sheathed, painted, coated, etc.) in a bent form. The arms 10, 10' of the wire coil spring are designed with shaped profiles to engage with the protrusion 4, such that the supporting portions of these arms are arranged substantially centrally aligned with the longitudinal axis C, BPCL passing through the bearing plate 2. Here, this arrangement is precisely adapted in the context of the system such that the height level of the supporting portions is lowered by arranging the supporting portions radially below the height level of the protrusion 4 relative to the radial axis (vertical axis).

[0042] The wire coil springs 5 ​​designed in this way (preferably with a rust-free configuration) are always bent and wound by cold working, thereby fundamentally reducing energy input while achieving high precision and high durability.

[0043] In a further, more detailed description, the support contact points K1, K2 of the two support portions of the wire coil spring 5 are bent substantially centered relative to each other, flush with the longitudinal axis T, without axial offset D. Here, the longitudinal axis T passing through the two support contact points K1, K2 is oriented parallel to the central longitudinal axis M, which extends perpendicularly to the winding axis B of the wire coil spring 5. Each support contact point K1, K2 is defined by metal rings 12, 12'. The metal rings 12, 12' are substantially closed at the end member side by means of closed arms 13, 13', by each associated closed arm 13, 13' being angled or bent to be oriented in the direction from which the corresponding arms 10, 10' of the wire coil spring 5 originate from the metal rings 12, 12'. Here, the metal rings 12, 12' are formed on the respective allocated arms 10, 10' to be oriented by bending asymmetrically relative to each other, particularly in alternating directions. Here, the shape of the metal rings can be defined as the so-called "semi-German metal rings". The end caps 14 and 14' of the closed support arms 13 and 13' of the metal rings 12 and 12' can be formed with bevels, rounded corners, or have some other non-sharp edge to prevent cutting. In particular, the manual assembly of the wheel brake by the technician is supported in a very special and safe manner, or the individual wire coil spring 5 has a special design to prevent cutting.

[0044] It goes without saying that the bearing plate (back plate) 2 of the disc brake liner 1 according to the invention is, in principle, configured as a cold-worked steel sheet back plate, which is essentially composed of conventional structural steel and can be cheaply protected against corrosion by coating and / or painting. Here, the design thickness d of the bearing plate 2 is at least approximately equal to or greater than the maximum design width of the wire coil spring 5, such that, as can be seen in the plan view, the wire coil spring 5 does not protrude beyond the bearing plate 2 or only slightly protrudes beyond it. At least as can be seen in a projection in one spatial direction, the contours of all longitudinal axes T, M coincide with and are congruent to the resulting center of the bearing plate 2, particularly coinciding with it. However, the height levels of the two lowered support contact points K1, K2 of the two support portions decrease in a certain region, wherein said lowered region is defined at least by the upper edge 16 of the protrusion 4 of the bearing plate 2 radially upward (radially outward relative to the hypothetical wheel rotation axis). In a more detailed description, the height levels of the two lowered support contact points K1, K2 of the two support portions decrease in a certain region, and wherein said region is defined radially downward (radially inward relative to the axis of rotation of the imaginary wheel) by the friction material 3 of the bearing plate 3. In a further more detailed description, the height levels of the two support contact points K1, K2 of the two support portions substantially coincide with or are substantially the same as the height level of the winding axis B of the wire coil spring 5. Furthermore, the profile shape of each spring arm 10, 10' includes at least one region or portion that can be understood as a peripheral portion 11, 11', which is integrally introduced in a strain-hardened form, i.e., a flexural rigidity form. Each peripheral portion 11, 11' of the wire coil spring 5 can be introduced separately between the winding half and the support portion. Each peripheral portion 11, 11' with a nearly flexural rigidity design can be defined by two lateral bending axes for local flexural reinforcement (generated by deformation) (strain hardening). Each peripheral portion 11, 11' may be angled in a non-linear manner and / or crank-shaped relative to the horizontal direction, particularly inclined obliquely relative to that horizontal direction. Furthermore, the two support contact points K1, K2 may be offset relative to each other by a certain distance via lever arms, such that the exemplary range of the combined total housing support force transmitted to the applied friction lining (i.e., the elastic preload of the compression spring wire coil spring 5) is limited to at most approximately 40 N - 60 N or less. Conversely, a preferred or exemplary preload range limitation may be provided, which specifies that the combined total clamping force in the force flow of the compression spring is as close as possible to at least approximately 5 N.

[0045] At least as can be seen in a spatial projection, each wire coil spring 5 has a profile bent at an angle in the shape of a bicycle handlebar. In one interpretation of the system construction (which is conserved for its practicality and space-saving form, and thus has a minimalist design), the wheel brake can be specified such that each wire coil spring 5 is fixed only to the disc brake pad 1, which is directly actuated by means of an actuating element, and thus the disc brake pad 1', positioned opposite to the aforementioned disc brake pad, has no wire coil spring 5 and is indirectly actuated by a reaction force, particularly through the brake caliper housing 18. In summary, the wire coil spring 5 of the present invention provides a particularly space-saving peripheral support configuration for a compact, hydraulically actuated and / or electromechanically actuated, and also purely electrically actuated, sliding caliper disc brake 17, wherein, in particular, a solution is also provided for a hydraulically sliding caliper disc brake that can be actuated in combination and can additionally have an electromechanically actuated parking brake device.

[0046] Accordingly, the friction lining 1 of the motor vehicle disc brake according to the invention is particularly preferably suitable for and specifically used for wheel brakes 17 in or at the axle of a driven passenger vehicle, especially suitable for and specifically used for special rear axle brakes.

[0047] For clarity, it should still be noted that the bearing plate 2 of the friction lining 1 according to the invention is provided with a hooked profile configuration, which is due to the fact that the bearing plate 2 can be laterally provided with two hammer-shaped retaining protrusions on its side for the purpose of engaging with the brake retainer when a braking force is introduced. These two hammer-shaped retaining protrusions are formed substantially mirror-symmetrically and opposite in diameter to each other, and wherein the two hammer-shaped retaining protrusions are horizontally aligned and positioned below the protrusions, such that engagement with the brake retainer by introducing force occurs at the same level as the brake piston axis or at a lower level below the brake piston axis, or alternatively substantially coincident with the center of the brake lining, and / or in a mixed form at one or more of the above positions.

[0048] List of reference numerals

[0049] 1. Friction linings for motor vehicle disc brakes

[0050] 2. Support plate

[0051] 3 Friction Materials

[0052] 4. Protrusion

[0053] 5. Metal wire coil spring

[0054] 6. Spring saddle

[0055] 7 chambers

[0056] 8. Hold the edge

[0057] 9, 9' Helical spring winding section

[0058] 10, 10' outrigger

[0059] 11, 11' Surrounding area

[0060] 12' metal ring

[0061] 13, 13' Closed outrigger

[0062] 14, 14' End Cap

[0063] 15' and 15' side protrusions (refer to the load-bearing plate) Figure 10 )

[0064] 16 (the upper edge of the protrusion of the bearing plate 2)

[0065] 17. Motor vehicle wheel brakes (e.g., slipper caliper brakes)

[0066] 18 Brake caliper housing

[0067] 19, 19' (hammer-shaped) retaining protrusion

[0068] 20 Friction Liner Wear Alarm Device (BWE)

[0069] 21. (Electronic) Mechanical (Fixed) Brake Actuation Device

[0070] 22. Service brake device (hydraulic piston) R (radial direction relative to the imaginary wheel axis of rotation)

[0071] Ax (the axial direction relative to the axis of rotation of the imaginary wheel)

[0072] T (tangential direction relative to the axis of rotation of the imaginary wheel)

[0073] HCL Hammerhead Guide Protrusion Center Axis

[0074] C. The central axis of the BPCL bearing plate (in the area of ​​the friction material coating).

[0075] The center (longitudinal) axis of the SCL and M wire coil springs (as seen in the plan view).

[0076] A1, A2 outrigger axis

[0077] D (axis offset between outrigger axes)

[0078] d. Thickness of the bearing plate

[0079] K1 and K2 support contact points

[0080] B (spring) winding axis

[0081] Δlh decreases the spacing

Claims

1. A friction lining (1) for a motor vehicle disc brake, comprising: a support plate (2) having a friction material coated on at least one upper portion; a wire coil spring (5) mounted in a clamping fit and straddle-mounted manner on a protrusion (4) without friction material, the wire coil spring serving as a friction lining compression spring, and the wire coil spring being symmetrically bent relative to a radial axis R and asymmetrically bent relative to longitudinal axes M, SCL and axial axis Ax; and a spring saddle (6) having a longitudinal axis C, BPC relative to the support plate (2). L is integrated as a chamber (7) in the protrusion (4), the spring saddle has a stepped descending profile and a narrowed retaining edge (8) defining the chamber (7), the retaining edge being elastically engaged in a form-locking expansion engagement between two helical spring winding regions (9, 9') that are diametrically offset from each other and spaced apart, such that the wire helical spring (5) is further configured to be form-locked onto the spring saddle (6) with the winding gradient of the wire helical spring limited to right-hand rotation in the forward direction and mounted on the support plate (2) in a manner that prevents relative rotation, and wherein, The wire coil spring (5) also has two arms (10, 10') oriented in the tangential direction to extend laterally to the side, and the arms are equipped with support portions defined at the ends for abutting against the brake caliper housing (18) as specified. The wire coil spring (5) is characterized in that it is formed of a non-rusting alloy steel wire material or a rust-resistant steel wire material, and the arms (10, 10') engage with the protrusion (4) in a shaped profile such that the support contact points (K1, K2) of the arms (10, 10') are centrally arranged with respect to the longitudinal axis C, BPCL passing through the bearing plate (2) and aligned with the longitudinal axis, and wherein, at the same time, the height level of the support contact points (K1, K2) is reduced by being arranged radially below the height level of the protrusion (4) relative to the radial axis R.

2. The friction lining (1) of a motor vehicle disc brake as described in claim 1, characterized in that, The wire coil spring (5) is bent and wound by cold forming.

3. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The support contact points (K1, K2) of the two support parts are configured to be bent substantially centered relative to each other, flush with the longitudinal axis T and without axial offset D.

4. The friction lining (1) of a motor vehicle disc brake as described in claim 2, characterized in that, The longitudinal axis T passing through the two support contact points (K1, K2) is oriented to be parallel to the central longitudinal axis M, which extends at right angles to the winding axis B of the wire coil spring (5).

5. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, Each support contact point (K1, K2) is defined by a metal ring (12, 12').

6. The friction lining (1) of a motor vehicle disc brake as described in claim 5, characterized in that, The metal ring (12, 12') is substantially closed at the end member side by means of closed arms (13, 13'), in such a way that each associated closed arm (13, 13') is bent at an angle or bent from the metal ring (12, 12') in the direction of the corresponding arm (10, 10') of the wire coil spring (5).

7. The friction lining (1) of a motor vehicle disc brake as described in claim 5, characterized in that, These metal rings (12, 12') are formed asymmetrically and in alternating ways on the respective distributed arms (10, 10').

8. The friction lining (1) of a motor vehicle disc brake as described in claim 5, characterized in that, Set up a half-German metal ring on each side.

9. The friction lining (1) of a motor vehicle disc brake as described in claim 6, characterized in that, The end caps (14, 14') of the closed arms (13, 13') of the metal ring (12, 12') are formed with bevels, rounded corners, or other non-sharp edges to prevent cutting.

10. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The bearing plate (2) is formed as a cold-formed steel sheet back plate.

11. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The support plate (2) has two side protrusions (15, 15') which are bent at an angle along the axial axis Ax in a crank-like manner.

12. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The design thickness d of the support plate (2) is at least approximately equal to or greater than the maximum design width of the wire coil spring (5), such that, as can be seen in the plan view, the wire coil spring (5) does not protrude beyond the thickness of the support plate or only slightly protrudes beyond the thickness of the support plate.

13. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, At least as can be seen in a projection in one spatial direction, the outlines of all longitudinal axes T and M coincide with and are congruent to the obtained center of the bearing plate (2).

14. The friction lining (1) of a motor vehicle disc brake as described in claim 3, characterized in that, The height of the two lowered support contact points (K1, K2) of the two support portions is reduced in a specified area, wherein the specified area is defined radially upward by the upper edge (16) of the protrusion (4) of the bearing plate (2).

15. The friction lining (1) of a motor vehicle disc brake as described in claim 3, characterized in that, The height of the two lowered support contact points (K1, K2) of the two support portions is reduced in a specified area, wherein the specified area is defined radially downward by the friction material (3) of the bearing plate (2).

16. The friction lining (1) of a motor vehicle disc brake as described in claim 3, characterized in that, The height of the two support contact points (K1, K2) of the two support parts is consistent with or approximately the same as the height of the winding axis B of the wire coil spring (5).

17. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The forming profile of each arm (10, 10') is configured as a peripheral portion (11, 11') integrally introduced in the form of strain hardening, i.e. flexural rigidity.

18. The friction lining (1) of a motor vehicle disc brake as described in claim 17, characterized in that, Each peripheral portion (11, 11') is introduced between the winding half and the support portion.

19. The friction lining (1) of a motor vehicle disc brake as described in claim 17, characterized in that, Each peripheral section (11, 11') is defined by two bending axes for the purpose of flexural reinforcement.

20. The friction lining (1) of a motor vehicle disc brake as described in claim 17, characterized in that, Each peripheral portion (11, 11') is angled in a non-linear manner and / or tilted obliquely in a crank-like manner relative to the horizontal direction.

21. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, These support contact points (K1, K2) are offset from each other by a certain distance via lever arms, so that the combined total housing support force F transmitted via the wire helical spring (5) is limited to a maximum of 60 Newtons.

22. The friction lining (1) of a motor vehicle disc brake as described in claim 21, characterized in that, The total shell support force is at least 5 N.

23. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The wire coil spring (5) is detachably fixed to the support plate (2) with an elastic clamping force ranging from 2 Newtons to 20 Newtons.

24. The friction lining (1) of a motor vehicle disc brake as described in claim 23, characterized in that, The average tension used to disassemble the wire coil spring (5) is limited to the range of 2 Newtons to 10 Newtons.

25. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The wire coil spring (5) is formed by bending non-rusting alloy stainless steel or rust-resistant stainless steel.

26. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, Viewed in at least one spatial direction, the wire coil spring (5) is designed with a profile that is bent at an angle.

27. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, Each wire coil spring (5) is fixed only to the disc brake pad (1), which is directly actuated by means of an actuating element. The disc brake pad (1'), which is positioned opposite to the aforementioned disc brake pad, does not have a wire coil spring (5) and is indirectly actuated by reaction force through the brake caliper housing (18).

28. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The wire coil spring (5) provides a space-saving peripheral support configuration for compact hydraulically actuated or electromechanically actuated sliding caliper disc brakes, and is also suitable for and specifically for hydraulic sliding caliper disc brakes that can be actuated in combination and can additionally have electromechanically actuated parking brake devices.

29. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The friction lining (1) of the motor vehicle disc brake is suitable for and specifically used for wheel brakes in or on the axle of a driven passenger vehicle.

30. The friction lining (1) of a motor vehicle disc brake as described in claim 1 or 2, characterized in that, The carrier plate (2) of the friction lining (1) of the motor vehicle disc brake is provided with a contoured configuration of protrusions (15, 15') with hooks, such that the carrier plate (2) is laterally positioned to engage with the brake retainer when braking force is applied, with two hammer-shaped retaining protrusions on the side, which are formed substantially mirror-symmetrically and opposite in diameter to each other, and wherein the two hammer-shaped retaining protrusions are horizontally aligned below the protrusion (4), such that engagement with the brake retainer when braking force is applied is at the same level as the brake piston axis or at a lower level below the brake piston axis, or alternatively substantially coincident with the center of the brake lining, and / or distributed in a mixed manner at one or more of the above positions.

31. A wire coil spring (5) for fixing to a support plate (2) of a friction lining (1) of a motor vehicle disc brake as described in any one of claims 1 to 30, the wire coil spring comprising two arms (10, 10') that are laterally angled and crank-shaped and include a support portion, characterized in that, The wire coil spring (5) is formed of rust-free alloy steel wire or rust-proof steel wire, and the arms (10, 10') are shaped with a curved profile such that the supporting portions of these arms are arranged substantially centrally and flush with the longitudinal axis BPCL passing through the bearing plate (2), and wherein, at the same time, the height level of the supporting portions is reduced by being arranged radially below the height level of the protrusion (4) substantially relative to the radial axis R, with a reduction of Δl. h .

32. A motor vehicle wheel brake (17) comprising a brake caliper housing (18) and a motor vehicle disc brake friction lining (1) as described in any one of claims 1 to 30, the disc brake lining having a wire coil spring (5) in the form of a compression spring.

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