Disc brake

Abstract

The invention relates to a disc brake (1), in particular for use in a utility vehicle, comprising a calliper (3) and a plate (4), wherein the plate (4) is supported on a first edge (43) and / or on a distally opposite second edge (44) against displacement along a retaining axis (H), wherein a central plane is defined which lies between the first edge (43) and the distally opposite second edge (44) of the plate (4) and lies substantially orthogonally with respect to the retaining axis (H), wherein a preloading element (6) is provided which establishes a preloading force between the calliper (3) and the plate (4), wherein the calliper (3) has a support (5) which is arranged and designed for engagement with the preloading element (6), wherein the preloading force acts along a force vector (F) which runs obliquely with respect to the central plane (M).

Description

[0001] disc brake

[0002] The present invention relates to a disc brake, in particular for use in a commercial vehicle, and to the use of a brake pad and a brake disc in a disc brake.

[0003] Disc brakes for use in commercial vehicles are known from the prior art. It has proven effective to design the brake caliper, which guides and applies force to the brake pads, as a floating caliper, which is displaceable relative to the axle-fixed part of the brake system along the axis of rotation of the brake disc. The mounting of the relative movable parts of such a brake caliper, especially a floating caliper, is extremely demanding. Particularly due to the significant heat generated within the brake system and the resulting temperature differences, considerable effort is required to prevent individual parts of the brake system from tilting and to avoid excessive play, which leads to rattling and excessive wear.In this context, it is known from the prior art to use preload elements that preload the brake pad carrier against the brake caliper or the brake carrier. However, these preload elements known from the prior art do not achieve optimal preload of the relative moving components of the brake system in all operating situations, and rattling and significant displacement movements can still occur, particularly during brake application and release.

[0004] The object of the present invention is to provide a disc brake that optimizes the guidance of the brake pads in the caliper and simultaneously simplifies the assembly of the disc brake. This object is achieved with a disc brake according to claim 1, the use of a brake pad and a brake disc according to claims 15 and 17, and a brake pad system according to claim 16.

[0005] According to the invention, a disc brake, particularly for use in a commercial vehicle, is provided, comprising a caliper and a plate, wherein the plate is supported against displacement along a retaining axis at a first edge and / or at a distally opposite second edge, wherein the first edge and the second edge have a substantially flat extent and are parallel to each other, and / or wherein a brake carrier is provided, which has two retaining surfaces which have a substantially flat extent and are parallel to each other, wherein the first edge can come into contact with or bear against the first retaining surface and / or the second edge against the second retaining surface, wherein a median plane is defined between the first edge and the distally opposite second edge of the plate, which is substantially orthogonal to the retaining axis, and wherein a preload element is provided.which establishes a preload force between the caliper and the plate, wherein the caliper has a support which is arranged and designed to engage with the preload element, wherein the preload force acts along a force vector which runs obliquely to the central plane and preferably preloads the plate in the direction of a leading side of the plate. The basic components of a disc brake according to the present invention are a caliper, which is preferably a floating caliper of a disc brake, a plate, which is advantageously a brake pad carrier, and a preload element. The caliper further has a support which extends like a bridge over the gap in the caliper in which the brake pad units and the brake disc are usually arranged. On this support, which can also be referred to as a pad holder,The preload element is supported. The preload element thus engages and / or acts on the saddle and the plate, establishing a preload force between the saddle and the plate, which acts along a force vector. To define geometric features relevant to the present invention, a median plane is defined, wherein the median plane is essentially orthogonal, i.e., with a deviation of a maximum of 5° to 10°, to a support axis. The support axis, in turn, is defined as an axis running between the first and second edges of the plate, along which the plate is preferably supported on a brake carrier of a brake system. Thus, the median plane is oriented perpendicular to this support direction, which runs parallel to the support axis. In other words, the median plane is a vertically oriented plane that intersects the plate and is also parallel to the actuating force transmitted to the plate.which in turn generates a braking force via the brake pads. The normal to the median plane is therefore parallel, or at least substantially parallel, to the support axis. Within the scope of the present invention, the first and second edges of the plate are designed as substantially flat outer surfaces. The parallel alignment of the plate's edges allows for a particularly optimized support of the plate on a brake system carrier with minimal play and the largest possible force transmission area, which significantly reduces the locally occurring stresses when high braking forces are applied. In this context, "substantially flat" particularly encompasses the fact that minor projections and recesses may be provided at the edges, but the average overall extent of each edge runs parallel to the average overall extent of the opposite edge. The two edges are preferably designed as flat surfaces.which are parallel to each other. Alternatively, "flat" can also mean "even". Alternatively or additionally, a brake carrier is provided in this context, which has a first and a second holding surface against which the plate can rest and be supported. In particular, the brake carrier has two holding horns, on each of which one of the holding surfaces is formed. These holding surfaces are designed to be particularly flat and / or even in order to achieve a particularly large area of ​​support for the plate and a reduction of stress peaks. The holding surfaces of the brake carrier are preferably parallel to each other and extend essentially orthogonally to the holding axis. The preload force applied by the preloading element acts in particular with an angular offset to the central plane, i.e., it does not run parallel to the central plane. This results inthat the plate is preferably pressed against the brake carrier by a force component extending along the holding axis, or held in positive engagement with a pressure piece of the disc brake. In particular, the plate is a brake pad carrier, wherein a brake pad, preferably ceramic, NAO, or organic, is integrally formed on the plate or fixed to the plate by means of conventional fastening methods. Advantageously, the force component of the preload force, which acts parallel to the holding axis, runs in the opposite direction to the force that is transmitted from a rotating brake disc to the brake pad and thus to the plate. This results in the definition of the guiding side of the plate, which is arranged with other components either on the side of the first edge or the second edge.Depending on the installation position of the plate in the commercial vehicle, the direction of rotation of the brake disc relative to the plate is defined when the commercial vehicle or vehicle is traveling forward. The leading side of the plate is defined as the side that faces opposite to the direction of rotation of the disc. In other words, the force component of the preload force of the preload element that is tangential to the direction of rotation of the brake disc acts against the direction of rotation of the brake disc. In this way, the plate in the disc brake can preferably be preloaded against the direction of rotation of the brake disc when the brake is released, thus preferably preventing the brake pads from locking or jamming against the brake disc. The plate can therefore be preloaded into a position where the risk of this is low.that the brake pads tilt and jam on the brake disc. With regard to the overall braking system, the force vector preferably does not run in the direction of the brake disc's axis of rotation, but rather obliquely to the corresponding radius of the brake disc. Preferably, the force vector has a directional component that runs tangentially to and opposite to the direction of rotation, or to the circumference of the brake disc.

[0006] In one embodiment, the disc brake is designed as a single-piston disc brake and features a pressure piece designed to transmit a compressive force perpendicular to the holding axis to the plate. The single-piston design of the disc brake offers the particular advantage of a highly weight-optimized design, meaning the disc brake is especially lightweight. Furthermore, the presence of only one centrally located force unit that applies the clamping force to the brake pads reduces the susceptibility to failure of the braking system and the likelihood of misalignment.At the same time, a disc brake designed as a single-piston disc brake requires improved guidance of the plate as well as improved support of the plate against a pressure piece, which is achieved within the scope of the present invention by the substantially flat edges of the plate and preferably also by a preferred engagement geometry between the plate and the pressure piece, which is described below. Within the scope of the present invention, a single-piston disc brake can also be referred to and designed as a single-piston disc brake.

[0007] In one embodiment, a first averaged force transmission surface is defined between the support and the prestressing element, and a second averaged force transmission surface is defined between the prestressing element and the plate. The prestressing force is transmitted via the first and second averaged force transmission surfaces, and the averaged force transmission surfaces are inclined to an orthogonal of the median plane. Within the scope of the present invention, it may be provided that the prestressing force is transmitted from the support to the prestressing element and / or from the prestressing element to the plate via a plurality of contact surfaces. Therefore, in order to determine the force vector for the prestressing force transmitted from the support via the prestressing element to the plate, it is provided to define averaged force transmission surfaces.The averaged force transmission surfaces are each orthogonal to the direction of the resultant force transmitted from one element to the adjacent element. Therefore, since the averaged force transmission surfaces are each oblique to an orthogonal aspect of the median plane, a resultant force is also transmitted along a vector oblique to the median plane. In one embodiment, at least one of the averaged force transmission surfaces is equidistant from the first edge of the plate as it is from the second edge of the plate and is thus intersected substantially at its midpoint by the median plane. In this case, the central force transmission surface is not perpendicular to the median plane, but forms an angle of less than 90° with it.In an alternative embodiment, at least one of the averaged force transmission surfaces is located at a different distance from the first edge than from the second edge, such that this averaged force transmission surface is thus eccentrically, or off-center, with respect to the lateral extent of the plate. All embodiments have in common that the resulting force transmitted from the support to the plate runs along the force vector, which is oblique to the central plane.

[0008] In one embodiment, at least one of the averaged force transmission surfaces forms an angle with a line orthogonal to the central plane, wherein the angle is 1° to 35°, preferably 1° to 20°, and particularly preferably 5° to 15°. The larger the angle that the respective averaged force transmission surface forms with the line orthogonal to the central plane, the more strongly the preload element presses the plate against one of its edges, either the first or the second. Simultaneously, the radial component of the preload force, i.e., in the direction of the axis of rotation of a brake disc, is reduced with increasing angle. In this context, maintaining the angle in the range of 1° to 20° has proven to be the most favorable compromise for a sufficient preload force acting radially and simultaneously a sufficient preload against one of the edges, and thus in the circumferential direction of the brake disc's rotation.The particularly preferred range of 10° to 20° allows the advantages of the present invention to be achieved with only minor modifications to existing saddles or brake calipers, in particular to reduce rattling.

[0009] In one embodiment, the median plane is equidistant from the first and second edges. In this embodiment, the median plane thus intersects the plate centrally. Furthermore, or alternatively, preferably, the contact surface of the plate formed at the first edge is parallel to the contact surface formed at the second edge, each with the brake carrier. In this embodiment, or more generally, the median plane is advantageously parallel to the first and second edges. Furthermore, the retaining axis preferably runs orthogonally to the first edge, the second edge, and the median plane. In one embodiment, the prestressing element has a first support section for bearing against the support and a first clamping section for bearing against the plate, wherein the prestressing element is elastically prestressed in the area between the first support section and the first clamping section.In a first embodiment, the prestressing element can be provided with only one support section on the column and only one clamping section on the plate. In this embodiment, a lateral support against slippage of the prestressing element is preferably also provided, i.e., the prestressing element preferably engages the column and the plate in a form-fitting manner.

[0010] Preferably, the plate has a first positioning section which engages positively with the preloading element in the area of ​​the first clamping section. For the positive-locking arrangement of the preloading element on the plate, at least one first positioning section is provided, which is advantageously formed integrally with the plate and can be brought into engagement with the preloading element via a corresponding contact geometry. In other words, the first positioning section is formed as a retaining lug on the upper surface of the plate, whereby the preloading element can be placed onto this positioning section via a corresponding recess or recess and brought into engagement there.

[0011] Furthermore, the prestressing element preferably has a second clamping section at its end distal to the first clamping section. The first clamping section rests on the plate in a first sub-area of ​​the second averaged force transmission surface, and the second clamping section rests on a second sub-area of ​​the second averaged force transmission surface. The orientation of the second averaged force transmission surface is the mean of the orientations of the first and second sub-areas. The resultant force transmitted in the first and second clamping sections acts along the force vector. Advantageously, the prestressing force is thus transmitted from the prestressing element to the plate in two sub-areas that are spaced apart from each other.As a mathematical aid, the averaged second force transmission area is determined from these two sub-areas, whereby the direction of the transmitted prestressing force and the corresponding averaged point of application result from this averaged second force transmission area. It is possible that the second averaged force transmission area is intersected centrally by the median plane, but due to its inclination relative to the median plane's perpendicular surfaces, a force oblique to the median plane is nevertheless transmitted from the prestressing element to the plate.

[0012] In one embodiment, the prestressing element has a second support section, which is spaced apart from the first support section and is designed to bear against the column. Additionally or alternatively, the prestressing element can have a first and a second support section, i.e., bearing against the column in two contact areas to transfer the corresponding counterforce to the prestressing force applied to the slab. Advantageously, the first and second support sections are spaced apart from each other in such a way as to ensure secure guidance and support of the prestressing element on the column.

[0013] In one embodiment, the plate has a second positioning section spaced apart from the first positioning section, with the preloading element engaging positively with the second positioning section in the area of ​​the second clamping section. Additionally or alternatively, the support element engages positively with a first and a second positioning section on the plate and is secured there against displacement at least transversely to the direction of the transmitted preload force.

[0014] In one embodiment, the distance of the first positioning section from the first side edge differs from the distance of the second positioning section from the second side edge. The first and second positioning sections are therefore not arranged symmetrically on the plate, but rather each is positioned closer to a first or second edge, respectively. The first and second edges are, in each case, the side edges of the plate closest to the respective positioning section. In other words, the first side edge is the edge of the plate that is closer to the first positioning section than the second positioning section. The arrangement of the positioning sections on the plate also determines the engagement position of the prestressing element on the plate and thus the point of application of the mean prestressing force transmitted from the prestressing element to the plate.

[0015] Preferably, the distance of the first positioning section from the first lateral edge to the distance of the second positioning section from the second lateral edge is in a ratio of 0.2 to 0.9, preferably 0.3 to 0.7, and particularly 0.3 to 0.5. The smaller the ratio of the distance of the first positioning section from the first edge to the distance of the second positioning section from the second edge, the greater the eccentricity of the arrangement of the positioning sections. Within the scope of the present invention, it has proven advantageous to select a range of approximately 0.3 to 0.7, particularly in order to achieve a preload force inclined to the central plane with relatively minor structural modifications to the brake caliper.

[0016] In one embodiment, the disc brake has a pressure piece designed to transmit a pressure force along a force axis to the plate, wherein the pressure piece has at least a first locking section which is designed and provided for support on a first engagement section formed on the plate, wherein the pressure piece has at least a second locking section spaced apart from the first locking section, which is designed and provided for support on a second engagement section provided on the plate spaced apart from the first engagement section, wherein the preload force applied by the preload element preloads the first locking section against the first engagement section and simultaneously preloads the second locking section against the second engagement section.Each of the locking sections, which can also be considered contact surfaces or support surfaces between the pressure piece and the plate, supports a specific engagement section of the plate against the pressure piece in a first or a second locking direction. Preferably, the force vector has a component parallel to the first locking direction and a component parallel to the second locking direction, such that the preload force applied by the preloading element preloads the first locking section against the first engagement section and simultaneously preloads the second locking section against the second engagement section.The preload force of the preload element is preferably oriented such that not only one of the locking sections is supported at the corresponding engagement section, but at least two locking sections are each supported at a corresponding engagement section. The clamping element thus supports the large-area support between the pressure piece and the plate in order to reduce stress peaks and wear between the contact surfaces of the pressure piece and the plate. At the same time, the clamping element reduces rattling and impacts, or vibrations of the plate relative to the pressure piece.

[0017] In one embodiment, the pressure piece has at least one contact surface against which the plate comes into contact to transmit the pressure force, wherein the first locking section and / or the second locking section is formed on a projection extending from the contact surface, and the corresponding first engagement section and / or the second engagement section is formed as a recess on the plate. Alternatively, however, the first locking section and / or the second locking section can also be formed by a recess, with the corresponding first engagement section and / or the second engagement section being formed as a projection on the plate. The contact surface can be formed by several surfaces, with the corresponding projection being arranged in each of these surfaces. In particular, the engagement sections and the locking sections are each integrally formed on the plate or...The pressure piece is designed as a pressure piece. Alternatively, individual locking sections or engagement sections could also be cast onto the plate or pressure piece or bonded there by a material connection. Eliminating intermediate elements reduces the system's susceptibility to failure and, in particular, prevents further wear between the individual components. In one embodiment, the first locking section and the second locking section are formed on a common projection or recess, with the first engagement section and the second engagement section correspondingly forming on a common recess or projection. In this embodiment, each projection thus has two obliquely or perpendicularly positioned contact surfaces, which form either the two locking sections or the two engagement sections.Similarly, each recess has corresponding engagement or securing sections. In this way, the mounting of the pressure piece on the plate can be achieved with a single projection engaging in a corresponding recess, securing the plate against both lateral displacement perpendicular to the force axis and rotation relative to the pressure piece.

[0018] In one embodiment, the disc brake comprises a brake carrier, wherein the plate has a first edge and a second edge distal to the first edge, the plate being guided against the brake carrier at the first and / or second edge and secured against displacement transverse to the median plane, preferably orthogonal to the median plane, relative to the brake carrier. The brake carrier is preferably the brake carrier of the disc brake and is, in particular, directly or indirectly fixed or connected to the axle, preferably the axle stub, of a vehicle's wheel suspension. The caliper can also be referred to as a brake caliper and is, in particular, designed as a floating caliper. In addition to being supported on the plate, the pressure piece can also be guided within the caliper. In other words, the pressure piece can be supported on both the caliper and the plate to absorb a tilting moment.In particular, the pressure piece is secured against rotation about the force axis by a support on the plate, especially by a positive locking mechanism. The caliper is arranged to be displaceable relative to the brake carrier. The pressure piece is positioned relative to the brake carrier, in particular by the guided engagement with the plate and the engagement of the plate with the brake carrier. In contrast to other disc brakes known from the prior art, in which the force transmission means acting on the brake pad, in particular spindles, are held and guided directly on the caliper, the present design allows for more cost-effective manufacturing of the caliper. Nevertheless, this ensures that the caliper, together with the pressure piece and the plate, is always held in the correct position and orientation relative to the brake disc, without the risk of tilting in the guide geometry of a brake carrier.

[0019] According to the invention, a brake pad and / or a plate are further used in a disc brake with the features described above, wherein the brake pad is, in particular, fixed to the plate. Alternatively, the use of a brake pad unit in a disc brake with the features described above is provided, wherein the brake pad unit comprises the plate and a brake pad fixed to the plate. A brake pad used in a disc brake with the features described above is, in particular, always optimally aligned relative to the brake disc, since it is already pre-tensioned against the brake carrier with a force component of the preload force in or against the direction of rotation of the brake disc relative to the caliper. This also minimizes the risk of the brake pad tilting or becoming misaligned due to the special guidance of the pressure piece.The plate or brake pad may have the features described above or below in relation to the plate and / or brake pad. Furthermore, the invention may also relate to a brake pad system for a disc brake as described above or below.This brake pad system comprises a plate or a brake pad assembly with a plate and, furthermore, a preloading element, wherein the plate has a first edge and / or a distally opposite second edge, wherein the first edge and the second edge have a substantially flat extent and are parallel to each other, wherein a median plane is defined between the first edge and the distally opposite second edge of the plate, which is substantially orthogonal to the retaining axis, wherein the preloading element is provided to establish a preload force between a caliper and the plate, wherein the preload force acts along a force vector which is oblique to the median plane and preferably preloads the plate in the direction of a leading side of the plate. The brake pad system therefore comprises a preloading element and a plate or a brake pad assembly which in turn has a plate.The features, embodiments and configurations shown within the scope of the invention with regard to the disc brake can also be implemented in the same way in the brake pad system, in particular in the preload element, the plate or the brake pad unit.

[0020] According to the invention, a brake disc is further used in a disc brake with the features described above, wherein the brake disc is arranged, in particular, between two brake pads or between two brake pad units, and wherein, in particular, one of the brake pads is formed on or fixed to the disc. When using a brake disc in a disc brake with the features described above, optimal positioning of the brake pads relative to the braking surface of the brake disc is always ensured, since, thanks to the optimized engagement and the guidance and positioning of the disc relative to the pressure piece, the brake pads fixed to the disc are always optimally arranged and can be brought into contact with the brake disc with a short actuation distance.

[0021] Advantageously, the disc brake is a commercial vehicle disc brake. A commercial vehicle within the meaning of the invention is a roadworthy vehicle with a permissible gross vehicle weight of more than 3.5 metric tons, preferably more than 7.5 metric tons, and particularly preferably more than 15 metric tons. The commercial vehicle can, in particular, be a trailer, especially a commercial vehicle trailer. The trailer can be configured as a semi-trailer. Furthermore, the disc brake is designed as a single-piston disc brake, which means that only one centrally located pressure piece is provided, which applies the clamping force acting on the plate and thus on the brake pad.

[0022] Another aspect of the invention may relate to a commercial vehicle with a disc brake as described above or below. Further advantages and features of the present invention will become apparent from the following description with reference to the accompanying figures. It is understood that features that are directly illustrated in only one of the figures may or should also be used in embodiments of other figures, unless this is prohibited by technical constraints or by explicit exclusion.

[0023] They show:

[0024] Fig. 1 shows a view of an embodiment of a disc brake;

[0025] Fig. 2 shows a perspective view of a disc brake;

[0026] Figs. 3 and 4 show two schematic views of two embodiments of selected components of a disc brake; and

[0027] Fig. 5 shows a schematic exploded view of the power transmission area of ​​a disc brake.

[0028] The embodiment of a disc brake 1 shown in Figure 1 comprises a brake carrier 9, a brake caliper 3, a plate 4, and a pressure piece 2, which is concealed in this view. The plate 4 is supported on the brake carrier 9 at its first edge 43 (shown on the left in the figure) and at its second edge 44 (shown on the right in the figure) by counter-displacements parallel to a holding axis H. The plate 4 is advantageously part of a brake pad assembly 48, which, in addition to the plate 4, includes a brake pad 46 (see Figure 2). Furthermore, the plate 4 is supported on its underside on the brake carrier 9 and is pre-tensioned against the brake carrier 9 by a clamping element 6 with a pre-tensioning force that extends along a mean force vector F. The clamping element 6, in turn, is supported by a support 5, which is fixed to or formed on the brake caliper 3.In this embodiment, the force vector F preferably runs obliquely to a median plane M which, in this embodiment, intersects the plate 4 centrally, such that the median plane M has the same distance S from the first edge 43 and from the second edge 44. Due to the oblique orientation of the force vector F, the plate 4 with its two engagement units 40 is pre-tensioned or held against the locking sections 22A, 22B (see Figs. 2 and 3) formed on two locking units 20 of the pressure piece 2, essentially across its entire surface. The locking units 20 are advantageously arranged on projections V on the pressure piece 2, the projections V being essentially cross-shaped or plus sign-shaped. In this configuration, the locking units 20 thus have straight or curved edges in both the vertical and horizontal directions.The plate 4 features parallel, extending locking sections 22A, 22B, against which the corresponding engagement sections 42A, 42B can engage. The corresponding engagement units 40 are advantageously arranged on recesses R formed in the plate 4. The recesses R have a slightly larger surface area in the plane of view of Fig. 1 than the projections V, in order to allow for a correspondingly tight fit.

[0029] Figure 2 shows a perspective view of a disc brake 1 with a caliper 3, a brake carrier 9, and a plate 4 mounted on the brake carrier 9. On the side facing the brake disc 8, a brake pad 46 is fixed to the plate 4. Furthermore, a support 5 is fixed to the caliper 3, which bridges the gap in the caliper 3 formed by the brake disc 8 and the brake pads 46. A preload element 6 is supported on each of the two brake pad carriers, which transmits a preload force to the plate 4. Advantageously, a clamping element 6 is provided on each of the two brake pad carriers, each of which is supported on the support 5. The arrow shown on the support 5 indicates the direction of rotation D of the brake disc 8, with the preload element 6 preloading the respective plate 4 against the direction of rotation D. This prevents the brake pads 46 from coming loose and the brake disc 8 from jamming with the brake pads 46.

[0030] The schematic view in Figure 3 shows an embodiment of a plate 4 which is secured between two corresponding retaining horns of a brake carrier 9 in the transverse direction, i.e., parallel to a retaining axis. A preloading element 6 applies a preload force to the upper surface of the plate 4, the resulting preload force acting along a force vector F. The force vector F is inclined to a median plane M. Furthermore, a first and a second positioning section 45A, 45B are formed on the plate 4, each extending through recesses provided in the preloading element 6 in the area of ​​the clamping sections 62A, 64B. The preloading element 6 is also supported by a first support section 64A on the support 5. The first positioning section 45A is located at a significantly greater distance from the first edge 43 than the second positioning section 45B is from the second edge 44.In this embodiment, the ratio of the smaller distance of one of the positioning sections 45A, 45B from the nearest edge 43, 44 to the respective larger distance is 0.3 to 0.6 times. In this preferred embodiment, the arrangement of the preload element 6, the support 5, and the corresponding positioning sections 45A, 45B is thus asymmetrical with respect to the central plane M. The preload element 6 is supported by a support 5 of the brake caliper (not shown). By applying a preload force obliquely to the plate 4, the first and second locking sections 22A, 22B are each pressed against the corresponding engagement sections 42A, 42B, such that a multitude of contact surfaces, and thus force transmission surfaces, are present on which the plate 4 rests against the pressure piece 2.The cross-sectional geometry of the locking units 20 and corresponding engagement units 40 is designed to provide as many contact lines or contact surfaces as possible on each of the projections V. In particular, the cylindrical geometry of the projection V shown on the right side of Figure 3, in combination with the diamond- or cuboid-shaped geometry of the recess R, ensures that the projection V rests against the recess R on at least two force transmission surfaces. Furthermore, in the embodiment shown on the left side of the plate 4, the first locking direction A and the second locking direction B run essentially vertically and horizontally, respectively, while in the embodiment shown on the right side, the locking directions A and B each form an angle of approximately 45° with the horizontal or with the holding axis A.Accordingly, the securing directions A, B on the left side of the plate 4 differ from the securing directions A and B on the right side of the embodiment of the plate 4 shown in Figure 3. Thus, preferably, not only is support ensured along a first securing direction A and a second securing direction B perpendicular to it, but the various engagement areas between the plate 4 and the pressure piece 2 reach further securing directions A, B along which forces can be transmitted between the pressure piece 2 and the plate 4 in a particularly optimized manner.

[0031] Figure 4 shows a schematic view of an embodiment of a plate 4, which is fundamentally similar to the embodiment shown in Figure 3. In contrast to the embodiment described above, the preloading element 6 has only one clamping section 62A for support on the plate 4 and two support sections 64A, 64B for support on the support 5. As in the embodiment described above, the plate 4 is supported on the brake carrier 9 against displacement along a holding axis H, with the force vector F running transversely and not perpendicularly to the holding axis H.

[0032] The schematic exploded view of the force transmission area of ​​a disc brake 1 shown in Figure 5 illustrates the definition of the first averaged force transmission area 36 and the second averaged force transmission area 66. The first averaged force transmission area 36 is defined as the force transmission area resulting from all contact surfaces involved in the force transmission between the support 5 and the preload element 6. In the present example, only one contact surface is provided between the support 5 and the preload element 6, so the first averaged force transmission area 36 corresponds to this contact surface. In contrast, two partial surfaces 65A, 65B are provided between the preload element 6 and the plate 4 for force transmission, and the second averaged force transmission area 66 is therefore defined as the sum of these and the imaginary mean force transmission area arranged centrally between the partial surfaces 65A, 65B.Both the size, i.e., the area, and the orientation of the averaged second force transmission surface 66 result from the size and orientation of the sub-surfaces 65A, 65B. Preferably, the force vector F is located centrally and orthogonally to the first averaged force transmission surface 36. Furthermore, preferably, the force vector F is also orthogonal to the second averaged force transmission surface 66. It is understood that the first sub-surface 65A is arranged directly on the underside of the first clamping section 62A, and the second sub-surface 65B is arranged directly on the underside of the second clamping section 62B. Adjacent to these sub-surfaces 65A, 65B, there is a recess through which the respective positioning section 45A, 45B extends. In the embodiment shown in Figure 5, the respective engagement geometry is advantageously defined with respect to a line M' parallel to the median plane M.Preferably, the median plane M lies midway between the first and second edges 43, 44, thus having the same distance to both edges 43, 44. In contrast, the line parallel to the median plane M' can lie off-center between the edges 43, 44 and be aligned parallel to the median plane M.

[0033] Reference symbol list:

[0034] 1 - Disc brake

[0035] 2 - Pressure piece

[0036] 3 - Saddle

[0037] 4 - Plate

[0038] 5 - Support

[0039] 6 - Preload element

[0040] 8 - Brake disc

[0041] 9 - Holder

[0042] 20 - Fuse unit

[0043] 22A - first fuse section

[0044] 22B - second fuse section

[0045] 24 - Plant area

[0046] 36 - first averaged force transmission area

[0047] 40 - Intervention unit

[0048] 42A - first intervention section

[0049] 42B - second intervention section

[0050] 43 - first edge

[0051] 44 - second margin

[0052] 45A - first positioning section

[0053] 45B - second positioning section

[0054] 46 - Brake pad

[0055] 48 - Brake pad unit 62A - first clamping section

[0056] 62B - second clamping section

[0057] 64A - first support section

[0058] 64B - second support section

[0059] 65A - first sub-area

[0060] 65B - second sub-area

[0061] 66 - second averaged power transmission area

[0062] 93 - first holding surface

[0063] 94 - second holding surface

[0064] A - first securing direction

[0065] B - second safety direction

[0066] D - Direction of rotation

[0067] F - mean force vector

[0068] H - Holding axis

[0069] K - Direction of force

[0070] M - Middle level

[0071] M' - Parallel to the middle plane

[0072] R - Return

[0073] S-distance

[0074] V-lead

Claims

Claims 1. Disc brake (1), in particular for use in a commercial vehicle, comprising a caliper (3) and a plate (4), wherein the plate (4) is supported against displacement along a retaining axis (H) at a first edge (43) and / or at a distally opposite second edge (44), wherein the first edge (43) and the second edge (44) preferably have a substantially flat extent and are preferably parallel to each other, and / or, wherein a brake carrier (9) is provided which has two retaining surfaces (93, 94) which have a substantially flat extent and are parallel to each other, wherein the first edge (43) can come into contact with or bear against the first retaining surface (93) and / or the second edge (44) against the second retaining surface (94), wherein a median plane (M) is defined between the first edge (43) and the distally opposite second edge (44) of the plate (4), which is substantially orthogonal to the retaining axis (H),wherein a prestressing element (6) is provided which establishes a prestressing force between the saddle (3) and the plate (4), wherein the saddle (3) has a support (5) which is arranged and designed to engage with the prestressing element (6), wherein the prestressing force acts along a force vector (F) which runs obliquely to the median plane (M) and preferably prestresses the plate (4) in the direction of a leading side of the plate (4).

2. Disc brake (1 ) according to claim 1, wherein the disc brake (1 ) is designed as a single-piston disc brake and has a pressure piece (2) which is designed to transmit a pressure force perpendicular to the holding axis (H) to the plate (4).

3. Disc brake (1) according to one of the preceding claims, wherein a first averaged force transmission surface (36) is defined between the support (52) and the preload element (6), and a second averaged force transmission surface (66) is defined between the preload element (6) and the plate (4), wherein the preload force is transmitted via the first and the second averaged force transmission surfaces (36, 66), and wherein the averaged force transmission surfaces (36, 66) are inclined to an orthogonal of the median plane (M).

4. Disc brake (1 ) according to claim 3, wherein at least one of the averaged force transmission surfaces (36, 66) encloses an angle (a) with an orthogonal of the median plane (M), wherein the angle (a) is 1° to 35°, preferably 1° to 20° and particularly preferably 10° to 20°.

5. Disc brake (1) according to one of the preceding claims, wherein the median plane (M) has the same distance (S) from the first edge (43) and from the second edge (44).

6. Disc brake (1) according to one of the preceding claims, wherein the preloading element (6) has a first support section (64A) for contact with the support (5) and a first clamping section (62A) for contact with the plate (4), wherein the preloading element (6) is elastically preloaded in the area between the first support section (64A) and the first clamping section (62A).

7. Disc brake (1) according to claim 6, wherein the plate (4) has a first positioning section (45A) which extends through the preloading element (6) in the area of ​​the first clamping section (62A), wherein the plate (4) has a second positioning section (45B) spaced away from the first positioning section (45A), which extends through the pretensioning element (6) in the area of ​​the second clamping section (62B).

8. Disc brake (1) according to claim 7, wherein the distance of the first positioning section (45A) from the first side edge (43) differs from the distance of the second positioning section (45B) from the second side edge (44), wherein preferably the distance of the first positioning section (45A) from the first side edge (43) to the distance of the second positioning section (45B) from the second side edge (44) is in a ratio of 0.2 to 0.9, preferably 0.3 to 0.7 and in particular 0.3 to 0.

5.

9. Disc brake (1) according to one of claims 7 or 8, wherein the preload element (6) has a second clamping section (62B) at its end distal to the first clamping section (62A), wherein the first clamping section (62A) bears against the plate (4) in a first partial surface (65A) of the second averaged force transmission surface (66) and the second clamping section (62B) bears against the plate (4) in a second partial surface (65B) of the second averaged force transmission surface (66), wherein the orientation of the second averaged force transmission surface (66) is the mean of the orientations of the first and second partial surfaces (65A, 65B), wherein the resultant force transmitted in the first clamping section (62A) and in the second clamping section (62B) acts along the force vector (F).

10. Disc brake (1) according to one of claims 7 or 8, wherein the preload element (6) has a second support section (64B) which is spaced apart from the first support section (64A) and is provided for contact with the support (5).

11. Disc brake (1) according to claim 2, wherein the pressure piece (2) has at least one first locking section (22A) having a first engagement section (42A) formed on the plate (4), wherein the pressure piece (2) has at least a second locking section (22B) spaced apart from the first locking section (22A), which is formed and provided for support on a second engagement section (42B) provided on the plate (4) spaced apart from the first engagement section (42A), wherein the preload force applied by the preloading element (6) preloads the first locking section (22A) against the first engagement section (42A) and simultaneously preloads the second locking section (22B) against the second engagement section (42B).

12. Disc brake (1) according to claim 11, wherein the pressure piece (2) has at least one contact surface (24) against which the plate (4) comes to rest in order to transmit the pressure force, wherein the first locking section (22A) and / or the second locking section (22B) is formed on a projection (V) extending from the contact surface (24), wherein the respective corresponding first engagement section (42A) and / or the second engagement section (42B) is formed as a recess (R) on the plate (4).

13. Disc brake (1 ) according to claim 12, wherein the first locking section (22A) and the second locking section (22B) are formed on a common projection (V) or on a common rebate (R), wherein the first engagement section (42A) and the second engagement section (42B) are correspondingly formed on a common rebate (R) or on a common projection (V).

14. Disc brake (1) according to one of the preceding claims, wherein the plate (4) is attached to the brake carrier at the first and / or second edge (43, 44). (9) is guided in a situ and secured against displacements transverse to the median plane (M), preferably orthogonal to the median plane (M), relative to the brake carrier (9).

15. Use of a brake pad (46) in a disc brake (1) according to any one of claims 1-14, wherein the brake pad (46) is fixed to the plate (4), or Use of a brake pad unit (48) in a disc brake (1 ) according to one of claims 1 - 14, wherein the brake pad unit (48) comprises the plate (4) and a brake pad (46) fixed to the plate (4).

16. Brake pad system for a disc brake (1 ) according to one of claims 1 - 14 comprising a plate (4) or a brake pad unit (48) with a plate (4) and a preloading element (6), wherein the plate (4) has a first edge (43) and / or a distally opposite second edge (44), wherein the first edge (43) and the second edge (44) have a substantially flat extent and are preferably parallel to each other, wherein a median plane (M) is defined between the first edge (43) and the distally opposite second edge (44) of the plate (4), which is substantially orthogonal to the holding axis (H), wherein the preloading element (6) is provided to establish a preload force between a saddle (3) and the plate (4), wherein the preload force acts along a force vector (F) which is oblique to the median plane (M) and preferably preloads the plate (4) in the direction of a leading side of the plate (4).

17. Use of a brake disc (8) in a disc brake (1) according to one of claims 1-14, wherein the brake disc (8) is arranged in particular between two brake pads (46) or between two brake pad units (48), and wherein the brake pads (46) are formed or fixed to the plate (4).

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