Disk brake

Abstract

A disk brake (1), in particular for use in a utility vehicle, having a pressure piece (2) and a plate (4); wherein the pressure piece has at least one bearing surface (24) against which the plate abuts in order to transmit a compressive force along a force axis (K) from the pressure piece to the plate; wherein the pressure piece has at least one first securing section (22A) which is designed and provided to be supported on a first engagement section (42A) formed on the plate; wherein the fact that the first securing section is supported on the first engagement section prevents displacement of the pressure piece relative to the plate along or parallel to a first securing direction, in particular via positive locking; wherein the first securing section has a contact surface which is formed and can be positioned to complement a contact surface of the first engagement section such that when the first securing section is supported on the first engagement section, the two contact surfaces come into contact with one another.

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 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.Particularly in the area of ​​fixing, guiding and transmitting force from the brake caliper to the brake pads, high forces are at work, which cause locally high material stresses in brake systems known from the prior art.

[0004] The object of the present invention is to provide a disc brake in which, particularly in the bearing and force transmission area between the brake caliper and the brake pads, material stresses are reduced, the guidance of the brake pads in the caliper is optimized, and at the same time the assembly of the disc brake is simplified. This object is achieved with a disc brake according to claim 1 and the use of a brake pad, a brake pad assembly, and a brake disc according to claims 18 and 19, as well as a plate according to claim 20.

[0005] According to the invention, a disc brake, particularly for use in a commercial vehicle, comprises a pressure piece and a plate, wherein the pressure piece has at least one contact surface against which the plate comes to rest in order to transmit a pressure force along a force axis from the pressure piece to the plate, wherein the pressure piece has at least one first locking section which is designed and provided for support on a first engagement section formed on the plate, wherein the support of the first locking section on the first engagement section prevents displacement of the pressure piece relative to the plate along or parallel to a first locking direction, in particular by positive locking, wherein the first locking section has a contact surface which is shaped and arranged complementarily to a contact surface of the first engagement section, such thatthat surface contact is present when supporting the first securing section at the first engagement section.

[0006] The essential basic components of the present disc brake are the pressure piece and a plate. The pressure piece is the component of the brake system that is longitudinally displaceable within a brake caliper (which can also be referred to simply as a caliper) and transmits a pressure force along a force direction to the plate. The brake pad is attached to the plate or formed integrally with it, and ultimately comes into contact with the brake disc. The pressure piece has a contact surface for force transmission to the plate. Advantageously, the plate is held and guided on the brake carrier in both the radial and tangential directions with respect to the axis of rotation of the brake disc. In one embodiment, the brake carrier, in turn, holds and guides the caliper.In operation, the plate, together with the brake pad attached to it, is secured against displacement in the tangential direction relative to the axis of rotation of a brake disc of the braking system, particularly to a brake carrier. Along the radial direction relative to the axis of rotation of the brake disc, the plate is advantageously secured both by the brake carrier and by a preload against the brake caliper of the braking system. The contact surface can be formed by several surfaces. To prevent displacement of the plate relative to the pressure piece parallel to the contact surface, a first securing section is formed on the pressure piece, which is designed for surface support against an engagement section provided on the plate.This achieves the largest possible support and force transmission, in particular by providing the locking section with a contact surface that is complementary to a corresponding contact surface of the engagement section and is aligned when the surfaces are in contact. The complementary contact surfaces on the locking section and engagement section advantageously lie in full contact with each other, thus preventing point-source force transmission. A key feature of the present invention is that, during brake operation, especially when a braking force is generated or a service brake is terminated, the plate, guided with tight clearance on the brake carrier, guides the pressure piece through the engagement of the locking sections with the engagement sections, and in particular secures it against displacements transverse to the force axis and rotation about the force axis.This means that the pressure piece is primarily guided by the plate during operation and has little or no contact with the caliper. This is particularly advantageous in the case of a single-piston disc brake caliper, as the plate and the pressure piece engaging with it are essentially held and guided by the brake carrier, allowing the pressure piece to be positioned with some play within the caliper. This design allows the plate and pressure piece to be positioned precisely and with minimal play relative to the brake disc via the brake carrier. A single-piston disc brake, where the brake pads are ultimately pressed against the brake disc by only a centrally located section of the pressure piece, can be designed to be particularly reliable thanks to this precise guidance of the pressure piece by the plate and brake carrier.In this way, the lightweight and low-maintenance design of the single-piston disc brake can be combined with a stable arrangement of the components. This avoids the need to create a precisely machined seat for the pressure piece in the caliper and thus reduces manufacturing costs for the disc brake. In one embodiment, the first locking direction is orthogonal to the contact surfaces between the first locking section and the first engagement section. This orientation ensures optimal and evenly distributed force transmission across the contact surfaces and avoids local stress peaks.In the preferred case of a rounded geometry of the first and second locking and engagement sections, the corresponding locking direction is assumed to be an averaged extension direction of the locking and engagement sections, to which the respective locking direction is defined orthogonally. In the preferred case of, for example, a concavely curved contact surface, the locking direction runs parallel and preferably collinearly to the radius of curvature of the contact surface.

[0007] In one embodiment, the pressure piece has a second locking section which is designed and provided for support on a second engagement section provided on the plate, wherein the support of the second locking section on the second engagement section prevents displacement of the pressure piece relative to the plate along or parallel to a second locking direction, in particular by positive locking.

[0008] In one embodiment, the pressure piece has a second locking section, which is designed and provided for support against a second engagement section provided on the plate. The support of the second locking section against the second engagement section prevents displacement of the pressure piece relative to the plate along or parallel to a second locking direction, in particular by means of a positive locking mechanism. Advantageously, the second locking section, analogous to the first locking section, has a contact surface which is shaped and arranged complementarily to a contact surface of the second engagement section, such that surface contact is present when the second locking section is supported against the second engagement section. The second locking direction is preferably orthogonal to the contact surface between the second locking section and the second engagement section.In this way, the first and second safety sections can advantageously reach the corresponding intervention sections for installation and support over their entire area.

[0009] Advantageously, at least one contact surface of the respective engagement section with the corresponding locking section has an area in the range of 5 mm. 2 up to 200 mm 2 , preferably 30 mm 2 up to 100 mm 2 , on. Tests have shown that a contact area larger than 5 mm 2 and preferably larger than 30 mm 2 This has a positive effect on the service life of the interface between the plate and the pressure piece, as stress peaks and associated wear can be reduced.

[0010] In preferred embodiments of the invention, the contact surfaces between the locking and engagement sections extend perpendicular to the force axis by approximately 5 mm to 30 mm and / or by 0.2 to 0.95 times the total extent of the respective locking or engagement section. Advantageously, the contact surfaces have a depth of extension measured parallel to the force axis, which is approximately in the range of 4 to 20 mm, wherein this depth of extension is advantageously 0.6 to 0.8 times the thickness of the plate.

[0011] Within the scope of the invention, it is preferably provided that the contact surfaces provided on the respective projections for bearing against the corresponding recesses are arranged only in the lateral region of the projection and the corresponding recess. In other words, the end face of a projection, which extends substantially parallel to the plane orthogonal to the force axis, is not in contact with the opposite base surface of a recess. The securing and engagement sections thus have a predominant extension parallel to the force axis and parallel to the holding axis. Put simply, the outer surface of a projection thus serves as a contact surface that bears against the corresponding inner outer surface of a recess.In one embodiment, the plate has a first edge and a second edge distal to the first edge, wherein the plate can be secured at the first and / or second edge against displacement perpendicular to the direction of force and along a holding axis, wherein the first securing direction and the second securing direction are inclined at a first angle or a second angle to the holding axis, each greater than 1°. The inclined orientation of the securing sections and engagement sections at a first angle or a second angle with respect to the holding axis preferably ensures that, when a securing section engages the opposite engagement section, support with force components collinear and perpendicular to the holding axis takes place. This particularly enables a large contact and force transmission area to reduce Hertzian surface pressure.In this way, the occurrence of local stress peaks can be reduced, since the forces occurring between the plate and the pressure piece can be transmitted via several and particularly large contact surfaces, also referred to in this context as force transmission surfaces.

[0012] In one embodiment, the first locking direction includes the first angle with the holding axis, which is preferably greater than 5°, and the second locking direction also includes a first angle, or a second angle different from the first, with the holding axis. An inclination of the locking and engagement sections relative to the holding axis ensures a large contact area of ​​the engagement sections with the locking sections, given a predetermined orientation of the support surfaces at an angle to the horizontal or to the holding axis. An angle greater than 5° results in a significant increase in the force components acting both parallel and perpendicular to the holding axis.Additionally, the second angle, which differs from the first, ensures that the assembly of plate and pressure piece is optimally adapted to a specific direction of rotation of the brake disc, as this achieves the largest possible force transmission of the holding forces acting between the pressure piece and the plate during braking. In one embodiment, the first engagement section and / or the second engagement section is designed as a recess on the plate. The engagement section(s) designed as a recess serve to receive at least one projection each. In another embodiment, the first locking section and / or the second locking section is formed on a projection extending from the contact surface.Alternatively, 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. In this context, it is preferred that both locking sections are formed on a projection or recess, particularly preferably on a common projection or recess. Preferably, the engagement sections are formed on a projection or recess, or particularly preferably on a common projection or recess, in or on the plate. The recesses can generally be formed as a cutout.In an alternative embodiment, in which a locking section is formed on a projection and a second locking section on a recess, it is advantageous to define a predetermined installation position of the plate relative to the pressure piece, which avoids assembly errors.

[0013] In one embodiment, the first engagement section and the second engagement section, and / or the first locking section and the second locking section, each define a polygonal cross-section, preferably with rounded corners. The polygonal shape of the engagement units defined by the engagement sections and the locking units defined by the locking sections results, firstly, in simplified and cost-effective manufacturing of the respective sections, and secondly, in large-area support of the locking units on the engagement units. Quadrilateral cross-sections are particularly preferred as polygonal cross-sections. In a simplified and particularly preferred embodiment, a rectangular cross-section is defined by both the engagement sections and the locking sections. This results in particularly cost-effective and simple manufacturing and support along two principal axes.In one embodiment, the first engagement section and the second engagement section and / or the first locking section and the second locking section each have a cross-section with at least partially rounded edges, preferably one engagement section and / or locking section having a straight extension. A rounded geometry on the inner surfaces of recesses and the outer flanks of projections achieves a particularly uniform force distribution when the engagement sections engage the locking sections. A combination of rounded, especially convex, surfaces and straight, preferably flat, surfaces is considered particularly advantageous, as this combines the benefits of a uniform force distribution with simplified manufacturing.

[0014] In one embodiment, the maximum extension length of the first engagement section is related to the maximum extension length of the second engagement section in a ratio of 0.1 to 0.8, preferably 0.4 to 0.6. Similarly, in another embodiment, the maximum extension length of the first locking section is related to the maximum extension length of the second locking section in a ratio of 0.1 to 0.8, preferably 0.4 to 0.6. The size ratio between the longest and shortest sides of the engagement units or locking units provides the desired support, which is more extensive in one locking direction than in the other, while simultaneously resulting in only minimal weakening of the plate due to the overall small recesses or cutouts.

[0015] Furthermore, preferably at least one projection has a smaller extension in or parallel to a plane orthogonal to the direction of force than the corresponding recess, such that the projection can be inserted into the recess with clearance. Advantageously, a clearance fit is provided between the projection and the corresponding recess engaging with the projection. Avoiding jamming of the projection in the recess reduces material stresses, particularly when individual components of the brake system heat up. Moreover, the clearance fit facilitates the mounting of a pressure plate, which simplifies the assembly of the brake system, especially when replacing brake pads that are fixed to the plates.

[0016] In one embodiment, a recess is provided which has a first engagement section and a second engagement section, wherein at least two projections are provided which can be brought into engagement with the recess or are already engaged, one of the projections having the first locking section and another of the projections having the second locking section. Particularly to save weight, in one embodiment a single projection, as already described, can be divided into several partial projections, each of which is designed and provided for locking and force transmission in essentially only one of the locking directions. In this way, with less weight, the force transmission surfaces can be optimally adjusted to the expected forces on the interface between the pressure piece and the plate.

[0017] The projection has a cross-section in a plane perpendicular to the direction of force, and the recess in the same plane has a cross-section, the area of ​​which is preferably 0.8 to 0.98 times, and more preferably 0.85 to 0.95 times, the area of ​​the recess cross-section. It has been shown that an optimal clearance fit, which prevents excessive rattling of the plate against the pressure piece, can be achieved particularly when the area of ​​the projection cross-section is 0.8 to 0.98 times that of the corresponding recess cross-section in the same plane. The projection cross-section is specifically defined as that in a cross-sectional plane parallel to the contact surface and / or perpendicular to the force axis. Similarly, the recess cross-section is preferably defined in the same cross-sectional plane.The relevant surface areas of the cut surfaces are then placed in the appropriate ratio to each other. In the test, the narrower range of 0.85 to 0.95 times the surface area of ​​the return cross-section achieved the best compromise between sufficient clearance to simplify assembly and simultaneously ensuring tight guidance of the plate on the pressure piece within the average temperature range of the braking system.

[0018] In one embodiment, the at least one recess has a chamfered, beveled, or rounded entry area, which facilitates the insertion of the corresponding projection into the recess. Preferably, at least one of the locking sections and at least one corresponding engagement section are not orthogonal to the plane that is orthogonal to the direction of force. The advantage of this embodiment is that it simplifies the assembly of the disc brake. In particular, the chamfered or rounded edge of the recess makes it easier to insert the corresponding projection into the recess, even with a preferably small clearance between the projection and the recess.In a further embodiment, not only is the entry area at the edge of a recess provided with a chamfer, but the projections and recesses are likewise chamfered at least on one of their side faces. In one embodiment, a projection is truncated pyramid-shaped and designed to engage with a similarly truncated pyramid-shaped recess. Analogous chamfered geometry of the projections and recesses is advantageously also possible based on other geometric shapes of the base surface in the plane perpendicular to the direction of force. A key advantage of this embodiment is that the base area of ​​a projection at the level of the force transmission surface is larger than the cross-sectional area in the plane parallel to the plane perpendicular to the direction of force, which a projection has at its end furthest from the force transmission surface.In other words, the cross-sectional area of ​​the projection and / or recess decreases with increasing distance from the force transmission surface. This embodiment allows the projection to slide into the respective recess and simultaneously increases the contact area available for force transmission between the plate and the pressure piece, thus avoiding local stress concentrations.

[0019] In one embodiment, the first locking section and the second locking section are formed on a common projection or a common recess, wherein the first engagement section and the second engagement section are correspondingly formed on a common recess or a common projection. In this embodiment, each projection thus has two mutually oblique or perpendicular contact surfaces, which form either the two locking sections or the two engagement sections. Analogously, each recess has the other of the corresponding engagement or locking sections.In this way, with just a single projection which engages in a corresponding recess, the mounting of the pressure piece on the plate can be achieved securely, whereby the pressure piece is secured both against lateral displacement perpendicular to the force axis and against rotation relative to the pressure piece.

[0020] According to one embodiment, at least one of the locking sections and / or at least one of the engagement sections is designed as a substantially flat or planar contact surface. The advantage of designing at least one of the locking sections or engagement sections as a flat or planar contact surface is that full-surface engagement can be achieved when supporting the plate on the pressure piece, thus avoiding local stress concentrations, such as Hertzian contact pressure. Simultaneously, a specific first and / or second locking direction can be defined by planar and flat contact surfaces, which, particularly in the interaction with a preload element described below, enables optimal fixation of the plate to the pressure piece and in the brake caliper of the disc brake. Within the scope of the present invention, the term "substantially" is always defined as "predominantly" or "to the greatest extent."In the context of the present invention, a substantially flat extent therefore means that the predominant part of the contact surface is planar and / or flat, with predominant preferably being considered as 60-95%, preferably as 70-90%.

[0021] In one embodiment, the area of ​​the contact surface defined between one of the locking sections and one of the engagement sections is 0.05 to 0.3 times, preferably 0.05 to 0.15 times, the total surface area of ​​the respective projection. The total surface area is preferably defined as the area of ​​the projection that has a portion extending along or parallel to the force axis. In other words, the total surface area of ​​the projection is the outer surface of the projection that is oriented in the direction of the corresponding recess and thus forms a potential locking section or engagement section.It is therefore preferred within the scope of the present invention that at least 0.05-0.3 times this theoretically available total contact area between the projection and the recess is actually used as a contact area between the projection and the recess, particularly when the plate is pre-tensioned against the pressure piece by means of a pre-tensioning element.

[0022] According to one embodiment, the first locking section and the second locking section are predominantly, preferably completely, surrounded by the contact surface. It has proven particularly advantageous to design the locking sections entirely within the contact surface and thus surrounded by it. In this way, a uniform force distribution can be achieved when the braking force is applied by the pressure piece and transmitted to the plate, while the locking sections simultaneously secure the plate against the pressure piece. In one embodiment, the locking sections, which are formed on one or more projections, protrude from the essentially flat contact surface, with the contact surface extending around the respective projection.In contrast, if the plate is guided and supported on the pressure piece by projections that partially encompass and support the edge of the plate, stress peaks occur particularly in this edge area, which can be reduced by the present embodiment with securing sections embedded in the contact surface.

[0023] In one embodiment, the first locking section and the second locking section form a locking unit, or two first locking sections form a locking unit and two second locking sections form a further locking unit, wherein the first engagement section and the second engagement section form an engagement unit, or two first engagement sections form an engagement unit and two second engagement sections form a further engagement unit, wherein the pressure piece has at least two locking units spaced apart from each other, and wherein the plate has at least two engagement units spaced apart from each other. Within the scope of the present invention, a locking unit is defined as a group of two locking sections with the features described above. Similarly, an engagement unit is defined as a group of two engagement sections.In one embodiment of the invention, the pressure piece has at least two locking units, i.e., two first and two second locking sections, which are spaced apart from one another. Correspondingly, the plate advantageously has at least two engagement units. It is understood in this context that there can be a greater number of locking units or engagement units provided on recesses than the corresponding locking units or engagement units provided on projections. This makes it possible, for example, to provide fixing options for a large number of differently shaped plates on a pressure piece equipped with locking units formed on recesses.Alternatively, a plate equipped with a multitude of engagement units formed on recesses can be designed for fixing to various pressure pieces of different braking systems.

[0024] Preferably, one of the locking units is designed with a different geometry and / or orientation relative to the holding axis than the other locking unit, and correspondingly, one of the engagement units is designed with a different geometry and / or orientation relative to the holding axis than the other engagement unit. In particular, by having one of the locking units have a different geometry and / or orientation than the other locking unit, a predefined installation direction of the plate on the pressure piece can be specified, wherein, in particular, the direction of rotation of the brake disc relative to the brake pad defines this installation direction.Furthermore, the use of engagement and locking units with different geometries allows for optimized and large-area support against displacement not only along the first and second locking directions, but also in other directions between the plate and the pressure piece. This minimizes wear on the locking and engagement units and, in particular, achieves a particularly material-friendly support of the plate against the pressure piece.

[0025] In one embodiment, the locking units are designed and aligned symmetrically to a plane orthogonal to the holding axis, and the engagement units are designed and aligned symmetrically to the same plane orthogonal to the holding axis. The advantage of the plane-symmetrical engagement geometry between the plate and the pressure piece is that it allows the plates to be arranged in a reversed configuration on the left and right sides of the vehicle.

[0026] In one embodiment, the plate has a brake lining on its side facing away from the first and second engagement sections, thus forming a brake lining unit. As previously described, the plate is preferably part of a brake lining unit, wherein a brake lining, preferably ceramic, NAO, or organic, is integrally molded onto the plate or attached to the plate by conventional fastening methods on the side of the plate facing away from the pressure piece. In this way, additional components are avoided wherever possible, so that the plate rests directly against the pressure piece and the brake lining is also directly connected to the plate or formed integrally. This simplifies the manufacturing of the brake lining unit. Furthermore, the elimination of intermediate elements reduces the disc brake's susceptibility to failure.

[0027] The disc brake is preferably designed as a single-piston disc brake. In contrast to the alternative solution of a two-piston disc brake, in which the brake pads are pressed against a brake disc by two parallel pressure pistons, the present disc brake is particularly lightweight. The single-piston disc brake design necessitates improved support of the disc and the caliper during braking, particularly to reduce tilting of the pressure piece along with the brake pad assembly. The disc brake according to the present invention is particularly well-suited for this purpose, as a combination of support of the disc via the first or second edge on the carrier and support acting in the plane perpendicular to the direction of force by the retaining elements on the engagement units allows for stable mounting of the disc and reduces tilting during braking.A single-piston disc brake can also be called a single-piston disc brake.

[0028] In one embodiment, the pressure piece has a central cylindrical section on the side opposite the contact surface, which is designed to actively participate in positioning the pressure piece along the force axis. The cylindrical section is a portion of the pressure piece extending along the force axis and has a length parallel to the force axis that is approximately 0.5 to 1 times the maximum extent of the pressure piece perpendicular to the force axis. This allows the cylindrical section, for example, to be designed as part of an adjustment mechanism that actively participates in setting the position of the pressure piece relative to the saddle along the force axis. In one embodiment, the cylindrical section has an internal thread. It is particularly preferred that the cylindrical section be designed as part of an adjustment mechanism.

[0029] In one embodiment of the disc brake, a preload element is provided, particularly on the brake plate, which preloads the plate, especially perpendicular and / or transversely to the direction of force, against a brake carrier, preferably such that one of the edges of the plate abuts a retaining horn of the brake carrier. The preload element is preferably an elastic spring steel element that engages the plate and preloads it transversely to the direction of force against the brake carrier, preferably against a retaining horn of the brake carrier. The preload element advantageously bears against the caliper of the disc brake, with the caliper in turn engaging the pressure piece with a clearance fit.

[0030] In a further embodiment, the pretensioning element establishes a pretensioning force between a saddle and the plate, which acts along a force vector. This force vector has a component parallel to the first locking direction and a component parallel to the second locking direction, such that the pretensioning force applied by the pretensioning element pretensions the first locking section against the first engagement section and simultaneously pretensions the second locking section against the second engagement section. The pretensioning force of the pretensioning element is preferably oriented such that not only one of the locking sections comes into contact with the corresponding engagement section for support, but at least two locking sections each come into contact with and are supported by a corresponding engagement section.The clamping element thus supports the large-area support which, according to the invention, is to be present between the pressure piece and the plate. At the same time, the clamping element reduces rattling and shocks, or vibrations of the plate relative to the pressure piece, which in turn reduces the wear of the locking and engagement units. The caliper is, in particular, a floating caliper of the disc brake.

[0031] In one embodiment, the disc brake comprises a caliper and a brake carrier, wherein the plate has a first edge and a second edge distal to the first edge, wherein the plate is guided against the brake carrier at the first and / or second edge and secured against displacement perpendicular to the direction of force and along a retaining axis relative to the brake carrier, wherein the pressure piece is guided on the plate and substantially secured against displacement transversely to the direction of force. In addition to being supported on the plate, the pressure piece can also be guided in 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.As previously mentioned, the disc brake comprises, in addition to the pressure piece and the brake plate, a caliper, which can also be designed as a floating caliper, and a brake carrier. The caliper can also be referred to as a brake caliper. The brake carrier of the disc brake is, in particular, directly or indirectly attached to or connected with the axle, preferably the axle stub of a vehicle's wheel suspension. The brake caliper, which is also referred to as a caliper, is arranged to be movable relative to the brake carrier. The pressure piece is positioned relative to the brake carrier, in particular by the guided engagement with the brake plate and the engagement of the brake plate with the brake carrier.In contrast to other disc brakes known from the prior art, where the force transmission elements 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 brake 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.

[0032] In one embodiment, the locking sections are integrally formed on the pressure piece or permanently fixed, while the engagement sections are integrally formed on the plate or permanently fixed, with the locking sections directly contacting and engaging the corresponding engagement sections without intermediate elements. In other words, the present invention specifically eliminates intermediate elements between the contact surface of the pressure piece and the plate. In particular, the engagement sections and the locking sections are each integrally formed on the plate or pressure piece, respectively. 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.

[0033] According to one embodiment, the at least one locking unit is completely surrounded by the contact surface or a plurality of contact surfaces in a section plane orthogonal to the force axis, wherein preferably the cross-sectional area of ​​the locking unit present in the section plane, in particular the projection formed on the pressure piece, bears a ratio of 0.05 to 0.3, preferably 0.1 to 0.2, to the contact surface. The small area ratio between the cross-sectional area of ​​the locking units and the contact surface responsible for transmitting the braking force advantageously results in only minimal material weakening of the contact surface on both the pressure piece and the plate. In a preferred embodiment, in which both locking units, or...If all projections and / or recesses are surrounded by a common mounting surface, i.e., if at least two separate mounting surfaces are not provided, the ratio is calculated from the sum of the cross-sectional areas of all projections / recesses and the area of ​​the common mounting surface by which they are surrounded.

[0034] According to the invention, a brake pad and / or a plate is used in a disc brake, wherein the brake pad is, in particular, fixed to the plate. A brake pad used in a disc brake with the features described above is always optimally aligned relative to the brake disc, and the risk of tilting or misalignment of the brake pad is always minimized due to the special guidance of the pressure piece. The plate or brake pad can have the features described above or below in relation to the plate and / or the brake pad.

[0035] According to the invention, a brake disc is used in a disc brake, wherein the brake disc is arranged, in particular, between two brake pads, 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.

[0036] 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 total mass of more than 3.5 t, preferably more than 7.5 t, and particularly preferably more than 15 t. The commercial vehicle can, in particular, be a trailer, especially a commercial vehicle trailer. The trailer can be configured as a semi-trailer.

[0037] Another aspect of the present invention relates to a plate, in particular for use in a disc brake, wherein the plate is preferably part of a brake pad unit of the disc brake, wherein a first engagement section is formed on the plate, which is preferably formed on a recess, wherein a second engagement section is formed spaced apart from the first engagement section, which is preferably formed on the same recess as the first engagement section or on a further recess, wherein the first engagement section is formed and aligned to support a pressure piece relative to the plate along a first locking direction, wherein the second engagement section is formed and aligned to support a pressure piece relative to the plate along a second locking direction, wherein the first locking direction and the second locking direction are preferably transverse to a force direction.The plate has two locking directions along which a force can be transmitted from a pressure piece to the plate, with the first locking direction being inclined or perpendicular to the second locking direction. Advantageously, the plate serves as the carrier plate for a brake pad and is part of a brake pad assembly for a disc brake. On its side facing away from the brake pad, the plate has two separately spaced engagement sections that support a pressure piece engaging in the engagement sections along a first and a second locking direction. These locking directions lie in a common plane and are not parallel to each other. This design makes the plate particularly suitable for use in a disc brake with reduced stress peaks and Hertzian surface pressure.

[0038] Another aspect of the present invention relates to a plate, in particular for use in a disc brake, wherein the plate is preferably part of a brake pad unit of the disc brake, wherein a first engagement section is formed on the plate, which is preferably formed on a recess, wherein a second engagement section is formed spaced apart from the first engagement section, which is preferably formed on the same recess as the first engagement section or on a further recess, wherein the first engagement section is designed and aligned to support a pressure piece relative to the plate, wherein the first securing direction extends transversely to a force direction along which a force can be transmitted from a pressure piece to the plate, wherein the second engagement section is designed and aligned to support the pressure piece on the plate along or parallel to a second securing direction.and wherein the first locking direction is inclined to the second locking direction. The plate is advantageously the carrier plate for a brake pad and is part of a brake pad assembly of a disc brake. The plate preferably has two spaced-apart engagement sections on its side facing away from the brake pad, which provide support for a pressure piece engaging in the engagement sections along a first and a second locking direction, wherein the locking directions lie in a common plane and are not parallel to each other. This makes the plate particularly suitable for use in a disc brake with reduced stress peaks and Hertzian surface pressure.

[0039] In one embodiment of the plate, the at least one recess has a chamfered, beveled, or rounded entry area, which facilitates the insertion of a corresponding projection into the recess, wherein preferably at least the engagement section is not orthogonal to the plane which is orthogonal to the direction of force.

[0040] In one embodiment of the plate, the first engagement section and / or the second engagement section are formed on a recess on the plate, wherein the recess has a depth measured parallel to the force axis which is 0.5 to 0.95 times, preferably 0.6 to 0.8 times, the thickness of the plate measured parallel to the force axis.

[0041] In one embodiment of the plate, at least one of the engagement sections has a substantially flat or planar contact surface. In another embodiment of the plate, the first engagement section and the second engagement section form an engagement unit, or two first engagement sections form one engagement unit and two second engagement sections form another engagement unit, wherein the plate has at least two engagement units which are spaced apart from each other.

[0042] In one embodiment of the plate, the plate has a first edge and a second edge distal to the first edge, wherein a retention axis runs substantially perpendicular to the first and second edges, wherein the plate has two engagement units, wherein two first engagement sections are formed on one of the engagement units and two second engagement sections are formed on the second of the engagement units, wherein the first engagement sections are each oriented such that the first securing direction includes a first angle with the retention axis and the second engagement sections are each oriented such that the second securing direction includes a second angle with the retention axis, wherein the first and the second angles are greater than 0° and less than 90°.

[0043] In one embodiment of the plate, the first securing direction includes the first angle with the holding axis, which is preferably greater than 5°, and wherein the second securing direction includes the second angle with the holding axis, which is different from the first angle.

[0044] Another aspect of the invention may relate to a commercial vehicle with a disc brake as described above or below.

[0045] 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 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 explicit exclusion. The figures show:

[0046] Fig. 1 shows a view of one embodiment of a plate,

[0047] Fig. 2 shows a view of one embodiment of a plate,

[0048] Figs. 3 to 5 show three perspective views of different embodiments of components of a disc brake.

[0049] Fig. 6 shows a view of an embodiment of a disc brake;

[0050] Fig. 7 shows a perspective view of an embodiment of components of a disc brake;

[0051] Figs. 8 and 9 are perspective views of another embodiment of components of a disc brake;

[0052] Fig. 10 shows a partially cutaway view of an embodiment of a disc brake;

[0053] Fig. 11 is a schematic top view of an area of ​​an embodiment of a disc brake;

[0054] Fig. 12 shows a side view of an embodiment of a plate;

[0055] Fig. 13 shows a blank for producing a printing piece;

[0056] Fig. 14 shows an embodiment of a pressure piece,

[0057] Fig. 15 shows an embodiment of a plate,

[0058] Fig. 16 shows another embodiment of a plate, Fig. 17 shows an embodiment of a pressure piece,

[0059] Fig. 18 shows a perspective view of an embodiment of a printing piece and a plate, and

[0060] Figs. 19 to 21 show another embodiment of a pressure piece and a plate.

[0061] Figures 1 and 2 show two embodiments of a plate 4 with engagement units 40 formed on it, each inclined to the holding axis H. Rectangular engagement units 40 are shown as an example in Figure 1, which are particularly easy to manufacture. The first engagement sections 42A are oriented such that the first locking direction A, defined by their orientation, is inclined at a first angle α to the holding axis H. Due to the essentially rectangular shape of the engagement units 40, the second angle β, which the second locking direction B forms with the holding axis H, is equal to the first angle but mirrored. This allows the engagement sections 42A and 42B to be supported on their long sides by the support sections (not shown), thus enabling particularly large-area support.It is understood that, according to one of the embodiments described below, the engagement sections 42A, 42B and, analogously, the corresponding locking sections 22A, 22B can also be arranged in non-perpendicular orientations, whereby the sum of the first and second angles α, β can be less than or greater than 90°. The embodiment of the plate 4 shown in Figure 1 has a symmetrical geometry, with the central plane M, which is orthogonal to the holding axis H, being the plane of symmetry. Within the scope of the present invention, it is provided that the engagement units 40 and locking units 20 shown in the embodiments of Figures 3-11 can also be arranged such that both locking directions A, B each enclose an angle α, β with the holding axis H that is greater than 1°.The embodiment of the plate 4 shown in Figure 2 shows further geometric variants of the engagement units 40 with rounded flanks and with combinations of rounded and straight first and second engagement sections, which, as in Figure 1, are each inclined to the holding axis H.

[0062] The embodiment of a plate 4 and a pressure piece 2 shown in Figure 3 demonstrates a way to achieve the largest possible support of the plate 4 on the pressure piece 2. Preferably, more than two projections V and correspondingly more than two recesses R are provided on the plate 4 and the pressure piece 2, on which locking units 20 and engagement units 40 are formed. In this embodiment, the locking and engagement units 20, 40 formed on the individual projections V and recesses R are each designed with substantially flat contact surfaces for force transmission in a multitude of different locking directions A, B. In this embodiment, the arrangement and geometry of the respective projections V and recesses R are symmetrical on the pressure piece 2 and plate 4, so that it is possible to reverse the installation direction of the plate 4.The plate 4 can also be arranged on the opposite side of a brake disc 8.

[0063] The embodiment shown in Figure 4 features, in particular, L-shaped projections V and corresponding recesses R, which also allow for large-area support along both the first securing direction A and the second securing direction B. All contact surfaces between the respective securing section 22A, 22B and the opposing engagement section 42A, 42B are essentially flat and planar, enabling almost complete and full-surface contact for force transmission.

[0064] While in the embodiments of Figures 3 and 4, as well as in the embodiments described above, the locking sections 22A, 22B are always located within the contact surface 24, Figure 5 shows an embodiment in which the central projection V with locking sections 22A, 22B formed thereon protrudes from a surface of the pressure piece 2 that is not directly in contact with the plate 4. This embodiment may be particularly advantageous if a defined contact surface 24, with a corresponding surface treatment to increase hardness, is provided only in the outer areas of the flange-like head of the pressure piece 2, but a corresponding locking mechanism against lateral displacement of the plate 4 relative to the pressure piece 2 is nevertheless required in the central area of ​​the pressure piece.It is understood that, in addition to the embodiments and combinations of projections V and recesses R on the pressure piece 2 and on the plate 4 shown here, further combinations or even a higher number of corresponding locking units 20 and engagement units 40 may be provided within the scope of the present invention. However, the greater the number of mutually engaging and positively interlocking sections, the more complex the surface design of the respective corresponding components becomes, and the greater the manufacturing effort. An arrangement of two spaced-apart engagement units 40 with locking units 20 engaging therein has therefore proven to be a particularly simple design, which has achieved optimal results both in terms of ease of manufacture and in terms of the transmissible forces.

[0065] The embodiment of a disc brake 1 shown in Figure 6 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 against displacement parallel to a holding axis H at its first edge 43 (shown on the left in Figure 6) and at its second edge 44 (shown on the right in Figure 6). Furthermore, the plate 4 is supported on its underside against the brake carrier 9 and is pre-tensioned against the brake carrier 9 by a clamping element 6 with a pre-tensioning force that acts 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. The plate 4 is preferably part of a brake pad assembly 48. 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 over a substantially full surface area. The locking units 20 are advantageously arranged on projections V on the pressure piece 2, the projections V being substantially 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 and 22B, to which the corresponding engagement sections 42A and 42B can connect. The corresponding engagement units 40 are advantageously arranged on recesses R formed on the plate 4. The recesses R have a slightly larger surface area in the plane of view of Figure 4 than the projections V, in order to allow for a correspondingly tight fit.

[0066] Figure 7 shows a perspective view of a plate 4 and a corresponding pressure piece 2. The plate 4 has two elongated recesses R of different sizes, each containing an engagement unit 40. The first engagement section 42A of each engagement unit 40 is preferably designed as a substantially rectangular and flat surface. The second engagement section 42B is semi-cylindrical in this embodiment. Correspondingly, the pressure piece 22 has differently sized, T-nut-shaped projections V, each containing a locking unit 20. Corresponding to the engagement sections 42A and 42B, the first locking section 22A is designed as a rectangular and substantially flat contact surface. The second locking section 22B is semi-cylindrical, analogous to the second engagement section 42B.The second locking section 22B and the second engagement section 42B are each designed such that they can be brought into contact with each other with as large a proportion of their total surface area as possible, in order to achieve a large force transmission area and minimize local stress peaks. The different geometries of the locking and engagement units 20, 40 allow for a predefined installation position of the plate 4 on the pressure piece 2.

[0067] The perspective view of another embodiment of a disc brake 1 shown in Figure 8 is similar to the embodiment shown in Figure 7, except that one of the projections, on which a locking unit 20 is provided, has a substantially cruciform cross-sectional geometry. The projection shown on the left in Figure 7 with the locking unit 20 formed on it is similar to the embodiment shown in Figure 5. The plate 4 and the brake pad 46 form a brake pad unit 48, which is usually designed as an integral unit. In other words, the brake pad 46 is preferably permanently fixed to the plate 4. In view of the asymmetrical design of the brake pad 46 provided on the plate 4, it is preferred in this embodiment to specify an installation direction of the plate 4 on the pressure piece 2.The different geometries of the respective locking units 20 with corresponding engagement units 40 (concealed) are advantageous here. Figure 9 shows the embodiment shown in Figure 8 from a different perspective. In this embodiment, the engagement units 40 are formed on recesses R in the material of the plate 4.

[0068] Figure 10 shows a partially cutaway view of a brake system with a disc brake 1. A brake disc 8 is arranged between two brake pads 46. At least one of the brake pads 46 is attached to or permanently fixed to a plate 4 according to one of the previously described embodiments and thus forms a brake pad unit 48 together with the plate 4. The cutaway section shows a section through a retaining element 20 formed on a projection V. The geometry of the projection V essentially corresponds to the embodiment shown in Figures 5 and 6. The pressure piece 2 is held and guided in a recess on the caliper 3.

[0069] The schematic view in Figure 11 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 force section 45A, 45B are formed on the plate 4, to which the preloading element 6 preferably engages with its first clamping section 62A and its second clamping section 62B in a positive-locking manner. The preloading element 6 is supported by a support 5 of the brake caliper (not shown). In particular, the preloading element 6 is supported by a first support section 64A on the support 5.In this preferred embodiment, the arrangement of the preload element 6, the support 5, and the corresponding force sections 45A, 45B is asymmetrical with respect to the central plane M. 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 is supported 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 9, 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 securing direction A and the second securing direction B run essentially vertically and horizontally, respectively, whereas in the embodiment shown on the right side, the securing 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 and 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 9.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 between the pressure piece 2 and the plate 4 can be transmitted in a particularly optimized manner.

[0070] Figure 12 shows a side view of a plate 4 with a brake pad 46 attached to it. The engagement unit 40 integrated into the plate 4 preferably has a depth T that is approximately 0.6 to 0.8 times the thickness of the plate 4 measured parallel to the force axis K. In this way, an optimal compromise can be achieved between maximizing the possible engagement area parallel to the force axis K between the engagement unit and the locking unit 40, 20, and protecting the transition area between the brake pad 46 and the plate 4 from the ingress of corrosive media.

[0071] Figure 13 shows an embodiment of a blank for a pressure piece 2, in which, in particular, pre-formed projections 20A are formed for further processing. These projections can then be used to form locking units 20, shaped as projections V, according to one of the preceding or following embodiments in a further manufacturing step, preferably milling or honing. The cross-sectional geometry of the projections 20A intended for further processing is designed such that a multitude of different embodiments of the locking units 20 provided within the scope of this invention can be formed from one and the same original geometry.

[0072] Figure 14 shows another preferred embodiment of a pressure piece 2, in which two locking units 20, designed as projections V, are provided and have a substantially square base shape. Furthermore, the locking units 20 have different orientations and are each pivoted relative to the holding axis H such that the first locking direction A forms a first angle α with the holding axis H and the second locking direction B forms a second angle β with the holding axis. This pivoting ensures that the first locking sections 22A provided on the left-hand locking unit 20 allow support along the first locking direction A, while the second locking sections 22B provided on the right-hand locking unit 20 allow support along the second locking direction B.In particular, in the preferred case where the pressure piece 2 designed according to Figure 14 is brought into engagement with a plate 4 according to the embodiment shown in Figure 15, the plate 4 is thus supported on the pressure piece 2 only in the area of ​​the substantially straight engagement sections 42A and 42B, which are arranged obliquely above and obliquely below. This results in the support in the first securing direction A taking place on a different projection V of the pressure piece than the support along the second securing direction B.The design of the locking units 20 according to Figure 14 as essentially square projections has the advantage that they are particularly easy to manufacture, and that the square basic shape of the projections V can be engaged with a variety of different geometries of engagement units 40, provided that these have suitable engagement sections 42A, 42B which allow for large-area contact with the locking sections 22A, 22B. Alternatively to the square basic shape, the locking units 20 can also have a rectangular cross-sectional geometry or a cross-sectional geometry analogous to the slotted shape of Figure 15, each of which is pivoted with a first angle α and / or a second angle β according to Figure 14.Similar to the embodiment of Figure 7, the embodiment of a pressure piece 2 shown in Figure 14 also shows slightly chamfered projections V, in which, particularly at the outer edge, a desired geometry is provided which facilitates insertion into the corresponding engagement unit 40 designed as a recess R.

[0073] Figure 15 shows a preferred embodiment of a plate 4 with two engagement units 40, which, analogous to the embodiment of the pressure piece in Figure 11, are pivoted at a first angle a and a second angle β relative to the holding axis H, in order to preferably engage in a large-area, positive-locking engagement with the projections V of the pressure piece 2 from Figure 11. The positive-locking engagement with the first engagement sections 42A shown on the right thus allows full-surface contact with the first locking sections 22A of the pressure piece and therefore support along the first locking direction A. Similarly, the alignment and essentially straight design of the second engagement sections 42B allows full-surface contact with the second locking sections 22B, which results in support of the plate 4 against the pressure piece 2 along the second locking direction B.The section line shown at the left engagement unit 40, in conjunction with the corresponding section shown on the right in the figure, illustrates the cross-sectional geometry of the plate 4 in the area of ​​the engagement unit 40. Preferably, the engagement unit 40 is designed as a local, elongated recess R, wherein this recess has a depth T in the material of the plate 4 that is in a ratio of 0.4 to 0.9 to the thickness D of the plate 4 in the area of ​​the engagement unit 40. It is understood that the deeper the recess is incorporated into the material of the plate 4, i.e., the larger the ratio described above, the greater the engagement area available for the positive locking engagement. However, this also results in a greater reduction in the strength of the plate 4.Tests conducted by the applicant of the present invention have shown that a range of 0.6 - 0.8 ensures a particularly good compromise between sufficient strength and a sufficiently large contact area between the locking units and the engagement units.

[0074] Figure 16 shows another embodiment of a plate 4 with engagement units 40 designed as a recess R. Similar to the embodiments of Figures 1 and 2, the engagement units 40 define first and second engagement sections 42A, 42B, each pivoted and aligned with the holding axis H such that the locking directions A, B form an angle α, β with the holding axis H that is greater than 0° and less than 90°. In contrast to the embodiments described above, however, the first locking direction A provided on the engagement unit 40 shown on the left in the figure forms a first angle α with the holding axis H, while the second locking direction B shown on the right in the figure forms a second angle β with the holding axis H. The first angle α and the second angle β are different from each other in this embodiment. Advantageously, the angles α, β are in the range of 40° to 80°.In one embodiment, the angles a, β differ from each other by approximately 5° to 25°. The advantage of the different inclinations of the first and second engagement sections 42A, 42B to the holding axis H lies in the fact that, for a specific direction of rotation of a brake disc 8 relative to the retaining plate 4, the fixing of the plate 4 to the brake carrier 9 is supported by optimally directed forces transmitted to engagement sections 42A, 42B. In particular, the engagement unit 40 on the leading side (i.e., the side first encountering the brake disc rotation) can have a shallower angle a, β than the side on the side facing away from the direction of rotation. This reduces, in particular, the tendency of the plate 4 to wedge itself against the brake carrier 9 during braking.It is understood that corresponding locking units 20 are formed on a corresponding pressure piece 2, which are also inclined at different first and second angles α and β to the holding axis H and can thus engage with the engagement units 40 according to Fig. 16 over a large area. Besides the polygonal and elongated shape shown in Fig. 13, which allows for particularly large-area support on the engagement sections 42A, 42B, the basic shapes of the engagement units 40 used in the previously discussed embodiments can also be used as the basic form of the engagement units 40. Accordingly, it is also provided within the scope of the invention to form the engagement units and locking units used in the previously discussed embodiments inclined at different angles α and β to the holding axis.

[0075] The embodiment of a pressure piece 2 shown in Figure 17 is advantageously designed to engage with the embodiment of a plate 4 shown in Figure 16. Preferably, the first angle a, which the first securing direction A encloses with the retaining axis H, corresponds to the first angle a present on the plate 4 in the embodiment of Figure 16. In this embodiment of the pressure piece 2, and advantageously also in the embodiment of the plate 4 of Figure 16, the first angle a is larger than the respective second angle β. This advantageously allows a specific installation orientation of the plate 4 relative to the pressure piece 2 to be predetermined.Secondly, the different inclination of the locking units 20 and engagement units 40 can allow improved force transmission between pressure piece 2 and plate 4 when a force acting externally on the assembly results from a specific direction of rotation of a brake disc of the disc brake system. This is particularly advantageous for brake systems designed for mounting on the left or right side of the vehicle, especially to optimize the corresponding force effect and braking force absorption with respect to the direction of rotation and preferably to allow optimized use of installation space on the respective side of the vehicle.

[0076] Figure 18 shows an embodiment of a pressure piece 2 and an associated plate 4, in which one of the locking units 20 on the pressure piece 2 is designed as a projection V and one of the locking units 20 as a recess R. Similarly, one of the engagement units 40 on the plate 4 is designed as a recess R and one of the engagement units 40 as a projection. It is understood that this basic possibility of providing a combination of at least one projection V and at least one recess R on the plate 4 and / or on the pressure piece 2 can also be used in the embodiments of Figures 1-17. Thus, in addition to the different angles a and β, a combination of projections V and R can also determine a specific installation position of the plate 4 on the brake system.

[0077] The embodiment of a pressure piece 2 shown in Figure 19 is advantageously designed to engage with the embodiment of a plate 4 shown in Figure 20. Preferably, in this embodiment, the first angle a corresponds to the second angle β, with both angles a and β being approximately 70° to 80° and preferably approximately 75°. The locking units 20 on the pressure piece 2, designed as projections V, and the engagement units 40 on the plate 4, designed as recesses R, advantageously have a cross-sectional geometry that combines a polygonal outer geometry with a rounded or chamfered outer geometry. Advantageously, the locking units 20 on the pressure piece 2 have a chamfered and polygonal outer geometry on their mutually facing sides. The remaining area of ​​each locking unit 20 has a substantially rectangular outer geometry.In contrast, the opposing sides of the engagement units 40 on the plate 4 are essentially rectangular with rounded corners. On their outward-facing sides, the engagement units 40 have an approximately semicircular outer geometry. A feature shown only in Fig. 19, but which can also be provided for all of the previously shown embodiments of a pressure piece 2, are the guide pins 28. These guide pins provide guidance and prevent rotation in the brake caliper, for example, when the plate 4 is disengaged from the pressure piece 2 because it is being replaced. To prevent unintentional rotation of the pressure piece 2 relative to the brake caliper in this situation, the guide pins engage the caliper 3 and secure the pressure piece 2 against rotation.It should be noted that when the plate 4 is engaged with the pressure piece, this function of the guide pins 28 is generally not used, since the engagement between the locking sections 22A, 22B and the engagement sections 42A, 42B allows for significantly more precise guidance of the pressure piece 2.

[0078] Figure 21 shows a top view of a pressure piece 2 according to the embodiment shown in Fig. 19. It can be seen that the pressure piece 2 is not designed as a simple, flat, sheet-like body, but has a cylinder section 26 on the side opposite the contact surface 24. In the present embodiment, the cylinder section 26 is sleeve-shaped and preferably has an internal thread. In other embodiments, the cylinder section 26 can be designed as part of a hydraulic piston. The cylinder section 26 is not merely a force-transmitting part of the brake, but actively participates in positioning the pressure piece 2 and the plate 4 along the force axis, for example, by being part of an adjustment mechanism.The design of the pressure piece 2 with a cylinder section 26 is preferably also present in the previously shown embodiments of pressure pieces 2 according to Figures 3 - 5, 7 - 10, 13, 14, 17 and 18.

[0079] Reference symbol list:

[0080] 1 - Disc brake

[0081] 2 - Pressure piece

[0082] 3 - Saddle

[0083] 4 - Plate 6 - Prestressing element

[0084] 8 - Brake disc

[0085] 9 - Brake carrier

[0086] 20 - Fuse unit

[0087] 22A - first fuse section

[0088] 22B - second fuse section

[0089] 24 - Plant area

[0090] 26 - Cylinder section

[0091] 28 - Guide pins

[0092] 40 - Intervention unit

[0093] 42A - first intervention section

[0094] 42B - second intervention section

[0095] 43 - first edge

[0096] 44 - second margin

[0097] 46 - Brake pad

[0098] 48 - Brake pad unit a - first angle ß - second angle

[0099] A - first securing direction

[0100] B - second safety direction

[0101] D - Thickness

[0102] F - Force vector

[0103] H - Holding axis

[0104] K - Direction of force

[0105] M - Middle level

[0106] R - Return

[0107] T - Depth

[0108] V-lead

Claims

Claims 1. Disc brake (1), in particular for use in a commercial vehicle, comprising a pressure piece (2) and a plate (4), wherein the plate (4) is preferably part of a brake pad unit (48) of the disc brake (1), wherein the plate (4) is preferably provided with a brake pad (46) and is guided in a radial and tangential direction by a brake carrier (9), wherein the pressure piece (2) has at least one contact surface (24) against which the plate (4) comes to rest in order to transmit a pressure force along a force axis (K) from the pressure piece (2) to the plate (4), wherein the pressure piece (2) has at least one first retaining section (22A) which is designed and provided for support on a first engagement section (42A) formed on the plate (4),wherein the support of the first locking section (22A) on the first engagement section (42A) prevents displacement of the pressure piece (2) relative to the plate (4) along or parallel to a first locking direction (A), in particular by positive locking, wherein the first locking section (22A) has a contact surface which is shaped and arranged complementary to a contact surface of the first engagement section (42A) such that surface contact is present when the first locking section (22A) is supported on the first engagement section (42A).

2. Disc brake (1 ) according to claim 1 , wherein the first locking direction (A) is orthogonal to the contact surfaces of the first locking section (22A) and the first engagement section (42A).

3. Disc brake (1) according to one of the preceding claims, wherein the pressure piece (2) has a second locking section (22B), which is designed and provided for support on a second engagement section (42B) provided on the plate (4), wherein the support of the second locking section (22B) on the second engagement section (42B) prevents a displacement of the pressure piece (2) relative to the plate (4) along or parallel to a second locking direction (B), in particular by positive locking.

4. Disc brake (1) according to claim 3, wherein the second locking section (22B) has a contact surface which is shaped and arranged complementarily to a contact surface of the second engagement section (42B) such that surface contact is present when the second locking section (22B) is supported on the second engagement section (42B), wherein the second locking direction (B) is preferably orthogonal to the contact surface between the second locking section (22B) and the second engagement section (42B).

5. Disc brake (1) according to one of the preceding claims, wherein the at least one contact surface of the respective engagement section (42A, 42B) with the corresponding locking section (22A, 22B) has an area in the range between 5 mm 2 up to 200 mm 2 , preferably 30 mm 2 up to 100 mm 2 , exhibits.

6. Disc brake (1) according to one of the preceding claims, wherein the first engagement section (42A) and / or the second engagement section (42B) is formed on a recess (R) on the plate (4), wherein the recess (R) has a depth (T) measured parallel to the force axis (K) which is 0.5 to 0.95 times, preferably 0.6 to 0.8 times, the thickness (D) of the plate (4) measured parallel to the force axis (K).

7. Disc brake (1) according to one of the preceding claims, wherein the plate (4) has a first edge (43) and a second edge (44) distal to the first edge (43), wherein the plate (4) can be secured at the first and / or second edge (43, 44) against displacements perpendicular to the force direction (K) and along a holding axis (H), wherein the first securing direction (A) and the second securing direction (B) are inclined at a first angle (a) or a second angle (β) to the holding axis (H), which is each greater than 1° and less than 90°, wherein the first securing direction (A) includes the first angle (a) with the holding axis (H), which is preferably greater than 5°, and wherein the second securing direction (B) includes the second angle (β) with the holding axis (H), which is different from the first angle (a).

8. Disc brake (1) according to one of the preceding claims, wherein the first engagement section (42A) and the second engagement section (42B) and / or the first locking section (22A) and the second locking section (22B) each define a polygonal cross-section.

9. Disc brake (1) according to one of claims 1 to 7, wherein the first engagement section (42A) and the second engagement section (42B) and / or the first locking section (22A) and the second locking section (22B) each define a cross-section with at least partially rounded edges, wherein preferably one engagement section (42A, 42B) and / or locking section (22A, 22B) has a straight extension.

10. Disc brake (1 ) according to one of the preceding claims, wherein a maximum extension length of the first engagement section (42A) to a maximum extension length of the second engagement section (42B) is in a ratio of 0.1 to 0.8, preferably 0.4 to 0.

6.

11. Disc brake (1) according to one of the preceding claims, wherein a maximum extension length of the first securing section (22A) to a maximum extension length of the second safety section (22B) in a ratio of 0.1 to 0.8, preferably 0.4 to 0.

6.

12. Disc brake (1) according to one of the preceding claims, wherein the first locking section (22A) and the second locking section (22B) form a locking unit (20), or two first locking sections (22A) form a locking unit (20) and two second locking sections (22B) form a further locking unit (20), wherein the first engagement section (42A) and the second engagement section (42B) form an engagement unit (40), or two first engagement sections (42A) form an engagement unit (40) and two second engagement sections (42B) form a further engagement unit (40), wherein the pressure piece (2) has at least two locking units (20) which are spaced apart from each other, wherein the plate (4) has at least two engagement units (40) which are spaced apart from each other.

13. Disc brake (1 ) according to claim 12, wherein one of the locking units (20) is designed with a different geometry and / or orientation with respect to the holding axis (H) than the other locking unit (20), and wherein one of the engagement units (40) is designed with a different geometry and / or orientation with respect to the holding axis (H) than the other engagement unit (40).

14. Disc brake (1 ) according to claim 12, wherein the locking units (20) are designed and aligned symmetrically to a plane orthogonal to the holding axis (H), and wherein the engagement units (40) are designed and aligned symmetrically to the plane orthogonal to the holding axis (H).

15. Disc brake (1) according to one of the preceding claims, wherein the disc brake is a single-piston disc brake, wherein the pressure piece (2) preferably has a central cylinder section (26) on the side opposite the contact surface (24), which is designed to actively participate in the positioning of the pressure piece (2) along the force axis (K).

16. Disc brake (1) according to one of the preceding claims, wherein a preloading element (6), in particular on the plate (4), is provided which preloads the plate (4), in particular perpendicular and / or transverse to the force direction (K), against a brake carrier (9), preferably such that one of the edges (43, 44) of the plate (4) abuts a retaining horn of the brake carrier (9), wherein the preloading element (6) establishes a preload force between a caliper (3) and the plate (4), which acts along a force vector (F), wherein the force vector (F) has a directional component parallel to the first locking direction (A) and a directional component parallel to the second locking direction (B), such that 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).

17. Disc brake according to one of the preceding claims, wherein at least one of the locking units (20) is completely surrounded in a section plane orthogonal to the force axis (K) by the contact surface (24) or by a plurality of contact surfaces (24), wherein preferably the cross-sectional area of ​​the locking unit (20), in particular of the projection (V) formed on the pressure piece (4), is in a ratio of 0.05 to 0.3, preferably 0.1 to 0.2 to the contact surface (24).

18. Use of a brake pad (46) and / or a plate (4) in a disc brake (1) according to any one of claims 1-17, wherein the brake pad (46) is in particular fixed to the plate (4), and / or Use of a brake pad unit (48) in a disc brake (1) according to one of claims 1 - 17.

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

20. Plate (4), in particular for use in a disc brake (1), wherein the plate (4) is preferably part of a brake pad unit (48) of the disc brake (1), wherein a first engagement section (42A) is formed on the plate (4), which is preferably formed on a recess (R), wherein a second engagement section (42B) is formed spaced apart from the first engagement section (42A), wherein the first engagement section (42A) is formed and aligned along or parallel to a first locking direction (A) for supporting a pressure piece (2) on the plate (4), wherein the second engagement section (42B) is formed and aligned along or parallel to a second locking direction (B) for supporting the pressure piece (2) on the plate (4), and wherein the first locking direction (A) is inclined to the second locking direction (B).

21. Plate (4) according to claim 20, wherein the first engagement section (42A) and / or the second engagement section (42B) is formed on a recess (R) on the plate (4), wherein the recess (R) has a depth (T) measured parallel to the force axis (K). exhibits a thickness (D) of the plate (4) which is 0.5 to 0.95 times, preferably 0.6 to 0.8 times, the thickness (D) of the plate (4) measured parallel to the force axis (K).

22. Plate (4) according to one of claims 20 - 21, wherein at least one of the engagement sections (42A, 42B) has a substantially flat or planar contact surface.

23. Plate (4) according to one of claims 20 - 22, wherein the first engagement section (42A) and the second engagement section (42B) form an engagement unit (40), or two first engagement sections (42A) form an engagement unit (40) and two second engagement sections (42B) form a further engagement unit (40), wherein the plate (4) has at least two engagement units (40) which are spaced apart from each other.

24. Plate (4) according to claim 23, wherein the plate (4) has a first rim (43) and a second rim (44) distal to the first rim (43), wherein a retention axis (H) extends substantially perpendicular to the first and second rims (43, 44), wherein the plate (4) has two engagement units (40), wherein two first engagement sections (42A) are formed on one of the engagement units (40) and two second engagement sections (42B) are formed on the second of the engagement units (40), wherein the first engagement sections (42A) are each oriented to the retention axis (H) such that the first locking direction (A) forms a first angle (a) with the retention axis (H) and the second engagement sections (42B) are each oriented to the retention axis (H) such that the second locking direction (B) forms a second angle (β) with the retention axis (H), wherein the first and the second angle (a, ß) are greater than 0° and less than 90°.

25. Plate (4) according to claim 24, wherein the first securing direction (A) includes the first angle (a) with the holding axis (H), which is preferably greater than 5°, and wherein the second securing direction (B) includes the second angle (ß) with the holding axis (H), which is different from the first angle (a).

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