Brake arrangement having a brake adjuster with a freewheel

Abstract

The invention relates to a brake arrangement having a brake adjuster (1) for automatically adjusting a brake (12), in particular a brake (12) having an inclined ball track, comprising: an input lever (2), the input lever (2) being configured to transmit a braking force for a brake cylinder (11); an output lever (3), the output lever (3) being configured to transmit the braking force to a brake (12); a brake clearance element (4) which is configured to set a clearance; a first freewheel (5) and a second freewheel (6), wherein the first freewheel (5) mechanically connects the input lever (2) to the output lever (3) in a first actuation direction and releases the same in a further, in particular opposite, actuation direction, and wherein the second freewheel (6) mechanically connects the brake clearance element (4) to the output lever (3) in the further actuation direction and releases the same in the first actuation direction.

Description

[0001] 119999P504PC 1 / 25 RENK GmbH

[0002] Description

[0003] Brake assembly with linkage divider with freewheel

[0004] The present invention relates to a brake arrangement with a linkage adjuster for the automated adjustment of a brake clearance.

[0005] Adjusting the brake clearance is an important process, particularly during maintenance and / or to ensure a defined clearance during operation of vehicles, especially motor vehicles. Brakes, and in particular brake pads, are wear parts that are a component of motor vehicles and guarantee safe driving. Adjusting the brake clearance serves to keep the brakes in a safe condition to regulate the vehicle's speed, especially to keep the brake cylinder stroke within specified limits. Adjustment is usually achieved via a gear mechanism, such as a worm gear or a thread.

[0006] The object of the present invention is to improve, in particular automatically, continuously variable and / or, in particular permanently, (at least substantially) constant, adjustment, and further in particular readjustment, of an air clearance.

[0007] This problem is solved by a linkage adjuster with the features of claim 1. The dependent claims relate to advantageous further developments.

[0008] According to one embodiment of the present invention, a linkage adjuster is provided. In one embodiment, the linkage adjuster has a drive lever, wherein the drive lever is configured to transmit a braking force to a brake cylinder, in particular to receive the braking force for transmission in the linkage adjuster. In one embodiment, the linkage adjuster has an output lever, wherein the output lever is configured to transmit a braking force to a brake, in particular a brake which has an inclined ball track, especially for actuation, and / or in particular a drum brake. In one embodiment, the linkage adjuster has a brake release element, which is configured in particular to adjust a brake clearance, in particular such that the clearance remains, at least substantially, constant, wherein the brake release element is in particular pre-tensioned.In one embodiment, the linkage adjuster has a first freewheel and a second freewheel. In one embodiment, the first freewheel is configured to mechanically connect the drive lever to the output lever in a first actuation direction, particularly in a freewheel manner, and to release it in a further, particularly opposite, actuation direction. In one embodiment, the second freewheel is configured to mechanically connect the brake release element to the output lever in a further, particularly opposite, actuation direction, particularly in a freewheel manner, and to release it in the first actuation direction.

[0009] The term "actuation direction," as used herein, is preferably to be understood as the actuation direction of the (respective) freewheel, in particular the first freewheel (where, in one embodiment, the "first actuation direction" specifies an axial / linear or a rotational direction, and the actuation direction of the second freewheel is or can be related to this), especially under the conditions that lead to the (respective) freewheel opening or closing, or, in particular, to a torque-transmitting mechanical connection or release. In one embodiment, the opening or closing includes a relative movement of the components on which the (respective) freewheel is arranged. Thus, the (respective) freewheel remains closed, for example, if a relative movement can be prevented, or is prevented, in particular by means of a spring element.In one version, the first freewheel and the second freewheel operate in opposite directions.

[0010] In one embodiment, the linkage adjuster is configured to transmit a braking force from a brake cylinder to a brake and, in particular, to maintain a brake clearance, at least substantially, constant or to compensate for brake wear, specifically such that the brake, in the unloaded state (119999P504PC 3 / 25 RENK GmbH), exhibits, at least substantially, the same clearance (after or with wear). Advantageously, in one embodiment, this allows the brake clearance to be automatically adjusted, particularly with the aid of the, at least substantially, backlash-free freewheels, and adjusted more precisely. Advantageously, in one embodiment, this enables the present linkage adjuster to be operated more precisely and / or more easily, particularly to maintain a clearance (or...Unwanted brake cooling, in particular brake cooling that exceeds a predetermined range), which occurs especially in linkage adjusters with threads, teeth or the like, is reduced or can be reduced, in particular by gear play / step of the teeth, etc.

[0011] In one embodiment, the first actuation direction is a first direction of rotation. In another embodiment, the subsequent actuation direction is a direction of rotation opposite to the first direction of rotation.

[0012] This allows, in one version, a more compact linkage adjuster to be advantageously realized.

[0013] In one embodiment, the first actuation direction is a first linear, in particular axial, direction. In another embodiment, the subsequent actuation direction is a direction opposite to the first linear direction, in particular an axial direction opposite to the first.

[0014] This allows, in one version, the use of freewheels or backstops (linear freewheels), and in particular the linkage adjuster can be implemented in a more compact design.

[0015] In one embodiment, the brake release element is mounted in the output lever. In another embodiment, the brake release element is mounted to rotate, in particular concentrically, with respect to / on the output lever and / or mounted in the output lever. In an alternative embodiment, particularly if the freewheel is a linear freewheel, the brake release element is mounted such that the brake release element is axially movable relative to the output lever or, in particular, is moved axially relative to the output lever when actuated, especially the brake, or in the axial direction of the output lever.

[0016] Advantageously, this design allows for a more compact linkage adjuster, requiring less installation space compared to manually operated linkage adjusters or those with threads or teeth. Furthermore, this design facilitates maintenance of the linkage adjuster, particularly compared to the conventional linkage adjusters described in the introduction.

[0017] In one version, the freewheel has a clamping piece freewheel or is designed as a clamping piece freewheel.

[0018] This can advantageously reduce play or unwanted brake cooling (further) in one embodiment, in particular allowing the freewheel to engage more directly or transmit torque, or to run more freely or not transmit torque, at least to a significant extent.

[0019] In one embodiment, the brake release element comprises at least one spring element, in particular a compression spring, a tension spring, a leaf spring, or the like. In one embodiment, the spring element is configured to support or pre-tension the brake release element against a housing of the linkage adjuster in the further actuation direction, in particular such that the brake release element can follow, or does follow, the output lever while or when the output lever passes through the brake release. In one embodiment, the spring element is configured in particular to provide a restoring force for the brake release element, in particular such that the second freewheel does not release, or cannot release, in the first actuation direction, in particular as long as or while the release clearance, which is provided in particular by the brake release element and / or is or can be specified by means of the brake release element, is not (yet) exhausted.This allows, advantageously, in one version, in particular with the aid of the brake ventilation element 119999P504PC 5 / 25 RENK GmbH, the brake ventilation to be adjusted or used for this purpose.

[0020] In one embodiment, the linkage adjuster has a stop, in particular an adjustable stop and / or a stop arranged on a housing, to limit the movement of the brake release element, especially in the first actuation direction and / or the subsequent actuation direction. In another embodiment, the linkage adjuster has a housing, wherein the housing, in particular (at least) one element of the housing or an arrangement of the housing, is configured, in particular additionally, to define brake release or a release clearance, in particular by means of the brake release element and / or the stop, in particular an adjustable stop. In another embodiment, the housing has two or more parts, which together form the housing. In another embodiment, the housing is designed such that a stop can be adjusted, in particular during the assembly of the linkage adjuster.

[0021] Advantageously, in one embodiment, this makes it possible for the linkage adjuster to be infinitely adjustable, in particular (also) by means of the freewheels which, compared to threads and / or gears, in particular have at least one adjustment travel which depends on the tooth spacing and / or on a transmission ratio, in particular in the case of a worm shaft to a worm wheel of a worm drive.

[0022] In one embodiment, the stop for the brake cooling element, which is particularly adjustable, has a pin. In another embodiment, the pin is configured to limit the movement, particularly the rotation, of the brake cooling element, so that the brake cooling or the cooling clearance can be adjusted, particularly limited.

[0023] Advantageously, this allows for easier adjustment of brake ventilation in one version. This allows, in one version, the 119999P504PC 6 / 25 RENK GmbH

[0024] Brake ventilation can be adjusted more easily. In one version, the linkage adjuster can be advantageously adapted more easily to other or different transmission types, particularly because of the adjustable stop.

[0025] In one embodiment, the linkage adjuster has a friction element and / or a throttle, particularly a hydraulic one, wherein the friction element and / or the throttle, particularly a hydraulic one, is / are configured to prevent any relative movement of the first and / or the second freewheel, particularly only the first freewheel, which would be unintentional. In one embodiment, the friction element and / or the throttle is configured to prevent any opening of the freewheel, particularly unintentional opening. In one embodiment, the friction element is formed and / or arranged between the drive lever and the output lever.

[0026] Advantageously, this allows the functionality of the linkage adjuster to be (further) improved in one design, in particular reducing and / or preventing faulty operation, especially faulty opening, of the freewheel(s).

[0027] According to one embodiment of the present invention, a brake assembly is provided. In one embodiment, the brake assembly comprises (at least) a linkage adjuster as described herein. In one embodiment, the brake assembly comprises a brake cylinder, wherein the brake cylinder is operatively connected to the drive lever of the linkage adjuster. In one embodiment, the brake cylinder (further) comprises a spring accumulator. In one embodiment, the brake assembly comprises a brake, in particular a disc brake, wherein the brake is operatively connected to the output lever of the linkage adjuster.

[0028] Advantageously, this allows for a more compact brake arrangement in one design, which automatically adjusts the brake venting, particularly without requiring manual adjustment. This allows for a longer maintenance interval in one design (119999P504PC 7 / 25 RENK GmbH). Furthermore, in one design, the brake arrangement enables more precise braking, especially more precise brake venting. It also allows for the automatic compensation of minor brake wear.

[0029] In one embodiment, the brake arrangement features a multi-disc brake, in particular a multi-disc brake as described below.

[0030] Advantageously, in one embodiment, particularly through a linkage adjuster described herein, a brake actuation path that is at least substantially constant can be achieved, especially for multi-disc brakes, and furthermore, especially for double-disc brakes. In one embodiment, this allows for an actuation range that is at least substantially unchanging, so that, in one embodiment, the design of the brake or brake arrangement can be simpler, and in particular, the design points of the brake or brake arrangement can be determined more precisely.

[0031] According to one embodiment of the present invention, a multi-disc brake, particularly for a superimposed steering gear, is provided. In one embodiment, the multi-disc brake has a clamping mechanism, wherein the clamping mechanism comprises a clamping element of a rotor, which can in particular (also) be referred to as a rotor clamping element or is a rotor clamping element, and a clamping element of a stator, which can in particular (also) be referred to as a stator clamping element or is a stator clamping element. In one embodiment, the multi-disc brake has an angular contact ball track configured to actuate the clamping mechanism, in particular axially with respect to a rotation of the rotor. In one embodiment, the multi-disc brake has, in particular, direct, liquid cooling of the clamping element of the stator or of the stator clamping element.In one embodiment, the multi-disc brake features cooling of the rotor, particularly indirect cooling, especially liquid cooling and / or air cooling. In another embodiment, the multi-disc brake features a double-disc brake or is designed as a double-disc brake. (See 119999P504PC 8 / 25 RENK GmbH.)

[0032] The design features the multi-disc brake, in particular the inclined ball track, and further in particular the (respective) ball track(s), of the inclined ball track mechanism having a split actuation and / or (each) a separately actuated actuation.

[0033] Advantageously, this allows for a more compact design in one version. In one version, this also advantageously enables more uniform wear and / or a more uniform distribution of braking force, and in particular, makes cooling easier to implement.

[0034] The term "direct liquid cooling," as used herein, preferably means that the liquid cooling acts directly on the stator clamping element and, in particular, does not cool via an intermediate heat transfer element or an intermediate volume. In one embodiment, the cooling system comprises a coolant, such as, in particular, a liquid or a liquid mixture, water, or a special refrigerant, which comes into contact, in particular directly, with the object or element to be cooled, especially the stator clamping element, and furthermore, in particular, without the need for an additional heat exchanger. In another embodiment, "direct cooling" means that the coolant does not flow around the brake, but rather allows it to run dry, furthermore, in particular, through the closed design of the direct cooling system (of the stator).

[0035] In one embodiment, the cooling system of the multi-disc brake is encapsulated, in particular such that a coolant is used, at least essentially, only for, and especially directly, cooling the stator(s) of the multi-disc brake. In another embodiment, the stator clamping element has at least one cooling channel.In one embodiment, the multi-disc brake has a coolant supply, in particular a plug-in tube, or in particular a flexible element for coolant supply, further in particular a hose-like element or a bellows supply, which is arranged on the clamping mechanism, wherein the coolant supply, in particular the plug-in tube, or in particular the flexible element for coolant supply, further in particular the hose-like element or the bellows supply, is configured to provide a fluid connection to at least one cooling channel of the clamping element of the stator. In one embodiment, the cooling channel has, in particular at least one, a cooling fin and / or, in particular at least one, a cooling rib.

[0036] The term "encapsulated," as used herein, is preferably to be understood as a (cooling) system, particularly a closed one, that protects or prevents a coolant within the system from contamination. In particular, "encapsulated" in one embodiment refers to the prevention of contamination, specifically that the encapsulated cooling system is designed to prevent the ingress of dirt and / or contaminants into the cooling system. In one embodiment, the encapsulated cooling system is not connected to a brake actuation, particularly a brake hydraulic system, and is furthermore, in particular, hydraulically separated from an actuation or actuation circuit of the multi-disc brake, particularly a dual-disc brake, and furthermore, in particular, independent or separate. The use of the term

[0037] The term "dual disc brake" is to be understood in particular without restriction to the general public.

[0038] The term "coolant supply," as used herein, is preferably to be understood as an element designed to establish a fluid connection, in particular a liquid-tight connection, especially between a liquid cooling system and an arrangement / device designed or configured to supply coolant to the multi-disc brake, in particular a dual-disc brake, and furthermore, is used specifically for this purpose. In one embodiment, the coolant supply has a seal for this purpose. In another embodiment, the coolant supply is designed to compensate for a clamping movement of the clamping element, in particular such that the fluid connection provided, in particular by the coolant supply, can be maintained. In another embodiment, the coolant supply is used to maintain the fluid connection.In one embodiment, the coolant supply, particularly with its axis, is arranged in the axial direction (particularly with respect to the multi-disc brake, especially a double-disc brake). In one embodiment, each clamping element of the stator or each stator clamping element of the multi-disc brake, especially a double-disc brake, has a coolant supply, in particular a plurality of 119999P504PC 10 / 25 RENK GmbH.

[0039] Coolant supply lines, which are arranged (in particular) circumferentially, and especially uniformly, distributed on the stator clamping element.

[0040] The term "plug-in tube," as used herein, is preferably to be understood as a tube-like element designed to establish a fluid connection, in particular a fluid-tight connection. In one embodiment, the plug-in tube has a seal for this purpose. In another embodiment, the plug-in tube is designed to compensate for a clamping movement of the clamping element, in particular such that the fluid connection provided, in particular by the plug-in tube, can be maintained or is maintained. In one embodiment, the plug-in tube is arranged, in particular with its axis, in the axial direction. In one embodiment, each clamping element of the stator or each stator clamping element of the multi-disc brake, in particular a double-disc brake, has a plug-in tube, in particular a plurality of plug-in tubes, which are arranged circumferentially, in particular uniformly, distributed on the stator clamping element.

[0041] Advantageously, this allows the multi-disc brake, especially the double-disc brake, to be cooled more easily in one design, and in particular makes it more efficient compared to a wet-running brake.

[0042] In one embodiment, the split or separately actuated actuator has a coupling element that realizes, or is configured for, a return to the (respective) actuator, particularly an independent return, and acts or can act in the axial direction of the multi-disc brake and / or in the circumferential direction, particularly in and / or against the direction of rotation of the multi-disc brake. In another embodiment, the actuator has a coupling element, in particular a beam-like (coupling) element, that couples, at least substantially, the at least two parts of the split actuator, which are configured, in particular, each to realize an actuation of one of the skewed ball tracks of the skewed ball track mechanism, in other embodiments, by means of a return element, which in particular has a spring element, further in particular at least one spring, or the like. 119999P504PC 11 / 25 RENK GmbH

[0043] In one embodiment, this advantageously allows for the implementation of an actuation mechanism that is particularly adapted to the operation, especially such that wear of the clamping mechanism can be adjusted using the split actuation or that the actuation can be used for this purpose. Advantageously, in one embodiment, the multi-disc brake can be reset, particularly after actuation, especially braking, using the coupling element.

[0044] In one embodiment, the skewed ball track is arranged centrally, particularly with respect to two stator clamping elements and two rotor clamping elements of the multi-disc brake, in particular a double-disc brake, , in particular, the skewed ball track, in one embodiment, is arranged in axial sequence between a first rotor clamping element and a first stator clamping element and a second stator clamping element and a second rotor clamping element, wherein the stator clamping elements each enclose the rotor clamping element, in particular with their, furthermore, directly, cooled working elements or adjustments.In one embodiment, the skewed ball track is arranged centrally, particularly with respect to two stator clamping elements and two rotor clamping elements of the multi-disc brake, in particular a double-disc brake. In one embodiment, the skewed ball track is arranged in axial sequence between a first rotor clamping element and a first stator clamping element, wherein the first stator clamping element in particular surrounds the first rotor clamping element, at least substantially, and a second stator clamping element and a second rotor clamping element, wherein the second stator clamping element in particular surrounds the second rotor clamping element, at least substantially.In one embodiment, the rotor clamping elements and the stator clamping elements are arranged, at least substantially, symmetrically to the clamping mechanism, in particular the skewed ball track is arranged centrally between the clamping elements, wherein in one embodiment a clamping mechanism is arranged on each side of the skewed ball track. In one embodiment, each coolant supply has its own, in particular separate, coolant supply. In one embodiment, a first coolant supply on a first axial side (with respect to a centrally arranged skewed ball track) has a first coolant supply, and a second coolant supply on a second axial side, which differs from the first axial side, has a second coolant supply. In one embodiment, the first coolant supply 119999P504PC 12 / 25 RENK GmbH and the second coolant supply have a common, in particular, coolant supply.In one embodiment, several coolant inlets are arranged, in particular evenly distributed around the circumference. In one embodiment, the multi-disc brake, in particular a double-disc brake, has one or more channels for supplying (fluid) to one or more coolant inlets. In one embodiment, each connecting tube has its own coolant supply. In one embodiment, a first connecting tube has a first coolant supply on a first axial side (with respect to a centrally arranged spherical track), and a second connecting tube has a second coolant supply on a second axial side that differs from the first axial side. In one embodiment, the first connecting tube and the second connecting tube have a common coolant supply. In one embodiment, several connecting tubes are arranged, in particular evenly distributed around the circumference.In one embodiment, the multi-disc brake, in particular the double-disc brake, has one or more channels for the (fluid) supply of one or more connecting tubes.

[0045] Advantageously, this design allows for a more even distribution of braking force across the clamping mechanisms, resulting in less wear and / or less maintenance, and enabling the transmission of a high or higher braking force, particularly for a longer period of time.

[0046] In one version, the multi-disc brake, in particular the double-disc brake, is designed as a parking and / or service brake.

[0047] This allows, in one embodiment, a more efficient parking brake function to be provided, particularly for heavy commercial vehicles that are stationary, or must remain stationary, for extended periods. Furthermore, in one embodiment, this enables more efficient and / or effective braking performance, especially at high speeds, without the multi-disc brake, particularly a dual-disc brake, overheating and / or becoming contaminated, particularly by contamination of the cooling system. 119999P504PC 13 / 25 RENK GmbH

[0048] In one embodiment, at least one of the clamping elements has a brake lining, in particular the clamping element of the rotor. In another embodiment, the clamping element of the rotor has (at least) a brake lining on each of the axial sides of the clamping element.

[0049] This advantageously allows for simpler maintenance, especially of the brake pads, and in particular maintenance of the multi-disc brake, especially the dual-disc brake, which requires little or no interaction with the cooling system, at least in essence.

[0050] Advantageously, the multi-disc brake described herein, in particular the double-disc brake, allows for longer maintenance periods, especially through a more even load on the brake pads, and in particular a more even wear of the brake pads.

[0051] In one embodiment, the inclined ball track is designed to be centrally controlled, in particular in such a way that the control of the inclined ball track acts, or can act, at least substantially, centrally between the stator clamping elements and the rotor clamping elements.

[0052] Advantageously, this makes it possible, in one embodiment, to operate the control more easily, in particular to distribute the effect of the actuation, especially evenly, to the rotor clamping elements.

[0053] In one embodiment, the inclined ball track has a split actuation mechanism that can actuate at least one ball track independently of another ball track of the inclined ball track or the inclined ball track mechanism, and is specifically designed or used for this purpose. In one embodiment, the inclined ball track has two or more tracks for balls, wherein the tracks can be actuated independently of, and in particular at least, one of the other tracks, or are designed for this purpose. In one embodiment, the multi-disc brake can have two tracks of an inclined ball track that can be actuated at least substantially independently of each other. In one embodiment, the multi-disc brake can have three or more tracks of an inclined ball track that can be actuated at least substantially independently of each other. 119999P504PC 14 / 25 RENK GmbH

[0054] The track features an inclined ball track. In one embodiment, one or more rotors can be arranged axially to the (respective) track, particularly on an axial side of the ball track, which can be braked, in particular by means of a (braking) actuation of the (respective) track. In one embodiment, two or more tracks (of an inclined ball track or an inclined ball track mechanism) can enclose one or more rotors, in particular such that the rotors, in particular the clamping elements of the rotors, are arranged between the two or more tracks. In one embodiment, one or more tracks (of the inclined ball track orof the skewed ball track mechanism) between the, in particular clamping elements of the, rotors, in particular such that the track and / or the tracks are surrounded symmetrically or asymmetrically (in axial direction) by, in particular clamping elements of the, rotors and / or are arranged symmetrically or asymmetrically between, in particular clamping elements of the, rotors.

[0055] Advantageously, this allows a braking force to be provided more easily in one embodiment, and in particular, braking can be more precise. Furthermore, it prevents, at least substantially, uneven wear of the brake, and in particular, brake wear can be made more uniform. In one embodiment, this advantageously allows braking to be applied more as needed.

[0056] In one embodiment, the multi-disc brake, in particular a double-disc brake, has a coupling element, in particular a spring assembly, which is designed in particular for resetting the multi-disc brake, in particular a double-disc brake, in particular for resetting the clamping mechanism.

[0057] Advantageously, this allows, in one design, the multi-disc brake, especially the double-disc brake, to be operated more reliably.

[0058] In one version, the clamping element, in particular the respective one, is formed, at least essentially, around the perimeter. 119999P504PC 15 / 25 RENK GmbH

[0059] In one embodiment, the clamping mechanism is arranged between the rotors and / or the multi-disc brake, in particular double-disc brake, is at least essentially symmetrical.

[0060] In one embodiment, the symmetrical design of the multi-disc brake, particularly a dual-disc brake, advantageously allows for a balanced distribution of braking force between the two discs, leading to improved braking performance and / or reduced wear. Furthermore, in another embodiment, the symmetry of the braking mechanism advantageously results in more consistent and / or predictable behavior, reducing the risk of unforeseen malfunctions, failures, or other disruptions, and improving the overall reliability of the multi-disc brake, particularly a dual-disc brake.

[0061] In one embodiment, the multi-disc brake, in particular a double-disc brake, comprises at least substantially a light metal. In particular, the multi-disc brake, in particular a double-disc brake, and / or a housing of the multi-disc brake, in particular a double-disc brake, is, in one embodiment, at least substantially made of, in particular at least, a light metal and / or manufacturable. In one embodiment, the housing has a passage, in particular a single- or multi-channel arrangement, which is configured to provide liquid cooling, in particular to provide liquid for cooling the stator clamping element or the clamping element of the stator. In one embodiment, the multi-disc brake, in particular a double-disc brake, and in particular the liquid cooling, are configured to be supplied with coolant from a gearbox.

[0062] In one embodiment, this can advantageously be achieved through the higher efficiency of the multi-disc brake described herein, in particular the double-disc brake, especially by the fact that a temperature can be maintained, at least substantially, below 600°C or below 500°C using the multi-disc brake described herein, in particular the double-disc brake, in one embodiment. This allows, in one embodiment, the multi-disc brake, in particular the double-disc brake, to be manufactured with reduced weight, in particular having a lower weight.

[0063] Further advantages and features will become apparent from the dependent claims and the exemplary embodiments. These are shown, in part schematically:

[0064] Fig. 1 : a linkage adjuster according to an embodiment of the present invention;

[0065] Fig. 2 A to G: the linkage adjuster of Fig. 1 in various positions with a schematic representation of the force flow; and

[0066] Fig. 3: shows schematically a brake arrangement according to one embodiment of the present invention.

[0067] In the figures, identical reference symbols denote identical, similar, or corresponding elements. Elements depicted in the figures are not necessarily shown to scale. Rather, the various elements depicted in the figures are represented in such a way that their function and general purpose are understandable to a person skilled in the art. Connections and couplings between functional units and elements shown in the figures can, unless expressly stated otherwise, also be implemented as indirect connections or couplings. Functional units can, in particular, be implemented as hardware, software, or a combination of hardware and software.

[0068] Fig. 1 schematically shows a linkage adjuster 1 in an embodiment described herein. The schematically shown linkage adjuster 1 has a drive lever 2 and an output lever 3, as well as a brake release element 4. The drive lever 2 is operatively connected to the output lever 3 via a freewheel, specifically in the direction of action of the freewheel, and is free in the opposite direction. Furthermore, the brake release element 4 is operatively connected to the output lever 3 via a second freewheel 5, specifically in the direction of action of the second freewheel 5, and is free in the opposite direction. The freewheels interact in such a way that brake release is automatically maintained or can be maintained at a constant level.

[0069] Figures 2A to 2G schematically show the actuation and adjustment of the brake release using the linkage adjuster 1 of Figure 1, particularly during the actuation and release of a brake 12. For better visibility of the force flow, hatching is omitted in Figures 2A to 2G. In particular, Figures 2A to 2G show the same features already described in Figure 1, so reference numerals are partially omitted. Figure 2A schematically shows a state in which the brake 12 is released or not actuated. The arrows indicate, in particular, a force flow in this position, specifically the force flow of the return force of the brake 12, which acts on the output lever 3, which acts via the second freewheel 5 on the brake release element 4, and further, in particular, on the spring element, which provides a counterforce.In the position shown, the second freewheel 5 is "actuated" in the further direction of actuation, so that the output lever 3 and the brake release element 4 are operatively connected via the second freewheel 5.

[0070] Fig. 2B schematically shows the closing of the brake 12. A braking force is received at the drive lever 2 and transmitted via the first freewheel 6, which establishes an effective connection between the drive lever 2 and the output lever 3 in the first actuation direction. Furthermore, the spring element holds the second freewheel 5 closed, so that, in particular, the brake release element 4 is or can be driven along with the output lever 3. The braking force that is thus transmitted to the brake 12, or can be transmitted, closes the brake 12.

[0071] Fig. 2C schematically shows a state in which the brake 12 is applied (not shown). The brake release element 4 has exhausted its release clearance or has traveled / overcome the distance provided for brake release, and has in particular reached a stop 7, which is in particular adjustable, 119999P504PC 18 / 25 RENK GmbH, which is or may be arranged in particular on a housing and / or which is provided by the housing.

[0072] Fig. 2D schematically shows a state in which the brake 12 is engaged, particularly with wear. Fig. 2D shows that the second freewheel 5 is no longer engaged, particularly because the brake release "path" is exhausted, and furthermore, in particular, the spring element, especially a compression spring, does not exert or cannot exert any "counter-pressure" on the freewheel, so that it opens, in particular, or releases the operative connection between the brake release element 4 and the output lever 3. The force flow acting for braking from the brake 12, in particular from the brake cylinder 11 (not shown), is further transmitted via the operative connection of the first freewheel 6 from the drive lever 2 to the output lever 3 and then to the brake 12 (not shown).

[0073] Fig. 2E schematically shows how the brake 12 reapplies, particularly during or at the end of a braking process. Specifically, the retraction of the brake 12, for example via (return) springs or the like, causes the output lever 3 to be "actuated" in the further direction of actuation, thereby engaging the second freewheel 5, thus establishing a operative connection to the brake release element 4. The brake release element 4 is thereby moved away from its stop 7, particularly with a counterforce from the spring element, especially a compression spring. Furthermore, the retraction of the brake 12 also acts on the drive lever 2 via the output lever 3, specifically by holding the first freewheel 6 in operative connection by means of a spring assembly of the brake cylinder 11.

[0074] Fig. 2F schematically shows a state in which the brake 12 is released and the wear from the (previously described) braking process has been reset. This is particularly evident from the position of the brake release element 4, which resets the brake release path and thus the release clearance. 119999P504PC 19 / 25 RENK GmbH

[0075] This means that the spring element, in particular the compression spring, is back in its initial position (see Fig. 2 A).

[0076] Fig. 2G shows a state in which the brake 12 is released and the spring brake is, or is being, retracted, at least substantially. This releases the first freewheel 6, so that, in particular, the drive lever 2 is moved further relative to the output lever 3 until the spring brake is, at least substantially, retracted. Accordingly, as indicated by the arrows, (only) a force is exerted or absorbed via the second freewheel 5. Thus, in one embodiment, it can be ensured that the clearance remains, at least substantially, constant when the brake 12 is re-actuated.

[0077] Fig. 3 schematically shows a brake arrangement 10 according to an embodiment described herein. The brake arrangement 10 has a linkage adjuster 1, as shown in particular in the figures described above or according to an embodiment described herein. Furthermore, the brake arrangement 10 has a brake cylinder 11, which in particular has a spring accumulator. A brake 12 is also shown, which is designed as a disc brake and is or can be actuated via the linkage adjuster 1. In one embodiment, the brake 12 can have a multi-disc brake, in particular a double-disc brake, which can be actuated in particular by means of an inclined ball track. A friction element, as described herein, can, in one embodiment, in particular be arranged between the drive lever and the driven lever (dashed outline).

[0078] In the present disclosure, "has an X" does not generally imply an exhaustive list, but is a short form of "has at least one X". 1 and also includes "has two or more X" as well as "has Y in addition to X". Although exemplary versions were explained in the preceding description, it should be noted that a large number of variations are possible. Furthermore, it should be noted that the exemplary versions are merely examples illustrating the 119999P504PC 20 / 25 RENK GmbH

[0079] The scope of protection is not intended to restrict applications and design in any way. Rather, the preceding description provides the skilled person with a guideline for implementing at least one exemplary embodiment, whereby various modifications, particularly with regard to the function and arrangement of the described components, can be made without leaving the scope of protection as defined by the claims and these equivalent combinations of features.

[0080] 119999P504PC 21 / 25 RENK GmbH

[0081] List of reference signs

[0082] I Linkage adjuster 2 Drive lever

[0083] 3 output levers

[0084] 4 Brake cooling element

[0085] 5 first free run

[0086] 6 second freewheel 7 stop

[0087] 10 Brake arrangement

[0088] II brake cylinder

[0089] 12 Brake

Claims

119999P504PC 22 / 25 RENK GmbH Patent claims 1. Brake arrangement (10) comprising a linkage divider (1) for automatic adjustment of a brake (12), wherein the linkage divider (1) comprises: - a drive lever (2), wherein the drive lever (2) is configured to transmit a braking force to a brake cylinder (11); a driven lever (3), wherein the driven lever (3) is configured to transmit the braking force to a brake (12); - a brake ventilation element (4) designed to adjust a ventilation clearance; - a first freewheel (5) and a second freewheel (6), wherein the first freewheel (5) mechanically connects the drive lever (2) to the output lever (3) in a first actuation direction and releases it in a further, in particular opposite, actuation direction; and wherein the second freewheel (6) mechanically connects the brake release element (4) to the output lever (3) in the further actuation direction and releases it in the first actuation direction; wherein the brake arrangement (10) comprises a brake cylinder (11), in particular a brake cylinder (11) comprising a spring accumulator, wherein the brake cylinder (11) is operatively connected to the drive lever (2) of the linkage divider (1) and / or wherein the brake arrangement (10) comprises a brake (12), in particular a disc brake, wherein the brake (12) is operatively connected to the output lever (3) of the linkage divider (1); and / or wherein the brake (12) comprises the brake assembly (10): - a clamping mechanism, wherein the clamping mechanism comprises a clamping element of a rotor and a clamping element of a stator; - an inclined ball track designed to actuate the clamping mechanism axially with respect to a rotation of the rotor; and - liquid cooling of the stator's clamping element.

2. Brake arrangement (10) according to the preceding claim, characterized in that the first actuation direction of the linkage adjuster (1) 119999P504PC 23 / 25 RENK GmbH is a first direction of rotation and the further direction of actuation is a direction of rotation opposite to the first direction of rotation.

3. Brake arrangement (10) according to one of the preceding claims, characterized in that the brake ventilation element (4) has at least one spring element.

4. Brake arrangement (10) according to one of the preceding claims, characterized in that the brake ventilation element (4) is mounted in the output lever (3).

5. Brake arrangement (10) according to one of the preceding claims, characterized by a stop (7), in particular adjustable and / or arranged on a housing, for limiting a movement of the brake release element (4), and / or characterized in that the linkage divider (1) has a housing, wherein the housing is configured to define a brake release, in particular by means of the brake release element (4).

6. Brake arrangement (10) according to the preceding claim, characterized in that the adjustable stop for the brake ventilation element (4) has a, in particular adjustable, pin which is configured to limit the movement, in particular a rotation, of the brake ventilation element (4).

7. Brake arrangement (10) according to one of the preceding claims, characterized in that the first freewheel (5) and / or the second freewheel (6) has a clamping freewheel and / or wherein the linkage divider (1) has a friction element, which is formed in particular between drive lever (2) and output lever (3).

8. Brake arrangement (10) according to one of the preceding claims, characterized in that the brake (12) has a multi-disc brake, 119999P504PC 24 / 25 RENK GmbH in particular a double disc brake which can be actuated using the inclined ball track.

9. Brake arrangement (10) according to one of the preceding claims, characterized in that the liquid cooling is encapsulated and / or that the clamping element of the stator has at least one cooling channel, and / or wherein the brake (12) has a coolant supply, in particular a plug-in tube, or in particular a flexible element, further in particular a hose-like element or a bellows supply, which is arranged on the clamping mechanism, wherein the coolant supply, in particular the plug-in tube, or in particular the flexible element, further in particular the hose-like element or the bellows supply, is configured to provide a fluid connection to the at least one cooling channel of the clamping element.

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