Brake for slowing the relative movement of two parts towards each other

Abstract

Brake (1) for braking the relative movement of two parts (3, 6) to each other, wherein in particular the first part (3) is a flap, such as a door of a motor vehicle, and the second part (6) is a chassis part, such as a pillar of a motor vehicle, to which the flap is hinged, comprising the brake (1): - a support section (10, 11) for supporting the brake (1) on the first part (3) and - a braking device (15) for braking a brake rod (4) connected to the second part (6) with a braking force (8), characterized in that the braking device (15) is supported on the support section (10, 11) by means of an intermediate measuring section (12, 13) in any case in the direction of the braking force (8) and the measuring section (12, 13) points substantially in a direction orthogonal to the direction of the braking force (8), so that the measuring section (12, 13) experiences a bending in the direction of the braking force (8) due to a braking-induced support of the braking device (15) relative to the support section (10, 11) and wherein a sensor (16) is provided for measuring the bending of the measuring section (12, 13) in the direction of the braking force (8).

Description

[0001] The invention relates to a brake for braking the relative movement of two parts to each other with the features of the preamble of claim 1. Furthermore, the invention relates to a corresponding arrangement and a corresponding system.

[0002] Brakes are used to slow down the relative movement of two parts moving relative to each other. Maximum slowing down is the releasable holding of the two parts in a specific relative position, which is why, in this context, stopping the movement of the two parts relative to each other is also subsumed under the term braking.

[0003] For braking, the brake, which is supported relative to a first part, has a braking device. The braking device acts on a brake rod connected to the second part. The brake rod is connected to the second part in such a way that when the second part moves relative to the first part, the brake rod is also moved relative to the braking device. If the brake rod is braked by the braking device, the movement of the second part relative to the first part is also braked.

[0004] The brake has a support section for supporting or connecting the brake to or against the first part. This section transmits the braking force exerted by the braking device to decelerate the movement of the two parts relative to each other, which essentially points in the direction in which the brake rod is moved toward the brake, to the first part.

[0005] Such a brake, which brakes a brake rod, is used, for example, in motor vehicle flaps, such as the doors (door flaps), the engine compartment lid, or the tailgate that closes the trunk. Such a brake is described, for example, in EP 3 266 968 B1.

[0006] In some applications, it is necessary to know the magnitude of the braking force applied to the brake rod. This is the case, for example, in the following scenario: A door is hinged to the pillar of a motor vehicle by means of a joint. A brake supported on the door slows the pivoting movement of the door relative to the pillar by braking a brake rod connected to the pillar and arranged eccentrically to the joint. The brake also serves to hold the door in a specific pivoting position.

[0007] To close a door held in a specific pivot position by the brake, the user presses on the door as usual. The resulting increase in force on the brake / braked brake rod assembly up to a predetermined release force should release the brake mechanism and allow the brake rod to move relative to the brake, allowing the user to pivot the door.

[0008] Other uses of a braking force signal are of course conceivable.

[0009] One proposal for measuring braking force is disclosed, for example, in EP 3 492 679 A1. It is assumed that two webs connecting two housing parts are compressed or stretched as a result of the applied force. This compression or stretching is measured using strain gauges.

[0010] Another method for measuring force is disclosed in WO 2018 / 087000 A1. Here, a load cell is used to measure the compressive force acting on the first part through the housing of the braking device.

[0011] A disadvantage of these designs is that they fail to take into account the fact that, due to the multitude of applications, different usage scenarios, position of the braking device relative to the brake rod, position of the two parts relative to each other, etc., the braking force applied by the brake, or rather the braking device, varies not only in its amplitude but also in its direction. For example, bending moments, torsional moments, and transverse forces can also act on the housing of the braking device, which can sometimes have a greater influence on the deformation of the housing or a load cell than the force resulting from user interaction with at least one of the two parts. A meaningful measurement of the tensile and compressive forces is difficult to achieve with the current state of the art.

[0012] Against this background, the invention aims to propose a brake that improves and simplifies the measurement of braking force. Furthermore, the invention aims to provide an arrangement of a brake and a brake rod, as well as a system comprising a first part and a second part, the relative movement of which is to be braked.

[0013] The first-mentioned object is achieved by a brake having the features of claim 1, the arrangement-related object by an arrangement according to claim 12, and the system-related claim by means of a system having the features of claim 14.

[0014] Advantageous embodiments emerge from the dependent claims and the description.

[0015] According to the invention, the braking device is supported on the support section, at least in the direction of the braking force, with a measuring section interposed. Thus, the supporting force is transmitted between the braking device and the support section via the measuring section. The measuring section is inserted between the braking device and the support section in the direction of the braking force; the support section is connected to one end of the measuring section, and the braking device is connected to the other end of the measuring section.

[0016] The measuring section essentially points in a direction orthogonal to the braking force direction. "Essentially" in the context of this formulation means that the measuring section is so perpendicular to the braking force direction that the measuring section is bent by the influence of the braking force direction, and this bending is measurable. The bending deformation of the measuring section is greatest when the measuring section is orthogonal to the braking force direction, which is why this is preferred. It is understood that for the bending deformation of the measuring section, it is freely bendable in its bending section and is therefore not supported on other elements in its bending section, for example by contacting them.

[0017] A sensor is attached to the measuring section, which measures the bending of the measuring section in the direction of the braking force. Such a sensor can measure the surface deformation of the measuring section and is designed, for example, as a strain gauge. Other sensors are also conceivable, such as one that measures the offset of the measuring section, whether absolute or relative, for example, relative to the support section, due to the bending.

[0018] In the measuring section, the braking force directed towards the brake rod in the direction of movement of the braking device is converted into a bending moment. This utilizes the elastic, i.e. fully reversible, deformation of the measuring section due to bending. Due to the material properties of the measuring section, this deformation is preferably linear to the bending force. The bending moment causes a much greater deformation in the material than a tensile / compressive force, so that it can be more easily detected by measuring sensors. This allows a signal yield up to ten times stronger than with a conventional tensile / compressive force measurement. Furthermore, any bending influences on the measuring object do not disproportionately distort the measurement compared to a pure tensile / compressive force measurement, thus reducing measurement errors.

[0019] By providing the measuring section as a separate section between the braking device and the support section, a clear interface is created between the braking device and the support section. Typically, the measuring section is located directly between a brake device housing associated with the braking device, which transmits the braking force of the braking device, and the support section. Furthermore, it is typically provided that the braking device is supported relative to one or more support sections only via one or more measuring sections, so that the entire support of the brake relative to the first part is measured by one or more sensors.

[0020] To focus the bending on the measuring section and thus increase the measurement signal, it is preferred that the support section be designed to be stiffer with respect to the direction of the braking force than the measuring section. This can be achieved, for example, by connecting the support section flatly to the first part. Another option is to reinforce the support section with regard to material thickness, material selection, or geometric reinforcements, such as ribs or beads.

[0021] It can also be provided that the measuring section is tapered compared to the material adjacent to the measuring section. This means that the measuring section has a smaller cross-section in this tapered area, and therefore a reduced width. The tapering is usually carried out transversely to the direction of extension of the measuring section and transversely to the direction of braking force, i.e. in the width direction of the measuring section. The material adjacent to the tapered area leads to the braking device or the support section. In the tapered area, the measuring section is weakened so that a bending moment leads to a particularly strong surface strain of the measuring section, which can be measured more effectively.

[0022] Typically, the measuring section is designed to be significantly narrower in the direction of the braking force than in the two orthogonal directions. The measuring section is thus designed like a sheet metal plate; a material thickness of approximately 2 to 5 mm is preferred, while the width of the measuring section is approximately 20 to 50 mm. This results in an essentially uniaxial deformation of the measuring section under the action of the braking force, which simplifies the evaluation.

[0023] It is preferably provided that the measurement of the bending in the measuring section is provided in the region of the end facing the braking device.

[0024] A sensor, positioned perhaps on the measuring section, measures in this area. Starting from the braking device, the force is applied directly to the measuring section, so the greatest bending stress is expected here.

[0025] In this embodiment, it is particularly preferred if the measuring section, with its tapered area, is directly connected to a solid extension of the braking device, typically the braking device housing, pointing in the direction of the braking force. The braking force is introduced from the solid extension into the weakened, tapered area. Due to the sudden material thinning caused by the tapering and the reduction in thickness in the direction of the braking force, the bending stress in the material is focused in this area.

[0026] If at least one strain gauge is provided as a sensor for measuring the bending of the measuring section in the braking force measurement, it can be provided, in particular, that a pair of strain gauges is arranged in the measuring area, with the two strain gauges forming the pair being aligned orthogonally to each other. In this way, temperature compensation can be enabled by forming a reference value for the resistance, as well as compensation for any torsional stress in the material. Typically, the two strain gauges are arranged in a grid.

[0027] An evaluation module is typically connected to the sensor, which is designed to determine the braking force based on the bending of the measuring section. This evaluation module is preferably located in the brake, usually close to the measuring section. The evaluation module does not have to output an absolute value of the braking force; in many cases, it is sufficient to perform a relative measurement. Furthermore, the braking force does not necessarily have to be specified in a force-specific unit (such as Newtons); it is sufficient to use a unit proportional to the braking force or a coded signal. By locating the evaluation module in the brake, the signal can be evaluated close to the sensor, which leads to lower measurement uncertainties.

[0028] The brake rod is held on the brake in a braking plane on the braking device. With respect to this braking plane, it is preferably provided that the support section is connected to the measuring section at the end facing away from the braking plane, and the braking device is connected to the measuring section at the end facing the braking plane. Thus, the introduction of the force from the braking device is close to the brake rod, so that the force transmission from the braking device to the measuring section runs approximately parallel to the braking plane. This further focuses the braking force on the measuring section.

[0029] In a preferred embodiment in this regard, the support section extends from the end of the measuring section facing away from the braking plane toward the braking plane. The measuring section and the support section, when viewed together, then form a U-shape in a side view. The measuring section and the support section can be aligned essentially parallel in their direction of extension. A curve is preferably provided at the transition from the measuring section to the support section; this curve can have a radius of 1 mm to 2.5 mm.

[0030] To prevent deformation of the measuring section relative to the support section, this design provides a gap between the support section and the measuring section in the direction of the braking force, particularly in the area where the braking device applies the supporting force to the measuring section. This prevents the measuring section from additionally supporting itself against the support section as a result of deformation. A gap is also provided between the braking device housing and the measuring section.

[0031] In order to provide a solid counter bearing for the end of the measuring section facing away from the braking plane, it can be provided that the web connecting the two legs - the measuring section and the support section - is designed as a material accumulation which corresponds approximately to twice, preferably three times the material thickness of the measuring section in the braking force direction.

[0032] It can be provided that the measuring section, the support section, and the brake device housing are formed as a single piece, together forming a measuring segment. This single-piece measuring segment enables a more continuous force flow from the brake device to the measuring section and the support section. This does not preclude the support section from having additional elements to support the brake. Such a single-piece measuring segment can be manufactured, for example, using a die-casting or injection-molding process.

[0033] In a further embodiment, it can be provided that the brake has at least two separate support sections and that the braking device is supported relative to the support sections by means of a measuring section leading to a respective support section. Thus, two sets each consisting of a support section and a measuring section are provided, with the two measuring sections being connected to the braking device, usually the braking device housing. By distributing the supporting force between two support sections, the individual support sections and also the individual measuring sections are each relieved of load. Preferably, the measuring sections are arranged opposite one another with regard to the direction of the braking force. This means that the two measuring sections protrude from the braking plane in opposite directions.

[0034] Both measuring sections can independently exhibit all the features mentioned above and below, also in the respective combinations.

[0035] Preferably, however, the measuring sections are designed symmetrically with respect to the braking plane, at least in their intended bending direction. This prevents the individual measuring sections from inducing torsional moments in each other during a supporting process. A symmetrical design of the measuring sections ensures that the two measuring sections are bent around mutually parallel axes by a braking force applied by the braking device.

[0036] It was found that it is sufficient to measure the bending of only one measuring section, thus using only one sensor. However, it is possible to measure the bending of both measuring sections.

[0037] It is further preferably provided that the braking device is supported relative to one or more support sections only via one or more measuring sections. The deflection of each measuring section due to the braking force is measured. This enables a comprehensive measurement evaluation and prevents the braking device from being supported on the first part via parallel, unmeasured force paths.

[0038] The braking device preferably acts on the brake rod with friction elements. This means that the braking device is designed so that one or more friction elements are pressed onto the brake rod with a contact force for braking, so that the movement between the braking device and the brake rod is reduced by friction. Once the brake rod has come to a stop relative to the braking device, a frictional connection is established between the braking device and the brake rod.

[0039] However, other braking mechanisms can also be used. In particular, it is conceivable to use a drive as the braking device that can also actively move the brake rod. In non-driving mode, such a drive holds the brake rod in a specific position and thus slows its relative movement to the braking device, at least through friction in the drive system.

[0040] To securely support the brake on the first part, the brake preferably has at least two spaced-apart fastening elements with which the brake is attached to the first part. The fastening elements are provided on one or distributed across at least two support sections. Such fastening elements can be nuts or screw bolts, for example; the latter, in particular, projecting from the support section. If a screw connection is used, fastening is usually carried out such that the screw bolts point in the direction of the braking force.

[0041] In a related development - which is also conceivable independently of any measurement of the braking force - it is provided that the two spaced-apart fastening elements are designed such that the distance between the two fastening elements is variable. This allows one and the same brake to be connected to different connection mimics of a first part. If, for example, different first parts are present which require a different distance between the fastening elements for connecting the brake, this requirement can be met with the same brake. By creating an interface between the fastening and the brake by variably adjusting the distance between the fastening elements, significantly more identical parts can be used, so that the brake as a whole can be manufactured cost-effectively even for first parts in smaller quantities.

[0042] To create a variable spacing configuration, a recess pointing in the variable direction is provided in at least one support section. The variable direction is the direction in which the spacing is to be variable. A complementary insert is inserted into this recess, which has a fastening element or cooperates with such a element and holds it in a predetermined position. To change the spacing, the insert is replaced or repositioned on the support section so that the fastening element is arranged at a different location in the variable direction. By providing a recess in the variable direction, the fastening element can be freely positioned along this recess with the aid of the insert.

[0043] The insert may include a fastener receptacle to hold the fastener, such as a screw or nut, in the intended position.

[0044] Preferably, the measuring section is made of a metallic material, such as a steel or aluminum alloy, although it may also be completely or partially coated with a plastic layer, such as overmolded. A metallic material has a wide linear deformation range and is sufficiently stable and fatigue-resistant, so it can be effectively used to utilize elastic deformation during the bending process.

[0045] The invention further relates to an arrangement of a brake as described above and a brake rod inserted into the brake. The brake rod can be braked by the braking device. Furthermore, the brake rod is designed to be connected to the second part.

[0046] With regard to this arrangement, it can be provided that the brake rod has an end stop, such as a hammer head, on the side opposite the support section, with which the brake rod is positively supported against the brake in an end position. Then, on the brake side, it can be provided that an opening is provided on the brake that is aligned with the end stop and leads from the support section to the opposite side, into which opening a pin-like support bolt is inserted. If the end stop hits the pin, the force is not guided into the support section via the measuring section, but directly via the pin-like support bolt into the support section. This effectively relieves the load on the measuring section in the event of an end stop.

[0047] Described below is a system of a previously described arrangement of brake and brake rod as well as a first part and a second part to be braked relative to the first part, wherein the brake is connected to the first part and the brake rod is connected to the second part.

[0048] In this case, it is preferably provided that the brake is mounted on the first part such that, in the system's operating position, the measuring section of the brake faces substantially in the direction of gravity, thus the braking plane is horizontal. The weight of the brake itself thus does not lead to torsional bending of the measuring section and thus does not lead to additional measurement errors; these loads act on the measuring section in the same axis as the braking force. This improves the measurement quality.

[0049] The invention is explained in more detail using two exemplary embodiments in the accompanying figures. They show: Fig. 1: A sketch of an installation situation of the brake according to the invention in a plan view, Fig. 2: a three-dimensional detailed view of the arrangement according to the invention, comprising a brake according to the invention and a brake rod, Fig. 3: an excerpt from Fig. 2, with the fasteners and inserts shown exploded, Fig. 4: a sectioned side view according to the arrangement of Fig. 2 with hidden fastening elements, Fig. 5: a three-dimensional view of the measuring segment and Fig. 6: an inventive development of the previously described brake.

[0050] Fig. 1 shows a system comprising a brake 1, shown only schematically, which is connected via fastening elements 2a, 2b (in the Fig. In the top view shown in Figure 1, only one fastening element 2a is visible) connected to a schematically illustrated first part 3, here a door of a motor vehicle, and to a brake rod 4 complementary to the brake 1, which is guided through the brake 1 and connected by means of a joint part 5 to a schematically illustrated second part 6, here a pillar of a motor vehicle. The first part 3 and the second part 6 are connected to one another via a schematically illustrated joint 7 and can be pivoted about this joint. The task of the brake 1 is to brake the relative movement between the first part 3 and the second part 6 or to hold the two parts 3, 6 in a specific relative position to one another. For this purpose, the brake 1 acts on the brake rod 4. By braking the brake 1 against the brake rod 4, a braking force 8 acts on the brake 1 – the same applies analogously to the brake rod 4.The direction of the braking force 8 is parallel to the plane of the paper.

[0051] With reference to the Fig. 2 to 5, the brake 1 is explained in more detail below. The braking device 15 is only partially shown in the figures; further details on the brake actuator system are omitted for clarity.

[0052] The brake 1 comprises a braking device 15, not shown in detail here, with two friction bodies 14a, 14b (see sectioned side view in Fig. 4), which are enclosed in a braking device housing 9 and supported thereon in the braking force direction 8, two support sections 10, 11 and measuring sections 12, 13 assigned to the respective support sections 10, 11. The two support sections 10, 11 and the two measuring sections 12, 13 are each constructed identically, so that in the following explanations the respective sections are only addressed in the singular; however, the explanations apply analogously to both corresponding sections.

[0053] The brake rod 4 is inserted into the brake 1 so that the braking device 15, or rather the friction bodies 14a, 14b arranged in the braking device housing 9, can act on it. If the braking device 15 acts on the brake rod 4 by at least one friction body 14a being pressed onto the brake rod 4 with a contact force pointing in the direction orthogonal to the longitudinal extent of the brake rod 4, this results in a braking force 8 which is opposite to the relative movement of the brake rod 4 to the brake 1 and is subject to the laws of friction. This braking force 8 must be transmitted to the brake 1 from the braking device 15 via its braking device housing 9 to the Fig. 2 to 5. The force is transmitted to the first part 3 via the support sections 10, 11, which in turn have fastening elements 2a, 2b, here screw bolts, that engage in the first part 3. A measuring section 12, 13 is inserted between the two support sections 10, 11 and the braking device 15. The measuring section 12, 13 extends orthogonally to the braking force 8, here orthogonally to the brake rod 4, or its intended direction of movement.

[0054] When the braking force 8 originating from the braking device 15 or the braking device housing 9 acts on the measuring section 12, 13, the measuring section 12, 13 is elastically deformed, or bent in the direction of the braking force 8. This bending is measured with a sensor 16, in this case a strain gauge. A special feature is that in this exemplary embodiment, only one of the two measuring sections 13 has a strain gauge as the sensor 16.

[0055] To concentrate the braking force on the measuring section 12, 13 and the resulting bending, the measuring section 12, 13 is as in Fig. 5, is waisted, thus bone-shaped compared to the adjacent material, namely the braking device 15, or the braking device housing 9 and the support section 10, 11. In addition, the measuring section 12, 13 is sheet-like in its material thickness, here with approximately 3 mm.

[0056] The braking device 15 adjoins the end of the measuring section 12, 13 that points toward the braking plane formed by the brake rod 4; the end of the measuring section 12, 13 pointing away from the braking plane and thus from the brake rod 4 adjoins the support section 10, 11. In this exemplary embodiment, the sensor 16 is arranged in the region of the measuring section 13 that lies toward the end of the measuring section 13 pointing toward the braking plane, thus toward the brake rod 4.

[0057] The support section 10, 11 extends from the end of the measuring section 12, 13 facing away from the braking plane, and thus from the brake rod 4, back to the braking plane, and thus to the brake rod 4. The measuring section 12, 13 and the support section 10, 11 thus together form a U-shape. A gap 17, 18 is left between the two legs—the measuring section 12, 13 on the one hand and the support section 10, 11 on the other—so that the measuring section 12, 13 can be freely bent relative to the support section 10, 11.

[0058] In the present case, the support section 10, 11, the measuring section 12, 13 and the braking device housing 9 are formed in one piece as a measuring segment from a die-cast aluminum housing.

[0059] The present brake 1 has two support sections 10, 11 and two associated measuring sections 12, 13. There is no further support compared to the first part 3, so that the entire braking force 8 is passed through the measuring sections 12, 13 and can thus be evaluated.

[0060] The brake 1 is connected to the first part 3 via the two fastening sections 2a, 2b.

[0061] It may well happen that the distance between the complementary fastening elements on the side of the first part 3 differs between different first parts. In order to reduce the variety of variants, it is provided that the support sections 10, 11 have fastening elements 2a, 2b whose distance is variable. The corresponding functionality is explained in particular with reference to Fig. 3 is explained in more detail.

[0062] The support sections 10, 11 each have a recess 19, 20. Inserts 21, 22 can be inserted into these recesses 19, 20, which in turn support the fastening elements 2a, 2b. The recesses 19, 20 are designed here as elongated recesses in the vertical axis direction, i.e., the direction of gravity. If the distance between the two fastening elements 2a, 2b is to be changed, only different inserts 21, 22 need to be provided, for example, inserts in which the fastening elements 2a, 2b are positioned closer to the braking plane.

[0063] In this embodiment, the fastening elements 2a, 2b themselves are square screws, with the respective screw head engaging behind the support section 10, 11 in the recess 19, 20.

[0064] Fig. 6 shows a further development of the arrangement according to the invention of a brake 1 with a brake rod 4. For identical parts, the same reference numerals as above are used in the following explanations.

[0065] In this embodiment, the brake rod 4 has an end stop 23 which is designed in the manner of a hammer head. If the brake 1 is moved towards the end stop 23 (in Fig. 6 to the right) the brake 1 hits the end stop 23.

[0066] To protect the measuring section 12, 13, the brake 1 has openings 24, 25 aligned with the end stop 23, into each of which a pin-like support bolt 26, 27 is inserted. The support between the brake 1 and the end stop 23 is provided by the end face of the support bolt 26, 27. This bolt is supported at its other distal end on the support section 10, 11, so that in this case, the force transmission via the measuring section 12, 13 is bypassed for safety reasons. In normal operational use, the section bolt 26, 27 plays no role.

[0067] Otherwise, the brake 1 is designed as explained with regard to the first embodiment.

[0068] The invention has been described using exemplary embodiments. Without departing from the scope of protection described by the applicable claims, numerous further embodiments for implementing the inventive concept will become apparent to those skilled in the art without the need for further explanation within the scope of these statements. List of reference symbols 1 brake 2a, 2b Fastening element 3 first part 4 brake rod 5 Joint part 6 second part 7 joint 8 Braking force (direction) 9 Brake device housing 10, 11 Support section 12, 13 measuring section 14a, 14b friction body 15 Braking device 16 sensors 17, 18 gap 19, 20 recess 21, 22 deployment 23 End stop 24, 25 breakthrough 26, 27 Support bolts QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] EP 3 266 968 B1

[0005] EP 3 492 679 A1

[0009] WO 2018 / 087000 A1

[0010]

Claims

[1] Brake (1) for braking the relative movement of two parts (3, 6) to each other, wherein in particular the first part (3) is a flap, such as a door of a motor vehicle, and the second part (6) is a chassis part, such as a pillar of a motor vehicle, to which the flap is hinged, the brake (1) comprising: - a support section (10, 11) for supporting the brake (1) on the first part (3) and - a braking device (15) for braking a brake rod (4) connected to the second part (6) with a braking force (8), characterized byin that the braking device (15) is supported on the support section (10, 11) in any case in the braking force direction (8) with the interposition of a measuring section (12, 13), and the measuring section (12, 13) points substantially in a direction orthogonal to the braking force direction (8), so that the measuring section (12, 13) undergoes a bending pointing in the braking force direction (8) due to a braking-related support of the braking device (15) relative to the support section (10, 11), and wherein a sensor (16) is provided for measuring the bending of the measuring section (12, 13) pointing in the braking force direction (8). [2] Brake according to claim 1, characterized by that the measuring section (12, 13) is tapered in the width direction compared to the material adjacent to the measuring section (12, 13). [3] Brake according to claim 1 or 2, characterized bythat the measuring section (12, 13) is designed to be considerably narrower in the braking force direction (8) than in the two directions orthogonal thereto. [4] Brake according to one of claims 1 to 3, characterized by that the measurement of the bending in the measuring section (12, 13) is provided in the region of the end of the measuring section (12, 13) leading to the braking device (15). [5] Brake according to one of claims 1 to 4, characterized by that the sensor (16) for measuring the bending of the measuring section (12, 13) pointing in the braking force direction (8) is based on the measurement of the surface expansion or surface compression of the measuring section (12, 13) and is designed in particular as a strain gauge. [6] Brake according to one of claims 1 to 5, characterized bythat the brake rod (4) is held in a braking plane and that the support section (10, 11) is connected to the measuring section (12, 13) at the end pointing away from the braking plane and the braking device (15) is connected to the measuring section (12, 13) at the end pointing towards the braking plane. [7] Brake according to claim 6, characterized by that the support section (10, 11) extends from the end of the measuring section (12, 13) pointing away from the braking plane in the direction of the braking plane, so that the measuring section (12, 13) and the support section (10, 11) together form a U-shape. [8] Brake according to one of claims 1 to 7, characterized by that the measuring section (12, 13), the support section (10, 11) and a braking device housing (9) of the braking device (15) are formed in one piece as a measuring segment. [9] Brake according to one of claims 1 to 8, characterized byin that the brake (1) has at least two support sections (10, 11) which are separate from one another, and the braking device (15) is supported relative to the support sections (10, 11) by means of a measuring section (12, 13) which leads to a respective support section (10, 11), and in that the measuring sections (12, 13) are arranged opposite one another with respect to the braking force direction (8), wherein in particular only one of the two measuring sections (12, 13) has a sensor (16) for measuring the bending pointing in the braking force direction (8). [10] Brake according to one of claims 1 to 9, characterized by that the brake (1) has at least two fastening elements (2a, 2b) spaced apart from one another, with which the brake (1) can be fastened to the first part (3), wherein the distance between the fastening elements (2a, 2b) is designed to be variable. [11] Brake according to one of claims 1 to 10, characterized bythat in any case the measuring section (12, 13) is made of a metallic material, such as a steel or aluminum alloy. [12] Arrangement of a brake (1) according to one of claims 1 to 11 and a brake rod (4) guided in the brake (1), wherein the brake rod (4) is designed to be connected to the second part (6). [13] Arrangement according to claim 12, characterized byin that the brake rod (4) has an end stop (23), such as a hammer head, on the side opposite the support section (10, 11), with which the brake rod (4) is supported in a form-fitting manner against the brake (1), and in that an opening (24, 25) aligned with the end stop (23) is provided on the brake (1) from the support section (10, 11) to the opposite side, into which opening a pin-like support bolt (26, 27) is inserted, so that the end stop (23) can be supported on the support section (10, 11) without the interposition of the measuring section (12, 13). [14] System of a brake (1) and a brake rod (4) according to one of claims 12 or 13, as well as a first part (3) and a second part (6) to be braked relative to the first part (3), wherein the brake (1) is connected to the first part (3) and the brake rod (4) is connected to the second part (6). [15] System according to claim 14, characterized bythat the measuring section (12, 13) of the brake (1) in the installation situation points essentially in the direction of gravity.

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