Brake cylinder for vehicle brake

Abstract

The invention relates to a brake cylinder for a vehicle brake, in particular for a commercial vehicle brake, comprising a spring device, the spring device (1) for generating a braking force and / or a restoring force for releasing the brake in the stroke direction (H) of the brake cylinder having at least a first section (2), wherein the first section (2) has a basic extent extending substantially on a first section plane, the normal of which is aligned substantially parallel to the travel direction (H) and / or deviates from the travel direction (H) by a maximum of 10, and wherein the first section (2) has, in particular alternately along its basic extent, a first sub-section (3) and a second sub-section (4), wherein, in the unloaded state, the first partial section (3) is spaced apart from the first section plane in the positive travel direction (H), and wherein, in the unloaded state, the second partial section (4) is spaced apart from the first section plane in the negative travel direction (H), wherein the first and second sub-sections (3, 4) are designed such that the distance from the first section plane is smaller in a loaded state when a spring force is generated than in an unloaded state.

Description

Technical Field

[0001] The invention relates to a brake cylinder for a vehicle brake, in particular a brake cylinder for a commercial vehicle brake, and to a vehicle brake having a brake cylinder. Background Art

[0002] The installation space for vehicle axles, in particular commercial vehicle axles and / or trailer axles, is often limited. Furthermore, it is advantageous if the spring center of the axle, i.e. in particular the distance between the connection points between the axle and the wheel suspension via the control arms or springs, can be designed to be as large as possible. This can, for example, achieve better rollover stability and / or greater steering angles in vehicles with steered axles. Furthermore, the steering angle can be directly dependent on the spring center, since adjacent components, such as control arms and brakes, can move towards each other during steering.

[0003] Here, it would be advantageous to reduce the number of components in order to be able to save costs, material and / or installation space.The component length of a brake cylinder, in particular a diaphragm or double diaphragm cylinder, is usually determined or influenced by its round wire spring and its spring travel. Summary of the invention

[0004] It is therefore an object of the present invention to provide a brake cylinder which reduces and / or can reduce the required installation space.

[0005] This object is achieved by a brake cylinder according to claim 1, a vehicle brake according to claim 9 and a use according to claim 10. Further advantages, features and advantageous embodiments of the invention are apparent from the dependent claims, the description and the drawings and their illustrations.

[0006] According to the invention, a brake cylinder for a vehicle brake, in particular for a commercial vehicle brake, is provided, which comprises a spring device, in particular a wave spring. Preferably, the spring device is designed to generate a braking force and / or a restoring force for releasing the brake in the stroke direction of the brake cylinder. Advantageously, the spring device surrounds the piston rod of the brake cylinder. In this way, installation space can be saved in particular. Although round wire springs (Runddrahtfedern) are usually used in the prior art to generate braking forces or restoring forces, it has been shown that wave springs (Wellenfeder) can shorten the brake drive stroke (Bremsbetätigungsweges) or cylinder stroke for generating braking forces, because wave springs require a shorter spring stroke (Federweg) and thus require less overall space to be able to generate the corresponding force. In particular, the wave spring can also be called a wave ring spring (Wellenringfeder). The wave spring can, for example, include a corrugated ring (gewellter Ring) made of sheet metal and / or flat wire. In the unloaded state, the corrugated ring may include antinodes or wave maxima and wave minima, wherein the antinodes are particularly designed to generate spring forces in the compressed state. Preferably, the spring force can be generated in the direction of movement or stroke; this direction can be particularly parallel to the extension direction of the piston rod or the piston rod of the brake cylinder. A plurality of corrugated rings can be arranged one after another in the stroke direction or the direction of movement, wherein the waves extend circumferentially around the direction of movement or the direction of stroke and / or perpendicular to the direction of movement or the direction of stroke. Advantageously, in particular in order to achieve a large spring stroke, the wave crests of the corrugated rings of the spring device respectively contact the troughs of the adjacent wave rings, which can also be basically referred to as corrugated rings. Commercial vehicles in the sense of the present invention are in particular vehicles with a permissible total weight of more than 3.5t, preferably more than 7.5t, particularly preferably more than 15t, and particularly preferably more than 18t. Commercial vehicles are in particular vehicles suitable for road travel and / or road vehicles. The commercial vehicle is advantageously a trailer, in particular a semitrailer. The brake cylinder can preferably be an air-driven, in particular compressed air-driven and / or air-driven, in particular compressed air-driven brake cylinder. For example, when used as part of a vehicle brake, the brake cylinder can be designed to be operated as a service brake by compressed air. Additionally or alternatively, when used as part of a vehicle brake, the brake cylinder can be designed to be activated as a parking brake by the spring force of a spring device. In other words, the spring device can be a functional component of the parking brake. The vehicle brake or the brake cylinder can, for example, be a diaphragm brake or brake cylinder, or a double diaphragm brake or brake cylinder. Additionally or alternatively, the vehicle brake can, for example, be a disc brake, a floating caliper brake and / or a drum brake.In the case of drum brakes, the installation space restrictions can also extend, for example, to the adjacent chassis, whereby the brake cylinder according to the invention can be particularly advantageous due to its space-saving properties. The brake cylinder can be designed so that the braking force can be offset by compressed air, for example, acting on the diaphragm of a diaphragm brake, so that the braking force caused by the spring device can be eliminated. In other words, the brake cylinder can be designed to put the spring device into a loaded state, in particular by compressed air, in which the spring device does not produce a braking effect. It can be provided that the spring device is permanently kept in a loaded state by compressed air during driving, so that no braking force is generated. Additionally or alternatively, the brake cylinder can be designed to generate a braking force in an unloaded state. The spring device can be designed to transmit the braking force to a brake mechanism, for example to a brake piston. The brake mechanism can be part of the brake cylinder in whole or in part. In particular, the braking force of the spring device can be generated by the spring force of the spring device.

[0007] Preferably, a brake cylinder for a vehicle brake, in particular for a commercial vehicle brake, is provided, comprising a spring device, wherein the spring device for generating a braking force in the stroke direction of the brake cylinder and / or for releasing a restoring force of the brake has at least a first section, wherein the first section has a basic extension extending substantially in a first section plane, wherein a normal to the first section plane is aligned substantially parallel to the stroke direction and / or deviates from the stroke direction by at most 10°, wherein the first section has a first subsection and a second subsection along its basic extension, in particular alternatingly, wherein in the unloaded state the first subsection is spaced apart from the first section plane in the positive stroke direction, and wherein in the unloaded state the second subsection is spaced apart from the first section plane in the negative stroke direction, wherein the first and second subsections are designed to be at a smaller distance from the first section plane in the loaded state when the spring force is generated than in the unloaded state. The brake cylinder is particularly preferably provided for a commercial vehicle brake or for a vehicle brake of a commercial vehicle. The spring device is in particular the spring device already described above. The spring force may correspond to the braking force. Advantageously, with a parking brake operated by a spring force, there is no risk of a reduction in the braking force in the event of a pressure drop when the vehicle is parked. The braking force of the spring device may be generated in particular by the spring force of the spring device. The braking force acts in particular in the stroke direction, in particular in the positive stroke direction. Alternatively or additionally, the spring device may be designed to release the brake. For example, it may be provided that the braking force, in particular the braking force of the service brake, is generated by compressed air or other mechanisms, and the task of the spring device is to generate a restoring force to release the brake. In particular, the restoring force may be designed to retract a push rod or a brake piston when the brake is not affected by compressed air, which push rod may also be referred to as or designed as a piston rod. The stroke direction may preferably be the direction in which the brake mechanism is driven, in particular the direction in which the brake piston moves when the brake is triggered and / or locked. A direction extending radially relative to the stroke direction is referred to as a radial direction in the context of the present invention. A direction extending circularly around the stroke direction of the brake cylinder or around the displacement axis, in particular around the central axis and / or perpendicular to the stroke direction and the radial direction is referred to as a circumferential direction. In particular, it can be provided that the brake mechanism can be moved in a positive stroke direction to trigger and / or lock the brake and can be moved in a negative stroke direction to release the brake. The first segment plane (or similarly one or more further segment planes) can be defined in particular by the fact that in the unloaded state, each of the first subsegment and the second subsegment is approximately at the same distance from the first segment plane. The distance between the first and second subsegments and the segment plane can refer to a maximum distance and / or an average distance. "Approximately" can mean a deviation tolerance of at most 15%, preferably at most 10% and particularly preferably at most 5% of the total distance.It can be provided that the sum of the average distances of the first sub-segment and the second sub-segment in the normal direction of the segment plane is approximately zero. The normal direction corresponds to the direction of the normal to the segment plane. The normal direction of the segment plane can be slightly inclined relative to the stroke direction, in particular up to 10°, preferably up to 5°. This advantageously allows for freedom in the design of the spring device, wherein the braking force can be unaffected or slightly affected. Preferably, the distance between the first segment and the second segment from the first segment plane is smaller in the loaded state than in the unloaded state. A smaller distance in the sense of the invention can also mean that there is no longer any distance. In other words, the brake cylinder can be designed so that in the loaded state, there is no distance or only a small distance between the first and second sub-segments and the first segment plane. The small distance can be a distance that is 50%, preferably 20%, particularly preferably 10%, and particularly preferably 5% smaller than the distance in the unloaded state. The brake cylinder and / or the spring device can be designed such that a spring force is generated by reducing the distance between the first subsection and the second subsection and the section plane, wherein the spring force is in particular a braking force and / or a braking force and / or generates a braking force / or a restoring force. The basic extension range does not necessarily have to extend along a straight line. In particular, the basic extension range can, for example, have a curved form. The basic extension range can correspond to the optionally curved longitudinal extension range of the first section. The arrangement of the first subsection and the second subsection can be arranged in a periodically changing manner. The first and second subsections can follow each other along the basic extension range, in particular follow each other alternately. As already explained, the spring device can in particular be a wave ring spring or a wave spring. It has been shown that with the brake cylinder according to the invention, installation space can be saved. This is made possible by the fact that the spring device according to the invention can lead to a shortened brake operating stroke or cylinder stroke for generating the braking force, because the spring device according to the invention requires less space than the round wire spring device usually used in the prior art. Advantageously, the length of the brake cylinder can be reduced in this way. In particular, a reduction of up to 50% in the extension of the component length in the stroke direction can be achieved compared to conventional round wire springs. If necessary, this value can be further increased, for example in the case of brakes with a plurality of mounted spring devices. It has been found that the stroke or spring stroke required for a brake cylinder used or used according to the prior art is often greater than the stroke or spring stroke required for the actual braking process on a part of the brake. By shortening the components of the brake cylinder, significant design advantages can be achieved for a more efficient vehicle design or construction, in particular in the area of ​​the vehicle axles. In addition, the brake cylinder according to the invention can have a reduced weight. In particular, the weight of the unsprung masses of the vehicle can thus be reduced.

[0008] According to one embodiment, the brake cylinder can have a fastening device for fastening to a vehicle brake. The fastening device can be designed, for example, to enable force-fitting and / or form-fitting and / or material-fitting fastening. The fastening device can, for example, comprise a bayonet lock and / or a clamp fastener. Advantageously, the fastening device can be used to facilitate the integration of the component into a brake, for example a disc brake. In addition, the fastening device can make it easier to retrofit the brake cylinder into an existing brake or brake system.

[0009] Advantageously, a first section of the spring device, in particular the entire spring device, is arranged circumferentially around an axis of movement of the brake cylinder, in particular around a central axis, which axis of movement is oriented substantially in the stroke direction. In particular, it can be provided that the basic extension of the first section is arranged in the circumferential direction. When viewed in the direction of the basic extension, the ends of the first section can be connected to each other and / or attached to each other. It can be provided that other sections of the spring device, in particular all sections of the spring device, are arranged circumferentially around an axis of movement of the brake cylinder, in particular around a central axis, which axis of movement is oriented substantially in the stroke direction. “Substantially in the stroke direction” can include design-related deviations from parallel alignment and / or deviations of up to 15°, preferably 10°, particularly preferably up to 5°. Preferably, the spring device can be aligned circularly around the axis of movement, in particular around the central axis. In particular, the center of the circle can lie substantially on the axis of movement. “Substantially” here can mean that the maximum distance of the center from the center is at most 15%, preferably at most 10%, particularly preferably at most 5% of the radius of the spring device. Advantageously, by the circumferential arrangement, in particular also by the arrangement perpendicular to the stroke direction or in the radial direction, a particularly effective optimization of the installation space can be achieved. In addition, a particularly uniform spring force can be generated in the stroke direction across the radial direction.

[0010] Advantageously, the first section comprises at least one intermediate section, which connects one of the first sub-sections with one of the second sub-sections, in particular elastically, and intersects with the first section plane. The at least one intermediate section can preferably be arranged between the corresponding first sub-section and the second sub-section, which are arranged adjacent to each other in the circumferential direction. Adjacent can in particular mean that no other first or second sub-section is arranged between two adjacent sub-sections, and / or no other sub-section is closer to the first or second sub-section than another sub-section of the two adjacent sub-sections. Advantageously, by making the two sub-sections move relative to each other in the stroke direction, the at least one intermediate section can be used to generate a particularly effective elastic spring force. The at least one intermediate section can be arranged centrally in the radial direction between the first sub-section and the second sub-section, and / or can be arranged outside the sub-section in the radial direction. Particularly preferably, the at least one intermediate section can be arranged between the two sub-sections in the circumferential direction. In particular, the first section may include a plurality of intermediate sections, each intermediate section connecting first and second subsections that are consecutive in the direction of the basic extension. The basic extension may particularly preferably extend in the circumferential direction. In particular, the first subsection and the second subsection may be arranged alternately in the circumferential direction, wherein the first subsection is connected to the second subsection that is located behind in the circumferential direction via the intermediate section, and vice versa. Advantageously, such an arrangement with intermediate sections makes it possible to obtain a particularly flat spring characteristic curve of the spring device. This applies in particular to brake cylinders, in particular to the parking brake part of the brake cylinder. In addition, the installation space can be reduced particularly effectively by such an arrangement.

[0011] Advantageously, the first section and / or one or more other sections of the spring device are designed essentially as a corrugated ring and / or an annular washer, wherein the antinodes of the corrugated ring and / or the annular washer correspond to the first and second subsections, wherein the ring and / or the annular washer are particularly arranged such that the center of the ring / annular washer is substantially arranged on the displacement axis of the brake cylinder oriented in the stroke direction, in particular on the central axis of the brake cylinder. Antinodes are particularly maxima and minima of the corrugated ring or the annular washer. When viewed in the stroke direction, the maximum and minimum of the wave correspond in particular to the maximum distance between the first and / or other section plane and the first and / or other section plane. The course of the wave can preferably be aligned in the direction of the basic extension. In particular, the circular course of the ring or the annular washer can essentially correspond to a circumferential direction extending around the displacement axis, in particular around the central axis. The area between the antinodes can particularly correspond to the intermediate section described herein. Advantageously, the corrugated ring or the annular washer can represent a way of providing the spring device according to the invention which is particularly simple in terms of conception and / or production technology and particularly effective in terms of spring force.

[0012] Advantageously, the spring device has at least one further section, in particular a plurality of further sections, corresponding to the first section, wherein the first section and the at least one further section are arranged one behind the other in the stroke direction, in particular arranged adjacent to one another. Advantageously, these multiple sections according to the invention can be used to increase the total spring force in a particularly effective manner in terms of material and installation space requirements. Corresponding to the first section, the further sections can each have a further section plane, wherein the further section plane can preferably be arranged parallel to the first section plane. Corresponding to the first section, the further section can have a first and a second sub-further section and an optional intermediate further section. All advantages and features associated with the first section can be transferred to the further sections in the same manner.

[0013] In an advantageous embodiment, segments adjacent to one another in the stroke direction are in contact with one another and / or are connected to one another. In particular, it can be provided that, when viewed in the stroke direction, a first subsegment of a segment is in contact with or connected to a second subsegment of a subsequent segment. Contact can be understood in particular as "touching". If necessary, the spring force can be further increased by contact or connection.

[0014] In an additional or alternative preferred embodiment, first and second subsegments of two adjacent segments arranged between two adjacent segment planes are directly opposite each other in pairs, in particular at a point of maximum distance from their segment planes, wherein, in particular, the opposing first and second subsegments are in contact with each other in the unloaded state and in the loaded state. The contacting first and second subsegments can in particular be connected to each other, in particular by material bonding. Advantageously, a particularly stable spring device can be achieved with this embodiment.

[0015] In an additional or alternative preferred embodiment, the segments have a maximum radial extension in a segment plane in a radial direction perpendicular to the stroke direction, wherein the maximum radial extension of successive segments is designed to be variable in the positive or negative stroke direction. Particularly preferably, the maximum radial extension of successive segments is designed to decrease monotonically, in particular strictly monotonically, in the positive or negative stroke direction, wherein the spring device is in particular conical, wherein the cone axis extends substantially in the stroke direction. When viewed in the radial direction, the maximum radial extension is in particular defined by the maximum extension of the respective segment. If the segments are in the form of a ring or in the form of a washer, the maximum radial extension can correspond to the circular diameter of the ring or washer. When viewed in the stroke direction, the end of the spring device with the smaller maximum radial extension can be adjacent to the diaphragm of the diaphragm cylinder. Advantageously, an improved adaptability to the installation space can be achieved with a spring device with a gradually decreasing radial extension. In particular, a spring characteristic that gradually increases with increasing load can be achieved by means of a conical design.

[0016] In an additional or alternative preferred embodiment, the segments have a maximum radial extension in a segment plane in a radial direction perpendicular to the stroke direction, wherein the maximum radial extension of consecutive segments is identical in the positive or negative stroke direction, in particular so that the spring device is cylindrical, wherein the cylinder axis extends substantially in the stroke direction. In particular, the maximum radial extension can be defined as above. By means of this embodiment, a particularly strong braking effect can be generated, if necessary. In particular, by means of a cylindrical design, a relatively constant and / or strongly increasing spring characteristic can be achieved.

[0017] Advantageously, the brake cylinder comprises two spring devices, each as described herein, which are spaced apart from one another in the stroke direction. It can be provided that components that do not belong to the spring devices, such as a diaphragm, are arranged between the spring devices. In other words, two separate spring devices can in particular be present. For example, one of the spring devices can be part of a parking brake and the other of the spring devices can be part of a service brake. Advantageously, several types of brakes can be combined in a particularly space-saving manner.

[0018] In an additional or alternative preferred embodiment, the brake cylinder comprises a spring device, in particular a conical or conical spring device, with a variable maximum radial extension as described herein and a cylindrical spring device. The two spring devices can be spaced apart from one another, in particular in the stroke direction. Advantageously, for example, a space-saving or space-adaptive variable spring device can be combined with a cylindrical spring device with a particularly strong spring force. This means that a particularly good adaptation to the available installation space can be achieved while achieving a high spring force.

[0019] In an advantageous embodiment, the ratio of the extension of the first of the two spring devices, in particular the conical spring device, in the stroke direction to the extension of the second of the two spring devices in the stroke direction is 0.3 to 0.9, preferably 0.5 to 0.8, particularly preferably 0.6 to 0.7. This ratio has proven to be particularly advantageous with regard to saving installation space. A ratio of 0.5 to 0.8 can be particularly advantageous in order to achieve a particularly usable spring force for both the conical spring and the cylindrical spring. A ratio of 0.6 to 0.7 can also be a particularly advantageous arrangement for providing a parking brake and a service brake.

[0020] In an advantageous embodiment, adjacent segments merge into one another in a spiral shape. The normals of the segments can be slightly inclined relative to the stroke direction, in particular by up to 10°, wherein the individual segments can in particular be arranged essentially parallel to one another. Preferably, the spiral shape can extend around a displacement axis of the brake cylinder extending in the stroke direction, in particular around a center axis of the brake cylinder. Preferably, a single segment can correspond to one turn of the spiral shape. The spiral design can advantageously achieve an increased spring force, whereby the braking force can be generated particularly effectively.

[0021] The brake cylinder is preferably a diaphragm cylinder or a double diaphragm cylinder. The diaphragm cylinder may preferably have a brake cylinder size of 10'' to 30'', preferably 16'' to 24''. The double diaphragm cylinder may preferably have a brake cylinder size of 10'' / 18'' to 30'' / 40'', preferably 16'' / 24'' to 20'' / 30''. In the case of a diaphragm cylinder, space optimization is particularly effective. In particular, if two spring devices are provided in the double diaphragm cylinder, the double diaphragm cylinder can benefit from optimization of the installation space in two ways. One of the two spring devices can be used, for example, as part of a service brake, while the other can be used, for example, as a parking brake.

[0022] The diaphragm cylinder may have a cylinder housing, wherein the spring device may be arranged in the cylinder housing. The cylinder housing may have a spring area for arranging the spring device and a compressed air area designed to be filled with compressed air. The compressed air area may have a compressed air inlet for filling with compressed air. In particular, the compressed air inlet may be aligned in the stroke direction. The spring area and the compressed air area may be separated by a diaphragm, wherein the diaphragm separates the spring area and the compressed air area from each other in an airtight manner, wherein the diaphragm is designed to compress the spring device by loading when compressed air is introduced into the compressed air area, wherein in particular, when compressed air is introduced into the compressed air area, the compressed air area increases due to the movement of the diaphragm, while the spring area decreases. The diaphragm cylinder may include a push rod or a piston rod for generating a braking force, wherein the push rod (which may also be a piston rod) is connected to the spring device and / or the diaphragm so that the push rod moves in the stroke direction when the spring device is contracted and withdrawn. The push rod can be arranged partially in the cylinder housing, in particular in the compressed air area, and partially outside the cylinder housing, wherein the push rod is particularly designed to partially move out of the cylinder housing when the spring device is contracted and withdrawn. The diaphragm cylinder may include a bellows (Faltenbalg) around the push rod outside the cylinder housing. A fork (Gabelkopf) configured to start the brake can be arranged at the end of the push rod facing away from the spring device. The push rod can be aligned substantially along the axis of movement of the diaphragm cylinder. The spring device can contact the diaphragm and / or be attached to the diaphragm with a first end when viewed in the stroke direction, and can contact the cylinder housing or be attached to the cylinder housing with a second end opposite to the first end when viewed in the stroke direction. For example, the diaphragm cylinder can be designed to load and compress the spring device through the diaphragm when compressed air is introduced into the compressed air area, so that the push rod is pushed out of the cylinder housing against the restoring force of the spring device to generate a braking force and / or a braking effect, and when the compressed air is released from the compressed air area, the diaphragm and the push rod are pushed back by the restoring force of the spring device to end the braking effect.

[0023] The double diaphragm cylinder may have a two-part cylinder housing having a first cylinder housing part and a second cylinder housing part, wherein the first spring device, in particular the first spring device as described herein, may be arranged in the first cylinder housing part. The first cylinder housing part may have a first spring area for arranging the first spring device and a first compressed air area designed to be filled with compressed air. The first compressed air area may have a first compressed air inlet for filling with compressed air. In particular, the first compressed air inlet may be aligned in a radial direction. The first spring area and the first compressed air area may be separated by a diaphragm, wherein the diaphragm separates the first spring area and the first compressed air area from each other in an airtight manner, wherein the diaphragm is configured to compress the first spring device by loading when compressed air is introduced into the first compressed air area, wherein, in particular, when compressed air is introduced into the first compressed air area, the first compressed air area increases due to the movement of the diaphragm and the first spring area decreases. The double diaphragm cylinder may include a first push rod for generating a braking force, wherein the first push rod is connected to the first spring device and / or the diaphragm so that the first push rod moves in the stroke direction when the spring device is contracted and withdrawn. The first push rod may be partially arranged in the cylinder housing, in particular in the first compressed air region, and partially arranged outside the cylinder housing, wherein the first push rod is particularly designed to partially move out of the cylinder housing when the first spring device is contracted and withdrawn. The double diaphragm cylinder may include a bellows surrounding the first push rod outside the cylinder housing. A fork configured to activate the brake may be arranged at the end of the first push rod facing away from the first spring device. The first push rod may be aligned substantially along the axis of movement of the double diaphragm cylinder. The first spring device may contact the diaphragm and / or be attached to the diaphragm with a first end when viewed in the stroke direction, and may contact the cylinder housing or be attached to the cylinder housing with a second end opposite to the first end when viewed in the stroke direction. The double diaphragm cylinder can be designed, for example, so that when compressed air is introduced into the first compressed air area, the first spring device is loaded and compressed by the diaphragm, so that the first push rod is pushed out of the first compressed air area against the restoring force of the first spring device to generate a braking force and / or a braking effect, and when the compressed air is released from the compressed air area, the diaphragm and the push rod are pushed back by the restoring force of the spring device to end the braking effect. The second spring area and the second compressed air area designed to be filled with compressed air can be arranged in the second cylinder housing part, wherein, in particular, the second compressed air area is arranged between the first cylinder housing part and the second spring area. In particular, the second spring device that can be activated in the stroke direction as described herein can be arranged in the second spring area. The second compressed air area can have a second compressed air inlet for filling with compressed air. In particular, the second compressed air inlet can be aligned in the radial direction.

[0024] The second spring area and the second compressed air area can be separated from each other in an airtight manner, so that when compressed air is introduced into the second compressed air area, the second spring device is compressed due to being loaded, so that in particular, when compressed air is introduced into the second compressed air area, the second compressed air area increases due to the movement and / or reduction of the second spring area. The double diaphragm cylinder may include a second push rod, wherein the second push rod contacts the diaphragm and is configured to move along the stroke direction with the second spring area, so that when the second spring device is contracted and withdrawn, the second push rod moves along the stroke direction and contracts the first spring device when the second spring device is withdrawn, thereby generating a parking brake force by the first push rod. The second push rod can be substantially aligned along the axis of movement of the double diaphragm cylinder. The second push rod can be a piston rod. The second spring device can have the features, advantages or embodiments disclosed in the context of the spring device. When viewed in the stroke direction, the second spring device can contact and / or be attached to one end of the second spring area facing the second compressed air area, and can contact or be attached to the cylinder housing with the other end. The double diaphragm cylinder can be designed, for example, such that when compressed air is introduced into the second compressed air area, the second spring device is loaded and compressed, so that the second push rod is pushed back, so that the first spring device is not loaded by the second spring device, and when the compressed air is released from the air compression area, the second push rod is pushed forward by the spring force of the second spring device, so that the first spring device is compressed and a braking effect is generated. Advantageously, the double diaphragm cylinder can be designed to generate a braking force of a service brake and a braking force of a parking brake. In particular, the first spring device can be designed to automatically release the service brake when no compressed air is present in the first compressed air area, wherein the second spring device can be designed to activate the parking brake when no compressed air is present in the second compressed air area.

[0025] Advantageously, the spring device is at least partially, in particular completely, made of metal, wherein the first section of the spring device is in particular made of metal. The spring device can be made of steel, for example. Production using metal is advantageous for use in brake cylinders, in particular in commercial vehicles. For example, a spring device made of metal can increase the stability and / or reliability of the spring device.

[0026] Advantageously, the spring device is manufactured from sheet metal in a plurality of sections, in particular at least the first section, wherein the other sections are also manufactured from sheet metal. Using sheet metal production, a particularly space-saving design of the spring device can be achieved, in particular a space-saving design in the stroke direction. Advantageously, the ratio of the extension of the sheet metal in the stroke direction to the extension of the first section in the radial direction can be less than 0.3, preferably less than 0.1, particularly preferably less than 0.05, wherein the lower limit of this ratio can be particularly greater than 0.001, preferably greater than 0.005, particularly preferably greater than 0.01. A ratio of less than 0.3 (and preferably greater than 0.001) can achieve a particularly space-saving design. A ratio in the range of less than 0.1 (and preferably greater than 0.005) can also save weight and material, while still maintaining good stability. A ratio of less than 0.05 (and preferably greater than 0.01) can be particularly effective here.

[0027] Advantageously, in the unloaded state, the ratio of the diameter of the spring device in the radial direction to the extension of the spring device in the stroke direction is 0.5 to 5, preferably 1 to 3, particularly preferably 1.1 to 2.0. Advantageously, with this ratio, a particularly space-saving design can be achieved. In particular, a ratio of 1 to 3 provides a particularly effective combination of installation space saving and stability. A ratio of 1.1 to 2.0 is particularly advantageous for commercial vehicle brakes.

[0028] Advantageously, the ratio of the diameter of the spring device in the radial direction to the spring travel of the spring device is 0.5 to 20, preferably 1 to 10, particularly preferably 2 to 8. This allows particularly good braking forces to be achieved.

[0029] Advantageously, the spring device comprises 2 to 20, preferably 3 to 10, particularly preferably 6 to 8 segments, which are arranged one behind the other, particularly in the stroke direction, wherein the segments are particularly the first segment and the further segments. Practice has shown that 2 to 20 segments can generate good braking forces. By using 3 to 10 segments, it is also possible to achieve good savings in installation space without falling below the required braking force. 6 to 8 segments have proven to be particularly effective.

[0030] Advantageously, the first section comprises 2 to 20, preferably 3 to 10, particularly preferably 4 to 8 first subsections and / or 2 to 20, preferably 3 to 10, particularly preferably 4 to 8 second subsections. Other sections can have a corresponding number of first and / or second subsections, in particular a plurality of subsections located in the same area. In conical embodiments, the number of subsections of other sections can optionally vary, for example becoming fewer as the cone diameter decreases. 2 to 20 subsections can be arranged particularly well in the brake cylinder. 3 to 10 subsections can achieve a particularly good combination of stability and braking force. 4 to 8 subsections are particularly advantageous in this respect, in particular for commercial vehicle brakes.

[0031] Another aspect of the invention is a vehicle brake, in particular a commercial vehicle brake, having a brake cylinder as described herein. All advantages and features of the brake cylinder can be transferred analogously to the vehicle brake and vice versa. The vehicle brake can be, for example, a disc brake, a floating caliper brake and / or a drum brake.

[0032] Another aspect of the invention is the use of a wave spring, in particular a spring arrangement as described herein, for a commercial vehicle brake. Preferably, the spring arrangement generates a braking force in the stroke direction of the brake cylinder and / or a restoring force for releasing the brake. All advantages and features of the brake cylinder and the vehicle brake can be transferred analogously to the use and vice versa. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] The various features and embodiments mentioned can be combined with each other, and the advantages associated with the various features also apply to the combination of these features. Other advantages and features of the present invention are derived from the following description of preferred embodiments according to the purpose of the present invention with reference to the accompanying drawings. The following description is intended only to illustrate the present invention and should not be interpreted as limiting the attached claims to any one embodiment. The various features disclosed in the illustrated embodiments can also be used in other embodiments, unless this is explicitly excluded.

[0034] Figure 1 A cross-sectional view of a brake cylinder according to a first embodiment of the present invention is shown.

[0035] Figure 2 A cross-sectional view of a brake cylinder according to a second embodiment of the present invention is shown. DETAILED DESCRIPTION

[0036] Figure 1A cross-sectional view of a brake cylinder according to a first embodiment of the present invention is shown. In this embodiment, the brake cylinder is a diaphragm cylinder. The diaphragm cylinder has a spring device 1 that generates a restoring force for releasing the brake along the stroke direction H of the brake cylinder, and the spring device 1 is shown in an unloaded state. The spring device 1 is arranged circumferentially around the displacement axis of the brake cylinder oriented along the stroke direction H. The spring device 1 has a first section 2 and a plurality of other sections 5. The other sections 5 are basically constructed in a similar manner to the first section 2. The first section 2 has a plurality of first subsections 3 and second subsections 4 along the direction of its basic extension, which extends in the circumferential direction U. The first subsections 3 correspond to the antinodes of the first section 2 of the wave-shaped ring, wherein these antinodes are deflected in the positive stroke direction H and can therefore also be referred to as crests. The second subsections 4 correspond to the antinodes of the first section 2 of the wave-shaped ring, wherein these antinodes are deflected in the negative stroke direction H. Therefore, these antinodes can also be referred to as troughs. In the present example, the normal of the plane corresponding to the first segment plane (not shown) extends in the stroke direction H, and the edge of the plane extends in the radial direction R in the illustration, wherein the first segment plane is arranged at the center of the first segment 2 when viewed in the stroke direction H, i.e., exactly in the middle between the first subsegment 3 and the second subsegment 4. The first subsegment 3 and the second subsegment 4 are elastically connected to each other via the middle segment 6, respectively, wherein the middle segment 6 intersects the first segment plane. The adjacent segments 2, 5 in the stroke direction H are in contact with each other, so that the first subsegment 3 and the second subsegment 4 of the two adjacent segments 2, 5 arranged between the two adjacent segment planes 2, 5 are directly opposite to each other in pairs at the point of the maximum distance from their segment planes. The first and second opposite subsegments 3, 5 are in contact with each other both in the unloaded state and in the loaded state (not shown here). The sections 2, 5 have a maximum radial extension in the radial direction R, wherein the maximum radial extension of successive sections 2, 5 is designed to decrease strictly monotonically in the negative stroke direction, or in this case conically. In the exemplary embodiment, the diaphragm cylinder also has a cylinder housing 16, which has a spring area 12 and a compressed air area 13, and the spring device 1 is arranged in the spring area 12. When compressed air is introduced into the compressed air area 13 through the compressed air inlet 15, the diaphragm 10 is pushed forward in the stroke direction H between the compressed air area 13 and the spring area 12, so that the spring device 1 is compressed. This also causes the push rod 14 to be pushed forward, thereby actuating the brake. If the compressed air is released from the compressed air area 13, the restoring force of the spring device 1 causes the push rod 14 to retract, thereby releasing the brake.

[0037] Figure 2 FIG. 2 shows a cross-sectional view of a brake cylinder according to a second embodiment of the present invention. In this embodiment, the brake cylinder is a double diaphragm cylinder. The double diaphragm cylinder has a first spring device 21 and a second spring device 31. The spring devices 21 and 31 are basically arranged in the same manner as Figure 1 The spring device 1 shown is constructed in a similar manner. The segments 25 of the first spring device 21 also have a maximum radial extension in the radial direction R, wherein the maximum radial extension of successive segments 25 is designed to decrease strictly monotonically or, in this case, conically in the negative stroke direction H. On the other hand, the segments 35 of the second spring device 31 have a constant maximum radial extension in the radial direction R, so that the second spring device is cylindrical. The double diaphragm cylinder has a cylinder housing 16, which has a first spring area 22 for arranging the first spring device 21, a second spring area 32 for arranging the second spring device 31, a first compressed air area 23 and a second compressed air area 33. When compressed air is introduced into the first compressed air area 23, the diaphragm 10 is pushed forward in the stroke direction H between the first compressed air area 23 and the first spring area 22, so that the spring device 21 is compressed. This also causes the first push rod 24 to be pushed forward, thereby actuating the brake. If compressed air is released from the first compressed air area 23, the restoring force of the spring device 21 contracts the push rod 24, thereby releasing the brake. On the other hand, the right part of the double diaphragm cylinder acts as a parking brake. If compressed air is present in the compressed air area 33 and the spring device 31 is compressed as a result, the brake is not activated. On the other hand, if the spring device is not compressed, it exerts pressure on the diaphragm 10 via the second push rod and thus on the first spring device 21, whereby the first spring device 21 is compressed, the first push rod 24 is pushed forward in the stroke direction H and the brake is activated.

[0038] List of reference numerals: 1- Spring device 2-First Section 3 - First subsection 4-Second subsection 5- Other sections 6-Middle section 12- Spring area 13- Compressed air area 14-Putter 15- Compressed air inlet 16-Cylinder housing 21-First spring device 22-First spring area 23-First compressed air area 24-First putt 25- Section of the first spring device 31-Second spring device 32-Second spring area 33-Second compressed air area 34-2nd putt 35- Section of the second spring device H-travel direction R - radial direction U - circumferential direction

Claims

1. A brake cylinder for a vehicle brake, in particular for a commercial vehicle brake, comprising a spring device (1), wherein: The spring device is in particular a wave spring.

2. The brake cylinder according to claim 1, in, The spring device (1) for generating a braking force in the stroke direction (H) of the brake cylinder and / or a restoring force for releasing the brake has at least a first section (2). wherein the first section (2) has a basic extension extending substantially in a first section plane, wherein the normal of the first section plane is aligned substantially parallel to the stroke direction (H) and / or deviates from the stroke direction (H) by at most 10°, wherein the first section (2) has, in particular alternately has, along its basic extension, a first subsection (3) and a second subsection (4), wherein, in the unloaded state, the first subsegment (3) is spaced apart from the first segment plane along the positive stroke direction (H), and wherein, in the unloaded state, the second subsegment (4) is spaced apart from the first segment plane along the negative stroke direction (H), The first and second subsections (3, 4) are designed to be at a smaller distance from the first section plane in a loaded state when a spring force is generated than in an unloaded state.

3. The brake cylinder according to claim 2, in, The first section (2) comprises at least one intermediate section (6), which connects one of the first subsections (3) to one of the second subsections (4), in particular elastically, and which intersects the first section plane. Therein, the first section (2) in particular comprises a plurality of intermediate sections (6), each of which connects the first and second subsections (3, 4) which are consecutive in the direction of the basic extension.

4. The brake cylinder according to any one of claims 2 to 3, in, The first section (2) and / or one or more further sections (5) of the spring device (1) are substantially designed as a corrugated ring and / or an annular washer, wherein the antinodes of the corrugated ring and / or the annular gasket correspond to the first and second subsections (3, 4), Therein, the ring and / or the annular washer is / are arranged in particular in such a way that the center of the ring / annular washer is arranged substantially on the movement axis of the brake cylinder oriented in the stroke direction (H).

5. The brake cylinder according to any one of claims 2 to 4, in, The spring device (1) has at least one further section (5), in particular a plurality of further sections (5), corresponding to the first section (2). Therein, the first section (2) and the at least one further section (5) are arranged one after the other in the stroke direction (H), in particular are arranged adjacent to one another.

6. The brake cylinder according to claim 5, in, The sections (2, 5) adjacent to each other along the stroke direction (H) are in contact with each other and / or connected to each other.

7. The brake cylinder according to any one of claims 5 to 6, in, The first and second sub-segments (3, 4) of two adjacent segments (2, 5) arranged between two adjacent segment planes are directly opposite each other in pairs, in particular directly opposite each other at the points of maximum distance from their segment planes, In particular, the first and second opposing subsections (3, 4) are in contact with each other in an unloaded state and in a loaded state.

8. The brake cylinder according to any one of claims 5 to 7, in, The segments (2, 5) have a maximum radial extension in the segment plane in a radial direction (R) perpendicular to the stroke direction (H), wherein the maximum radial extension of successive segments (2, 5) is designed to decrease monotonically, in particular strictly monotonically, in the positive or negative stroke direction (H), The spring device (1) is particularly designed to be conical, and the cone axis of the cone extends substantially along the stroke direction (H).

9. The brake cylinder according to any one of claims 5 to 8, in, The segments (2, 5) have a maximum radial extension in the segment plane in a radial direction (R) perpendicular to the stroke direction (H), The maximum radial extension of consecutive sections (2, 5) is designed to be the same along the positive or negative stroke direction (H), in particular so that the spring device (1) is cylindrical, and the cylinder axis of the cylinder extends substantially along the stroke direction (H).

10. A brake cylinder according to any one of the preceding claims, in, The brake cylinder comprises two spring devices according to any one of the preceding claims, Therein, the spring devices are spaced apart from one another along the stroke direction (H).

11. The brake cylinder according to claim 8 and / or 9 and / or 10, in, The brake cylinder comprises a conical spring device (21) and a cylindrical spring device (31).

12. A brake cylinder according to any one of the preceding claims, in, The brake cylinder is a diaphragm cylinder or a double diaphragm cylinder.

13. A brake cylinder according to any one of the preceding claims, in, In the unloaded state, the ratio of the diameter of the spring device (1) in the radial direction (R) to the extension of the spring device (1) in the stroke direction (H) is 0.5 to 5, preferably 1 to 3, particularly preferably 1.1 to 2.

0.

14. A vehicle brake, in particular a commercial vehicle brake, having a brake cylinder according to any of the preceding claims.

15. Use of a wave spring for commercial vehicle brakes, in particular in a spring device (1) or in a brake cylinder according to any one of claims 1 to 13.

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