Brake cylinder for a vehicle brake

Abstract

Brake cylinder for a vehicle brake, in particular a commercial vehicle brake, comprising a spring device, wherein the spring device (1) for generating a braking force and / or a restoring force for releasing a brake in a stroke direction (H) of the brake cylinder has at least a first section (2), wherein the first section (2) has a basic extension extending substantially on a first section plane, wherein a normal of the first section plane is oriented substantially parallel to the stroke direction (H) and / or deviates from the stroke direction (H) by a maximum of 10°, wherein the first section (2) has, in particular alternately, first subsections (3) and second subsections (4) along its basic extension, wherein the first subsections (3) are spaced apart from the first section plane in the positive stroke direction (H) in the unloaded state.and wherein the second subsections (4) are spaced apart from the first section plane in the negative stroke direction (H) in the unloaded state, wherein the first and second subsections (3, 4) are designed to have a smaller distance to the first section plane in the loaded state while generating a spring force than in the unloaded state.

Description

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

[0002] The installation space for vehicle axles, especially commercial vehicle axles and / or trailer axles, is generally limited. Furthermore, it can be advantageous to maximize the spring center of the axle, i.e., the distance between the axle's mounting points on the wheel suspension via control arms or springs. This can, for example, improve rollover stability and / or, in vehicles with steering axles, allow for a greater steering angle. Additionally, the steering angle can be directly dependent on the spring center, as adjacent components, such as control arms and brakes, may move towards each other during steering.

[0003] A reduction in the number of components would be advantageous here, particularly to save costs, material, and / or installation space. The component length of brake cylinders, especially diaphragm or double-diaphragm cylinders, is generally determined or influenced by their round wire springs and their spring travel.

[0004] DE 36 21 926 A1 relates to a brake parking device for use on road vehicles.

[0005] DE 10 2019 120 409 A1 shows a brake arrangement for a wheel hub drive of a vehicle.

[0006] DE 11 2018 006 744 T5 refers generally to vehicle braking systems.

[0007] It is therefore an object of the invention to provide a brake cylinder in which the required installation space is reduced and / or can be reduced.

[0008] This problem is solved 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 will become apparent from the dependent claims, the description, and the figures and their description.

[0009] According to the invention, a brake cylinder for a vehicle brake, in particular a commercial vehicle brake, is provided comprising a spring device, wherein the spring device is a wave spring. Advantageously, the spring device surrounds a piston rod of the brake cylinder. This allows for a significant saving of installation space. The wave spring can also be referred to as a wave ring spring. The wave spring can, for example, comprise corrugated rings made of sheet metal and / or flat wire. In the unloaded state, the corrugated rings can include antinodes or maxima and minima, wherein the antinodes are particularly designed to generate a spring force in a compressed state. The spring force can preferably be generated in a displacement or stroke direction, this direction being particularly parallel to the extension direction of the piston rod or a piston rod of the brake cylinder.Several corrugated rings can be arranged one behind the other in the direction of travel or displacement, wherein the corrugations run circumferentially around the direction of travel or travel and / or perpendicular to the direction of travel or travel. Advantageously, particularly to achieve a large spring travel, the crests of a corrugated ring of the spring assembly contact the troughs of the corrugated ring or an adjacent corrugated ring, which can (fundamentally) also be referred to as a corrugated ring. A commercial vehicle within the meaning of the invention is, in particular, a vehicle that has a permissible total weight of more than 3.5 t, preferably more than 7.5 t, particularly preferably more than 15 t, and most preferably more than 18 t. The commercial vehicle is, in particular, a road-legal and / or road-bound vehicle. Advantageously, the commercial vehicle is a trailer, in particular a semi-trailer.The brake cylinder can preferably be an air-operated, in particular compressed air-operated, and / or air-operable, in particular compressed air-operable, brake cylinder. For example, the brake cylinder can be designed to be operated as a service brake by compressed air when used as part of a vehicle brake system. Additionally or alternatively, the brake cylinder can be designed to be activated as a parking brake by means of a spring force from the spring assembly when used as part of a vehicle brake system. In other words, the spring assembly can be a functional part of a parking brake system. 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.With drum brakes, space constraints can extend to the adjacent chassis, making the brake cylinder according to the invention particularly advantageous due to its space-saving properties. The brake cylinder can be designed so that compressed air, for example acting on a diaphragm of the diaphragm brake, can counteract the braking force, thus canceling the braking force generated by the spring assembly. In other words, the brake cylinder can be designed to place the spring assembly, particularly by means of compressed air, into a loaded state in which the spring assembly does not produce a braking effect. It can be provided that the spring assembly is continuously held in a loaded state by means of compressed air during driving in order to prevent the generation of a braking force.Additionally or alternatively, the brake cylinder can be designed to generate braking force in the unloaded state. The spring device can be designed to transmit the braking force to a braking mechanism, e.g., a brake piston. The braking mechanism can be, wholly or partially, part of the brake cylinder. The braking force of the spring device can, in particular, be generated by a spring force of the spring device.

[0010] Preferably, a brake cylinder for a vehicle brake, in particular a commercial vehicle brake, is provided, comprising a spring device, wherein the spring device for generating a braking force and / or a restoring force for releasing a brake in a stroke direction of the brake cylinder has at least a first section, wherein the first section has a basic extent extending substantially on a first section plane, wherein a normal of the first section plane is oriented substantially parallel to the stroke direction and / or deviates from the stroke direction by a maximum of 10°, wherein the first section has, in particular alternately, first subsections and second subsections along its basic extent, wherein the first subsections are spaced apart from the first section plane in the positive stroke direction in the unloaded state.and wherein the second sections are spaced away from the first section plane in the negative stroke direction in the unloaded state, wherein the first and second sections are designed to have a smaller distance to the first section plane in the loaded state, generating a spring force, 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 can correspond to the braking force. Advantageously, with a spring-operated parking brake, there is no risk that the braking force will decrease due to a pressure drop while the vehicle is parked. The braking force of the spring device can in particular be generated by a spring force of the spring device. The braking force acts in particular in the stroke direction,especially in the positive stroke direction. Alternatively or additionally, the spring device can be configured to release a brake. For example, it may be provided that a braking force, especially of a service brake, is generated by compressed air or another mechanism, and the spring device has the task of generating a restoring force to release the brake. The restoring force can be configured, in particular, to retract a push rod, which can also be referred to as a piston rod or be designed as such, or a brake piston when the brake is not pressurized with compressed air. The stroke direction can preferably be the direction in which the brake mechanism is actuated, in particular the directionin which a brake piston is moved when the brake is released and / or engaged. A direction extending radially to the stroke direction is referred to as the radial direction within the scope of this invention. A direction extending circularly around the stroke direction or a displacement axis, in particular the central axis, of the brake cylinder and / or perpendicular to the stroke direction and the radial direction is referred to as the circumferential direction. In particular, it can be provided that the brake mechanism is movable in the positive stroke direction for release and / or engagement and in the negative stroke direction for release of the brake. The first section plane (or analogously one or more further section planes) can be defined in particular bythat, in the unloaded state, the first and second sections are each approximately the same distance from the first section plane. The spacing of the first and second sections from the section plane can refer to a maximum distance and / or an average distance. "Approximately" can mean a deviation tolerance of a maximum of 15%, preferably a maximum of 10%, and particularly preferably a maximum of 5%, of the total distance. It can be provided that the average distance of the first and second sections in the normal direction of the section plane sums to approximately zero. The normal direction corresponds to the direction of the normal of the section plane. The normal direction of the section plane can be tilted slightly relative to the stroke direction, in particular by up to 10°, preferably by up to 5°. This advantageously allows for greater freedom in the design of the spring device.the braking force may not be affected or only minimally affected. Preferably, the first sections and the second sections have a smaller distance to the first section plane in the loaded state than in the unloaded state. A smaller distance within the meaning of the invention can also mean that there is no distance at all. In other words, the brake cylinder can be designed such that the first and second subsections have no or only a negligible distance to the first section plane in the loaded state. A negligible distance can be a distance that is less than 50%, preferably less than 20%, particularly preferably less than 10%, and most preferably less than 5%, of the distance in the unloaded state. The brake cylinder and / or the spring device can be designed such thatthat by reducing the distance of the first and second subsections from the section plane, a spring force is generated, wherein the spring force is in particular the braking force and / or restoring force and / or generates. The basic extent need not necessarily be straight. In particular, the basic extent can, for example, have a curved shape. The basic extent can correspond to a longitudinal extent of the first section, which may optionally be curved. The arrangement of the first and second subsections can be provided to vary periodically. The first and second subsections can follow one another along the basic extent, in particular alternately. The spring device can – as already explained – in particular be a wave ring spring or a wave spring. It has been shown that a saving in installation space can be achieved with the brake cylinder according to the invention. This can be made possible by,The spring device according to the invention can shorten the brake actuation travel or the cylinder stroke used to generate the braking force because the spring device according to the invention requires less space than a round wire spring typically used in the prior art. Advantageously, this also allows the length of the brake cylinder to be reduced. In particular, a reduction in the component length in the stroke direction of up to 50% can be achieved compared to conventional round wire springs. This value can potentially be improved even further, for example, in brakes with multiple spring devices. It has been observed that the stroke or spring travel used in the prior art, or required by the brake cylinder used, is often greater.than is necessary for the actual braking process by the brake. Shortening the brake cylinder component can result in a significant design advantage for the more efficient design and configuration of vehicles, particularly in the area of ​​the vehicle axles. Additionally, the brake cylinder according to the invention can have a reduced weight. In particular, this can reduce the weight of the vehicle's unsprung mass.

[0011] According to one embodiment, the brake cylinder can have a mounting device for attachment to a vehicle brake. The mounting device can be configured, for example, to enable a friction-fit, positive-fit, and / or material-fit connection. The mounting device can, for example, include a bayonet fitting and / or a clamping connection. Advantageously, the mounting device facilitates the integration of the component into a brake, e.g., a disc brake. Furthermore, the mounting device can facilitate the retrofitting of the brake cylinder into existing brakes or brake systems.

[0012] Advantageously, the first section of the spring assembly, and in particular the complete spring assembly, is arranged circumferentially around a displacement axis, particularly a central axis, of the brake cylinder that is oriented substantially in the stroke direction. In particular, it can be provided that the basic extension of the first section is arranged circumferentially. The ends of the first section, viewed in the direction of its basic extension, can be connected to one another and / or attached to one another. It can be provided that further sections of the spring assembly, and in particular all sections of the spring assembly, are arranged circumferentially around a displacement axis, particularly a central axis, of the brake cylinder that is oriented substantially in the stroke direction. "Substantially in the stroke direction" can include a design-related deviation from a parallel alignment and / or a deviation of a maximum of 15°, preferably 10°, and particularly preferably a maximum of 5°.The spring device can preferably be arranged in a circular pattern around the displacement axis, in particular the central axis. The center of the circle can lie substantially on the displacement axis. "Substantially" here means that the center is located a maximum of 15%, preferably a maximum of 10%, and particularly preferably a maximum of 5%, of the radius of the spring device from the center. Advantageously, a circular arrangement allows for particularly efficient optimization of installation space, especially perpendicular to the stroke direction or in the radial direction. Furthermore, a particularly uniform spring force can be generated in the stroke direction across the radial direction.

[0013] Advantageously, the first section comprises at least one intermediate section that connects one of the first subsections to one of the second subsections, particularly elastically, and that intersects the plane of the first section. The at least one intermediate section can preferably be arranged between each first subsection and a second subsection that are adjacent to each other, particularly in the circumferential direction. Adjacent can, in particular, mean that no other first or second subsection is arranged between the two adjacent subsections and / or that no other subsection is closer to the first or second subsection than the other of the two adjacent subsections. Advantageously, the at least one intermediate section can be used to generate a particularly efficient elastic spring force by moving the two subsections relative to each other in the stroke direction.The at least one intermediate section can be arranged radially centrally inside between the first and second subsections and / or radially outside the subsections. Particularly preferably, the at least one intermediate section can be arranged circumferentially between two subsections. The first section can, in particular, comprise a plurality of intermediate sections, each connecting successive first and second subsections in the direction of the basic extension. Particularly preferably, the basic extension can be circumferential. In particular, first and second subsections can be provided alternately in the circumferential direction, with the first subsections being connected to the second subsections following in the circumferential direction by the intermediate sections, and vice versa.Advantageously, such an arrangement with intermediate sections can enable a particularly flat spring characteristic curve for the spring device. This can be especially well-suited for use in brake cylinders, particularly for the parking brake section of the brake cylinder. Furthermore, such an arrangement allows for a particularly efficient reduction in installation space.

[0014] Advantageously, the first section and / or one or more further sections of the spring device are essentially designed as a corrugated ring(s) and / or ring disc(s), wherein the antinodes of the corrugated rings and / or ring discs correspond to the first and second sections, and the rings and / or ring discs are arranged such that the center point of the rings / ring discs is located essentially on a displacement axis, particularly the central axis, of the brake cylinder oriented in the stroke direction. The antinodes particularly denote the maxima and minima of the corrugated rings or ring discs. The maxima and minima of the corrugations correspond in particular to the maximum distance of the first and / or further section from the first and / or further section plane in the stroke direction. The orientation of the corrugations can preferably be aligned in the direction of the basic extension.In particular, the circular shape of the rings or ring discs can essentially correspond to the circumferential direction around the axis of displacement, especially the central axis. Areas between the corrugated sections can correspond in particular to the intermediate sections as described herein. Advantageously, corrugated rings or ring discs can represent a conceptually and / or technically particularly simple and, with regard to spring force, efficient way of providing the spring device according to the invention.

[0015] Advantageously, the spring device comprises at least one further section, and 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, and in particular adjacent to each other. Advantageously, the multiple sections according to the invention enable a particularly efficient increase in the overall spring force with regard to material and installation space requirements. The further sections can each have further section levels corresponding to the first section, wherein the further section levels can preferably be arranged parallel to the first section level. The further sections can have further first and second subsections, as well as optionally further intermediate sections, corresponding to the first section.All the advantages and features relating to the first section can be applied analogously to the subsequent sections.

[0016] In an advantageous embodiment, adjacent sections in the stroke direction contact each other and / or are connected to each other. In particular, it can be provided that the first subsections of one section contact or are connected to the second subsections of the next section in the stroke direction. "Contact" in this context can be understood to mean, in particular, "touching each other." The spring force can be further increased by this contact or connection.

[0017] In a further or alternatively preferred embodiment, first and second subsections of two adjacent sections, arranged between two adjacent section planes, are positioned in pairs, particularly at the point of greatest distance from their section plane, directly opposite each other, wherein, in particular, opposing first and second subsections contact each other in both the unloaded and loaded states. The contacting first and second subsections can, in particular, be connected to each other by a material bond. Advantageously, this embodiment enables a particularly stable spring device.

[0018] In an additionally or alternatively preferred embodiment, the sections on the section planes have a maximum radial extent in a radial direction perpendicular to the stroke direction, wherein the maximum radial extent of successive sections is variable in the positive or negative stroke direction. Particularly preferably, the maximum radial extent of successive sections in the positive or negative stroke direction is monotonically, and in particular strictly monotonically, decreasing, wherein the spring device is preferably conical with a cone axis extending substantially in the stroke direction. The maximum radial extent is defined in particular by the greatest radial extent of the respective section. If the sections are annular or disk-shaped, the maximum radial extent can correspond to the circular diameter of the rings or disks.Viewed in the direction of travel, the end of the spring assembly with a smaller maximum radial extension can abut a diaphragm of the diaphragm cylinder. Advantageously, a spring assembly with a decreasing radial extension allows for improved adaptation to the installation space. In particular, a conical design enables a spring characteristic that increases progressively with increasing load.

[0019] In an additionally or alternatively preferred embodiment, the sections on the section planes have a maximum radial extent in a radial direction perpendicular to the stroke direction, wherein the maximum radial extent of successive sections is the same in the positive or negative stroke direction, in particular such that the spring device is cylindrical with a cylinder axis extending substantially in the stroke direction. The maximum radial extent can be defined, in particular, as above. With this embodiment, a particularly strong braking effect can optionally be generated. In particular, a cylindrical design can enable a relatively constant and / or steeply increasing spring characteristic.

[0020] Advantageously, the brake cylinder comprises two spring assemblies, each as described herein, wherein the spring assemblies are spaced apart from each other in the direction of travel. Components not belonging to the spring assemblies, e.g., a diaphragm, may be arranged between them. In other words, there may be two separate spring assemblies. For example, one of the spring assemblies may be part of a parking brake and the other part of a service brake. Advantageously, several types of brakes can thus be combined in a particularly space-saving manner.

[0021] In an additionally or alternatively preferred embodiment, the brake cylinder comprises a spring assembly with variable maximum radial extension as described herein, in particular a conical or cone-like spring assembly, and a cylindrical spring assembly. The two spring assemblies can be spaced apart from each other, particularly in the stroke direction. Advantageously, for example, a space-saving or space-adapted variable spring assembly can be combined with a cylindrical spring assembly with a particularly strong spring force. This allows, in particular, a very good adaptation to the available installation space while simultaneously achieving a high spring force.

[0022] In an advantageous embodiment, the extension in the stroke direction of a first of the two spring devices, in particular the conical spring device, to the extension in the stroke direction of a second of the two spring devices, in particular the cylindrical spring device, is in a ratio of 0.3 to 0.9, preferably 0.5 to 0.8, and most preferably 0.6 to 0.7. Such a ratio has proven particularly advantageous with regard to saving installation space. A ratio of 0.5 to 0.8 can be particularly advantageous for achieving 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.

[0023] In an advantageous embodiment, adjacent sections transition into one another in a spiral fashion. The normals of the sections can be slightly inclined relative to the stroke direction, in particular by up to 10°, with the respective sections being arranged substantially parallel to one another. The spiral can preferably extend around a displacement axis, in particular a central axis, of the brake cylinder running in the stroke direction. A single section can preferably correspond to one revolution of the spiral. An increased spring force can advantageously be achieved by a spiral design, thereby enabling particularly efficient generation of the braking force.

[0024] Advantageously, the brake cylinder is a diaphragm cylinder or a double diaphragm cylinder. The diaphragm cylinder preferably has a brake cylinder size of 10 to 30", more preferably 16 to 24". The double diaphragm cylinder preferably has a brake cylinder size of 10 / 18" to 30 / 40", more preferably 16 / 24" to 20 / 30". Space optimization is particularly effective with diaphragm cylinders. In particular, a double diaphragm cylinder can benefit from space optimization in two ways if two spring devices are provided in the double diaphragm cylinder. One of the two spring devices can be used, for example, as part of a service brake, while another spring device can serve, for example, as a parking brake.

[0025] The diaphragm cylinder can have a cylinder housing, wherein the spring device can be arranged in the cylinder housing. The cylinder housing can have a spring section in which the spring device is arranged and a compressed air section designed for filling with compressed air. The compressed air section can have a compressed air inlet for filling with compressed air. The compressed air inlet can be oriented, in particular, in the stroke direction. The spring section and the compressed air section can be separated by a diaphragm, wherein the diaphragm separates the spring section and the compressed air section from each other airtight, wherein the diaphragm is designed to compress the spring device by applying pressure when compressed air is introduced into the compressed air section, wherein, in particular, the compressed air section enlarges and the spring section shrinks when compressed air is introduced into the compressed air section due to displacement of the diaphragm.The diaphragm cylinder can include a pushrod or piston rod for generating a braking force, wherein the pushrod, which can also be a piston rod, is connected to the spring assembly and / or the diaphragm such that the pushrod is moved in the stroke direction when the spring assembly contracts and extends. The pushrod can be arranged partially within the cylinder housing, particularly in the compressed air area, and partially outside the cylinder housing, wherein the pushrod is specifically designed to be moved partially out of the cylinder housing when the spring assembly contracts and / or extends. The diaphragm cylinder can include a bellows that surrounds the pushrod outside the cylinder housing. A clevis, configured to activate a brake, can be arranged at the end of the pushrod opposite the spring assembly.The push rod can be aligned essentially along the displacement axis of the diaphragm cylinder. Viewed in the stroke direction, the spring assembly can have one end contacting the diaphragm and / or being attached to the diaphragm, and the other end contacting or being attached to the cylinder housing. The diaphragm cylinder can be configured, for example, such that when compressed air is introduced into the compressed air chamber, the spring assembly is loaded and compressed by means of the diaphragm, causing the push rod to be pushed out of the cylinder housing against the restoring force of the spring assembly to generate a braking force and / or braking effect. Conversely, when the compressed air is released from the compressed air chamber, the diaphragm and the push rod are pushed back by the restoring force of the spring assembly to terminate the braking effect.

[0026] The double diaphragm cylinder can have a two-part cylinder housing comprising a first cylinder housing part and a second cylinder housing part, wherein a first spring device, particularly as described herein, can be arranged in the first cylinder housing part. The first cylinder housing part can have a first spring area in which the first spring device is arranged and a first compressed air area configured for filling with compressed air. The first compressed air area can have a first compressed air inlet for filling with compressed air. The first compressed air inlet can, in particular, be oriented radially.The first spring section and the first compressed air section can be separated by a diaphragm, wherein the diaphragm provides an airtight seal between the first spring section and the first compressed air section, and wherein the diaphragm is designed to compress the first spring assembly under load when compressed air is introduced into the first compressed air section, wherein, in particular, the first compressed air section enlarges and the first spring section shrinks when compressed air is introduced into the first compressed air section by displacement of the diaphragm. The double diaphragm cylinder can include a first pushrod for generating a braking force, wherein the first pushrod is connected to the first spring assembly and / or the diaphragm such that the first pushrod is moved in the stroke direction when the first spring assembly contracts and extends.The first pushrod can be arranged partially within the cylinder housing, particularly in the first compressed air section, and partially outside the cylinder housing. The first pushrod is specifically designed to be partially moved out of the cylinder housing during contraction and / or extension of the first spring assembly. The double diaphragm cylinder can include a bellows that surrounds the first pushrod outside the cylinder housing. A clevis, configured to activate a brake, can be arranged at the end of the first pushrod opposite the first spring assembly. The first pushrod can be oriented substantially along the displacement axis of the double diaphragm cylinder.The first spring assembly can, viewed in the direction of stroke, have a first end that contacts the diaphragm and / or is attached to the diaphragm, and a second end that is opposite the first end in the direction of stroke and is also connected to the cylinder housing or attached to the cylinder housing. The double diaphragm cylinder can, for example, be designed such that when compressed air is introduced into the first compressed air chamber, the first spring assembly is loaded and compressed by means of the diaphragm, so that the first push rod is pushed out of the cylinder housing against the restoring force of the first spring assembly to generate a braking force and / or braking effect, and that when the compressed air is released from the compressed air chamber, the diaphragm and the push rod are pushed back by the restoring force of the spring assembly to end the braking effect.The second cylinder housing part can include a second spring section and a second compressed air section, designed for filling with compressed air, wherein the second compressed air section is arranged, in particular, between the first cylinder housing part and the second spring section. The second spring section can include a second spring device, particularly as described herein, which can be activated in the stroke direction. The second compressed air section can have a second compressed air inlet for filling with compressed air. The second compressed air inlet can, in particular, be oriented radially.

[0027] The second spring section and the second compressed air section can be hermetically sealed such that the second spring assembly is compressed under load when compressed air is introduced into the second compressed air section, specifically by the displacement and / or reduction of the second spring section when compressed air is introduced. The double diaphragm cylinder can include a second pushrod, wherein the second pushrod contacts the diaphragm and is designed to be displaced in the stroke direction with the second spring section, such that the second pushrod is moved in the stroke direction when the second spring assembly contracts and extends, and the first spring assembly contracts when the second spring assembly extends, thus generating a parking brake force by means of the first pushrod.The second push rod can be oriented essentially along the displacement axis of the double diaphragm cylinder. The second push rod can be a piston rod. The second spring assembly can have the features, advantages, or embodiments disclosed above and below in relation to the spring assembly. Viewed in the stroke direction, the second spring assembly can contact and / or be attached to one end of the second spring section facing the second compressed air section, and contact or be attached to the cylinder housing at the other end.The double diaphragm cylinder can be designed, for example, such that when compressed air is introduced into the second compressed air chamber, the second spring assembly is loaded and compressed, thus pushing the second push rod back so that the first spring assembly is not loaded by the second spring assembly. Conversely, when the compressed air is released from the compressed air chamber, the second push rod is pushed forward by the spring force of the second spring assembly, thus compressing the first spring assembly and generating the braking effect. Advantageously, the double diaphragm cylinder can be configured to generate both a service brake and a parking brake braking force.In particular, the first spring device can be designed to automatically release a service brake when there is no compressed air in the first compressed air area, and the second spring device can be designed to activate a parking brake when there is no compressed air in the second compressed air area.

[0028] Advantageously, the spring assembly is at least partially, and in particular entirely, made of metal, with the first section of the spring assembly being made of metal. The spring assembly can, for example, be made of steel. Manufacturing it from metal can be advantageous for use in brake cylinders, especially in commercial vehicles. For example, a metal spring assembly can provide increased stability and / or reliability.

[0029] Advantageously, the spring device is manufactured section by section, in particular at least the first section, from sheet metal, with the subsequent sections also being manufactured from sheet metal. Manufacturing from sheet metal can enable a particularly space-saving design of the spring device, especially in the stroke direction. Advantageously, the ratio of the sheet metal's extension 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, and particularly preferably less than 0.05, with a lower limit of this ratio being particularly greater than 0.001, preferably greater than 0.005, and particularly preferably greater than 0.01. A ratio less than 0.3 (and preferably greater than 0.001) can enable a particularly space-saving design.A ratio of less than 0.1 (and preferably greater than 0.005) can also allow for weight and material savings while maintaining good stability. A ratio of less than 0.05 (and preferably greater than 0.01) can be particularly efficient in this regard.

[0030] Advantageously, in the unloaded state, the radial diameter of the spring assembly is to the stroke length of the spring assembly in a ratio of 0.5 to 5, preferably 1 to 3, and particularly preferably 1.1 to 2.0. This ratio advantageously allows for a particularly space-saving design. In particular, a ratio of 1 to 3 offers a particularly efficient combination of space savings and stability. A ratio of 1.1 to 2.0 can be especially advantageous for commercial vehicle brakes.

[0031] Advantageously, the radial diameter of the spring device is in a ratio of 0.5 to 20, preferably 1 to 10, and particularly preferably 2 to 8, to the spring travel of the spring device. This allows for a particularly good braking force to be achieved.

[0032] Advantageously, the spring device comprises 2 to 20, preferably 3 to 10, and particularly preferably 6 to 8, sections, wherein the sections are arranged one behind the other, particularly in the stroke direction, with the sections being, in particular, the first section and the subsequent sections. It has been found that 2 to 20 sections can generate good braking force. With 3 to 10 sections, a significant saving of installation space can also be achieved without compromising the required braking force. 6 to 8 sections can prove to be particularly efficient.

[0033] 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. The further sections can have a corresponding number of first and / or second subsections, in particular a number of subsections in the same range. In a conical embodiment, the number of subsections of the further sections can optionally vary, e.g., decrease with a smaller cone diameter. 2 to 20 subsections can be particularly well arranged in a brake cylinder. 3 to 10 subsections can provide a particularly good combination of stability and braking force. 4 to 8 subsections can be particularly advantageous in this respect, especially for commercial vehicle brakes.

[0034] Another aspect of the invention is a vehicle brake, in particular a commercial vehicle brake, with a brake cylinder as described herein. All the advantages and features of the brake cylinder can be transferred analogously to the vehicle brake and vice versa. The vehicle brake can, for example, be a disc brake, a floating caliper brake, and / or a drum brake.

[0035] Another aspect of the invention is the use of a wave spring, in particular a spring device as described herein, for a commercial vehicle brake. All the advantages and features of the brake cylinder and the vehicle brake can be transferred analogously to the application and vice versa.

[0036] Individual features and embodiments mentioned above can be combined with one another, and the advantages associated with each feature also apply to a combination of these features. Further advantages and features of the invention will become apparent from the following description of preferred embodiments of the subject matter according to the invention with reference to the accompanying figures. The following description serves only to clarify the invention and should not be interpreted as limiting the accompanying claims to any one of the embodiments. Individual features disclosed in the embodiments shown can also be used in other embodiments, unless this has been expressly excluded. The figures show Fig. 1 a sectional view of a brake cylinder according to a first embodiment of the invention, Fig. 2 a sectional view of a brake cylinder according to a second embodiment of the invention.

[0037] Fig. Figure 1 shows a sectional view of a brake cylinder according to a first embodiment of the invention. In this embodiment, the brake cylinder is a diaphragm cylinder. The diaphragm cylinder has a spring device 1 for generating a restoring force to release a brake in a stroke direction H of the brake cylinder, the spring device 1 being shown here in its unloaded state. The spring device 1 is arranged circumferentially around a displacement axis of the brake cylinder oriented in the stroke direction H. The spring device 1 has a first section 2 and several further sections 5. The further sections 5 are basically constructed analogously to the first section 2. The first section 2 has several first subsections 3 and second subsections 4 in the direction of its basic extent, which here runs in the circumferential direction U.The first subsections 3 each correspond to the antinodes of the ring-shaped first section 2, where the antinodes are deflected in the positive stroke direction H and can therefore also be called wave crests. The second subsections 4 each correspond to the antinodes of the ring-shaped first section 2, where the antinodes are deflected in the negative stroke direction H. Therefore, these antinodes can also be called wave troughs. The first section plane (not shown) corresponds in this example to a plane whose normal runs in the stroke direction H and whose edge runs in the radial direction R in this representation, with the first section plane being located in the center of the first section 2, namely exactly midway between the first subsections 3 and the second subsections 4, as seen in the stroke direction H.The first subsections 3 and the second subsections 4 are each elastically connected to one another by intermediate sections 6, which intersect the first section plane. Sections 2, 5 adjacent in the stroke direction H are in contact with each other, such that first subsections 3 and second subsections 4 of two adjacent sections 2, 5, arranged between two adjacent section planes 2, 5, lie directly opposite each other in pairs at the point of greatest distance from their section plane. Opposite first and second subsections 3, 5 touch each other in both the unloaded and loaded states (not shown here). The sections 2, 5 have a maximum radial extent in the radial direction R, whereby the maximum radial extent of successive sections 2, 5 is strictly monotonically decreasing in the negative stroke direction, or in this case, conically decreasing.In this embodiment, the diaphragm cylinder further comprises a cylinder housing 16, which includes a spring section 12 in which the spring assembly 1 is arranged, and a compressed air section 13. When compressed air is introduced into the compressed air section 13 through the compressed air inlet 15, a diaphragm 10 is advanced between the compressed air section 13 and the spring section 12 in the stroke direction H, thus compressing the spring assembly 1. This also advances a push rod 14, which in turn actuates the brake. When the compressed air is released from the compressed air section 13, the restoring force of the spring assembly 1 retracts the push rod 14 and releases the brake.

[0038] Fig. Figure 2 shows a sectional view of a brake cylinder according to a second embodiment of the 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, 31 are basically analogous to the one shown in Fig.The spring device 1 shown in Figure 1 is constructed as follows. The sections 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 sections 25 in the negative stroke direction H is strictly monotonically decreasing, or in this case, conically decreasing. The sections 35 of the second spring device 31, on the other hand, 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 section 22 in which the first spring device 21 is arranged, a second spring section 32 in which the second spring device 31 is arranged, a first compressed air section 23, and a second compressed air section 33.When compressed air is introduced into the first compressed air chamber 23, a diaphragm 10 is advanced in the stroke direction H between the first compressed air chamber 23 and the first spring chamber 22, thus compressing the spring assembly 21. This also advances a first push rod 24, which in turn actuates a brake. When the compressed air is released from the first compressed air chamber 23, the restoring force of the spring assembly 21 retracts the push rod 24 and releases the brake. The right-hand part of the double diaphragm cylinder, however, serves as a parking brake. This is not activated when there is compressed air in the compressed air chamber 33 and thus the spring assembly 31 is compressed.If, on the other hand, 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, which compresses the first spring device 21, pushes the first push rod 24 forward in the stroke direction H and activates the brake. Reference symbol list: 1 spring device 2 first section 3 first subsection 4 second subsection 5 further section 6 Intermediate section 12 spring range 13 Compressed air area 14 Push rod 15 Compressed air inlet 16 cylinder housings 21 first spring device 22 first spring area 23 first compressed air area 24 first push rod 25 sections of the first spring device 31 second spring device 32 second spring area 33 second compressed air area 34 second push rod 35 sections of the second spring device H Lifting direction R Radial direction U circumferential direction

Claims

[1] Brake cylinder for a vehicle brake comprising a spring device (1) wherein the spring device is a wave spring. [2] Brake cylinder according to claim 1, wherein the spring device (1) for generating a braking force and / or a restoring force for releasing a brake in a stroke direction (H) of the brake cylinder has at least a first section (2), wherein the first section (2) has a basic extent extending on a first section level, wherein a normal of the first section plane is aligned parallel to the stroke direction (H) or deviates from the stroke direction (H) by a maximum of 10°, wherein the first section (2) has first subsections (3) and second subsections (4) along its basic extent, wherein the first subsections (3) are spaced apart from the first section plane in the positive stroke direction (H) in the unloaded state, and wherein the second subsections (4) are spaced apart from the first section plane in the negative stroke direction (H) in the unloaded state, wherein the first and second subsections (3, 4) are designed to have a smaller distance to the first section plane in the loaded state while generating a spring force than in the unloaded state. [3] Brake cylinder according to claim 2, wherein the first section (2) comprises at least one intermediate section (6) which connects one of the first subsections (3) with one of the second subsections (4) and which intersects the first section plane. [4] Brake cylinder according to one of claims 2 to 3, wherein the first section (2) and / or one or more further sections (5) of the spring device (1) are designed as corrugated rings or ring discs, where the antinodes of the corrugated rings or ring discs correspond to the first and second subsections (3, 4). [5] Brake cylinder according to any one of claims 2 to 4, wherein the spring device (1) has at least one further section (5) corresponding to the first section (2), wherein the first section (2) and the at least one further section (5) are arranged one behind the other in the direction of lifting (H). [6] Brake cylinder according to claim 5, wherein the sections (2, 5) on the section planes have a maximum radial extent in a radial direction (R) perpendicular to the stroke direction (H), wherein the maximum radial extension of successive sections (2, 5) is monotonically decreasing in the positive or negative stroke direction (H). [7] Brake cylinder according to one of claims 5 to 6, wherein the sections (2, 5) on the section planes have a maximum radial extent in a radial direction (R) perpendicular to the stroke direction (H), wherein the maximum radial extension of successive sections (2, 5) is the same in the positive or negative stroke direction (H). [8] Brake cylinder according to one of the preceding claims, wherein the brake cylinder comprises two spring devices each according to one of the preceding claims, wherein the spring devices are spaced apart from each other in the stroke direction (H). [9] Vehicle brake with a brake cylinder according to one of the preceding claims. [10] Use of a wave spring in a brake cylinder according to any one of claims 1 to 8 for a commercial vehicle brake.

Images