Pressure container for storing pressurized fluids, and method for producing same

Abstract

The invention relates to a pressure container system (100) for storing pressurized fluids. A pressure container comprising at least one tubular hollow body (15) with a cross-sectional area and a longitudinal extension for receiving the fluid comprises an inspection device and a closable fluidic connecting means for fluidically connecting the interior of the hollow body to the area surrounding the hollow body. The hollow body is designed such that a section of the longitudinal extension of the hollow body adjoins another section thereof or another such hollow body. The pressure container additionally comprises at least one shape-securing element which is designed to fix the position of the two sections relative to each other, thereby forming a hollow body composite, wherein the at least one shape-securing element is at least partly arranged between the aforementioned adjoining sections without engaging into the fluid receiving volume of the two sections. The invention likewise relates to a method for producing an embodiment of the pressure container system, the shape-securing element of which is designed as a stabilizing strap (30a-30d).

Description

[0001] Pressure vessel for storing pressurized fluids, method for producing the same

[0002] The invention relates to a pressure vessel system for storing pressurized fluids according to the preamble of claim 1. The invention also relates to a pressure vessel system using such a pressure vessel and to methods for producing the pressure vessel.

[0003] In addition to cylindrical or spherical pressure vessels, there are also those formed by one or more tubular hollow bodies. These hollow bodies are deformed in such a way that sections are lined up next to each other, thus forming a compact package.

[0004] Tubular is understood here to mean an elongated hollow body whose length is significantly greater than the largest dimension of its cross-sectional area and whose cross-sectional area can assume various shapes, for example, an ellipse or a circle, or shapes in which the border line is partially straight. Accordingly, such a tubular hollow body can be defined by its length and its cross-sectional area. Cross-sections that are at least partially round or oval, or essentially rectangular, are also known, although an essentially rectangular cross-section can also be formed as a result of the juxtaposition of the hollow bodies.

[0005] For this purpose, the hollow body can have rigid, elastic or plastic walls, so that various deformations are possible to optimize the volume utilization.

[0006] To fill the hollow body with a fluid and to remove it, the hollow body has a closable connecting means for fluidically connecting the inner cavity of the hollow body to its surroundings, which includes, in particular, a consumer and a fluid supply source. The hollow body can be closed at one end or connected at both ends to devices for filling or removing fluid.

[0007] In addition to the actual pressure vessel, a pressure vessel system includes the necessary control devices, known in various designs, for monitoring and controlling the physical quantities required for safe storage.

[0008] In the following, the term pressure vessel shall include not only the hollow body containing the fluid but also those components which serve to ensure the stability of the hollow body as such and of the entire assembly, both during storage and during transport.

[0009] Such pressure vessel systems are used for the storage and transport of any fluid, in particular liquid, gaseous or supercritical hydrogen as well as natural gas. Pressure vessels for the storage of fluids below 200K are referred to as cryogenic pressure vessels. They are used, for example, in storage facilities, vehicles, ships and aircraft to store and transport liquid or gaseous fuel, such as natural gas or hydrogen. The fuel can be used to drive an energy converter, such as a fuel cell, a turbine or an internal combustion engine. Pressure vessel systems are also used to store pneumatic or hydraulic energy or, in conjunction with an actuator element, such as a piston, to perform process work or to influence fluid properties and reaction sequences, such asby means of high-pressure fluid atomization and distribution in combustion engines. Another use of pressure vessel systems is as buoyancy aids and capsules for underwater, earth exploration, and space facilities. The pressure vessel systems are designed, for example, for a working pressure of 5 bar, 10 bar, 100 bar, 200 bar, 350 bar, 500 bar, 700 bar, 1000 bar, or more. The pressure values ​​mentioned are frequently used nominal operating values ​​of the fluid to be stored; the pressure in the pressure vessel system can obviously assume any value between the minimum and maximum values ​​derived from the nominal operating value. Derivation regulations for the minimum and maximum values ​​can be found in the applicable standards, such as UNECE GTR13.

[0010] Fluids here are understood to mean gases, liquids and supercritical gases or liquids.

[0011] Depending on the application, type of fluid, required pressure and temperature, ambient conditions, available installation space and other conditions, the pressure vessel systems must meet different requirements, so there are very different pressure vessel systems and manufacturing processes.

[0012] For example, DE 102014 225 045 A1 discloses pressure vessels in the aforementioned operating range, which are classified as Type 1 to Type 5 based, among other things, on the structure of the wall and the pressure absorption capacity. The pressure vessels consist of a metal or a liner made of metal or plastic, which is surrounded by a composite material. The liner is intended to support the manufacturing process for the composite shell and also ensure the tightness of the wall of the pressure vessel. Pressure vessels made of a composite material without a liner are also known. US 2001 / 0004902 A1 discloses a pressure vessel in which a pipeline with an essentially rectangular cross-section is wound in a spiral or meandering manner. A filling device for the pipeline is arranged in the free center of the winding. As a result of the tight winding, the forces exerted on the wall by the pressure are absorbed by the adjacent sections of the pipeline.The inner and outer enclosure of the winding is realized by an inner and outer hoop, which consists of an inner metal ring coated with epoxy resin and outer carbon or glass fibers.

[0013] What the known designs have in common is that they each address individual aspects of pressure vessel design and manufacture, but do not result in sufficiently safe, easily manufactured, and efficient pressure vessels that are easy to integrate into high-volume applications. In particular, pressure vessels made of composite materials, which are generally preferred today due to their good volume and weight utilization, are sensitive to deviations from the safe operating range due to overpressure, excessive temperature, and external forces, as well as to negative pressure and low temperature, inverse operating loads, and significant temperature and pressure fluctuations.

[0014] There is therefore a need for an inherently safe, easy-to-manufacture and efficient pressure vessel that can be easily and safely integrated into a wide variety of installation spaces, even in high-volume applications.

[0015] Furthermore, the pressure vessel and a pressure vessel system using the latter must meet very high requirements regarding operational safety and robustness against external influences such as deformation and fire as well as aging due to corrosion and material fatigue.

[0016] Preventing deformation of the pressure vessel is particularly important when filling with a pressurized fluid, since the resulting geometry of the pressure vessel is in a precarious equilibrium during filling due to static and dynamic overdetermination, and known countermeasures against disturbances of this equilibrium are ineffective. Stabilizing the structure of the pressure vessel against unwanted deformation is desirable, for example, against the bulging of the vessel walls and stretching forces acting on the pipe at working pressure.

[0017] Especially for mobile applications, it is desirable to utilize available installation space and limit overall weight. At the same time, low system complexity and simple manufacturing should be achieved, and problems with sealing the connections between individual storage volumes should be avoided.

[0018] At the same time, there is also a need to divide the actual pressure vessel into a number of smaller pressure vessels in order to limit the amount and flow rate of the fluid escaping in the event of a defect and to comply with legal requirements by allowing smaller pressure vessels to be emptied by suitable safety devices in the event of excessive pressure or temperature and to minimize the effect of pressure vessel bursting, as described, for example, in the UN regulation for the approval of hydrogen-powered vehicles and their components, UNECE R134.

[0019] The object underlying the invention is achieved with a pressure vessel according to claim 1, its integration into a pressure vessel system according to claim 9, devices using the pressure vessel system according to claims 12 and 13, and a method for producing the pressure vessel according to claim 14. Related advantageous embodiments are described in the respective dependent claims.

[0020] The pressure vessel according to the invention comprises a tubular hollow body as described above in the prior art. This hollow body is defined by its cross-sectional area and length and encloses a fluid-absorbing volume. In the following, a section of the length of such a hollow body will be referred to as the "section of the longitudinal extension" or, for short, "section" to clearly identify this specific feature.

[0021] The pressure vessel according to the invention is formed by at least one such hollow body, the longitudinal sections of which are arranged in a row such that one section of the longitudinal section of the hollow body adjoins another section of the same or another hollow body, preferably of the same type. Multiple rows of sections with a variable floor plan of the pressure vessel are possible in various ways, for example, if one or more hollow bodies are wound or folded in a meandering manner.

[0022] Alternatively or additionally, a hollow body can have a collector from which at least two branches branch off. At least two such fork- or comb-shaped hollow bodies can be pushed into one another, so that the branches of both hollow bodies alternately adjoin one another. To form such structures, it is advantageous if the hollow body(s) is / are deformable.

[0023] Such designs can be achieved by determining the required design of the hollow body with regard to the position and extent of the required bends and / or branches as well as their spacing during the manufacture of the hollow body, or by using flexible hollow bodies so that the desired shape is only achieved during the manufacture of the pressure vessel.

[0024] Due to the various arrangements of the longitudinal sections of the at least one hollow body made possible in this way, a dense packing of the fluidically connected longitudinal sections with a polygonal, elliptical, or free-form outline is formed. A polygonal outline has three or more corners, whereby the corners may be apparently rounded due to their formation from one or more tubular hollow bodies. An elliptical outline also includes circular outlines as a special form of ellipse.

[0025] The plan view is understood to be the projection of the outer edge of the package onto the upper or lower plane bounding the package. For the purposes of the invention, it is possible, but not necessary, for both possible plan views to be dimensionally identical. For the sole purpose of differentiation, the side of the hollow body facing the plan view is referred to as the underside, and the side opposite the underside is referred to as the top side. For the purpose of clearly identifying planes and directions, the plan view is referred to as the XY plane of a Cartesian coordinate system, and the Z direction is perpendicular to it.

[0026] Depending on the desired storage volume and the available installation space for the pressure vessel, the storage volume can be manufactured in a single layer or in several layers arranged one above the other or next to one another. The layers can be designed differently, e.g., to adapt the geometry of the pressure vessel to the available installation space or to optimally integrate other components of the pressure vessel system into its geometry. Installation space within the meaning of the invention is understood to mean any space that can be assigned to a device within its external dimensions, regardless of whether the installation space is completely closed or open on one or more sides.

[0027] The inventive design of the pressure vessel allows not only the use of a single hollow body but also the connection of several such hollow bodies, preferably two, three or more of them, so that large-volume and geometrically complex shaped pressure vessels are possible. For better understanding, the following description of the invention refers, unless expressly stated otherwise, to one hollow body or its longitudinal extent, but can also be applied analogously to several of them. The pressure vessel according to the invention further comprises at least one shape-securing element, optionally several of them, which secure the shape achieved by means of the juxtaposition of the sections of the longitudinal extent of the hollow body and, in particular, prevent the pressure vessel from bulging towards the top or bottom.At least one shape-securing element and each additional element are arranged between two adjacent sections of the longitudinal extension and fix the position of the two sections relative to one another. For this purpose, the shape-securing element at least partially encompasses both sections or is connected to them. In a simple embodiment, these shape-securing elements are at least partially adhesively bonded, soldered, or welded joints of the adjacent sections, but can also be clamps or bands that alternately encompass the top and bottom sides of adjacent sections. Sufficiently rigid shape-securing elements, such as clamps, can be shaped in such a way that they simultaneously function as supports for absorbing and transmitting external forces. The shape-securing elements can also be realized by an organic structure or biological culture.When using biological cultures, e.g. fungal mycelium, it is advantageous that they can grow through narrow gaps and take on other functions, e.g. supporting structure, consolidation, buffering of external mechanical forces, heat protection. The manufacturing and post-treatment conditions required for the use of mycelium are known. The described shape-securing elements can also be used in combination with one another. Due to the shape and arrangement of the shape-securing elements between the sections of at least one hollow body, they are each fixed relative to the adjacent section. Unlike in the prior art, no special passages or openings are required in the hollow body to connect the components to one another. Such a connection of the sections to one another permits higher pressures, increases reliability and at the same time enables a very wide variety of geometries and thus applications.In particular, the upper and lower clasping of the sections proves to be a stable arrangement even for complex geometries.

[0028] The sections of the one or more hollow bodies connected by means of the one or more shape-securing elements are hereinafter collectively referred to as the hollow body composite.

[0029] Accordingly, in one embodiment, these shape-securing elements are band-shaped, referred to here as stabilizing bands. These secure the sequencing of the sections of the longitudinal expansion of the hollow body, thereby achieving the desired shape, by being interwoven with the tubular hollow body. The sections of the longitudinal expansion and the stabilizing bands are arranged in such a way that the position of the stabilizing bands relative to the top and bottom of the sections of the longitudinal expansion regularly changes. In addition to the variable possibilities for the design and insertion of the stabilizing bands during the process and depending on the shape of the hollow body, such a hollow body composite proves to be particularly stable.

[0030] The underside can be the side of a layer of sections of the longitudinal extension(s) in which the above-mentioned floor plan lies. The top side is opposite the underside. The terms top and bottom serve here merely as a reference to the shape of the hollow body for the purpose of unambiguous description. Evidently, when considering the design of the shape-securing elements and thus also the interweaving of stabilizing bands and sections of the longitudinal extension(s), it is irrelevant which of the two sides of a layer is referred to as the top and bottom. Likewise, top and bottom have no reference to gravity, but only to the floor plan. To clearly distinguish the top and bottom, those sections of the wall of a hollow body which connect the top and bottom are referred to as the "lateral wall".

[0031] If a height is described below with reference to the geometry of the hollow body, hollow body assembly, or pressure vessel system, this should be understood in the direction of the distance between the top and bottom of the hollow body. According to the illustrations in the figures, this distance lies in the Z-direction used there.

[0032] The interweaving is possible in various ways. In the densest interweaving, each stabilizing band alternates from one top side to the adjacent bottom side at each section of a longitudinal extension between the two adjacent sections. The adjacent stabilizing band alternates between the bottom side and the adjacent top side between the adjacent sections of the longitudinal extension. Alternatively, two or more stabilizing bands can be interweaved next to each other and in the same way. Alternatively or additionally, more than one section can be spanned above or below by one or more stabilizing bands. Alternation within the interweaving is also possible. The type and extent of interweaving depends, for example, on the material of the hollow bodies and / or the pressure of the stored fluid, as well as on the application of the pressure vessel and other factors.

[0033] In a further embodiment, supports are at least partially inserted between the sections of the hollow bodies, preferably between their lateral walls, to absorb and transmit external forces. Such forces acting on the pressure vessel from the outside must be determined depending on the use and the resulting available installation space, so that the required supports can be configured on this basis in terms of type, extent and position. The supports can extend between an upper and a lower stabilizing band, particularly when using stabilizing bands as shape-securing elements, but can also be distributed arbitrarily within the hollow body composite. The supports can be made of, for example, metal, fiber composite material, plastic, glass, ceramic, or organic material, e.g., bamboo or wood. The supports can be connected to other components, such as, for example,tension-absorbing casing, heat exchanger, permeate collection chamber explained below, and by means of these connections also form shape-securing elements.

[0034] If a pressure vessel has several layers of hollow bodies stacked on top of or next to one another as described above, these stacked layers can be connected to one another as a whole by means of the described stabilizing bands, or these layers can be connected to one another by means of additional stabilizing bands. The connection can also be made by means of stabilizing bands that comprehensively connect the entire stack on the outside and / or run within the individual layers and are optionally crossed with one another between them. Alternatively or additionally, the arrangement of the at least one hollow body interwoven with stabilizing bands can be designed, at least in sections, with a pressure-absorbing support and / or a tension-absorbing casing. The pressure-absorbing support is used, for example, in the region of the arrangement which is at least partially enclosed by the hollow body.For example, in a spiral arrangement, the pressure-absorbing support can be provided by a centrally positioned coil body that remains within the arrangement, or by the walls of a central module. The strength design of the pressure-absorbing support ensures the dimensionally stable compensation of the forces acting on it. Depending on the desired geometry of the pressure vessel, a coil body can also be used off-center and, if necessary, remain in the arrangement. The same applies to the use of multiple coil bodies, although the aforementioned arrangements are not limited to coiled hollow bodies.

[0035] The tension-absorbing casing of sections of hollow bodies connected with shape-securing elements consists, for example, of tension-absorbing bands or of several connected tension-absorbing parts, such as a frame or housing filled with clips or similar. For example, a housing for a triangular floor plan, for example, can be designed in such a way that it completely encloses the hollow body assembly and, due to its rigidity and strength, absorbs the forces caused by the internal pressure of the fluid stored in the pressure vessel parallel to the base area of ​​the pressure vessel. The tension-absorbing casing can be connected to supports in a force-absorbing manner and can be constructed in a single or multi-layer manner. The tension-absorbing casing is advantageously designed in such a way that failure of the casing due to a temporally extended course, e.g.characterized by an adjusted modulus of elasticity, a casing material with structural hardening upon stretching, a multi-layer structure with identical or different properties of the individual layers, and / or a noticeable change in measurable properties of the casing, e.g., frequency response, strain, deformation, electrical impedance. The change in the measurable properties is evaluated to control the safety devices, and the pressure vessel is relieved before final failure.

[0036] The following illustration uses a combination of the pressure-absorbing support and the tension-absorbing bands, without limiting the invention in this respect. For example, with a spiral geometry of the hollow bodies, it would be possible to use the tension-absorbing bands in the manner of an at least partial toroidal wrapping even without a pressure-absorbing support. The arrangement of the tension-absorbing wrapping is consistent with the direction of the forces acting from the geometry of the plan, essentially perpendicular to the outline of the plan, which forces are ideally to be compensated by tension-absorbing bands arranged in the direction of the force or acting vectorially superimposed in this direction. In the special case of at least partially elliptical and circular outlines, the resulting radial forces can be efficiently compensated with tension-absorbing bands in the circumferential direction.Particularly in the case of an at least partially polygonal floor plan, the outwardly directed wall(s) of the hollow body must be stabilized in their shape against the effect of the internal pressure by means of a suitable enclosure and, if necessary, in cooperation with the tension-absorbing bands. The outwardly directed wall of a hollow body is the straight wall close to the boundary line of the floor plan, to which no adjacent section of the previously described hollow bodies can be assigned and which therefore has no compensation for the pressure forces of the fluid resulting from an adjacent arrangement of the sections. The enclosure can, for example, be a force-absorbing ring or frame, a solid or, e.g.made of metal foam, a foamed body with a flat surface adjacent to the hollow body and a flat or profiled or at least partially curved outwards-facing surface, or another hollow body shaped similarly to the described body. This additional hollow body can be filled with its own fluid for additional purposes, e.g. as a buffer element against external forces or to contribute to the usable fluid volume of the pressure vessel. The enclosure can also be designed as a section-by-section enclosure and also in combination with the elements listed as examples and other elements. The properties of the body or hollow body, such as strength, rigidity, steepness of the curvature, adhesion or sliding properties of the surface, are optimized for optimal interaction with the tension-absorbing bands.In one embodiment, a sufficiently rigid design of the enclosure ensures that the forces emanating from the pressure vessel act on the tension-absorbing casing exclusively parallel to the footprint of the pressure vessel, which leads to reduced mechanical stresses in the tension-absorbing casing and thus to very good material utilization. For the purposes of the invention, the enclosure is regarded as sufficiently rigid if the ratio of the strains in the tension-absorbing casing caused by deformations of the enclosure to the strains in the tension-absorbing casing caused by the internal pressure of the hollow body composite in the X or Y direction is small. According to the invention, strains are relative changes in expansion with respect to a corresponding original expansion, and a ratio of these strains is to be regarded as small in particular if it is <0.5, preferably <0.2, more preferably <0.1, particularly advantageously <0.05. The requirement for the described pressure-absorbing support and / or enclosure and / or tension-absorbing enclosure as well as the optimal parameters therefor can be determined by computer-aided simulation or tests.

[0037] The terms "stabilizing bands" and "tensile bands" are defined broadly according to the invention. In addition to a substantially rectangular cross-section, the term also encompasses substantially square and round cross-sections, as well as fiber bundles and the like. Stabilizing bands include, for example, ropes, wires, flat woven bands, rovings, or other band-, strand-, or bundle-shaped connecting elements that are flexible for forming the intersections or coverings described above. Rovings are known for reinforcing highly stressed components and consist of a multitude of parallel filaments. The latter can be made of various materials.

[0038] The stabilizing bands or tension-absorbing bands can be made of metal, plastic, organic material, fiber or composite material, or a combination of these, or the materials can be combined with one another. Examples of fiber and fiber composite materials that are considered are carbon, glass, basalt, silicon carbide, aramid (e.g., Kevlar), polypropylene (e.g., Innegra), polyester (e.g., Vectran), polyethylene (e.g., Dyneema), organic fibers (e.g., silk), or synthetic resins (e.g., epoxy resin). The stabilizing bands are dimensioned in such a way that they exclusively transform the unstable equilibrium of the hollow body geometry caused by the static or dynamic overdetermination of the system into a stable equilibrium.The stabilizing bands can also be designed in such a way that, in the event of a failure of the tension-absorbing casing, they allow the geometry to expand, thereby reducing the pressure of the fluid in the pressure vessel. They also secure the hollow body assembly as such and thus significantly reduce the hazard potential of the pressure vessel. The tension-absorbing bands are dimensioned in such a way that they can compensate for the compressive forces of the hollow body(s) acting in the X and Y directions, or radially in the case of an elliptical outline, as well as the stretching forces resulting from bending of the hollow body(s).

[0039] Stabilizing bands within the meaning of the invention are those designs that are suitable for being interlaced and interwoven with the hollow bodies used in the manner described, and that absorb the forces that can act on the packing of the hollow body(s) as a result of the pressurization of the pressure vessel and its use, and that ensure the shape and tightness of the pressure vessel. The interweaving with stabilizing bands can also enable a certain relative movement of the shaped parts with respect to the stabilizing bands introduced as at least one entire assembly. The arrangement can also be reinforced against relative movement by combining the bands with the above-described adhesives, soldering, welding, clamping, or strengthening material, such as a resinified filler, mycelium.

[0040] According to various embodiments, a variety of pressure vessel geometries can be produced. For example, one or more hollow bodies can be wound around a central axis or deformed in a meandering or serpentine shape. The central axis can also be part of a central geometric body. Further diverse design options are permitted by hollow bodies that have a collector from which two or more branches branch off. Such a collector can, for example, be the connecting web of a comb-shaped hollow body, with the teeth of the comb being formed by the branches. The use of two or more hollow bodies of the same or different geometry multiplies the variability of the geometry of the pressure vessel and thus its adaptability to a wide variety of applications.

[0041] The hollow bodies themselves can be pre-formed with the desired geometry and / or can be deformable and can also have cross-sectional areas that allow the greatest possible volume utilization for the achievable storage volume. For example, the cross-sectional area of ​​the at least one hollow body can be substantially rectangular, at least in sections. According to the invention, a cross-sectional area is still substantially rectangular if two opposite sides of the cross-sectional area are straight and run parallel to one another, with a length that is greater than the distance between the two sides. It is irrelevant whether the other two sides of the cross-sectional area are curved or partially straight. Such a cross-sectional area can, for example, be a rectangle whose corners are rounded.The cross-sectional area can be prefabricated in this form or, as a result of the above-mentioned shaping of the hollow body, its longitudinal extension can be created by arranging the sections in conjunction with stabilization using stabilizing bands. Alternatively, ellipsoidal, e.g., round, cross-sectional areas can also be used, at least in some sections. The shape of the inner contour of the hollow body and the shape of the outer contour of the hollow body can be different, for example, in a combination of an oval outer contour with an ellipsoidal inner contour.

[0042] According to various embodiments, a hollow body can be made of metal, such as aluminum, magnesium, copper, titanium alloys, stainless steel or heat-treated steel, plastic, glass, organic material, fiber or composite material or a combination of these, e.g. glass fiber reinforced aluminum, e.g. Glare, and optionally with a surface coating, e.g. nickel, plastic. The hollow body itself can be dimensionally stable, at least in some areas, during or after production or flexible. The selection of the respective material takes into account not only the nominal pressure but also the interactions with the fluid to be stored and the environment. The hollow body can, for example, be produced seamlessly by drawing or extrusion or by roll forming or folding, e.g. for a multi-chamber cross-section or an at least essentially B-shaped cross-section produced from a strip, and closing the joint.A combination of materials in the form of a liner with a pressure-resistant casing that determines the geometry of the hollow body, for example made of a deformable plastic or metal, is also possible.

[0043] The surface of the hollow body can also be at least partially coated. The coating can be used to make the hollow body corrosion-resistant, to electrically insulate it, to impart special sliding or other properties to the hollow body, to glue, solder, weld, or process the hollow body in a later production step. In addition to preparing the surface of the hollow body (e.g., activating it or applying a primer), it is also possible to coat it with the functional material itself, e.g., adhesive or solder.

[0044] Advantageous dimensioning of the lateral wall of the hollow body takes into account the forces that vary in direction and magnitude along the circumference when pressure is applied, and adapts the wall thickness or material strength of the component absorbing the mechanical stresses along the circumference of the hollow body in such a way that the significant mechanical stresses within the wall are uniform. For example, it is intended to vary the wall thickness over the circumference of the hollow body in such a way that the wall thickness of the curved sections, the straight sections, and the transition areas, as well as the wall thicknesses of opposite sections, can differ from one another and can change discontinuously or continuously over the circumference. For example, with extruded, rolled, roll-formed, or folded profiles, variable wall thicknesses and material differentiations can be realized during the manufacture of the semi-finished product.It is also possible to change wall thicknesses by reworking at least some sections, for example to reinforce or strengthen transitions and pipe ends. It is also possible to locally change the strength of materials by adapted surface treatment, forming and tempering steps. Procedures for such optimization, which take into account not only the compressive forces acting on the hollow body but also the interaction forces with adjacent elements, are known to the person skilled in the art. Furthermore, and in particular when using spiral, braided, woven or non-woven hoses, e.g. made of metal, plastic or fiber materials, as pressure-resistant sheathing, it is possible to increase the strength of the pressure-resistant sheathing by changing the filament angle to the circumferential line along the circumference of the hollow body and by incorporating additional filaments running in the direction of the longitudinal extension in certain areas or by inserting patches, i.e.Patch-like or area-by-area reinforcement of the wall, preferably but not restrictively between the pressure-resistant casing and the liner, to adapt to the varying forces. The patches and their connection to the pressure-resistant casing are to be dimensioned in their overlap with the less stressed area in such a way that the shear forces acting between the patches and the pressure-resistant casing are absorbed and the patches can contribute to the compressive strength of the casing. In a particularly advantageous embodiment when using a spiral, braided, woven or non-woven hose as a pressure-resistant casing, the patches are part of a liner that defines the cross-sectional shape and can be manufactured, for example, by pultrusion. In one possible embodiment, the liner is a composite of a preferably elastic support structure that stretches the spiral, braided, woven or non-woven hose into the desired cross-sectional shape, e.g.made of plastic, fiber composite material, metal, and of a preferably closed sleeve, e.g. made of plastic, which ensures tightness. The elements of this composite can be arranged in certain areas in the cross-section of the profile, e.g. the closed sleeve can also incorporate the supporting structure into the formation of the tightness of the hollow body through a material transition. In one possible design, the angle of the fiber path of the spiral, braided, woven or scrim hose varies over its circumference in such a way that the angle of the filaments on the curved sides is small compared to the circumferential line, preferably 0° to 30°, and larger on the straight sides, e.g. 30° to 60°, and the filaments can thus absorb the tensile force in the circumferential direction that is higher on the curved sides than on the straight sides, with an optimal, constant filament cross-section.The angular variation of the filaments over the circumference preferably occurs continuously and is supported if necessary by local fixation of the filaments, e.g. partial bonding to the walls of the hollow body or by the structural design of the spiral, braided, woven or scrim tube, e.g. type of braid and distortion that varies over the circumference. The resulting reduced force absorption capacity of the spiral, braided, woven or scrim tube on the curved sides in the direction of longitudinal extension is compensated for by the filaments of the patches attached to the curved sides, which then preferably run in the direction of longitudinal extension. Patches can also be used at other locations on the hollow body that are subject to higher loads, e.g. bends, or pressure vessels, e.g. side surfaces. The design of the hollow body structure can be carried out by simulation or based on experimental results.

[0045] In an advantageous embodiment, the hollow body is designed as a flat tube. This means that its cross-sectional area has a significantly greater extent in a second direction of its extension, for example in the Z direction according to the figures described below, compared to its first extension perpendicular thereto, in this case in the Y direction. According to the invention, a cross-sectional area is designed to be substantially flat in particular when the extension in the Z direction is greater than 3 times, preferably 5 times, more preferably than 10 times, and particularly advantageously greater than 50 times the extension in the Y direction. The assignment to the Y and Z directions was chosen here solely for the purpose of clarity. Obviously, the designation can also be different, as long as the rectangular relationship between both extension directions is maintained.The flat design means that the majority of the wall is non-curved, and in this majority of the wall, the mechanical stresses within the wall are uniform, meaning that their variation, particularly across the wall thickness, can be considered negligible. This type of design enables the realization of thick-walled hollow bodies with predominantly uniform material utilization and thus also the use of the materials at higher working pressures than in previously known solutions, particularly for plastics and aluminum in medium- and high-pressure applications.

[0046] In a further embodiment, the wall of the hollow body has at least one recess or groove which runs in the direction of its longitudinal extent in order to reduce the wall stresses within the sides parallel to the XY plane, in particular near the surface of the wall facing the fluid. This at least one groove is narrower in its tangential extent than in its radial extent and can vary in these extents. According to the invention, radial is understood to be a dimension emanating from the central axis of the hollow body, and tangential is understood to be a dimension touching the radial dimension at the surface of the hollow body. The wall thickness, at least in a region having the groove, is dimensioned such that the groove and wall are functionally designed according to the description.

[0047] In a further embodiment, both of the above-mentioned embodiments, ie the flat design of the hollow body with the formation of at least one trench in the sides parallel to the XY plane, are combined.

[0048] In a further embodiment, the hollow body is dimensioned in its cross-sectional area such that, in the case of a wall which contains a pressure-resistant covering, e.g. made of rovings, the pressure-resistant covering can consist of a few layers, preferably only one layer, whereby the mechanical stresses within the pressure-resistant covering are very uniform and result in very good material utilization.

[0049] A hollow body can be dimensioned in its cross-section and wall thickness such that, in the event of a wall failure—i.e., a defect associated with an outflow of the fluid contained within the hollow body—it self-constricts, thereby limiting the fluid's outflow velocity. This self-constriction can be supported by an expansion of the adjacent hollow bodies as a result of the pressure difference between the hollow bodies caused by the defect.

[0050] In further embodiments, a hollow body can have internal partition walls and / or webs which extend at least partially along the longitudinal extent of the hollow body and, among other things, stabilize the hollow body. The partition walls or webs can also be dimensioned such that they support the outer walls of the hollow body, and in particular the straight sides, in absorbing the compressive forces. In conjunction with such partition walls or webs, the curved sides can also be multiple curved sides. Likewise, the partition walls or webs can be used in conjunction with suitable connections or closures to create a flow path with a forward and return path within a hollow body.

[0051] Surface structures formed on the inner surface of the hollow body, which can serve to swirl flows occurring in the hollow body, for example in the event of a leak or breakage of the hollow body, are also possible.

[0052] Alternatively or additionally, swirl structures can also be formed in the cross-section. For example, a hollow body can be designed as a multi-chamber tube. The internal structure of the hollow body can be designed essentially in the direction of flow of the fluid, such as as walls, or directionally neutral, such as as open-pore foam, and can at least partially contribute to absorbing forces. Such swirl and cross-sectional structures bring about a reduction in the maximum flow velocity or at least a partial self-closing of an outflow cross-section in the event of a defect in a hollow body due to a displacement of parts of the swirl and cross-sectional structures to the outflow cross-section caused by the flow and can be determined by computer-aided simulation or tests, depending in particular on the fluid and the pressure range for which the pressure vessel is designed.

[0053] Alternatively or additionally, cross-sectional tapers, i.e. locally limited reductions in the cross-sectional area, are possible for this purpose and can be calculated or experimentally designed. Cross-sectional tapers are also advantageous in areas where particular loads and external hazards to the hollow body are to be expected. In such areas, multiple and / or greater tapers can be arranged. For example, tapers and / or internal structures can be advantageous at the turning points of meandering hollow bodies or in the corner areas of hollow bodies wound into polygonal layers. The resulting free spaces between the sections of the hollow body can be used to introduce elements that further increase the strength in this area, e.g. through stabilizing material, clamps, wrappings or sheathing.Tapering can also be advantageous when connecting hollow bodies to collectors, adapters and connections in order to reduce the increased material stresses that may occur on the hollow bodies and / or to provide this area with additional clamping, wrapping or wrapping to increase the strength of the connection in a space-saving manner.

[0054] Such cross-sectional changes and structures within a hollow body are suitable for limiting the spread of a defect in the pressure vessel to a partial volume. They are preferably dimensioned such that, in addition, the pressure drop within the hollow body during filling and removal is negligible, but in the event of a defect in part of the hollow body, it is so limiting that the stored fluid is released with only a slight change in the local ambient pressure. Cross-sectional tapers can also be used to route lines, i.e. fluid or electrical connections, between the center and the outer area of ​​the pressure vessel within the flat envelope contour or to anchor fastenings within the flat envelope contour. Furthermore, the empty spaces in the pressure vessel created by the cross-sectional tapers can be used as vent openings for the spaces enclosed by the pressure vessels.

[0055] Furthermore, external elements which are attached to the pressure vessel or the

[0056] Pressure vessel systems can be assigned to pressure vessels, which are suitable for at least partially absorbing externally acting forces. These can completely or partially surround the cavity of the hollow body composite. Partial surrounding can, for example, take the form of a pressure-absorbing enclosure that at least partially covers several sides of the pressure vessel. Such pressure-absorbing enclosures can be containers that are deformable at least in sections and filled with an incompressible fluid. Such a fluid is able to distribute the force exerted by an intrusion body over a larger area, so that the intrusion pressure on the contour to be protected is small. Apparently, the deformability of the overall arrangement of incompressible fluid and its container is small enough to rule out local pressing through of the intrusion body onto the contour to be protected, in particular of a hollow body.At the same time, the container of the incompressible fluid should be able to absorb the thermal expansion of the incompressible fluid.

[0057] Force-absorbing elements can also be optionally or additionally incorporated into the hollow body, such as filaments surrounding the hollow body, which are aligned according to the force to be absorbed and arranged more or less densely. Elements that reinforce the hollow body, such as stiffeners arranged in its fluid-absorbing volume, for example, in the form of partition walls or webs, spring elements supported on the wall, or others, are also possible. Additional force-absorbing elements can also be integrated into the wall of the hollow body.

[0058] According to a further embodiment of the pressure vessel system, the control device, which serves to monitor and control physical variables of the fluid and / or the pressure vessel, is arranged within a layer of a shaped hollow body or within several layers of hollow bodies arranged one above the other, so that the hollow body(s) at least partially surround(s) the control device, preferably along the circumference of the component arranged there. According to a further, optimized embodiment of the pressure vessel system, the inventive design of the hollow body assembly allows for additional components of the pressure vessel system, such as energy converters and / or energy storage devices and / or other components, to be arranged within the hollow body assembly and thus protected.This particularly applies to sensitive equipment belonging to the environment of the pressure vessel system, which can thus also be arranged in the space surrounded by the hollow bodies in order to protect them from external influences, such as impact, shock. In particular, when the pressure vessel is used in conjunction with an electrolyzer, fuel cell, battery and / or electronics, the at least partial accommodation of these parts in the space surrounded by the hollow bodies can eliminate the need for additional protective components and result in an overall more favorable use of volume and material. The structure of the hollow body composite and its production described below supports the arrangement of the control device and any optionally addable further component within a distance between sections of the at least one hollow body.For this purpose, it is possible for the required distance during the deformation of at least one section to be made larger than a selectable extension depending on the shape of the control device and its components, so that the latter can be inserted into the distance. Analogously, one or more components can also be inserted. For this purpose, an additional distance can be formed between sections in the hollow body composite to accommodate the additional component, or the distance accommodating the control unit can be increased in accordance with the additional component to be inserted.

[0059] In particular, monitoring the fluid temperatures as well as the surface temperatures and surface forces of the pressure vessel is important for its use. Accordingly, in further embodiments, the pressure vessel can have arrays of sensors distributed on the surface of the hollow body, which serve to monitor a variety of surface temperatures and / or surface forces and / or deformations and which are operatively connected to the control device.

[0060] Such sensor arrangements are advantageously positioned so that the effects of excessive external temperatures and forces, as well as deformations of the pressure vessel, can be recorded with spatial resolution, making this information available for evaluation purposes related to the safety of the pressure vessel. In addition to the temperature and the acting forces and deformations, the internal and external pressure can also be measured, optionally with local differentiation. In various applications, the position of the pressure vessel system and the amount of fluid in the pressure vessel may also be of interest, and the pressure vessel system may be equipped with appropriate sensors and data processing systems.Optionally, the control unit can also be designed and configured to either acquire the data and transmit it to an external data processing unit, or to preprocess and transmit the acquired data, or even evaluate the data. Depending on the configuration, control signals for controlling the pressure vessel system can be generated based on the acquired data, either by the control unit or by an external data processing unit.

[0061] The sensors for determining the required data can be arranged on the hollow body and / or on the stabilizing bands and / or on the supports and enclosures, and / or on the tension-absorbing bands, whereby the stabilizing bands or the tension-absorbing casing, due to their arrangement in the pressure vessel, are preferably suitable for accommodating the sensors and regularly distributing them on the pressure vessel as well as for establishing the connection to the control device or to other components of the pressure vessel system.

[0062] Such additional components can, for example, be devices for setting and maintaining a defined temperature of the stored fluid. Heat exchangers, heating elements and / or radiation-absorbing layer materials can be used for active or passive cooling and / or heating of the fluid. For example, the pressure vessel can be at least partially combined with a heat exchanger or heating element, which, for example, supports the emptying of the pressure vessel. Optionally, the heat exchanger or heating element comprises expansion elements, such as embossings, meanders and recesses, to adapt its shape to the pressure vessel geometry that changes due to pressure and temperature changes. For example, the heat exchanger or heating element can consist of at least one coiled pipe whose heat-conducting contact surface to the pressure vessel is enlarged with at least one embossed metal and / or expanded metal.In another embodiment, a heating element can be designed as a heating foil, which is arranged between the sections of the longitudinal extension(s) and heats the pressure vessel in sections or evenly across its entire extension. In a further embodiment, the pressure vessel can be part of a cryogenic container, either alone or with another specified device, and can be surrounded by additional thermal insulation.

[0063] Further designs of the pressure vessel and / or additional components of the pressure vessel system may relate to the permeation of the fluid to be stored in the pressure vessel through the wall of the hollow body. In particular, the permeation potential, which varies in magnitude over the circumference of the hollow body, must be taken into account when carefully dimensioning the wall thickness of the hollow body. Thus, the permeation potential in the region of the adjacent sides of the hollow body(s) is considerably lower than the permeation potential of the surface portions of the hollow body facing the top or bottom of the pressure vessel, so that the wall thickness in the region of the adjacent sides of the hollow body(s) can be made thinner than is required in the region of the surface portions of the hollow body(s) facing the top or bottom of the pressure vessel to achieve low permeation.If the wall of the hollow body(s) is / are constructed from a combination of two, optionally more than two layers, the material combination of the layers can be designed such that a first layer limits permeation from the hollow body and a second layer is permeable to the permeate. Depending on the fluid and the materials used, said first layer can be the layer further inside or further outside in relation to the second layer. For example, in a wall design consisting of an inner liner and an outer pressure-resistant casing, the liner can limit permeation and, in contrast, the pressure-resistant casing can be permeable. Optionally, it is also possible for the liner itself to offer negligible resistance to permeation, with permeation being limited exclusively by the pressure-resistant casing.The described significantly uneven distribution of permeation resistance in the layer structure counteracts delamination of the individual layers in hollow bodies with multiple layers and enables the use of the pressure vessel without the minimum filling pressure required for many pressure vessels. This results in easier handling of the pressure vessel during use, greater robustness, and simplified manufacturing, commissioning, and maintenance processes. In particular, it is also possible to evacuate the pressure vessel, i.e., apply a negative pressure to reduce residual gas concentrations in the pressure vessel to negligible levels, thereby shortening cleaning, purging, initial filling, and inerting processes.

[0064] Reducing the permeation resistance of a structural element can be achieved, for example, by locally reducing the wall thickness or by perforating or microperforating the structure. In another embodiment of a permeable, pressure-resistant casing made of fiber composite material, the microperforation can be achieved, for example, by using a foamed resin. In another embodiment for a permeable liner, perforation can be created, for example, by a mesh or grid structure, and in particular by microperforation, for example, by subsequent laser contouring and / or by suitable selection and stretching of the material. Other material combinations in the wall to produce the desired degree of permeation are possible.

[0065] In a further embodiment, the pressure vessel is at least partially provided with a further casing which receives the permeate and supplies it for controlled processing.

[0066] In a further embodiment, the permeate can be collected in a low-pressure storage device, such as an absorber, a liquid organic hydrogen carrier (LOHC) or as a gas, and made available to the connected consumer in a controlled manner. Furthermore, this enclosure can also be designed such that it expands when a pressure vessel part bursts and absorbs at least part of the bursting energy through deformation. In a further embodiment, the devices for removing and storing the permeate are located in the center of the pressure vessel arrangement, optionally together with the elements for monitoring and control, and optionally also with other components of a device using the pressure vessel system, hereinafter also referred to as the surrounding device.

[0067] In various designs, depending on the respective application of the pressure vessel system, components of the surrounding equipment can form a functional and structural unit with the pressure vessel system. For example, components that serve to generate, store, or convert energy can form an energy module with the pressure storage system, which can be adapted to the respective application and integrated into it with little effort and, if necessary, can be replaced. Such additional components of a surrounding equipment can be an electrolyzer and / or a fuel cell, or a combination of both. A design of the pressure vessel system with an electrical energy converter and / or electrical storage can also serve as an energy module. For example, an energy module containing an electrolyzer or a combination of electrolyzer and fuel cell canwith a solar panel, which can form a structural unit with the energy module, and create a storage device for photovoltaically generated energy. An energy module containing a fuel cell can be designed in its interfaces to a vehicle such that it can be used to convert a conventional battery-electric vehicle to hydrogen propulsion by replacing the drive battery using the same vehicle interfaces. Further applications are possible and are described as examples in the figures.

[0068] In a further embodiment, particularly for pressure vessel geometries with at least partially non-parallel opposing side surfaces, those surfaces on which a tension-absorbing casing is arranged are structured at least in sections. The structuring can, for example, provide opposing surfaces that are parallelized at least in sections, have a defined surface roughness, or be structured in another way such that the static friction between the tension-absorbing casing and the structured surface of the hollow body composite is increased. In this way, with such special pressure vessel geometries, the position of the tension-absorbing casing is functionally secured according to the pressure range to be achieved and the stretching forces that arise during use.Such surface structures include serrated, stepped, ribbed, or combinations of different surface structures. Surface structures with smaller structures in the millimeter or micrometer range are also usable, whereby the respective material combination of the adjacent surfaces and the expected forces must be taken into account for the design of the structures.

[0069] In a further preferred embodiment, the enclosure, the stepped or ribbed surfaces, and the above-mentioned pressure-absorbing enclosure form functionally integrated elements in that one component comprises the three elements and at least one of the elements serves the three functions. In a further embodiment, the enclosure, the stepped or ribbed surfaces, and an additional pressure vessel volume located within the enclosure form functionally integrated elements in that one component comprises the three elements and at least one of the elements serves the three functions. Further combinations are possible.

[0070] In further embodiments, at least two of the functions pressure vessel, surface temperature detection, surface force detection, heat exchanger, heating element, supports, permeate collector, shock absorber, heat absorber, fastening and decoupling form at least one functionally integrated element.

[0071] The use of a heat exchanger also allows for monitoring the physical conditions of the pressure vessel. This allows the flow, pressure, and temperature values ​​prevailing in a fluid heat exchanger to be recorded and evaluated. In the event of a significant and predefined change, the safety system can be activated, for example, triggering a service alert or relieving the pressure vessel if necessary. The recording, evaluation, and subsequent steps can be implemented entirely or partially by the control device and / or an additional device that are communicatively linked to each other according to the interrelationship of their functions.

[0072] In a further embodiment, the filling and / or discharge line of the pressure vessel can comprise at least one element for actively expanding the fluid, such as an expander, turbine, or compressed gas engine. This element extracts a portion of the thermodynamic energy released from the fluid during filling and / or emptying of the pressure vessel and converts it into a form usable for other purposes. Thus, for fluids with a negative Joule-Thomson coefficient in the operating range, active expansion during overflow filling of the pressure vessel from a storage tank can be used for temperature management of the pressure vessel.

[0073] In a further embodiment, a heat exchanger is connected upstream and / or downstream of the element for actively expanding the fluid. In a further embodiment, at least one of the heat exchangers is connected to the heating, cooling, or refrigeration circuit of an external component. An external component is understood here to be a device that is not part of the pressure vessel system, but is at least fluidically connected to it.

[0074] In a further embodiment, the temperature of the pressure vessel (including the fluid contained therein) is regulated by means of devices for active fluid expansion, heat exchangers, heating devices, and connections to the heating, cooling, and refrigeration circuits of the surrounding equipment in such a way that the temperature cycles of the pressure vessel are minimized at a low permissible temperature level and heating or cooling power is provided to the surrounding equipment as needed. For example, when the pressure vessel is used as a cryogenic pressure vessel, the energy extracted from the fluid through active expansion can be returned to the cryogenic pressure vessel as heat to control the optimal operating temperature.A “permissible” temperature level is understood here to mean the temperature range in which the materials and components of the device concerned should be, particularly during their use, so that the properties and shelf life required for the application are guaranteed.

[0075] In a further embodiment, the pressure vessel system or the pressure vessel comprises fastening means designed for connection to an external device, in particular for fastening the pressure vessel to at least one external component. The fastening means and their connection of the pressure vessel system to the external component are designed such that the pressure vessel absorbs a force emanating from the external component.

[0076] In one possible embodiment, at least one fastening element is arranged in the center, i.e., the geometric center or center of mass of the pressure vessel. The latter variant has the advantage of better balancing the vertical forces. Deviations from the respective center are taken into account to the extent that a resulting less favorable force distribution by the fastening elements and / or the stabilizing components of the pressure vessel system described here and / or the situation in use compensates for or permits this. In a further embodiment, the fastening elements can be designed to be load-bearing, i.e., to absorb forces from the external component.For example, the connecting elements can be designed to be deformable and / or fail-safe, allowing relative movement between the pressure vessel and the external component when forces exceed a predefined limit value based on the load-bearing capacity of the pressure vessel or pressure vessel system. Depending on various parameters, such as the dimensions and weight of the pressure vessel system and the external component in which the pressure vessel system is to be used, connecting elements can alternatively be arranged both on the pressure vessel and on those components of the pressure vessel system that cannot be assigned to the pressure vessel.

[0077] The pressure vessel system, in its respective adapted forms, can be used for the storage of technical fluids such as compressed air, oxygen, carbon dioxide, nitrogen, welding gas, hydrogen, CNG (compressed natural gas), LNG (liquefied natural gas), ethanol or others. It can be combined with other storage devices such as conventional liquid and pressure vessels, caverns, chemically or physically acting absorber storage devices, and energy converters such as reformer systems, electrolyzers, fuel cells, internal combustion engines, turbines, compressed gas engines, heat generation systems, as well as energy generation and conversion systems and systems for the production, treatment and processing of technical fluids. The pressure vessel system can also be used for the storage of a working fluid, i.e. for the provision of pressurised energy, e.g. for pneumatically or hydraulically acting devices or process media for the respective application.

[0078] The pressure vessel can be used in stationary facilities, such as solar hydrogen converter modules, individual buffer or large storage systems and refueling, process and earth exploration systems, for the transport of fluids, e.g. with containers, tankers, trailers, wagons, ships, as well as in mobile systems, such as pressure accumulators, compressors, breathing apparatus, rescue equipment, lighters, scooters, bicycles and cargo bikes, pedelecs, motorcycles, wheelchairs, industrial trucks, cars, mobile homes and caravans, off-road vehicles, pickup trucks, vans, trucks, team vehicles and trailers, buses, rail vehicles, submarines, diving equipment, boats, ships, helicopters, small, large and hypersonic aircraft as well as spacecraft and stations. The pressure vessel can be permanently attached to the facility orbe connected to the system or can be connected to another pressure vessel system as a removable storage unit, as an extension storage unit, or as a reserve storage unit. For this purpose, the pressure vessel system has suitable connecting means.

[0079] The list provides an overview of the diversity of applications, but is not exhaustive. The flat design enables particularly advantageous application in plate-shaped construction elements, in particular for the use of the pressure vessel system according to the invention in or on buildings, such as noise and visual barriers, and building surfaces as well as, for example, on building roofs, in particular as a hydrogen-storing support element for solar or solar-hydrogen converter modules or as a replacement for elements of the outer skin of a building, such as pools, paths, parking areas, terraces, balconies, stairs, walls and roof surfaces. In the same way, the pressure vessel according to the invention can also be used in container floors, walls and roofs. In this case, the pressure vessel according to the invention can take on functions of the conventionally used elements such as, for example, covering, supporting structure, sealing and appearance.In addition to the space-saving installation, another advantage is that when the pressure vessel is used as an external building element, any permeating hydrogen can escape safely into the atmosphere. Not exclusively, but particularly when used as an element of a basin, the heat reservoir enclosed by the basin can be used to even out the pressure vessel temperature and the temperature of the fluid contained in the pressure vessel. In the same way, the pressure vessel according to the invention can also be used as a structural element in mobile applications, such as in vehicles, including as floors, walls, roofs; in ships, including for decks, walls and bulkheads; and in aircraft, including for intermediate floors, walls, wings and tail units, and in particular for the shell structures of flying wings. These applications are made possible by the particularly advantageous properties of the pressure vessel according to the invention with regard to burst resistance.

[0080] The hollow body(s) or the hollow body composite or the pressure vessel of the device according to the invention can be manufactured using known manual and additive manufacturing processes, e.g., 3D printing. The current state of the art in this field enables the production of undercutting and interlocking, but possibly not materially bonded, contours, as well as the combination of different materials to adapt to the desired function of the respective contours in a continuous production sequence. 3D printing is advantageous in that all elements of the pressure vessel and other elements of the pressure vessel system, i.e., hollow bodies, shape-securing elements, tension-absorbing casing, heat exchangers, permeate collection chamber, etc., can be produced in a monolithic composite despite their functional and structural differences, resulting in process reliability superior to other processes.The current state of the art has the disadvantage of still being insufficiently suitable for creating structures with properties comparable to fiber materials, and the still insufficient economic viability of these processes for high-volume applications. The description of the process according to the invention therefore focuses on depicting a manufacturing process that is already economically suitable for high-volume applications.

[0081] The inventive method for producing the pressure vessel system is characterized by the essential process steps according to claim 14. This relates to the special embodiment according to claim 2, which uses at least two stabilizing bands as shape-securing elements. The following exemplary description of the production is based on only one hollow body, but can also be applied analogously to two or more hollow bodies:

[0082] First, at least one tubular hollow body, optionally two or more, is provided, which is characterized by its cross-sectional area Q and its longitudinal extension L running perpendicular thereto. The hollow body is apparently designed for use as a pressure vessel and includes a sealable fluidic connection means. If multiple hollow bodies are used, they can be connected to one another by means of suitable connection means to form a common cavity.

[0083] The hollow body is deformed in such a way that a section of the longitudinal extent of the hollow body lies at a distance next to another section of the same or another hollow body of the same type. In the following, the two adjacent sections, regardless of whether the sections are assigned to one or two hollow bodies, are shortened and referred to as the first and second section for the purpose of differentiation, and the said shape-securing distance is referred to as the stabilization distance. If two hollow bodies are used, for example if they are deformed lying next to one another, the two hollow bodies can optionally be separated from one another by separating bands, at least during their deformation. One use of the separating bands is described as an example in the description of the method for producing a pressure vessel.

[0084] Subsequently, the mechanical connection is made by means of at least two stabilizing bands in such a way that the first stabilizing band is located on the upper side and the second stabilizing band is located on the lower side of the first section and that the position of each stabilizing band changes relative to the respective upper and lower side of the two sections by each of the two stabilizing bands running through the stabilizing distance between the two sections.

[0085] After the sections of the at least one hollow body are loosely interwoven with the at least two stabilizing bands, the pressure vessel is shaped using the stabilizing bands in such a way that the distance between the two sections is reduced to such an extent that the two sections adjoin one another without locally closing them, and that the stabilizing bands cross the sections.

[0086] The type and angle of the intersection have been described in detail for the device so that reference can be made to them.

[0087] Subsequently, the position of the two sections and the stabilizing bands are fixed relative to each other in order to stabilize the previously manufactured shape of the pressure vessel for its use.

[0088] To complete the pressure vessel system, a control device is established as a communicative connection to the pressure vessel. The control device serves, in particular, to monitor the fluid temperatures as well as the surface temperatures and surface forces of the pressure vessel and is accordingly connected to the sensors on and in the hollow body physically and / or via wireless data transmission. Like such control devices themselves, including the associated sensors, their data acquisition, processing, and forwarding are well known to those skilled in the art.

[0089] The integration of the control unit into the pressure vessel system and the establishment of the communicative connection can be inserted into the previously described process steps at various times. For example, the control unit can form the basis for the deformation of the hollow bodies, and the connection can be established at a later time. Other designs are also possible.

[0090] The design of a hollow body as a pressure vessel is determined primarily by the type of fluid to be stored, the maximum pressure expected or to be generated within the hollow body, and the temperature at which the fluid is to be stored. The necessary design specifications for this are well known to those skilled in the art and are specified by standards.

[0091] The same applies to the sealable fluidic connecting means with which the hollow body is fluidically connected to its environment, i.e. for the purpose of filling and removing the fluid.

[0092] The at least one hollow body is deformed in such a way that sections thereof lie next to one another. If two or more hollow bodies are used, sections of the same or a different hollow body can lie next to one another. The deformation can be achieved, for example, by winding one, optionally two or more hollow bodies already arranged next to one another, around a central axis or a central object. Folds, for example meandering or other folds, are possible, as are other embodiments. To form reversal or bending points, the hollow body can be designed with suitable tapers at the relevant points or can be provided with them during the deformation.

[0093] To mechanically connect the sections of the hollow body(s) using two or more stabilizing bands, the latter are interwoven with the tubular, deformed hollow body(s), as described above for the pressure vessel system, so that the sections are braced on both sides and local deflection of the pressurized hollow body from the manufactured shape can be reliably prevented. Depending on the size and desired geometry of the pressure vessel, the number, positions, and type of stabilizing bands can be freely selected; practical tests and computational simulations can be used for this purpose.

[0094] The connection between the hollow body(s) and the stabilizing bands can be achieved due to the stabilizing gaps existing between the sections at this point in production, through which the stabilizing bands can alternate between the top and bottom. The function of the stabilizing bands is, in particular, to secure the position of the hollow bodies relative to one another and, moreover, to create specific floor plan geometries using the hollow body sections. The following description of the invention based on a strictly evenly distributed and mutually perpendicular arrangement of both components represents only one embodiment of many different forms. The features of the pressure vessel and the method for its production can be applied analogously to other pressure vessel geometries.For the rectangular shape described above, for example, it may prove advantageous for the stabilizing bands of the finished pressure vessel to be substantially perpendicular to each other at the intersection points with the sections, whereby the angle between the centerline of the stabilizing band and the center axis of the hollow body can be measured. In other cases, the direction and distribution of the stabilizing bands can be adapted to suit very differently shaped hollow bodies, such as those with a polygonal or circular outline.

[0095] Alternative connection patterns are also possible, reducing the manufacturing effort without compromising the stability of the pressure vessel. For example, each stabilizing band, or less exposed stabilizing bands, can span two or three, sometimes even more, adjacent sections before the band passes through the stabilizing gap, depending on the plan geometry and the expected forces.

[0096] After the sections have been mechanically connected, the final shaping of the pressure vessel takes place by reducing the distance between the sections, preferably until they border one another. Obviously, to maintain the functionality of the hollow body, the shaping must be carried out in such a way and to such an extent that the sections are not closed, not even locally, for example where stabilizing bands engage or where other components of the pressure vessel system border a hollow body. This shaping is supported, among other things, by the pressure-resistant design of the hollow bodies, as this entails a minimum level of load-bearing capacity of the walls, even if they are designed to be malleable to a limited extent. According to one embodiment, the approach of the hollow bodies to one another can continue beyond the contact of the adjacent sections, so that the cross-sectional areas deform.Apparently, the functional necessity of an open passage along the entire hollow body represents the limit for the deformation of the cross-sectional area. Deforming the cross-sectional area into a rectangle allows for high volume utilization for fluid storage. The higher compressive strength of a cross-sectional area rounded at the points outside the adjacent walls of the hollow body compared to a perfectly rectangular cross-sectional area must be taken into account, so for an optimal design, the wall thickness must be varied around the circumference of the pipe wall. The optimal shape of the cross-sectional area and the circumferential profile of the pipe wall thickness with regard to compressive strength and volume utilization can be determined by simulation.

[0097] The shaping can optionally be carried out using the stabilizing bands by shortening their course within the "interweaving" of the pressure vessel. This is achieved by pulling on the sections of the stabilizing bands running outside the "interweaving" in the direction of their primary course through the interweaving. In this case, a substantially right-angled intersection between the sections and the stabilizing bands can be advantageous. In a further embodiment, the shaping can be carried out using special devices, which support the shortening of all stabilizing bands to the maximum length necessary in the interweaving, so that these, as in the aforementioned alternative, can be used to fix the created shape of the pressure vessel. The fixation can be achieved by a suitable connection of the bands to one another and / or by means of components that stabilize the pressure vessel.

[0098] In one embodiment of the method for producing a pressure vessel, two or more hollow bodies can be used, each comprising at least two sections. Each hollow body is deformed in such a way that both have a distance between their two sections such that a section of the first hollow body can be arranged in the distance between the two sections of the second hollow body. This can, for example, be two round or square-shaped spirals whose individual turns have the required distance. In the same way, two meander- or serpentine-shaped hollow bodies can be used which are identical or similar to one another in that the sections of the hollow bodies have the required distances for the sections of the other hollow body.Comb-shaped hollow bodies which have a collector from which at least two, optionally several sections extend and which have the required spacing, can also be used. The described spacing between the sections of the two hollow bodies allows both hollow bodies to be combined in an interlocking manner in a feeding movement, so that the sections of the first and second hollow body lie alternately next to one another, each with a stabilizing spacing set. With comb-shaped hollow bodies, it is also possible to braid a hollow body forming the pressure vessel using a tool which is also designed in a comb-like manner. The tool first clamps the stabilizing bands into a three-dimensional braid, into which the comb-like hollow body is then inserted and the tool is removed, whereby the comb-shaped hollow body takes over the clamping function of the tool.It is clear that in this case the distance between the sections of the comb-shaped hollow body inserted into the braid only needs to be spaced apart to allow insertion into the braid and this type of braiding can also be used with isolated linear hollow bodies. Depending on their shape, the feed movement of the hollow bodies after their deformation can take place in the X and / or Y direction, e.g. isolated or comb-like hollow bodies, or in the Z direction, e.g. spiral or meander-shaped hollow bodies. The combination of two hollow bodies enables various applications. For example, one end of the first hollow body can be fluidically connected to one end of the second hollow body and both of the remaining ends of the two hollow bodies, optionally only one of them, have the fluidic connecting means for filling or removing the fluid.Apparently, in the second case, the second, still open end is sealed fluid-tight. A permanently fluid-tight closure of an end can be achieved, for example, by welding, soldering, gluing, plugging, stretching, crimping, flanging, or folding this end directly or by using an additional closure element that can be adapted to the contour of the hollow body. Furthermore, the closure can be reinforced in its resistance to internal pressure and pressure cycles by embedding it in a pressure-resistant surrounding material, e.g., wrapping, clamping shoes, or potting.Particularly when the cross-section of the end to be closed deviates from a circular shape, the closure element can be designed such that it tightly encloses the outer contour of the hollow body and overlaps over a sufficiently long section so that the shear forces acting between the hollow body and the closure element as a result of friction are sufficient to compensate for the compressive forces acting on the closure element in the longitudinal direction of the hollow body and to reliably prevent the closure element from slipping. The described shear forces can be reinforced, supplemented, or replaced by shrinking and / or structuring the interacting surfaces of the hollow body and closure element to at least partially create a form-fitting connection and / or by a material-to-material connection such as welding, soldering, or gluing.The frictional and / or positive and / or material-fit connection can also ensure the tightness of the connection or the tightness of the connection can be created additionally or solely by sealing elements introduced on the front or circumference, e.g. O-ring, Z-ring, sealing lip, bellows. The introduced sealing elements and the surfaces of the hollow body or the closure element that interact with them are preferably designed in such a way that the pressing force of the interacting surfaces on the sealing elements increases with increasing internal pressure of the hollow body and their sealing effect is itself reinforced with the pressure load. The connection between the hollow body and the closure element can also be created in the same way as the connection between the hollow body and the closure element.In further embodiments, the hollow body is connected to a connecting element or another hollow body in such a way that the front ends of the hollow body itself can be closed as already described and the hollow body is provided laterally with a fluid connecting piece, which may extend through the hollow body and has flanges resting on the walls. In an advantageous embodiment, the walls of the longitudinally adjacent sections between the hollow body and the connecting element or between the hollow bodies are perforated to match each other, thereby establishing the fluidic connection. The perforation and any additional deep structuring of the wall surfaces can be incorporated into the walls of the hollow body, for example by means of mechanical, electron beam or laser drilling, and must be taken into account when dimensioning the wall thickness in this area.In this case, small-scale perforation is preferable to the formation of fluidic connections with a large cross-section due to the greater uniformity of the loads in the wall. The optimal dimensioning can be found through computer-aided simulation. A particular advantage of using the adjacent side surfaces as the fluid connection surface is that the pressing force required for tightness as well as all the elements required to absorb the forces between the adjacent sections are already present due to the design principle of the pressure vessel. In particular, when using hollow bodies that are suitably coated, e.g. solder-plated, adhesive-coated or sealant-coated, at least in this area, the connection that is fluidically tight against the environment can be manufactured integrated into the manufacture of the pressure vessel.Furthermore, with this type of connection, it is possible to establish a fluidic connection across several consecutively adjacent sections, thereby creating a collector integrated into the hollow body. The integrated collector can also be a hollow body that connects the perforations of the adjacent sections and is itself perforated. The fluid connection or connecting elements can be part of the winding body or the wall of the central module or a secondary module and the enclosure, or can be designed as adapters to common standard connections for pressure systems, such as welded connections, clamp connections, or conical screws. The distinction between central module and secondary module is made according to their arrangement in the pressure vessel system.According to the embodiment described above, the central module is surrounded by the hollow body assembly and, due to its design, is protected from external damage or influences, so that it also includes, in particular, sensitive control and monitoring devices. The secondary module, on the other hand, accommodates devices that cannot be arranged in the central module, for example, due to the available space for the pressure vessel system, and are less susceptible to external influences. The secondary module can therefore be arranged outside the hollow body assembly but with a functional and communicative connection to the pressure vessel system and the central module.

[0099] The shaping of the pressure vessel and the subsequent fixation can be carried out as described above using the stabilizing bands of both hollow bodies, which encompass the sections of the two hollow bodies in the XY direction and in the Z direction, respectively. The tensile direction of the stabilizing bands essentially coincides with that of the respective feed direction in order to allow both hollow bodies to interlock as closely as possible and thus achieve the desired optimal volume utilization. Alternatively, an external device can also be used. The interlocking feed in the XY direction or in the Z direction can be carried out using stabilizing bands, as described above for the shaping of the pressure vessel. The aforementioned correspondence of the directions "essentially" includes significant angular deviations at which the described result can still be achieved.Which angular deviations are included depends primarily on the plan geometry of the hollow body composite. Examples include deviations of up to + / - 15°, preferably up to + / - 10°, more preferably up to + / - 7°, and even more preferably up to + / - 5°.

[0100] In further embodiments of the method, a deformation of the hollow body can comprise a partial deformation of the sections of the longitudinal extension, for example in order to produce the internal structures and tapers described above for the pressure vessel, for example to influence the bursting behavior, or to optimize particularly stressed areas. For example, cross-sectional tapers can also be advantageous in areas in which the hollow body is to have a tight bend, e.g. in the formation of corners along the sections of the longitudinal extension. A taper can be produced, for example, by stretching a composite body with a moldable liner as the inner layer and a sheath as the outer layer, which circumferentially encloses the liner and determines the geometry of the hollow body. This meansthat the composite body is stretched in the direction of its longitudinal extension to such an extent that the composite body is tapered in one section without closing the hollow body there. The deformation of the hollow body can optionally or additionally also include a change in the cross-sectional area, which can be produced, for example, by inflation, compression, internal high-pressure forming, pressing, shrinking, or other suitable processes. For the sake of distinction, such deformation should be referred to as internal deformation. It can occur before or after the two sections are arranged relative to one another.

[0101] In further supplementary process steps, supports can be inserted between the sections of the at least one hollow body using stabilizing bands before the sections are connected. These can, for example, extend perpendicular to the floor plan and / or in a direction deviating from it.

[0102] They conduct forces acting from the outside through the sections and thus provide protection against damage to at least one hollow body.

[0103] Furthermore, the control device can be inserted within a distance between sections of the at least one hollow body, wherein said distance becomes larger during the deformation of the section than the extent of the control device. Thus, the control device can be protected and, if the shaping is carried out subsequently using stability bands, fixed by said bands. If a further component is inserted, said distance between the sections of the hollow body is visibly larger than the extent of the at least one further inserted component or the sum of both extents.

[0104] The pressure vessel is wrapped with tension-absorbing bands to compensate for the internal pressure acting on the sides located between the top and bottom, and in the case of curved sections of the hollow body, to compensate for the stretching forces. Additional devices arranged on the outer wall of the pressure vessel can be enclosed by the tension-absorbing bands or arranged outside the tension-absorbing bands. Such devices can be sensor arrays, the aforementioned heat exchanger, variable buffer volumes for absorbing fluid permeate in the event of a leak or rupture of the shell or wall of the hollow body, or other devices.

[0105] When using the pressure vessel as a cryogenic vessel, the previously described design of the pressure vessel and its manufacture allow the arrangement of a heating element on the pressure vessel after the deformation of the at least one hollow body such that the heating element can be in thermal contact, preferably in direct thermal contact, with the at least one hollow body. A heating element designed as a heating foil can be operated with an electrical power supply. In the case of a cryogenic pressure vessel, this is advantageously encased in thermal insulation, preferably a radiation shield vacuum insulation.

[0106] Coating the walls of the pressure vessel or the aforementioned tensile sheathing with a heat-absorbing layer is also advantageous. In addition to conventional insulation, an intumescent coating can also be considered as a heat-absorbing coating, which protects the vessel from sudden, high heat input. Such coatings form an intumescent protective layer with high thermal insulation capacity above a certain temperature increase. In another embodiment, flame-retardant thermal insulation materials can be used, such as cork, composites containing fungal mycelium, or others. Cork is characterized by high insulating capacity, high heat absorption, self-extinguishing through coking, high dimensional stability under heat exposure, and an excellent environmental impact.

[0107] The production of a possible embodiment of the pressure vessel according to the invention with an arrangement of two hollow bodies wound around a common axis, hereinafter referred to as the winding axis, is illustrated by the following process steps. To create further embodiments, process steps can be omitted, added, or interchanged in their sequence, and supplemented with quality assurance measures. The pressure vessel according to the invention is manufactured, for example, by performing the following sequential process steps:

[0108] Feeding a first and a second hollow body and a first and a second separating belt to a winding system, alternating layering of the hollow bodies and the separating belts,

[0109] Winding the layering onto a winding body that forms the center of the arrangement and defines the geometry,

[0110] Separating the hollow bodies by removing the separating bands,

[0111] Contouring of the hollow bodies, for example by internal high-pressure forming (other processes are possible),

[0112] Positioning of the hollow bodies true to shape with respect to the winding axis and angle around the winding axis but spaced apart from each other along the winding axis,

[0113] Inserting a first plane of stabilizing bands spaced apart and crossed between the spaced hollow bodies, displacing the two hollow bodies along the winding axis towards each other and beyond, so that the two hollow bodies are again spaced apart after the displacement, but with a substantially swapped position relative to the ground plan, and in conjunction with the introduced stabilizing bands, they span an open three-dimensional mesh (more details in the description of Fig. 5a, 5b and Fig. 6a, 6b),

[0114] Passing a second level of intersecting stabilizing bands between the spaced hollow bodies as well as between the spaced stabilizing bands of the first level of stabilizing bands,

[0115] Supplying the central module connected to a first heat exchanger and a group of supports with devices for monitoring and controlling physical variables and for temporarily storing the permeate of the pressure vessel,

[0116] Positioning the assembly in a form-true manner with respect to the winding axis and angle around the winding axis, but spaced apart from each other along the winding axis, moving the hollow bodies and the assembly along the winding axis into a common plane while simultaneously tightening the stabilizing bands, so that the hollow bodies with the inserted stabilizing bands form a closed three-dimensional mesh, but in the area of ​​the central module a one-sided two-dimensional mesh, the heat exchanger contacts one surface formed by the interwoven hollow bodies and the supports reach through between the hollow bodies and stabilizing bands,

[0117] Attaching the ends of the taut stabilizing bands to the assembly, pressure-tight connection of the outer ends of the hollow bodies,

[0118] Adjusting cycle stability by autofrettage,

[0119] Supplying and assembling a second heat exchanger,

[0120] Supplying and assembling a pressure-absorbing enclosure with integrated hydraulically acting force-absorbing elements for absorbing lateral forces, the fastening elements, the stabilising material and the monitoring devices,

[0121] Connecting the hollow bodies, heat exchangers and monitoring devices to the central module,

[0122] Wrapping the assembly with tension-absorbing bands in such a way that pressure relief, connection and maintenance openings for the central module as well as fastening elements remain free, but an otherwise uniform tension-resistant wrapping is achieved,

[0123] Strengthening the wrapping by resinifying, gluing or welding,

[0124] Feeding, assembling and sealing a permeate-tight enclosure with integrated fastening and deforming elements in the event of excessive force for integration into a surrounding facility,

[0125] Application of a heat-absorbing layer, such as intumescent foaming heat protection paint or heat protection film.

[0126] Deviations in the sequence are possible where a process step does not necessarily require the previous step. When using more than two hollow bodies, the layering and / or interweaving of the hollow bodies with the stabilizing bands can be achieved by repeating the corresponding process steps listed above.

[0127] The description was made for the case of winding the hollow bodies around a central winding axis, which is perpendicular to the plan to be formed or with deviations therefrom of up to 45°, preferably up to 50°, more preferably up to 55°, more preferably up to 60°, more preferably up to 65°, more preferably up to 70°, more preferably up to 75°, more preferably up to 80°, more preferably up to 85°. Analogously, the deformation of the hollow bodies, as explained above, can take place in a variety of other ways, so that as a result two or more, in particular a plurality of sections of the longitudinal extent of several hollow bodies adjoin one another. For the plan views of the arrangement of the deformed hollow bodies that can be achieved in this way, a reference axis can always be defined which, analogous to the above winding axis, is perpendicular to the plan and is surrounded by the sections. For example, this reference axis can be located in the geometric center of gravity of the plan.Other positions are possible for carrying out the method according to the invention. Regardless of the type of deformation of the hollow bodies, this axis shall always be referred to as the winding axis.

[0128] The invention will be explained in more detail below using exemplary embodiments. To develop further embodiments, one skilled in the art would combine the features described above and below, as far as they deem appropriate and helpful.

[0129] The drawings described below illustrate by way of example, ie without limiting the invention to this embodiment, a pressure vessel and a pressure vessel system for mobile hydrogen storage and show in

[0130] Fig. 1A to Fig. 1G show exemplary embodiments of the hollow bodies according to the prior art and according to the invention;

[0131] Fig. 2A, an exemplary embodiment of a form winding with two hollow bodies as the first manufacturing step of an exemplary manufacturing sequence;

[0132] Fig. 2B Section B - B of the form winding according to Fig. 2A

[0133] Fig. 3A to Fig. 10B show a continued exemplary production sequence for producing a pressure vessel according to the invention, wherein Fig. B in each case shows the sectional view according to section B - B of the respective associated Fig. A;

[0134] Fig. 11 shows an exemplary embodiment of a pressure vessel system for storing hydrogen in a vehicle;

[0135] Fig. 12A to Fig. 16 exemplary embodiments of the geometric shape for different uses.

[0136] The figures depict the features of the invention only schematically and to the extent necessary for their understanding. They make no claim to completeness or scale. For example, the plan view G is drawn larger than the actual projection of the winding of the two hollow bodies onto the XY plane for clarity. The size and spacing of various components also do not always correspond to the actual dimensions for a better overview of the figures.

[0137] Fig. 1A to Fig. 1G show examples of hollow bodies 1, hollow bodies 2 (Fig. 1E) and hollow bodies s (Fig. 1F, Fig. 1G). In the embodiments shown, the compressive strength in the X and Z directions is created according to the attached XYZ coordinate system by the casing 1a (Fig. 1A to Fig. 1D) and the walls of the tubes 2a (Fig. 1E), 3a (Fig. 1F, Fig. 1G). For elongated cross-sections, as shown in Fig. 1F and Fig. 1G, the hollow body is characterized by an upper side O and a lower side U lying parallel to the XY plane with respect to the XYZ coordinate system belonging to the two figures Fig. 1E and Fig. 1F, as well as by lateral walls S connecting the upper and lower sides. The liner 1b (Fig. 1A to Fig. 1D) serves to define the shape and stabilize the sheath 1a during production and can be changed in dimension and shape after slipping over the sheath 1a by stretching 1c (Fig. 1B) or widening 1d of the braid (Fig. 1B), e.g. by inflation.The sheath 1a forms, at least in sections, an empty pipe, for example a single-layer or at least partially multi-layered spiral, braided, woven, or scrim hose or the like, and can also be changed in diameter and shape during production of the pressure vessel by stretching 1c or compressing 1d (leading to widening of the braid). The texture of the spiral, braided, woven, or scrim hose or the like can vary in sections and also in layers. The terms spiral, braided, woven, or scrim hose are possible embodiments of how the forces acting in the circumferential direction and the direction of longitudinal expansion can be absorbed by the sheath in cooperation with the sheathed and surrounding components, but are not limiting.Laid-on tubes are known to those skilled in the art as consisting of a sheet-like structure formed by several superimposed layers of parallel, stretched filaments. The filament layers can have different orientations and / or different filament thicknesses.

[0138] In a further embodiment (Fig. 1C, Fig. 1D), the orientations of the filaments of the sheath 1a are adapted to the magnitude of the circumferential force and have a greater angular deviation from the circumferential line in regions with a lower magnitude of the force 1e acting in the circumferential direction than in regions with a higher magnitude 1f. Correspondingly, the liner 1b contains filaments 1g for absorbing the forces in the direction of the longitudinal extension of the hollow body 1. Furthermore, the liner 1b is thinner in regions with a lower permeation potential 1h than in regions with a higher permeation potential 1i. Furthermore, the liner 1b contains a spring element 1j for clamping the sheath 1a.

[0139] In a further embodiment, the covering 1a is composed of individual sections to form a possibly shaped hollow body into which the preferably flexible liner 1b is drawn.

[0140] In the simplest case, the pressure vessel can be formed by a tubular hollow body 2 (Fig. 1E) with a wall 2a. Intermediate walls 3b (Fig. 1F, Fig. 1G), which run, for example, parallel to the central axis M (Fig. 1A to Fig. 1G) of the tubular hollow body 1 (Fig. 1A to Fig. 1D) or 2 (Fig. 1E) or 3 (Fig. 1F, Fig. 1G), serve to stabilize the tube wall 3a (Fig. 1F, Fig. 1G) against collapse and contribute to the compressive strength and rigidity of the pressure vessel. In a further embodiment, the curved regions 3c of the tube wall 3a have a greater wall thickness than the straight regions 3d. In another embodiment, the transition regions between straight and curved sections are made thicker to absorb bending stresses (not shown). In another embodiment, the opposing sections are constructed with different wall thicknesses (not shown). These designs are examples.Further versions, including combinations of the versions shown, are possible.

[0141] Fig. 1 G shows the cross-section of the hollow bodies 1 used, indicating the essential parameters of the hollow body 1. For better clarity, these are not shown again in the following figures, but are also to be applied there according to Fig. 1G.

[0142] Fig. 2A shows an example of the form-winding of two formable hollow bodies 10a, 10b. A first hollow body 10a and a second hollow body 10b as well as a first separating band 4a and a second separating band 4b are alternately layered on top of one another (not shown). This layering is wound, optionally by means of a winding system, around a winding body 5 which forms the center of the arrangement and defines the geometry. The winding body 5 has, by way of example but not by way of limitation, a rectangular cross-section, so that the winding also has a rectangular cross-section. Fig. 2B shows the right-hand half of this winding as a section B-B, so that the alternating sequence of the two hollow bodies 10a, 10b, the separating bands 4a, 4b lying between them, and the central winding body 5 can be seen lying next to one another. To distinguish between the two hollow bodies, these are shown in Fig. 2A and Fig. 2B and in each further figure from Fig. 3A to Fig.10B is provided with different hatching. Other layer sequences and additional layers are possible. The cross-sections of the hollow bodies 10a, 10b are shown uniformly in the process variant shown, but can also be different.

[0143] In this and the subsequently described embodiments, the hollow bodies 10a, 10b or 11a, 11b or 12a, 12b have an oval cross-sectional area Q, as shown in Fig. 1G. Such a design of the hollow bodies supports dense packing and high volume utilization. Alternatively, other hollow body designs can also be used. The longitudinal extent L, running parallel to the central axis M of each hollow body 10a, 10b, is indicated by an arrow. As a result of the winding of the two hollow bodies around a quadrangular winding body 5, the hollow body has a rectangular plan view G (represented by a dashed line). According to the above definition of the plan view, this spans the XY plane, on which the winding axis W rests at a right angle, in the Z direction of the coordinate system used here. Relative to the XYZ coordinate system, the top side O and bottom side U are parallel to the XY plane. The statement “over” or"Below" refers to the Z-direction, in which the winding axis W runs in the illustration described here. According to the viewing direction of section B-B, the top side is visible in Fig. 2A, while in Fig. 2B the top side is "below." In each of the two windings, the sections of each longitudinal extension L are spaced apart by a distance A. The distance A is uniform in the process variant shown, but can also be different.

[0144] Fig. 3A and Fig. 3B show the separated hollow bodies 10a and 10b in plan view and in section B-B. For separation, the separating bands 4a, 4b (Fig. 2A) and the central winding body 5 are removed from the winding without dissolving it again. During the removal of the separating bands, the two hollow bodies 10a, 10b are separated from each other.

[0145] Fig. 4A and Fig. 4B show, in plan view and as a section B - B, examples of the contoured hollow bodies 11a and 11b, which have tapered portions 20, for example, distributed at the corners of the winding and along their longitudinal extents L. The hollow bodies 11a and 11b contoured in this way, for example by internal high-pressure forming, as well as the positioning of the hollow bodies 11a and 11b are true to shape with respect to the central winding axis and the angle around the winding axis, but spaced apart by the distance H along the winding axis. To distinguish the distance H from a later process step, this distance between the two hollow bodies 11a and 11b is defined as +H. This means that the underside U of the hollow body 11a and the top side O of the hollow body 11b are arranged offset from one another by the distance +H along the winding axis W.

[0146] Fig. 5A and Fig. 5B show, in plan view and as a section B - B, the insertion of a first layer of spaced-apart, crossed stabilizing bands 30a and 30b. The bands are arranged in the gap formed by the height difference +H between the contoured hollow bodies 11a and 11b, so that the stabilizing bands 30a and 30b run parallel to the top side O of the hollow body 11b and to the bottom side U of the hollow body 11a. Fig. 6A and Fig. 6B show, in plan view and as a section B - B, the insertion of a second layer of spaced-apart, crossed stabilizing bands 30c, 30d. These are also inserted into a gap between the two layers of contoured hollow bodies 11a, 11b.For this purpose, the two hollow bodies 11a and 11b are offset again along the winding axis W, so that the hollow bodies 11a and 11b, with the already introduced stabilizing bands 30a and 30b, form an open three-dimensional mesh with the two hollow bodies 11a and 11b now spaced opposite one another along the winding axis. In this method step, the sections of the first hollow body 11a are spaced opposite one another from the sections of the second hollow body 11b. This distance is referred to as -H to distinguish the direction from the previous distance +H. The amount of -H can differ from the amount of +H. This means that the top side O of the hollow body 11a and the bottom side U of the hollow body 11b are offset from one another by the distance -H along the winding axis W. A second plane of intersecting stabilizing bands 30c and 30d can be inserted into this distance.This can preferably be done in such a way that the latter lie between the spaced stabilizing bands 30a and 30b of the first layer.

[0147] In this process step, or optionally in another, a central module 40 can be positioned in the center of the winding. Such a central module 40 can, for example, have devices for monitoring and controlling physical variables (control device) and / or for temporarily storing the permeate. Other or further functions of the central module 40 are possible using suitable devices. Furthermore, in this phase of the process, supports 50 can be positioned, which are arranged in such a way that they can absorb external forces introduced into the pressure storage system. By way of example, but not by way of limitation, these extend parallel to the winding axis.

[0148] Fig. 7A and Fig. 7B show, in plan view and section B-B, the displacement of the two hollow bodies 11a and 11b, the central module 40, and the supports 50 (not shown in Fig. 6B, 7B, 8B, 9B, 10B as they are concealed by the stabilizing bands 30) along the winding axis W into a common position while simultaneously tightening the stabilizing bands 30a to 30d, so that the hollow bodies 11a and 11b, with the inserted stabilizing bands 30a to 30d, form a closed three-dimensional mesh. Apparently, the described insertion of the stabilizing bands 30a to 30d in the area of ​​the central module 40 results in a one-sided two-dimensional mesh. The supports 50 extend between the hollow bodies 11a and 11b and the stabilizing bands 30a to 30d. The tightened stabilizing bands 30a to 30d can now be attached to the hollow bodies 11a and 11b, and the outer ends of the hollow bodies 11a and 11b can be pressure-tightly connected.In the illustrated embodiment, the inner ends of the hollow bodies 11a and 11b are connected to the central module 40 by means of the closable fluidic connecting means (not shown), so that the now fluidically connected hollow bodies 11a and 11b can be filled and removed via the central module 40. Other designs of the closures and closable fluidic connecting means are possible.

[0149] Fig. 8A and Fig. 8B show, in plan view and as a section B-B, the hollow body composite 15 with the arrangement of the two hollow bodies 11a and 11b according to Fig. 7A, 7B after their final shaping. This can be achieved by pressure-assisted expansion of the hollow bodies 11a and 11b to form expanded hollow bodies 12a and 12b and / or by tightening the stabilizing bands 30a to 30d such that the distance between the hollow bodies 11a, 11b is reduced. When shaping by tightening the stabilizing bands 30a to 30d, the flexural rigidity of the hollow bodies 11a and 11b is such that the tightening of the stabilizing bands leads to the sections being brought closer together without significantly narrowing them. The flexural rigidity required for this can be determined by testing or computer-aided simulation.

[0150] After this step, the supports 50 (not shown in Fig. 8B because they are covered by the stabilizing bands 30) are located between the two widened hollow bodies 12a and 12b and between the two sets of stabilizing bands 30a to 30d, ie in the gaps of the produced mesh and can, in such an embodiment, absorb external forces acting in particular in the vertical direction, ie perpendicular to the base area.

[0151] Fig. 9A and Fig. 9B show, in plan view and as a section B-B, the completion of the hollow body assembly 15 of Fig. 8A, 8B with a pressure-absorbing enclosure 60 designed as a hydraulically acting force-absorbing element, which encompasses the mesh made of sections of the two expanded hollow bodies 12a and 12b and the stabilizing bands 30a to 30d. Furthermore, the hollow body assembly 15 can have a material 70, such as mycelium, that stabilizes the interior and partially or completely fills the remaining spaces. Furthermore, the hollow body assembly 15 can have fastening elements (not shown) as well as further monitoring devices (not shown) arranged outside the central module 40.

[0152] Fig. 10 shows the further completion of the arrangement of Fig. 8 with, for example, tubular heat exchangers 80a and 80b, which extend along the sections of the hollow bodies 12a, 12b, so that the heat exchangers 80a, 80b thermally contact the surfaces formed by the hollow bodies 12a and 12b interwoven with the stabilizing bands 30a to 30d. Subsequently, the following components, which are now functionally connected to one another, can be wrapped: hollow body composite 15, heat exchanger 80a, 80b, central module 40 with monitoring devices, pressure-absorbing enclosure 60 designed as a force-absorbing element, stabilizing material 70. The arrangement is enclosed, for example with a tension-absorbing enclosure 90a, 90b, in such a way that pressure relief, connection and maintenance openings for the central module 40 as well as fastening elements remain free, but an otherwise uniformly tensile-resistant enclosure is achieved.The tension-absorbing sheath can be formed using tension-absorbing bands. Finally, the sheath can be solidified by resinification, gluing, or welding. Alternative tension-absorbing sheaths for the assembly or at least for subassemblies thereof are also possible, as is a tension-absorbing sheath composed of parts.

[0153] Fig. 11 shows the pressure vessel system 100, which can be installed in a vehicle and is preferably intended for the storage of hydrogen, as a completed arrangement according to Fig. 10, as well as the devices contained in the central module 40 for monitoring and controlling physical variables and for temporarily storing the permeate 401 to 418. The arrangement is provided with a sensor matrix film for the spatially resolved detection of the surface temperature of the pressure vessel and externally acting pressure 101, as well as a casing for receiving the permeate 102, which is designed as a burst shock absorber 103 on the side facing away from the vehicle in such a way that the burst shock absorber 103 expands upon excessive release of fluid from the hollow bodies 12a and 12b, absorbing pressure energy and attenuating the formation of a pressure wave into the environment. The arrangement further comprises a heat-absorbing layer 104, such asintumescent, foaming heat protection varnish, which completely surrounds the arrangement. The permeate collection chamber 105 enclosed by the casing for receiving the permeate 102 further comprises a heat buffer (not shown), such as a phase change material, which is thermally contacted with the hollow bodies 12a and 12b. Fasteners 106, which deform under excessive force, are integrated into the casing for receiving the permeate 102 and are used to connect the pressure vessel system 100 to a surrounding device 500. The hollow bodies 12a and 12b are connected to the filling line by a check valve 401, to the withdrawal line by a shut-off valve 402, and to the blow-off line by an overpressure and overtemperature valve 403. The blow-off line empties via the blow-off opening 404. The permeate collection chamber 105 is also connected to the blow-off opening 404 via a pressure relief valve 405.During normal operation, the permeate pump 407 discharges the permeate at approximately ambient pressure from the permeate collection chamber 105 via the check valve 406 and feeds it to the low-pressure accumulator, such as an absorber, 408. The low-pressure accumulator 408 is optionally equipped with an electric heating element 409 for withdrawing the fluid. The filling and withdrawal lines are equipped with expanders 410a and 410b, which are controllable via a generator 411 and ensure the cooling of the expanding gas. The generator 411 transfers the electrical energy generated in this process to the surrounding equipment. Heat exchangers 412a and 412b are assigned to the expanders 410a and 410b, which thermally condition the fluid before and after expansion, respectively, as well as the fluid discharged from the low-pressure accumulator 408. The fluid thermally conditioned for withdrawal is adjusted to the discharge pressure of the pressure vessel system 100 via the pressure regulator 413 and fed to the connection of the withdrawal line 414.The pressure vessel system 100 is connected to the filling device of the surrounding device 500 via the connection of the filling line 415. The heat or cold supply of the heat exchangers 80a, 80b, 412a, and 412b can be controlled collectively by means of the heat or cold supply of the surrounding device 500 and individually by means of the valves 416a to 416d. The devices for monitoring and controlling physical variables and for temporarily storing the permeate 401 to 417 exchange signals and data with the control unit 418. The control unit 418 also exchanges signals and data with the surrounding device and generates instructions for implementing the operating strategy and safety functions for the devices 500 for monitoring and controlling physical variables and for temporarily storing the permeate 401 to 417.

[0154] Fig. 12A and Fig. 12B show an exemplary application of the pressure vessel system 100 according to the invention with a partially closed envelope geometry, as well as the adapted arrangement of hollow bodies 12, stabilizing bands (not shown), central module 40, secondary module 41, and tension-absorbing casing 90a in a floor assembly of a vehicle 510, respectively in sections B-B (Fig. 12A) and C-C (Fig. 12B). Here, the stabilizing bands and the tension-absorbing casing 90a are designed, by way of example, such that both legs of the partially closed envelope geometry are segments of the pressure vessel that are independently interwoven with the stabilizing bands (not shown) and surrounded by the tension-absorbing casing 90a, whereby the central module is relieved of the forces of the pressure vessel. The pressure vessel system 100 is connected to the front section 511 and the rear section 512 of the vehicle in a load-bearing manner. The drive motor 513 is located in the rear section 512.In addition to the devices for controlling and monitoring the pressure vessel, the central module 40 contains a fuel cell 514 and a battery 515. The auxiliary module 41 contains auxiliary units required for operation, such as voltage converters. A non-load-bearing design of the pressure vessel system 100 and its integration into the vehicle 510 is also possible. In particular, the arrangement can also be designed such that it can be used to convert a conventional battery-electric vehicle to hydrogen propulsion by replacing the drive battery using the same interfaces to the vehicle. Fig. 13 shows an exemplary application of the pressure vessel system 100 according to the invention with an elongated shell geometry, as well as the adapted arrangement of hollow bodies 12, stabilizing bands (not shown), auxiliary module 41, and tension-absorbing casing 90a in a scooter 520.The pressure vessel system 100 can at least partially take over the load-bearing function of the usually present step beam or replace it (not shown).

[0155] Fig. 14A shows an exemplary application of the pressure vessel system 100 according to the invention with a triangular envelope geometry, as well as the adapted arrangement of hollow bodies 12, stabilizing bands (not shown), central module 40, secondary module 41, and tension-absorbing sheath 90 in a bicycle 530. The pressure vessel system 100 can at least partially assume the load-bearing function of the conventionally present frame or replace it (not shown). The triangular shape means that special measures may be required to stabilize the pressure vessel system 100. This is because, without additional measures for the shape-stabilizing, tension-absorbing sheath 90 (Fig. 13B), especially when formed from tension-absorbing bands, the triangular shape does not provide sufficient support to compensate for the stretching forces of the wound hollow body(s) 12. The enlargement of the detail designated D in Fig. 14A according to Fig.14B shows, as an additional measure, a step 65 of the enclosure 60, whereby the step 65 provides the necessary support for the tension-absorbing sheath 90. Other surface structures for accommodating the tension-absorbing sheath 90 are possible as alternatives or in addition.

[0156] Fig. 15 shows an exemplary application of the pressure vessel system 100 according to the invention with a partially curved envelope geometry as well as the adapted arrangement of hollow bodies 12, stabilizing bands (not shown), central module 40, secondary module 41 and tension-absorbing casing 90a in a wing 540 of an aircraft. Fig. 15A shows a vertical section through a wing, Fig. 15B a strip-shaped section of a sectional view along the section line B-B shown in Fig. 15A. The pressure accumulator can be adapted, for example, to the shape of a boat hull in an appropriate manner. In such applications, the pressure vessel system 100 can at least partially take over the load-bearing function of the usually present stiffening structures or replace them (not shown). In such and other comparable applications, the surface structuring described for Figs. 14A, 14B, such asStepping 65 of the enclosure 60 (both not shown) are used. Fig. 16 shows an exemplary application of the pressure vessel system 100 according to the invention with a cylindrical shell geometry 551 as well as the adapted arrangement of hollow bodies 12, stabilizing bands (not shown), central module 40, secondary module 41, and tension-absorbing enclosure 90 in a cryogenic container 550.

[0157] Particularly in the case of elongated geometries as in Fig. 12 and Fig. 13, but also in the case of other geometries, it can be advantageous to form the hollow bodies 12a, 12b in a comb-like shape. It is also possible to assemble the hollow bodies 12 individually, i.e. without a fluid-tight connection to one another, into an arrangement interwoven with the stabilizing bands 30a and 30c, which are then connected to a fluid system using hollow bodies designed as collectors or are formed by means of at least one internal collector as described above, e.g. by perforating the adjacent walls (not shown). At least one collector can be integrated into at least one central module 40 or secondary module 41. In addition to the tension-absorbing casing 90 shown, the arrangement can be surrounded by a further tension-absorbing casing (not shown), preferably designed orthogonally thereto.The tension-absorbing sheath can be further impregnated with resin in such a way that the resin ensures the pressure-tightness of the connection points or the collectors and the hollow bodies 12. In this arrangement, the forces in the direction of the longitudinal extension of the hollow bodies 12a, 12b (X-direction of the hollow bodies) are absorbed by the tension-absorbing sheath 90b, and the forces in the X-direction of the collectors are absorbed by the tension-absorbing sheath 90a, so that the hollow bodies 12a, 12b and collectors are freed from these forces. This makes it possible to use simpler hollow bodies 10a, 10b and collectors optimized for absorbing forces in the Y and Z directions, such as those available, for example, with wound fiber composite profiles.

[0158] Pressure vessel for storing pressurized fluids, method for producing the same

[0159] List of reference symbols Composite pipe a Covering b Liner c Stretching d Compression e Area with low force in circumferential direction f Area with higher force in circumferential direction g Filaments h Areas with low permeation potential i Areas with higher permeation potential j Spring element Pipe a Pipe wall Multi-chamber pipe a Pipe wall b Intermediate wall, web Separating bands a First separating band b Second separating band Winding body 0 Hollow body 0a First hollow body 0b Second hollow body 0c Side walls 0d Curved walls 0e Stiffening 1 Hollow body contoured 1a First hollow body contoured 1b Second hollow body contoured 2 Hollow body widened 2a First hollow body widened 2b Second hollow body widened 5 Hollow body composite 0 Tapering 0 Stabilizing bands 0a First stabilizing bands b Second stabilizing bands c Third stabilizing bands d Fourth stabilizing bands Central module Secondary module Supports pressure-absorbing Enclosures grading stabilizing materialHeat exchanger a first heat exchanger b second heat exchanger tension-absorbing casing a first tension-absorbing casing b second tension-absorbing casing Pressure vessel 0 Pressure vessel system 1 Sensor mat 2 Casing for absorbing the permeate 3 Burst shock absorber 4 Heat-absorbing layer 5 Permeate collection chamber 6 Force-deforming fastening 1 Check valve filling line 2 Shut-off valve pressure vessel 3 Overpressure and overtemperature valve 4 Blow-off opening 5 Overpressure valve casing 6 Check valve permeate pump 7 Permeate pump 8 Low-pressure accumulator 9 Electric heater permeate accumulator 0 Expander 0a Filling expander 0b Withdrawal expander 1 Generator 2 Heat exchanger Withdrawal and filling line 2a Connection side 2b Vessel side 3 Pressure regulator 4 Connection withdrawal line 415 Connection filling line

[0160] 416 valves heat exchanger

[0161] 416a first valve heat exchanger

[0162] 416b second valve heat exchanger

[0163] 416c third valve heat exchanger

[0164] 416d fourth valve heat exchanger

[0165] 417 Heat exchanger connection

[0166] 418 control unit

[0167] 500 surrounding facilities

[0168] 510 vehicles

[0169] 511 front end

[0170] 512 rear carriage

[0171] 513 engine

[0172] 514 Fuel cell

[0173] 515 battery

[0174] 516 auxiliary units

[0175] 520 scooters

[0176] 530 bicycles

[0177] 540 wing

[0178] 550 cryogenic containers

[0179] 551 Envelope geometry

[0180] A distance

[0181] A' distance with A' < A

[0182] B Cutting plane

[0183] C cutting plane

[0184] D Detail

[0185] H Height offset

[0186] H+ Height offset first direction

[0187] H- Height offset opposite direction

[0188] L Linear expansion

[0189] M central axis

[0190] Q cross-section

[0191] O Top

[0192] U bottom

[0193] V Volume

[0194] S side wall

[0195] W winding axis

Claims

Pressure vessel for storing pressurized fluids, method for producing the same 1. A pressure vessel for storing pressurized fluids, comprising at least one tubular hollow body enclosing a fluid-receiving volume V, having a cross-sectional area Q and a longitudinal extent L for receiving the fluid to be stored, wherein the at least one hollow body has a closable fluidic connecting means for fluidically connecting the interior of the hollow body to its surroundings, wherein the hollow body is designed such that a section of the longitudinal extent of the hollow body, hereinafter also referred to as section, adjoins a further section of the same or another such hollow body, characterized in that the pressure vessel further comprises at least one shape-securing element, which is designed to fix the position of the two sections relative to one another, forming a hollow body composite having a floor plan G,wherein the at least one shape-securing element is arranged at least in sections between said adjacent sections without interfering with the fluid receiving volume of one or both sections.

2. Pressure vessel according to claim 1, characterized in that at least two stabilizing bands are arranged as shape-securing elements, which are interwoven with the at least two adjacent sections of the at least one tubular hollow body, wherein the stabilizing bands and the sections cross each other in that one stabilizing band runs from the top side of the first section between the sections to the bottom side of the second section and the second stabilizing band runs from the bottom side of the first section between the sections to the top side of the second section.

3. Pressure vessel according to claim 1 or 2, characterized in that a shape-securing element is an organic structure, in particular a fungal mycelium and / or at least one soldering point and / or adhesive point and / or welding point, the latter points directly connecting the walls of the adjacent sections to one another.

4. Pressure vessel according to one of the preceding claims, characterized in that the hollow body is designed as a flat tube whose cross-sectional area in a first direction has an extension which is greater than twice the extension in a second direction perpendicular thereto and / or that the hollow body has, at least in sections, a recess in its wall which runs parallel to the longitudinal extension L.

5. Pressure vessel according to one of the preceding claims, characterized in that the wall of the at least one hollow body has at least one element from the following list: scrim, braid, spiral hose, patch-like / regional reinforcement e.g. on curves, multi-layer wall, a deformable liner which is covered with a geometry-defining, deformable plastic or a geometry-defining metal, section-by-section reductions in the cross-sectional area, webs running at least sectionally along the longitudinal extent and stiffening this section, stiffening of the cross-section by internal transverse webs, superficial or cross-sectional swirl structures, external force-absorbing elements, varying wall thickness, perforation.

6. Pressure vessel according to one of the preceding claims, characterized in that the pressure vessel comprises pressure-absorbing supports or shape-securing elements which are designed as pressure-absorbing supports, wherein the supports are arranged between sections of the at least one hollow body and are designed to absorb external forces acting on the pressure vessel.

7. Pressure vessel according to one of the preceding claims, characterized in that the hollow body composite has a tension-absorbing casing and / or a pressure-absorbing enclosure, which are formed by bands and / or frames and / or housings.

8. Pressure vessel according to claim 7, characterized in that a surface of the hollow body composite, on which a tension-absorbing casing is arranged, has at least in sections a surface structure such that the static friction between the tension-absorbing casing and the structured surface of the hollow body composite is increased.

9. Pressure vessel system for storing pressurised fluids, comprising a pressure vessel for receiving the fluid to be stored and a control device designed to monitor and control physical variables of the fluid and / or the pressure vessel containing the fluid, as well as for filling and emptying the pressure vessel, characterised in that the pressure vessel is designed according to one of the preceding claims.

10. Pressure vessel system according to claim 9, characterized in that the pressure vessel system and / or a hollow body and / or the hollow body composite of the pressure vessel system has force-absorbing elements which are designed to at least partially absorb forces acting from outside on the hollow body or the hollow body composite or the pressure vessel system.

11. Pressure vessel system according to one of claims 9 or 10, characterized in that the pressure vessel system comprises at least one further component from the following list: electrical energy converter, electrolyzer, electrical storage, fuel cell, wherein the component is at least partially arranged within the pressure vessel system in such a way that it is at least partially surrounded by its hollow body composite.

12. Fuel-operated means of transport with a reservoir for storing the fuel, characterized in that the reservoir is designed as a pressure vessel system according to one of claims 9 to 11 and the hollow body assembly of the pressure vessel system is designed with a floor plan G such that at least the hollow body assembly, optionally including the control unit of the pressure vessel system, further optionally the pressure vessel system can be integrated into an existing installation space of the means of transport.

13. Structural element, in particular of a building or a container or a solar module or a liquid container, wherein the structural element is at least partially plate-shaped, characterized in that a pressure vessel system according to one of claims 1 to 11 is at least partially a component of the plate-shaped section of the structural element and at least the hollow body composite, optionally including the control unit, alternatively the pressure vessel system is plate-shaped with a height less than or equal to the thickness of the plate-shaped section of the structural element.

14. A method for producing a pressure vessel according to any one of claims 2 to 8, comprising the following method steps: Providing at least one tubular hollow body having a cross-sectional area Q and a longitudinal extent L, wherein the hollow body is designed for use as a pressure vessel and comprises a closable fluidic connecting means; Deformation of the at least one hollow body to form a floor plan G of the pressure vessel such that a section of the longitudinal extent of the hollow body is located at a distance next to at least one further section of the same or another hollow body, subsequently the adjacent sections of the longitudinal extent are shortened and Distinction between first and second sections and said distance is referred to as the shape-securing distance; mechanical connection of the first section to the second section by means of at least two stabilising bands designed as shape-securing elements in such a way that the first stabilising band lies on the upper side and the second stabilising band on the lower side of the first section and that the position of the second and, analogously, each further stabilising band changes relative to the respective upper and lower sides of the two sections in that the stabilising bands run through the shape-securing distance lying between the two sections; Shaping the pressure vessel in such a way that the distance between the two sections is reduced such that the two sections adjoin one another without locally closing the two sections, and that the stabilising bands cross the sections; and Fixation of the position of the two sections and the stabilizing bands relative to each other.

15. A method according to claim 14 for forming a pressure vessel system comprising at least two hollow bodies, comprising the following method steps for mechanically connecting the sections of both hollow bodies: Deformation of the at least two hollow bodies with respect to a winding axis located on the plan view G such that a section of the longitudinal extent of the first hollow body lies next to at least one section of the second hollow body while maintaining a shape-securing distance; Positioning the two hollow bodies in a shape-true manner with respect to the winding axis and the respective angle around the winding axis, but spaced apart from one another along the winding axis; Inserting a first layer of spaced and crossed stabilizing bands between the spaced hollow bodies; Offsetting the two hollow bodies along the winding axis relative to each other in such a way that the two hollow bodies are in a common position after the offsetting and the stabilizing bands run in sections between the sections of both hollow bodies.

16. Method according to claim 14 or 15 for forming a pressure vessel system comprising at least two hollow bodies, the following further method steps comprehensive: Continuing the displacement of the two hollow bodies along the winding axis beyond their adjacent position until both hollow bodies lie one above the other at a distance along the winding axis; - Inserting a second layer of spaced-apart and crossed stabilizing bands between the superimposed spaced-apart hollow bodies and between the spaced-apart stabilizing bands of the first layer; Offsetting the two hollow bodies along the winding axis relative to each other in such a way that the two hollow bodies are in a common position after the offsetting and the stabilizing bands of the second layer run in sections between the sections of both hollow bodies.

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