KR20010090714A - Hydrostatic pressure retainment system - Google Patents

Abstract

The pressure vessel includes a matrix structure extending in three dimensions. The matrix is subjected to hydrostatic (three-axis or three-dimensional) tensions that occur when sustaining the loading induced by the pressure of the compressed fluid stored inside a series of interleaved gaps at the contact points of the matrix. The fluid impermeable outer covering is surrounded by the matrix and kept adjacent. The pressure vessel may take an irregular shape. Moving devices, including the main trunk device, are provided for inlet and discharge of fluid. In the liquid state, the solid surface component is mounted on the matrix and turns into the solid state, fixing this component to the matrix by internal bonds.

Description

HYDROSTATIC PRESSURE RETAINMENT SYSTEM

To maintain the gas under high pressure, a vessel with a cavity with a spherical, cylindrical, elliptical, torus or composite outer wall should be used. There is the most effective form to withstand the tensile strength induced in the wall by internal pressure, but this is not the most effective structure possible. In addition, the conventional outer shell form does not effectively fit in the available space. There are many examples in the prior art in which internal supports of various structures are introduced into the interior of the pressure vessel to be suitable for non-general forms. However, all pressure vessels that are not common in the prior art share excess weight characteristics. All of this is heavier than the same general pressure vessels due to the inefficient use of structural materials. The present invention confers less weight than the same conventional pressure vessel processed from the same material.

Another disadvantage of conventional containers is that if the wall structure is damaged due to stress induced by pressure, the container will be greatly destroyed. Sudden release of compressed gas and wall debris can cause an explosion and have serious consequences for nearby people and equipment.

In prior patent application WO 97/27105, USSN 08592004, it may have a high pressure storage tank for gas, in particular comprising a reinforcing matrix disposed on the tank body and attached to its inner wall, said matrix of You can move 50%. However, high pressure storage tanks are difficult and expensive to manufacture and do not have sufficient strength to withstand the high pressures from these tanks.

A disadvantage of the aforementioned, non-patent invention of ERG Aerospace, which describes the use of DUOCEL open cell aluminum foam as an internal support inside an irregularly shaped pressure vessel, is that it is difficult to manufacture and is expensive and has high pressure associated with the tank. It does not have sufficient strength to withstand

Mannesmann AG patent WO98 / 33004 describes a container for storing a compressed gas surrounded by an outer metal wall in a hollow chamber with open-cell foam bonded to an outer wall. However, such a reinforcement container cannot withstand the pressure caused by the high pressure storage tank.

Homogeneous isotropic materials such as steel have mechanical properties, including tensile strength, which are the same in all points (homogeneous) and in all directions (isotropic). Thus, steel can sustain tensile strength at all three Cartesian axes simultaneously. In this way, however, the material is not usually used. Generally, materials are loaded in one direction (axial loading) or in two directions (planar loading). Some of the material capacity that can maintain loading is left unused, limiting structural efficiency. When tensioned, the filaments or fibers are subjected to axial loads. The capacity of the material to support the load in the other two directions is not used. The compressed gas storage pressure vessel in the form of a conventional shell is plane loaded. At all points of this wall, the material is stressed in two directions defined by the plane that abuts the outer surface at this point, as shown in FIGS. The capacity of the material to support the loading in the direction orthogonal to a given plane remains unused. In addition, axial and planar loading cause angular deformation in the material, which is a major cause of structural failure.

It is advantageous to load the material equally in all directions (hydrostatic loading, triaxial loading or three-way loading). The material is fully used under hydrostatic loading (or triaxial loading or three way loading) and there is no capacity not being used for further loading. This ideal condition does not cause any angular deformation. The absence of each strain imparts increased yield strength to the material at hydrostatic loading. Thus, a small volume of material is required to process the container, thus reducing the weight as compared to conventional outer shell pressure vessels. Pressure vessels are ideally suited for structurally hydrostatic tensile loading because the reacted fluid pressure is hydrostatic.

This structure takes the form of an inner matrix having a cavity for containing pressurized fluid. The matrix carries most of the pressure induced loading. A weakly stressed thin solid outer cover is attached to the matrix to retain the fluid. The ability of each part of the matrix material to support loading in one axis (worst case) or in three axes (best case) depends on the three-dimensional detail structure of the matrix.

One example of a matrix structure that realizes the properties required for the best matrix is a body made of a material having a series of spherical spaces interconnected at the point of contact. This contact point forms a hole, the size of the hole between adjacent spaces not exceeding more than 10%, preferably 5%, more preferably 2%, and!% Of the space surface area is advantageous. This matrix structure allows a significant amount of material to undergo hydrostatic (three-axis, three-dimensional) tension. This space is spherical in shape and formed in a similar size. This space is distributed evenly over the matrix and is oriented in the plane center three-dimensionally. Continuity is maintained at all three sizes. Hydrostatically optimally shaped structures impart ideal structural efficiency because most matrix materials can be placed under hydrostatic tensile load when used as internal matrix in pressure vessels.

8 is a photograph of a conventional foam. This support is a simple axial member overall due to the irregular structure and the absence of the cell walls. The form of this structure cannot effectively support the hydrostatic tensile load of the matrix material when used as the inner matrix in a pressure vessel.

Relative density is the volume percentage of the parent material in the total volume of the matrix. In the case of the best matrix form, the matrix intensity will change linearly with relative density. The density required is the ratio of the hydrostatic tensile strength (maximum pressure stored) to the hydrostatic tensile strength of the parent material, including design factors. The plane-centered three-dimensional orientation provides about 67% of the maximum gas capacity achievable for certain spherical space shapes. This is equivalent to a relative density of about 33%. Therefore, the matrix has about 30% to 35%, or about 2% to 30%, or about 35% to 50%, depending on the parent material and the packing method.

1 and 2, the volume of parent material required to process a conventional shell shaped spherical pressure vessel 10 is similar to the volume required to process a matrix type spherical pressure vessel 12. This is an approximation for a thin walled sphere.

Maximum stress: _I = σ ₂ = pr / 2t Shell thickness: t = pr / 2σ

Surface Area: S = 4πr ² Material Volume: small = St = 4πr ² pr / 2σ

small = 2 πpr ^{3 /} σ (eq.60)

Where: σ = maximum stress, parent material

p = maximum stored pressure

r = shell thickness

S = surface area

V _small = volume of shell material

For the matrix type spherical pressure vessel 12, the outer cover is not a critical load bearing structure and therefore cannot be considered. The volume of material required to form the matrix is the product of the spherical partial volume and the matrix density.

Sphere Volume: V _sph = 4 / 3πr ³

Thus V _small = 4 / 3πr ³ * p / σ = 1.33πpr ³ /σ(eq.62)

Where V _sph = volume of the spherical part

V _small = volume of matrix material

Comparing Equations 60 and 62 shows the material efficiency advantages. The optimal matrix structure can theoretically be improved by 33% for spherical shells. Examples show that improvement can be made by more than 20%.

3 and 4, the volume of parent material required to process a conventional shell type cylindrical pressure vessel 14 is equal to the volume required to process a matrix type cylindrical pressure vessel 16. This is an approximation for a thin walled cylinder and ignores the end closure. Hoop stress I is twice the longitudinal stress ₂ in all outer shell cylinders.

Max stress: max = σ ₁ = pr / t Shell thickness: t = pr / σ

Surface Area: S = 2πrl Material Volume: small = St = 2πrlpr / σ

small = 2πpr ² l / σ (eq.66)

Where: I = length of cylinder

For the cylindrical type pressure vessel 16 of the matrix type, the outer cover is not a critical load bearing structure and therefore will not be considered. The volume of material required from the matrix is the product of the cylinder volume and the matrix density.

Cylinder volume: _cyl = πr ² l

Thus: V _mmil = πr ² l * P / σ = πpr ² l / σ (eq.68)

Where: V _cyl = volume of cylinder

Comparing Eqs. 66 and 68 shows the material efficiency advantages. The optimal matrix structure can theoretically be improved by 50% for the cylindrical shell. An example shows that 40% or more can be improved.

The relatively thin, lightweight outer cover can be attached to the matrix or formed integrally with the matrix as a monolithic structure. For the purpose of analysis, the thin outer cover can be molded as a number of small, interconnected, circular plates. There may be circles with varying radii. The maximum radial size of this circle will be determined by the size of the matrix gap. Figure 5 shows a polygon with a circle with radius = a and the number of sides = n. The thickness of the outer cover required is a function of hydraulic pressure, allowable material stress and polygonal radial size. In polygonal plates the maximum stress is exerted on the outer edge of each plate, according to Roark's equation for stress and strain. The following data are obtained from Roark's number 20 in Table 26:

n 3 4 5 6 7 8 9 10 ?? β ₂ 1.423 1.232 1.132 1.068 1.023 0.99 0.964 0.944 0.75

Max stress: max = -β ₂ qa ² / t ² Thickness:

(eq.72)

Where: σ _max = maximum allowable stress

β ₂ = coefficient obtained from the table

a = radius of polygon

q = hydraulic

t = film thickness

This example shows the efficiency of a matrix pressure vessel. A circular polygon, with the number of sides = ??, radius = matrix space radius, has a β ₂ value = 0.75 and will be used as the worst case. Assuming a hydrostatically optimal matrix made of 6061 T6 aluminum with a pore size of 0.0625 inch radius and a yield strength of 40k psi: Thickness in formula 72 is summarized as q = 450 psi, 6k psi and 15k psi.

Solid surface components, such as outer covers, filling nozzles, and the like, may be monolithically formed or attached to the matrix.

This application is based on 60 / 095,509, filed with Robert J. Setlock, Jr., filed with the US Patent Office on June 8, 98, entitled "Fluid Static Pressure Maintenance System and High Strength Coupling Method."

The present invention relates generally to pressure vessels, and in particular to apparatus and methods for maintaining pressurized fluids within a three-dimensional structural matrix and for coupling these components to the matrix.

DETAILED DESCRIPTION OF THE INVENTION The present invention can be fully understood, with obvious knowledge of its features and advantages, in the following detailed description of the preferred embodiments shown in the accompanying drawings:

1 shows a spherical shell shaped pressure vessel showing two dimensional stresses exerted on the shell;

2 shows a matrix type spherical pressure vessel showing the matrix without the outer cover;

3 shows a cylindrical shell shaped pressure vessel without end closure, showing the two-dimensional stress applied to the shell;

4 shows a matrix type cylindrical pressure vessel showing a matrix without an outer cover;

5 shows a polygon with a circle with radius = a and the number of sides = n;

FIG. 6 shows a hydrostatically optimized shape showing uniformly distributed spherical gaps with adjacent gaps at each center point and small passages connecting each gap; FIG.

FIG. 7 shows a hydrostatically optimized form, showing the plane-centered cube orientation of the spherical gap.

8 is a photograph of a conventional foam;

9 is a sectional view showing a fluid static pressure retention mechanism constructed in accordance with the present invention;

10 is an enlarged view of part 12 of FIG. 10 showing a cross section of the main passage; And

11 is a cross sectional view through a matrix with a solid surface component showing penetration of the constituent material into the matrix;

According to the present invention there is provided a hydrostatic holding mechanism for a compressed fluid capable of withstanding high internal pressures. The pressure retention mechanism includes a matrix for supporting the load generated by the pressure of the compressed fluid. The matrix structure includes a body of material having a series of spherical spaces interconnected at the point of contact. This contact point forms a hole, the pore size between the contact spaces not exceeding 10% or more, preferably 5%, more preferably 2% and advantageously 1% or less of the space surface area. This matrix structure has the form of a closed open space such that a significant amount of material is hydrostatically (triaxial, three-dimensional) stretched. Such spaces are preferably spherical and compact. This space is uniform with respect to the entire matrix and is oriented in plane centered three dimensions.

This matrix is preferably metal, for example aluminum, steel, stainless steel.

The outer cover surrounds the matrix to store the compressed fluid inside the matrix. The outer cover has an inner side attached to the matrix outer boundary. The outer cover cannot penetrate into the fluid being stored and remains in contact with the matrix outer interface.

The means of movement is provided for releasing the fluid from the matrix to draw the fluid into the matrix.

Fluid static pressure retention mechanisms with closed spatial structures cannot be achieved by standard metal foam manufacturing techniques. This type of instrument can be made by using an investment casting technique that uses small, uniform spherical balls. For example, a gas-containing structure may prepare a molded outer skin of a metal similar to the inner matrix formed, form the inner matrix by coating beads of volatiles such as carbamide with powdered metal and then add the beads to the container. , And can be made by ensuring that there are tubes or manifolds that are processed into powder metal layers and that access the system. The unit is heated to about 200 ° C. which can cause the metal slurry to adhere while the carbamide beads are volatilized and discharged through the manifold. The 'green' container can be sintered in a high temperature furnace to provide a machined structure. Internally, due to the construction method, the cells are all spherical and the inner-connectors are compact and at the point of contact with the adjacent cells, this consists of a small interconnect and porous form between each cell, thus maximizing the strength of the entire matrix.

Adding organic spheres to the vat is best achieved by "blizzard" packing to reduce irregularities, but a simple single size cell structure will leave 67% of the volume empty as free space. This volume portion can be increased by using smaller size spheres that fit efficiently into the spaces between the different spheres. Experimental results show that the ratio of diameters is in the range of 7: 1 and 10: 1 and is optimized when the ratio of small spheres is 18-20%. Again using the "snowstorm" packing technique, the structure can be made quite uniform using the required size range and sphere ratio.

Another embodiment is to use a powder metal skin that can prevent all shrinkage problems.

The space between the spherical gaps oriented in the form of a plane-centered cube is the radius ratio d _small = d _large (√2-1), where d _small is the diameter of the small gap and d _large is the diameter of the large gap. can do. This type of process is repeated with smaller spherical gaps to form a lower density structure. Other manufacturing techniques include metal forming methods, such as those described in US Pat. No. 5,151,246, in the name of Fraunhofer-Gesellschaft, the contents of which are incorporated herein by reference. This method can be made to achieve the required structure, rapid prototyping technique and the like of the present invention.

6, 7, 9 and 10, a fluid static pressure retention mechanism for storing compressed fluid is shown at 20. A mechanism that weighs less than the same conventional pressure vessel processed from the same material includes a three-dimensional matrix 22 for supporting the load generated by the pressure of the compressed fluid. This matrix can be processed into a variety of materials and structures. Polymers, metals and composites can be used to form matrices of hydrostatically optimized forms. FIG. 7 shows a hydrostatically optimized form with the face-centered cubic orientation of a spherical gap, which is the preferred structure for realizing the present invention. Each cell is spherical in shape and evenly distributed throughout the matrix structure. Each cell 26 has a continuous wall 28 that completely encloses the space or gap 30 to contain the compressed fluid. These gaps 30 are connected to each other through relatively small openings or holes 32 in the cell wall 28. This hole 32 ensures a uniform distribution of the fluid throughout the matrix 22. The outer dimension limits of the matrix 22 define the outer boundary 34.

All parts of the matrix 22 are subjected to hydrostatic tension when supporting pressure induced loads due to the three-dimensional nature of the hydrostatically optimized form 24. This matrix 22 has a relative density of about 30% to 35% or about 2% to 30%, or about 35% to 50%, depending on the parent material and the packing method. However, a novel feature that weighs less than conventional pressure vessels is independent of relative density. The low weight characteristic depends entirely on the structural efficiency of the matrix form.

The outer covering 36 surrounds the matrix 22 and cannot penetrate the fluid to contain the compressed fluid inside the matrix 22. The outer covering 36 has an inner side 40 opposite the outer side 38. The outer covering inner surface 40 is attached to the matrix outer boundary 34. The outer covering 36 remains adjacent above the matrix outer boundary 34. The outer boundary 34 and the outer covering 36 can have any shape that can be considered. This is because most of the stress is supported by the matrix and partly by the outer covering 36 so that the hoop stress is no longer a limiting factor. Therefore, the outer boundary 34 structure may be symmetrical or irregularly shaped.

The outer covering 36 and the matrix 22 of the hydrostatic pressure retention mechanism 20 are formed to withstand the same hydraulic pressure with the same design factor and are made of the same parent material, the outer face 38 of the outer covering 36. It has a total structural mass that is significantly less than the overall structural mass of an equivalent conventional shell type pressure vessel having the same total volume measured for.

Movement means are provided for releasing the fluid from the matrix 22 and for introducing the fluid into the matrix 22. In particular, the moving means comprises at least one nozzle 42 attached to the outer covering 36. This nozzle 42 has an inner face 44, a penetrating orifice 46 that connects to the matrix gap 30. A network of main trunks 48 may be provided, in communication with nozzle orifices 46 and matrix gaps 30. 9 is a cross-sectional view of the main trunk line 48. This main trunk 48 comprises a smaller size and larger number of tubes 50 while advancing from the nozzle orifice 46 toward the matrix gap 30. This tube 50 includes a number of holes 52 for carrying the fluid, as shown in FIG. 10. The main trunk 48 collects fluid faster from the matrix 22 during discharge and speeds up the fluid flow through the system to distribute the fluid faster to the matrix 22 during inflow. The main trunk 48 and the matrix 22 can be machined into a single monolithic structure or it can be made separately. The main trunk 48 is made of another material that is attachable and compatible with the matrix 22 structure or made of the same material as the matrix 22.

When the solid outer covering 36 is not provided as a monolithically formed matrix portion, the new attachment device shown in FIG. 11 has a solid outer covering 36 or a solid surface component 54 outside of the matrix 22. It is adapted to integrally mount to interface 34. The outer covering 36 or component 54 is processed into the matrix 22 in the solid state when the component inner surface or the entire component 54 is in the liquid state. This component inner face is allowed to extend a predetermined distance 56 into the matrix 22. The components are solidified to fix the components to the matrix 22. Thus a strong internal coupling structure is formed. This economic attachment device can be used with irregular outer boundary structures. Application methods include, but are not limited to, potting, dipping, spraying, brushing and vacuum spraying to preserve. The outer covering should be thick enough to mechanically protect it from impact, penetration, and the like. Labels may be attached to provide information on material type, safety and instructions. The covering may have decorative properties and in some systems biologically suitable materials may be applied.

A method for maintaining fluid static pressure for storing compressed fluid is described. The method extends the matrix structure 22 to the outer boundary surface 34 in three dimensions; Surround the matrix 22 with an outer covering 36 through which fluid can pass; Attaching the inner surface 40 of the outer covering 36 to the boundary surface 34 of the matrix 22; Maintain outer covering 36 adjacent the matrix outer boundary face 34; Introducing a fluid under pressure into the matrix 22; To store the compressed fluid in the gap 30 inside the matrix 22; To store the compressed fluid inside the matrix 22 with an outer covering 36; Impart hydrostatic loading to the matrix 22 material by the pressure of the compressed fluid; Support loading under hydrostatic tension in all portions of the matrix 22 material; Discharging the fluid from the matrix 22.

Another procedure involves attaching the nozzle 42 to the outer covering 36 and connecting the matrix gap 30 and the orifice 46 through the nozzle 42.

Another procedure connects the nozzle orifice 46 and the matrix gap 30 with the main trunk 48 of the network structure; Distributes fluid to the matrix 22 through the main trunk 48 during inflow; Collecting fluid from the matrix 22 through the main trunk 48 during discharge.

Another procedure involves placing the outer boundary 34 of the matrix 22 and the inner surface of the component side by side when the inner surface material is in a liquid state; Impregnating the matrix gap 30 to a predetermined depth with an inner material; Changing the inner material to a solid state, thereby fixing the components to the matrix 22.

Another step involves forming the outer interface with an irregular structure.

Another step forms the matrix 22; Forming a matrix by using an investment process.

Another step involves forming the matrix 22: forming the matrix from Fraunhofer-type metal foams that are adjusted to open small pores between adjacent gaps.

Another step involves forming the matrix by using a rapid circular process.

As can be seen from the above detailed description, the present invention allows more efficient hydrostatic loading with less material to significantly reduce weight without introducing two-dimensional loading in relatively thick walls; It can take a structure with reduced symmetry to fit inside any given envelope without being limited to spherical, cylindrical, elliptical or toric shapes; Does not explode if the wall is structurally damaged; There is a need to provide a system for maintaining pressurized fluid, including a method for firmly attaching solid surface components to a matrix of all surface structures.

Although the invention has been shown and described in the preferred embodiments, those skilled in the art can make modifications that are functionally equivalent to the invention. For example, the fluid static pressure maintaining mechanism shown in FIG. 9 and described above is a rectangular parallelepiped. It will be appreciated that any form or structure, symmetry or asymmetry can all be used. Accordingly, it should be understood that the above detailed description of embodiments of the invention is provided by way of example only. Various modifications may be made to the structure without departing from the scope of the invention as set forth in the appended claims.

Claims (34)

In a pressure retention device comprising a matrix for supporting a loading caused by the pressure of a compressed fluid, the matrix structure consists of a body having a series of spherical gaps which are joined to each other at a contact point, the contact point forming a small hole and Pressure retaining device, in which the size of the hole between adjacent gaps does not exceed more than 10% of the inner surface area of the gap. 2. The apparatus of claim 1, wherein the matrix structure is spherical in shape and comprises gaps evenly distributed throughout the matrix. 2. The apparatus of claim 1, wherein the matrix structure consists of gaps of similar size. 2. The apparatus of claim 1, wherein the matrix structure consists of gaps in face centered cubic orientation. The device of claim 1, wherein the mass of material in the matrix is under tension selected from the group consisting of hydrostatic, triaxial, three-dimensional, or combinations thereof. The device of claim 1, wherein the pore size between adjacent gaps does not exceed at least 5% of the interior surface area of the gap. The device of claim 1, wherein the pore size between adjacent gaps does not exceed at least 2% of the interior surface area of the gap. The device of claim 1, wherein the pore size between adjacent gaps does not exceed 1% or more of the interior surface area of the gap. The method of claim 1, wherein there is an outer covering surrounding the matrix for storing the compressed fluid inside the matrix, the outer covering having an inner surface attached to the matrix outer boundary surface, and the other covering can penetrate into the fluid. And the outer covering remains adjacent to the matrix outer boundary. The device of claim 1 comprising moving means for introducing fluid into the matrix and for discharging fluid from the matrix. The apparatus of claim 1, wherein the apparatus is for storing compressed fluid. 2. The pressure maintaining device of claim 1, wherein the moving device comprises at least one nozzle attached to an outer covering, the nozzle having an inner surface, the nozzle having a through orifice connected to the matrix gap. 3. The device of claim 2, wherein the moving device comprises a main trunk of the network structure connected with the matrix gap and the nozzle orifice to distribute the fluid to the matrix during inflow and to collect the fluid in the matrix during discharge. Pressure holding device. The pressure retention device of claim 1, wherein the inner surface extends a predetermined distance into the matrix to fix the inner surface to the matrix. The pressure retention device of claim 1, wherein the outer interface structure is irregular. The pressure retention device of claim 1, wherein the matrix comprises a structural foam. The pressure retention device according to claim 6, wherein the matrix is a Fraunhofer type metal foam. A fluid static pressure maintaining device for storing compressed fluid, (a) a matrix for supporting the loading generated by the pressure of the compressed fluid, the matrix extending three-dimensionally to the outer interface, the matrix being a series of mutually bonded at the contact points to contain the compressed fluid Having a gap of, the gaps are connected for uniformly distributing the fluid, and all portions of the matrix are subjected to hydrostatic tension when supporting pressure induced loading; (b) an outer covering surrounding the matrix for storing the compressed fluid inside the matrix, the outer covering having an inner surface opposite the outer surface, the outer covering inner surface attached to the matrix outer boundary surface; The outer covering is incapable of fluid penetration and the outer covering remains adjacent to the matrix outer boundary surface; (c) a moving device for introducing fluid into the matrix and for releasing the fluid from the matrix, wherein: (d) The equivalent conventional shell type of the outer covering of the matrix and the hydrostatic pressure retaining device is formed to withstand the same hydraulic pressure with the same design factor and is made of the same parent material and has the same total volume measured against the outer covering outer surface made of the same parent material. A pressure holding device having a total structural mass less than the total structural mass of the pressure vessel. 19. The pressure maintaining device of claim 18, wherein the moving device comprises one or more nozzles attached to an outer covering, the nozzle having an inner face, the nozzle having a hole through which a matrix gap is communicated. 20. The pressure maintaining device of claim 19, comprising a main trunk of the network structure in communication with the matrix gaps and nozzle holes for dispensing fluid into the matrix during ingress and collecting fluid in the matrix during discharge. 19. The pressure maintaining device of claim 18, wherein the inner surface extends a predetermined distance into the matrix to secure the inner surface to the matrix. 19. The pressure retention device of claim 18, wherein the outer interface structure is irregular. 19. The pressure maintaining device of claim 18, wherein said matrix is a structural foam. 24. The pressure maintaining device of claim 23, wherein said matrix is a Fraunhofer type metal foam. In the fluid static pressure maintaining method for storing the compressed fluid, (a) extending the matrix structure to outer boundaries in three dimensions; (b) surround the matrix with an outer covering in which fluid cannot penetrate; (c) attaching the inner surface of the outer covering to the outer boundary of the matrix; (d) maintain outer covering adjacent the matrix outer boundary; (e) introducing the fluid into the matrix under pressure; (f) store the compressed fluid in a series of apertures interconnected at the points of contact within the matrix; (g) store the compressed fluid inside the matrix with an outer covering; (h) induce loading in the matrix by the pressure of the compressed fluid; (i) support loading with hydrostatic tension in all parts of the matrix; (j) a process consisting of discharging the fluid from the matrix. The method of claim 24, (a) attaching a nozzle to the outer covering; (b) connecting the matrix gap and the orifice through the nozzle. The method of claim 26, (a) connecting the matrix gap and the nozzle orifice with the reticulated edge; (b) distribute the fluid to the matrix through the trunk during inflow; (c) collecting the fluid from the matrix through the trunk during discharge. The method of claim 25, (a) arranging the outer boundary of the matrix and the inner surface of the constituent components side by side when the inner material remains in the liquid state; (b) injecting the matrix gap with the inner material to a predetermined depth; (c) converting the inner material into a solid state, and attaching this component to the matrix. 26. The method of claim 25, comprising forming an outer interface with an irregular structure. The method of claim 25 including forming a matrix from the structural foam. 31. The method of claim 30 including forming a matrix from the Fraunhofer type metal foam. A fluid static pressure maintaining device for storing compressed fluid, (a) a matrix for supporting the loading generated by the pressure of the compressed fluid, the matrix extending to the outer interface in three dimensions, the matrix having a gap containing the compressed fluid, and having The part is subjected to hydrostatic tension when supporting pressure induced loading; (b) an outer covering surrounding the matrix for storing the compressed fluid inside the matrix, the outer covering having an inner surface attached to the matrix outer boundary surface, the outer covering incapable of fluid penetration; The outer covering is kept adjacent to the matrix outer boundary; (c) a pressure retention device comprising a moving device for introducing fluid into and exiting the fluid from the matrix. A method of filling a pressure vessel including a fluid static pressure maintaining device with a fluid when pressure is applied, (a) a pressure vessel having a filling body and a tank body having at least two opposing inner walls defining an interior volume; And (Ii) a reinforcing matrix attached to the inner wall and disposed in the tank body, said reinforcing matrix structure consisting of a body having a series of spherical gaps joined together at a contact point, the contact point forming a small hole and between adjacent gaps. Obtain a pressure vessel with a fluid static pressure holding device whose pore size does not exceed at least 5% of the inner surface area of the gap, (b) partially filling the pressure vessel with a fluid under pressure. A method of storing a fluid under pressure in a pressure vessel including a hydrostatic pressure maintaining device, (a) a pressure vessel having a filling body and a tank body having at least two opposing inner walls defining an interior volume; And (Ii) a reinforcing matrix attached to the inner wall and disposed in the tank body, said reinforcing matrix structure consisting of a body having a series of spherical gaps joined together at a contact point, the contact point forming a small hole and between adjacent gaps. Obtain a pressure vessel with a fluid static pressure holding device whose pore size does not exceed at least 5% of the inner surface area of the gap, (b) placing the fluid under pressure in a pressure vessel; (c) allowing the fluid to remain in the pressure vessel when pressure is applied.