Self-cleaning pressure filling system

Abstract

The present invention relates to a pressure filling system (1) comprising a pressure filling tank (20) having a longitudinal axis (A), the pressure filling tank including a pressure vessel wall (22) having an inner surface (24) surrounding a cavity (26), and having an inlet section (12), a central section (14), and an outlet section (16) along the longitudinal axis (A); The pressure-fill system (1) includes a particle inlet (10) defining an inlet opening (28) in an inlet section (12) and a particle outlet (18) defining an outlet opening (30) in an outlet section (16); Here, a gas supply (44) opening into the cavity (26) at the inlet (12) is arranged to introduce a gas stream (2) into the cavity (26) in such a manner that the gas stream (2) rotates around the longitudinal axis (A) within the cavity (26).

Description

[Technical Field]

[0001] The present invention relates to a pressure filling system comprising a pressure filling tank having a longitudinal axis, the pressure filling tank including a pressure vessel wall having an inner surface surrounding a cavity, and having an inlet portion, a central portion, and an outlet portion along the longitudinal axis, the pressure filling tank including a particle inlet defining an inlet opening in the inlet portion, and a particle outlet defining an outlet opening in the outlet portion. The present invention also relates to a method of cleaning a pressure filling tank having a longitudinal axis, the pressure filling tank including a pressure vessel wall having an inner surface surrounding a cavity, and having an inlet portion, a central portion, and an outlet portion along the longitudinal axis. [Background technology]

[0002] The background to this invention is the pre-expansion of foamed particles using infrared radiation. In contrast to steam pre-expansion, this so-called dry expansion allows for relatively quick cleaning of the system, enabling rapid material changes. This type of pre-expansion unit is interesting in that the particles do not contain a blowing agent, as in EPP. To enable pre-expansion of such particles, an increase in the particle's internal pressure is required instead of a blowing agent. For this purpose, the particles are loaded with pressurized gas in a pressure-filling system. This is done in a process or pressure-filling tank, in which the gas pressure is gradually increased after the particles are introduced. This can be done with or without simultaneous heating of the tank interior. Depending on other factors, a process without heating can take several days. With heating, the process can be completed within a few hours. The loaded particles are then transported to a storage tank or stored in a process tank, where a constant elevated pressure is maintained, allowing the particles to be stored for longer periods. For further processing, the particles are transported to the pre-expansion unit. The transport must be relatively rapid to avoid a buildup of pressure within the particles. For this purpose, the conveying can also be carried out in a conveying line under increased pressure directly to a pre-expander. In a dry pre-expander, the particles are heated by infrared radiation and expanded to a predetermined size by increasing the internal pressure.

[0003] One problem with such foam particles is that they tend to adhere to the inner surface of the pressure vessel wall. As a result, particles can remain in the pressure-filled tank even after it has been emptied. This is particularly problematic before each material change. For example, when changing materials to change color or to particles with different dimensions or properties, the remaining particles can become clearly visible as foreign bodies in the finished foam product. For this reason, pressure-filled tanks must be cleaned before each material change.

[0004] Cleaning is performed by a cleaning lance, which is inserted through a cleaning port in the pressure-filled tank. Gas is blown into the tank under high pressure through the lance, and the lance is manually operated to remove particles from as much area of ​​the interior surface as possible. Summary of the Invention [Problem to be solved by the invention]

[0005] It should be noted that the present invention is not limited to applications in which the pre-expansion of the foamed particles is carried out by infrared radiation. This technology was mentioned at the beginning, since it was the driving force behind the present invention. However, the present invention can also be combined, for example, with subsequent steam pre-expansion. Against this background, the object of the present invention is to largely automate the entire cleaning process. [Means for solving the problem]

[0006] This object is achieved by a pressure filling system according to claim 1 and a method according to claim 20.

[0007] The present invention provides a pressure filling system of the type described above, in which a gas supply opening is provided into the cavity of the inlet section, the gas supply opening being configured to introduce a gas flow, preferably an air flow, into the cavity, the gas flow rotating about the longitudinal axis within the cavity.

[0008] The method according to the invention therefore comprises the step of introducing a gas flow into the cavity at the inlet section, the gas flow within the cavity being arranged to rotate about the longitudinal axis.

[0009] The present invention utilizes the geometry of a pressure-filled tank to provide a gas supply that is preferably located and configured in a fixed position relative to the pressure vessel wall, such that the gas flow moves from the inlet to the outlet along the inner surface while rotating about the longitudinal axis, thereby passing at a high relative velocity along the largest possible surface area of ​​the inner surface.

[0010] A pressure-filling system, as used herein, is understood to be a system specifically configured to supply gas under sufficient pressure. A pressure-filled tank, therefore, refers to a tank with sufficient pressure resistance. Currently, maximum pressures of 6 to 10 bar are common. When the term "pressure" is used or a value is indicated, this refers to an overpressure relative to atmospheric or air pressure. However, considering ever-larger particle volumes, much higher pressures, such as 50 bar or more, may be used in the future. A pressure-filling system must be configured to supply gas at a pressure of at least 1 bar, preferably at least 3 bar, and a pressure-filled tank must therefore be pressure-resistant to at least 1 bar, preferably at least 3 bar. To be able to withstand such pressures with a tank capacity of 200 liters or more, sufficient for production standards, the tank wall thickness should preferably be at least 5 mm, particularly preferably at least 8 mm. Alternatively and / or in addition to a thick wall, reinforcing elements, such as beads, folds, bands, or longitudinal ribs extending circumferentially around the container wall, are preferred.

[0011] Preferably, the pressure-filled tank comprises a maximum internal cross-sectional area at its central portion perpendicular to its longitudinal axis, in other words, the pressure-filled tank is thickest at its central portion.

[0012] Furthermore, the central portion is preferably cylindrical, which is particularly preferred from the viewpoint of manufacturing technology.

[0013] The inlet section preferably comprises an internal cross-sectional area perpendicular to the longitudinal axis, which cross-sectional area increases continuously from the inlet opening to the central section along the longitudinal axis. In other words, the inlet section preferably widens in a funnel-like manner from the inlet opening to the central section along the longitudinal axis. A particularly preferred embodiment of the funnel-shaped widening inlet section is a conical widening.

[0014] The outlet section therefore preferably comprises an internal cross-sectional area perpendicular to the longitudinal axis which decreases continuously from the central section to the outlet opening along the longitudinal axis, in other words the outlet section preferably tapers funnel-like, or in a particularly preferred embodiment conically, from the central section to the outlet opening along the longitudinal axis.

[0015] A cylindrical central section and a conically widening inlet section and a conically tapering outlet section are preferred for manufacturing reasons because these simple shapes can be produced using simple tooling and blanks made from sheet material.

[0016] The inner surface of the inlet section also has a maximum funnel opening angle β plotted against the longitudinal axis. e ≦45°, preferably β e It is advantageous for the inlet section to have a minimum funnel opening angle β ≦35°. A large funnel opening angle means that the cavity expands too quickly at the inlet section. As a result, the gas flow introduced into the cavity is not deflected sufficiently tangentially to the longitudinal axis, which adversely affects the formation of swirl flow. Furthermore, the inner surface of the inlet section preferably has a minimum funnel opening angle β , plotted against the longitudinal axis. e ≧20°, preferably β e ≥ 25°. A small funnel opening angle excessively limits the volume of the pressure-filled tank for a given overall length.

[0017] The inner surface of the outlet section also preferably has a maximum funnel opening angle β plotted against the longitudinal axis. a≦45°, preferably β a Similar considerations as for the inlet section apply here, and the maximum funnel opening angle at the outlet section may preferably be configured somewhat more acutely to take into account the weakening of the gas flow caused by wall friction in the direction of the outlet section.

[0018] The maximum funnel opening angle is understood to be the maximum angle at which a tangent in a radial plane covers the inner surface of the inlet or outlet section plotted between the inner wall of the container and the longitudinal axis. In the case of a conical tapering or widening, the maximum funnel opening angle corresponds to a constant funnel opening angle in the radial plane.

[0019] Preferably, the outlet section tapers more sharply along the longitudinal axis than the inlet section widens along the longitudinal axis, in other words the maximum funnel opening angle β at the outlet section a and the maximum funnel opening angle β at the inlet e However, the following relationship exists: β a ≦β e It is particularly preferable that the compound contains β a <β e and particularly preferably, β a <β e It is -3°.

[0020] The weakening of the flow from the inlet to the outlet can thus be compensated to some extent.

[0021] It has been found that the best cleaning results can be achieved when the gas supply opens into the inlet section through an inlet opening. Alternatively, the gas supply can also open into the inlet section tangentially to the longitudinal axis of the inlet opening and away from the inlet section downward toward the outlet section. In this case, it is preferred that the gas supply includes at least two or more openings into the inlet section. Gas supply through the inlet opening of the particle inlet has the advantage that the gas flow first passes through the particle inlet along the same path as the particles being filled, so that residues in this area are also captured and removed by the gas flow.

[0022] This embodiment can be particularly preferably realized by a gas supply comprising a gas guide arranged at least partially at the particle inlet, the gas flow being set to rotate by the gas guide.

[0023] The gas guide member advantageously comprises at least two gas guide vanes arranged symmetrically around the longitudinal axis.

[0024] Preferably, the particle inlet is designed as a port coaxial with the longitudinal axis. In this case, the gas guide vanes advantageously extend radially from the longitudinal axis to the inner surface of the particle inlet, along which they form outer vane edges that are at least partially inclined with respect to the direction of the longitudinal axis. This results in a vane shape that imposes a tangential component of motion on the incoming gas.

[0025] It is particularly preferred that the outer edges of the vanes form a curved shape whose inclination angle relative to the direction of the longitudinal axis increases from the inlet opening towards the outlet opening. A gas guide element with gas guide vanes configured in this way has proven to be advantageous in terms of improved deflection of the gas flow in the circumferential direction compared to gas guide vanes with straight outer edges.

[0026] Particularly preferably, the maximum axial inclination angle of the end of the outer blade edge on the outlet side is greater than or equal to 30°, particularly preferably greater than or equal to 40°, very particularly preferably greater than or equal to 45° relative to the direction of the longitudinal axis.

[0027] In combination with one or more of the foregoing features, the pressure filling system is advantageously further configured such that the ratio of the cross-sectional area of ​​the inlet opening to the maximum internal cross-sectional area is 1.5:100 or greater.

[0028] The shape of the pressure-filled tank is further specified by the maximum internal cross-sectional area F max The ratio of the square root of the length L of the pressure-filled tank along the longitudinal axis from the inlet opening to the outlet opening is

number

[0029] A particularly advantageous embodiment of the pressure filling system provides that a shear stress of at least 1 Pa, preferably at least 5 Pa, particularly preferably at least 10 Pa, can be generated by the rotating gas flow over a surface area of ​​at least 80%, preferably at least 85%, particularly preferably at least 90% of the inner surface, at a distance of 1 mm from the inner surface.

[0030] The method according to the invention is therefore advantageously configured in such a way that a shear stress of at least 1 Pa, preferably at least 5 Pa, particularly preferably at least 10 Pa, is generated by the rotating gas flow over an area of ​​at least 80%, preferably at least 85%, particularly preferably at least 90% of the inner surface at a distance of 1 mm from the inner surface.

[0031] The method is further advantageously configured in that the cavity has a volume V, the inner surface has a dimension F, and the gas flow, preferably an air flow, is introduced under conditions of an inlet pressure P of 3 to 12 bar, preferably 6 to 10 bar, and / or a mass flow rate S of 20 to 100 kg / s. Preferably, the gas flow is introduced under these conditions for at least 0.5 seconds, particularly preferably at least 1 second, and / or at most 5 seconds, particularly preferably at most 3 seconds.

[0032] The pressure filling system therefore advantageously comprises a gas pressure source, preferably a compressed air source, which can be connected to the gas supply of the gas-filled tank and is arranged to provide an air flow at an inlet pressure P of 3 to 12 bar, preferably 6 to 10 bar. Here again, overpressure relative to atmospheric pressure or air pressure is meant. Furthermore, the gas pressure source is preferably arranged to provide a gas flow at a mass flow rate S of 20 to 100 kg / s. These values ​​have proven advantageous in most cases for generating the above-mentioned shear stress values.

[0033] Preferably, the gas pressure source is arranged to provide a gas flow for at least 0.5 seconds, particularly preferably at least 1 second, which duration has been shown to be generally sufficient to completely empty the tank and remove any adhering particles.

[0034] Furthermore, the gas pressure source is preferably arranged to provide a gas flow for a maximum of 30 seconds, preferably for a maximum of 5 seconds, particularly preferably for a maximum of 3 seconds, which makes it possible to limit the gas consumption and thus the dimensions of the gas pressure source.

[0035] In a preferred embodiment, the gas pressure source comprises a discontinuous gas pressure source such as a gas accumulator, in particular a compressed air accumulator. Gas accumulators or discontinuous gas pressure sources generally have the advantage that they can provide a high mass flow rate at high pressure. At the same time, the gas accumulator can be filled with a relatively low volumetric or mass flow rate, since cleaning is only repeated at long intervals. Therefore, a small, cost-effective compressor is generally sufficient.

[0036] Alternatively, a continuous gas pressure source, such as a blower, can also be supplied as a compressed air source. This can also be used to generate large mass flow rates relatively cheaply. However, the pressure that can be generated is relatively low, which means that the cleaning process can be time consuming.

[0037] In the case of a discontinuous gas pressure source, the supply of gas flow can be time-limited, for example, simply by sizing the gas pressure reservoir. A continuous gas pressure source can be switched on or off as needed, regardless of the type of gas pressure source. The pressure filling system preferably includes a switching element for switchably interrupting the air flow. Such a switching element can be realized, for example, as a valve device or a flap device.

[0038] The method also preferably provides for grounding the gas loading tank, so that the gas loading tank includes an electrical ground connection, which may reduce the number of particles that become attached and therefore the need for cleaning in the first place.

[0039] The method is further advantageously configured in that the introduction of the gas flow into the cavity comprises the introduction of an ionized gas, in particular ionized air, and therefore the pressure filling system advantageously comprises a gas or air ionizer connected to a gas supply. [Brief explanation of the drawings]

[0040] Further advantages and features of the invention will be explained below with reference to the embodiments shown in the drawings. [Figure 1] 1 is a side cross-sectional view of a pressure filling system according to a first embodiment of the present invention. [Figure 2] 2 is a perspective view of a gas guide element installed in the pressure filling system according to FIG. 1; [Figure 3] FIG. 4 is a side view of the gas guide member. [Figure 4] 2 is a schematic diagram showing the flow path of the introduced gas flow in the pressure filling system according to FIG. 1; [Figure 5] 10 is a side cross-sectional view of a second embodiment of a pressure filling system according to the present invention. FIG. [Figure 6] FIG. 10 is a side cross-sectional view of a third embodiment of a pressure filling system according to the present invention. [Figure 7] 10 shows a side view of a fourth embodiment of a pressure filling system according to the present invention with a modified gas supply. [Figure 8] 10 shows a side view of a fifth embodiment of a pressure filling system according to the present invention with a modified particle inlet. DETAILED DESCRIPTION OF THE INVENTION

[0041] FIG. 1 illustrates a first embodiment of a pressure-filling system 1 according to the present invention, with a longitudinal axis A. All components described below are essentially rotationally or angularly symmetric about this axis. These include a particle inlet 10, an inlet section 12, a central section 14, an outlet section 16, and a particle outlet 18, arranged in the direction of gas flow, characterized by arrow 2. While not shown, an inspection window or through-hole, e.g., for an optional process monitoring probe, may also be arranged laterally in one of the aforementioned sections, inlet, or outlet, thereby breaking the rotational or angular symmetry. It should be understood that "essentially" here refers specifically to the embodiment and to the present invention in general to pressure-filling systems in which the pressure-filling tank comprises a rotationally or angularly symmetric basic shape, but is not completely rotationally or angularly symmetric due to connections and functional attachments or internal structures.

[0042] The inlet section 12, the central section 14, and the outlet section 16 together form a pressure-filled tank 20 having a common pressure vessel wall 22, the inner surface 24 of which encloses a cavity 26. The particle inlet 10 and the particle outlet 18 are each designed as ports coaxial with the longitudinal axis A. The particle inlet 10 defines an inlet opening 28 in the inlet section 12. Similarly, the particle outlet 18 defines an outlet opening 30 in the outlet section 16. Particles to be pressure-filled are introduced into the pressure-filled tank 22 through the particle inlet, and the pressure-filled particles are discharged from the pressure-filled tank 22 through the particle outlet.

[0043] The pressure-filled tank 20 has a maximum internal cross-sectional area 32 at the central portion 14, perpendicular to the longitudinal axis A. In this embodiment, the central portion 14 is cylindrical along its entire length, so the cross-sectional area 32 is constant along its entire length. The inlet portion 12 has an internal cross-sectional area, perpendicular to the longitudinal axis A, that increases continuously along the longitudinal axis A from the inlet opening 28 to the central portion 14. In this case, the inlet portion 12 widens conically along the longitudinal axis A from the inlet opening 28 to the central portion. Mirroring this, the outlet portion 16 has an internal cross-sectional area, perpendicular to the longitudinal axis A, that gradually decreases along the longitudinal axis A from the central portion 14 to the outlet opening 30. Specifically, in the first example shown, the outlet portion 16 also tapers conically along the longitudinal axis A from the central portion 14 to the outlet opening 30. Thus, the interior surface 24 of the inlet section 12 has a constant funnel opening angle β subtending between the longitudinal axis A and the interior surface 24. e The same applies to the outlet section 16, whose inner surface 24 is plotted against the longitudinal axis A and has a constant funnel opening angle β a In the present embodiment shown in FIG. e and the funnel opening angle β of the outlet portion 16 a is the same.

[0044] A gas guide 34 is disposed at the particle inlet 10 and will be described in more detail below with reference to FIGS. 2 and 3. The gas guide 34 is part of the gas supply, which may include, in addition to the gas guide, for example, a gas feedthrough, a gas connection to a gas line, and / or a valve (not shown) for limiting the pressure and / or flow rate of the gas stream. In the illustrated embodiment, the gas supply opens into the cavity 26 of the pressure-filled tank 20 through an inlet opening 28 of the inlet 12. Particles introduced into the pressure-filled tank 22 through the particle inlet travel through the gas guide. This allows the gas to travel the same path as the particles during subsequent cleaning before reaching the cavity 26, so that cleaning also includes part of the particle transport path.

[0045] 2 and 3 show enlarged views of the gas guide member 34. In the embodiment shown in FIG. 1, the gas guide member 34 is positioned completely within the particle inlet 10. However, it may also be positioned offset downwards in the direction of the gas flow 2 and protrude into the inlet section 12. Local prepositions such as "below," "under," "above," or "over" in this specification refer to the direction of gravity, which in the embodiment shown corresponds to the flow direction of the gas flow 2. The gas guide member 34 includes a total of six gas guide vanes 36 arranged rotationally or axisymmetrically about the longitudinal axis A. The gas guide vanes 36 extend in a radial direction R from the longitudinal axis A to the inner surface of the particle inlet 10, forming outer vane edges 38 along the inner surface of the particle inlet 10 that are at least partially inclined relative to the direction A. More precisely, in the embodiment of the gas guide element 34 shown here, the outer vane edges 38 form a curved curve with an increasing inclination angle α relative to the direction of the longitudinal axis A from the inlet opening 28 towards the outlet opening 30, the angle α defining an acute angle plotted against a tangent to the curved curve of the outer vane edges 38 relative to the longitudinal axis A. At the axial outlet end 40, the maximum inclination angle α relative to the direction of the longitudinal axis A is max is 50° in the embodiment shown. The outlet or lower end 40 of the outer vane edge 38 is located in the plane of the inlet opening 28 in the first example of FIG.

[0046] 4 shows the results of a mathematical simulation of the pressure-filling system 1 according to the embodiment of FIG. 1. The gas stream 2 introduced into the cavity 26 of the inlet section 12 through the gas supply opening is rotated within the cavity 26 about the longitudinal axis A by the gas guiding member 34 disposed at the particle inlet 10. This is shown in the simulation by the spiral streamline 42. The simulation showed that in this embodiment, a shear stress of at least 10 Pa can be generated by the rotating gas stream over more than 80% of the area of ​​the inner surface 24 at a distance of 1 mm from the inner surface 24.

[0047] 5 shows a second embodiment of the pressure filling system according to the present invention, which is essentially different from the first embodiment according to FIG. 1 in that the inlet section 12 and the outlet section 16 each have a different shape, and also change the overall shape of the pressure vessel wall 22, the cavity 26, and the inner surface 24. Specifically, the inlet section 12 and the outlet section 16 each still have a frustoconical shape, and in this case the maximum funnel opening angles of the inlet section 12 and the outlet section 16, respectively, are β e =30°, β a =20°, β a =β e It is -10°.

[0048] In this example, simulation of the flow pattern within cavity 26 showed that the optimized geometry, at a distance of 1 mm from the inner surface 24, allows a shear stress of at least 10 Pa to be generated over more than 90% of the area of ​​the inner surface 24 by a gas flow that is otherwise configured to rotate similarly.

[0049] FIG. 6 illustrates a third embodiment of a pressure-filling system 1 according to the present invention, which differs substantially from the second embodiment of FIG. 5 in that the inlet section 12, central section 14, and outlet section 16 are no longer depicted with simple linear profiles, i.e., conical and cylindrical, but rather with more complex curved paths. Specifically, the inner cross-sectional area of ​​the inlet section 12 continues to gradually increase along the longitudinal axis A from the inlet opening 28 to the central section 14, in a general manner referred to herein as "funnel-shaped." Similarly, the inner cross-sectional area of ​​the outlet section 16 continues to taper along the longitudinal axis A continuously and in a generally funnel-shaped manner from the central section 14 to the outlet opening 30. Again, the inner surface 24 of the inlet section 12 is plotted against the longitudinal axis (A) at a maximum funnel opening angle β. e ≦30°, and the inner surface 24 of the outlet section 16 has a maximum funnel opening angle β a Maximum funnel opening angle β≦20° e and β a are formed by the angle between the longitudinal axis A and the tangent to the inner cross-sectional profile at the point of maximum cross-sectional area increase or decrease (or mathematically the maximum or minimum derivative of the curve), respectively.

[0050] The central portion 14 is further disposed between the inlet portion 12 and the outlet portion 16, and the boundary between the inlet portion 12 and the central portion 14, on the one hand, and the boundary between the central portion 14 and the outlet portion 16, on the other hand, are both located in the region between the points of increasing and decreasing maximum cross-sectional area. Also, in this example, the pressure-filled tank 20 has a maximum internal cross-sectional area 32 perpendicular to the longitudinal axis A at the central portion 14.

[0051] Unlike the previously shown embodiments, here the gas guide member 34 protrudes slightly downward into the inlet section beyond the inlet opening 28, but is still at least partially, or even mostly, located within the particle inlet 10.

[0052] Figure 7 shows a fourth embodiment of the pressure filling system 1 according to the invention, which differs from the second embodiment of Figure 5 only by a modified gas supply 44. This gas supply 44 opens tangentially into the cavity 26 at the inlet 12, in this case the funnel-shaped pressure vessel wall 22. This opening is located almost directly below the inlet opening, again ensuring that the gas flow, which is set to rotate, almost completely flushes the cavity 26 of the pressure filling tank 20. In this case, the rotation is caused by the tangential introduction and inward redirection of the gas flow along the conical inlet 12.

[0053] Figure 8 shows a fifth embodiment of a pressure filling system 1 according to the invention, which differs from the second embodiment of Figure 5 by a modified particle inlet 50. At the inlet section 12, this inlet does not open axially into the cavity 26, but with a radial component perpendicular to the funnel-shaped pressure vessel wall 22. As in embodiments 1 to 3, the gas supply is axial, with rotation provided by the gas guide member 34.

[0054] It should be understood that the present invention also includes further combinations and variations of modified particle inlets and gas supplies. [Explanation of symbols]

[0055] 1 Pressure Filling System 2 Gas flow, arrow 10 particle inlet 12 Entrance 14 Central part 16 Exit section 18 Particle outlet 20 Pressure Filling Tank 22 Pressure vessel wall 24 Inner 26 Cavity 28 Inlet opening 30 outlet opening 32 Maximum internal cross-sectional area 34 Gas guide member 36 Gas guide vane 38 outer blade edge 40 Outlet end (of gas guide vane) 42 Spiral streamlines 44 Gas supply section 50 particle inlet A longitudinal axis R Radial direction α max Maximum tilt angle β a Funnel opening angle at outlet β e Funnel opening angle at the inlet

Claims

1. A pressure filling system (1) comprising a pressure filling tank (20) having a longitudinal axis (A), the pressure filling tank including a pressure vessel wall (22) having an inner surface (24) surrounding a cavity (26), and having an inlet section (12), a central section (14), and an outlet section (16) along the longitudinal axis (A); the pressure-filling system (1) comprising a particle inlet (10) defining an inlet opening (28) in the inlet section (12) and a particle outlet (18) defining an outlet opening (30) in the outlet section (16); a gas supply (44) opening into the cavity (26) at the inlet (12) is arranged to introduce a gas flow (2) into the cavity (26) in such a way that the gas flow (2) rotates around the longitudinal axis (A) within the cavity (26). Pressure filling system (1).

2. the pressure-filled tank (20) comprises a maximum internal cross-sectional area (32) perpendicular to the longitudinal axis (A) at the central portion (14); A pressure filling system (1) according to claim 1.

3. The central portion (14) is cylindrical. A pressure filling system (1) according to claim 1 or 2.

4. the inlet section (12) comprises an internal cross-sectional area perpendicular to the longitudinal axis (A) which increases continuously along the longitudinal axis (A) from the inlet opening (28) to the central section (14); A pressure filling system (1) according to any one of claims 1 to 3.

5. the inlet section (12) widens in a funnel or cone shape along the longitudinal axis (A) from the inlet opening (28) to the central section (14); A pressure filling system (1) according to any one of claims 1 to 4.

6. the outlet section (16) comprises an internal cross-sectional area perpendicular to the longitudinal axis (A) which is characterized in that it decreases continuously along the longitudinal axis (A) from the central section (14) to the outlet opening (30); A pressure filling system (1) according to any one of claims 1 to 5.

7. the outlet section (16) is characterized in that it tapers in a funnel-like or conical manner from the central section (14) to the outlet opening (30) along the longitudinal axis (A), A pressure filling system (1) according to any one of claims 1 to 6.

8. the outlet section (16) tapers more sharply along the longitudinal axis (A) than the inlet section (12) widens along the longitudinal axis (A), A pressure filling system (1) according to any of claims 4 or 5 and 6 or 7.

9. a gas supply (44) opening into the cavity (26) through the inlet opening (28) of the inlet section (12), the gas supply (44) including a gas guide member (34) at least partially disposed within the particle inlet (10), A pressure filling system (1) according to any one of claims 1 to 8.

10. The gas guide member (34) comprises at least two gas guide vanes (36) arranged axisymmetrically around the longitudinal axis (A). A pressure filling system (1) according to claim 9.

11. characterised in that the particle inlet (10) is designed as a port coaxial with the longitudinal axis (A), A pressure filling system (1) according to any one of claims 1 to 10.

12. the gas guide vanes (36) extend in a radial direction (R) from the longitudinal axis (A) to an inner surface of the particle inlet (10) and form outer vane edges (38) along the inner surface of the particle inlet (10), the outer vane edges being at least partially inclined with respect to the direction of the longitudinal axis (A), A pressure filling system (1) according to claim 10 or 11.

13. the outer vane edges (38) form a curved shape whose inclination angle with respect to the direction of the longitudinal axis (A) increases from the inlet opening (28) to the outlet opening (30). A pressure filling system (1) according to claim 12.

14. The maximum inclination angle (α ｍａｘ ) is at least 30°, preferably at least 40°, particularly preferably at least 45° relative to the direction of the longitudinal axis (A); A pressure filling system (1) according to claim 13.

15. a shear stress of at least 1 Pa, preferably at least 5 Pa, particularly preferably at least 10 Pa, can be generated by the rotating gas flow over an area of ​​at least 80%, preferably at least 85%, particularly preferably at least 90% of the inner surface (24) at a distance of 1 mm from the inner surface (24), A pressure filling system (1) according to any one of claims 1 to 14.

16. a gas pressure source is provided connectable to the gas supply (44) and arranged to provide a gas flow at an inlet pressure P of 3 to 12 bar, preferably 6 to 10 bar. A pressure filling system (1) according to any one of claims 1 to 15.

17. the gas pressure source is arranged to provide a gas flow at a mass flow rate S of 20 kg / s to 100 kg / s; A pressure filling system (1) according to any one of claims 1 to 16.

18. the gas pressure source is arranged to provide the gas flow for at least 0.5 seconds, preferably at least 1 second. A pressure filling system (1) according to any one of claims 1 to 17.

19. The gas pressure source includes a gas pressure accumulator. A pressure filling system (1) according to any one of claims 16 to 18.

20. 1. A method for cleaning a pressure-filled tank (20) having a longitudinal axis (A), the pressure-filled tank including a pressure vessel wall (22) having an inner surface (24) surrounding a cavity (26), and having an inlet section (12), a central section (14), and an outlet section (16) along the longitudinal axis (A), the method comprising introducing a gas stream (2) into the cavity (26) at the inlet section (12), the gas stream (2) being configured to rotate within the cavity (26) about the longitudinal axis (A).

21. a shear stress of at least 1 Pa, preferably at least 5 Pa, particularly preferably at least 10 Pa, is generated by the rotating gas flow over an area of ​​at least 80%, preferably at least 85%, particularly preferably at least 90% of the inner surface (24) at a distance of 1 mm from the inner surface (24), 21. The method of claim 20.

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