PRESSURE GAS SPRING WITH OVERPRESSURE PROTECTION, AND METHOD FOR MANUFACTURING THE PRESSURE GAS SPRING

Abstract

The invention relates to a gas spring (100) comprising a pressure tube (110) and a fluid with a fluid pressure confined by the pressure tube (110), in a fluid-tight manner in an operating state of the gas spring (110). A wall (120) of the pressure tube (110) has a local taper (130), where the taper (130) forms a predetermined rupture point of the wall (120), adapted to open to release a portion of the fluid from the pressure tube (110), in a controlled manner when the fluid pressure exceeds a limit pressure. The wall thickness, of the wall (120), has a line-shaped minimum (131) within the taper (130), where the wall thickness increases monotonically from the minimum (131) to an edge (132) of the taper (130), in all circumferential directions around the longitudinal axis (LA) of the pressure tube (110).The invention also relates to a method of manufacturing the pressurized gas spring (100).

Description

PRESSURE GAS SPRING WITH OVERPRESSURE PROTECTION, AND METHOD FOR MANUFACTURING THE PRESSURE GAS SPRING FIELD OF INVENTION [1] The invention relates to a pressure gas spring comprising a pressure tube and a fluid having a fluid pressure confined in a fluid-hermetically sealed manner by the pressure tube, a wall of the pressure tube having a local taper, wherein the taper forms a predetermined rupture point of the wall adapted to open to release a portion of the fluid from the pressure tube, in a controlled manner when the fluid pressure exceeds a limit pressure. [2] The invention also relates to a method for manufacturing the pressurized gas spring, according to the invention. BACKGROUND OF THE INVENTION [3] A gas spring is filled with a pressurized fluid. If the gas spring gets too hot, for example in a fire, the fluid pressure can rise sharply. [4] To comply with the relevant transport regulations, pressurized gas springs have different mechanisms to ensure safe pressure relief in case of fire. [5] Up to now, for example, a damping groove on the inner side of the sleeve wall of a pressurized gas spring, through which fluid can flow past the piston of the pressurized gas spring during operation of the pressurized gas spring, has been designed as a predetermined rupture line at which the sleeve wall must tear in case of fire, so that fluid can flow out of the pressurized gas spring. [6] However, the damping groove, which serves as a predetermined breaking line, has the following disadvantages: The damping groove extends over a large part of the length of the pressurized gas spring. The position, shape, and dimensions of the damping groove are determined by its damping function and, therefore, cannot always be optimally adapted to the overpressure protection requirements. Furthermore, the embossing process of the grooves (whether pressed or rolled) results in strain hardening of the sleeve wall in this area, which affects the opening behavior of the groove. [7] Other types of overpressure protection, for example, overpressure valves, are associated with high manufacturing costs. SUMMARY OF THE INVENTION Technical problem [8] The task of the invention is to create a pressurized gas spring that can be manufactured at low cost with reliable and safe overpressure protection, and a low-cost manufacturing process for the same. Qfconnn / eznz / B / Yi Technical solution [9] The present invention provides a pressurized gas spring according to claim 1, which solves the technical problem. The problem is further solved by a method for manufacturing the pressurized gas spring, according to claim 9. Favorable embodiments are the subject of the dependent claims.

[10] The invention relates to a pressurized gas spring comprising a pressure tube and a fluid confined in a fluid-tight, particularly gas-tight, manner by the pressure tube in an operating state of the pressurized gas spring. The pressure tube is, for example, substantially hollow-cylindrical in its shape. The pressure tube is manufactured from steel, aluminum, plastic, and / or a composite material, for example.

[11] A working piston can be guided in the pressure tube so that it can slide along a longitudinal axis of the pressure tube. A piston rod can be associated with the working piston, which is guided out of the pressure tube along the longitudinal axis at one end of the pressure tube, for example, by a guide and seal assembly.

[12] The preferred fluid is a gas, for example, nitrogen. In the operating state of the pressurized gas spring, the fluid pressure within the operating temperature range of the pressurized gas spring is, for example, from 50 bar to 500 bar, and in particular from 100 bar to 300 bar. The operating temperature range extends, for example, from -50 °C to +200 °C, and in particular from -30 °C to +100 °C.

[13] A pressure tube wall has a localized taper, where the taper forms a predetermined rupture point in the wall, adapted to open and allow a portion of the fluid to be released from the pressure tube in a controlled manner when the fluid pressure exceeds a threshold pressure. When the fluid pressure exceeds the threshold pressure, the pressure tube bursts at the predetermined rupture point formed by the taper, allowing a portion of the fluid to escape from the pressure tube and reduce the fluid pressure to an ambient pressure of the pressurized gas spring. The predetermined rupture point thus acts as overpressure protection.

[14] To distinguish it from the operating state of the pressure gas spring with the predetermined breaking point closed, the state of the pressure gas spring, after the release of the overpressure protection with the predetermined breaking point open, is referred to in the following as the protection state.

[15] The preferred limiting pressure is above, for example, 50% above, the maximum expected fluid pressure in the operating condition and operating temperature range, and below the burst pressure of the pressure tube without a predetermined rupture point. This prevents undesirable activation of the overpressure protection during operation of the pressurized gas spring, and uncontrolled bursting of the pressure tube in the event of a fire.

[16] The wall thickness has a minimum in the form of a line, particularly in the form Qfconnn / eznz / B / YiAi of point, within the taper, where the wall thickness increases monotonically from the minimum to an edge of the taper in all circumferential directions around the longitudinal axis of the pressure pipe, particularly in all directions along the wall. The edge is the boundary line at which the wall thickness, starting from the minimum, reaches the value of the wall thickness of the wall free of taper.

[17] Due to the shape of the taper, only a small opening forms in the wall around the minimum when the overpressure protection is activated. Since the wall thickness increases uniformly toward the edge of the taper, the wall does not tear over a large area, unlike an elongated groove as the predetermined rupture point. The small opening allows the fluid to escape from the pressure pipe in a controlled and relatively slow manner.

[18] A point-shaped form, within the meaning of the invention, is understood as a special case of a line-shaped form, specifically as a line-shaped form with length 0. A point-shaped minimum has the advantage that the aforementioned effects are particularly pronounced. A line-shaped minimum has the advantage that it can be produced particularly easily, for example, by flattening an outer side of the wall in a wall-sleeving region.

[19] The terms "line-shaped," "dot-shaped," and "monotonously increasing" are not to be understood as mathematically exact within the meaning of the invention. Deviations from an exact line-shaped or dot-shaped form, or an exactly monotonous increment, that fall below the usual tolerances in the manufacture of pressurized gas springs, for example, below 0.1 mm, or within the range of a surface roughness of the pressure tube of the pressurized gas spring, have no function within the meaning of the invention. Description of preferred modalities

[20] The preferred taper forms a concavity on an external side of the wall that faces away from the fluid. Creating the taper in the form of a concavity is easier on the outside than on the inside of the fluid-facing wall. Furthermore, with an external concavity, as opposed to an internal one, there is no risk of affecting the movement of a piston in the pressure tube or the seal between the piston and the pressure tube. This means that the taper of the pressure tube can be positioned at any suitable point for reliable and safe overpressure protection, and not only outside the piston's stroke path.

[21] The taper is preferably located in a sleeve region of the wall surrounding the longitudinal axis of the pressure tube. On one end face of the pressure tube is usually the guide and seal assembly through which the piston rod is guided out of the pressure tube. On the other end face is usually a connecting element for attaching the gas spring to other components. Therefore, it would be complicated to further associate the taper with one of the end faces. Moreover, the backflow of fluid exiting through the sleeve region acts Qfconnn / eznz / B / YiAi transversely to the longitudinal axis of the pressure tube. This makes it less likely that recoil will set the pressurized gas spring in motion than if the fluid emerged from one of the end faces and thus caused recoil along the longitudinal axis.

[22] Preferential taper forms a lenticular concavity in the wall. In the case of a cylindrical lens shape, the lenticular concavity causes a line-like minimum in wall thickness, and the wall thickness increases monotonically along the curvature of the lens toward the edge of the concavity. In the case of a spherical lens shape, the lenticular concavity causes a point-like minimum in wall thickness at the center of the concavity, and the wall thickness increases monotonically toward the edge of the concavity in all directions along the wall. A lenticular concavity can be easily created, especially in a curved sleeve region of the wall, by using machining methods commonly employed in the manufacture of pressurized gas springs, for example, by milling.

[23] The preferred radius of curvature for the taper is 20 mm to 200 mm, with a greater preference for 50 mm to 150 mm, and a higher preference for 100 mm. A smaller radius of curvature results in a smaller taper area and a steeper wall thickness slope from the minimum to the edge of the taper. A small area is favorable for controlled and relatively slow fluid discharge. However, a steep slope favors uncontrolled tearing of the wall around the taper. The aforementioned values ​​have been shown to be a suitable compromise for safe and reliable overpressure protection, for example, in tests on a steel pressure pipe with a wall thickness of 2 mm and an outside diameter of 29 mm.

[24] The preferred taper edge is elliptical, particularly circular. An elliptical edge can be easily created, especially in a curved sleeve region of the wall, using machining methods commonly employed in the manufacture of pressurized gas springs, for example, by milling.

[25] A large half-shaft of the elliptical rim preferably measures from 4 mm to 40 mm, particularly from 15 mm to 20 mm, with the highest preference being 17 mm. A small half-shaft of the elliptical rim preferably measures from 1 mm to 10 mm, particularly from 5 mm to 7 mm, with the highest preference being 6 mm. The above values ​​have been shown, for example, in tests for a steel pressure pipe with a wall thickness of 2 mm and an outside diameter of 29 mm, to be adequate for safe and reliable overpressure protection.

[26] The minimum wall thickness at the edge of the taper is preferably 20% to 80%, preferably 25% to 60%, and particularly preferably 30% to 40% of the edge wall thickness. The minimum wall thickness at the edge of the taper is preferably 0.4 mm to 1.6 mm, preferably 0.5 mm to 1.2 mm, and particularly preferably 0.6 mm to 0.8 mm. The aforementioned values ​​have been proven, for example, in tests on a steel pressure pipe with an edge wall thickness of 2.0 mm, to be adequate for safe and reliable overpressure protection. Qfconnn / eznz / B / YiAi

[27] The preferred gas spring comprises a guide tube arranged coaxially to the pressure tube within the pressure tube, with the pressure tube forming a projection onto the guide tube along the longitudinal axis of the pressure tube. The preferred gas spring comprises a separating piston movable within the pressure tube along the longitudinal axis, wherein the separating piston separates a working chamber in the guide tube, an annular chamber radially to the longitudinal axis between the guide tube and the pressure tube, and a support chamber in the projection between them in a fluid-tight manner in the operating state of the gas spring. The annular chamber is filled with a compensating medium that presses the separating piston in the operating state, with a compensating pressure in a direction that enlarges the working chamber.In the operating state, the support chamber is filled with a support fluid, specifically a support gas, which presses the separating piston with a support pressure in a direction that reduces the working chamber size. In the operating state, the working chamber is filled with a working fluid, specifically a working gas, at a working pressure.

[28] In the design of the gas spring, as described in the preceding paragraph, the compensating means displaces the separating piston when the gas spring heats up, thereby enlarging the working chamber. This reduces the increase in working pressure caused by heating, thus reducing the temperature dependence of the gas spring's spring force. The principle of this temperature-compensated gas spring is known, for example, from publications EP 1 795 777 A2, DE 10 2020 123 636 A1, and DE 10 2021 124 843 A1.

[29] The guide tube is designed, for example, as the working cylinder described in document DE 10 2021 124 843 A1. The separation piston is designed, for example, as the compensating piston described in document DE 10 2021 124 843 A1.

[30] The design of the pressure gas spring, as a temperature-compensated pressure gas spring, creates the additional problem that, in the event of a fire, the working pressure of the working fluid, the compensation pressure of the compensation medium, and the support pressure of the support fluid must be safely and reliably relieved.

[31] The additional preference problem is solved by the predetermined rupture point of the wall, formed by the taper which is designed to open to release part of the compensating medium, working fluid and support fluid from the pressure tube, in a controlled manner when the compensating pressure, working pressure or support pressure exceeds a limit pressure.

[32] The taper of the preferred wall abuts the support chamber, where the separating piston can be moved into a locking position in which the working chamber and the annular chamber are connected to the predetermined rupture point in a fluid-conducting manner when the predetermined rupture point is opened. This arrangement has the advantage that, in the event of a fire, the support fluid can flow first out of the pressure pipe through the point Qfconnn / eznz / B / YiAi of predetermined rupture. Due to the reduced support pressure, the compensating medium and working fluid can then move the separation piston beyond the predetermined rupture point, into the support chamber. This allows the working fluid and compensating medium to exit the pressure tube through the predetermined rupture point as well.

[33] The taper of the preferred wall is located outside the stroke path along which the separating piston can travel along the longitudinal axis in the pressurized gas spring operating state. This ensures that the separating piston is not in a position where the compensating medium is in contact with the predetermined rupture point when the predetermined rupture point opens. In this case, some of the compensating medium might escape from the pressure tube at high pressure before the support pressure displaces the separating piston, allowing the support fluid to escape. Since the compensating medium, unlike the support fluid, is usually liquid, the risk of property damage or injury is greater if the liquid compensating medium escapes first at high pressure, and then the gaseous support fluid escapes at a lower pressure, than the reverse.

[34] The invention relates to a method for manufacturing a gas spring, according to the invention. The method comprises providing the gas spring pressure tube, wherein the wall of the pressure tube preferably has a homogeneous wall thickness, and creating the taper of the pressure tube wall, preferably by removing material from an outer and / or inner side of the wall. Due to the advantages mentioned above, the material removal preferably takes place from the outer side of the wall.

[35] The preferred material is removed by machining, preferably by drilling, milling, grinding, turning and / or shaping and / or ablation, preferably by laser ablation.

[36] Milling, shaping and laser ablation have the particular advantage that they only slightly heat the wall, thus avoiding heat-related changes in the material properties of the wall, which could lead to uncontrolled behavior of the predetermined breaking point in the event of a fire.

[37] Material removal can create a defined contour of a concavity in the wall of the pressure pipe, for example, a contour with a rounded edge and / or a rounded bottom, to facilitate painting the pressure pipe. The contour can be defined, for example, by the shape of a cutting tool used for material removal, such as a drill bit or a milling head.

[38] The provision of the pressure tube and the creation of the preferred taper are carried out in a common process step, for example, by a forming process and / or additive manufacturing of the pressure tube with the taper. The forming process and / or additive manufacturing includes, in particular, die casting of the pressure tube, for example, from aluminum, injection molding of the pressure tube, for example, from plastic, and / or 3D printing of the tube. Pressure Qfconnn / eznz / B / YiAi. BRIEF DESCRIPTION OF THE DRAWINGS

[39] Other advantages, objectives and properties of the invention are explained with reference to the following description and accompanying drawings, in which exemplary embodiments of the invention are shown.

[40] Figure 1 shows a schematic longitudinal section through the pressure tube of a pressurised gas spring, according to the invention.

[41] Figure 2 shows a schematic view of the pressure tube of Figure 1.

[42] Figure 3 shows a schematic longitudinal section through a pressurized gas spring, according to the invention, in the operating state.

[43] Figure 4 shows a schematic longitudinal section through the pressurised gas spring of Figure 2, at a moment of overpressure protection release.

[44] Figure 5 shows a schematic longitudinal section through the pressurised gas spring of Figure 2, after the overpressure protection release moment. DETAILED DESCRIPTION OF THE INVENTION Figure 1

[45] Figure 1 shows a schematic longitudinal section through the pressure tube 110 of a pressure gas spring 100, according to the invention, along the longitudinal axis LA of the pressure tube 110, which is made of steel and is essentially hollow-cylindrical in its shape, for example. The pressure tube 110 has, for example, an inner diameter of 25 mm, an outer diameter of 29 mm, and a wall thickness of 2 mm.

[46] In an operating state of the gas spring pressure 100, the pressure tube 110 fluid-tight confines a fluid (not shown) having a fluid pressure.

[47] A wall 120, of the pressure tube 110 shown, has a local taper 130, wherein the taper 130 forms a predetermined rupture point of the wall 120, adapted to open to release a portion of the fluid from the pressure tube 110, in a controlled manner when the fluid pressure exceeds a limit pressure.

[48] ​​The wall thickness, of wall 120, has a point minimum 131 within the taper 130, where the wall thickness increases monotonically from the minimum 131 to an edge 132 of the taper 130, in all directions along wall 120.

[49] The taper 130 shown forms a concavity on an external side 121 of the wall 120 that is oriented away from the fluid, and is located in a jacket region 122 of the wall 120 surrounding the longitudinal axis LA.

[50] The taper 130 shown forms a lenticular concavity in the wall 120, where the radius of curvature of the concavity is, for example, 100 mm.

[51] For example, the minimum wall thickness, from wall 120 to minimum 131, is 0.7 mm. QAonnn / eznz / B / YiAi Figure 2

[52] Figure 2 shows a schematic view of the pressure tube of Figure 1.

[53] In Figure 2 it can be observed that the edge (132), of the taper (130) shown, is elliptical in its shape, where a semi-major axis of the elliptical edge (132) measures, for example, 17 mm. Figure 3

[54] Figure 3 shows a schematic longitudinal section through a pressure gas spring 100, according to the invention, along the longitudinal axis LA of the pressure tube 110 in the operating state. The pressure tube 110 can be designed in the same way as the pressure tube 110 shown in Figure 1 and Figure 2.

[55] The pressure gas spring 100, shown in Figure 3, comprises a guide tube 140 arranged coaxially to the pressure tube 110 within the pressure tube 110, with the pressure tube 110 forming a projection 160 onto the guide tube 140 along the longitudinal axis LA of the pressure tube 110.

[56] The pressure gas spring 100 shown comprises a separating piston 150 movable in the pressure tube 110 along the longitudinal axis LA, wherein the separating piston 150 separates a working chamber 141 in the guide tube 140, an annular chamber 111 radially to the longitudinal axis LA between the guide tube 140 and the pressure tube 110, and a support chamber 161 in the projection 160 from each other in a fluid-tight manner in the operating state of the pressure gas spring 100.

[57] The guide tube 140 is designed, for example, as the working cylinder 1 described in document DE 10 2021 124 843 A1, and the separation piston 150 is designed, for example, as the compensating piston 10 described in document DE 10 2021 124 843 A1.

[58] The annular chamber 111 shown is filled with a compensating fluid (not shown), which presses the separating piston 150 with a compensating pressure in a direction that enlarges the working chamber 141 in the operating state. In the operating state, the support chamber 161 is filled with a support fluid (not shown), which presses the separating piston 150 with a support pressure in a direction that reduces the working chamber 141. In the operating state, the working chamber 141 is filled with a working fluid (not shown) at a working pressure.

[59] The predetermined rupture point of the wall 120, formed by the taper 130, is designed to open in order to release a portion of the compensating medium, working fluid, and support fluid from the pressure tube 110, in a controlled manner when the support pressure exceeds a limit pressure.

[60] The taper 130, of the wall 120 shown, is adjacent to the support chamber 161 and is located outside the stroke path HW on which the separating piston 150 is displaceable along the longitudinal axis LA, in the operating state of the pressure gas spring 100.

[61] The taper 130 shown forms a concavity on an outer side 121 of the wall 120 Qfconnn / eznz / B / YiAi which is oriented away from the fluid, and is located in a jacket region 122 of the wall 120 surrounding the longitudinal axis LA.

[62] The working piston 170 is slidably guided along the longitudinal axis LA, in the guide cylinder 140. A piston rod 171 is associated with the working piston 170, which is guided out of the pressure tube 110 along the longitudinal axis LA, by a guide and seal assembly 172 at one end of the pressure tube 110. The working piston 170, the piston rod 171 and the guide and seal assembly 172 can be designed as in known pressure gas springs. Figure 4

[63] Figure 4 shows a schematic longitudinal section through the pressure gas spring 100 of Figure 2, along the longitudinal axis LA of the pressure tube 110, at the moment of overpressure protection release. At the moment of release, the support pressure exceeds the limit pressure, so that the predetermined rupture point formed by the taper 130 opens.

[64] This allows the support fluid to flow out of the pressure tube 110, through the predetermined open rupture point (white arrow). As the support pressure then decreases, the separation piston 150 is displaced by the compensating and working means beyond its stroke path HW into the support chamber 161 (black arrow). Figure 5

[65] Figure 5 shows a schematic longitudinal section through the pressure gas spring 100 of Figure 2, along the longitudinal axis LA of the pressure tube 110, after the overpressure protection release moment.

[66] In Figure 5, the separating piston 150 is pushed by the compensating medium and the working medium to a safe position in which the working chamber 141 and the annular chamber 111 are connected to the predetermined rupture point in a fluid-conducting manner. Therefore, the working fluid and the compensating medium can flow through the support chamber to the predetermined rupture point and out of the pressure tube 110 through the open predetermined rupture point (white arrows). List of reference symbols

[67] Qfconnn / eznz / B / YiAi 100 Pressure gas spring 110 Pressure tube 111 Annular chamber 120 Wall 121 Outer side 122 Sleeve region 130 Taper 131 Minimum 132 Edge 140 Guide tube 141 Working chamber 150 Separation piston 160 Projection 161 Support chamber 170 Working piston 171 Piston rod 172 Guide and sealing package HW stroke path LA Longitudinal shaft

Claims

1. A pressure gas spring (100), comprising a. a pressure tube (110) and b. a guide tube (140) arranged coaxially to the pressure tube (110) in the pressure tube (110), c. wherein the pressure tube (110) forms a projection (160) onto the guide tube (140) along the longitudinal axis (LA) of the pressure tube (110), d. wherein the pressure gas spring (100) comprises a separating piston (150) movable in the pressure tube (110) along the longitudinal axis (LA), e. wherein the separating piston (150) fluid-tightly separates a working chamber (141) in the guide tube (140), an annular chamber (111) radially to the longitudinal axis (LA) between the guide tube (140) and the pressure tube (110), and a support chamber (161) in the projection (160) in an operating state of the gas spring under pressure (100), f.wherein the annular chamber (111) is filled with a compensating means that presses the separating piston (150) in the operating state, with a compensating pressure in a direction that enlarges the working chamber (141), g. wherein the support chamber (161) is filled in the operating state with a support fluid that presses the separating piston (150) with a support pressure in a direction that makes the working chamber (141) smaller, h. wherein the working chamber (141) is filled with a working fluid that has a working pressure in the operating state, characterized in that i. a wall (120) of the pressure tube (110) has a local taper (130) adjacent to the support chamber (161), j.wherein the taper (130) forms a predetermined rupture point of the wall (120) adapted to open to release a portion of the compensating fluid, the working fluid, and the support fluid from the pressure pipe (110), in a controlled manner when the support pressure exceeds a limit pressure, k. wherein the wall thickness of the wall (120), within the taper (130), has a line-shaped minimum (131), I. wherein the wall thickness increases monotonically from the minimum (131) to an edge (132) of the taper (130) in all circumferential directions around the longitudinal axis (LA) of the pressure pipe (110), m. wherein, when the predetermined rupture point opens, the separation piston (150) is displaceable to a locking position in which the working chamber (141) and the annular chamber (111) are connected to the predetermined rupture point in a QRonnn / eznz / B / YiAi fluid conduction manner.

2. The pressure gas spring (100) according to claim 1, characterized in that a. the line-shaped minimum of the wall thickness (120) is point-like, b. wherein the wall thickness increases monotonically from the minimum (131) to an edge (132) of the taper (130) in all directions along the wall (120).

3. The pressurized gas spring (100) according to claim 1, characterized in that the conicity (130) forms a concavity on an external side (121) of the wall (120) that is oriented away from the fluid.

4. The pressurized gas spring (100) according to claim 1, characterized in that the taper (130) is located in a sleeve region (122) of the wall (120) surrounding the longitudinal axis (LA).

5. The pressurized gas spring (100) according to claim 1, characterized in that the taper (130) forms a lenticular concavity in the wall (120), 6. The gas spring under pressure (100) according to claim 5, characterized in that the radius of curvature of the concavity is from 20 mm to 200 mm.

7. The pressurized gas spring (100) according to claim 1, characterized in that the edge (132) of the taper (130) is elliptically shaped, 8. The gas spring (100) according to claim 7, characterized in that a. the major half-axis of the elliptical rim (132) measures from 4 mm to 40 mm, and / or b. the minor half-axis of the elliptical rim (132) measures from 1 mm to 10 mm.

9. The gas spring pressure (100) according to claim 1, characterized in that a. the minimum wall thickness, of the wall (120) at the minimum (131), is from 20% to 80% of the edge wall thickness at the edge (132) of the taper (130), and / or b. the minimum wall thickness, of the wall (120) at the minimum (131), is from 0.4 mm to 1.6 mm.

10. The gas spring pressure (100) according to claim 1, characterized in that the taper (130) of the wall (120) is located outside the stroke path (HW) on which the separating piston (150) is displaceable along the longitudinal axis (LA), in the operating state of the gas spring pressure (100).

11. A method of manufacturing the pressure gas spring (100) according to any of claims 1 to 10, comprising the following steps: a. Providing the pressure tube (110) with the pressure gas spring (100), b. Creating the taper (130) of the wall (120) of the pressure tube (110).

12. The method according to claim 11, characterized in that the creation of the taper (130) of the wall (120) is carried out by removing material from the wall (120).

13. The method according to claim 12, characterized in that the creation of the taper (130) of the wall (120) is carried out by removing material from an external side (121) of the wall (120).

14. The method according to claim 12, characterized in that the removal of material is carried out by mechanization and / or ablation.

15. The method according to claim 11, characterized in that the provision of the pressure tube (110) and the creation of the taper (130) are preferably carried out in a common process step by a forming process and / or an additive manufacturing process of the pressure tube (110) with the taper (130).

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