Gas pressure spring with temperature compensation and method for manufacturing the gas pressure spring

Abstract

The invention relates to a gas pressure spring (50) comprising a working piston (2) displaceably guided in a working cylinder (1) along a stroke axis (H), a compensation cylinder (12) surrounding the working cylinder (1) and a compensation piston (10) of hollow cylindrical shape and displaceably guided in the compensation cylinder (12) along the stroke axis (H). The working cylinder (1) has an open end (1b) at which the compensation cylinder (12) forms a projection (15) beyond the working cylinder (1) with a closed end (15b). The compensation piston (10) separates from each other a working chamber (1a) arranged in the working cylinder (1), a compensation chamber (12a) arranged between the working cylinder (1) and the compensation cylinder (12) and a restoring chamber (15a) arranged in the projection (15) and is open at the upper side (10a) of the balance piston (10) facing the working chamber (1a). The gas spring (50) includes a seal (8) disposed on an upper side (10a) of the balance piston (10), which seals the balance piston (10) against the working cylinder (1) and the balance cylinder (12).

Description

[Technical field]

[0001] The present invention relates to a gas pressure spring according to the preamble of claim 1 and to a method for manufacturing a gas pressure spring. [Background technology]

[0002] From the state of the art, gas pressure springs are known in which the temperature dependence of the spring force is compensated for by a compensation medium.

[0003] EP 1 795 777 A2 describes a gas spring having an actuating cylinder in which a working piston is movably guided. The annular space formed between the actuating cylinder and the compensating cylinder is filled with a compensating medium which expands when the temperature increases. The open end of the actuating cylinder opposite the piston outlet end is closed by a pot-shaped compensating piston. When the compensating medium expands, it displaces the compensating piston, as a result of which the volume of the actuating cylinder increases.

[0004] DE 3141295 A1 relates to a gas spring consisting of a container with a piston connected to a piston rod sliding on its inner wall. A space filled with an expansion material is located between a partition wall fixed to the container and a disk piston, which corresponds to a movable partition wall for the space filled with the expansion material. The gas spring also comprises a working chamber with a pressurized gas filling. When the temperature increases, the expansion material expands and moves the disk piston further away from the partition wall fixed to the container, thereby increasing the size of the working chamber.

[0005] Known gas springs with temperature compensation are typically complex in design, require significantly more installation space than gas pressure springs without temperature compensation, or are unable to compensate for temperature dependencies over the entire temperature range relevant to the application. Summary of the Invention

[0006] The object of the invention is to create an economical, simply constructed gas pressure spring, the spring force of which is temperature independent over as wide a temperature range as possible, and an economical and reliable method for its production. [Means for solving the problem]

[0007] The present invention provides a gas pressure spring according to claim 1 which achieves the technical object. This object is also achieved by a method for manufacturing a gas pressure spring according to claim 13. Advantageous embodiments follow from the dependent claims.

[0008] The gas pressure spring comprises an actuating piston which is movably guided in an actuating cylinder along a stroke axis over a stroke range, the actuating piston being preferably movable relative to the actuating cylinder along the stroke axis, the actuating cylinder preferably being of hollow cylindrical shape and / or being arranged coaxially with the stroke axis.

[0009] The gas pressure spring comprises a compensation cylinder which surrounds the working cylinder in a radial direction relative to the stroke axis, the compensation cylinder preferably being of hollow cylindrical shape and / or being arranged coaxially with the stroke axis, and the compensation cylinder preferably being rigidly attached to the working cylinder.

[0010] The gas pressure spring comprises a compensation piston of hollow cylindrical shape which is movably guided in a compensation cylinder along a stroke axis, the compensation piston being preferably arranged coaxially with the stroke axis, the compensation piston being preferably movable along the stroke axis relative to the compensation cylinder and the working cylinder.

[0011] The actuating cylinder has an open end along the stroke axis. By "open" it is meant at least that gas can freely exit the working cylinder and enter the working cylinder through the open end. Preferably the open end is completely open.

[0012] At the piston rod end of the working cylinder opposite the open end along the stroke axis, the piston rod attached to the working piston is preferably led out of the working cylinder through a sealing device. The sealing device preferably closes the piston rod end to gas. "Closed" means that gas cannot escape or enter the working cylinder at the piston rod end.

[0013] According to an embodiment of the actuation cylinder, which is also advantageous for gas pressure springs in general, independently of the other features of the invention, the actuation cylinder preferably has a sealing area outer diameter, measured radially to the stroke axis, in a sealing area between the stroke area and the piston rod end of the actuation cylinder, where the piston rod leaves the actuation cylinder, which sealing area outer diameter is larger than the stroke area outer diameter of the actuation cylinder. The sealing area outer diameter is, for example, between 18 mm and 21 mm and is preferably constant over the sealing area.

[0014] Due to the enlarged sealing area outer diameter, the sealing device can be positioned and held completely in the actuation cylinder, in particular in the actuation cylinder, even if the piston rod has a large diameter, for example 10 mm. This means that no separate holding element is needed to hold the sealing device. The holding element can be, for example, a sleeve, in particular an aluminum sleeve, which is inserted into the piston rod end of the actuation cylinder. As a result, the gas spring is produced very easily and economically.

[0015] The compensating cylinder forms a projection that covers the working cylinder at its open end, with a closed end along the stroke axis.

[0016] At the piston rod end of the compensation cylinder which is opposite to the closed end along the stroke axis, the piston rod of the gas pressure spring is preferably led out of the compensation cylinder through a sealing device which preferably closes the piston rod end against gas.

[0017] The compensation piston separates from one another an actuating chamber arranged in the actuating cylinder, a compensation chamber arranged between the actuating cylinder and the compensation cylinder, and a reset chamber arranged preferably gas-tight in the projection.

[0018] The compensation piston preferably has a cylinder bottom on the underside of the compensation piston facing the reset chamber, the cylinder bottom being preferably aligned perpendicular to the stroke axis and / or being closed.

[0019] The compensation piston preferably comprises a cylinder jacket arranged partially between the working cylinder and the compensation cylinder. The cylinder jacket preferably extends around the stroke axis and / or is closed. Arranging the cylinder jacket partially between the working cylinder and the compensation cylinder has the advantage that the installation length of the gas pressure spring is reduced.

[0020] The compensation piston is open at its upper side facing the working chamber, which has the advantage that the gas pressure spring can be designed particularly compactly, since the interior of the compensation piston acts as part of the working chamber.

[0021] The compensation piston is preferably pot-shaped, with the cylinder bottom corresponding to the pot bottom and the cylinder jacket corresponding to the pot wall.

[0022] A hollow cylindrical or pot-shaped compensation piston has the advantage that the working, compensation and reset chambers can be separated with particularly low material requirements.

[0023] A compensation medium is preferably disposed within the compensation chamber, the compensation medium displacing the compensation piston towards the closed end when the compensation medium is heated.

[0024] The compensation medium preferably comprises an expanded material, in particular an expanded wax, particularly preferably a mixture of expanded wax and oil. The compensation medium can in particular consist of an expanded material, an expanded wax or a mixture of expanded wax and oil. The compensation medium can be designed, for example, like the compensation medium described in EP 1795777 (A2). The expanded wax can be designed, for example, like the expanded wax described in DE 102020113749 A1. The pressure of the compensation medium is, for example, between 70 bar and 350 bar.

[0025] A reset means is preferably disposed within the reset chamber, the reset means displacing the compensation piston away from the closed end when the compensation medium cools.

[0026] The reset means preferably comprises or is a reset gas, which is preferably the same gas that fills the actuation chamber as the actuation gas. The reset gas and / or actuation gas is, for example, nitrogen. The reset means may comprise or be formed of a mechanical reset element, for example a spring, in particular a compression coil spring.

[0027] The gas pressure of the working gas is, for example, 20 bar to 250 bar. The gas pressure of the reset gas is, for example, 20 bar to 350 bar.

[0028] The gas pressure spring is arranged above, in particular on, the compensation piston and is provided with a seal, in particular just one seal, which is preferably movable together with the compensation piston along the stroke axis, and which seals, in particular gas-tightly, the compensation piston from the working cylinder and the compensation cylinder.

[0029] In previously known gas pressure springs with temperature compensation, as described for example in EP 1795777 A2, at least two seals are required to seal the compensation piston against the working and compensating cylinders. The sealing of the working and compensating cylinders according to the invention with a single seal leads to a much simpler and more economical manufacture of the gas pressure spring and reduces possible leak points, thus allowing reliable operation of the gas pressure spring over a long service life.

[0030] In order for the seal to be able to seal both the working cylinder and the compensation cylinder, it must be located on the upper side of the compensation cylinder. Based on the prior art, locating the seal on the upper side of the compensation piston does not seem promising, since only a small contact surface is available on the open upper side for attaching the seal to the compensation piston.

[0031] However, tests surprisingly showed that it is not necessary to mount a seal on the compensation piston: in fact, during operation of the gas spring, the seal is pressed sufficiently strongly against the compensation piston by the pressure of the compensation medium, so that the seal reliably performs its sealing function.

[0032] Advantageously, the seal is not attached to the compensation piston, in particular not to the compensation piston, nor to the compensation or working cylinder, which makes it possible to produce the gas spring very easily and economically.

[0033] Description of the types of embodiments The compensation piston is preferably sealed against the working cylinder and the compensation cylinder only by seals. The gas pressure spring therefore does not include any additional seals between the working cylinder and the compensation piston and the compensation cylinder and is therefore particularly simple in design. The seals are preferably in one piece.

[0034] The seal preferably comprises a sealing ring, for example an O-ring, extending about the stroke axis. Particularly preferably, the seal is a sealing ring extending about the stroke axis.

[0035] The seal preferably comprises or consists of polyurethane and / or acrylonitrile butadiene rubber, which has the particular advantage that only low friction forces arise between the seal and the compensation cylinder.

[0036] The compensation piston is preferably in one piece and can be obtained, for example, by being formed from a compensation piston blank. A one-piece compensation piston has the advantage that the manufacture of the gas spring is simplified and the compensation piston does not include any connection points that could cause leakage.

[0037] The compensation piston preferably comprises or is made of aluminum or plastic. A particularly light and economical compensation piston can be produced from the above-mentioned materials. Due to the shape and arrangement of the compensation piston according to the invention, the compensation piston is stable even when using the above-mentioned materials, despite the high pressures that prevail in gas pressure springs.

[0038] The gas pressure spring preferably comprises a guide element for movably guiding the compensation piston relative to the compensation cylinder along the stroke axis, the guide element preferably comprising a guide sleeve arranged in a projection between the compensation cylinder and the compensation piston, in particular coaxially with the stroke axis. The guide element can be attached to the compensation piston or to the compensation cylinder. The guide element can, for example, be integrated with the compensation piston or the compensation cylinder. The guide element can, for example, comprise a guide ring, in particular of plastic, which can be fastened to the compensation piston, in particular by a locking connection. The guide element advantageously prevents tilting of the compensation piston relative to the working cylinder and the compensation cylinder, which could impair the sealing function of the seals in the compensation piston.

[0039] Preferably, the compensation piston comprises a cylinder rim, preferably adjacent to the upper side, which projects radially relative to the stroke axis beyond the cylinder jacket, and the seal is arranged on the cylinder rim, which provides an enlarged contact area between the seal and the compensation piston, so that the seal performs its sealing function particularly reliably. In addition, the seal can be moved more reliably along the stroke axis together with the compensation piston and, if necessary, can be attached to the compensation piston.

[0040] Preferably, the cylinder rim projects radially outward beyond the cylinder jacket, so that the reset chamber is increased for a given installation length, since an intermediate space is available for the reset means between the cylinder jacket and the compensation cylinder, which opens into the reset chamber. As a result, the reset means has a lower pressure, which makes sealing of the gas spring easier. In order to prevent the compensation piston from getting stuck in the compensation cylinder, despite the cylinder rim projecting radially outward, the gas pressure spring in this embodiment preferably comprises the aforementioned guide element. The guide element is preferably attached to the compensation piston or designed integrally with the compensation piston, so that the guide element and the cylinder rim do not interfere with each other.

[0041] The distance of the compensation cylinder from the working cylinder, measured radially to the stroke axis, is preferably greater in the stroke region than in an end region of the working cylinder located between the stroke region and the open end of the working cylinder.

[0042] The smaller distance in the end region results in a smaller cross-sectional area of ​​the compensation chamber perpendicular to the stroke axis in the end region, so that for a given temperature rise, the compensation piston is displaced further towards the closed end of the compensation cylinder by the expansion of the compensation medium, so that the working chamber is further enlarged and a greater compensation of the temperature dependence of the spring force of the gas pressure spring is provided.

[0043] Since the distance in the stroke region of the working piston is not shortened, the compensation chamber can still contain a sufficient amount of compensation medium for effective temperature compensation.

[0044] For example, the distance in the end region is 10% to 50%, preferably 20% to 40%, particularly preferably 30% smaller than in the stroke region. The distance in the end region is, for example, 1 mm to 8 mm, preferably 2 mm to 4 mm, particularly preferably 2.5 mm. The distance in the stroke region is, for example, 2 mm to 12 mm, preferably 3 mm to 6 mm, particularly preferably 3 mm to 3.5 mm. With the abovementioned distance values, a large, particularly complete compensation of the temperature dependence of the spring force of the gas pressure spring can be achieved over a typical operating temperature range of gas pressure springs, for example from -10 ° C to +60 ° C.

[0045] Preferably, the distance of the compensation cylinder from the working cylinder in the end region and / or stroke region is independent of the position along the stroke axis. In this embodiment, the distance is constant in the end region and / or stroke region along the stroke axis, which makes the gas pressure spring very easy to make.

[0046] The end area outer diameter of the working cylinder, measured radially to the stroke axis, is preferably larger in the end area of ​​the working cylinder than the stroke area outer diameter of the working cylinder, measured radially to the stroke axis in the stroke area. Such an expansion of the working cylinder in the end area shortens the distance between the working cylinder and the compensation cylinder without changing the shape of the compensation cylinder or the working cylinder in the stroke area. Thus, the shortened distance is achieved with as few modifications as possible compared to gas pressure springs from the prior art. The gas pressure spring can therefore be produced particularly easily and economically, in particular using known components and methods.

[0047] The end region outer diameter of the working cylinder is preferably 101% to 150%, preferably 105% to 130%, particularly preferably 110% to 120%, most preferably 112% to 113% of the stroke region outer diameter of the working cylinder. The end region outer diameter is, for example, 15 mm to 25 mm, preferably 16 mm to 22 mm, particularly preferably 18 mm to 21 mm. The stroke region outer diameter is, for example, 10 mm to 20 mm, preferably 15 mm to 19 mm, particularly preferably 17 mm to 18 mm. With the above-mentioned values ​​of the outer diameter, a large compensation of the temperature dependence of the spring force of the gas pressure spring can be achieved over the typical operating temperature range of gas pressure springs.

[0048] Preferably, the outer diameter of the working cylinder in the end regions and / or in the stroke region is independent of the position along the stroke axis. In this embodiment, the distance is constant in the end regions and / or in the stroke region along the stroke axis, which makes the gas pressure spring very easy to make.

[0049] The compensation cylinder inner diameter of the compensation cylinder, measured radially to the stroke axis, is preferably 110% to 200%, preferably 140% to 170%, particularly preferably 150% to 160%, most preferably 155% to 157% of the stroke area outer diameter of the working cylinder. The compensation cylinder inner diameter is, for example, 20 mm to 30 mm, preferably 23 mm to 27 mm, particularly preferably 25 mm. With the above-mentioned values ​​of the compensation cylinder inner diameter, a large compensation of the temperature dependence of the spring force of the gas pressure spring can be achieved over the typical operating temperature range of gas pressure springs.

[0050] Preferably, the inner diameter of the compensation cylinder is independent of the position along the stroke axis. In this embodiment, the inner diameter of the compensation cylinder is constant along the stroke axis, which makes the gas pressure spring very easy to make.

[0051] The stroke region and the end region of the actuating cylinder are preferably integrally connected to one another. The stroke region and the end region can be connected to one another, for example, by a material bond, in particular they can be welded, soldered and / or glued to one another. The stroke region and the end region can be connected to one another, for example, in a form-fit and / or force-fit manner, in particular they can be screwed, latched and / or clamped to one another.

[0052] The actuating cylinder may, for example, comprise or consist of metal, in particular steel, and / or plastic.

[0053] The wall thickness of the actuating cylinder radially to the stroke axis is preferably substantially the same in the stroke and end regions of the actuating cylinder, preferably independent of the position along the stroke axis, except for a reduction in the wall thickness caused by the expansion of the actuating cylinder, especially in the end regions, for example a reduction of up to 0.2 mm. In this embodiment, the wall thickness of the actuating cylinder is constant along the stroke axis, which makes it particularly easy to make a gas pressure spring.

[0054] The wall thickness of the compensation cylinder radial to the stroke axis is preferably independent of the position along the stroke axis. In this embodiment, the wall thickness of the compensation cylinder is constant along the stroke axis, which makes it particularly easy to make a gas pressure spring.

[0055] The working cylinder and / or the compensating cylinder preferably comprise a non-uniformly drawn tube, for example a tube having a welded seam along the stroke axis.

[0056] A method for manufacturing a gas pressure spring includes forming or machining a compensation piston blank into a compensation piston. The compensation piston can be made, for example, by deep drawing a compensation piston blank made of aluminum.

[0057] The method preferably comprises providing an actuation cylinder blank, preferably in the form of a non-uniformly drawn tube, which is shaped as a hollow cylinder and has an outside diameter transverse to its longitudinal axis that is independent of its position along the longitudinal axis. The outside diameter is therefore constant along the stroke axis. The actuation cylinder blank may in particular be an actuation cylinder of a known gas pressure spring. The actuation cylinder blank preferably has material properties that depend on the azimuth angle to its longitudinal axis, for example by means of a weld seam along the longitudinal axis. Such an actuation cylinder blank can be produced very easily and cheaply, in that it is drawn and welded from steel, for example.

[0058] The method preferably includes forming an actuation cylinder blank into an actuation cylinder of the gas pressure spring, the forming including widening an outer diameter of the actuation cylinder blank in at least one end region of the actuation cylinder blank.

[0059] The expanding preferably comprises inserting a mandrel into at least one end region and preferably, prior to inserting the mandrel, placing a sleeve extending about the longitudinal axis around the end region of the working cylinder blank, so that the end region abuts the sleeve after expanding. This advantageously allows the diameter of the working cylinder blank, whose material properties depend on the azimuth angle relative to its longitudinal axis, to be expanded to a diameter that is azimuth independent. [Brief description of the drawings]

[0060] [Figure 1] 1 shows, by way of example, a schematic longitudinal section along the stroke axis of an embodiment of a gas pressure spring according to the invention. [Diagram 2] By way of example, a schematic longitudinal section along the stroke axis of a further embodiment of a gas pressure spring according to the invention is shown in FIG.

[0061] FIG. 1 shows a schematic longitudinal section along a drive axis A of a linear drive 50 according to the invention.

[0062] The illustrated gas pressure spring 50 comprises a working piston 2 which is movably guided in a working cylinder 1 along a stroke axis H over a stroke range HB, a compensation cylinder 12 which surrounds the working cylinder 1 radially relative to the stroke axis H, and a compensation piston 10 which is shaped like a hollow cylinder and is movably guided in the compensation cylinder 12 along the stroke axis H relative to the working cylinder 1 and the compensation cylinder 12.

[0063] The working cylinder 1 has an open end 1b along the stroke axis H, and the compensation cylinder 12 forms at the open end 1b a projection 15 which covers the working cylinder 1 having a closed end 15b along the stroke axis H.

[0064] The compensation piston 10 separates an actuation chamber 1a, which is arranged in the actuation cylinder 1, a compensation chamber 12a, which is arranged between the actuation cylinder 1 and the compensation cylinder 12, and a reset chamber 15a, which is arranged in the protrusion 15, from each other.

[0065] The compensation piston 10 comprises a cylinder bottom 10b and a cylinder jacket 10c which is partially arranged between the working cylinder 1 and the compensation cylinder 12 on its underside facing the reset chamber 15a. The compensation piston 10 is open on its upper side 10a facing the working chamber 1a.

[0066] The gas pressure spring 50 comprises a seal 8, for example a sealing ring, arranged on the upper side 10a of the compensation piston 10, concentric with the stroke axis H. The seal 8 seals the compensation piston 10 from the working cylinder 1 and the compensation cylinder 12.

[0067] At the piston rod end 1c of the working cylinder 1 opposite the open end 1b along the stroke axis H, the piston rod 6 attached to the working piston 2 is preferably led out of the working cylinder 1 through a sealing device 20.

[0068] In the embodiment shown in FIG. 1, the distance of the compensation cylinder 12 from the working cylinder 1, measured radially to the stroke axis H, is greater in the stroke region HB than in the end region EB of the working cylinder 1, which is between the stroke region HB and the open end 1b of the working cylinder 1.

[0069] In this embodiment, the reduction in distance in the end region EB occurs because the end region outer diameter EAD of the working cylinder 1, measured radially to the stroke axis H, is greater than the stroke region outer diameter HAD of the working cylinder 1 in the stroke region HB, measured radially to the stroke axis H. The end region outer diameter EAD is, for example, 18 mm to 21 mm and is preferably constant over the end region EB. The stroke region outer diameter HAD is, for example, 17 mm to 18 mm and is preferably constant over the stroke region HB.

[0070] The compensation cylinder inner diameter AID of the compensation cylinder 12 is, for example, 25 mm and is preferably constant along the stroke axis H. Figure 2

[0071] FIG. 2 shows a schematic longitudinal section along the stroke axis H of a further embodiment of a gas pressure spring 50 according to the invention.

[0072] The gas pressure spring 50 shown in Figure 2 differs from the gas pressure spring 50 shown in Figure 1 in that the working cylinder 1 has a sealing area outer diameter DAD, measured radially to the stroke axis H, in a sealing area DB between the stroke area HB and the piston rod end 1c of the working cylinder 1, where the piston rod 6 leaves the working cylinder 1, which sealing area outer diameter DAD is greater than the stroke area outer diameter HAD of the working cylinder 1. The sealing area outer diameter DAD is, for example, between 18 mm and 21 mm and is preferably constant over the sealing area DB. [Explanation of symbols]

[0073] 1 Working Cylinder 1a Inner working chamber 1b Open end 1c Piston rod end 2 Working piston 6 Piston rod 8. Seal 10 Compensating piston 10a Upper 10b Cylinder bottom 10c Cylinder Jacket 10d cylinder rim 12 Compensating cylinder 12a Compensation chamber 15 Protrusion 15a Reset Chamber 15b Closed end 18 Guidance elements 20 Sealing device 50 Gas pressure spring AID compensation cylinder inner diameter DAD sealing area outer diameter DB Ceiling Area EAD end area outer diameter EB edge area H Stroke Axis HAD Stroke Area Outer Diameter HB Stroke Area

Claims

1. A gas pressure spring (50), a. an actuating piston (2) movably guided in an actuating cylinder (1) along a stroke axis (H) over a stroke region (HB); b. a compensation cylinder (12) surrounding said working cylinder (1) in a radial direction relative to said stroke axis (H); c) a hollow cylindrical compensation piston (10) movably guided in the compensation cylinder (12) along the stroke axis (H); d. The actuating cylinder (1) has an open end (1b) along the stroke axis (H); e. the compensating cylinder (12) forms a protrusion (15) covering the working cylinder (1) at the open end (1b) and having a closed end (15b) along the stroke axis (H); f. The compensation piston (10) i. hermetically separating an actuation chamber (1 a) disposed in the actuation cylinder (1), a compensation chamber (12 a) disposed between the actuation cylinder (1) and the compensation cylinder (12), and a reset chamber (15 a) disposed in the protrusion (15) from each other; ii. open at the upper side (10a) of the compensation piston (10) facing the working chamber (1a); g. A gas pressure spring (50) characterized by a seal (8) arranged on the upper side (10a) of the compensation piston (10), sealing the compensation piston (10) from the working cylinder (1) and the compensation cylinder (12).

2. 2. A gas pressure spring (50) according to claim 1, characterized in that the compensation piston (10) is sealed from the working cylinder (1) and the compensation cylinder (12) only by the seal (8).

3. 2. A gas pressure spring (50) according to claim 1, characterized in that the seal (8) comprises a sealing ring extending around the stroke axis (H), preferably a sealing ring extending around the stroke axis (H).

4. A gas pressure spring (50) according to any one of claims 1 to 3, characterized in that the seal (8) comprises polyurethane and / or acrylonitrile-butadiene rubber, preferably consisting of polyurethane or acrylonitrile-butadiene rubber.

5. A gas pressure spring (50) according to any one of claims 1 to 3, characterized in that the compensation piston (10) is in one piece.

6. A gas pressure spring (50) according to any one of claims 1 to 3, characterized in that the compensation piston (10) comprises, preferably consists of, aluminum or plastic.

7. 4. A gas pressure spring (50) according to claim 1, characterized in that the guide element (18) movably guides the compensation piston (10) relative to the compensation cylinder (12) along the stroke axis (H), the guide element (18) preferably comprising a guide sleeve arranged in the projection (15) between the compensation cylinder (12) and the compensation piston (10).

8. a. The compensation piston (10) comprises a cylinder jacket (10c) partially disposed between the working cylinder (1) and the compensation cylinder; b) the compensating piston (10) comprises a cylinder rim (10d) adjacent to the upper side (10a) and projecting beyond the cylinder jacket (10c) in a radial direction relative to the stroke axis (H); A gas pressure spring (50) according to any one of claims 1 to 3, characterized in that the seal (8) is arranged on the cylinder rim (10d).

9. 4. A gas pressure spring (50) according to claim 1, characterized in that the distance of the compensation cylinder (12) from the working cylinder (1), measured radially relative to the stroke axis (H), is greater in the stroke region (HB) than in an end region (EB) of the working cylinder (1) between the stroke region (HB) and the open end (1b) of the working cylinder (1).

10. 10. The gas pressure spring (50) according to claim 9, characterized in that an end area outer diameter (EAD) of the actuating cylinder (1) measured radially to the stroke axis (H) is greater than a stroke area outer diameter (HAD) of the actuating cylinder (1) in the stroke area (HB) measured radially to the stroke axis (H).

11. 10. A gas pressure spring (50) according to claim 9, characterized in that the stroke region (HB) and the end region (EB) of the working cylinder (1) are integrally connected to one another.

12. 4. The gas pressure spring (50) according to claim 1, wherein the actuating cylinder (1) has, in a sealing area (DB) between the stroke area (HB) and a piston rod end (1c) of the actuating cylinder (1) opposite the open end (1b) along the stroke axis (H) at which a piston rod (6) attached to the actuating piston (2) emerges from the actuating cylinder (1), a sealing area outer diameter (DAD) measured radially relative to the stroke axis (H), the sealing area outer diameter (DAD) being larger than the stroke area outer diameter (HAD) of the actuating cylinder (1).

13. A method for manufacturing a gas pressure spring (50) according to any one of claims 1 to 3, comprising the steps of: A method characterized by the step of forming or machining a compensating piston blank into said compensating piston (10).

14. a. providing an actuation cylinder blank, said actuation cylinder blank being shaped as a hollow cylinder and having an outer diameter transverse to its longitudinal axis that is independent of its position along said axis; b. forming the actuation cylinder blank into the actuation cylinder (1) of the gas pressure spring (50); 14. The method of claim 13, wherein said forming step includes widening said outer diameter of said actuation cylinder blank in at least one end region of said actuation cylinder blank.

15. 15. The method of claim 14, wherein the expanding comprises inserting a mandrel into the at least one end region and, preferably, before inserting the mandrel, placing a sleeve extending about the longitudinal axis around the end region such that the end region abuts the sleeve after expansion.

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