Dampers, especially hydraulic dampers

Abstract

mute a. comprising a housing (2) i. a longitudinal axis (5) and ii. a working space (8) enclosed by the housing (2), b. with a damping fluid located at least partially in the work space (8), c. comprising a piston unit (10) i. a piston rod (11) which can be displaced along the longitudinal axis (5) and which is sealed at one housing end (3) and leads out of the housing (2), ii. a piston (12; 12a) attached to the piston rod (11), which divides the working space (8) into a first partial working space (14) and a second partial working space (15), iii. a flow channel (16) connecting the first partial work chamber (14) and the second partial work chamber (15), iv. a compensation room (22) which is connected to the first sub-workroom (14) and / or to the second sub-workroom (15), v. an adjusting element (27) for adjusting a flow cross-sectional area of ​​the flow channel (16), wherein the adjusting element (27) can be moved between an open position in which the flow cross-sectional area is maximal and a closed position in which the flow cross-sectional area is minimal, wherein fluid flow between the compensation chamber (22) and the partial working chambers (14, 15) is prevented in the closed position, characterized by vi. a compensating channel (20, 21, 26) connected to the flow channel (16) and connected to the compensating chamber (22), wherein in the closed position of the adjusting element (27) a fluid flow from the flow channel (16) into the compensating channel (20, 21, 26) is prevented.

Description

[0001] The invention relates to a damper, in particular a hydraulic damper.

[0002] DE 10 2010 029 180 A1 discloses a hydraulic damper designed as a twin-tube damper.

[0003] DE 10 2013 008 888 A1 discloses a vibration damper for a vehicle.

[0004] US 5 316 114 A discloses a friction-controlled hydraulic shock absorber.

[0005] AT 219 435 B discloses a hydraulic monotube vibration damper.

[0006] The invention is based on the object of providing a damper, in particular a hydraulic damper, which is designed to be small and has the same functionality as a twin-tube damper, in particular the adjustability of the damper up to a blockage, the freedom of idle stroke and / or the position independence.

[0007] The object is achieved according to the invention by a damper having the features of claim 1. The damper, which is designed in particular as a hydraulic damper, comprises a housing with a longitudinal axis and with a working chamber enclosed by the housing. A damping fluid, in particular a hydraulic medium, in particular oil, in particular a hydraulic oil, or gas, in particular air, is provided in the working chamber. The damper further comprises a piston unit which has a piston rod which is displaceable along the longitudinal axis and is arranged in particular concentrically to the longitudinal axis. At one housing end, the piston rod is led out of the housing in a sealed manner. The piston unit further comprises a piston fastened to the piston rod, which piston is displaceable in a sealed manner, in particular within the housing. The piston divides the working chamber into a first partial working chamber and a second partial working chamber.The partial working chambers are connected to each other via a flow channel. Furthermore, the piston unit comprises a compensation chamber that can be connected to the first partial working chamber and / or to the second partial working chamber. In particular, the compensation chamber can be connected to the first partial working chamber and / or to the second partial working chamber via the flow channel. The compensation chamber serves to accommodate the damping fluid displaced as a result of the piston rod being pushed in.

[0008] The piston unit further comprises an adjusting element for adjusting a flow cross-sectional area of ​​the flow channel. The adjusting element can in particular be displaced from an open position, in which the flow cross-sectional area is maximum, to a closed position, in which the flow cross-sectional area is minimal and in particular equal to zero. In the closed position, the flow channel is closed. Flow of the damping fluid through the flow channel is prevented in the closed position. In the closed position of the adjusting element, displacement of the piston unit is prevented. In the closed position of the adjusting element, the damper is reliably blocked. In the closed position, the first partial working chamber is reliably separated from the second partial working chamber. Fluid flow from the first partial working chamber into the second partial working chamber is prevented.In the closed position, the compensation chamber is also separated from the first partial working chamber and the second partial working chamber. Fluid flow between the compensation chamber and the partial working chambers is prevented. In particular, the compensation chamber is fluidically separated from the working chamber in the closed position of the adjusting element.

[0009] The adjustment element can be moved continuously, i.e., steplessly, between the open and closed positions. Alternatively, a stepped adjustment of the adjustment element with discrete adjustment steps is conceivable. This allows defined, predefined damping levels to be set easily and with repeatable accuracy. A stepped adjustment of the adjustment element is conceivable, for example, by a mechanical ratchet on the adjustment element, which corresponds to a locking element that engages the ratchet, allowing defined damping levels to be set. The risk of a damping level set in this way being accidentally changed is eliminated.

[0010] The adjustment element can be adjusted inside or outside the damper. For further information, see DE 10 2016 209 824 A1 and DE 10 2016 209 826 A1.

[0011] Because the compensation chamber is located in the piston unit and, in particular, integrated into the piston unit, the damper is designed to be compact. In particular, the required installation space is reduced compared to the twin-tube damper known from the prior art, whereby the damper according to the invention, in particular, has the same functionality as the twin-tube damper.

[0012] The damper according to the invention enables a position-independent damping function, i.e., independent of the damper's inclination angle relative to the horizontal. In particular, the damper's damping function is independent of whether the damper is installed with the piston rod tilted upwards, i.e., against gravity, or downwards, i.e., with gravity.

[0013] The damper according to the invention ensures zero idle stroke. This means that every extension or retraction of the piston unit causes a displacement of the damping fluid and thus a damping effect.

[0014] The damper according to the invention allows the damping effect to be adjusted up to the point of blocking the damper.

[0015] A compensating channel, which can be connected to the flow channel and is connected to the compensating chamber, simplifies the fluid connection between the compensating chamber and the flow channel. In particular, the compensating channel can be separated from the flow channel by the adjusting element. In the closed position of the adjusting element, fluid flow from the flow channel into the compensating channel is prevented.

[0016] A damper according to claim 2 is designed to be particularly simple. The damper is particularly compact. The damper housing is designed to be simple and cost-effective. The damper is robust.

[0017] A damper according to claim 3 features increased functional integration. Because the flow channel is at least partially integrated into the piston rod, an additional component for the flow channel is unnecessary. In particular, the flow channel is integrated exclusively into the piston rod. In particular, the flow channel runs within the piston rod.

[0018] A damper according to claim 4 enables an uncomplicated connection of the flow channel with the first and / or second partial working chamber. At least one transverse bore and in particular several transverse bores are provided on the piston rod. The flow cross-sectional area of ​​the flow channel is predetermined by the cross-sectional area of ​​the at least one transverse bore. It is possible to variably adjust the size of the flow cross-sectional area by changing the number of transverse bores, the size of the individual transverse bores and / or the contour of the transverse bores. In particular, the transverse bores are each designed identically. However, the transverse bores can also be designed differently. The transverse bores can be offset from one another along the longitudinal axis. Additionally or alternatively, several transverse bores can be arranged along a circumferential line, i.e. in a plane perpendicular to the longitudinal axis.

[0019] In a damper according to claim 5, the flow channel is easily integrated into the piston rod. In particular, the piston rod has an inner cylindrical surface. The outer surface of the piston rod can be cylindrical or have a non-circular outer contour. In particular, the piston rod has a hollow space.

[0020] A damper according to claim 6 simplifies the adjustment of the damping effect. In particular, the adjustment element is arranged outside the housing. An adjustment lever of the adjustment element is oriented, in particular, radially to the longitudinal axis.

[0021] A damper according to claim 7 is designed to be particularly compact. The adjusting element is integrated into the piston rod. The adjusting element is designed, in particular, as a rod or needle, which is rotatable relative to the piston rod and, in particular, is arranged rotatably within the piston rod.

[0022] A damper according to claim 8 is particularly small and compact and has a robust construction. In particular, the compensation chamber is enclosed by the piston and the housing. In an advantageous embodiment, the compensation chamber is completely enclosed by the piston.

[0023] In a damper according to claim 9, a return flow of the damping fluid from the compensation chamber into one of the partial working chambers is improved.

[0024] A compensating element according to claim 10 enables improved return flow of the damping fluid from the compensating chamber into one of the partial working chambers. The compensating element comprises, in particular, a foamed cellular rubber as a compressible material.

[0025] Both the features specified in the patent claims and the features specified in the following exemplary embodiments of the damper according to the invention are suitable, either individually or in combination with one another, for further developing the subject matter of the invention. The respective combinations of features do not represent any limitation with regard to further developments of the subject matter of the invention, but are essentially merely exemplary in nature.

[0026] Further features, advantages, and details of the invention will become apparent from the following description of exemplary embodiments with reference to the drawings. In these: Fig. 1 a sectional, perspective view of a damper according to the invention according to a first embodiment, Fig. 2 an enlarged sectional view of a piston unit of the damper according to Fig. 1 in an unblocked arrangement, Fig. 3 a Fig. 2 corresponding representation of the damper in a blocked arrangement, Fig. 4 a Fig. 1 corresponding representation of a damper according to a second embodiment, in which the compensation chamber is completely enclosed by the piston, Fig. 5 an enlarged sectional view of the piston unit of the damper in Fig. 4 in an unblocked arrangement, and Fig. 6 a Fig. 5 corresponding representation of the damper in a blocked arrangement.

[0027] A damper 1 comprises a tubular housing 2 with a first housing end 3 and an oppositely arranged second housing end 4. The housing 2 is designed as a cylindrical tube. The housing 2 has a longitudinal axis 5.

[0028] At the first housing end 3, the housing 2 is provided with an opening that is closed by a guide and sealing unit 6. The second housing end 4 is closed by a bottom wall 7. A second fastening element 9 is provided at the second housing end 4. The second fastening element 9 is fastened, in particular welded, to an outer side of the bottom wall 7. The housing 2 encloses a working chamber 8. The working chamber 8 is filled with a damping fluid. The damping fluid is in particular oil, in particular a hydraulic oil.

[0029] The damper 1 further comprises a piston unit 10 with a piston rod 11 and a piston 12. The piston 12 is attached to the piston rod 11 and guided displaceably in the housing 2 along the longitudinal axis 5. The piston rod 11 is sealed out of the housing 2 by the guide and sealing unit 6. At its end opposite the piston 12, the piston rod 11 is connected to a first fastening element 13.

[0030] The piston 12 divides the working chamber 8 into a first partial working chamber 14, which faces the first housing end 3, and a second partial working chamber 15, which faces the second housing end 4. The first partial working chamber 14 is delimited by the housing 2, the guide and sealing unit 6, and the piston 12. The second partial working chamber 15 is delimited by the housing 2, the piston 12, and the bottom wall 7. The first partial working chamber 14 and the second partial working chamber 15 are interconnected by a flow channel 16.

[0031] The piston 12 comprises two, in particular identically designed, annular discs 17, which are arranged on the piston rod 11 at a distance from one another with respect to the longitudinal axis 5. On their outer side, the annular discs 17 each have an annular sealing element 18, which is inserted into a designated outer groove on the annular disc 17.

[0032] The annular discs 17 are mounted with a clearance fit on the piston rod 11 and are fixed to the piston rod 11 by means of a fastening element (not shown), in particular a retaining nut. A spacer sleeve 19 is arranged between the two annular discs 17. According to the exemplary embodiment shown, the fixing of the annular discs 17 to the piston rod 11 can be effected, for example, by the annular disc 17 facing the first housing end 3, which in Fig. 2, shown on the left, rests against a radially projecting contact shoulder 35 of the piston rod 11. The axial distance between the annular discs 17 is guaranteed by the spacer sleeve 19. The annular disc 17 facing the second housing end 4, which in Fig. 2 is arranged on the right, is fixed to the piston rod 11 by the retaining nut not shown.

[0033] Alternatively, it is conceivable that the annular disc 17 facing the second housing end 4 has an internal thread and is screwed directly onto an external thread of the piston rod 11, thereby fixing the piston 12 as a whole to the piston rod 11. In this case, a separate retaining nut would be unnecessary. Alternatively, each of the annular discs 17 can be axially fixed by a retaining nut.

[0034] The spacer sleeve 19 is mounted on the piston rod 11 with a clearance fit. The spacer sleeve 19 is essentially hollow-cylindrical. An inner diameter of the spacer sleeve 19 essentially corresponds to the outer diameter of the piston rod 11. The spacer sleeve 19 has a circumferential inner groove 20 on its inner surface facing the piston rod 11. The inner groove 20 extends in particular along the entire inner circumference of the spacer sleeve 19. The spacer sleeve 19 further has at least one transverse channel 21, which is fluidically connected to the inner groove 20. The transverse channel 21 is oriented transversely, in particular vertically and in particular radially, with respect to the longitudinal axis 5.

[0035] The piston 12 has a compensation chamber 22, which is annular in shape. The compensation chamber 22 is defined in the axial direction by the two annular discs 17. In the radial direction relative to the longitudinal axis 5, the compensation chamber 22 is enclosed on its inner side by the spacer sleeve 19 and on its outer side by the housing 2. The compensation chamber 22 is partially filled with the damping fluid. The remainder of the compensation chamber 20 is filled with a gas, in particular air.

[0036] A volume compensation element, also referred to as compensation element 23, is arranged in the compensation chamber 22. The compensation element 23 comprises, in particular, a compressible material, in particular a foamed cellular rubber. It is also possible to omit the compensation element 23. In this case, the compensation chamber 22 is designed as a hollow chamber.

[0037] The transverse channel 21 flows into the compensation chamber 22.

[0038] The piston rod 11 is tubular and has an inner cavity 25. At least one first transverse bore 24 is arranged in the piston rod 11. Several first transverse bores 24 can also be provided, which are in particular identical in design. According to the exemplary embodiment shown, the first transverse bore is designed with a round flow cross-sectional area. The first transverse bore 24 can have a different flow cross-sectional area, in particular with a different contour. The first transverse bore 24 is designed as a through-opening through the annular-cylindrical piston rod 11. The first transverse bore 24 enables a fluid connection from the first partial working chamber 14 into the inner cavity 25 of the piston rod 11. The cavity 25 opens into the second partial working chamber 15 in the axial direction relative to the longitudinal axis 5. The flow channel 16 comprises the cavity 25 and the at least one first transverse bore 24.The first transverse bore 24 is arranged between the piston 12 and the guide and sealing unit 6 with respect to the longitudinal axis 5. Regardless of the insertion position of the piston rod 11 with the piston 12 in the housing 2, the first transverse bore 24 always opens into the first partial working chamber 14.

[0039] The piston rod 11 has at least one second transverse bore 26, in particular a plurality of second transverse bores 26, which enables a fluid connection of the cavity 25 via the inner groove 20 and the transverse channel 21 into the compensation chamber 22. According to the exemplary embodiment shown, the at least one second transverse bore 26 is identical to the at least one first transverse bore 24. The second transverse bore 26 can have a different size and / or contour than the first transverse bore 24. The at least one second transverse bore 26, the inner groove 20, and the transverse channel 21 form a compensation channel that can be connected to the flow channel 16. It is conceivable to dispense with the inner groove 20. By using the inner groove 20, the assembly of the spacer sleeve 19 on the piston rod 11 is simplified, in particular independent of a rotational position relative to the longitudinal axis 5.

[0040] An adjusting element 27 is arranged in the cavity 25 of the piston rod 11. The adjusting element 27 is arranged concentrically to the longitudinal axis 5. The adjusting element 27 is sealed in the piston rod 11 by means of a sealing ring 28. To accommodate the sealing ring 28, the adjusting element 27 can have an outer groove into which the sealing ring 28 is inserted. Otherwise, the adjusting element 27 is designed as a solid cylinder. The adjusting element 27 is designed as a rod or a needle.

[0041] The adjusting element 27 is mounted in the piston rod 11 with no play in the radial direction relative to the longitudinal axis 5. The adjusting element 27 has a recess 29 at a first end arranged in the housing 2. The recess 29 is shaped like a segment of a circle in a plane perpendicular to the longitudinal axis 5. The recess 29 flattens the adjusting element 27 at its first end. Along the longitudinal axis 5, the recess 29 extends from an area located at the level of the first partial working chamber 14 to beyond the second transverse bores 26. The first transverse bores 24 and the second transverse bores 26 can be exposed or covered by the adjusting element 27 through the recess 29. The recess 29 is part of the flow channel 16. The cavity 25 of the piston rod 11 is partially exposed through the recess 29.

[0042] At a second end opposite the first end, the adjusting element 27 has an adjusting lever 30. The adjusting lever 30 is arranged in the region of the first fastening element 13 and connected to the adjusting element 27. The first fastening element 13 has a recess 31 for this purpose. The adjusting lever 30 is arranged in particular in a bore in the adjusting element 27. The bore runs in particular perpendicular to the longitudinal axis 5. Provision can be made for the adjusting lever 30 to be screwed into the bore with an external thread into a matching internal thread. This simplifies assembly. The adjusting lever 30 is easily replaceable.

[0043] The adjusting element 27 can be rotated in the cavity 25 of the piston rod 11 via the adjusting lever 30. The adjusting element 27 is rotatably mounted in the piston rod 11.

[0044] The adjustability of the flow cross-sectional area of ​​the flow channel 16 and the compensation channel 26, 20, 21 is explained in more detail below.

[0045] Fig. Figure 2 shows the damper in an unblocked configuration. In the unblocked configuration, the adjusting element 27 is arranged in the cavity 25 of the piston rod 11 such that a fluid connection is established from the first partial working chamber 14 via the first transverse bores 24 into the recess 29. This enables fluid flow from the first partial working chamber 14 into the second partial working chamber 15 and vice versa. Furthermore, fluid flow is possible from the partial working chambers 14, 15 via the flow channel 16 and the compensation channel 26, 20, 21 into the compensation chamber 22 and in the reverse direction.

[0046] Because the adjusting element 27 is in accordance with Fig. 2 is in the open position, the first transverse bores 24 and the second transverse bores 26 are completely exposed by the adjusting element 27. The flow cross-sectional area of ​​the flow channel 16 is at its maximum.

[0047] The flow cross-sectional area is adjusted by actuating the adjusting element 27, in particular by rotating the adjusting element 27 about the longitudinal axis 5.

[0048] Rotation of the adjusting element 27 occurs in particular by actuating the adjusting lever 30. Rotation of the adjusting element 27 causes a relative displacement of the recess 29 with respect to the first transverse bores 24 and the second transverse bores 26. Upon rotation of the adjusting element 27, the first transverse bores 24 and the second transverse bores 26 are successively covered. Depending on the rotational movement, i.e., the size of the angle of rotation of the adjusting element 27 with respect to the longitudinal axis 5, the area of ​​the first transverse bores 24 and the second transverse bores 26 sealed by the adjusting element 27 can be variably adjusted. As a result, the flow cross-sectional area of ​​the flow channel 16, in particular the flow cross-sectional area into the flow channel 16, can be variably adjusted.

[0049] At the Fig. In the arrangement shown in Figure 3, the adjusting element 27 is in the closed position. In the closed position, at least the first transverse bores 24 and in particular also the second transverse bores 26 are completely covered by the adjusting element 27. Fluid flow through the flow channel 16 and in particular into the compensation channel 26, 20, 21 is thereby blocked. The damper 1 is in a blocking arrangement. Actuation of the damper in both the insertion direction 32 and the extension direction 33 is prevented, i.e., blocked.

[0050] According to the illustrated embodiment, the first transverse bores 24 and the second transverse bores 26 are arranged identically on the piston rod 11 with respect to a rotational angle position about the longitudinal axis 5. As a result, the first transverse bores 24 and the second transverse bores 26 are simultaneously covered upon rotation of the adjusting element 27.

[0051] It is fundamentally conceivable to arrange the first transverse bores 24 and the second transverse bores 26 offset from one another with respect to their rotational position on the piston rod 11, so that when the adjusting element 27 is in a rotational position, the first transverse bores 24 are covered for a fluid connection to the first partial working chamber 14, but the second transverse bores 26 can be arranged at least partially exposed for a fluid connection to the compensation chamber 22. Accordingly, a reverse setting is also conceivable, according to which a fluid connection to the first partial working chamber 14 via the first transverse bores 24 is at least partially opened and a fluid connection via the second transverse bores 26 into the compensation chamber 22 is blocked.

[0052] The smaller the flow cross-sectional area that can be variably set by the adjusting element 27, the greater the throttling effect of the hydraulic damper 1. The damping of the hydraulic damper 1 is harder, the smaller the flow cross-sectional area of ​​the flow channel 16 is.

[0053] The function of the damper is described below.

[0054] In the damper 1, the adjusting element 27 is in the Fig. 2. The damper 1 is unblocked. When the piston rod 11 with the piston 12 moves in the insertion direction 32, damping fluid flows from the second partial working chamber 15 via the flow channel 16 into the first partial working chamber 14. The damping fluid is decelerated as it flows through the flow channel 16, causing the damping effect. Since the flow cross-sectional area of ​​the flow channel 16 is at its maximum in the open position of the adjusting element 27, the damping effect of the damper 1 is minimal in this arrangement. The damper has a soft damping characteristic.

[0055] By inserting the piston rod 11, volume is displaced in the first partial working chamber 14. The damping fluid thus displaced can flow from the working chamber 8, in particular the first partial working chamber 14, via the flow channel 16 and the compensation channel 26, 20, 21 into the compensation chamber 20.

[0056] When the piston rod 11 is actuated in the extension direction 33, the fluid flows accordingly in the opposite direction.

[0057] When the adjusting element 27 is adjusted as described above, the fluid flows are in principle identical, whereby with a reduced flow cross-sectional area of ​​the flow channel 16 the damping effect is increased, i.e. the damper 1 has a harder damping characteristic.

[0058] If the adjusting element 27 is in the Fig. 3, the flow of damping fluid in the housing 2 is blocked. Actuation of the damper 1 is then reliably prevented in both the insertion direction 32 and the extension direction 33.

[0059] In the following, with reference to Fig.4 to 6, a second embodiment of the invention is described. Structurally identical parts are given the same reference numerals as in the first embodiment, to the description of which reference is hereby made. Structurally different but functionally similar parts are given the same reference numerals with a suffix "a."

[0060] A key difference compared to the first embodiment is that the piston 12a completely encloses the compensation chamber 22. The compensation chamber 22 is integrated into the piston 12a. For this purpose, the piston 12a has an outer cylinder jacket wall 34 on its outer side facing the housing 2. According to the embodiment shown, the outer cylinder jacket wall 34 is designed in two parts, in that a sleeve section is formed on the end face of each of the annular discs 17. The sleeve section is in particular designed in one piece with the annular disc 17. Alternatively, it is conceivable to fasten the sleeve section to the end face of the annular disc 17, in particular by welding it.

[0061] Particularly in the event that a compensating element 23 is arranged in the compensating chamber 22, it is fundamentally also conceivable to design the outer cylinder jacket wall 34 as an outer spacer sleeve, which is arranged as a separate component in the axial direction between the annular discs 17, similar to the spacer sleeve 19. The compensating element 23 can serve as a radial spacer between the spacer sleeve 19 and the outer cylinder jacket wall 34. It is also conceivable for the outer cylinder jacket wall 34 to be formed as a sleeve section exclusively on one of the annular discs 17. The respective other annular disc 17 can then be designed analogously to one of the annular discs 17 according to the first exemplary embodiment.

[0062] It is advantageous if the outer cylinder jacket wall 34 is arranged in the radial direction of the longitudinal axis 5 without play relative to the inner wall of the housing 2, so that a displacement of the piston rod 11 with the piston 12a is not negatively affected by the outer cylinder jacket wall 34.

[0063] With regard to the function of the damper 1a, in particular the adjustment of the adjustment element 27, and the damping function of the damper 1a, reference is made to the above explanations of the damper 1.

Claims

[1] Damper a. with a housing (2) comprising i. a longitudinal axis (5) and ii. a working chamber (8) enclosed by the housing (2), b. with a damping fluid located at least partially in the working chamber (8), c. with a piston unit (10) comprising i. a piston rod (11) which is displaceable along the longitudinal axis (5) and which is sealed out of the housing (2) at one housing end (3), ii. a piston (12; 12a) attached to the piston rod (11) which divides the working chamber (8) into a first partial working chamber (14) and a second partial working chamber (15), iii. a flow channel (16) connecting the first partial working chamber (14) and the second partial working chamber (15), iv. a compensation chamber (22) connected to the first partial working chamber (14) and / or to the second partial working chamber (15), v. an adjusting element (27) for adjusting a flow cross-sectional area of the flow channel (16), wherein the adjusting element (27) can be displaced between an open position in which the flow cross-sectional area is maximum and a closed position in which the flow cross-sectional area is minimum, wherein a fluid flow between the compensation chamber (22) and the partial working chambers (14, 15) is prevented in the closed position, characterized by vi. a compensation channel (20, 21, 26) connected to the flow channel (16) and connected to the compensation chamber (22), wherein in the closed position of the adjusting element (27) a fluid flow from the flow channel (16) into the compensation channel (20, 21, 26) is prevented. [2] Damper according to claim 1, characterized by that the damper (1; 1a) is designed as a single-tube damper. [3] Damper according to one of the preceding claims, characterized bythat the flow channel (16) is at least partially integrated into the piston rod (11). [4] Damper according to claim 3, characterized by that the flow channel (16) has at least one transverse bore (24) arranged in the piston rod (11), wherein the at least one transverse bore (24) opens into the first partial working chamber (14) and / or into the second partial working chamber (15). [5] Damper according to one of the preceding claims, characterized by that the piston rod (11) is tubular. [6] Damper according to one of the preceding claims, characterized by that the adjusting element (27) has an adjusting lever (30) which is oriented transversely to the longitudinal axis (5). [7] Damper according to one of the preceding claims, characterized by that the adjusting element (27) is designed to be displaceable relative to the piston rod (11). [8] Damper according to one of the preceding claims, characterized bythat the compensation chamber (8) is integrated into the piston (12; 12a) and is at least partially enclosed by the piston (12; 12a). [9] Damper according to one of the preceding claims, characterized by a compensating element (23) arranged in the compensating chamber (22). [10] Damper according to claim 9, characterized by that the compensating element (23) comprises a compressible material.

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