阅读说明：本技术 减振器和具有这种类型的减振器的机动车辆 (Vibration damper and motor vehicle having a vibration damper of this type ) 是由 蒂洛·雷曼 于 2020-11-19 设计创作，主要内容包括：本发明涉及减振器和具有这种类型的减振器的机动车辆。减振器(10)包括：同轴布置的外管(11)和内管(12)；引导单元(13),其在第一端(14)分别封闭所述外管(11)和所述内管(12)；具有底部阀(16)的底部单元(15),该底部单元布置在所述内管(12)的第二端(17),所述外管(11)和所述内管(12)塑性变形,使得所述引导单元(13)以形状锁合的方式连接到所述外管(11)和所述内管(12),并且所述内管(12)塑性变形,使得所述底部单元(15)以形状锁合的方式连接到所述内管(12),和/或,所述外管(11)和所述内管(12)以一体结合的方式连接到所述引导单元(13),并且所述内管(12)以一体结合的方式连接到所述底部单元(15)。(The present invention relates to a shock absorber and a motor vehicle having a shock absorber of this type. The shock absorber (10) includes: an outer tube (11) and an inner tube (12) arranged coaxially; a guide unit (13) closing the outer tube (11) and the inner tube (12) respectively at a first end (14); -a bottom unit (15) with a bottom valve (16), which is arranged at the second end (17) of the inner tube (12), -the outer tube (11) and the inner tube (12) are plastically deformed such that the guide unit (13) is connected to the outer tube (11) and the inner tube (12) in a form-locking manner, and-the inner tube (12) is plastically deformed such that the bottom unit (15) is connected to the inner tube (12) in a form-locking manner, and/or-the outer tube (11) and the inner tube (12) are connected to the guide unit (13) in an integrated manner, and-the inner tube (12) is connected to the bottom unit (15) in an integrated manner.)

1. A shock absorber (10) for a motor vehicle, comprising:

-an outer tube (11) and an inner tube (12) arranged coaxially;

-a guide unit (13) closing the outer tube (11) and the inner tube (12), respectively, at a first end (14);

a bottom unit (15) arranged at a second end (17) of the inner tube (12),

characterized in that the outer tube (11) and the inner tube (12) are plastically deformed such that the guide unit (13) is connected to the outer tube (11) and the inner tube (12) in a form-fitting manner, and the inner tube (12) is plastically deformed such that the base unit (15) is connected to the inner tube (12) in a form-fitting manner, and/or the outer tube (11) and the inner tube (12) are connected to the guide unit (13) in an integrated manner, and the inner tube (12) is connected to the base unit (15) in an integrated manner.

2. The shock absorber as set forth in claim 1,

it is characterized in that the preparation method is characterized in that,

the outer tube (11) and the inner tube (12) fix the guide unit (13) and the base unit (15) in place by the plastic deformation.

3. The shock absorber according to claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outer tube (11) and the inner tube (12) are connected to the guide unit (13) and/or the inner tube (12) is connected to the base unit (15) in a form-fitting manner by crimping, rolling, caulking and/or locking beads.

4. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the outer tube (11) and the inner tube (12) are connected to the guide unit (13) and/or the inner tube (12) is connected to the base unit (15) in an integrally bonded manner by welding.

5. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

as a result of the plastic deformation, the outer tube (11) has at least one first flange (18) which is configured radially inward, and the guide unit (13) has at least one first recess (19), into which first flange (18) engages, so that the guide unit (13) is fixed in position in the outer tube (11).

6. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

as a result of the plastic deformation, the inner tube (12) has at least one first flange (21) and at least one second flange (22) which is configured radially inward, the first flange (22) engaging into at least one first recess (23) of the base unit (15) and the second flange (22) engaging into at least one second recess (24) of the guide unit (13), so that the inner tube (12) and the base unit (15) are fixed in position in the outer tube (11).

7. The shock absorber according to claim 5 or 6,

it is characterized in that the preparation method is characterized in that,

the recesses (19, 23, 24) have a continuous circumferential configuration or a partial circumferential configuration.

8. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

due to the plastic deformation, the outer tube (11) has at least one second flange (25) which is configured radially inward, and the guide unit (13) has a guide plate (26) which has a guide sleeve (27) for guiding a piston rod (28), the second flange pressing on the guide plate (26).

9. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the outer pipe (11) and the inner pipe (12) have a plurality of flanges (18, 21, 22, 25) which are distributed uniformly in the circumferential direction in the outer pipe (11) and/or the inner pipe (12).

10. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the guide unit (13) and the base unit (15) each have at least one first sealing element (29) which seals the guide unit (13) and the base unit (15) in a fluid-tight manner against the inner tube (12).

11. The shock absorber as set forth in claim 10,

it is characterized in that the preparation method is characterized in that,

the guide unit (13) and the base unit (15) each have a sealing region (31) which receives the first sealing element (29) and projects into the inner tube (12), the first sealing element (29) being arranged axially within a respective flange (21, 22) of the inner tube (12).

12. The vibration damper according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the bottom unit (15) has at least one second sealing element (32) which is arranged radially on the outside and seals the bottom unit (15) toward the outer tube (11).

13. A motor vehicle having at least one shock absorber (10) as claimed in claim 1.

Technical Field

The invention relates to a shock absorber and a motor vehicle. A vibration damper according to the preamble of patent claim 1 is known, for example, from DE 102011087597 a 1.

Background

Shock absorbers are commonly used in motor vehicles, and in the fields of moving vehicles and industry. In the case of shock absorbers, a distinction is generally made between monotube shock absorbers and multitube shock absorbers, with twin tube shock absorbers often being used as multitube shock absorbers.

A dual tube shock absorber basically has an inner tube and an outer tube arranged coaxially. A working piston is movably arranged in the inner tube, which working piston divides the inner space of the inner tube into a first working space and a second working space. Here, the working space is filled with a damping medium, for example with damping oil. The working piston is fixedly connected to a piston rod, through which vibrations are introduced into the shock absorber and are damped by the shock absorber. In the case of a compression of the piston rod into the inner tube, damping oil flows from the first working space through the working piston into the second working space, resulting in a flow of a portion of damping oil through the bottom valve into the compensation space due to the additional volume of the immersed piston rod. The compensation space is usually formed between the outer tube and the inner tube. Damping gas for preloading damping oil is introduced into the compensation space, which damping gas is compressed by the damping oil when compressed. In the event of rebound, the damping oil is transferred back into the working space of the inner tube again by the damping gas.

DE 102011087597 a1, which is cited first, already discloses, for example, a double tube damper, in which the outer tube is closed on the piston rod side by a sealing guide element. For this purpose, the outer tube is connected to the seal guide element in a force-fitting manner by means of a press fit. A double tube damper of this type has a higher complexity in the assembly of the individual damper parts than a damper in which the inner parts are fastened in a form-fitting manner. In addition, double tube dampers of this type cannot be produced on existing production and/or assembly plants for monotube dampers, since they usually do not have pressed-in internal parts, but are fastened only in a form-fitting manner. Thus increasing the production cost.

Disclosure of Invention

The invention is therefore based on the object of specifying a vibration damper which can be produced inexpensively and is simplified by means of a structurally improved design. The invention is based on the object of specifying a motor vehicle having a vibration damper of this type.

According to the invention, said object with regard to the vibration damper is achieved by the subject matter of claim 1. For a motor vehicle, the above object is achieved by the subject matter of claim 13.

In particular, the object is achieved by a shock absorber for a motor vehicle having an outer tube and an inner tube which are arranged coaxially, comprising a guide unit which closes the outer tube and the inner tube, respectively, at a first end, and having a bottom unit which is arranged at a second end of the inner tube. The outer tube and the inner tube are plastically deformed such that the guide unit is connected to the outer tube and the inner tube in a form-locking manner and the inner tube is plastically deformed such that the base unit is connected to the inner tube in a form-locking manner and/or the outer tube and the inner tube are connected to the guide unit in an integrated manner and the inner tube is connected to the base unit in an integrated manner.

The present invention has various advantages. The form-locking connection of the outer and inner tubes to the guide unit can be produced simply and quickly by plastic deformation of the outer and inner tubes, thus saving costs. In the case of plastic deformation, the outer tube and the inner tube are mechanically deformed in such a way that a form-locking connection is formed between the respective tube and the corresponding cell. The plastic deformation of the outer tube and/or the inner tube can be carried out by crimping, rolling, caulking and/or lock crimping. The outer tube and the inner tube are plastically deformed in such a way that the inner tube is fixedly connected to the guide unit and the base unit and the outer tube is fixedly connected to the guide unit. Here, the inner tube engages into the guide unit and the base unit, as a result of which a form-locking connection is formed. Furthermore, the outer tube engages into the guide unit, as a result of which a form-locking connection is formed.

By the integral joining connection of the tubes with the respective units, a reliable connection is advantageously established which prevents damage. Furthermore, the integral bonding connection can be produced simply and inexpensively by means of conventional bonding methods.

Furthermore, the positive and integral connection has the advantage that the guide unit and the base unit are not pressed or pretensioned into the inner and/or outer tube, so that the assembly of the vibration damper is significantly simplified. As is known from DE 102011087597 a1, in contrast to pressed-in inner parts, the requirements on the dimensional accuracy of the inner part or guide unit and base unit of the vibration damper according to the invention are made lower, since there is no need for pressing-in with a precise fit. Thus, the guide unit and the bottom unit can be introduced in a convenient manner, for example together with the inner tube, into the outer tube. Thus reducing the production cost of the shock absorber.

Furthermore, it is advantageous if the sealing of the interior of the vibration damper is decoupled from the fastening of the guide unit and the base unit. In other words, the damper has a structurally improved configuration due to the functional separation.

Another advantage of the present invention is that the shock absorber according to the present invention can be produced on existing manufacturing and/or assembly equipment for monotube shock absorbers, since the outer tube and the inner tube are connected to the guide unit or the base unit by plastic deformation of the two tubes. In the case of the production of monotube shock absorbers, the inner parts are often not fixed by a compression fitting, that is to say preferably by a form-locking connection, so that the shock absorber according to the invention can be manufactured on existing equipment for monotube shock absorbers. Accordingly, purchasing additional manufacturing or assembly equipment is avoided, thus providing significant cost savings.

The guide unit is arranged at a first end (in particular on the piston rod side) of the shock absorber. The guide unit serves to close the inner and outer tubes and to guide a piston rod which extends out of the inner tube through the guide unit in the case of a rebound phase or is retracted into the inner tube through the guide unit in the case of a compression phase.

A bottom unit is arranged at the second, in particular bottom-side, end of the inner tube, a bottom valve regulating the throughflow of damping medium, preferably damping oil, during operation, in particular in the case of a rebound phase or a compression phase.

Preferred embodiments of the invention are specified in the dependent claims.

In the case of a particularly preferred embodiment, the outer tube and the inner tube fix the guide unit and the base unit in place by plastic deformation. The guide unit and the base unit may be rotationally and axially fixed. The outer tube and the inner tube may exhibit a plastic deformation which fixes or holds the guide unit and the base unit in their position. It is conceivable that the guide unit and the bottom unit are fixed in place only by plastic deformation of the outer tube and the inner tube. The positional fixing of the guide unit and the base unit can be produced simply and quickly by plastic deformation of the outer tube and the inner tube, and is therefore inexpensive.

In a further particularly preferred embodiment, the outer tube and the inner tube are connected to the guide unit and/or the inner tube is connected to the base unit in a form-fitting manner by crimping, rolling, caulking and/or a locking bead. In other words, the outer tube and the inner tube can be crimped, rolled, caulked and/or lockcrimped to the guide unit for a form-locking connection. Additionally or alternatively, the inner tube may be crimped, rolled, caulked and/or lockcrimped to the base unit for a form-locking connection. Here, the inner tube and the outer tube are preferably plastically deformed by means of at least one joining tool in such a way that at least one plastic deformation is formed, which forms a form-locking connection with the guide unit and the base unit.

The configuration of the plastic deformation of the outer pipe and the inner pipe is not limited to the above bonding method. Additionally or alternatively, other shaping methods not mentioned can be used for the plastically deformed configuration.

The outer tube and the inner tube are preferably connected to the guide unit in an integrally bonded manner by welding. Additionally or alternatively, the inner tube may be connected to the base unit in an integral connection by welding. Thus, a secure connection of the tube to the respective unit is advantageously established.

In the case of a preferred embodiment, the outer tube has at least one first flange configured radially inward as a result of the plastic deformation, and the guide unit has at least one first recess. Here, the first flange engages into the first recess, so that the guide unit is fixed in position in the outer tube. In other words, the first flange of the outer tube forms a form-locking connection with the first recess of the guide unit. This has the advantage that a fixed and/or stable connection is formed between the outer tube and the guide unit, which connection is subjected to high operating pressures during operation.

The first flange of the outer tube may protrude into the first recess of the guide unit, which thus holds the guide unit in a fixed manner against displacement and rotation. The first flange of the outer tube may completely or partially fill the first recess of the guide unit. The first flange of the outer tube may directly or indirectly contact the first recess of the guide unit.

In the case of a further preferred embodiment, the inner tube has at least one first flange and at least one second flange which are configured radially inwards as a result of the plastic deformation. Here, the first flange engages into at least one first recess of the base unit and the second flange engages into at least one second recess of the guide unit, so that the inner tube and the base unit are fixed in position in the outer tube. In other words, the first flange of the inner tube forms a form-locking connection with the first recess of the bottom unit, while the second flange of the inner tube forms another form-locking connection with the second recess of the guide unit. This has the advantage that an easily established and stable connection is constructed between the inner tube and the guide unit and the base unit in order to fix the position of the guide unit and the base unit.

The first flange of the inner tube may protrude into the first recess of the bottom unit, said first flange thus holding the bottom unit in a fixed manner against displacement and rotation. The two flanges of the inner tube may completely or partially fill the recesses of the guide unit and the bottom unit. The two flanges of the inner pipe may be in direct or indirect contact with the second recess of the guide unit and the first recess of the bottom unit.

The recess is preferably of continuous circumferential configuration or of partial circumferential configuration. The continuous circumferential recess facilitates the formation of a form-locking connection between the two pipes and the corresponding coupling partners or guide units and/or base unit, since the form-locking connection can be formed in the circumferential direction of the pipes independently of the rotational position of the pipes and the coupling partners. Assembly is thus simplified and costs are thus saved. Instead, the desired, fixed rotational orientation of the two tubes relative to the respective coupling partners is simplified by the local circumferential recess.

In order to connect the tubes to the respective units in a form-locking manner by plastic deformation, the guide unit and the bottom unit have the above-mentioned recesses. The recess is thus adapted to interact with the respective tube in a form-locking manner. In the case of an integrally bonded connection of the tubes with the respective unit, the guide unit and/or the bottom unit may have, at least sectionally, a smooth wall to which the respective tube is welded. It is conceivable here for the walls of the guide unit and the base unit to have a completely smooth construction (in particular without recesses) in the region of the integrally joined connection.

In a further preferred embodiment, the outer tube has at least one second flange, which is formed radially inward, as a result of the plastic deformation, and the guide unit has a guide plate with a guide sleeve, against which the second flange is pressed. The guide plate with the guide sleeve can be pressed in the axial and/or radial direction by the second flange of the outer tube, so that the guide plate with the guide sleeve is held in a positionally fixed manner. The guide sleeve serves for axially guiding the piston rod. In other words, the piston rod is axially displaceably guided by the guide sleeve. The second flange of the outer tube has the advantage that the guide unit is fixed to the outer tube in an improved manner and thus the functional reliability is increased.

In general, the outer and inner tubes can have a plurality of flanges which are distributed uniformly in the circumferential direction on the outer and/or inner tube. The stability of the form-locking connection between the respective pipe and the respective unit is thus increased and the safety against failure is thus increased.

Preferably, the guide unit and the base unit each have at least one first sealing element, which seals the guide unit and the base unit in a fluid-tight manner against the inner tube. For this purpose, the respective sealing element may interact in a fluid-tight manner with the inner surface of the inner tube or may be in direct contact with the inner tube. The inner space or the two working spaces of the inner tube are therefore advantageously sealed towards the outside. This helps ensure the functional reliability of the damper.

In a preferred embodiment, the guide unit and the base unit each have a sealing region which receives the first sealing element and projects into the inner tube. The first sealing element may be arranged axially within a respective flange of the inner tube. In other words, the first sealing element is arranged within the respective flange of the inner tube in a longitudinal direction towards the centre of the inner tube. Thus, the respective first sealing element is arranged in the inner tube at a deeper level than the respective first flange of the inner tube.

The bottom unit preferably has at least one second sealing element which is arranged radially on the outside and seals the bottom unit towards the outer tube. This ensures a controlled throughflow of damping medium between the compensation space and the inner space of the inner tube.

The invention relates to a motor vehicle having at least one vibration damper according to the invention, according to a further independent claim 13. Reference is made here to the advantages described in connection with the damper. Furthermore, the motor vehicle may alternatively or additionally have individual features or a combination of features already mentioned above in relation to the vibration damper.

Drawings

In the following, the invention will be elucidated in further detail with reference to the drawings. The illustrated embodiment represents an example of how a shock absorber according to the present invention may be constructed.

In the drawings:

figure 1 shows a longitudinal section through a shock absorber according to a preferred exemplary embodiment of the present invention,

figure 2 shows a detail of the form-locking connection between the outer of the vibration damper according to figure 1 and the guide unit,

figure 3 shows a perspective view of the shock absorber according to figure 1,

figure 4 shows a longitudinal section through a shock absorber according to another preferred exemplary embodiment of the present invention,

FIG. 5 shows a detail of the form-locking connection between the outer tube of the vibration damper and the guide unit according to FIG. 4, an

Fig. 6 shows a perspective view of the damper according to fig. 4.

Detailed Description

Fig. 1 and 4 each show a longitudinal section through a vibration damper 10, in particular a dual tube vibration damper, according to a corresponding exemplary embodiment of the invention. Specifically, fig. 1-3 illustrate a first exemplary embodiment of a shock absorber 10 according to the present invention, and fig. 4-6 illustrate a second exemplary embodiment of a shock absorber 10 according to the present invention. Hereinafter, two exemplary embodiments of shock absorber 10 are described.

Hereinafter, shock absorber 10 according to fig. 1 and 4 is referred to as a dual tube shock absorber. The dual tube damper has an outer tube 11 and an inner tube 12 arranged coaxially. The inner tube 12 is arranged on the outer tube 11. An annular gap 33 is formed between the outer tube 11 and the inner tube 12, which annular gap 33 forms a compensation space 34 for receiving damping gas and damping oil. The tubes 11, 12 will be described in more detail later.

In addition, the double tube damper has a piston 35, which piston 35 divides the inner space of the inner tube 12 into a first working space 36 and a second working space 37. The working spaces 36, 37 are filled with damping oil. A piston 35 is axially movably arranged in the inner tube 12 and is connected to the distal end of the piston rod 28.

Furthermore, the dual tube damper has a guide unit 13 arranged at a first (in particular piston-rod side) end 14 of the dual tube damper. The guide unit 13 encloses the outer tube 11 and the inner tube 12, and the piston rod 28 is axially movably guided in the guide unit 13. During operation, the piston rod 28 is retracted through the guide unit 13 into the inner tube 12 in case of a compression phase and extends out of the inner tube 12 through the guide unit 13 in case of a rebound phase.

According to fig. 1, 2, 4 and 5, the guide unit 13 comprises a guide body 38, a guide plate 26 with a guide sleeve 27, and an intermediate element 39. The guide body 38 has two recesses 19, 24 with a radially outward circumferential shape on the guide body 38. The two recesses 19, 24 may have a continuous circumferential configuration or a partial circumferential configuration.

In particular, the first recess 19 is configured in a first axial portion 41 of the guide body 38, while the second recess 24 is configured in a second axial portion 42 of the guide body 38. The first axial portion 41 is arranged axially on the outside with respect to the inner tube 12, while the second axial portion 42 is arranged axially on the inside. The first axial portion 41 protrudes radially beyond the second axial portion 42, the first axial portion 41 being in direct contact with the outer tube 11, and the second axial portion 42 being in direct contact with the inner tube 11.

As shown in fig. 1 to 3 and 4 to 6, the outer pipe 11 and the inner pipe 12 are plastically deformed in such a manner that they have a plurality of flanges 18, 21, 22, 25. Specifically, the outer tube 11 has a plurality of first flanges 18 and a plurality of second flanges 25. Alternatively, the outer tube 11 may have a single first flange 18 and a single second flange 25. The flanges 18, 25 of the outer tube 11 are formed on a first (in particular piston-side) end 14' of the outer tube 11. Further, the inner tube 12 has a plurality of first flanges 21 and a plurality of second flanges 22. It is also conceivable for the inner tube 12 to have a single first flange 21 and a single second flange 22. The first flange 21 of the inner tube 12 is arranged at a first (in particular piston rod side) end 17' of the inner tube 12. The second flange 22 of the inner tube 12 is arranged at a second (in particular opposite to the first end 17') end 17 of the inner tube 12.

The flanges 18, 21, 22, 25 have a radially inward configuration due to plastic deformation of the tubes 11, 12. The flanges 18, 21, 22, 25 may have a partial circumferential or continuous circumferential configuration. As can be seen in fig. 3 and 6, the flanges 18, 25 are evenly distributed in the outer tube 11 in the circumferential direction. The flanges 21, 22 of the inner tube 12 may likewise be configured so as to be evenly distributed in the circumferential direction in the inner tube 12.

As is clearly visible in fig. 2 and 5, the outer tube 11 is plastically deformed in such a way that the first flange 18 engages into the first recess 19 of the guide body 38 of the guide unit 13. In other words, the outer tube 11 and the guide body 38 of the guide unit 13 are connected in a form-locking manner by the first flange 18 and the first recess 19. The outer tube 11 is connected to the guide body 38 of the guide unit 13 in a form-fitting manner by means of a locking bead. Alternatively, the outer tube 11 can also be connected to the guide body 38 of the guide unit 13 in a form-fitting manner by crimping, rolling and/or caulking. Due to the locking bead, the outer tube 11 is plastically deformed in such a way that the first flange 18 is pressed into the first recess 19 of the guide unit 13. In other words, the outer tube 11 is connected to the guide body 38 of the guide unit 13 by means of a locking bead in a form-locking and force-locking manner. The guide body 38 of the guide unit 13 is fixed in position in the outer tube 11 by means of the first flange 18.

Furthermore, fig. 2 and 5 show the second flange 25 of the outer tube 11, the second flange 25 having a radially inward configuration due to plastic deformation of the outer tube 11. The second flange 25 is pressed onto the guide plate 26, whereby the guide plate 26 with the guide sleeve 27 is fixed. The guide sleeve 27 serves for guiding the piston rod 28. The guide plate 26 is arranged between the first flange 18 and the second flange 25, the guide plate 26 being supported on a guide body 38 of the guide unit 13 via an intermediate element 39. The intermediate element 39 may have an annular configuration. An axial pressure connection is formed between the guide body 38, the intermediate element 39 and the guide plate 26 by the two flanges 18, 25 of the outer tube 11.

According to fig. 1 and 4, the second axial section 42 of the guide body 38 of the guide unit 13 projects into the inner tube 12 and has a sealing region 31 'which receives the first sealing element 29'. The first sealing element 29' interacts in a fluid-tight manner with the inner surface of the inner tube 12. In other words, the first sealing element 29' seals the guide body 38 of the guide unit 13 towards the inner tube 12.

The second recess 24 of the guide unit 13 is configured in the transition between the sealing region 31' of the guide body 38 and the first axial portion 41. The inner tube 12 is plastically deformed in the region of the second recess 24 in such a way that the second flange 22 engages into the second recess 24 of the guide body 38 of the guide unit 13. In other words, the inner tube 12 and the guide body 38 of the guide unit 13 are connected in a form-locking manner by the second flange 22 of the inner tube 12 and the second recess 24 of the guide body 38.

The inner tube 12 is connected to the guide body 38 of the guide unit 13 in a form-fitting manner by means of a locking bead. Alternatively, the inner tube 12 can also be connected to the guide body 38 of the guide unit 13 in a form-fitting manner by crimping, rolling and/or caulking. Due to the locking bead, the inner tube 12 is plastically deformed in such a way that the second flange 22 is pressed into the second recess 24 of the guide unit 13. In other words, the inner tube 12 is connected to the guide body 38 of the guide unit 13 by means of a locking bead in a form-locking and force-locking manner. The inner tube 12 is fixed in place on the guide body 38 of the guide unit 13 by means of the second flange 22. The second flange 22 of the inner tube 12 is arranged in the axial direction between the first sealing element 29' and the first flange 18 of the outer tube 12. In other words, the first sealing element 29' of the guide unit 13 is arranged in the axial direction within the second flange 22 of the inner tube 12.

Furthermore, the dual tube damper comprises a bottom unit 15 with a bottom valve 16 and a bottom body 43, the bottom valve 16 being arranged in the bottom body 43. The bottom unit 15 is arranged at the second end 17 of the inner tube 12. The base body 43 has a first recess 23, the first recess 23 being formed in the base body 43 in a radially outward circumferential manner. The recess 23 may have a continuous circumferential configuration or a partially circumferential configuration. In particular, the first recess 23 is configured in the first axial portion 44 of the bottom body 43.

The bottom body 43 has a second axial portion 45, the second axial portion 45 adjoining the first axial portion 44. With respect to the inner tube 12, the first axial portion 44 is axially disposed on the inner side, while the second axial portion 45 is axially disposed on the outer side. The second axial portion 45 projects radially outwardly beyond the first axial portion 44, the second axial portion 45 being in direct contact with the outer tube 11, and the first axial portion 44 being in direct contact with the inner tube 11.

According to fig. 1 and 4, the first axial portion 44 of the bottom body 43 of the bottom unit 15 protrudes into the inner tube 12 and has a sealing area 31' which receives the first sealing element 29 ″. The first sealing element 29 "interacts in a fluid-tight manner with the inner surface of the inner tube 12. In other words, the first sealing element 29 "seals the bottom body 43 of the bottom unit 15 towards the inner tube 12. The second sealing element 32 is arranged radially on the outside in the second axial portion 45 of the bottom body 43. The second sealing element 32 interacts in a fluid-tight manner with the outer tube 11. The sealing elements 29', 29", 32 may be formed by O-rings, respectively.

The first recess 23 of the bottom unit 15 is configured in the transition between the sealing area 31' of the bottom body 43 and the second axial portion 44. The inner tube 12 is plastically deformed in the region of the first recess 23 in such a way that the first flange 21 engages into the first recess 23 of the bottom body 43 of the bottom unit 15. In other words, the inner tube 12 and the bottom body 43 are connected in a form-locking manner by the first flange 21 of the inner tube 12 and the first recess 23 of the bottom body 43.

The inner tube 12 is connected to the bottom body 43 in a form-locking manner by means of a locking bead. Alternatively, the inner tube 12 can also be connected to the bottom body 43 in a form-fitting manner by crimping, rolling and/or caulking. By means of the locking bead, the inner tube 12 is plastically deformed in such a way that the first flange 21 is pressed into the first recess 23 of the bottom body 43. In other words, the inner tube 12 is connected to the bottom body 43 of the bottom unit 15 in a form-locking and force-locking manner by means of the locking bead. The inner tube 12 is held in place on the bottom body 43 of the bottom unit 15 by the first flange 21. The first flange 21 of the inner tube 12 is arranged in the axial direction between the first sealing element 29 "of the bottom unit 15 and the second sealing element 32 of the bottom unit 15. In other words, the first sealing element 29 "of the bottom unit 15 is arranged in the axial direction within the first flange 21 of the inner tube 12.

List of reference numerals

10 vibration damper

11 outer tube

12 inner pipe

13 guide unit

14 first end of shock absorber

14' first end of the outer tube

15 bottom unit

16 bottom valve

17 second end of inner tube

17' first end of inner tube

18 first flange of outer tube

19 first recess of guide unit

21 first flange of the inner pipe

22 second flange of the inner pipe

23 first recess of bottom unit

24 second recess of guide unit

25 second flange of the outer tube

26 guide plate

27 guide sleeve

28 piston rod

29', 29 "first sealing element

31. 31 "sealing area

32 second sealing element

33 annular gap

34 compensation space

35 piston

36 first work space

37 second work space

38 guide body

39 intermediate element

41 first axial portion of the guide body

42 second axial portion of the guide body

43 bottom body

44 first axial portion of the bottom body

45 second axial portion of the bottom body