Vibration damper for a vehicle trailer and trailer axle with a vibration damper

Abstract

Vibration damper (10) for a trailer axle of a vehicle trailer, comprising a first damping element (11a) and a second damping element (11b), wherein the damping elements (11a, 11b) are formed from elastomer and each axially bear against a damper contact element (12), and at least one piston rod (13) with a damper piston (14) is provided, characterized in that the damper piston (14) is arranged between the damping elements (11a, 11b), wherein both damping elements (11a, 11b) axially bear against the damper piston (14) for damping a tensile force and / or a compressive force, wherein the damping elements (11a, 11b) are introduced under prestress in a cylindrical damper housing (16) so that the damper piston (14) is firmly clamped between the damping elements (11a, 11b), wherein the second damping element (11b) is mounted on the piston rod (13) is arranged pushed into the damper housing (16),wherein the second damping element (11b) is hollow-cylindrical, and wherein the second damping element (11b) is pressed onto the piston rod (13).

Description

[0001] The invention relates to a vibration damper for a vehicle trailer and a trailer axle with a vibration damper. A vibration damper according to the preamble of patent claim 1 is known, for example, from EP 0 886 078 A2.

[0002] It is well known that trailers are equipped with vibration dampers to prevent the trailer from rocking or swinging while driving. Conventional dampers, such as hydraulic dampers, gas-filled dampers, or dampers with an elastomer as the damping medium, are used for this purpose. Elastomer dampers have the advantage of eliminating the need for liquid or gaseous damping media.

[0003] From the aforementioned EP 0 886 078 A2, a vibration damper is known that has two bearing elements. The bearing elements are designed as hollow cylinders that can be moved inside one another. Each of the bearing elements is closed by a spring contact area designed as a base. An elastomer spring element is arranged in each of the two bearing elements. A piston and another spring contact area are arranged between the elastomer spring elements. If the vibration damper or the bearing elements are compressed, the elastomer spring elements are also compressed. The disadvantage here is that the vibration damper can only dampen compressive forces that occur.

[0004] DE 2 223 314 A shows a bumper with an elastomer spring. The bumper is essentially tubular. The bumper further comprises a piston arranged on a piston rod. The piston rod extends through the elastomer spring. The piston rests against the elastomer spring. To dampen a compressive force, the elastomer spring is compressed by the piston. The piston is limited in a tensile direction by the housing. Thus, the aforementioned bumper can also dampen only a compressive force.

[0005] DE 10 2016 211 923 A1 discloses a damping device used to dampen vibrations and / or shocks. This device comprises a cylindrical housing and a piston mounted on a piston rod and movable in the longitudinal direction of the housing. Damping elements preloaded by end caps are arranged axially on both sides of the piston. Furthermore, a method for manufacturing the damping device and a chairlift are described.

[0006] The invention is therefore based on the object of providing a vibration damper for a trailer axle of a vehicle trailer, which, thanks to a simple design, prevents the vehicle trailer from swinging upwards during driving and thus ensures high driving stability of the vehicle trailer. The invention is further based on the object of providing a trailer axle with a vibration damper.

[0007] According to the invention, this object is achieved with regard to the vibration damper by the subject matter of claim 1. With regard to the trailer axle, the above-mentioned object is achieved by the subject matter of claim 11 (trailer axle).

[0008] The invention offers several advantages. The arrangement of the damper piston between the damping elements enables fast and precise damping when the trailer is in motion. Furthermore, this results in a compact design for the vibration damper. The contact of the damping elements with the damper piston ensures direct and rapid force introduction when a damping situation arises. In other words, a tensile force and / or compressive force to be damped is damped quickly and precisely. This significantly improves the damping behavior of the vibration damper.

[0009] Alternatively or additionally, the damper piston is embedded in at least one of the damping elements to dampen a tensile force (not according to the invention). This has the advantage that the tensile force to be damped is transmitted directly from the damper piston to the damping element. Preferably, the damper piston bears directly against the damping element to transmit the tensile force to the damping element.

[0010] The interaction of the damper piston with the damping elements advantageously dampens a tensile force and / or a compressive force. Another advantage is that the elastomer design of the damping elements results in a low weight of the vibration damper. Furthermore, the damping elements have the advantage of reducing the sealing effort on the vibration damper and enabling easy replacement of the damping elements. Another advantage is that the elastomer design of the damping elements significantly reduces the overall cost of the vibration damper.

[0011] In a particularly preferred embodiment, the first damping element and the second damping element have different hardness values, in particular different SHORE hardnesses. This is advantageous because the different hardnesses of the damping elements allow a defined rebound or compression stage of the vibration damper to be set. The first damping element can preferably be made of a harder elastomer than the second damping element. The first damping element can form the compression stage, and the second damping element can form the rebound stage of the vibration damper.

[0012] It is also conceivable for the damping elements to form the compression and / or rebound stages. This has the advantage that each damping element performs a dual function of damping the tensile force and the compressive force, respectively. This allows the damping elements to be made smaller, resulting in a more compact design for the vibration damper.

[0013] In a preferred embodiment, the first damping element is hollow-cylindrical. The second damping element is hollow-cylindrical according to the invention. This has the advantage that the hollow-cylindrical design allows the piston rod to be guided through the respective damping element. This allows the damping elements to be arranged in the vibration damper with improved guidance. Furthermore, the hollow-cylindrical design of the first damping element has the advantage that during damping or compression of the damping elements, the material or volume of the damping elements can escape into the existing cavity in the damping element. The hollow-cylindrical design thus enables the volume of the damping element to be displaced during damping. The first damping element can also be conical.The damping element can preferably also have further recesses which bring about a targeted damping characteristic, in particular a spring characteristic.

[0014] The damping elements are preferably arranged coaxially with each other. This coaxial arrangement of the damping elements enables simple and quick installation of the damping elements, for example, in a vibration damper housing. Furthermore, the coaxial arrangement of the damping elements has the advantage that the tensile or compressive force in a damping situation can be better absorbed and thus damped.

[0015] According to the invention, the damping elements are arranged in a cylindrical damper housing. This results in a compact and simple design of the vibration damper. Furthermore, the cylindrical damper housing has the advantage that when mounted on a trailer or the trailer's wheel suspension, the vibration damper does not create any additional interfering edges. This allows for a variety of installation positions of the vibration damper on the trailer.

[0016] Not according to the invention, each damping element has a piston recess, in particular a blind bore, in which the damper piston is guided. This allows the damper piston to be guided in the damping element without additional guide elements. The damper piston is thus preferably arranged displaceably in the piston recess of the damping element. During driving operation, the damping piston can interact with a force transmission surface of the damping element to dampen a tensile force. The piston can compress the damping element or introduce the resulting tensile force into the damping element. By directly introducing the tensile force into the damping element, a fast and precise response behavior of the vibration damper is achieved.

[0017] In a further preferred embodiment, the damper piston is operatively connected to the first damping element for damping a compressive force and / or the damper piston is operatively connected to the second damping element for damping a tensile force. In other words, the damper piston cooperates with the first damping element to dampen the compressive force. The first damping element, in cooperation with the damper piston, thus forms the compression stage of the vibration damper. The first damping element is compressed, in particular pressed, by the damper piston. The second damping element, preferably with the damper piston, forms the rebound stage of the vibration damper. By distributing the rebound stage or compression stage among the damping elements, a targeted adjustment of the damping characteristics, in particular the spring characteristics, of the vibration damper is possible.

[0018] In a particularly preferred embodiment, a first damper piston is operatively connected to the second damping element and / or a second damper piston is operatively connected to the first damping element to dampen a tensile force. This has the advantage of enabling a combination of the damping properties of the two damping elements. In other words, in a damping situation that occurs, the first damping element can be pressed against the second damping element, thereby combining the material properties of the harder elastomer with the material properties of the softer elastomer. This enables a variety of damping characteristics of the vibration damper. Furthermore, it allows a complex spring characteristic curve of the vibration damper to be set.

[0019] In another particularly preferred embodiment, the damper system elements interact with the damping elements to dampen a compressive force. For example, the damper system elements are pressed against the damping elements in a damping situation. This allows a compressive force to be damped. This represents a simple solution for transmitting a compressive force to the damping elements, enabling a simple design of the vibration damper.

[0020] The damper system elements preferably have at least one through-hole through which the piston rod protrudes. Each damper system element can comprise at least one through-hole through which a piston rod protrudes. Preferably, a piston rod is slidably arranged in a through-hole of the respective damper system element. The through-hole has the advantage that the piston rod can be guided within it. This results in stable damping behavior of the vibration damper.

[0021] In a preferred embodiment, the damper system element and / or the piston rod comprise at least one fastening element. The fastening element can be connectable to a frame of a vehicle trailer and / or a wheel suspension of a vehicle trailer. Preferably, the vibration damper has two fastening elements. The fastening elements can connect the vibration damper to the frame of the vehicle trailer and / or the wheel suspension of the vehicle trailer.

[0022] Preferably, the fastening element is arranged on the piston rod in such a way that the damper contact element is clamped, in particular pressed, against the damping element. This has the advantage that the damping elements can be preloaded and thus adapted to the current or expected load condition. Specifically, the damping characteristics of the vibration damper can be adjusted in this way. The fastening elements can be arranged on the piston rod in a rotatable manner.

[0023] The fastening elements can be connected to the piston rod by a threaded connection. The preload of the damping elements can be adjusted by rotating the fastening elements. It is advantageous that the fastening elements allow the preload of the damping elements to be variably, particularly continuously, adjusted.

[0024] A subordinate aspect not according to the invention relates to a shock absorber for a vehicle trailer, in particular for a trailer axle. The shock absorber comprises at least one damping element and at least two damper contact elements. The damping element is formed from an elastomer and bears against the damper contact elements. The damper contact elements are arranged opposite one another on the damping element. The damper contact elements are clamped, in particular pressed, against the damping element by at least one tensioning element.

[0025] The clamping element advantageously allows the preload of the damping element to be specifically set or adjusted. Furthermore, the clamping element holds the damper system elements in a fixed position on the damping element. The damper system elements can be held on the damping element without additional fixing components. Another advantage is that the clamping element enables simple assembly of the shock absorber and facilitates replacement of the damping element. The clamping element can have a defined spring characteristic. In other words, the clamping element can dampen small tensile forces through material expansion. The shock absorber can thus dampen compressive forces and / or tensile forces.

[0026] According to the invention, the damping element preferably forms a first damping element. Furthermore, a second damping element is provided. The damping elements can have different hardness values, in particular different SHORE hardnesses. At least one guide element, which projects into the damping elements, can be arranged between the damping elements. The damping elements can be guided by the guide element along a longitudinal axis of the guide element. Furthermore, the guide element can fix the damping elements in a direction transverse to the longitudinal axis of the guide element. This advantageously increases the transverse stability of the shock absorber. The guide element advantageously increases the stability of the shock absorber.

[0027] In a preferred embodiment not according to the invention, the tensioning element is formed by a locking cable, in particular a Bowden cable. The tensioning element as a locking cable has the advantage that any tensile force that occurs can be dampened by stretching the locking cable.

[0028] The guide element can have a through-bore through which the tensioning element is guided. By passing the tensioning element through the guide element, the first damping element and the second damping element can advantageously be preloaded in the direction of the longitudinal axis of the shock absorber. Furthermore, this results in a compact design of the shock absorber.

[0029] In a further preferred embodiment not according to the invention, the respective damper contact element has at least one through-opening in which a tension unit is arranged. The tensioning element can be accommodated in the tension unit. Furthermore, a compressive force can be transmitted to the damper contact element by the tension unit. It is advantageous that the tension unit accommodates the tensioning element, and the tension unit transmits a compressive force to the damper contact element. This functional integration enables a compact design of the shock absorber.

[0030] According to the invention, the traction unit preferably has at least one fastening element that can be connected to a frame of a vehicle trailer and / or to a wheel suspension of a vehicle trailer. The fastening element connects the shock absorber to the frame or wheel suspension. Furthermore, the fastening element serves to absorb the vibrations that occur and to transmit forces to the shock absorber.

[0031] A subordinate aspect of the invention relates to a trailer axle with at least one vibration damper according to one of claims 1 to 10.

[0032] Regarding the advantages of the trailer axle, reference is made to those explained in connection with the vibration damper. Furthermore, the trailer axle can alternatively or additionally feature individual or a combination of several of the features previously mentioned in relation to the vibration damper.

[0033] The invention will be explained in more detail below with reference to the accompanying drawings. The illustrated embodiments represent examples of how the vibration damper and trailer axle according to the invention can be designed.

[0034] In these show: Fig. 1a is a perspective side view of a vibration damper according to a preferred embodiment of the invention; Fig. 1b a perspective side view of the vibration damper according to Fig. 1a; Fig. 2a a perspective view of a trailer axle according to a preferred embodiment of the invention; Fig. 2b a perspective view of a trailer axle according to a further preferred embodiment of the invention; Fig. 3a is an exploded view of a vibration damper according to another preferred embodiment of the invention; Fig. 3b a perspective side view of the vibration damper according to Fig. 3a; Fig. 4a is a perspective side view of a shock absorber according to a preferred embodiment not according to the invention; Fig. 4b an exploded view of the shock absorber according to Fig. 4a without damping elements; Fig. 5a is a perspective side view of a shock absorber according to a further preferred embodiment not according to the invention, and Fig. 5b a perspective side view of the shock absorber according to Fig. 5a in the pressurized state.

[0035] Fig. 1a and Fig. 1b shows a perspective side view of a vibration damper 10 according to an exemplary embodiment of the invention. The vibration damper 10 comprises a first damping element 11a and a second damping element 11b. Furthermore, the vibration damper 10 comprises two piston rods 13, each with a damper piston 14, and two damper contact elements 12. The damping elements 11a, 11b can have different hardness values, in particular different SHORE hardnesses. The first damping element 11a can be formed from a harder elastomer than the second damping element 11b. It is also conceivable for the second damping element 11b to be formed from a harder elastomer than the first damping element 11a. The damping elements 11a, 11b can thus be formed from elastomers with different properties.

[0036] The damping elements 11a, 11b can also be formed from different elastomers. The damping elements 11a, 11b can be formed from a combination of several different elastomers. This has the advantage that a multitude of different damping characteristics can be produced for the damping elements 11a, 11b and thus for the vibration damper 10. The damping elements 11a, 11b can have a progressive and / or degressive and / or linear spring characteristic, in particular a spring characteristic curve.

[0037] The elastomers of the damping elements 11a, 11b are particularly dimensionally stable and elastically deformable. The damping elements 11a, 11b can be formed from the following elastomers or elastomer materials: acrylonitrile butadiene rubber (NBR) and / or hydrogenated acrylonitrile butadiene rubber (H-NBR) and / or fluorocarbon rubber (FPM) and / or fluorocarbon rubber (FKM) and / or ethylene propylene diene rubber (EPDM) and / or epichlorohydrin rubber (ECO), chloroprene rubber (CR) and / or perfluorocarbon rubber (FFKM) and / or polyurethane elastomer (PUR) and / or natural rubber (NR) and / or polyamide (PA).

[0038] The damping elements 11a, 11b can be cylindrical. The damping elements 11a, 11b can also be cuboid-shaped. Furthermore, the damping elements 11a, 11b can have a conical shape.

[0039] The respective damping element 11a, 11b has a piston recess 41, in particular a blind hole. The piston recess 41 is open toward a first axial end 47 of the respective damping element 11a, 11b. The piston recess 41 has an inner force transmission area 49. As shown in Fig. As can be clearly seen in Figure 1a, the force transmission area 49 of the respective damping element 11a, 11b is formed by a force transmission surface. The force transmission surface is circular in shape. The force transmission surface can also be formed by a rectangular surface.

[0040] According to Fig. 1a, the piston recess 41 of the respective damping element 11a, 11b is cylindrical. The piston recess 41 is formed by a blind hole. Furthermore, the damping element 11a, 11b has a first through-opening 41a. The through-opening 41a of the damping element 11a, 11b is also cylindrical. The first through-opening 41a can have a square cross-section. The first through-opening 41a is formed in the respective damping element 11a, 11b such that the through-opening 41a connects a second axial end 48 of the damping element 11a, 11b to the piston recess 41. In other words, the first through-opening 41a of the damping element 11a, 11b forms a free passage between the second axial end 48 of the damping element 11a, 11b and the piston recess 41.The first through-opening 41a is formed in the damping element 11a, 11b such that the through-opening 41a extends from the first axial end 47 of the damping element 11a, 11b to the force transmission area 49 of the piston recess 41. The piston recess 41 and the first through-opening 41a of the damping element 11a, 11b can be arranged coaxially with one another in the damping element 11a, 11b.

[0041] The respective damping element 11a, 11b further comprises a second through-opening 41b. The second through-opening 41b of the damping element 11a, 11b extends from the first axial end 47 of the damping element 11a, 11b to the second axial end 48 of the damping element 11a, 11b. The damping element 11a, 11b has a longitudinal axis. The second through-opening 41b is formed eccentrically in the damping element 11a, 11b relative to the longitudinal axis. The through-openings 41a, 41b and the piston recess 41 are formed in the damping element 11a, 11b in the direction of the longitudinal axis of the damping element 11a, 11b. Likewise, the piston recess 41 and the first through-opening 41a are formed eccentrically in the damping element 11a, 11b relative to the longitudinal axis of the damping element 11a, 11b. In other words, the through-openings 41a, 41b and the piston recess 41 are arranged radially offset in the damping element 11a, 11b relative to the longitudinal axis of the damping element 11a, 11b.The through openings 41a, 41b and the piston recess 41 therefore have a radial distance from the longitudinal axis of the damping element 11a, 11b.

[0042] As described above, the vibration damper 10 comprises two piston rods 13, each having a damper piston 14. The damper piston 14 is arranged at an inner end 13a of the piston rod 13. In other words, the damper piston 14 on the piston rod 13 forms the inner end 13a of the piston rod 13. The damper piston 14 has a cylindrical shape. The damper piston 14 can also have a cuboid shape. The piston rod 13 can be cylindrical and / or cuboid.

[0043] The piston rod 13 further comprises a fastening element 15. The fastening element 15 is connected to the piston rod 13 in a tensile-resistant manner. The fastening element 15 can be connected to the piston rod 13 by a threaded connection. In this case, it is conceivable for the fastening element 15 to be screwed onto the piston rod 13. Furthermore, the fastening element 15 can have a connecting pin that is screwed into the piston rod 13. The fastening element 15 can be connected to the piston rod 13 in a form-fitting and / or friction-fitting and / or material-fitting manner. The fastening element 15 can be connected to the piston rod 13 by welding, clamping, gluing, shrinking, form-fitting elements or by another connection method and / or form-fitting element.

[0044] As in the Fig. 1a and Fig. As shown in Figure 1b, the vibration damper 10 has two damper contact elements 12. The damper contact elements 12 are disc-shaped. The damper contact elements 12 have a cylindrical shape. The damper contact elements 12 can also have a cuboid shape. The damper contact elements 12 can also be designed differently. The damper contact elements 12 can be formed by a contact plate. The damper contact elements 12 can be formed by pressure plates. The damper contact elements 12 include a through-opening 42. Furthermore, the damper contact elements 12 can also have further through-openings. The through-opening 42 is formed in the direction of the longitudinal axis in the damper contact element 12.

[0045] For vibration damper 10 according to Fig. 1a and Fig. 1b, the damping elements 11a, 11b are arranged coaxially with one another. The damping elements 11a, 11b are arranged coaxially with one another in such a way that the piston recess 41 of the second damping element 11b and the first through-opening 41a of the second damping element 11b are arranged coaxially with the second through-opening 41b of the first damping element 11a. The piston recess 41 of the second damping element 11b and the first through-opening 41a of the second damping element 11b and the second through-opening 41b of the first damping element 11a have a common longitudinal axis that runs parallel to the longitudinal axis of the damping elements 11a, 11b.

[0046] Furthermore, the damping elements 11a, 11b are arranged coaxially with one another such that the second through-opening 41b of the second damping element 11b is arranged coaxially with the first through-opening 41a of the first damping element 11a and the piston recess 41 of the first damping element 11a. The second through-opening 41b of the second damping element 11b and the first through-opening 41a of the first damping element 11a and the piston recess 41 of the first damping element 11a have a further common longitudinal axis that runs parallel to the longitudinal axis of the damping elements 11a, 11b. The longitudinal axes are spaced apart from one another. Furthermore, the longitudinal axes of the through-openings 41, 41a, 41b are spaced apart from the longitudinal axis of the damping elements 11a, 11b.

[0047] According to Fig. 1b, the damping elements 11a, 11b are each arranged with their second axial ends 48 abutting one another. The first axial ends 47 of the damping elements 11a, 11b are thus arranged in the opposite direction to the longitudinal axis of the damping elements 11a, 11b. In other words, the damping elements 11a, 11b are arranged with their first axial ends 47 extending axially outward from a center. A damper contact element 12 is arranged at the first axial ends 47 of the respective damping element 11a, 11b. In other words, the vibration damper 10 comprises two damper contact elements 12, which are each arranged axially opposite one another on the damping elements 11a, 11b. The damper contact elements 12 can be arranged coaxially with the damping elements 11a, 11b.The respective damper system element 12 is arranged on the respective damping element 11a, 11b such that the through-opening 42 of the damper system element 12 is arranged coaxially with the second through-opening 41b of the damping element 11a, 11b. In summary, the damping elements 11a, 11b and the damper system elements 12 are arranged relative to one another such that the through-openings 42, 41a, 41b form a free passage in the direction of the longitudinal axis, extending from the respective damper system element 12 to the piston recess 41 of the respective damping element 11a, 11b.

[0048] As in Fig. As can be clearly seen in Figure 1a, the vibration damper 10 has two piston rods 13. The piston rods 13 are arranged in the through-openings 41a, 41b, 42 so as to be displaceable in the direction of the longitudinal axis. Furthermore, the damper pistons 14 of the piston rods 13 are also displaceable in the direction of the longitudinal axis in the respective piston recesses 41 of the damping elements 11a, 11b. The damper piston 14 is guided in the piston rod recess 41 of the respective damping element 11a, 11b.

[0049] The damper contact elements 12 are each arranged between the first axial end 47 of the damping element 11a, 11b and the fastening element 15. The depth or length of the piston recess 41 can define a damper travel when damping a compressive force. The damper contact elements 12 can act as an axial stop for the respective damper piston 14. To transmit a tensile force to the damping elements 11a, 11b, the damper piston 14 of the respective piston rod 13 interacts with the force transmission area 49 of the respective damping element 11a, 11b.

[0050] Fig. 1b shows the assembled state of the vibration damper 10 according to Fig. 1a. Here, the damper system elements 12 are arranged adjacent to the damping elements 11a, 11b. The respective damper pistons 14 of the piston rods 13 rest against the force transmission areas 49 of the respective damping elements 11a, 11b. It is conceivable that the damper system elements 12 are pressed against the damping elements 11a, 11b. This can be achieved, for example, by the fastening elements 15.

[0051] Furthermore, Fig. 1b shows a further fastening element 15c of a frame (not shown) and / or a wheel suspension (not shown) of a vehicle trailer, which can be connected to one of the fastening elements 15. The fastening elements 15, 15c have a fastening opening. The fastening opening of the fastening elements 15, 15c is designed as a through-opening. As shown in Fig. As can be seen in Figure 1b, the fastening elements 15, 15c are arranged coaxially with the through holes. The fastening elements 15, 15c can also be arranged differently relative to one another.

[0052] For vibration damper 10 according to Fig. 1a and Fig. 1b, the damper pistons 14 cooperate with the respective damping element 11a, 11b to dampen a tensile force. For this purpose, the damper pistons 14 are embedded in the damping elements 11a, 11b, as described above. The tensile force is transmitted to the respective damper element 11a, 11b by the fastening elements 15, the piston rods 13, and the damper pistons 14. The tensile force is transmitted from the damper piston 14 through the force transmission area 49 of the respective damping element 11a, 11b to the damping element 11a, 11b. Specifically, according to Fig. 1a and Fig. 1b, a first damper piston 14a is operatively connected to the second damping element 11b to dampen the tensile force. In addition, a second damper piston 14b is operatively connected to the first damping element 11a to dampen the tensile force.

[0053] When the tensile force is transferred from the damper pistons 14 to the respective damping element 11a, 11b, the two damping elements 11a, 11b are pressed against each other in the direction of their longitudinal axis. The damping elements 11a, 11b are compressed by the tensile force or by the damper piston 14. In other words, when a tensile force is applied, the damping elements 11a, 11b are deformed relative to each other, in particular elastically deformed, by the damper pistons 14. This corresponds to tensile force damping. During tensile force damping, both damping elements 11a, 11b form the rebound stage of the vibration damper 10.

[0054] When a compressive force is dampened by the vibration damper 10, the damper contact elements 12 are pressed against the damping elements 11a, 11b. The compressive force is transferred from the fastening elements 15 to the damper contact elements 12. The damper contact elements 12 then transfer the compressive force directly to the damping elements 11a, 11b. In other words, each damper contact element 12 rests against a damping element 11a, 11b, whereby the compressive force is transferred from the damper contact element 12 directly to the damping element 11a, 11b. The damping elements 11a, 11b are thus pressed together, in particular compressed, by the damper contact elements 12 when a compressive force is dampened. This corresponds to compression damping of the vibration damper 10. The damper contact elements 12 interact with the damping elements 11a, 11b to dampen the compressive force.

[0055] For the vibration damper 10 according to the Fig. 1a and Fig. 1b, it is conceivable that the damping elements 11a, 11b are arranged in a damper housing 16. This has the advantage of increasing damper stability. Furthermore, the damper can be protected against environmental influences. Furthermore, it is conceivable that the entire vibration damper is arranged in a damper housing.

[0056] In Fig. 2a and Fig. 2b shows a trailer axle 50 with two swing arms 54. A wheel 52 is arranged on each swing arm 54. The two swing arms 54 are connected to each other by a transverse axle element 53. A vibration damper 10 according to Fig. 1a and Fig. 1b. The swing arms 54 are arranged opposite each other on the transverse axle element 53.

[0057] According to Fig. 2a shows a trailer axle 50 in which the vibration dampers 10 dampen a compressive force. The vibration dampers 10 are connected to the swing arm 54 by the fastening element 15. The vibration damper 10 is further connected to a frame of the vehicle trailer (not shown) by a further fastening element 15. The vibration damper 10 is arranged on the swing arm 54 in such a way that the vibration damper 10 is subjected to a compressive force when the wheel 52 moves upwards. Furthermore, the vibration damper 10 is arranged on the swing arm 54 in such a way that the vibration damper 10 is subjected to a tensile force when the wheel 52 moves downwards. The direction of movement of the wheel 52 is represented by the arrow 54. Furthermore, the direction of force 44 of the compressive force is represented by the arrow 44 on the vibration damper 10, corresponding to the direction of movement of the wheel.If the vibration damper 10 is subjected to a tensile force or the wheel 52 moves downwards, the arrows 44, 45 would point in the opposite direction.

[0058] In Fig. 2b, the trailer axle 50 also has two swing arms 54. On each swing arm 54, a vibration damper 10 according to Fig. 1a and Fig. 1b. The vibration damper 10 is arranged on the swing arm 54 such that upon an upward movement of the wheel 52, the vibration damper 10 is subjected to a tensile force. Furthermore, the vibration damper 10 is arranged on the swing arm 54 such that upon a downward movement of the wheel 52, the vibration damper 10 is subjected to a compressive force. Just as in Fig. 2a, is in Fig. 2b, the vibration damper 10 is connected to the swing arm 54 by a fastening element 15 in a force-transmitting manner. The vibration damper 10 can be connected to a frame of the vehicle trailer (not shown) by a further fastening element 15c. Arrows 44, 45 represent the direction of movement of the wheel 52 and the direction of force acting on the vibration damper 10, respectively. If the vibration damper 10 were subjected to a compressive force or if the wheel 52 were to move downward, the arrows 44, 45 would point in the opposite direction.

[0059] According to Fig. 3a and Fig. 3b shows a vibration damper 10 according to a further embodiment of the invention. Fig. 3a shows the vibration damper 10 in an exploded view to explain the individual components.

[0060] The vibration damper 10 comprises a first damping element 11a, a second damping element 11b, a piston rod 13 with a damper piston 14, two damper contact elements 12, and a damper housing 16. For fastening the vibration damper 10, it comprises two fastening elements 15, with a first fastening element 15a being associated with a first damper contact element 12a. Furthermore, a second fastening element 15b is associated with the piston rod 13.

[0061] The materials and the material properties with regard to damping characteristics and elasticity, in particular deformability, of the damping elements 11a, 11b correspond to those of the damping elements 11a, 11b according to Fig. 1a and Fig. 1b. Furthermore, the piston rod 13 and the damper piston 14 correspond to Fig. 3a and Fig. 3b of the piston rod 13 and the damper piston 14, as in Fig. 1a and Fig. 1B. The design of the fastening elements 15 corresponds to the design of the fastening elements 15 according to Fig. 1a and Fig. 1b.

[0062] The damping elements 11a, 11b according to Fig. 3a and Fig. 3b are cylindrical. The damping elements 11a, 11b have a hollow cylindrical shape. The damping elements 11a, 11b can also be cuboid-shaped. Furthermore, the damping elements 11a, 11b can additionally or alternatively have a conical shape.

[0063] The damper piston 14 is arranged in a fixed position on the piston rod 13. The damper piston 14 is arranged in a fixed position on the inner end 13a of the piston rod 13. The inner end 13a of the piston rod 13 is arranged in the damper housing 16. The damper piston 14 can also be arranged along the piston rod 13. The damper piston 14 can be arranged on the piston rod 13 such that the damper piston 14 is axially spaced from the inner end 13a of the piston rod 13. In other words, the damper piston 14 can be arranged on the piston rod 13 such that the piston rod 13 protrudes axially from the damper piston 14 in a longitudinal direction of the vibration damper 10. The damper piston 14 can therefore also be pushed onto the piston rod 13. The damper piston 14 can be connected to the piston rod 13 in a form-fitting and / or force-fitting and / or material-fitting manner.

[0064] The damper piston 14 can be cylindrical. The damper piston 14 can have a hollow cylindrical shape. The damper piston 14 can also be cuboid-shaped. In general, the damper piston 14 can have a shape other than cylindrical. The damper piston 14 is arranged in the damper housing 16. The damper piston 14 and the damper housing 16 can be arranged coaxially with one another. The damper piston 14 is arranged with the piston rod 13 in the damper housing 16 so that it can be axially displaced.

[0065] The damping elements 11a, 11b are arranged in the damper housing 16. The damping elements 11a, 11b can be arranged coaxially with the damper housing 16. Likewise, the damping elements 11a, 11b can be arranged coaxially with the damper piston 14 and the piston rod 13 in the damper housing 16. The damping elements 11a, 11b are arranged in the damper housing 16 such that a distance, in particular a clearance, can be formed between the damping elements 11a, 11b and the damper housing 16.

[0066] The distance between the damping elements 11a, 11b and the damper housing 16 can form a compensation volume. Specifically, the compensation volume can be formed by an annular gap formed between the damping elements 11a, 11b and the damper housing 16. When damping the compressive force and / or the tensile force, the compensation volume advantageously enables radially outward deflection of the elastomer of the respective damping element 11a, 11b. By appropriately dimensioning the compensation volume, the damping behavior of the vibration damper 10 can be adjusted according to the desired operating conditions.

[0067] The damping elements 11a, 11b are arranged in the damper housing 16. The damping elements 11a, 11b are arranged between the damper contact elements 12, which form a first damper contact element 12a and a second damper contact element 12b. The first, in particular harder, damping element 11a is arranged axially between the first damper contact element 12a and the damper piston 14. The first damper contact element 12a forms a first damping stop 17. The first damping element 11a axially bears against the first damping stop 17 in the axial longitudinal direction of the vibration damper 10. A distance, in particular an axial play, can be formed between the first damping element 11a and the first damping stop 17. The first damping element 11a forms the compression stage of the vibration damper 10.When the compressive force is dampened, the piston rod 13 is pushed into the damper housing 16, and the first damping element 11a is compressed by the damper piston 14. The resulting compressive force is thus dampened by the vibration damper 10. This corresponds to compressive force damping.

[0068] The second, in particular softer, damping element 11b rests axially on the second damper contact element 12b in the longitudinal direction of the vibration damper 10. The second damper contact element 12b forms a second damper stop 18. In other words, the second damping element 11b rests longitudinally on the second damper stop 18. A distance, in particular an axial play, can also be formed between the second damping element 11b and the second damper contact element 12b or the second damping stop 18. The second damping element 11b is arranged between the second damper contact element 12b and the damper piston 14. The second damping element 11b forms the rebound stage of the vibration damper 10. When the tensile force is damped, the piston rod 13 is partially pulled out of the damper housing 16, and thus the second damping element 11b is compressed, in particular, by the damper piston 14.The tensile force is thus dampened by the vibration damper 10. This corresponds to the tensile force damping.

[0069] In general, it is conceivable that the first damping element 11a and the second damping element 11b are inserted under preload in the damper housing 16. In this case, the damper piston 14 is firmly clamped, in particular clamped, between the damping elements 11a, 11b. This achieves a precise and rapid response of the vibration damper 10.

[0070] According to the invention, the second damping element 11b is arranged in the damper cylinder 16, pushed onto the piston rod 13. The second damping element 11b is hollow-cylindrical in shape. The damping element 11b is pressed onto the piston rod 13.

[0071] The damper piston 14 is thus arranged axially between the first damping element 11a and the second damping element 11b. The damper piston 14 is arranged in the damper housing 16 such that the damper piston 14 is force-coupled to the damping elements 11a, 11b for damping the compressive force and / or the tensile force. In other words, the damping elements 11a, 11b are operatively connected to the damper piston 14 for damping the compressive force and / or the tensile force, respectively.

[0072] The damper housing 16 is formed by a tube with a circular cross-section.

[0073] Fig. 3b shows the assembled state of the vibration damper 10 according to Fig. 3a. The piston rod 13 protrudes from the damper housing 16 in such a way that a damping travel 46 is formed. The vibration damper 10 is shown in the undamped state. When damping a tensile force, the damper travel 46 can double. When damping a compressive force, the damping travel 46 can correspond to a maximum spring deflection of the vibration damper 10.

[0074] Fig. Figure 4a shows a shock absorber 20 for a vehicle trailer according to an embodiment not according to the invention. The shock absorber 20 comprises a first damping element 21a, a second damping element 21b, and two damper contact elements 22. The damping elements 21a, 21b are each formed from an elastomer. The materials and the material properties with regard to damping characteristics and elasticity, in particular deformability, of the damping elements 21a, 21b correspond to those of the damping elements 11a, 11b according to Fig. 1a and Fig. 1b. The damping elements 21a, 21b will be discussed in more detail later.

[0075] The shock absorber 20 further comprises a guide element 23, two tension units 30 and a tensioning element 24. As in Fig. As can be clearly seen in Figure 4b, the guide element 23 is formed by a disc and two pins. The guide element 23 is rotationally symmetrical. The guide element 23 can also be cuboid-shaped. The guide element 23 can thus also have an angular, in particular rectangular, cross-section.

[0076] The pins are arranged axially opposite one another on the guide element 23. The pins extend from the disc of the guide element in the direction of a longitudinal axis of the guide element 23. The pins can be arranged coaxially with the disc. The guide element 23 has a through-bore 43. The through-bore 43 extends through the pins and the disc of the guide element 23. The pins have an outer diameter that is smaller than an outer diameter of the disc of the guide element 23. The pins can also have a square cross-section.

[0077] The traction unit 30 comprises a clamping element receptacle 31, a pressure element 32, and a locking element 33. The clamping element receptacle 31 is formed by a tube. The clamping element receptacle 31 can also be formed by a shaped tube. The clamping element receptacle 31 can be partially or completely hollow-cylindrical. The clamping element receptacle 31 can also have an angular, in particular rectangular, cross-section.

[0078] Furthermore, the pressure element 32 is formed by a pressure disc or a pressure plate. The pressure disc 32 has a circular cross-section. The pressure element 32 can also have a rectangular cross-section. Furthermore, the traction unit 30 comprises a fastening element 25. The fastening element 25 has a through-opening through which the traction unit 30 can be connected to a frame of a vehicle trailer or a wheel suspension of a vehicle trailer.

[0079] The pressure element 32 is arranged on the clamping element receptacle 31, in particular arranged axially. The pressure element 32 can be arranged by being pushed onto the clamping element receptacle 31. The pressure element 32 can have an inner diameter that essentially corresponds to an outer diameter of the clamping element receptacle 31. The pressure element 32 is arranged on the clamping element receptacle 31 at a distance from a free end 31a of the clamping element receptacle 31. The fastening element 25 described above is arranged on a further end 31b of the clamping element receptacle 31, opposite the free end 31a. The fastening element 25 is connected to the clamping element receptacle 31 in a fixed position. The pressure element 32 is also arranged on the clamping element receptacle 31 at a distance from the further end 31b of the clamping element receptacle 31.

[0080] A locking element 33 is arranged between the pressure element 32 and the fastening element 25. The locking element 33 is arranged on the clamping element receptacle 31 in such a way that the locking element 33 can be guided, in particular inserted, radially into the clamping element receptacle 31. The locking element 33 can be formed by a locking screw. Furthermore, the locking element 33 can be formed by a locking pin or a locking shaft.

[0081] The damper system elements 22 have a through-opening 42. The through-opening 42 of the damper system elements 22 is formed by a through-bore. The through-opening 42 is formed concentrically on the damper system element 22. The damper system elements 22 can each be formed by a pressure plate. A first damper system element 22a forms a first end of the shock absorber 20, and a second damper system element 22b forms a second end of the shock absorber 20. The damper system elements 22 can also be designed as a shell or a cup. The damper system elements 22 can be designed such that each damper system element 22 can accommodate a damping element 21a, 21b. In other words, the damper system element 22 can be designed such that the damping element 21a, 21b can be inserted into the damper system element 22.As a result, when damping a compressive force, an improved force introduction from the respective damper system element 22 into the respective damping element 21a, 21b is achieved.

[0082] In the assembled state of the shock absorber 20 according to Fig. 4a, the guide element 23 is arranged between a first damping element 21a and a second damping element 21b. The guide element 23 can be arranged coaxially with the damping elements 21a, 21b. The damping elements 21a, 21b lie opposite one another on the guide element 23.

[0083] According to Fig. 4a, the damping elements 21a, 21b are hollow cylindrical. The guide element 23 engages with a respective pin in a damping element 21a, 21b. In other words, the guide element 23 is arranged between the damping elements 21a, 21b such that the guide element 23 extends into the damping elements 21a, 21b. The guide element 23 fixes the damping elements 21a, 21b in a direction transverse to the longitudinal axis of the guide element 23. This achieves a stable damper structure.

[0084] The first damper element 22a is arranged axially on the first damping element 21a. The second damper element 22b is arranged axially on the second damping element 21b. The damper elements 22 are arranged coaxially with the damping elements 21a, 21b and the guide element 23. The damper elements 22 bear directly against the damping elements 21a, 21b. This enables direct pressure force introduction into the damping elements 21a, 21b to dampen a pressure force. The damper elements 22 are arranged axially opposite one another on the two damping elements 21a, 21b.

[0085] When a compressive force is applied to the shock absorber 20, the damper contact elements 22 compress the damping elements 21a, 21b. The compressive force is transmitted to the respective damper contact element 22 by the tension unit 30. In other words, the compressive force occurring in a damping situation is transferred by the tension unit 30 to the respective damper contact element 22. As a result, the damping elements 21a, 21b are subsequently compressed, thereby damping the compressive force.

[0086] As in Fig. 4a and Fig. As shown in Figure 4b, the shock absorber 20 comprises two tension units 30. Each tension unit 30 is arranged in the through-opening 42 of the damper contact element 22. The two tension units 30 are arranged axially opposite one another on the respective damper contact element 22. To dampen a compressive force, the tension unit 30 interacts with the damper contact element 22. The tension unit 30 interacts with the damper contact element 22 in such a way that a force flow is created to transmit the compressive force to the damping elements 21a, 21b.

[0087] The shock absorber 20 further comprises a tensioning element 24. The tensioning element 24 clamps, in particular presses, the damper contact elements 22 against the damping elements 21a, 21b. The tensioning element 24 can be formed by a locking cable 24a, in particular a Bowden cable. Furthermore, the tensioning element 24 can also be formed by a locking rod or a locking shaft.

[0088] The tensioning element 24 can be partially elastic. The tensioning element 24 or the locking cable 24a can be elastic. The tensioning element 24 is received in the tensioning element receptacle 31. The tensioning element 24 extends through the damping elements 21a, 21b and the guide element 23. The tensioning element 24 is guided through the through-bore 43 of the guide element 23. The tensioning element 24 can be fixed in the longitudinal direction in the tension unit 30 by the locking element 33. The tensioning element 24 forms an axial tensile force limiter of the shock absorber 20. The damper contact elements 22 are clamped against the damping elements 21a, 21b by the tensioning element 24.

[0089] If, for example, a tensile force occurs on the shock absorber 20, the tensioning element 24 can dampen a slight tensile force as a locking cable 24a by stretching the locking cable 24a. Generally, it is conceivable that the damping elements 21a, 21b can be pre-tensioned by the tensioning element 24 via the tension unit 30 and the damper system elements 22. Furthermore, the pre-tensioning of the damping elements 21a, 21b can be variably adjusted, in particular changed, by the tensioning element 24. The shock absorber 20 according to Fig. 4a and Fig. 4b can thus dampen any compressive force as well as a small tensile force.

[0090] Fig. 5a and Fig. 5b show a further non-inventive embodiment of the shock absorber 20 according to Fig. 4a and Fig. 4b. In contrast to the shock absorber 20 according to Fig. 4a and Fig. 4b, the shock absorber 20 according to Fig. 5a and Fig. 5b only has a damping element 21. Furthermore, the shock absorber 20 does not include a guide element 23, as in Fig. 4a and Fig. 4b. The design and arrangement of the damper system elements 22 and the damping element 21 according to Fig. 5a and Fig. 5b correspond to the design and arrangement of the damper system elements 22 and the damping elements 21a, 21b according to Fig. 4a and Fig. 4b. Furthermore, the damping element 21 corresponds to one or both damping elements 21a, 21b according to Fig. 4a and Fig. 4b. The materials and the material properties with regard to damping characteristics and elasticity, in particular deformability, of the damping element 21 according to Fig. 5a and Fig. 5b correspond to those of the damping elements 11a, 11b according to Fig. 1a and Fig. 1b.

[0091] The train unit 30 according to Fig. 5a and Fig. 5b, in contrast to the train unit 30 according to Fig. 4a and Fig. 4b no pressure element 32. In the traction unit 30 according to the Fig. 5a and Fig. 5B, the clamping element holder 31 is firmly connected to the respective damper system element 22. Furthermore, it is conceivable that the pulling unit 30, like the one in Fig. 4a and Fig. 4b described traction unit 30 is formed.

[0092] In Fig. Figure 5a shows the shock absorber 20 in the unloaded state. It can be seen that a gap is formed between the free ends 31a of the clamping element receptacles 31. This gap essentially corresponds to the damping travel for damping a compressive force. Fig. 5b, the shock absorber 20 is shown in the pressurized state. A compressive force to be damped acts on the shock absorber 20, which is transmitted via the respective tension units 30 through the damper contact elements 22 to the damping element 21. The clamping element 24 clamps the damper contact elements 22 against the damping element 21, in particular pressing them. The shock absorber 20 according to Fig. 5a and Fig. 5b enables a small size, a simple design and a low weight of the shock absorber 20. List of reference symbols 10 vibration dampers 11, 21 Damping element 11a, 21a first damping element 11b, 21b second damping element 12, 22 Damper system element 12a, 22a first damper system element 12b, 22b second damper system element 13 Piston rod 13a inner end of the piston rod 14 damper pistons 14a first damper piston 14b second damper piston 15, 25 Fastener 15a first fastening element 15b second fastening element 15c additional fastening element 16 damper housing 17 first damper stop 18 second damper stop 20 shock absorbers 23 Guide element 24 clamping element 24a locking rope 30 train units 31 Clamping element holder 31a free end of the clamping element holder 31b further end of the clamping element holder 32 pressure element 33 Locking element 41 Piston recess of the damping element 41a first through-opening of the damping element 41b second through-opening of the damping element 42 Through opening of the damper system element 43 Through hole of the guide element 44 Direction of force 45 Direction of movement of the wheel 46 Damping travel 47 first axial end of the damping element 48 second axial end of the damping element 49 Power transmission range 50 trailer axle 51 Wheel suspension 52 wheels 53 Cross-axle element 54 swing arm

Claims

[1] Vibration damper (10) for a trailer axle of a vehicle trailer with a first damping element (11a) and a second damping element (11b), wherein the damping elements (11a, 11b) are formed from elastomer and each axially bear against a damper contact element (12), and at least one piston rod (13) with a damper piston (14) is provided, characterized byin that the damper piston (14) is arranged between the damping elements (11a, 11b), wherein both damping elements (11a, 11b) bear axially on the damper piston (14) for damping a tensile force and / or a compressive force, wherein the damping elements (11a, 11b) are introduced under prestress in a cylindrical damper housing (16) so that the damper piston (14) is firmly clamped between the damping elements (11a, 11b), wherein the second damping element (11b) is arranged in the damper housing (16) pushed onto the piston rod (13), wherein the second damping element (11b) is designed as a hollow cylinder, and wherein the second damping element (11b) is pressed onto the piston rod (13). [2] Vibration damper according to claim 1, characterized by that the first damping element (11a) and the second damping element (11b) have different hardness values. [3] Vibration damper according to claim 1 or 2, characterized bythat the first damping element (11a) is formed from a harder elastomer than the second damping element (11b). [4] Vibration damper according to one of the preceding claims, characterized by that the first damping element (11a) is hollow-cylindrical. [5] Vibration damper according to one of the preceding claims, characterized by that the damping elements (11a, 11b) are arranged coaxially to one another. [6] Vibration damper according to one of the preceding claims, characterized by that the damper piston (14) is operatively connected to the first damping element (11a) for damping a compressive force and / or the damper piston (14) is operatively connected to the second damping element (11b) for damping a tensile force. [7] Vibration damper according to one of the preceding claims, characterized by that the damper system elements (12) interact with the damping elements (11a, 11b) to dampen a compressive force. [8] Vibration damper according to one of the preceding claims, characterized by that the damper system elements (12) have at least one through-opening (42) through which the piston rod (13) projects. [9] Vibration damper according to one of the preceding claims, characterized by that the damper system element (12) and / or the piston rod (13) comprise at least one fastening element (15) which can be connected to a frame of a vehicle trailer and / or a wheel suspension (51) of a vehicle trailer. [10] Vibration damper according to claim 9, characterized by that the fastening element (15) is arranged on the piston rod (13) such that the damper contact element (12) is braced against the damping element (11). [11] Trailer axle with at least one vibration damper (10) according to one of claims 1 to 10.

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