Traction stop for vibration damper and vibration damper having traction stop

Abstract

The invention relates to a traction stop (10) for a shock absorber (1), comprising at least one elastically deformable damping element (14, 14a, 14b) and an annular main body (13), which has a central guide opening (15) for the passage of a piston rod (4) and at least one receiving opening (17, 17a, 17b), the damping element (14, 14a, 14b) has a receiving opening (17, 17a, 17b) which is introduced into the axial end face (16a, 16b) and is open in the axial direction with respect to the central axis (100), the damping element (14, 14a, 14b) being received in the receiving opening (17, 17a, 17b) in the axial direction with an axial overhang (103) in the unloaded state, the receiving opening (17, 17a, 17b) having a usable space (18) in which the damping element (14, 14a, 14b) can be inserted into the receiving opening (17, 17a, 17b). The damping element (14, 14a, 14b) can be elastically deformed in the loaded state so as to enter the available space, so that the damping element (14, 14a, 14b) is completely accommodated in the accommodating opening (17, 17a, 17b).

Description

Technical Field

[0001] The present invention relates to a traction stop for a shock absorber having the features of the preamble of claim 1. The invention also relates to a shock absorber having the traction stop. Background Technology

[0002] It is well known to use traction stop dampers on shock absorbers, which are located on a support plate on the piston rod side. When the piston rod moves out of its maximum position from the cylinder, the traction stop damper is clamped between the support plate and the piston rod guide, and the elastic deformation of the traction stop damper absorbs the impact energy.

[0003] For example, document DE 10 2018 207 909 B3 discloses a traction stop for a shock absorber, which includes an elastomeric element radially supported via an annular collar, wherein the elastomeric element extends axially along the collar and is supported on a support ring. Multiple individual elastomeric elements are present, each radially housed within a receiving opening of the collar. Summary of the Invention

[0004] The purpose of this invention is to provide a shock absorber with a traction stop, characterized by a robust structure and low noise.

[0005] This objective is achieved by a traction stop having the features of claim 1 and a shock absorber having the features of claim 14. Advantageous designs are derived from the dependent claims, drawings, and / or description.

[0006] The subject of this invention is the construction of a traction stop for and / or suitable for a shock absorber. In particular, the traction stop is used to form an axial stop when the piston rod of the shock absorber is in the maximum extended position.

[0007] The traction stop has at least one or exactly one elastically deformable damping element. Specifically, the damping element applies damping to the traction stop when the piston rod reaches its maximum extension position. In other words, as the piston rod moves out of the cylinder, the damping element impacts the end stop within a predetermined end stroke range of the piston. Specifically, the traction stop functions within the piston's end stroke range, but is ineffective or non-functional within the piston's normal stroke range. The damping element may be substantially annular and / or rotationally symmetric about the longitudinal axis of the piston rod.

[0008] Furthermore, the traction stop has an annular base. This base has a central guide opening for the piston rod to pass through and at least one, or exactly one, receiving opening for accommodating a buffer element, which is introduced into the axial end face of the base and opens in the axial direction about the central axis. Specifically, the base serves as a reinforcement for the elastically deformable buffer element. Specifically, the base can move relative to the piston rod along the longitudinal axis. Preferably, the buffer element is arranged coaxially with respect to the base and / or the piston rod about the longitudinal axis.

[0009] The damping element, in its unloaded state, is received in the receiving opening with an axially protruding portion in the axial direction. In other words, the damping element is arranged to have a protruding portion relative to the axial end face of the base in the axial direction. The damping element can preferably be supported on the end stop of the damper in a resilient manner in the axial direction. This end stop can be formed by a support ring fixed to the piston rod and / or a piston rod guide.

[0010] Within the scope of this invention, it is proposed that the receiving opening has available space, and the buffer element, under load, can elastically deform to enter this available space, such that the buffer element is fully received within the receiving opening. In other words, upon reaching the end stop, the buffer element can deform so that it is fully submerged in the receiving opening. It is proposed that the buffer element initially bears an initial and / or small traction stopping force at the beginning of the loading state, and then, particularly after the buffer element has submerged in the receiving opening, the substrate bears a full and / or large traction stopping force. Preferably, the substrate can be considered in the overall characteristic curve. For this purpose, after the softer buffer element has fully submerged, the substrate can also elastically deform, preferably having higher strength, more precisely, a higher elastic modulus. Therefore, the overall characteristic curve of the traction stop can initially be flat, and then become steeper or more gradual with increasing deformation.

[0011] The advantage of this invention is that, under high traction stop forces, the additional available space allows the buffer element to be fully deformed into the receiving opening, protecting it from damage. Another advantage is that the substrate, depending on the design or material, can form additional, particularly more rigid, buffers, which can be taken into account in the overall characteristic curve, thereby achieving a gradual increase in damping force. Thus, even very high stop forces can be borne or damped by the traction stop, significantly improving the noise behavior of the shock absorber.

[0012] In one specific implementation, the buffer element is proposed to be fully housed or contained within a receiving opening under load, such that the substrate is directly and / or planarly supported on the end stop via its axial end face. Specifically, "housed" is understood to mean that the buffer element can deform and / or deform into the receiving opening, such that the buffer element is surrounded and / or supported by the substrate on most of its circumferential surface. By fully housing or containing a softer buffer element, it can be reliably protected from high loads. Furthermore, by directly or planarly supporting the substrate, a greater degree of asymmetry is achieved on the characteristic curve of the softer buffer element.

[0013] In one specific design, the available space is formed by an undercut, into which the buffer element deforms radially under load and / or can deform radially and enter. Specifically, under load, more precisely, when subjected to axial deformation force, the buffer element can be axially supported within the matrix and can radially elastically deform into the undercut to accommodate the excess volume of the buffer element. Specifically, the undercut is understood as a radially widened portion of the receiving opening within the matrix. For this purpose, the diameter of the receiving opening is selected such that it is smaller than the diameter of the widened portion, at least at the outlet portion on the end side, i.e., at the axial end face. Specifically, the undercut causes the receiving opening to narrow radially in the axial direction. The undercut and the resulting radial deformation ensure that the buffer element deforms or is accommodated within the receiving opening under load and thus does not become trapped between the matrix and the end stop.

[0014] In one improved embodiment, the available space defines an available volume that is greater than the volume of the axially protruding portion of the buffer element. In other words, after the buffer element has fully deformed into the receiving opening, an unoccupied remaining volume remains between the buffer element and the base. Specifically, the protruding volume is understood as the portion of the buffer element that protrudes axially from the receiving opening and / or extends beyond the axial end face in the unloaded state, i.e., the relaxed state. This unoccupied remaining volume can compensate for tolerances that may arise, for example, due to thermal expansion. This ensures that the buffer element is always fully contained within the receiving opening in the loaded state.

[0015] In one specific implementation, the ratio of available space volume to excess volume is proposed to be between 1.8:1 and 1.5:1. In other words, the available space volume is preferably more than 1.5 times and / or less than 1.8 times the excess volume. Alternatively or optionally, the remaining volume is greater than 50% and / or less than 80% of the excess volume. Therefore, a receiving opening is proposed that provides sufficient available space for the buffer element.

[0016] In another specific implementation, the ratio of the excess volume to the total volume of the buffer element is proposed to be between 1:5 and 1:6. In other words, the excess volume is less than 0.2 times and / or more than 0.1 times the total volume. Alternatively or optionally, the excess volume is greater than 10%, preferably greater than 15%, and particularly greater than 20% of the total volume. Therefore, a traction stop is proposed in which a large portion of the buffer element can be arranged within the receiving opening and thus securely held within it.

[0017] In one possible and specific implementation, the receiving opening is constructed as an axially through opening, wherein the buffer element extends beyond the axial structural height of the substrate on both sides. In other words, the receiving opening is also additionally open in the opposite axial direction, wherein the buffer element, in the unloaded state, is additionally received in the receiving opening with an axially protruding portion in the opposite axial direction. The available space is preferably constructed in the substrate at the center of the receiving opening and / or at the center between the two end sides. In principle, the buffer element can protrude with different axial protrusions on both sides to achieve a target force characteristic curve with a progressively increasing damping force. Alternatively, the buffer element can protrude with equal axial protrusions on both sides to avoid the need to assemble the traction stop according to its positional orientation. In principle, the receiving opening can be constructed as a through opening surrounding the longitudinal axis, i.e., the central axis, in which a circumferential and / or annular buffer element is received. However, the substrate can also alternatively have multiple circumferentially spaced receiving openings, preferably through holes, in which a single buffer element is received respectively. The cushioning element can be locked in the receiving opening in a form-fitting and / or force-transmitting and / or material-attached manner to prevent detachment. For example, the cushioning element can be formed during the manufacture of the matrix using injection molding technology and / or connected to the matrix via an injection connection. Therefore, a traction stop is proposed that allows for elastic support on both sides via the cushioning element.

[0018] In an alternative implementation, the traction stop has buffer elements on both sides, each buffer element having an axially protruding portion accommodated in a corresponding receiving opening in the unloaded state, and fully deformable and / or capable of fully deforming into the corresponding receiving opening in the loaded state. In other words, the traction stop has another elastically deformable buffer element, and the base has another receiving opening introduced into a particularly opposing axial end face and open in the axially opposite direction about the central axis. In the unloaded state, this other buffer element has an axially protruding portion accommodated in the other receiving opening in the axially opposite direction. Furthermore, this other receiving opening has another usable space into which another buffer element can fully elastically deform in the loaded state. In principle, the buffer elements and / or receiving openings can be designed to be structurally identical or completely the same to avoid the need to assemble the traction stop according to positional orientation. Alternatively, the buffer elements and / or receiving openings can also be designed differently to achieve a target force characteristic curve with a progressively increasing damping force. Preferably, the receiving openings are designed as recesses surrounding the longitudinal axis, i.e., the central axis, in which circumferential and / or annular buffer elements are respectively accommodated. The buffer elements can be form-fitted and / or force-transmittingly locked in the corresponding receiving openings to prevent them from falling out. Therefore, an alternative traction stop is proposed, which achieves elastic support on both sides by two buffer elements.

[0019] In one specific design, two buffer elements are each formed by an O-ring, and two receiving openings are each formed by a circumferential groove. The groove can have a T-shape, trapezoidal shape, or dovetail shape to form an undercut. Specifically, the narrowing of the receiving opening retains the O-ring within the opening without it falling out. The groove can be formed in the substrate non-cuttingly, for example by embossing or crimping, or cut-shaped in the substrate, for example by milling or turning, or formed in the substrate during manufacturing, for example by injection molding. Thus, a traction stop is proposed, characterized by easy assembly. Furthermore, the O-ring can be pre-assembled in the corresponding receiving groove, wherein the narrowing of the receiving opening ensures that the O-ring will not fall out.

[0020] In one improved embodiment, two receiving openings and / or two buffer elements are optionally arranged opposite to or offset from each other. Specifically, "opposite" means that the two receiving openings and / or buffer elements are introduced into their respective end faces opposite each other with a common pitch circle diameter. In other words, the two receiving openings and / or buffer elements have the same diameter and / or the same radial distance from the central axis or longitudinal axis. Specifically, "offset" means that the two receiving openings and / or buffer elements are introduced into their respective end faces offset from each other with different pitch circle diameters. In other words, the two receiving openings and / or buffer elements have different diameters and / or different radial distances from the central axis or longitudinal axis. Therefore, a traction stop is proposed in which the influence characteristic curve can be easily influenced according to the radial offset between the buffer elements.

[0021] In one improved embodiment, the available space volumes of the two available spaces and / or the axial overhangs of the two buffer elements and / or the overhang volumes and / or the total volume and / or the hardness grades are different. The force characteristic curve can be selectively influenced by changing the volume of the receiving opening and / or the volume of the buffer elements and / or changing the position and / or design of the buffer elements, to achieve, for example, a gradual increase in damping force. For example, a set of parts consisting of multiple different substrates and / or buffer elements can be provided, from which appropriate substrates and / or appropriate buffer elements and / or arbitrary combinations can be selected according to the desired traction stop characteristics. The substrates can, for example, be designed with different groove depths, materials, structural heights, etc. The buffer elements or O-rings can, for example, be designed with different hardness grades, designs, volumes, etc. Optionally, multiple traction stop portions in the traction stop section can be arranged sequentially, i.e., stacked vertically, in the axial direction about the longitudinal axis or central axis, so that the elastic coefficients or stiffnesses of the traction stop portions can be accumulated or connected in series. This allows for a simple and targeted modification of the force characteristic curve, thus increasing versatility.

[0022] In another feasible implementation, the substrate is proposed to be formed of at least two or exactly two substrate portions separated radially in the region accommodating the opening, these substrate portions being connected to each other by form-fitting connections and / or force-transmitting connections. Specifically, the at least two substrate portions can be connected to each other by insertion and / or rotational movement. The substrate portions can be connected to each other, for example, by plug-in connections and / or snap-fit ​​connections, such as hooks, annular snap-fit ​​connections, or fixed beak connections. Alternatively, the at least two substrate portions can also be connected to each other by snap-fit ​​connections. As an alternative or optional supplement, the substrate portions can also be connected to each other by material connections, such as welded connections, adhesive connections, or brazed connections. By adopting a multi-piece, particularly two-piece, design for the substrate, the available space in the substrate, especially the undercut, can be significantly and more easily integrated into the manufacturing process.

[0023] In one specific embodiment, the matrix is ​​made of plastic and / or metal alloy, and the cushioning element is made of rubber material and / or elastomer. For example, nitrile rubber (also known as Nitrile Butadiene Rubber (NBR)) can be used as the rubber material. As an alternative or optional supplement, the matrix has a higher strength and / or modulus of elasticity than the cushioning element, i.e., the cushioning element has a lower strength and / or modulus of elasticity than the matrix. For example, the Shore hardness of the cushioning element can be between 70 and 90.

[0024] Another subject of the invention relates to a shock absorber having a traction stop as described above or according to any one of claims 1 to 13. In particular, the shock absorber is configured for and / or suitable for applying damping to vibrations. The shock absorber is preferably configured as a hydraulic damper. In particular, the shock absorber can be configured for and / or suitable for a vehicle chassis. The shock absorber preferably has at least one cylinder filled with a damping medium, in which a piston rod is axially guided about a longitudinal axis. In particular, the piston rod defines the longitudinal axis. The shock absorber preferably has a piston that is kinematically coupled to the piston rod within the cylinder and divides the cylinder into at least two working spaces.

[0025] In one specific embodiment, the damper has a support ring axially fixed to the piston rod and a piston rod guide for axially guiding the piston rod, wherein a traction stop is axially arranged and / or can be supported between the support ring and the piston rod guide. The piston rod guide can be configured, for example, as an end cap that fluid-tightly seals the cylinder at its end. The support ring is configured to surround the piston rod and / or is arranged coaxially with the piston rod. Specifically, the support ring is arranged within a working space on the piston rod side. The support ring can be fixed to the piston rod axially spaced from the piston. Alternatively, the support ring can also form part of a damping valve on the piston. Attached Figure Description

[0026] Further features, advantages, and effects of the present invention are given in the following description of preferred embodiments of the invention. The accompanying drawings illustrate:

[0027] Figure 1 A cross-sectional view of a shock absorber with a traction stop section, as an embodiment of the present invention, is shown.

[0028] Figure 2 A partial cross-sectional view of a traction stop for a shock absorber, as an embodiment of the present invention, is shown.

[0029] Figure 3 It shows Figure 2 Detailed view of the traction stop in the middle;

[0030] Figure 4 It shows Figure 2 Another detailed view of the base of the traction stop section;

[0031] Figure 5 An alternative embodiment of the traction stop is shown in cross-sectional view;

[0032] Figure 6 Another alternative embodiment of the traction stop is shown in a detailed sectional view;

[0033] Figure 7 An alternative embodiment of the traction stop is shown in a detailed cross-sectional view. Detailed Implementation

[0034] Figure 1 A shock absorber 1 is shown, which is suitable, for example, for a vehicle wheel suspension. The shock absorber 1 is constructed as a twin-tube damper and has an inner cylinder 2 and an outer cylinder 3 for this purpose, wherein the inner cylinder 2 is arranged radially spaced within the outer cylinder 3 in a manner coaxial with respect to a longitudinal axis or a central axis 100. The inner cylinder 2 and the outer cylinder 3 are at least partially filled with a damping medium, such as hydraulic oil.

[0035] The piston rod 4, together with the piston 5, is axially movable within the inner cylinder 2. The piston 5 divides the inner cylinder 2 into a working space 6a on the piston rod side and a working space 6b away from the piston rod. The working space 6a on the piston rod side is closed at the end by a piston rod guide 7, which guides the piston rod 4 in an axial direction about the longitudinal axis 100.

[0036] The piston 5 includes two damping valves 8 and 9, which generate damping force according to direction. An additional functional unit for generating a stopping force that resists the extension movement of the piston rod 4 is a traction stop 10, which is supported on a support ring 11 fixed to the piston rod 4. For example, the support ring 11 can be securely connected to the piston rod 4 via a form-fit connection. Alternatively, the traction stop 10 can also be supported on the piston 5, more specifically, on the damping valves 8, via a support disc. The traction stop 10 limits the maximum extension of the piston rod 4 in the axial direction 101, and more specifically applies damping when it reaches the end stop 12 formed by the piston rod guide 7.

[0037] Figure 2 The traction stop 10 is shown in partial cross-section, revealing that it comprises an annular base 13 and two elastically deformable buffer elements 14a and 14b. The base 13 has a central guide opening 15 through which the piston rod 4 is guided during installation. For this purpose, the guide opening 15 is configured as a through-hole extending through the base 13 in an axial direction about the longitudinal axis 100. Thus, the base 13 is arranged in a form-fitting manner on the piston rod 4 in the radial direction, more precisely, centered on the piston rod, and is movable relative to the piston rod 4 in the axial direction.

[0038] Furthermore, the base 13 has receiving openings 17a and 17b on both sides that extend into axial end faces 16a and 16b, respectively, and each receiving opening accommodates one of the buffer elements 14a and 14b. The first receiving opening 17a is open along the axial direction 101, such that the first buffer element 14a partially extends beyond the axial first end face 16a. The second receiving opening 17b is open along the opposite axial direction 102, such that the second buffer element 14b partially extends beyond the axial second end face 16b.

[0039] In the illustrated embodiment, the two receiving openings 17a, 17b and the two buffer elements 14a, 14b are arranged axially opposite to each other, or more precisely, overlapping each other. In other words, the diameters of the two receiving openings 17a, 17b and the two buffer elements 14a, 14b and their radial distances from the longitudinal axis 100 are equal.

[0040] The two receiving openings 17a and 17b are each configured as annular grooves around the longitudinal axis 100. The two cushioning elements 14a and 14b are each configured as O-rings. The substrate 13 can be configured as a plastic ring or a metal ring. The O-rings can be made of NBR (nitrile butadiene rubber) or an elastomer. Here, the substrate 13 has a strength and / or elastic modulus greater than that of the cushioning elements 14a and 14b.

[0041] Figure 3A detailed illustration of a receiving opening 17a with a buffer element 14a is shown, wherein the following description similarly applies to another receiving opening 17b and another buffer element 14b. Buffer elements 14a and 14b, in their unloaded state, are received in their respective receiving openings 17a and 17b along the axial direction 101 or the opposite axial direction 102 and have a certain axial overhang. This axial overhang 103 is, for example, less than 1 / 4 of the total cross-sectional diameter of the buffer elements 14a and 14b. For example, buffer elements 14a and 14b are each constructed as 22×4 O-rings, with a cross-sectional diameter of 4 mm and an axial overhang 103 of 0.9 mm.

[0042] The receiving openings 17a and 17b each have a usable space 18 formed by a circumferential undercut 19. This usable space 18 forms a deformation space for the corresponding buffer elements 14a and 14b, which, when loaded—more precisely, when subjected to a stopping force acting in the opposite axial direction 102—can radially displace, or more precisely deform, into this deformation space. Therefore, the buffer elements 14a and 14b expand and contract axially under load, and can additionally flow into or expand and contract radially into the usable space 18. The usable space 18 is designed such that the corresponding buffer elements 14a and 14b can be fully submerged into the receiving opening 17a according to the stopping force, causing the base 13 to make surface contact with the axial end faces 16a and 16b. This allows the softer buffer elements 14a and 14b to be housed or supported within the corresponding receiving openings 14a and 14b, and thus not to bear high loads.

[0043] When subjected to load, the softer buffer element 14a should withstand the initial stopping force, i.e., a smaller stopping force. Subsequently, after the buffer elements 14a and 14b have sunk in, the base 13 can withstand the full stopping force. Therefore, the base 13 defines the maximum extension length of the piston rod 4. After the buffer elements 14a and 14b have fully sunk into the corresponding receiving openings 17a and 17b, the base 13 can further withstand or dampen the stopping force depending on the specific material, and this can be taken into account in the force characteristic curve of the traction stop 10. Therefore, the force characteristic curve of the traction stop 10 is initially flat and becomes steeper and / or more gradual as the stroke increases.

[0044] Figure 4 A detailed view shows the receiving opening 17a without the cushioning element 14a, wherein the description below similarly applies to the other receiving opening 17b. Receiving openings 17a and 17b can be formed in the substrate 13, for example, by milling, turning, embossing, or crimping. Alternatively, receiving openings 17a and 17b can also be constructed in the substrate 13 within the framework of a forging or injection molding process.

[0045] To form the undercut portion 19, the receiving opening 17a has an opening profile that tapers along the axial direction 101, while the receiving opening 17b has an opening profile that tapers along the opposite axial direction 102, so that the receiving openings 17a and 17b each have a narrowing portion 20 in the region of the axial end faces 16a and 16b, respectively. For example, in the case of a 22×4 O-ring, the receiving openings 17a and 17b have an opening diameter 104 of approximately 3.7 mm and an opening depth 105 of approximately 3.1 mm in the region of the narrowing portion 20. Therefore, the diameter of the narrowing portion 20 is smaller than the diameter of the O-ring, so that the O-ring (also as...) Figure 3 As shown, the O-ring is surrounded on both sides in the narrowed region 20, so that it remains in the corresponding receiving openings 17a, 17b and does not fall out. In cross-section, the receiving openings 17a, 17b have, for example, a dovetail shape.

[0046] To form the undercut 19, the two side surfaces 21a, 21b accommodating the openings 17a, 17b are inclined relative to each other at an opening angle 106 along the direction of the narrowing 20. For example, the opening angle 106 can be at least 40°, preferably 48°. The two side surfaces 21a, 21b transition to the bottom surface 22 via a fillet radius 107, the distance from the bottom surface to the end surfaces 16a, 16b defining the opening depth 105. For example, the fillet radius 107 can be between 0.8 mm and 1.6 mm, preferably between 1.2 mm and 1.4 mm. Similarly, another fillet radius 108 can be provided in the region of the narrowing 20 to avoid sharp transitions and thus protect the corresponding cushioning elements 14a, 14b from damage. For example, this other fillet radius 108 can have a radius of 0.25 mm.

[0047] Based on the opening angle 106 and the fillet radius 107, the usable space 18 can thus be defined. Here, the usable space 18 should have a larger usable volume than the volume of the axially protruding portion 103, so that unoccupied remaining volume is left when the buffer elements 14a, 14b are fully accommodated in the corresponding receiving openings 17a, 17b. For example, the remaining volume may be greater than 0.5% and / or less than 20%, preferably greater than 8% and / or less than 14% of the total volume of the corresponding buffer elements 14a, 14b.

[0048] Therefore, an accommodating opening 17a, 17b is proposed, which on the one hand provides sufficient usable space 18 under different thermal expansion of buffer elements 14a, 14b, and on the other hand can guide or support buffer elements 14a, 14b, thereby achieving a higher degree of asymptoticity in the force-stroke diagram of buffer elements 14a, 14b.

[0049] Figure 5An alternative embodiment of the traction stop 10 is shown, in which the two buffer elements 14a, 14b are arranged offset from each other. For this purpose, the undercut 19 of the first receiving opening 17a is formed only on the radially inner side 21b, while the radially outer side 21a extends straight, or more precisely, parallel, relative to the longitudinal axis 100. The undercut 19 of the second receiving opening 17b is formed on the radially outer side 21a, while the radially inner side 21b extends straight, or more precisely, parallel, relative to the longitudinal axis 100. Thus, the narrowing portions 20 of the two receiving openings 17a, 17b are arranged offset from each other in the radial direction. Accordingly, the diameters of the two O-rings must be different.

[0050] By staggering the receiving openings 17a, 17b on the end faces 16a, 16b of the substrate 13 and the buffer elements 14a, 14b, and by changing the volume of the receiving openings 17a, 17b, the characteristic curve trend in the force-stroke diagram can be altered. Furthermore, the buffer elements 14a, 14b can be provided according to different hardness grades (Shore hardness), designs, engagement depths, etc., to further alter the characteristic curve trend or performance. Additionally, the characteristic curve trend can optionally be altered by the accumulation and / or series connection of multiple traction stops 10.

[0051] Figure 6 An alternative embodiment of the traction stop 10 is shown, in which the base 13 is formed of two base portions 23a, 23b, which are radially separated in the region accommodating the openings 17a, 17b. The two base portions 23a, 23b can be connected to each other via a form-fit connection 24, such as a hook / fixed beak connection, a snap-fit ​​connection, or a pull-out connection, to secure these portions. The form-fit connection 24 can be generated, for example, by pull-out movement of the two base portions 23a, 23b in the axial direction about the longitudinal axis 100 and / or by rotational movement in the circumferential direction about the longitudinal axis 100. By separating the base 13 in the region accommodating the openings 17a, 17b, the undercut 19 can be manufactured more conveniently and cost-effectively, for example, by injection molding.

[0052] Figure 7Another alternative embodiment of the traction stop 10 is shown, in which the traction stop 10 has an axially continuous receiving opening 17 in which an axially continuous buffer element 14 is arranged. The receiving opening 17 and the buffer element 14 can be configured to be annular around the longitudinal axis 100. The buffer element 14 extends axially beyond the axial structural height of the base 13 on both sides with axially protruding portions 103. For example, the axially protruding portions 103 on both sides of the base 13 are the same size. The undercut portion 19 can be axially centered within the receiving opening 17 by means of annular grooves on the inner and outer surfaces of the surrounding receiving opening 17. In this case, the available space 18 has a usable space volume that is also greater than the sum of the volumes of the protruding portions of the two axially protruding portions 103, so that the buffer element 14 can be fully accommodated in the receiving opening 17 under load.

[0053] List of reference numerals in the attached diagram:

[0054] 1. Vibration damper

[0055] 2 Inner cylinder

[0056] 3. Outer cylinder

[0057] 4 Piston rod

[0058] 5 pistons

[0059] Workspaces 6a and 6b

[0060] 7 Piston rod guide section

[0061] 8, 9 Damping valves

[0062] 10 Traction stop section

[0063] 11 Support ring

[0064] 12 End stop

[0065] 13 Matrix

[0066] 14a and 14b buffer elements

[0067] 15 guide openings

[0068] 16a and 16b end faces

[0069] 17a, 17b contain openings

[0070] 18 available spaces

[0071] 19. Undercut

[0072] 20 Narrowing section

[0073] Side views of 21a and 21b

[0074] 22 bottom

[0075] 23a, 23b matrix portions

[0076] 24 Shape-fitting connection parts

[0077] 100 Longitudinal axis

[0078] 101 Axial direction

[0079] 102. Opposite directions of the axis

[0080] 103 Axial Excess Part

[0081] 104 Opening diameter

[0082] 105 Opening depth

[0083] 106 Opening angle

[0084] 107 Corner radius

[0085] 108 Another corner radius.

Claims

1. A traction stop (10) for a shock absorber (1), the traction stop having -At least one elastically deformable cushioning element (14, 14a, 14b), - An annular base (13) having a central guide opening (15) for the piston rod (4) to pass through and at least one receiving opening (17, 17a, 17b) introduced into an axial end face (16a, 16b) and open in the axial direction about the central axis (100), wherein, The buffer elements (14, 14a, 14b) are accommodated in the accommodating openings (17, 17a, 17b) with axially protruding portions (103) along the axial direction in the unloaded state. Its features are, The receiving openings (17, 17a, 17b) have available space (18), and the buffer elements (14, 14a, 14b) can elastically deform under load to enter the available space, so that the buffer elements (14, 14a, 14b) are completely accommodated in the receiving openings (17, 17a, 17b).

2. The traction stop (10) according to claim 1, characterized in that, The buffer elements (14, 14a, 14b) are fully housed in the receiving openings (17, 17a, 17b) in the loaded state, so that the base (13) can be directly and / or planarly supported on the end stop (12) of the damper (1) through the axial end faces (16a, 16b).

3. The traction stop (10) according to claim 1 or 2, characterized in that, The available space (18) is formed by an undercut (19), and the buffer elements (14, 14a, 14b) are radially deformable and / or capable of radially deforming and entering the undercut (19) under the loaded state.

4. The traction stop (10) according to any one of the preceding claims, characterized in that, The available space (18) defines an available space volume that is greater than the volume of the axially extended portion (103) of the buffer elements (14, 14a, 14b).

5. The traction stop (10) according to claim 4, characterized in that, The ratio of the available space volume to the excess volume is between 1.8:1 and 1.5:

1.

6. The traction stop (10) according to claim 4 or 5, characterized in that, The ratio of the excess volume to the total volume of the buffer elements (14, 14a, 14b) is between 1:5 and 1:

6.

7. The traction stop (10) according to any one of the preceding claims, characterized in that, The receiving opening (17) is configured as an axial through opening, wherein the buffer element (14) is received in the receiving opening (17) with axially extended portions (103) on both sides in the axial direction in the unloaded state.

8. The traction stop (10) according to any one of claims 1 to 6, characterized in that, The traction stop (10) has two buffer elements (14a, 14b) and receiving openings (17a, 17b) respectively introduced into the axial end faces (16a, 16b). The two buffer elements (14a, 14b) are accommodated in the corresponding receiving openings (17a, 17b) with axial overruns in the unloaded state and can elastically deform into the corresponding available space (18) in the loaded state, so that the two buffer elements (14a, 14b) are completely accommodated in the corresponding receiving openings (17a, 17b).

9. The traction stop (10) according to claim 8, characterized in that, The two buffer elements (14a, 14b) are each formed by an O-ring, and the two receiving openings (17a, 17b) are each formed by a circumferential groove.

10. The traction stop (10) according to claim 8 or 9, characterized in that, The two receiving openings (17a, 17b) and / or the two buffer elements (14a, 14b) are arranged opposite to each other or staggered from each other.

11. The traction stop (10) according to any one of claims 8 to 10, characterized in that, The available space volumes of the two available spaces (18) and / or the axial overhangs (103) and / or the overhang volumes of the two buffer elements (14a, 14b) and / or the total volume and / or the hardness grades (Shore hardness) are not the same.

12. The traction stop (10) according to any one of the preceding claims, characterized in that, The base (13) is formed by two base portions (23a, 23b) that are radially separated in the region of the receiving openings (17, 17a, 17b), and the base portions are connected to each other by form-fitting connections and / or force-transmitting connections.

13. The traction stop (10) according to any one of the preceding claims, characterized in that, The substrate (13) is made of plastic and / or metal alloy and / or has higher strength than the cushioning elements (14, 14a, 14b), and the cushioning elements (14, 14a, 14b) are made of rubber material and / or elastomer and / or have lower strength than the substrate (13).

14. A shock absorber (1) having a traction stop (10) according to any one of the preceding claims.

15. The vibration damper (1) according to claim 14, characterized in that, The shock absorber has a support ring (11) axially fixed to the piston rod (4) and a piston rod guide (7) for axially guiding the piston rod (4), wherein the traction stop (10) is axially arranged and / or can be supported between the support ring (11) and the piston rod guide (7).

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