Damping device for a bicycle

Abstract

The invention relates to a damping device (28) for a bicycle (10), comprising an outer tube (30) and an inner tube (32) arranged coaxially to same, wherein a compensation chamber (34) for receiving hydraulic fluid is formed between the outer tube (30) and the inner tube (32), and a piston (40) which is connected to a piston rod (42) and which is arranged so as to be movable back and forth within the inner tube (32), wherein the interior of the inner tube (32) is divided by the piston (40) into a piston-rod-remote working chamber (44) and a piston-rod-side working chamber (46), and wherein the damping device (28) has a valve device (50) mounted on the outside of the outer tube (30) and having a compression damping valve (52) for damping the piston movement in the compression stage and having a rebound damping valve (54) for damping the piston movement in the rebound phase, and wherein the valve device (28) has a valve body (72) with an inner fluid channel (66) and an outer fluid channel (64) which is arranged radially outwards with respect to the inner fluid channel (66), and has a first and a second disc spring stack (74, 76) which are mounted on opposite sides of the valve body (72), and wherein the first disc spring stack (74) at least partially radially covers the inner fluid channel (66) and wherein the second disc spring stack (76) at least partially radially covers the inner and the outer fluid channel (64, 66) and has a fluid passage (88) which is fluidically connected to the inner fluid channel (66).

Description

[0001] Damping device for a bicycle

[0002] The invention relates to a damping device for a bicycle and to a rear wheel damper of a bicycle with such a damping device.

[0003] Bicycles, especially mountain bikes, are often equipped with shock absorbers to dampen the bicycle's movement when riding over uneven terrain. Typically, the movement of each wheel, i.e., the rear wheel and the front wheel, is dampened by a separate shock absorber. For example, the rear wheel is connected to the bicycle frame via a rear shock absorber, and the front wheel via a suspension fork. The rear shock absorber and / or the suspension fork often incorporate a damping device with a single-tube or multi-tube shock absorber. The terms "top," "bottom," "front," and "rear" used in this application refer to the usual operating position of a damping device and a suspension fork or shock absorber on a bicycle. A suspension fork with a damping device is known from DE102015115678A1.

[0004] When driving on uneven terrain, comfortable damping is desirable, ideally with progressive damping. High-amplitude vibrations between the piston rod and the inner tube present a challenge: high damping forces are required to achieve optimal driving dynamics without simultaneously increasing the damping force in the range of low excitation amplitudes, which would negatively impact ride comfort.

[0005] Based on this, the object of the present invention is to provide a damping device for a bicycle that enables increased riding safety and comfort, particularly on uneven surfaces and / or at high damping speeds, and which should also be inexpensive and easy to manufacture. This object is achieved according to the invention by a device with the features of independent claim 1. Advantageous embodiments are described in the dependent claims.

[0006] A damping device for a bicycle comprises, according to a first aspect, an outer tube and an inner tube arranged coaxially to it, wherein a compensating chamber for receiving hydraulic fluid is formed between the outer tube and the inner tube, and a piston connected to a piston rod, which is arranged to be movable back and forth within the inner tube, wherein the interior of the inner tube is divided by the piston into a working chamber remote from the piston rod and a working chamber on the side of the piston rod, and wherein the damping device has a valve assembly located outside the outer tube. The valve assembly is, in particular, located completely outside of and separate from the piston, wherein the piston, for example, has a valve separate from the valve assembly.The valve assembly preferably comprises a compression stage valve for damping the piston movement during the compression stage and a rebound stage valve for damping the piston movement during the rebound stage. The valve assembly has a valve body with an inner fluid channel and an outer fluid channel arranged radially outward from the inner fluid channel. The valve assembly also has a first and a second spring washer assembly mounted on opposite sides of the valve body. The first spring washer assembly at least partially radially covers the inner fluid channel, and the second spring washer assembly at least partially radially covers both the inner and outer fluid channels and has a fluid passage arranged in fluid communication with the inner fluid channel.

[0007] The compression stage valve and the rebound stage valve are preferably identical in design. Both the compression stage valve and the rebound stage valve are preferably designed to allow hydraulic fluid to flow through them in both directions. Preferably, each compression stage valve and the rebound stage valve has a valve body with a first and a second spring washer assembly. The valve body preferably has a plurality of inner and outer fluid channels. The fluid channels preferably extend from one end face of the valve body to the opposite end face and are, in particular, arranged separately from each other, preferably fluidically separated. The outer fluid channels are preferably all arranged radially outwards from the inner fluid channels.The outer fluid channels are arranged in a ring-like configuration on an outer circular annulus with an outer ring diameter, while the inner fluid channels are arranged in a ring-like configuration on an inner circular annulus with an inner ring diameter, within the valve body. The outer and inner circular annulus are preferably arranged coaxially with the valve body. The fluid channels preferably extend substantially or completely through the valve body in the axial direction. In particular, the outer and inner fluid channels are each arranged at a uniform distance from one another. The inner and outer fluid channels are preferably identical in design.

[0008] The outer and / or inner fluid channels have, for example, a round, circular, oval, or oblong cross-sectional area. In particular, the geometry of the cross-sectional areas of the inner fluid channels differs from that of the outer fluid channels.

[0009] The fluid channels are each covered in a fluid-tight manner by at least one or exactly one spring washer assembly. Preferably, the valve assembly, in particular the compression stage valve and / or the rebound stage valve, has a first spring washer assembly that is designed and arranged such that it completely covers the inner fluid channels, in particular in a fluid-tight manner. Preferably, the first spring washer assembly is arranged such that it determines the flow cross-section of the inner fluid channels when flow occurs in a first flow direction, in particular by at least partially or completely sealing the inner fluid channels in a fluid-tight manner. In particular, the first spring washer assembly rests against an end face of the valve body in such a way that, depending on the flow velocity, it seals the inner fluid channels when flow occurs in a first flow direction or at least partially or completely opens the flow cross-section.The first spring washer assembly is preferably arranged such that it completely closes the inner fluid channels when fluid flows through them in a second direction opposite to the first. When fluid flows through the inner channels in the second direction, the first spring washer assembly is preferably designed as a check valve, thus preventing flow in the second direction.

[0010] The first flow direction is preferably the main flow direction. In the case of a pressure-stage valve, the main flow direction is the flow direction of the hydraulic fluid during a piston movement in the compression direction, while in the case of a rebound-stage valve, the main flow direction is the flow direction of the hydraulic fluid during a piston movement in the extension direction.

[0011] The first spring washer assembly preferably comprises a plurality of spring washers, which are arranged, for example, parallel to one another and, in particular, abut one another. The spring washers are, in particular, annular in shape. In particular, the spring washers all have the same diameter and are optionally identical in design. The first spring washer assembly is preferably designed and arranged such that it does not cover the flow cross-section of the outer fluid channels at all or only partially.

[0012] In particular, the valve assembly, especially the compression stage valve or the rebound stage valve, is in a closed position when the first spring washer assembly rests against the valve body in such a way that it at least partially or completely closes the internal fluid channels. The valve assembly is preferably in an open position when the first spring washer assembly is lifted from the valve body by the hydraulic flow in the main flow direction and forms an opening cross-section between the first spring washer assembly and the valve body.

[0013] The second spring washer assembly is designed and arranged such that it completely, and in particular fluid-tightly, covers the outer fluid channels when flow occurs in the first flow direction. When flow occurs in the outer fluid channels in the first flow direction, the second spring washer assembly is preferably designed as a check valve, thus preventing flow in the first flow direction. In particular, the second spring washer assembly rests against an end face of the valve body such that, depending on the flow velocity, it closes the outer fluid channels when flow occurs in the second flow direction or at least partially or completely opens the flow cross-section. The second spring washer assembly is preferably designed and arranged such that it does not cover the flow cross-section of the inner fluid channels, or only partially covers it.

[0014] The second spring washer assembly comprises, for example, exactly one, two, or more spring washers, which are / are annular in shape. Preferably, the second spring washer assembly has an outer diameter that is larger than the outer annular diameter on which the outer fluid channels of the valve body are arranged, such that the second spring washer assembly projects radially beyond the outer fluid channels. Preferably, the second spring washer assembly has an outer diameter that is less than or equal to the outer diameter of the valve body.

[0015] The second spring washer assembly has at least one fluid passage arranged such that hydraulic fluid can flow through the passage into the inner fluid channel. This arrangement ensures that, in the first flow direction (main flow direction) of the hydraulic fluid, the fluid passage is hydraulically upstream of the inner fluid channel, thus enabling flow control via the fluid passage. The second spring washer assembly therefore preferably functions as a pre-throttle when the fluid flows through the valve assembly, in particular the compression valve or the rebound valve, in the main flow direction.

[0016] The damping device preferably comprises an outer tube and an inner tube arranged coaxially to and within the outer tube, which is also referred to, for example, as a damper tube. The inner tube preferably has a smaller diameter than the outer tube and is arranged radially spaced from it, so that a compensating chamber filled with hydraulic fluid is formed between the inner and outer tubes. The outer tube and the inner tube are preferably attached at their lower ends to a base piece that seals the hydraulic fluid-filled inner and outer tubes in a fluid-tight manner. For example, a bottom valve or a fluid passage is arranged in the base piece, which fluidly connects the compensating chamber to the interior of the inner tube, in particular to the piston rod-side working chamber. In particular, the base piece does not have a valve.At the upper end of the outer tube, the damping device preferably has a sealing package that is attached to the outer tube and the inner tube and seals the interior of the outer tube and the inner tube in a fluid-tight manner.

[0017] A piston and a piston rod attached to it are arranged to be axially movable within the inner tube and coaxially to it. The piston preferably rests fluid-tight against the inner wall of the inner tube with its outer diameter and is slidably mounted along the inner wall of the inner tube in the axial direction, the inner tube preferably forming a guide for the piston. The piston rod extends, in particular, from the piston towards the closure assembly and centrally through it, the closure assembly having, for example, a central bore. Preferably, the piston rod is slidably mounted through the closure assembly in a fluid-tight manner in the axial direction. The piston preferably divides the interior of the inner tube into a first working chamber furthest from the piston rod and a second working chamber closer to the piston rod. The piston optionally includes a valve assembly.

[0018] The compression stage valve is preferably arranged and designed such that it dampens the movement of the piston in the compression stage when the piston moves towards the bottom valve. The rebound stage valve is preferably arranged and designed such that it dampens the movement of the piston in the rebound stage when the piston moves towards the sealing assembly. The compression stage valve and the rebound stage valve are preferably identical and arranged separately from each other outside the outer tube. The compression stage valve is described below by way of example, although the same applies to the rebound stage valve. The compression stage valve is preferably designed such that hydraulic fluid can flow through it in both directions. By way of example, the compression stage valve has a valve body with a plurality of fluid channels, in particular two fluid channels.The fluid channels are each covered in a fluid-tight manner by a spring washer assembly, wherein the spring washer assemblies are each pre-tensioned in the closing direction by a spring element, in particular a coil spring. The pre-tension of at least one of the spring washer assemblies is preferably adjustable by means of an adjusting device. Preferably, the adjusting device is connected to a contact area for the spring element such that, when the adjusting device is rotated in the axial direction, the contact area moves along the central longitudinal axis and preferably compresses or releases the spring element.

[0019] According to a first embodiment, the second spring washer assembly has a plurality of fluid passages. For example, the number of fluid passages in the second spring washer assembly corresponds to the number of internal fluid channels in the valve body. The total cross-sectional area of ​​the fluid channels can be varied by adjusting the number of fluid passages in the second spring washer assembly, thus adapting the effect of pre-throttling the hydraulic flow to the desired damping.

[0020] According to a further embodiment, the fluid passages are arranged in an annular configuration relative to each other. Preferably, the centers of all fluid passages are located on an annular ring arranged concentrically to the second spring washer assembly. Preferably, the valve body has an annular recess on its end face facing the second spring washer assembly, which is concentric to the annular ring of fluid passages and into which the inner fluid channels open.

[0021] According to a further embodiment, the cross-sectional area of ​​all fluid passages is smaller than the cross-sectional area of ​​all internal fluid channels. According to a further embodiment, the first spring washer assembly is designed and arranged such that, when fluid flows through the valve body in a first flow direction, it forms a maximum opening cross-section between the first spring washer assembly and the valve body, and the cross-sectional area of ​​all fluid passages of the second spring washer assembly is smaller than this maximum opening cross-section. Such a smaller cross-sectional area of ​​the fluid passages ensures that the second spring washer assembly functions as a pre-throttle when fluid flows through the compression stage valve or the rebound stage valve in the respective main flow direction.Particularly in the case of high flow velocities, the characteristic is preferably generated at the fluid passages of the second spring washer assembly. This also ensures that the damping increases progressively with a further increase in flow velocity.

[0022] According to a further embodiment, all fluid passages are identical. According to a further embodiment, each fluid passage has a circular, oval, oblong, or slotted cross-section. According to a further embodiment, the fluid passages are evenly spaced from one another. This ensures a uniform flow of hydraulic fluid around the circumference of the valve body to the first spring washer assembly, causing it to lift evenly from the valve body.

[0023] According to another embodiment, the fluid passages are spaced unevenly apart. Optionally, at least two fluid passages have different cross-sectional geometries and / or cross-sectional areas. This ensures an uneven flow onto the first spring washer assembly, allowing the point of separation from the valve body to be adjusted. This can, for example, be used to minimize noise.

[0024] According to a further embodiment, the first spring washer assembly comprises a bypass washer with a bypass opening. A spacer washer is preferably arranged between the valve body and the first spring washer assembly, bearing against an end face of the valve body and against a spring washer of the spring washer assembly. Preferably, the first spring washer assembly comprises a bypass washer that forms the end of the first spring washer assembly facing the valve body. In particular, a plurality of radially inwardly extending recesses, especially bypass openings, are arranged in the bypass washer, forming a fluid passage. The recesses preferably extend radially inward from the outer circumference of the bypass washer and are preferably spaced evenly apart from one another. The bypass washer preferably rests directly against the spacer washer.The spacer disk preferably has an outer diameter that is smaller than that of the bypass disk and, in particular, smaller than the diameter of the annular ring on which the inner fluid channels are arranged. A bypass flow preferably also flows through the recesses in the bypass disk from the valve inlet to the valve outlet, even when the valve is closed.

[0025] According to a further embodiment, a compensating valve for amplitude-dependent damping of the piston movement is arranged hydraulically in parallel to the valve assembly. Preferably, the compensating valve is arranged hydraulically in parallel to the piston. The compensating valve is preferably fluidically connected to the working chamber furthest from the piston rod and the working chamber closer to the piston rod. The parallel arrangement of the compensating valve enables optimal damping of low-amplitude oscillations exclusively via the compensating valve, while larger amplitudes are damped via the parallel valves of the valve assembly.

[0026] In particular, the balancing valve has a buffer chamber formed within a buffer tube and a separating piston arranged therein, which fluidically divides the buffer chamber into a first sub-chamber and a second sub-chamber. Preferably, the buffer tube is arranged coaxially with the balancing valve housing. The separating piston is mounted to be axially movable within the buffer chamber and preferably rests fluid-tight against the inner wall of the buffer tube. The first sub-chamber is preferably directly connected to the working chamber furthest from the piston rod via a first through-hole in the buffer tube, while the second sub-chamber is preferably directly connected to the working chamber on the piston rod side via a second through-hole in the buffer tube. The separating piston is preferably arranged to be axially movable within the buffer chamber and is particularly designed as a floating piston, diaphragm, or fixed, axially movable disc.Within the buffer chamber, a separating disc is arranged, for example, between the separating piston and the first through-bore, and preferably has a plurality of flow passages. The separating disc serves, in particular, as a stop for the separating piston during axial movement towards the first through-bore, in order to prevent the first through-bore from closing abruptly.

[0027] Preferably, the separating piston is axially movable between a rebound stage end position, in which the first passage is fluid-tightly sealed by the separating piston, and a compression stage end position, in which the second passage is fluid-tightly sealed by the separating piston. In the compression stage end position, the separating piston preferably rests against the bottom, in particular the lower cylinder bottom surface, of the buffer chamber. Preferably, in the compression stage end position, the separating piston seals the second passage in a fluid-tight manner and preferably fluidly separates the piston rod-side working chamber from the second sub-chamber. In the rebound stage end position, the separating piston preferably rests against opposite cylinder bottom surfaces of the buffer chamber. For example, in the rebound stage end position, the separating piston rests fluid-tightly against the separating disc.Preferably, in the rebound end position, the separating piston seals the first passage hole fluid-tight and preferably fluidly separates the working chamber furthest from the piston rod from the first partial chamber in the rebound end position. For example, the separating piston indirectly seals the passage holes in the compression end position or the rebound end position by, for example, resting against a stop and preventing the fluid flow through the respective passage holes.

[0028] For piston rod movements with a small amplitude, preferably corresponding at most to the stroke of the separating piston between the rebound and compression end positions, the piston rod experiences very little or no damping. Piston rod movements with a larger amplitude are preferably damped by means of the compression or rebound valve.

[0029] Optionally, the damping device has a gas tank which is hydraulically arranged parallel to the compensating valve and directly connected to the valve assembly, in particular to the rebound valve and / or the compression valve.

[0030] In particular, the compression and rebound valves are designed such that the damping, especially the damping force generated by the compression or rebound valve, is manually adjustable. The preload of at least one of the spring washer assemblies is preferably adjustable by means of an adjusting device. The adjusting device of the rebound and / or compression valve preferably comprises an adjusting rod. The adjusting rod extends, in particular, from the compression or rebound valve housing and is optionally arranged coaxially with the compression or rebound valve housing.Preferably, the adjusting rod is rotatably mounted about its central longitudinal axis and is connected, in particular, to a contact area for the spring element such that, when the adjusting rod is rotated axially, the contact area moves along the central longitudinal axis, thus preferably compressing or releasing the spring element. The adjusting rod is preferably designed and arranged such that it can be manually actuated, and in particular rotatably, from outside the valve housing.

[0031] The invention optionally also includes a rear shock absorber for a bicycle with at least one damping device as described above. The terms "top," "bottom," "front," and "rear" used in this application refer to the usual operating position of a bicycle with a damping device. The rear shock absorber is preferably connected to the bicycle frame and the rear wheel, so that the movement of the rear wheel is dampened by means of the rear shock absorber.

[0032] According to one embodiment, the rear shock absorber comprises a spring and a spring plate attached to the outer tube, against which the spring is supported. In particular, the rear shock absorber includes a spring housing, preferably tubular, which preferably completely surrounds the spring. The outer tube of the damping device is preferably arranged coaxially to the spring housing and has a smaller diameter than the latter. The outer tube is preferably arranged radially spaced from the spring housing, with an annular space formed between the outer tube and the spring housing, in which the spring is at least partially arranged.

[0033] The invention optionally also includes a bicycle comprising a rear shock absorber and a damping device as described above. The rear shock absorber is preferably connected to the bicycle frame and the rear wheel of the bicycle and has a damping device such that the movement of the rear wheel is dampened by means of the rear shock absorber.

[0034] Description of the drawings

[0035] The invention is explained in more detail below with reference to several exemplary embodiments and the accompanying figures.

[0036] Fig. 1 shows a schematic representation of a bicycle with a suspension fork and a rear shock absorber in a side view according to an exemplary embodiment.

[0037] Fig. 2 shows a schematic representation of a rear wheel damper in a perspective view according to an exemplary embodiment.

[0038] Fig. 3 shows a schematic representation of a rear wheel damper in a

[0039] Longitudinal section view according to an exemplary embodiment.

[0040] Fig. 4 shows a schematic representation of the pressure stage valve / retraction stage valve in a longitudinal sectional view according to an exemplary embodiment.

[0041] Fig. 5 shows a schematic exploded view of the compression / retraction valve according to one embodiment. Fig. 6 shows a schematic longitudinal sectional view of a section of the compression / retraction valve according to one embodiment.

[0042] Fig. 7 shows two schematic representations of a spring washer in a top view according to two further embodiments.

[0043] Fig. 1 shows a schematic representation of a bicycle 10 with a suspension fork 12 and a rear shock absorber 14. Fig. 1 shows a bicycle 10 in an operating position, where the terms used below, such as "top", "bottom", "front", and "rear", refer to the operating position of the bicycle 10 shown. The suspension fork 12 is preferably connected to the bicycle frame and front wheel of the bicycle 10 and preferably has a damping device so that the movement of the front wheel is dampened by means of the suspension fork 12. The rear shock absorber 14 is preferably connected to the bicycle frame and the rear wheel and also has, for example, a damping device 28 so that the movement of the rear wheel is dampened by means of the rear shock absorber 14.

[0044] Figures 2 and 3 each show a rear shock absorber 14, with Figure 2 showing a perspective view and Figure 3 a longitudinal section view of the rear shock absorber 14. The rear shock absorber 14 has two mounting elements, in particular mounting holes, which are arranged at opposite ends of the rear shock absorber 14 and serve to attach the rear shock absorber 14 to the bicycle frame. These are also referred to, for example, as shock absorber eyes. Depending on the design of the bicycle frame, the installation position of the rear shock absorber 14 can vary, so that the orientation of the rear shock absorber 14 shown in Figure 2 does not always correspond to the installation position. The terms "top" and "bottom" therefore refer to the orientation of the rear shock absorber 14 shown in Figure 2. The upper mounting element is referred to, for example, as the shock absorber head, and the lower mounting element is referred to, for example, as the shock absorber foot 18.The rear wheel damper 14 has a damping device 28 with a valve device 50, which are designed for hydraulic damping of the piston rod movement.

[0045] The rear wheel damper 14 includes, for example, a spring 38, which can be, for instance, an air spring as shown in Fig. 2 or a coil spring as shown in Fig. 3. The spring 38 is optionally completely enclosed by a spring housing 22, which is particularly tubular. The spring housing 22 is particularly rigidly connected to the upper mounting element, with the spring 38 preferably bearing against it at one end. At the opposite end, the spring 38 is supported, for example, by a spring plate 24, which is attached to the outer tube 30 of the damping device 28.

[0046] The damping device 28 comprises, for example, an outer tube 30, which is arranged coaxially to the spring housing 22 and has a smaller diameter than the latter. The outer tube 30 is preferably arranged radially spaced from the spring housing 22, with an annular space being formed between the outer tube 30 and the spring housing 22, in which the spring 38 is at least partially arranged. Coaxial to and within the outer tube 30, an inner tube 32 is arranged, which is also referred to, for example, as a damper tube 32. The inner tube 32 has a smaller diameter than the outer tube 30 and is arranged radially spaced from it, so that a compensating chamber 34 filled with a hydraulic fluid is formed between the inner tube 32 and the outer tube 30.The outer tube 30 and the inner tube 32 are preferably attached at their lower ends to a base piece 36, which seals the inner tube 32 and outer tube 30, filled with hydraulic fluid, against the gas space 38 in a fluid-tight manner. For example, a bottom valve or a fluid passage is arranged in the base piece 36, which fluidically connects the compensation chamber 34 with the interior of the inner tube 32, in particular the piston rod-side working chamber 46. In particular, the base piece 36 does not have a valve.

[0047] A piston 40 and a piston rod 42 attached to it are arranged to be axially movable within and coaxial to the inner tube 32. The piston 40 preferably bears fluid-tightly against the inner wall of the inner tube 32 with its outer diameter and is slidably mounted along the inner wall of the inner tube 32 in the axial direction, the inner tube 32 preferably forming a guide for the piston 40.

[0048] The piston 40 preferably divides the interior of the inner tube 32 into a first working chamber 44, located away from the piston rod, and a second working chamber 46, located on the side of the piston rod, using fluid technology.

[0049] At the upper end of the outer tube 30, the damping device 28 has a sealing assembly 48, which is attached to the outer tube 30 and the inner tube 32 and seals the interior of the outer tube 30 and the inner tube 32 fluid-tight. The piston rod 42 extends from the piston 40 towards the sealing assembly 48 and centrally through it. Preferably, the piston rod 42 is able to slide fluid-tightly in the axial direction through the sealing assembly 48. The piston rod 42 preferably extends in the axial direction to the upper end of the spring housing 22 and is particularly fixedly connected to it, so that the spring housing 22 and the piston rod 42 are preferably not movable relative to each other.

[0050] The valve assembly 50 is, by way of example, arranged entirely outside the outer tube 30 and the spring housing 22. The valve assembly 50 comprises, by way of example, a first valve 52, also referred to as the compression stage valve 52, and a second valve 54, also referred to as the rebound stage valve 54. The compression stage valve 52 is preferably arranged and configured such that it dampens the movement of the piston 40 in the compression stage when the piston moves in the compression direction D. The rebound stage valve 54 is preferably arranged and configured such that it dampens the movement of the piston 40 in the rebound stage when the piston moves in the extension direction Z.

[0051] The damping device 28 further comprises a compensating valve 26, which is preferably arranged hydraulically parallel to the piston 40 and the valve assembly 50. The compensating valve 26 is preferably an amplitude-selective valve, which is provided in particular in addition to the rebound valve and the compression valve. The compensating valve 26 is preferably designed and arranged such that it dampens the piston movement within the inner tube 32 in an amplitude-dependent manner. The damping device 28 also comprises a gas tank 20, which is preferably hydraulically connected directly to the valve assembly 50 and hydraulically arranged parallel to the compensating valve 26.

[0052] The damping device 28 preferably comprises a valve housing 16. Within the valve housing 16, the valve assembly 50, the compensating valve 26, and the gas tank 20 are at least partially arranged. Preferably, the valve assembly 50 and the compensating valve 26 are completely arranged within the valve housing 16. The valve housing 16 is preferably manufactured by machining, sand casting, sintering, and / or 3D printing. The valve housing 16 preferably comprises a compression valve housing 56 for receiving the compression valve 52 and a separate rebound valve housing 58 for receiving the rebound valve 54. Additionally, the valve housing comprises a compensating valve housing 60 for receiving the compensating valve 26 and a gas tank housing 62 for receiving the gas tank 20.

[0053] Figures 4 to 6 each show an embodiment of a compression stage valve 52 or a rebound stage valve 54, wherein the compression stage valve 52 and the rebound stage valve 54 are preferably identical. For the purposes of this description, reference is made to the compression stage valve 52, and the same applies to the rebound stage valve 54. The compression stage valve 52 is preferably designed to allow hydraulic fluid to flow through it in both directions. By way of example, the compression stage valve 52 has a valve body 72 with a plurality of fluid channels 64, 66, in particular two or more fluid channels 64, 66. The fluid channels 64, 66 preferably extend from one end face of the valve body 72 to the opposite end face and are arranged separately from each other, preferably fluidically separated from each other.By way of example, the valve body 72 has a plurality of outer fluid channels 64 and a plurality of inner fluid channels 66, wherein the outer fluid channels 64 are arranged radially outward from the inner fluid channels 66. The outer fluid channels 64 are arranged annularly relative to each other on an outer circular ring with an outer ring diameter of , wherein the inner fluid channels 66 are arranged annularly relative to each other on an inner circular ring with an inner ring diameter of within the valve body 72. The outer and inner circular rings are preferably arranged coaxially with the valve body 72. The fluid channels 64, 66 preferably extend substantially or completely through the valve body 72 in the axial direction. By way of example, the outer fluid channels 64 and the inner fluid channels 66 are each arranged at a uniform distance from each other.

[0054] The outer and / or inner fluid channels 64, 66 have, for example, a round, circular, oval, or oblong cross-sectional area. For example, the valve body 72 has ten outer fluid channels 64, each with an oval cross-sectional area, and six inner fluid channels, each with a circular cross-sectional area. Preferably, the outer fluid channels 64 are all identical. In particular, the inner fluid channels 66 are all identical.

[0055] The fluid channels 64, 66 are each covered in a fluid-tight manner by a spring washer assembly 74, 76. The spring washer assemblies 74, 76 are preferably attached to opposite end faces of the valve body 72. Preferably, the pressure stage valve 52 has a first spring washer assembly 74 which is designed and arranged such that it completely covers the inner fluid channels 66, in particular in a fluid-tight manner. Preferably, the first spring washer assembly 74 is arranged such that it determines the flow cross-section of the inner fluid channels 66 when flow occurs in a first flow direction, and in particular closes the inner fluid channels 66 at least partially or completely in a fluid-tight manner.In particular, the first spring washer assembly 74 rests against an end face of the valve body 72 such that, depending on the flow velocity, it closes the inner fluid channels 66 during flow in a first direction or at least partially or completely opens the flow cross-section. The first spring washer assembly 74 is preferably arranged such that it completely closes the inner fluid channels during flow in a second direction, which is opposite to the first. During flow in the second direction through the inner fluid channels 66, the first spring washer assembly 74 is preferably designed as a check valve, thus preventing flow in the second direction.The first flow direction is preferably the main flow direction; in the case of the pressure stage valve 52, this is in particular a piston movement in the compression direction D, and in the case of the rebound stage valve 54, this is in particular a piston movement in the tension direction Z. The first spring washer assembly 74 is preferably designed and arranged such that it does not cover the flow cross-section of the outer fluid channels 64, or only partially covers it. The first spring washer assembly 74 comprises, by way of example, a plurality of spring washers arranged parallel to one another and, in particular, abutting one another. By way of example, the first spring washer assembly 74 has four parallel spring washers, which are annular in shape and, in particular, all have the same diameter.An exemplary spacer washer 68 is arranged between the valve body 72 and the first spring washer assembly 74. This spacer washer bears against an end face of the valve body 74 and against a spring washer of the spring washer assembly 74. Preferably, the spring washers of the first spring washer assembly have an outer diameter that is larger than the inner annular diameter and therefore project radially beyond the inner fluid channels 66. Alternatively, the spring washers of the first spring washer assembly preferably have an outer diameter that is smaller than the outer annular diameter and does not cover the outer fluid channels 64 at all or only partially. Preferably, the first spring washer assembly 74 has a bypass washer 70 that forms the end of the first spring washer assembly 74 facing the valve body 72.The bypass disc 70 has a plurality of radially inwardly projecting recesses, in particular bypass openings, which form a fluid passage. The recesses preferably extend radially inward from the outer circumference of the bypass disc 70 and are preferably spaced evenly apart from one another. In particular, the recesses are aligned with the inner fluid channels 66, so that a fluid flow through the recesses is enabled. The bypass disc 70 preferably rests directly against the spacer disc 68.

[0056] The pressure stage valve 52 is in a closed position when the first spring washer assembly 74 rests against the valve body 72, thus at least partially closing the inner fluid channels 66. Even in the closed valve position, a bypass flow from the valve inlet to the valve outlet is maintained via the recesses in the bypass disc 70. Preferably, the pressure stage valve 52 has a second spring washer assembly 76, which is designed and arranged such that it completely covers the outer fluid channels 64, in particular in a fluid-tight manner. Preferably, the second spring washer assembly 76 is arranged such that it determines the flow cross-section of the outer fluid channels 64 when flow occurs in a second direction, opposite to the first flow direction, and in particular closes the outer fluid channels 64 at least partially or completely in a fluid-tight manner.In particular, the second spring washer assembly 76 rests against an end face of the valve body 72 such that, depending on the flow velocity, it closes the outer fluid channels 64 when flow occurs in the second flow direction or at least partially or completely opens the flow cross-section. The second spring washer assembly 76 is preferably arranged such that it completely closes the outer fluid channels 64 when flow occurs in the first flow direction. When flow occurs in the first flow direction through the outer fluid channels 64, the second spring washer assembly 76 is preferably designed as a check valve, thus preventing flow in the first flow direction.

[0057] The second spring washer assembly 76 is preferably designed and arranged such that it does not cover, or only partially covers, the flow cross-section of the inner fluid channels 66. The second spring washer assembly 76 comprises, by way of example, exactly one spring washer, which is annular in shape. Preferably, the second spring washer assembly 76 has an outer diameter that is larger than the outer annular diameter and therefore projects radially beyond the outer fluid channels 64. Preferably, the second spring washer assembly 76 has an outer diameter that is less than or equal to the outer diameter of the valve body 72.

[0058] Preferably, the second spring washer assembly 76 has a plurality of fluid passages 88. The fluid passages 88 are preferably arranged in alignment with the inner fluid channels 66, so that hydraulic fluid can flow through the fluid passages 88 and the inner fluid channels 66, preferably in both flow directions. The fluid passages 88 preferably have a cross-sectional area that is smaller than the cross-sectional area of ​​the inner fluid channels 66.

[0059] The fluid passages 88 are arranged in an annular arrangement relative to each other and have, in particular, a circular, oval, oblong or slot-shaped cross-sectional area.

[0060] The spring washer assemblies 74, 76 are each pre-tensioned in the closing direction by a spring element 78, 80, in particular a coil spring. On the side of the second spring washer assembly 76 facing away from the valve body 72, a pre-tensioning washer 90, which is also annular in shape, is located, for example. The spring element 78 rests against the pre-tensioning washer 90 in such a way that it exerts a force on the pre-tensioning washer 90, and thus also on the second spring washer assembly 76, in the closing direction of the pressure-stage valve 52.

[0061] The preload of at least one of the spring washer assemblies 74, 76 is preferably adjustable by means of an adjusting device 82. The adjusting device 82 comprises, in particular, an adjusting rod extending from the pressure stage valve housing 56 and extending coaxially to the pressure stage valve housing 56. Preferably, the adjusting rod 84 is rotatably mounted about its central longitudinal axis 66, 68 and is connected, in particular, to a contact area 86 for the contact of the spring element 78, 80 such that, when the adjusting rod 84 is rotated in the axial direction, the contact area 86 moves along the central longitudinal axis 66, 68 and thus preferably compresses or relaxes the spring element 78, 80. Preferably, the pressure stage valve 52 has two contact areas 86 for the respective contact of a spring element 78, 80, each of which is connected to the adjusting rod 84 in the manner described.

[0062] Fig. 7 shows the second spring washer assembly 76 in two different embodiments. The fluid passages 88 are arranged at uniform intervals. The left embodiment, by way of example, has five elongated fluid passages 88 extending radially. In the right embodiment, the fluid passages 88 are spaced unevenly and arranged in an annular pattern. The six fluid passages 88 have a circular cross-sectional area.

[0063] When fluid flows through the valve 52, 54 in the first direction, the second spring washer assembly 76 acts as a pre-throttle, so that, especially at high flow velocities, the fluid flow is throttled before entering the inner flow channels 66. Additionally, the second spring washer assembly 76 functions as a check valve with respect to the outer flow channels 64. When fluid flows through the valve 52, 54 in the second direction, the second spring washer assembly 76 creates a characteristic on the outer fluid channels 64.

[0064] Reference symbol list

[0065] 10 bicycles

[0066] 12 Suspension fork

[0067] 14 rear wheel dampers

[0068] 16 Valve housings

[0069] 18 damper foot

[0070] 20 gas tank

[0071] 22 spring housings

[0072] 24 spring plates

[0073] 26 Compensating valve

[0074] 28 Damping device

[0075] 30 Outer pipe

[0076] 32 Inner tube / Damper tube

[0077] 34 Compensation area

[0078] 36 bottom piece

[0079] 38 spring

[0080] 40 pistons

[0081] 42 Piston rod

[0082] 44 working space far from piston rod

[0083] 46 piston rod side working space

[0084] 48 sealing packs

[0085] 50 Valve assembly

[0086] 52 first valve / pressure stage valve

[0087] 54 second valve / rebound valve

[0088] 56 pressure stage valve housings

[0089] 58 Rebound valve housings

[0090] 60 balancing valve housings

[0091] 62 gas tank housings

[0092] 64 external fluid channels

[0093] 66 internal fluid channels

[0094] 68 spacer

[0095] 70 Bypass disc

[0096] 72 valve bodies

[0097] 74 first spring washer package

[0098] 76 second spring washer package /

[0099] 78 Spring element

[0100] 80 spring element

[0101] 82 Adjustment device

[0102] 84 Adjustment rod

[0103] 86 Investment area

[0104] 88 Fluid passage

[0105] 90 Preload disc

Claims

23 / 26 Patent claims 1. Damping device (28) for a bicycle (10) comprising an outer tube (30) and an inner tube (32) arranged coaxially thereto, wherein a compensation chamber (34) for receiving hydraulic fluid is formed between the outer tube (30) and the inner tube (32), and a piston (40) connected to a piston rod (42) which is arranged to be reciprocally movable within the inner tube (32), wherein the interior of the inner tube (32) is divided by the piston (40) into a working chamber (44) remote from the piston rod and a working chamber (46) on the side of the piston rod, and wherein the damping device (28) comprises a valve assembly (50) mounted outside the outer tube (30), wherein the valve assembly (28) comprises a valve body (72) with an inner fluid channel (66) and an outer fluid channel (64) arranged radially outward from the inner fluid channel (66), and a first and a second spring washer assembly. (74, 76) shows,which are attached to opposite sides of the valve body (72), characterized in that the first spring washer assembly (74) at least partially radially covers the inner fluid channel (66) and wherein the second spring washer assembly (76) at least partially radially covers the inner and outer fluid channels (64, 66) and has a fluid passage (88) which is arranged in fluid communication with the inner fluid channel (66).

2. Damping device (28) according to claim 1, wherein the second spring washer assembly (76) has a plurality of fluid passages (88).

3. Damping device (28) according to claim 2, wherein the fluid passages (88) are arranged in an annular arrangement relative to each other.

4. Damping device (28) according to one of the preceding claims, wherein the cross-sectional area of ​​all fluid passages (88) is smaller than the cross-sectional area of ​​all internal fluid channels (66).

5. Damping device (28) according to one of the preceding claims, wherein the first spring washer assembly (74) is designed and arranged such that, when fluid flows through the valve body (72) in a first flow direction, it forms a maximum opening cross-section between the first spring washer assembly (74) and the valve body (72), and wherein the cross-sectional area of ​​all fluid passages (88) of the second spring washer assembly (76) is less than the maximum opening cross-section.

6. Damping device (28) according to one of the preceding claims, wherein the fluid passages (88) are all identically designed.

7. Damping device (28) according to one of the preceding claims, wherein the fluid passages (88) each have a circular, oval, oblong or slotted cross-section.

8. Damping device (28) according to one of the preceding claims, wherein the fluid passages (88) are spaced evenly apart from each other.

9. Damping device (28) according to one of claims 1 to 7, wherein the fluid passages (88) are spaced unevenly apart from each other.

10. Damping device (28) according to one of the preceding claims, wherein the first spring washer assembly (74) has a bypass washer (70) with a bypass opening.

11. Damping device (28) according to one of the preceding claims, wherein a compensating valve (26) is arranged hydraulically parallel to the valve device (50) for amplitude-dependent damping of the piston movement.

12. Rear wheel damper (14) for a bicycle (10) comprising at least one damping device (28) according to one of the preceding claims.

13. Rear wheel damper (14) according to claim 12, wherein the rear wheel damper (14) has a spring (38) and a spring plate (24) attached to the outer tube (30) against which the spring (38) is supported.

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