Two-wheel vehicle damping device having control unit depending on frequency, motor cycle having front fork, rear wheel damper and two-wheel vehicle damping device

Abstract

To provide a two-wheel vehicle damping device having improved damping characteristics.SOLUTION: A two-wheel vehicle damping device 1 has a cylinder 2 filled with a damping fluid, a piston rod 3 guided by the cylinder 2, and a piston unit 4 that is fixed to the piston rod 3 and divides the cylinder 2 into a first operation space 10 and a second operation space 11. The piston unit 4 has a piston valve 12, and a main volume flow 103 flows when the piston rod 3 moves in a tension direction 101. The piston unit 4 has a piston valve 13, and the main volume flow 103 flows when the piston rod 3 moves in a compression direction 102. A control unit 5 fixed to the piston rod 3 is provided, and the control unit 5 is configured to influence the main volume flow 103 based on a control volume flow 104 generated by the piston valves 12, 13 depending on an excitation frequency.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a motorcycle damping device for a motorized motorcycle having the features of the preamble of claim 1. The invention also relates to a front fork and a rear wheel damper having the motorcycle damping device, and to a motorcycle having a front fork and / or a rear wheel damper. [Background technology]

[0002] Vibration damping (damping) for two-wheeled vehicles, particularly motorcycles, is known, which is used to damp vibrations during vehicle operation. For this purpose, two-wheeled vehicles are usually equipped with a front fork and a rear wheel damper with integrated vibration dampers for damping and cushioning the front and rear wheels. In this case, a compromise between riding safety and riding comfort must always be found. Therefore, a hard-set vibration damper has an optimal high damping force characteristic line for high riding safety. If high comfort requirements are to be met, the vibration damper must be set as soft as possible. With conventional vibration dampers with non-electronic damping valve devices that can be adjusted using an actuator, finding this compromise can be very difficult.

[0003] Patent Document 1 discloses a hydraulic shock absorber including first and second front forks, each of which includes an outer tube, an inner tube displaceably fitted to the outer tube, a cylinder disposed in the outer tube and / or inner tube, a piston displaceably fitted to the cylinder, a piston rod having one end fixed to the inner tube or the outer tube and the other end attached to the piston, first and second oil chambers disposed on the opposite side of the piston, a damping adjustment section disposed on a throughflow track connecting the first and second oil chambers to adjust the throughflow speed of oil flowing through the throughflow track, an actuator for adjusting the damping force of the damping adjustment section, and an adjustment mechanism for allowing oil to flow through the throughflow track only in one direction, wherein the piston of the first front fork has a damping valve for allowing oil to flow in the same direction as the flow through the adjustment mechanism, and the piston of the second front fork has a damping valve for allowing oil to flow in the opposite direction to the direction of oil flowing through the adjustment mechanism of the first front fork. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] German Patent Application Publication No. 602007014143 Summary of the Invention [Problem to be solved by the invention]

[0005] The object of the present invention is to provide a motorcycle damping device of the type mentioned at the outset, which has improved damping properties (damping behavior). [Means for solving the problem]

[0006] The problem is solved by a motorcycle damping device having the features of claim 1, a front fork having the features of claim 8, a rear wheel damper having the features of claim 12 and a motorcycle having the features of claim 15. Advantageous embodiments are evident from the dependent claims, the drawings and / or the present description.

[0007] The subject matter of the present invention is designed for and / or suitable for motorized two-wheeled vehicles, in particular motorcycles. In particular, a motorcycle damping device can be understood as a vibration damper that is designed in particular for two wheels, preferably for the front and / or rear wheels. The vibration damper is preferably designed as a hydraulic damper.

[0008] The motorcycle damping device includes at least one or exactly one cylinder at least partially or completely filled with a damping fluid. The motorcycle damping device further includes a piston rod, which is guided in the cylinder so as to be axially movable relative to the longitudinal axis. In particular, the piston rod is guided at least partially in the cylinder coaxially relative to the longitudinal axis. Preferably, the piston rod is axially movable in the cylinder in a tensile direction and a compressive direction relative to the longitudinal axis. Preferably, the piston rod is pulled out of the damper tube in a tensile direction under tensile load, and pressed into the damper tube in a compressive direction under compressive load. For example, the damper device includes a piston rod guide, through which the cylinder is closed at an end and the piston rod is guided.

[0009] The motorcycle damping device comprises a piston unit fixed at its end to the piston rod and dividing the cylinder into a first working space on or facing the piston rod and a second working space away from or opposite the piston rod, in particular, the piston unit being kinematically coupled to the piston rod so that the piston unit moves together with the movement of the piston rod in the tension and compression directions.

[0010] The piston unit comprises a piston valve, also called a tension stage valve, acting in the tension direction of the piston rod, through which the main volume flow flows when the piston rod moves in the tension direction, i.e., during withdrawal. The piston unit further comprises a piston valve, also called a compression stage valve, acting in the compression direction of the piston rod, through which the main volume flow flows when the piston rod moves in the compression direction, i.e., during compression. In particular, the tension stage valve is used to generate a damping force when the motorcycle damping device is tensioned, and the compression stage valve is used to generate a damping force when the motorcycle damping device is compressioned. In particular, the tension stage valve and the compression stage valve are configured as check valves that are only effective in one flow direction.

[0011] Preferably, the piston unit comprises a working piston, which is radially adjacent to the inner circumference of the cylinder. The working piston preferably comprises a group of tension-stage passages through which the main volumetric flow flows during tension movement of the piston rod and a group of compression-stage passages through which the main volumetric flow flows during compression movement of the piston rod. Particularly preferably, the tension-stage valve comprises at least one tension-stage valve disc, which covers the tension-stage passages in order to influence the flow through them during tension movement. In particular, the at least one tension-stage valve disc covers the tension-stage passages so that the tension-stage passages are open during tension movement and closed during compression movement. Particularly preferably, the compression-stage valve comprises at least one compression-stage valve disc, which covers the compression-stage passages in order to influence the flow through them during compression movement. In particular, the at least one compression-stage valve disc covers the compression-stage passages so that the compression-stage passages are open during compression movement and closed during tension movement. In particular, at least one tension stage valve disc and / or compression stage valve disc is formed by a spring disc, optionally comprising a plurality of valve discs, preferably a plurality of spring discs, grouped together in a common disc package.

[0012] The present invention proposes that the motorcycle damping device comprises a control unit fixed to the piston rod, which is configured to influence the main volume flow through one of the piston valves based on a control volume flow occurring as a function of the excitation frequency. Simply put, the control unit is used to influence the speed-dependent and / or frequency-dependent damping force of the tension stage valve or the compression stage valve. For this purpose, the control unit is operatively connected to the piston valves. Preferably, the control unit acts on each valve disc of the corresponding piston valve. Preferably, the control volume flow flows to the control unit parallel to the main volume flow, bypassing the piston valve, and the control unit acts on the associated piston valve based on the control volume flow. In other words, the control volume flow flows to the control unit via a bypass.

[0013] The advantage of the present invention is that a motorcycle damping device with a frequency-dependent damping force characteristic line is proposed, which is simple to configure and inexpensive due to the integration of a control unit. The frequency-dependent influence of the main volume flow allows for different damping forces at the same configuration and different excitation frequencies. The proposed motorcycle damping device significantly improves the riding characteristics of motorcycles.

[0014] In one specific implementation, when the excitation frequency is reduced, the control unit increases the spring force acting on the piston valve, thereby increasing the flow resistance through the corresponding piston valve and therefore the damping force. In particular, at low excitation frequencies, a larger control volume flow occurs than at high excitation frequencies. This allows for slow pressure changes to be transmitted to the control unit. In particular, a low excitation frequency can be understood as an excitation frequency less than 5 Hz, preferably less than 1 Hz. In particular, a high excitation frequency can be understood as an excitation frequency greater than 5 Hz, preferably greater than 10 Hz. This makes it easy to influence the dependence of the damping force characteristic curve on the excitation frequency.

[0015] In one structural configuration, the control unit comprises a control pot fixed to the piston rod and a control piston axially displaceable in the control pot and axially defining a control space contained in the control pot. The control piston is supported axially in relation to the longitudinal axis on an assigned piston valve and is axially displaced toward the assigned piston valve when fluid pressure increases in the control space, thereby increasing the damping force of the piston valve. The control space is preferably filled with damping fluid via a control volume flow depending on the excitation frequency, whereby the control piston is displaced and at least indirectly increases or decreases the pressure on the valve disc of the associated piston valve. The control piston thus acts on the valve disc in its closing direction. In particular, the control piston is arranged in the control pot so as to be limitedly displaceable in order to define soft and hard damping force characteristic lines between its first axial end and its second axial end. Particularly preferably, the control piston, the control pot, or the piston rod is provided with an outlet orifice that defines the discharge of damping fluid from the control space. Therefore, a particularly simple and convenient control unit is proposed.

[0016] In one development, the control unit comprises a spring device for axially loading the piston valve and the control piston with a predetermined spring force, such that the control piston is supported axially relative to the longitudinal axis on the assigned piston valve via the spring device. In particular, the spring device is biased upon displacement of the control piston toward the valve disc, thereby increasing the spring force load on the piston valve, particularly the valve disc, by the spring device. Preferably, the piston rod passes through the piston unit and the control unit centrally, so that the piston unit and the control unit are centered on the piston rod. The spring device can comprise a plurality of Belleville spring-like spring elements, which are stacked coaxially relative to the longitudinal axis and are supported at least indirectly on the control piston or piston valve at their outer diameters. Particularly preferably, the spring device and the control piston are centered and / or linearly guided relative to each other via a guide bush that can be fastened to the piston rod.

[0017] In one specific embodiment, the control unit is assigned to a piston valve acting in the tension direction, and a control passage is formed in and / or within the piston rod, connecting the first working space with the control space such that a control volume flow flows from the first working space through the control passage to the control space when the piston rod moves in the tension direction. In particular, the control piston is preferably supported on the tension stage valve, in particular on at least one tension stage valve disc, via a spring device. The control passage can be formed by one or more radial and / or axial holes in the piston rod. However, instead, the control passage can also be formed by an axially extending recess, indentation, groove, or the like. The control unit can optionally have a connecting passage connecting the first working space with the second working space, which is arranged so that the connecting passage is at least partially closed by the control piston when the control piston is axially displaced toward the tension stage valve and is re-opened when the control piston is axially displaced in the opposite direction. This allows the throughflow of the damping fluid into the control space to be further controlled and thus influences the hard damping force characteristic line more clearly.

[0018] In an alternative configuration, the control unit is assigned to a piston valve acting in the compression direction, and a control passage is formed in and / or within the piston rod, connecting the second working space with the control space such that a control volume flow flows from the second working space through the control passage into the control space when the piston rod moves in the compression direction. In particular, the control piston is preferably supported on the compression stage valve, in particular on at least one compression stage valve disc, via a spring device. The control passage can be formed by one or more radial and / or axial holes in the piston rod. However, instead, the control passage can also be formed by an axially extending recess, indentation, groove, or the like. The control unit can optionally have a connecting passage connecting the second working space with the first working space, which is arranged so that the connecting passage is at least partially closed by the control piston when the control piston is axially displaced toward the compression stage valve and is re-opened when the control piston is axially displaced in the opposite direction. This allows the throughflow of the damping fluid into the control space to be further controlled and thus influences the hard damping force characteristic line more clearly.

[0019] In one development, a through-flow passage is formed in the piston rod, connecting the first and second working spaces in flow communication. An adjustable needle valve is arranged in the through-flow passage to adjust the through-flow resistance of the bypass volumetric flow through the through-flow passage. In other words, the through-flow speed of the damping fluid flowing through the return passage can be adjusted via the needle valve. The damping force can thus be adjusted via the needle valve based on the through-flow resistance. The bypass volumetric flow preferably bypasses the piston unit and the control unit. The needle valve preferably has an adjustment needle that is axially displaceable relative to the through-flow passage to at least partially close the through-flow passage. For example, the adjustment needle can be adjusted axially relative to the through-flow passage via an external adjustment mechanism, for example, in the form of a locking position, also known as a click. The bypass volumetric flow can be generated or flow through the needle valve during a tension or compression movement of the piston rod. In particular, the bypass volumetric flow flows from the second working space to the first working space via the needle valve during a compression load. Correspondingly, a bypass volume flow flows from the first working space through the needle valve to the second working space under tensile load.

[0020] Another object of the present invention relates to a front fork with a motorcycle damping device, as described above. In particular, the front fork is configured as a telescopic suspension fork. The front fork is used to guide the front wheel, and the motorcycle damping device performs the role of damping when the motorcycle moves over unevenness in the road surface. The front fork optionally includes a spring device (suspension device) that performs the role of suspension when the motorcycle moves over unevenness in the road surface.

[0021] In one specific embodiment, the front fork has first and second fork legs (wishbones), and the motorcycle damping devices are arranged on the first and second fork legs. In principle, the first and second fork legs can be identical in structure. However, preferably, the motorcycle damping device of one fork leg is configured for a frequency-dependent effect of the damping force under tension load, and the motorcycle damping device of the other fork leg is configured for a frequency-dependent effect of the damping force under compression load.

[0022] In one structural configuration, a control unit is assigned to the piston valve or tension stage valve acting in the tension direction in the first fork leg so that the main volume flow is influenced frequency-dependently during tension loading, and a control unit is assigned to the piston valve or compression stage valve acting in the compression direction in the second fork leg so that the main volume flow is influenced frequency-dependently during compression loading. In particular, the control unit in the first fork leg is arranged in the second working space, and the control piston is supported axially on the tension stage valve, preferably via a spring device. During tension movement, the control volume flow in the first fork leg flows parallel to the main volume flow from the first working space to the control space via the control passage. In particular, the control unit in the second fork leg is arranged in the first working space, and the control piston is supported axially in the opposite direction on the compression stage valve, preferably via a spring device. During compression movement, the control volume flow in the second fork leg flows parallel to the main volume flow from the second working space to the control space via the control passage. Therefore, frequency-selective damping can be easily achieved during both tension and compression movements of the suspension fork.

[0023] In one development, the first and second fork legs each have an outer tube and an inner tube displaceably arranged on the outer tube, and the motorcycle damping devices of the first and second fork legs are arranged on the inner and outer tubes. In principle, the outer tubes of both fork legs can be connected to each other via a fork bridge, and the inner tubes each have an axle bracket that accommodates the axle of the front wheel. In particular, the outer tubes then form stanchion tubes, and the inner tubes form dip tubes. This arrangement is also called an inverted fork. In this case, the piston rods can each be connected to the outer tubes. Optionally, the spring device can then be arranged on the outer tube coaxially with the piston rod. However, instead of this, the inner tubes of both fork legs can be connected to each other via a fork bridge, and the outer tubes each have an axle bracket that accommodates the axle of the front wheel. In particular, the inner tubes then form stanchion tubes, and the outer tubes form dip tubes. The piston rods can then each be coupled to the inner tube, and the spring device can then optionally be arranged in the inner tube coaxially with respect to the piston rods.

[0024] Another subject of the present invention relates to a rear wheel damper having a motorcycle damping device, as described above. In particular, the rear wheel damper is configured as a telescopic damper. The rear wheel damper is used to elastically support a rear swing fork, and the motorcycle damping device performs a damping function when the motorcycle moves over unevenness in the road surface. Preferably, the rear wheel damper includes a spring device (suspension device) that performs a suspension function when the motorcycle moves over unevenness in the road surface. In principle, the spring device can be arranged outside the cylinder. However, instead of this, the spring device can also be arranged in a separate cylinder that is at least partially housed in the cylinder and / or movably connected to the piston rod.

[0025] In one specific embodiment, the control unit is selectively assigned to the piston valve acting in the tension direction or the tension stage valve or the piston valve acting in the compression direction or the compression stage valve in the rear wheel damper so that the main volume flow is influenced frequency-dependently during tension or compression load. In particular, the control unit is selectively arranged in the first or second working space, and the control piston is axially supported, preferably via a spring device, in the tension stage valve or the compression stage valve. Thus, during tension movement, the control volume flow can flow parallel to the main volume flow from the first working space to the control space via the control passage. Alternatively, during compression movement, the control volume flow can flow parallel to the main volume flow from the second working space to the control space via the control passage. Thus, frequency-selective damping can be easily achieved during tension or compression movement of the rear wheel damper.

[0026] In one possible development, the rear wheel damper can have a compensation reservoir in flow communication with the second working space, and a displaceable separating piston is arranged in the compensation reservoir, separating the chamber filled with damping fluid from the chamber filled with gas. In particular, the compensation reservoir is used to provide the damping fluid in the second working space with a compensation potential during piston rod dips and / or thermal deformation. The chamber filled with damping fluid can then be in flow communication with the second working space via an opening.

[0027] Another subject of the invention is a motorcycle having a front fork and / or a rear wheel damper as described above. In principle, the motorcycle has just one rear wheel damper set for frequency-selective damping during tension or compression movements. However, instead of this, the motorcycle can also have two rear wheel dampers, one set for frequency-selective damping during tension movements and the other set for frequency-selective damping during compression movements.

[0028] Further features, advantages and operations of the present invention will be apparent from the following description of preferred embodiments of the invention. [Brief explanation of the drawings]

[0029] [Figure 1] 1 is a cross-sectional view of a motorcycle damping device having a control unit acting in the direction of tension during high frequency excitation, according to an embodiment of the present invention; [Figure 2] 2 is a view similar to FIG. 1 showing the motorcycle damping device during low frequency excitation; [Figure 3] 1, showing a motorcycle damping device with a control unit acting in the compression direction. [Figure 4] 2 is a cross-sectional view of a first fork leg of a front fork having a motorcycle damping device according to FIG. 1; [Figure 5] 4 is a cross-sectional view of a second fork leg of a front fork having a motorcycle damping device according to FIG. 3. FIG. [Figure 6] 2 is a cross-sectional view of a rear wheel damper having the motorcycle damping device according to FIG. 1; [Figure 7] 6, but showing an alternative configuration of a rear wheel damper with a motorcycle damping device according to FIG. 1. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0030] 1 shows a motorcycle damping device 1 for use as a vibration damper for a motorized two-wheeled vehicle, preferably a motorcycle. The motorcycle damping device 1 comprises a cylinder 2 filled with a damping fluid and a piston rod 3, which is guided axially in the cylinder 2 about its longitudinal axis 100.

[0031] The motorcycle damping device 1 further includes a piston unit 4 and a control unit 5, which are commonly arranged on a piston rod pin 6 on the end side of the piston rod 3. The piston rod pin 6 is a portion of the piston rod 3 where the diameter is reduced. The piston unit 4 and the control unit 5 are attached to the piston rod pin 6 and are axially clamped via fixing means 7, for example, a piston rod nut.

[0032] The piston unit 4 comprises a working piston 8 arranged coaxially with respect to a longitudinal axis 100, which is radially sealed with respect to the longitudinal axis 100 via a piston seal 9 and is in contact with the inner periphery of the cylinder 2, dividing the cylinder interior space of the cylinder 2 into a first working space 10 on the piston rod side and a second working space 11 on the opposite side of the piston rod 3. The working piston 8 is fixed to the piston rod pin 6 and is therefore axially displaceable together with the piston rod 3.

[0033] The piston unit 4 comprises a piston valve 12, also called tension stage valve, acting on the piston rod 3 in a tension direction 101, and a piston valve 13, also called compression stage valve, acting on the piston rod 3 in a compression direction 102, which piston valves 12, 13 cooperate with a number of flow passages 14 formed in the working piston 8. Each of the piston valves 12, 13 comprises at least one valve disc 15 axially covering the flow passages 14. For example, the flow passages 14 can be divided into a group of tension stage passages and a group of compression stage passages.

[0034] During axial movement of the piston rod 3 relative to the cylinder 2, damping fluid is forced through the flow passage 14 or parts of the flow passage 14 and is damped by the valve disc 15, the damping force at least partly depending on the spring elasticity of the valve disc 15. The piston valve 12, 13 can be formed by several valve discs 15 stacked one on top of the other, a so-called valve disc package, and the number, size and shape of the individual valve discs 15 in the valve disc package determine the compression pressure, damping characteristic curve and damping behavior (damping characteristics) of the motorcycle damping device 1.

[0035] The control unit 5 comprises a control piston 16 arranged coaxially with respect to the operating piston 8 and a control pot 17 fixed to the piston rod pin 6, the control piston 16 being accommodated in the control pot 17 so as to be axially displaceable. The control pot 17 comprises a cylindrical pot wall 18 and a ring-disk-shaped pot bottom 19 connected to the pot wall 18. The control piston 16 is in radially sealed contact with the pot wall 18 via a sealing ring 20, and axially defines a control space 21 contained (enclosed) in the control pot 17.

[0036] In the illustrated embodiment, the control unit 5 is assigned to a piston valve 12 acting in the pulling direction 101, and a control passage 22 formed in the piston rod pin 6 connects the first working space 10 in terms of flow with the control space 21. Furthermore, the control piston 16 is provided with a discharge passage 23 which connects the control space 21 in terms of flow with the second working space 11.

[0037] The control unit 5 comprises a spring device 24, via which the control piston 16 is supported on the piston valve 12 (tension stage valve) in the tension direction 101. The spring device 24 comprises a spacer ring 25, an intermediate ring 26, spacer discs 27 and several spring discs 28, 29. A group of spring discs 28 is assigned to the piston valve 12, and a group of spring discs 29 is assigned to the control piston 16, with both groups of spring discs 28, 29 spaced apart axially via the intermediate ring 26. The spring discs 28 assigned to the piston valve 12 are supported in the region of their outer periphery on the valve disc 15 of the piston valve 12 via the spacer ring 25. The spring discs 29 assigned to the control piston 16 are supported in the region of their outer periphery on the control piston 16 and in the region of their inner periphery on the control piston 16 via the spacer discs 27. At this time, the spring device 24 urges the valve disc 15 axially toward the flow passage 14 and the control piston 16 toward the pot bottom 19 with a predetermined spring force.

[0038] The control unit 5 further comprises a guide sleeve 30 through which the control piston 16 and the spring device 24 are arranged or guided in the axial direction. The guide sleeve 30 extends through the control piston 16 and the spring device 24, which are guided to slide on the outer jacket surface of the guide sleeve 30 during displacement of the control piston 16 in the axial direction relative to the longitudinal axis 100. The guide sleeve 30 comprises, at its end facing the piston valve 12, a radial enlargement which axially limits the displacement stroke of the spring device 24 in the direction of the piston valve 12.

[0039] The pot bottom 19 defines an axial end stop 31 for the control piston 16, which limits the axial movement of the control piston 16 in the direction of the pot bottom 19 and influences a soft damping force characteristic curve. For this purpose, the end stop 31 is configured as an at least partial bulge of the pot bottom 19. The guide sleeve 30 defines a further axial end stop 32 for the control piston 16, which limits the axial movement of the control piston 16 in the direction of the piston valve 12 and influences a hard damping force characteristic curve. The further end stop 32 is formed by a radial step in the guide sleeve 30, on which at least one abutment disk 33 is axially supported.

[0040] The piston rod 3 or the piston rod pin 6 has a through-flow channel 34 extending parallel to the control channel 22. The through-flow channel 34 passes through the piston rod 3 coaxially with respect to the longitudinal axis 100 and connects the two working spaces 10, 11 to one another in terms of flow. A needle valve 35 is arranged in the hollow piston rod 3, which influences or throttles the flow through the through-flow channel 34. The needle valve 35 has an axially displaceable adjustment needle 36 that at least partially closes the through-flow channel 34. The throttle cross section of the needle valve 35 is determined by the axial position of the adjustment needle 36. For example, the adjustment needle 36 can be adjusted in its axial position relative to the through-flow channel 34 via an external adjustment mechanism (not shown). The adjustment needle 36 is elastically supported in the piston rod 3 in the direction of the through-flow channel 34 via a needle spring 37.

[0041] During a pulling or rebound movement of the piston rod 3 in the pulling direction 101, a main volume flow 103 moves from the first working space 10 to the second working space 11 via the piston valve 12 acting in the pulling direction 101. In parallel with this, a control volume flow 104 moves from the first working space 10 to the control space 21 via the control passage 22. If the fluid pressure in the control space 21 increases, the control piston 16 is displaced in the direction of the piston valve 12 and thereby further biases the spring device 24, which increases the damping force.

[0042] In the case of high excitation frequencies, for example higher than 10 Hz, the control space 11 is not filled at all or only slightly filled by the control volume flow 104 due to the rapid and small axial movement of the piston rod 3, so that the control piston 16 remains at the first end stop 31 and the damping force is maintained at a predetermined low level.

[0043] In the case of a low excitation frequency, for example lower than 1 Hz, the control space 11 is filled with the control volume flow 104 due to a larger and slower axial movement of the piston rod 3, so that the control piston 16 moves towards the second end stop 32, as shown in Fig. 2. This urges the spring device 24 until the control piston 16 abuts against the second end stop 32. This causes the spring device 24 to have a maximum urge (force), and therefore the motorcycle damping device 1 also has a maximum damping force characteristic curve. The magnitude of the urge (force) acting on the valve disc 15 can then be determined by the stiffness of the spring device 24 and the stroke of the control piston 16.

[0044] Furthermore, during tension and / or compression movements, a bypass volume flow 105 flows between the first working space 10 and the second working space 11 via the through-flow passage 34 and the needle valve 35, bypassing the piston unit 4 and the control unit 5, thereby further influencing the damping force depending on the axial position of the adjusting needle 36. For example, the bypass volume flow 105 can flow from the first working space 10 to the second working space 11 via the needle valve 35, parallel to the main volume flow 103 and the control volume flow 104, during tension movements of the piston rod 3.

[0045] Figure 3 shows an alternative configuration of the motorcycle damping device 1, in which the individual components are structurally identical to the arrangement shown in Figures 1 and 2. Therefore, only essential differences in arrangement and function will be described below.

[0046] In the illustrated embodiment, the control unit 5 is assigned to a piston valve 13 acting in the compression direction 102, and a control passage 22 formed in the piston rod pin 6 connects the second working space 11 in flow-technical terms with the control space 21. Furthermore, the control piston 16 has a discharge passage 23 which connects the control space 21 in flow-technical terms with the first working space 10. The control piston 16 is supported in the compression direction 102 on the piston valve 13 (compression stage valve) via a spring device 24.

[0047] During a compression or rebound movement of the piston rod 3 in the compression direction 102, a main volume flow 103 moves from the second working space 11 to the first working space 12 via the piston valve 13 acting in the compression direction 102. In parallel to this, a control volume flow 104 moves (flows) from the second working space 11 via the control passage 22 to the control space 21. When the fluid pressure in the control space 21 increases, the control piston 16 is displaced in the direction of the piston valve 13 and, depending on the excitation frequency, biases the spring device 24, which increases or decreases the damping force.

[0048] For example, a bypass volume flow 105 can flow from the second working space 11 to the first working space 10 via the needle valve 35 parallel to the main volume flow 103 and the control volume flow 104 during compression movement of the piston rod 3.

[0049] 4 and 5 show one fork leg (wishbone) 38, 39 of a motorcycle front fork 40. As also shown in FIGS. 1 to 3, the fork legs 38, 39 each include an inner tube 41 and an outer tube 42, and the tube 41 is disposed in the outer tube 42 so as to be axially displaceable about a longitudinal axis 100. The inner tube 41 and the outer tube 42 are sealed together via a sealing device 43 fixed to the outer tube 42.

[0050] The front fork 40 is formed as a telescopic suspension fork, and the motorcycle damping device 1 plays a role in damping. Furthermore, as shown in Figs. 1 to 3, the front fork 40 is provided with one spring device (suspension device) 44 for each of the fork legs 38, 39, and the spring device plays a role in suspension. In this case, the spring device 44 can be disposed inside the cylinder 2 and can be directly supported by the piston rod 3.

[0051] The front fork 40 is configured as, for example, a so-called inverted fork, whereby the outer tube 41 forms a stanchion tube and the inner tube 42 forms a dip tube. The outer tubes 41 of both fork legs 38, 39 can be connected to each other via a fork bridge (not shown). The inner tubes 42 are each connected to an axle bracket 45 that houses a wheel axle of the front wheel.

[0052] The first and second fork legs 38, 39 are each equipped with a motorcycle damping device 1, which is arranged on an outer tube 41 and an inner tube 42. In principle, the frequency-dependent motorcycle damping devices 1 of the first and second fork legs 38, 39 can be selectively set for a tensile load according to FIG. 1 or a compressive load according to FIG. 3. Preferably, however, as shown in FIGS. 4 and 5, the frequency-dependent motorcycle damping device 1 of the first fork leg 38 is configured for a tensile load according to FIG. 1, and the frequency-dependent motorcycle damping device 1 of the second fork leg 39 is configured for a compressive load according to FIG. 3. In other words, the damping force of the front fork 40 can be influenced both in the tensile direction 101 and in the compressive direction 102, depending on the excitation frequency.

[0053] 6 and 7 show two different configurations of a rear wheel damper 46 for a motorcycle. The rear wheel damper 46 has a fixing hole 47 which is directly connected to the cylinder 2 of the motorcycle damping device 1. The cylinder 2 therefore forms the damper tube of the rear wheel damper 46.

[0054] The rear wheel damper 46 is formed as a telescopic damper, and the motorcycle damping device 1 plays a role in damping. In addition, the rear wheel damper 46 includes a spring device 44, which plays a role in suspension. In this case, the spring device 44 can be disposed outside the cylinder 2 and can be supported in the cylinder 2 via a spring seat 48.

[0055] As shown in Figure 7, the rear wheel damper 46 can further comprise a compensation reservoir 49, which is connected in terms of flow to the second working space 11. In the compensation reservoir 49, a displaceable separating piston 50 is connected to the second working space 11 and separates a chamber 51 filled with damping fluid from a chamber 52 filled with gas, which is filled in the chamber 51 with an overpressure in order to provide a compensation possibility for the damping fluid in the cylinder 2 during immersion and thermal expansion of the piston rod 3.

[0056] Unlike the case of a front fork 40, which always comprises two fork legs 38, 39, the motorcycle damping device 1 of the rear wheel damper 46 can be set for a frequency-dependent tensile load according to Figure 1 or for a frequency-dependent compressive load according to Figure 3. In other words, the damping force of the individual rear wheel damper 46 can be influenced depending on the excitation frequency for a load in the tensile direction 101 or for a load in the compressive direction 102. However, if a motorcycle is provided with two rear wheel dampers 46, it is also possible in principle to set the motorcycle damping device 1 of one rear wheel damper for a frequency-dependent tensile load and the motorcycle damping device 1 of the other rear wheel damper for a frequency-dependent compressive load. [Explanation of symbols]

[0057] 1 Motorcycle damping device 2 cylinders 3 Piston rod 4 piston units 5. Control Unit 6 Piston rod pin 7 Fixing means 8 Working Piston 9 Piston seal 10 First Operating Space 11 Second Operating Space 12 Piston valve acting in the tensile direction 13 Compression-acting piston valve 14 Flow Passage 15 Valve disc 16 Control piston 17 Control Pot 18 Pot wall 19 Pot bottom 20 Seal ring 21 Control Space 22 Control Corridor 23 Discharge passage 24 Spring device 25 Spacer ring 26 Intermediate Ring 27 Spacer disc 28 Spring disc facing piston valve 29 Spring disc facing the control piston 30 Guide sleeve 31 first end stopper 32 Second end stopper 33 Contact disc 34 Through passage 35 Needle valve 36 Adjustment needle 37 Needle spring 38 First Fork Leg 39 Second Fork Leg 40 front fork 41 Inner tube 42 outer tube 43 Sealing device 44 Spring device 45 axle bracket 46 Rear wheel damper 47 Fixing hole 48 Spring seat 49 Compensation Reservoir 50 Separate piston 51 Chamber filled with damping fluid 52 Gas-filled chamber 100 Longitudinal axis 101 Tensile direction 102 Compression direction 103 Main volume flow 104 Controlled Volume Flow 105 Bypass volume flow

Claims

1. A motorcycle damping device (1) for a motorized two-wheeled vehicle, in particular a motorcycle, comprising: at least one cylinder (2) at least partially filled with damping fluid; a piston rod (3) guided in said cylinder (2) so as to be axially movable relative to a longitudinal axis (100); a piston unit (4) fixed at its end to the piston rod (3) and dividing the cylinder (2) into a first working space (10) on the piston rod side and a second working space (11) on the side opposite the piston rod (3); the piston unit (4) comprises a piston valve (12) acting in a tension direction (101) of the piston rod (3), through which a main volume flow (103) flows when the piston rod (3) moves in the tension direction (101), and the piston unit (4) comprises a piston valve (13) acting in a compression direction (102) of the piston rod (3), through which a main volume flow (103) flows when the piston rod (3) moves in the compression direction (102), a control unit (5) fixed to the piston rod (3), the control unit being configured to influence the main volume flow (103) on the basis of a control volume flow (104) generated by one of the piston valves (12, 13) in dependence on the excitation frequency.

2. 2. The motorcycle damping device (1) according to claim 1, characterized in that when the excitation frequency is reduced, the spring force acting on the piston valves (12, 13) is increased by the control unit (5), thereby increasing the flow resistance through the corresponding piston valves (12, 13) and therefore the damping force.

3. 3. The motorcycle damping device according to claim 1, wherein the control unit comprises a control pot fixed to the piston rod and a control piston axially displaceable in the control pot and axially defining a control space contained in the control pot, the control piston being supported in the axial direction relative to the longitudinal axis in the direction of the assigned piston valve, and displacing axially in the direction of the assigned piston valve when the fluid pressure in the control space increases, so that the damping force of the piston valve is increased.

4. 4. The motorcycle damping device (1) according to claim 3, characterized in that the control unit (5) comprises a spring device (24) for axially loading the piston valves (12, 13) and the control piston (16) with a predetermined spring force, and the control piston (16) is supported on the assigned piston valve (12, 13) in the axial direction relative to the longitudinal axis (100) via the spring device (24).

5. 5. The motorcycle damping device (1) according to claim 3 or 4, characterized in that the control unit (5) is assigned to a piston valve (12) acting in the pulling direction (101), and a control passage (22) is formed in and / or within the piston rod (3), which control passage connects the first working space (10) with the control space (21) in such a way that, when the piston rod (3) moves in the pulling direction (101), the controlled volume flow (104) flows from the first working space (10) via the control passage (22) to the control space (21).

6. 5. The motorcycle damping device (1) according to claim 3 or 4, characterized in that the control unit (5) is assigned to a piston valve (13) acting in the compression direction (102), and a control passage (22) is formed in and / or within the piston rod (3), which control passage connects the second working space (11) with the control space (21) in such a way that, when the piston rod (3) moves in the compression direction (102), the controlled volume flow (104) flows from the second working space (11) via the control passage (22) to the control space (21).

7. 7. The motorcycle damping device (1) according to claim 1, wherein the piston rod (3) is formed with a through-flow passage (34) which connects the first and second working spaces (10, 11) in a technical flow manner, and an adjustable needle valve (35) is arranged in the through-flow passage (34) in order to adjust the through-flow resistance of the bypass volumetric flow (105) flowing through the through-flow passage (34).

8. A front fork (40) having a motorcycle damping device (1) according to any one of claims 1 to 7.

9. 9. A front fork (40) according to claim 8, characterized in that it comprises first and second fork legs (38, 39), and the motorcycle damping device (1) is arranged in the first and second fork legs (38, 39).

10. 10. A front fork (40) according to claim 9, characterized in that the control unit (5) is assigned to the piston valve (12) acting in the tensile direction (101) in the first fork leg (38) so that the main volume flow (103) is influenced frequency-dependently under tensile loads, and the control unit (5) is assigned to the piston valve (13) acting in the compression direction (102) in the second fork leg (39) so that the main volume flow (103) is influenced frequency-dependently under compressive loads.

11. The front fork (40) according to claim 9 or 10, characterized in that the first and second fork legs (38, 39) each have an outer tube and an inner tube (41) displaceably arranged in the outer tube, and the motorcycle damping device (1) of the first and second fork legs (38, 39) is arranged in the inner tube (41) and the outer tube (42).

12. A rear wheel damper (46) comprising a motorcycle damping device (1) according to any one of claims 1 to 7.

13. 13. A rear wheel damper (46) according to claim 12, characterized in that the control unit (5) is assigned in the rear wheel damper (46) selectively to the piston valve (12) acting in the tensile direction (101) or to the piston valve (13) acting in the compressive direction (102) so that the main volume flow (103) is influenced frequency-dependently under tensile or compressive loads.

14. 14. A rear wheel damper (46) according to claim 12 or 13, characterized in that the rear wheel damper (46) comprises a compensation reservoir (49) which is in flow communication with the second working space (11), and in which a displaceable separation piston (50) is arranged which separates a chamber (51) filled with damping fluid from a chamber (52) filled with gas.

15. A motorcycle comprising a front fork (40) according to any one of claims 8 to 11 and / or a rear wheel damper (46) according to any one of claims 12 to 14.

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