A damping device for damping the movement of movable parts, in particular furniture parts, windows and / or doors

Abstract

The present invention relates to a damping device (1) for damping the movement of movable parts, in particular furniture parts, windows and / or doors, the damping device (1) comprising: - a cylinder (3); - a piston (5) guided linearly in particular within the cylinder (3) and damped by a damping fluid (4); - a piston rod (6) connected to the piston (5), wherein the damping device (1), preferably the piston (5), includes at least one flow path (9) for passing the damping fluid (4) therethrough, the flow path (9) having a flow cross-section (11), and the damping device (1) includes at least one throttle (10) for setting the flow cross-section (11) for passing the damping fluid (4) during the damping stroke, and the piston (5) and / or at least one throttle (10) are formed such that the piston (5) is rotatable relative to at least one throttle (10), and / or at least one throttle (10) is rotatable relative to the piston (5), and / or at least one throttle (10) is rotatable via the longitudinal movement of the piston (5) during the damping stroke inside the cylinder (3).

Description

Technical Field

[0001] The present invention relates to a damping device for damping the movement of movable parts, in particular furniture parts, windows and / or doors, comprising a cylinder, a piston guided linearly in particular in the cylinder and damped by a damping fluid, and a piston rod coupled to the piston. The damping device, preferably the piston, includes at least one flow path for passing the damping fluid, the flow path having a flow cross-section, and the damping device includes at least one throttle for setting the flow cross-section for passing the damping fluid during the damping stroke. The present invention further relates to the use of such a damping device. The present invention further relates to furniture, doors or windows provided with at least one such damping device.

[0002] From German Utility Model No. 202011108658, there is already known a damping device that utilizes a volume constant holding element in the form of a movable seal having a groove control portion in the backflow region of the damping fluid in order to enable a groove design adapted to volume changes caused by the seal element and uniform damping characteristics. The grooves can generate a volume flow rate that varies for different operating positions, thereby making it possible to achieve that the damping start point is higher than the damping end point depending on the distance from the piston with respect to the degree of damping capacity provided by the damping device.

[0003] The disadvantage in the prior art is that during the damping stroke, since the sealing element also moves over a groove with a variable cross-section, in the region of the groove with a large cross-section, only a small braking force can be caused. Moreover, a damping device with a given groove cross-section is not flexible enough to adjust to changes in the given situation of the furniture. This is because different dimensions, different movement mechanisms and / or movement courses of the movable furniture parts lead to changes in the damping characteristics. The damping device needs to be individually adapted with respect to any specific requirements during use and for each specific piece of furniture, regarding structural designs such as the geometry of the groove. Furthermore, especially when changing the piston speed, except for a uniform damping characteristic, compensation to the desired speed profile of the damping device cannot be carried out.

[0004] Therefore, the objective technical problem of the present invention is to provide a damping device improved over the prior art in which the disadvantages of the prior art are at least partially eliminated, and which is particularly excellent in terms of high damping capacity and / or constant damping capacity over the entire damping stroke.

[0005] This problem is solved by the characterizing part of claim 1.

[0006] Therefore, according to the present invention, it is assumed that the piston and / or at least one throttle is / are formed such that the piston is rotatable relative to at least one throttle, and / or at least one throttle is rotatable relative to the piston, and / or at least one throttle is rotatable through the longitudinal movement of the piston during the damping stroke inside the cylinder.

[0007] Thereby, for the first time, it becomes possible to adapt the damping capacity to the piston speed without the need for a groove that undesirably impairs the damping characteristics over the damping stroke within the cylinder.

[0008] By rotation, at least one throttle can partially cover at least one flow path for reducing the cross-sectional area of the flow-through. For example, at least one throttle opening and at least one flow path completely coincide at the start of the damping stroke. In this case, during the progress of the damping stroke, the damping cross-sectional area is preferably reduced to zero, especially for setting the damping capacity during the damping progress.

[0009] A positive characteristic in this regard is that, through the interaction between at least one throttle and at least one flow path of the piston, the cross-sectional area of the flow-through for the damping fluid can be adapted to the desired damping characteristics and / or the passage of the damping fluid can be set during the progress of the damping stroke. For example, at least one throttle can cover at least one flow path to a greater extent, starting from the start of the damping stroke where generally a high speed of the piston exists, to the operating position in the region of the end of the damping stroke where generally a low speed of the piston is desired, whereby the cross-sectional area of the flow-through for damping is preferably gradually reduced.

[0010] Particularly preferably, the piston is rotatable relative to at least one throttle, and / or at least one throttle is rotatable relative to the piston, and / or at least one throttle is rotatable within the cylinder during the progress of the damping stroke via the longitudinal movement of the piston and by means for rotating at least one throttle that is separate from at least one throttle and the damping fluid, whereby the cross-sectional area of the flow-through can be reduced.

[0011] Preferably, at least one throttle includes a throttle opening for passing the damping fluid. However, this is generally not necessarily required. At least one throttle can completely cover, partially cover, and / or not cover at least one flow path during the progress of the damping stroke to adjust the amount of damping fluid passing through the piston.

[0012] Preferably, at least one throttle is arranged on the upstream side of the piston in the passing direction of the damping fluid during the damping stroke, and particularly preferably on the end face of the piston.

[0013] Particularly preferably, the piston includes at least one flow path. In this case, generally, at least one flow path is formed by the region between the piston and the cylinder, and it is also conceivable that during the progress of the damping stroke, it is partially covered by at least one throttle.

[0014] For example, the groove in the cylinder can also be reduced and / or enlarged in cross-section by at least one throttle during the progress of the damping stroke. Generally, the groove can exist supplementarily to the flow path that is partially covered by at least one throttle inside the piston during the progress of the damping stroke.

[0015] Preferably, the flow path is formed such that the damping fluid passes or flows through from the region upstream of the piston to the region downstream of the piston in the flow-through direction or inside the piston during the progress of the damping stroke. This damping fluid can generally exist in the form of a liquid or as a gas.

[0016] As described at the beginning, the use of such damping devices in furniture parts, doors and / or windows is also protected in this specification.

[0017] The damping device offers the advantage that it can achieve a damping stroke over a large angular range of the part to be damped. Conventional damping devices are designed to damp the area immediately before the closed position in an area of approximately 20°. In contrast, the damping device according to the invention can damp an angular range of 90°, in which case, in particular, due to the interaction between at least one throttle and at least one flow path, the increased stress costs for the movement of the member can be reduced, for example by the damping device being set to be substantially inactive by the damping cross-section. Therefore, the user of the member generally preferably does not have to work on the damping device over a defined angular range, where the area in front of the closed position can preferably be effectively damped depending on the speed of the piston.

[0018] As described at the beginning, herein, furniture provided with at least one such damping device, a door provided with at least one such damping device, and a window provided with at least one such damping device are also protected, where a furniture part movable relative to the furniture body can be damped between an open position and a closed position by at least one damping device, the door can be damped between an open position and a closed position by at least one damping device relative to the door frame, or the window can be damped between an open position and a closed position by at least one damping device relative to the window frame.

[0019] The at least one damping device can here be used for external retrofitting as an additional component and / or can be used as an integrated component part. The at least one damping device can for example be integrated into furniture fittings, window fittings, or door fittings.

[0020] Advantageous embodiments of the invention are defined in each of the dependent claims.

[0021] Preferably, the damping device is suitable for furniture fittings or assembly fittings and includes a cylinder in which a damping fluid is arranged. Here, the piston is movable at a speed by a damping fluid during the damping stroke, Here, at least one flow path having a flow cross-section is provided, and the damping fluid can pass through the piston during the damping stroke through the flow path, Here, at least one control piston is provided, and the control piston is movably, preferably shiftably, supported within and / or on the piston, Here, the flow cross-section of the flow path can be changed by the movement of the control piston relative to the piston, Here, at least one stress accumulator, preferably a restoring spring, is provided, and the stress accumulator applies a restoring force to the control piston relative to the piston, and the restoring force cancels at least one flow stress that can act on the control piston by the damping fluid during the damping stroke.

[0022] Preferably, it is assumed that at least one flow path having a flow cross-section is provided, and the damping fluid can pass through the piston during the damping stroke through the flow path. Here, the following: At least one control piston is provided, and the control piston is movably, preferably shiftably, supported within and / or on the piston, Here, the flow cross-section of at least one flow path can be changed by the movement of at least one control piston relative to the piston, Here, at least one stress accumulator, preferably a restoring spring, is provided, and the stress accumulator applies a restoring force to at least one control piston relative to the piston, and the restoring force cancels at least one flow stress that can act on at least one control piston by the damping fluid during the damping stroke, Here, at least one control throttle is provided, and in the control throttle, a pressure drop proportional to the flow stress and the speed of the piston occurs, Here, a target speed for the piston (5) is preset, which depends on the position of the piston relative to the cylinder, Here, at least one control piston is movable relative to the piston such that, at a piston speed higher than the target speed, the flow cross-section of at least one flow path can be reduced against the restoring force, preferably wherein the target speed for the piston, which depends on the position of the piston relative to the cylinder, is - by means of at least one further stress accumulator, particularly preferably by means of a spring which applies a stress against the restoring force to at least one control piston, and / or - by means of an adjustment means for the throttle opening of at least one control throttle, and / or - by means of at least one groove in the inner wall of the cylinder having a variable groove cross-section, predetermined, which is characterized in that.

[0023] Particularly preferably, the following: At least one control throttle is provided, in which a pressure drop proportional to the flow stress and the speed of the piston occurs, wherein the target speed for the piston, which depends on the position of the piston relative to the cylinder, is predetermined, Here, at least one control piston is movable relative to the piston such that, at a piston speed higher than the target speed, the flow cross-section of the flow path can be reduced against the restoring force, preferably wherein the target speed for the piston, which depends on the position of the piston relative to the cylinder, is assumed to be predetermined by means of at least one spring which applies a stress against the restoring force to the control piston, and / or by means of an adjustment means for the throttle opening of at least one control throttle, and / or by means of at least one groove in the inner wall of the cylinder having a variable groove cross-section.

[0024] According to an advantageous design of the invention, it is assumed that the piston includes at least two, preferably exactly two, flow paths, in which case preferably the at least two flow paths are assumed to be arranged symmetrically with respect to the end face of the piston.

[0025] Due to the symmetrical arrangement, components such as pistons are symmetrically loaded, thereby increasing the service life of the damping device and / or preventing the tilting of components such as pistons within the cylinder. When there are multiple flow paths, these flow paths can be arranged on the end face of the piston at a distance from the symmetry axis of the piston, and the flow cross-section can be closed and / or opened during the rotation of the piston or at least one throttle in a defined manner.

[0026] In an advantageous form, it is assumed that at least one flow path is arranged on one end face of the piston and / or at least one throttle is arranged on the end face of the piston.

[0027] Thereby, the damping fluid can flow directly into the piston at the center. In this case, the damping fluid starts from the upstream region of the piston and flows through to the downstream region of the piston, and / or in some cases, the side openings in the piston that flow through the sealing element are not required. Generally, during the progress of the damping stroke, the fluid chamber in the upstream region of the piston is reduced by the movement of the piston, and the fluid chamber in the downstream region of the piston increases accordingly.

[0028] Particularly preferably, it is assumed that the piston and at least one throttle are formed so as to be movably coupled to each other in the longitudinal direction and / or separated from each other in the rotational direction during the progress of the damping stroke.

[0029] The longitudinal movement of the piston and / or at least one throttle occurring along the axis of the damping device can transmit the rotational movement of the piston and / or at least one throttle.

[0030] According to an advantageous embodiment of the invention, it is assumed that the flow cross-section is variable by rotation of the piston relative to at least one throttle and / or by rotation of at least one throttle relative to the piston.

[0031] The damping device preferably includes a hollow piston rod separate from the piston rod, by means of which the piston is rotatable relative to at least one throttle, where preferably the hollow piston rod is particularly preferably arranged directly on the piston and / or the hollow piston rod is particularly preferably arranged in the cylinder and / or guided via a twisted sleeve track. It has been found to be advantageous.

[0032] Generally, during the damping stroke, the piston is stationary in the rotational direction and guided in the cylinder so that at least one throttle is rotated, or at least one throttle is stationary in the rotational direction and guided in the cylinder during the damping stroke so that the piston can be rotated. In this case, the superposition of both rotational movements is also conceivable.

[0033] The hollow piston rod is preferably arranged between the cylinder and the piston on the side opposite to the end face of the piston. In this case, the hollow piston rod is guided along the sleeve track to move the piston relative to the throttle during the damping stroke. The sleeve track may be designed, for example, as a groove in the cylinder, along which the hollow piston rod is moved, in which case the twist can cause a rotational movement during the longitudinal movement of the piston.

[0034] Generally, the piston and at least one throttle may be formed to be movably coupled to each other in the longitudinal direction, whereby at least one throttle is interlocked longitudinally along the axis of the damping device together with the piston during the progress of the damping stroke.

[0035] An advantageous application form of the present invention is that the damping device includes magnets, preferably bar magnets and / or permanent magnets, and due to these magnets, at least one throttle is rotatable relative to the piston. In this case, preferably, the magnets are arranged, particularly preferably directly, on at least one throttle, and / or it is assumed that the magnets are rotatable via at least one metal strip, particularly preferably a steel strip, arranged on at least one, particularly preferably a cylinder.

[0036] Due to the magnetic interaction between the magnet and the metal strip arranged on the cylinder, at least one throttle can rotate during the longitudinal movement of at least one throttle inside the cylinder in order to reduce the flow cross-section (during damping) and / or to expand it (during the restoration of the damping device).

[0037] Particularly preferably, at least two metal strips are provided, and / or at least one metal strip is twisted and arranged on the cylinder.

[0038] It has been found that two metal strips are particularly advantageous for the rotation of the bar magnet, and the bar magnet can be guided along the metal strip in the cylinder along the twist (on the inner peripheral surface of the cylinder having an angular range that changes longitudinally for the rotation of at least one throttle).

[0039] In one embodiment of the present invention, the damping device includes a spring for applying stress to the piston, and the spring is arranged on at least one throttle. In this case, it is assumed that due to the spring, at least one throttle is rotatable relative to the piston. In this case, preferably, the spring is fixedly connected to at least one throttle, and / or it is assumed that at least one throttle is rotatable via the compression of the spring.

[0040] When the spring is compressed at its fixed free end, this compression automatically causes the rotation of the further free end of the spring. This inherent rotation in the compression process can be used to rotate at least one throttle arranged in the spring during the damping stroke. The degree of rotation can be adapted to the desired degree, for example, via the spring length, the spring cross-section or the diameter of the spring.

[0041] According to a preferred embodiment of the present invention, the damping device includes an impeller, and it is assumed that at least one throttle can rotate relative to the piston by means of the impeller. In this case, preferably, the impeller is preferably arranged directly on at least one throttle and / or can rotate via the passage of the damping fluid and / or is assumed to include at least two, particularly preferably four blades.

[0042] Particularly preferably, these blades are set to be inclined in the longitudinal direction of the damping device, so that the passage of the damping fluid into the piston through at least one throttle and / or vice versa can generate the rotation of at least one throttle arranged on the impeller.

[0043] Even more preferably, the damping device includes at least one telescopic device, and it is assumed that at least one throttle can rotate relative to the piston by means of the telescopic device. In this case, preferably, at least one telescopic device can rotate via a torsion guide and / or a guide arranged in a cylinder, particularly preferably, and / or is assumed to include a plurality of telescopic members that can expand and contract inside and outside and / or with each other.

[0044] The telescopic device is preferably arranged at at least one throttle between the side facing the end face of the piston and the cylinder. The guide can be formed, for example, as a twisted sleeve in the cylinder and / or the telescopic device in order to rotate the throttle together during the progress of the damping stroke via the telescopic device. During the damping stroke, the telescopic device is compressed in the longitudinal direction and can be shifted to the initial position during the restoration of the damping device.

[0045] The arrangement, structural design and positioning of the hollow telescopic rod can be used in the telescopic device and vice versa.

[0046] In a further embodiment, the damping device includes a sealing element, in which case the sealing element is formed as a braking element and / or is assumed to act parallel and / or in series with at least one flow path in the passing direction.

[0047] Basically, a sealing element may be provided to prevent the passage of the damping fluid between the cylinder and the outside in the piston, whereby the damping device is completely blocked in a flow path completely covered by at least one throttle. However, the sealing element can also allow a small amount of damping fluid to pass through, so that the sealing element functions as a braking element and / or damping is generated even when the flow path is completely closed.

[0048] In an advantageous configuration of the invention, the piston includes an output valve in the form of a control piston, in which case the output valve makes the flow cross-section of the fluid outflow opening of the piston and / or a further flow cross-section variable, and in this case, preferably, the output valve is assumed to act parallel and / or in series with an optionally existing sealing element and / or at least one throttle.

[0049] If the outlet valve is connected in parallel to at least one throttle and / or braking element, the passage through the braking element and / or at least one throttle can function as a control pressure for the outlet valve. In this case, the damping device is provided in the sense of a bypass line, which can preferably be switched between two operating positions (active damping via at least one flow path and blocked damping).

[0050] The outlet valve can adapt the damping action of the damping device such that the piston speed is adapted to a desired reference speed. In this case, at the start of the damping stroke in which a high piston speed occurs, a high damping action is generated, and this increased damping action decreases until the end of the damping stroke at which a low piston speed is desired. The desired reference speed can represent a linear curve of the speed over the damping distance, although generally other reference speed curves are also possible. Thereby, the damping action can be generated as a function of the desired reference speed during the progress of the damping stroke, depending on the distance as well as on the speed.

[0051] Particularly preferably, it is assumed that the control piston is arranged outside and / or inside the piston. In this case, preferably, at least one control piston is preloaded relative to the piston by a control piston spring and / or the piston can be stressed by a spring that may be present, and / or it is assumed that the outlet valve is formed as a pressure equalizer (Druckwaage).

[0052] The control piston can transmit the pressure differential at the piston via its function as a pressure equalizer. In this case, depending on the present pressure differential at the piston, the flow cross-section and / or a further flow cross-section at at least one flow path and / or fluid outflow opening decreases or increases. Therefore, the control piston can act as a pressure equalizer, in which case preferably, during the progress of the damping stroke, damping fluid permanently flows through the piston.

[0053] Particularly preferably, the damping device includes a fluid chamber filled with a damping fluid, and it is assumed that the fluid chamber is defined by at least a cylinder, optionally by a sealing element present, by a piston, and / or by a piston rod.

[0054] According to a preferred embodiment, the damping device includes a constant-volume holding element, and the constant-volume holding element keeps the volume available for the damping fluid in the fluid chamber constant at any position of the piston together with the piston rod, and / or in this case, the sealing element forms the constant-volume holding element together, is movable relative to the cylinder, and is preferably stressed by a spring that may be present on the side opposite to the fluid chamber of the cylinder.

[0055] According to a particularly preferred example, at least one throttle and the piston are formed to be rotatable relative to each other such that the flow cross-section can be reduced during the damping stroke, preferably depending on the distance in the longitudinal direction and / or depending on the speed of the piston.

[0056] Thereby, the damping capacity during the damping stroke is adapted to the desired damping effect. In this case, the damping capacity can be controlled depending on the axial position of the piston and / or depending on the speed of the piston inside the cylinder in order to achieve automatically setting the speed of the movable part to a desired reference speed, particularly via an output valve that may be present.

[0057] In the following, further details and advantages of the present invention will be described in more detail with reference to the embodiments shown in these drawings based on the description of the drawings.

Brief Description of the Drawings

[0058]

Figure 1

Figure 2

Figure 3a

Figure 3b

Figure 3c

Figure 3d

Figure 4a

Figure 4b

Figure 4c

Figure 5

Figure 6

Figure 7a

Figure 7b

Figure 8

Figure 9

Figure 10a

Figure 10b

Figure 10c

Figure 11

Figure 12a

Figure 12b

Figure 13a

Figure 13b

Figure 14

[0059] In FIG. 1, a damping device 1 for damping the movement of a movable part such as a furniture part, a window or a door is shown. This damping device 1 comprises a cylinder 3, a piston 5 linearly guided within the cylinder 3 and damped by a damping fluid 4, and a piston rod 6 coupled to the piston 5.

[0060] The piston 5 and the throttle 10 are formed such that, during the relative movement of the piston 5 inside the cylinder 3, the throttle 10 is rotatable relative to the piston 5 and inside the cylinder 3 (via the longitudinal movement of the piston 5 during the progress of the damping stroke and).

[0061] FIG. 2 differs from FIG. 1 only in that the piston rod 6 is further pushed into the cylinder 3 for damping, whereby the throttle 10 is rotated relative to the piston 5.

[0062] The damping device 1 includes a magnet 15 formed in the form of a bar magnet as a permanent magnet for rotating the throttle 10. Due to this permanent magnet, the throttle 10 is rotatable relative to the piston 5 during the progress of the damping stroke.

[0063] The magnet 15 is disposed directly on the throttle 10, where the magnet 15 is rotatable via two metal strips 16 in the form of a twisted steel strip disposed on the cylinder 3. These strips 16 are disposed outside the cylinder 3, and in this case, these strips 16 may generally be disposed on the inner circumferential surface of the cylinder 3. The number of these strips 16 is generally arbitrary, and in this case, the number is preferably provided to be the same as the number of free ends of the magnet 15.

[0064] Generally, a kinematic inversion of the rotation is also possible, in which case the piston 5 is rotated relative to the throttle 10 during the movement of the piston 5 in the cylinder 3. This may be envisaged, for example, in one preferred embodiment, in which case the rotation of the damping device 1 is generated by a hollow piston rod, in which case the piston 5 is rotatable relative to the throttle 10 by the hollow piston rod. The hollow piston rod can be disposed directly on the piston 5 and can be guided, for example, via a twisted sleeve track (similar to the movement mechanism for the twisted strip 16 using forced guidance along the sleeve track) disposed on the cylinder 3.

[0065] Figure 3a shows an exploded view of the component parts interacting with the throttle 10 of the damping device of an embodiment with a magnet 15.

[0066] The damping capacity, which is provided depending on the differential speed between the actual speed of the piston 5 and the desired reference speed of the piston 5, is generated in the damping device 1 via the interaction between the throttle 10 and the piston 5. For this purpose, the piston 5 includes at least one flow path 9 for passing the damping fluid 4, where in this case, this flow path 9 has a flow cross-section 11, and the damping device 1 includes a throttle 10 for setting the flow cross-section 11 for passing the damping fluid 4 during the damping stroke via the relative rotation between the throttle 10 and the piston 5.

[0067] Figures 3b to 3d visualize various throttle positions along the damping stroke, where in this case, the flow cross-section 11 is changed by the magnet 15, which is erased in these drawings. By the rotation of the throttle 10 relative to the piston 5, the flow cross-section 11 can be enlarged and reduced, whereby the damping capacity can be adapted.

[0068] The piston 5 includes exactly two flow paths 9, where in this case, these two flow paths 9 are symmetrically arranged with respect to one end face 12 of the piston 5. The number of these flow paths 9 is generally arbitrary.

[0069] The throttle 10 is arranged on the end face 12 of the piston 5, where in this case, this is not necessarily required in the flow path 9 arranged on the end face 12.

[0070] The piston 5 and at least one throttle 10 are formed such that they are movably coupled to each other in the longitudinal direction 32 during the progress of the damping stroke and separated from each other in the rotational direction 33 during the progress of the damping stroke.

[0071] Figures 4a to 4c show the kinematic coupling between the throttle 10 and the piston 5 in the longitudinal direction during relative rotation orthogonal to the longitudinal direction of the damping device 1.

[0072] Starting from the relative positioning in Figure 4b, the flow cross-section 11 in Figure 4a changes due to the rotation of the piston 5 relative to the throttle 10 (during the active movement of the throttle 10 in the rotational direction). In Figure 4c, the flow cross-section 11 for the damping fluid 4 is significantly reduced compared to Figure 4b.

[0073] Figure 5 shows further means for rotating between the throttle 10 and the piston 5 in order to change the flow cross-section 11 by rotation. In this case, a spring 17a for rotation is provided. This spring 17a can, for example, represent the restoring spring of the damping device 1 that exists anyway, and this restoring spring is used in the sense of a dual function for the adjustment of the flow cross-section 11 via the throttle 10.

[0074] In two enlarged detailed cross-sections of the cross-sectional view, it is clear that the damping device 1 includes a spring 17a for applying stress to the piston 5, and this spring 17a is arranged directly (similarly considered indirectly) on the throttle 10. By compressing the spring 17a, the rotation of the free end of the spring 17a arranged on the throttle 10 automatically occurs. In this case, the throttle 10 is rotated relative to the piston 5 by the spring 17a in order to adapt the flow cross-section 11 to the desired damping capacity.

[0075] In this embodiment, the spring 17a is fixedly coupled to the throttle 10, and this throttle 10 is rotatable via the compression of the spring 17a. In this case, generally, alternatively or additionally, a spring 17a for rotating the piston 5 may be arranged on the piston 5.

[0076] Figure 6 differs from Figure 5 only in that the piston 5 is moved in the direction of the damping stroke inside the cylinder 3, whereby the flow cross-section 11 changes via the spring 17a.

[0077] To show the rotation of the throttle 10 relative to the piston 5 initiated by the spring 17a, FIGS. 7a and 7b show two changing rotational positions of the throttle 10 by different flow cross-sections 11 with the spring 17a removed.

[0078] The spring 17a provided for the rotation of the throttle 10 has its free end position-fixed and fixed to the inner surface of the cylinder 3. Therefore, during the compression of the spring 17a, a rotational movement is transmitted to the throttle 10 (by the connection between the spring 17a and the throttle 10), whereby the flow cross-section 11 of the flow passage 9 for the piston 5 is adjusted.

[0079] FIG. 8 shows a further embodiment of the damping device 1. In this case, the damping device 1 includes a telescopic device 20, and by means of this telescopic device 20, the throttle 10 is rotatable relative to the piston 5.

[0080] The telescopic device 20 is supported on the end face of the inner surface of the cylinder 3. In this case, a guide part 21 twisted along the outer peripheral surface is used in the interaction with a guide pin for rotation. The telescopic device 20 is arranged inside the restoring spring 17. In this case, an arrangement outside the spring 17 and a damping device 1 without the spring 17 are also possible.

[0081] (Similar to the rotation of the throttle 10 via the spring 17), by fixing the telescopic device 20 at one end of the cylinder 3, a fixed point for the rotation of the throttle 10 (due to the kinematic connection between the throttle 10 and the telescopic device 20) is provided during the progress of the damping stroke during the telescopic movement.

[0082] FIG. 9 is different from FIG. 8 only at the point where the damping device 1 is moved along the damping stroke. Thereby, the telescopic device 20 is in an extended position with a changed flow cross-section 11.

[0083] FIG. 10a shows that the telescopic device 20 for the rotation of the aperture 10 via the telescopic device 20 includes three telescopic members 22 that can telescopically move inside and outside and relative to each other, and they are shown in a contracted state and an extended state.

[0084] FIG. 10b shows the components of the telescopic device 20 in an exploded view and in an assembled state. In this case, the spring 17 promotes the telescopic process but is not generally necessary.

[0085] FIG. 10c shows that the telescopic device 20 exists in a fully contracted state, and in this state, the aperture 10 is generally rotated relative to the piston 5 to the maximum extent with respect to the starting position.

[0086] FIG. 11 shows a further design of the damping device 1 in an exploded view and in an assembled state. In this case, a impeller 18 is used for the rotation of the aperture 10.

[0087] At two positions along the damping stroke according to FIGS. 12a and 12b, it is clear that the impeller 18 causes the aperture 10 to rotate relative to the piston 5 during the progress of the damping movement. For this purpose, the impeller 18 is directly arranged on the aperture 10 in this example and is rotatable through the passage of the damping fluid 4. In this case, a plurality of blades 19 are provided, and these blades 19 cause the rotation of the aperture 10 by the damping fluid 4 flowing through.

[0088] The impeller 18 acts in the same way as a turbine. In this case, an engaging movement between the damping fluid 4 and the blades 19 is generated for the rotation of the aperture.

[0089] FIGS. 13a and 13b differ from FIGS. 12a / 12b only in terms of the viewing angle changed for the cross-sectional view. Generally, a seal element 7 may be provided, whereby the piston rod 6 moves through. This damping device 1 includes a seal element 7. In this case, the seal element 7 is formed as a braking element 23 and acts in series with the flow path 9 in the passing direction of the damping fluid 4.

[0090] Generally, it may be assumed that the sealing element 7 acts parallel to the flow path 9 in the flow direction in the form of the braking element 23.

[0091] As is apparent in FIG. 14, supplementarily to the rotation of the throttle 10 (of all embodiments), the piston 3 can also include an outlet valve 24 in the form of a control piston 25, in which case, by the outlet valve 24, the flow cross-section 11 of the fluid outflow opening of the piston 5 or a further flow cross-section can be changed, in which case the outlet valve 24 acts parallel or in series to the sealing element 7 or the throttle 10.

[0092] The control piston 25 may be arranged outside the piston 5, in which case, in this embodiment, the control piston 25 is arranged inside the piston 5, in which case the control piston 25 is preloaded relative to the piston 5 by a control piston spring 28, and the piston 5 can be stress-loaded by a spring 17. Thereby, the outlet valve 24 is formed as a pressure equalizer 29.

[0093] The damping device 1 may be provided with an outlet valve 24 by a rotatable throttle 10 and a further outlet valve 24 via a control piston 25.

[0094] The damping device 1 includes a fluid chamber 8 filled with a damping fluid 4, and the fluid chamber 8 is defined by a cylinder 3, a sealing element 7, a piston 5, and a piston rod 6.

[0095] The damping device 1 includes a constant volume holding element 30, and the constant volume holding element 30 holds the volume available for the damping fluid 4 in the fluid chamber 8 constant at any position of the piston 5 together with the piston rod 6, and is stress-applied by a spring 17 on the side 31 opposite to the fluid chamber of the piston 5. The sealing element 7 may be formed movably relative to the cylinder 3 and / or may together form a constant volume holding member 30, but this is generally unnecessary.

[0096] By means of the throttle 10 described above, the piston 5 can be formed to be rotatable relative to the throttle 10 such that during the damping stroke, the flow cross-section 11 can be reduced depending on the distance in the longitudinal direction or depending on the speed of the piston 5.

[0097] According to the present invention, the damping device 1 can be used for a movable furniture part, a door or a window. In this case, for example, a furniture part, a door or a window that is movable relative to a furniture body, a door frame or a window frame can be damped between an open position and a closed position via the damping device 1, and thus the furniture, the door or the window may be provided with the damping device 1.

[0098] The damping device 1 is suitable for furniture fittings or assembly fittings. The piston 5 is movable at a speed by a damping fluid during the damping stroke. In this case, a flow path having a flow cross-section is provided, and the damping fluid can pass through the piston 5 during the damping stroke through the flow path. The control piston 25 is generally provided in all embodiments. The control piston 25 is shiftably supported within or on the piston 5. In this case, the flow cross-section of the flow path can be changed by the movement of the control piston 25 relative to the piston 5.

[0099] The stress accumulator 28 in the form of a restoring spring applies a restoring force to the control piston 25 relative to the piston 5, and the restoring force cancels at least one flow stress that can act on the control piston 25 by the damping fluid during the damping stroke.

[0100] A control throttle is provided, in which a pressure drop proportional to the flow stress and the speed of the piston 5 occurs. In this case, a target speed for the piston 5, which depends on the position of the piston 5 relative to the cylinder 3, is preset. In this case, the control piston 25 is movable relative to the piston 5 such that the flow cross-section of the flow path can be reduced against the restoring force when the speed of the piston 5 is higher than the target speed.

[0101] The target speed for the piston 5, which depends on the position of the piston 5 relative to the cylinder 3, may be preset, for example, by a spring that applies a stress against the restoring force to the control piston 25, by means for adjusting the throttle opening of a control throttle, or by a groove in the inner wall of the cylinder having a varying groove cross-section.

Claims

1. A damping device (1) for damping the movement of a movable part, in particular a furniture part, a window and / or a door, comprising: - a cylinder (3); - a piston (5) guided linearly in particular within the cylinder (3) and damped by a damping fluid (4); - a piston rod (6) coupled to the piston (5), wherein the damping device (1), preferably the piston (5), includes at least one flow passage (9) for passing the damping fluid (4); the flow passage (9) has a flow cross-section (11); the damping device (1) includes at least one throttle (10) for setting the flow cross-section (11) for passing the damping fluid (4) during a damping stroke, characterized in that the piston (5) and / or the at least one throttle (10) are formed such that the piston (5) is rotatable relative to the at least one throttle (10), and / or the at least one throttle (10) is rotatable relative to the piston (5), and / or the at least one throttle (10) is rotatable via the longitudinal movement of the piston (5) during the damping stroke inside the cylinder (3).

2. The damping device (1) according to claim 1, wherein the piston (5) includes at least two, preferably exactly two, flow passages (9), and preferably the at least two flow passages (9) are symmetrically arranged with respect to an end face (12) of the piston (5).

3. The damping device (1) according to claim 1 or 2, wherein the at least one flow passage (9) is arranged on one end face (12) of the piston (5), and / or the at least one throttle (10) is arranged on the end face (12) of the piston (5).

4. The damping device (1) according to any one of claims 1 to 3, wherein the piston (5) and the at least one throttle (10) are formed to be movably coupled to each other in a longitudinal direction (32) and / or separated from each other in a rotational direction (33) during the damping stroke.

5. The flow cross-section (11) is variable by rotation of the piston (5) relative to the at least one throttle (10) and / or by rotation of the at least one throttle (10) relative to the piston (5), the damping device (1) according to any one of claims 1 to 4.

6. The damping device (1) includes a hollow piston rod by which the piston (5) is rotatable relative to the at least one throttle (10), preferably the hollow piston rod is arranged directly on the piston (5) and / or the hollow piston rod is arranged on the cylinder (3), and / or it is assumed that the hollow piston rod is guided via a twisted sleeve track, the damping device (1) according to any one of claims 1 to 5.

7. The damping device (1) includes a magnet (15), preferably a bar magnet and / or a permanent magnet, by which the at least one throttle (10) is rotatable relative to the piston (5), preferably the magnet (15) is arranged directly on the at least one throttle (10) and / or the magnet (15) is rotatable via at least one metal strip (16) arranged on the cylinder (3), preferably a steel strip, the damping device (1) according to any one of claims 1 to 6.

8. At least two metal strips (16) are provided and / or the at least one metal strip (16) is twisted and arranged on the cylinder (3), the damping device (1) according to claim 7.

9. The damping device (1) includes a spring (17a) for applying stress to the piston (5), the spring (17a) is arranged on the at least one throttle (10), by which the at least one throttle (10) is rotatable relative to the piston (5), preferably the spring (17a) is fixedly connected to the at least one throttle (10) and / or it is assumed that the at least one throttle (10) is rotatable via compression of the spring (17a), the damping device (1) according to any one of claims 1 to 8.

10. The damping device (1) includes an impeller (18). By means of the impeller (18), the at least one throttle (10) is rotatable relative to the piston (5). Preferably, the impeller (18) is arranged, particularly preferably directly, on the at least one throttle (10) and / or is rotatable via the passage of the damping fluid (4), and / or is assumed to include at least two, particularly preferably four blades (19). The damping device (1) according to any one of claims 1 to 9.

11. The damping device (1) includes at least one telescopic device (20). By means of the telescopic device (20), the at least one throttle (10) is rotatable relative to the piston (5). Preferably, the at least one telescopic device (20) is rotatable, particularly preferably twisted and / or via a guide part (21) arranged on the cylinder (3), and / or is assumed to include a plurality of telescopic members (22) that can be telescoped inside and outside and / or with each other. The damping device (1) according to any one of claims 1 to 10.

12. The damping device (1) includes a seal element (7), and the seal element (7) - is configured as a braking element, and / or - acts parallel to the at least one flow path (9) in the flow direction, and / or - acts in series with the at least one flow path (9) in the flow direction. The damping device (1) according to any one of claims 1 to 11.

13. The piston (3) includes an output valve (24) in the form of a control piston (25). By means of the output valve (24), the flow cross-section (11) of the fluid outflow opening of the piston (5) and / or a further flow cross-section is variable. Preferably, the output valve (24) is assumed to act parallel and / or in series with the seal element (7) and / or the at least one throttle (10) that may be present. The damping device (1) according to any one of claims 1 to 12.

14. The control piston (25) is arranged outside and / or inside the piston (5). Preferably, the at least one control piston (25) is preloaded relative to the piston (5) by a control piston spring (28), and / or the piston (5) can be stressed by a spring (17) which may be present, and / or the outlet valve (24) is assumed to be formed as a pressure equalizer (29), the damping device (1) according to claim 13.

15. The damping device (1) includes a fluid chamber (8) filled with the damping fluid (4), and the fluid chamber (8) is defined by at least the cylinder (3), optionally by a seal element (7) present, by the piston (5), and / or by the piston rod (6), the damping device (1) according to any one of claims 1 to 14.

16. The damping device (1) includes a constant volume holding element (30), and the constant volume holding element (30) keeps the volume available for the damping fluid (4) in the fluid chamber (8) constant at any position of the piston (5) together with the piston rod (6), and / or the seal element (7) together forms the constant volume holding element (30) and is movable relative to the cylinder (3), on the side (31) opposite to the fluid chamber of the cylinder (3), and is preferably stressed by a spring (17) which may be present, the damping device (1) according to any one of claims 12 to 14 and claim 15.

17. The at least one throttle (10) and the piston (5) are formed to be rotatable relative to each other such that during the progress of the damping stroke, the flow cross-section (11) can be reduced, preferably depending on the distance in the longitudinal direction and / or depending on the speed of the piston (5), the damping device (1) according to any one of claims 1 to 16.

18. The piston (5) is rotatable relative to the at least one throttle (10), and / or the at least one throttle (10) is rotatable relative to the piston (5), and / or the at least one throttle (10) is rotatable within the cylinder (3) during the progress of the damping stroke by means of a means for rotating the at least one throttle (10) which is separate from the at least one throttle (10) and the damping fluid (4), whereby the flow cross-section (11) can be reduced, the damping device (1) according to any one of claims 1 to 17.

19. Use of the damping device (1) according to any one of claims 1 to 18 in a furniture part, a door and / or a window.

20. A piece of furniture comprising at least one damping device (1) according to any one of claims 1 to 18, wherein a furniture part movable relative to the furniture body can be damped between an open position and a closed position by the at least one damping device (1).

21. A door comprising at least one damping device (1) according to any one of claims 1 to 18, wherein the door can be damped between an open position and a closed position by the at least one damping device (1) relative to a door frame.

22. A window comprising at least one damping device (1) according to any one of claims 1 to 18, wherein the window can be damped between an open position and a closed position by the at least one damping device (1) relative to a window frame.

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