Damping device for furniture fittings or architectural fittings

Abstract

A damping device (1) for furniture fittings or building fittings, comprising a cylinder (3) with a damping fluid (4) arranged therein and a piston (5) operable via a piston rod (6), the piston being movable at a speed by the damping fluid (4) during a damping stroke, at least one flow passage (42) being provided with a flow cross-section (17), through which the damping fluid (4) can pass through the piston (5) during the damping stroke, at least one adjusting piston (12) being movably, preferably slidably supported within and / or on the piston (5), the movement of at least one adjusting piston (12) relative to the piston (5) enabling the flow cross-section (17) of at least one flow passage (42) to be changed, at least one accumulator (20), preferably a return spring, loading a restoring force on at least one adjusting piston (12) relative to the piston (5), the restoring force counteracting at least one flow force that can be exerted on at least one adjusting piston (12) by the damping fluid (4) during the damping stroke, at least one control orifice (29) being provided for a pressure drop proportional to the flow force and the speed of the piston (5), a target speed for the piston (5) being defined depending on the position of the piston (5) relative to the cylinder (3), the at least one adjusting piston (12) being movable relative to the piston (5) such that the flow cross-section (17) of at least one flow passage (42) can be reduced against the restoring force when the speed of the piston (5) is higher than the target speed, the damping device (1).

Description

Technical Field

[0001] The present invention relates to a damping device in the form of the superordinate concept described in claim 1. Furthermore, the present invention relates to a method for controlling the movement of a movable furniture part by adjusting the damping rate with at least one such damping device. Furthermore, the present invention relates to the use of such a damping device, as well as furniture, doors, and windows provided with at least one such damping device.

[0002] A damping device already known from the specification of German Utility Model No. 202011108658 utilizes a volume constant holding member in the form of a floating seal with a groove control section in the backflow region of the damping fluid in order to enable a groove configured to adapt to volume changes caused by a seal element and uniform damping characteristics.

[0003] In the prior art, various dimensional designs, various movement trajectories and / or movement courses of the movable furniture part change the damping characteristics, so that there is a drawback that the damping device cannot be adjusted flexibly according to the changed situation of the furniture. The damping device has to be individually adapted, in particular, for any special requirements during use and for any special furniture, via a structural configuration such as the geometry of the groove. Since the damping device always adjusts the speed of the movable furniture part to zero, due to the dependence of the damping device on the dimension setting (and / or the speed of the movable furniture part), a constant damping behavior cannot be obtained under various movable furniture parts and / or changing speeds of the movable furniture part.

[0004] Therefore, the technical problem addressed by the present invention is to at least partially eliminate the drawbacks of the prior art, and to provide an improved damping device over the prior art, which is excellent in a constant damping behavior or constant damping characteristics and does not depend on the dimension setting and / or speed of the movable furniture part, as well as a method for controlling the movement of the movable furniture part.

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

[0006] According to the present invention, therefore, at least one adjusting piston is movably, preferably slidably, supported within and / or on the piston. By the movement of at least one adjusting piston relative to the piston, the flow cross-section of at least one flow passage can be changed. At least one accumulator, preferably a return spring, which loads a restoring force on at least one adjusting piston relative to the piston, is provided. The restoring force counteracts at least one flow force that can be applied to at least one adjusting piston by the damping fluid during the damping stroke, and at least one control orifice is provided where a pressure drop proportional to the flow force and the speed of the piston takes place. A target speed for the piston, which depends on the position of the piston relative to the cylinder, is defined. When the speed of the piston is higher than the target speed, at least one adjusting piston is movable relative to the piston such that the flow cross-section of at least one flow passage can be reduced against the restoring force. Preferably, the target speed for the piston, which depends on the position of the piston relative to the cylinder, - at least one adjusting piston is loaded with a force against the restoring force by at least one further accumulator, particularly preferably by a spring, and / or - by the adjustability of the orifice opening of at least one control orifice, and / or - is defined by at least one groove provided on the inner wall of the cylinder with a varying groove cross-section has been specified.

[0007] For the first time, the damping device can have an automatic adjustment which is initiated via at least one adjustment piston, in particular based on the pressure behavior and / or the force behavior and / or by means of a control signal for at least one adjustment piston in at least one control orifice and / or at least one brake element. By means of this automatic adjustment, it is possible to generate a stronger damping action and a weaker damping action depending individually on the force acting on the piston rod. Such damping actions result in a particularly harmonious damping course of the movable furniture part even when the force action on the movable furniture part and / or on the damping device changes strongly. Thus, the speed of the movable furniture part always or continuously approximates a desired speed profile which is defined, for example, by at least one further accumulator acting between the cylinder and the piston. In this case, such an event is independent of the mass of the movable furniture part and / or of the transmission of force from the retraction mechanism to the damping device.

[0008] Furthermore, in particular when the piston speed is changed and / or when the dimensional setting of the movable furniture part is changed, an assimilation of the damping device to a (optionally defined) desired speed profile takes place in the sense of a uniform damping characteristic or a constant damping behavior.

[0009] Thereby, when the piston speed relative to the cylinder changes, it is possible to automatically assimilate the differential speed of the piston relative to the cylinder to the desired speed profile, thereby ensuring a uniform and / or harmonious damping force during the damping stroke, whether the speed of the piston is excessively high or undesirably low.

[0010] The damping adjustment is particularly preferably carried out as a function of the speed with respect to the piston relative to the cylinder. In this case, alternatively or additionally, an adjustment depending on the distance can also be carried out, whereby in particular the damping behavior is automatically adapted to the changing dimensional setting and / or speed of the movable part.

[0011] If the speed of the piston or a movable furniture part (or window or door) drops below a target speed defined by the structural configuration of the damping device, the damping device can automatically switch to an inactive state, whereby the braking of the piston and / or the movable furniture part is not carried out until the speed rises above the target speed.

[0012] Furthermore, the adaptation to the speed reference curve may be carried out whether the speed of the piston is too high or too low, whereby a particularly user-friendly handling of furniture equipped with such a damping device can be ensured by a harmonious and constant motion course.

[0013] Furthermore, without the need for structural modifications, the damping device can be used in a relatively large range of the movable furniture part. For example, the damping device according to the invention can operate in a relatively wide output range and / or can be flexibly adapted to a new required range by appropriately selecting the accumulator in the damping device.

[0014] Furthermore, the damping device exhibits advantageous collision behavior. When the desired reference speed of the piston relative to the cylinder is reached, in the region of the closed position of the movable furniture part, there is substantially no damping output, and / or generally the collision region of the damping device is arranged at a safe distance from the operating region of the damping device, so that damage to component elements is effectively avoided in particular. Therefore, damage is prevented or avoided even when the furniture is used inappropriately. Furthermore, the damping device makes the retraction time from at least a partially open position of the movable furniture part to the closed position of the movable furniture part more constant. This is because when the reference speed of the piston relative to the cylinder is dropped below, substantially no damping by the damping device occurs, and thus the movable furniture part can offset the effective time in the temporal course of the movement of the movable furniture part.

[0015] Furthermore, in an assembly consisting of at least one damping device and a retraction device, the retraction force of the retraction device can be reduced, whereby the haptics are improved for the user of the assembly.

[0016] The flow of damping fluid through the inlet opening of the piston is related to the speed of the piston relative to the cylinder and causes a pressure drop in the forward region. For example, such a pressure drop can be converted by a pressure equalizer (Druckwaage) into the sliding of at least one adjustment piston, in which case the spring preload loading the piston of at least one further accumulator can function as a reference speed. Depending on the position of at least one adjustment piston along the movement distance of the at least one adjustment piston relative to the piston, an output valve can be realized that provides a flow cross-section of the damping fluid flowing through the outlet opening of the piston.

[0017] Depending on the flow cross-section, a pressure of the damping fluid is generated in the forward region, which defines the damping force and thus the damping output of the damping device.

[0018] In other words, a control signal for the output signal in an output valve in the form of at least one adjustment piston (arranged on the outer or inner surface) interacting with the piston can be generated via the force behavior / pressure behavior - due to, for example, the amount of fluid flowing through at least one control orifice, the spring force, etc. - (for example, via a brake element and / or the fluid flow flowing through at least one control orifice), in which case a change in the flow cross-section is caused, for example, via an overlap or cross-section change of at least one flow passage.

[0019] In addition to this, the damping device can be compactly configured by at least one adjustment piston, has a particularly long service life with little maintenance, can flexibly adapt to various requirements, does not require complex components, is economically advantageous, and enables user-friendly assembly.

[0020] The advantage of such a structural configuration lies in that the damping output can be realized via at least one adjustment piston, which is different from the pure position dependence of the piston in the cylinder (e.g., via the groove in the damper) and the pure speed dependence of the piston in the cylinder (a function of speed or pressure difference, e.g., via the throttle interacting with the piston) in the sense of a controlled throttle. The speed dependence of the damping output can depend on the position of at least one adjustment piston in the cylinder, whereby the speed profile can be changed depending on the distance of at least one adjustment piston. When the pressure rises, a damping force acts so that the pressure is consequently reduced. The speed dependence can be converted into a pressure dependence, and the piston speed can consequently result in a variable cross-section realized by at least one adjustment piston. Preferably, a pressure-dependent control orifice is used and / or a reaction force dependent on distance is generated.

[0021] The output valve can generally be configured to be connected in parallel and / or in series to at least one control orifice and / or brake element. Generally, the outflow opening and / or the inflow opening or the flow cross-section can be related to at least one adjustment piston, at least one control orifice and / or the piston (in the kinematically opposite sense).

[0022] As described at the beginning, a method for controlling the movement of a movable furniture part by adjusting the damping rate by means of at least one damping device according to any one of the preceding claims, wherein when the speed of the movable furniture part relative to at least one damping device and / or the speed of the piston relative to the cylinder is higher than the target speed, at least one adjustment piston is moved relative to the piston against the return force, the flow cross-section of at least one flow passage is reduced, and the movable furniture part and / or the piston are moved so as to be braked to the target speed. In particular, it is specified that in the case of a speed lower than the target speed, at least one damping device is inoperative, and patent protection is also claimed for the method characterized thereby.

[0023] The idea underlying the present invention is to adjust a predefined desired speed profile of the damping device depending on the damping distance of the movable furniture part. This is achieved by the damping device generating a damping force in response to the speed difference with respect to the desired speed profile, where the desired speed profile is, particularly preferably, a linear speed curve having a constant slope. In other words, it can be ensured that the damping device automatically and / or always approximates or assimilates to the predefined speed profile. When the speed difference is negative - thus, the current speed of the piston relative to the cylinder is less than the desired speed - the damping device can cut off the damping force.

[0024] For example, at least one adjustment piston may be moved to a relative position with respect to the piston such that the damping fluid can flow through the piston substantially without resistance - by the pressure of the damping fluid on at least one adjustment piston - against the force load by at least one other accumulator. The maximum damping effect regarding the damping stroke section is such that there is no overlap between at least one fluid outflow opening and at least one outlet opening, and thus the movement of the piston in the cylinder is obtained at a relative position that is caused only by the compressibility of the damping fluid.

[0025] In the context of the present invention, overlap means that the outflow area of at least one fluid outflow opening of at least one adjustment piston intersects (or vice versa) with the inflow area of at least one outlet opening of the piston, thereby creating a flow cross-section for the damping fluid between at least one adjustment piston and the piston. However, the cross-section of the fluid outflow opening and / or the outlet opening may vary from the inflow area of at least one fluid outflow opening or to the outflow area of at least one outlet opening, and such events can be controlled by the pressure behavior specifically present in the damping device in the adjustment via the positioning of at least one adjustment piston relative to the piston. The cross-section of the outflow area of at least one fluid outflow opening and the cross-section of the inflow area of at least one outlet opening may generally be different; however, particularly preferably, they are configured to be of the same size and / or are formed in the form of cylindrical openings or holes.

[0026] The damping fluid may generally be present in the form of a gas and / or a liquid, and particularly preferably, a damping fluid in the liquid phase can be used. The damping device may be formed as a pneumatic device and / or a hydraulic device.

[0027] At least one control orifice and / or at least one adjustment piston can have a fixed and / or position-dependent and / or velocity-dependent flow cross-section. For example, the flow cross-section can be adjusted via the rotation of at least one control orifice relative to the piston.

[0028] As described at the beginning, patent protection is also claimed for the use of such damping devices in movable furniture parts, doors, and / or windows.

[0029] As described at the beginning, patent protection is also claimed for furniture provided with at least one such damping device, in which at least one movable furniture part is damped between an open position and a closed position relative to a furniture cabinet by means of at least one damping device.

[0030] As described at the beginning, patent protection is also claimed for a door provided with at least one such damping device, in which the door is damped between an open position and a closed position relative to a door frame by means of at least one damping device.

[0031] As described at the beginning, patent protection is also claimed for a window provided with at least one such damping device, in which the window is damped between an open position and a closed position relative to a window frame by means of at least one damping device.

[0032] Generally, the damping action can act in the direction of the closed position and / or in the direction of the open position. 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 region immediately in front of the closed position in a range of about 20°. In contrast, the damping device according to the invention can damp an angular range of up to 90°, in particular by the interaction of at least one control orifice and at least one flow passage, the increased force applied to move the member can be reduced, and / or the damping device can be substantially deactivated by a damping cross-section. Thus, the user of this member generally does not need to operate on the damping device over a preferably defined angular range, and at this time the region in front of the closed position can preferably be effectively damped depending on the piston speed.

[0033] Further advantageous embodiments of the invention are defined in the dependent claims.

[0034] Particularly preferably, it is specified that at least one adjustment piston is arranged on the piston from the outside and / or inside the piston and / or is present in the form of an outlet valve of the piston, and preferably, the flow cross-section of at least one flow passage can be changed via at least one control orifice and / or by at least one adjustment piston, whereby the speed of the piston can be adjusted.

[0035] At least one adjustment piston may be movable translationally relative to the piston and / or may be controlled via at least one control orifice that is movable translationally and / or rotationally relative to the cylinder.

[0036] In a preferred embodiment of the invention, at least one adjustment piston is preloaded relative to the piston by at least one additional accumulator and / or by at least one accumulator, and / or a force can be applied to the piston by at least one additional accumulator.

[0037] By means of at least one additional accumulator, the speed reference curve for the desired target speed curve of the piston and / or the movable furniture part can be adjusted via the behavior of the force acting on the piston. The speed reference curve can alternatively or additionally be adapted in other ways - for example, via the groove cross-section in the cylinder that depends on the position and interacts with at least one adjustment piston or via the spring constant of the accumulator.

[0038] Advantageously, the piston includes at least one inlet opening facing the front region of the fluid chamber, which is arranged on the side of the piston opposite to the piston rod, and at least one outlet opening facing the rear region of the fluid chamber, which is arranged on the side of the piston facing the piston rod. At least one adjustment piston includes at least one fluid inlet opening facing the front region of the fluid chamber and at least one fluid outlet opening facing the rear region of the fluid chamber. It is specified that the damping fluid can flow from the front region of the fluid chamber into the rear region of the fluid chamber through at least one fluid outlet opening and at least one outlet opening during the damping stroke of the damping device.

[0039] By changing the position of the piston and / or at least one adjustment piston in the cylinder, the inlet opening and the outlet opening may generally be exchanged. In this case, generally, it is important that the flow of the fluid in the flow cross-section of at least one flow passage is adjusted by the differential velocity, in particular, through the interaction between at least one adjustment piston and at least one control orifice.

[0040] According to an advantageous configuration of the present invention, it is specified that at least one adjustment piston is arranged completely inside or completely outside the piston. Preferably, at least one stopper for at least one adjustment piston is arranged on the piston, preferably facing the front region.

[0041] By being completely arranged inside the piston, an advantageously compact damping device can be obtained. Particularly advantageously, the relative pressure difference between the external space of the piston and / or at least one adjustment piston can be utilized to adjust the relative positioning of at least one adjustment piston with respect to the piston. When it is completely arranged outside the piston, particularly good force transmission can be achieved for the transmission of the overlap of the openings along the flow cross-section required for the desired speed of the piston.

[0042] At least one stopper secures at least one adjustment piston against undesired dropping out of the piston and / or limits the travel distance of at least one adjustment piston relative to the piston. For example, for easy assembly of at least one adjustment piston, at least one stopper may be arranged slidably and / or rotatably on the piston. However, stoppers that are materially connected to the piston are also conceivable.

[0043] Generally, at least one adjustment piston may be arranged outside / inside the piston in a predetermined region. Grooves that are distance-dependent, such as flow grooves, are also conceivable. For example, by torsion or compression, a reduced / increased flow cross-section can be generated for a reduced / enhanced damping output.

[0044] Advantageously, it has been determined that the speed of the piston relative to the cylinder during the damping stroke is adjustable by an overlap in the flow cross-section of at least one flow passage, preferably by an overlap between a fluid outflow opening that may be present in some cases and an outlet opening that may be present in some cases. Preferably, the overlap defines the flow cross-section of the damping fluid and / or it has been determined that the flow cross-section is changeable by the relative position of at least one adjustment piston relative to the piston.

[0045] The overlap and the resulting flow cross-section for the damping fluid (generally starting from the front region of the fluid chamber and going towards the rear region, for example) can define an output valve, which enables an automatic and continuous change of the damping force and / or the speed of the piston relative to the cylinder in order to adjust the damping device.

[0046] It has been found to be advantageous that the overlap and / or the change in the speed of the piston relative to the cylinder can be continuously changed during the damping stroke.

[0047] According to an advantageous embodiment of the present invention, at least one adjustment piston and the piston are formed as a pressure equalizer, and the overlap in the flow cross-section of at least one flow passage, preferably the overlap between a fluid outflow opening that may exist in some cases and an outlet opening that may exist in some cases, can be decreased when the pressure of the damping fluid for at least one adjustment piston and / or in the region of the overlap is increased, and / or can be increased when the pressure for at least one adjustment piston (12) and / or in the region of the overlap is decreased.

[0048] With the configuration as a pressure equalizer, the damping characteristics can be adjusted particularly effectively. In this case, a particularly compact damping device can be guaranteed, and / or no complex components are required.

[0049] In order to be able to guarantee a certain speed, the excess pumping flow can be derived, for example, through an adjustable measuring orifice provided with a bypass check valve arranged in a downstream pressure equalizer and / or a pressure equalizer slider. At this time, the volume flow moves the pressure equalizer slider in the direction of the outlet. The task of the pressure equalizer is to maintain the difference between the pressures generated in front of and behind the measuring orifice at a certain level set by the spring force, thereby enabling a certain volume flow to be generated at the outlet. The pressure generated at the throttle point acts on the end face of the pressure equalizer slider, and the pressure at the outlet acts on its back. Due to the constant force compensation, the position of the pressure equalizer is changed by the pressure fluctuations in front of and behind the measuring orifice. In this case, the volume flow cross-section at the outlet is decreased or enlarged. Starting from the inlet, the flow in the direction of the outlet can be carried out with less loss in the sense of a check valve.

[0050] The pressure equalizer can include the problem of maintaining a substantially constant volumetric flow independent of pressure and / or temperature. The volumetric flow can be constant and can depend on the volumetric flow cross-section of the throttle orifice. The pressure equalizer can be used for inflow control and / or outflow control. Generally, the throttle orifice can be provided together with the pressure equalizer and a spring, and the throttling can be performed at the throttle cross-section in the direction of the outlet starting from the inlet. To keep the volumetric flow constant independent of pressure, the pressure equalizer can include a control edge arranged downstream of the throttle orifice. The pressure equalizer can be moved by a spring. When the pressure equalizer is flowed through, the inlet pressure acts on the pressure equalizer and slides the pressure equalizer. In this case, the volumetric flow cross-section at the control edge of the pressure equalizer is reduced, whereby the pressure difference at the throttle orifice can be kept constant. When there is a balance of forces, the movement of the pressure equalizer can be stopped. The pressure equalizer can always compare the pressure difference at the throttle orifice with a value defined by the spring parameter and / or the preload. By means of an always-performed readjustment, a constant volumetric flow can be achieved. Generally, adjustment means such as an adjusting screw can be provided, and by means of this adjustment means, the degree of the volumetric flow can be changed within an adjustable boundary. The volumetric flow starting from the outlet and going towards the inlet can depend on the cross-section of the throttle orifice, and in this case, the function of the pressure equalizer can be stopped. The pressure equalizer can be arranged upstream and / or downstream of the throttle orifice.

[0051] The volumetric flow valve can function as a pressure equalizer, in which case the pressure equalizer is formed depending on the distance, so that a reference velocity depending on the distance is depicted. Thereby, as a goal, a damping device that damps to a desired reference velocity is realized, different from a damping device that causes damping such that no velocity exists anymore.

[0052] The pressure equalizer may be configured such that the piston is preloaded by a first spring force via at least one other accumulator, and at least one adjustment piston is preloaded by another spring force via at least one accumulator, - based on the difference between the fluid pressure in the front region of the fluid chamber and the fluid pressure inside the piston and / or at least one adjustment piston - such that the first spring force and the second spring force always remain in balance when a pressure drop occurs. Thereby, a special position of the adjustment piston is generated based on a defined other spring force. Since the volume flow of the damping fluid, which can be associated with the speed of the piston relative to the cylinder, is proportional to the pressure drop, the position of at least one adjustment piston becomes a control signal for the current speed of the piston relative to the cylinder. In other words, the pressure equalizer generates a control signal in the form of an adjustment piston position that is proportional to the speed of the piston relative to the cylinder.

[0053] Via each position of at least one adjustment piston, the overlap between the fluid outflow opening and the outlet opening can be adjusted, continuously changing the variable flow cross-section for the damping fluid, whereby the overlap functions as an adjustable outlet valve of the damping device so that the flow cross-section can always be adapted to a desired speed reference curve.

[0054] At least one other accumulator, preferably a spring, is provided, and it has been found advantageous for this accumulator to be arranged on the piston and / or at least one adjustment piston inside the cylinder in order to form a preferably linear speed reference curve of the damping device.

[0055] The accumulator preload of at least one other accumulator associated with the piston can define a reference speed of the piston relative to the cylinder. Depending on the force of the accumulator via the piston distance, a speed reference profile can be defined.

[0056] Advantageous embodiments are provided with at least one accumulator, preferably a spring, which is arranged inside the piston and / or on the piston and on at least one adjustment piston. Preferably, at least one accumulator acts between the piston and the cylinder end face of at least one adjustment piston and / or at least one other accumulator acts between the piston and the inner wall of the cylinder.

[0057] In the prior art, the control signal for the damping output basically depends on the absolute speed of the piston relative to the cylinder, whereby the regulation of the speed cannot be fully guaranteed.

[0058] Due to the spring preload of at least one accumulator associated with at least one adjustment piston, the control signal corresponding to the damping output depends via at least one adjustment piston on the differential speed of the piston relative to the cylinder with respect to the reference speed of the piston relative to the cylinder. Thereby, it can be ensured that the damping device always approximates the speed of the piston in the cylinder to the speed reference curve in the sense of adjusting the speed of the piston in the cylinder from either speed excess or speed deficiency, whereby the amount of the speed difference is reduced or eliminated by the damping device without at least one adjustment piston.

[0059] At least one accumulator may be used to regulate how much damping fluid can flow through the piston from the front region to the rear region and / or at what pressure by the damping fluid the cross-sectional area of the flow is enlarged or reduced by changing the overlap and / or how much enlargement or reduction of the overlap is caused via at least one adjustment piston.

[0060] Particularly preferably, during the damping stroke of the damping device, at least one accumulator can change the overlap in the flow cross-section of at least one flow passage, preferably the overlap between a fluid outflow opening that may be present and an outlet opening that may be present, and the speed of the piston relative to the cylinder can be increased by an increase in the overlap and / or decreased by a decrease in the overlap.

[0061] In an embodiment of the present invention, the overlap in the flow cross-section of at least one flow passage can be automatically reduced or eliminated via the speed difference of the piston relative to the cylinder with respect to the speed reference curve, and it is assumed that the speed difference can be transmitted by at least one other accumulator that may be present and / or at least one accumulator such that the relative position of at least one adjustment piston with respect to the piston occurs.

[0062] The overlap can be defined by two separate components and / or openings that at least partially overlap each other.

[0063] The speed difference between the desired speed of the piston relative to the cylinder - the speed of the piston without at least one adjustment piston relative to the speed reference curve - forms a speed difference curve to be adapted that is caused by the movement or force action of a movable furniture part with respect to at least one other accumulator. In this case, in the combination of both accumulators, the assimilation of the speed curve to the speed reference curve caused by at least one other accumulator - accumulated by the speed difference curve and the speed reference curve - becomes possible.

[0064] The speed difference of the piston to be reduced or eliminated defines the inlet size and the outlet size to be adjusted as a control signal for an output valve formed by at least one adjustment piston.

[0065] According to a preferred embodiment of the present invention, it is specified that the overlap in the flow cross-section of at least one flow passage can be automatically changed by the speed difference of the piston relative to the cylinder, relative to the speed reference curve, which is transmitted via at least one other accumulator and / or at least one accumulator that may be present in some cases.

[0066] It has been found to be preferable that the speed of the piston during the damping stroke can be changed by at least one other accumulator and / or at least one accumulator that may be present in some cases, via the relative position of at least one adjusting piston relative to the piston.

[0067] Since adaptation to the speed reference curve is only possible via the changed positioning of at least one adjusting piston relative to the piston, no additional components or electronic control modules are required in addition to the mechanically generated movement of at least one adjusting piston via at least one accumulator.

[0068] More preferably, it is specified that at least one other accumulator and at least one accumulator are preferably arranged parallel to each other, preferably in the direction of the damping stroke, and preferably, it is specified that at least one other accumulator and at least one accumulator are arranged coaxially.

[0069] Thereby, the force transmission between the piston and at least one adjusting piston is promoted. In this case, tipping of at least one adjusting piston relative to the piston is prevented, and particularly precise adjustment of the damping force or piston speed over the damping stroke distance can be ensured.

[0070] In another embodiment of the present invention, it may be specified that at least one sealing element is provided, in which case the fluid chamber is defined at least in a predetermined region by this at least one sealing element, and preferably it is specified that the piston rod is movable through at least one sealing element.

[0071] Generally, another sealing element may be arranged, for example, at a location such as the outer peripheral surface of the piston and / or the inner peripheral surface of the cylinder.

[0072] The at least one sealing element can exist, for example, in the form of a brake element or in the form of a section at at least one control orifice, in which case a complete or partial seal at the inner wall of the cylinder is possible. For example, a slight fluid flow through a brake element can be utilized for the functionality of the damping device, which functions in at least one regulating piston (formed as a pressure equalizer) as an output valve as a control signal for the output signal. However, generally, such a form of sealing element is not necessarily required.

[0073] According to an advantageous configuration of the present invention, it is specified that at least one piston rod is movable relative to the cylinder directly or indirectly by a movable furniture part, preferably via a linear movement, a rotational movement, and / or a swivel movement.

[0074] Generally, the damping device can be used in all structural configurations of furniture and / or movable furniture parts whose movement course is to be damped. Particularly preferably, a swivel movement caused by the rotation of a movable furniture part, preferably a furniture flap or the like, is directly converted into a linear movement of the piston rod. When it is indirectly converted to the piston rod, a sliding element, a coated surface, a transmission device, and / or a control cam can be considered, but generally it is not necessary.

[0075] Advantageously, the sealing element is formed as a braking element and / or acts parallel to at least one flow passage and / or at least one control orifice in the flow direction of the damping fluid and / or acts in series with at least one flow passage and / or at least one control orifice in the flow direction of the damping fluid.

[0076] At least one control orifice may be connected in series and / or in parallel with respect to at least one adjusting piston.

[0077] Advantageously, the damping device includes a fluid chamber filled with damping fluid, and it is specified that the fluid chamber is defined at least by a cylinder, optionally an existing sealing element, a piston, and / or a piston rod.

[0078] Particularly preferably, the damping device includes a constant volume holding element that keeps the volume provided for the damping fluid in the fluid chamber constant at any position of the piston including the piston rod, and / or the sealing element together forms the constant volume holding element, is movable relative to the cylinder, and is preferably loaded with a force by another accumulator that may optionally exist on the side opposite to the fluid chamber.

[0079] According to a preferred embodiment of the present invention, grooves are formed on the inner wall of the cylinder, and it is specified that during the damping stroke, the damping fluid can flow from the front region of the fluid chamber to the rear region of the fluid chamber through these grooves.

[0080] Particularly preferably, in an embodiment of the present invention, at least one adjusting piston is movable translationally relative to the piston and / or at least one control orifice during the damping stroke, preferably depending on the longitudinal distance of the piston and / or depending on the speed.

[0081] Alternatively or additionally, the piston and / or at least one control orifice may be configured such that the piston is rotatable relative to at least one control orifice and / or at least one control orifice is rotatable relative to the piston, via longitudinal movement of the piston, during a damping stroke inside the cylinder.

[0082] Thereby, in special applications, the damping output can be adapted to the piston speed without the need for grooves or another accumulator in the cylinder that may disadvantageously impair the damping characteristics over the damping stroke.

[0083] At least one control orifice can partially cover at least one flow passage by rotation in order to reduce the flow cross-section. For example, at least one orifice opening and at least one flow passage coincide at the start of the damping stroke, and during the damping stroke, - in particular, to adjust the damping output during the damping process, the damping cross-section is preferably reduced to zero.

[0084] In addition, an advantageous feature is that the interaction between at least one control orifice and at least one flow passage of the piston can adapt the cross-section for the flow-through or flow cross-section of the damping fluid to the desired damping characteristics and can regulate the flow-through of the damping fluid during the damping stroke. For example, at least one control orifice can cover at least one flow passage to a greater extent starting from the start of the damping stroke, where generally a high piston speed occurs, towards the operating position in the region of the end of the damping stroke, where generally a low piston speed is desired, whereby the flow cross-section for damping is preferably continuously and / or, for example, via the orifice opening, reduced.

[0085] Particularly preferably, the piston includes at least two, preferably exactly two flow passages, and preferably, it is specified that at least two flow passages are arranged symmetrically with respect to the end face of the piston, and / or - at least one flow passage is arranged on the end face of the piston, and / or at least one control orifice is arranged on the end face of the piston, and / or - the piston and at least one control orifice are formed such that they are longitudinally kinematically connected to each other during the damping stroke and / or separated from each other in the rotational direction during the damping stroke, and / or - the cross-sectional flow area can be changed by the rotation of the piston relative to at least one control orifice and / or by the rotation of at least one control orifice relative to the piston, and / or - the at least one control orifice and the piston are formed to be rotatable relative to each other such that the cross-sectional flow area (17) can be reduced, preferably depending on the longitudinal distance of the piston (5) and / or the speed, during the damping stroke. This has been specified.

[0086] Preferably, it has been specified that the damping device has a hollow piston rod that can rotate the piston relative to at least one control orifice. Preferably, the hollow piston rod is particularly preferably arranged directly on the piston, and / or the hollow piston rod is particularly preferably arranged on the cylinder and / or guided via a twisted slide track.

[0087] Preferably, the damping device is specified to have a magnet, preferably a bar magnet and / or a permanent magnet, which can rotate at least one control orifice relative to the piston, and preferably the magnet is particularly preferably arranged directly at least one control orifice, and / or the magnet is particularly preferably rotatable via at least one metal strip, particularly preferably a steel strip, arranged in the cylinder.

[0088] Preferably, it is specified that at least two metal strips are provided and / or at least one metal strip is twisted and arranged in the cylinder.

[0089] Preferably, the damping device has a spring for loading a force on the piston, which is arranged at least one control orifice, and it is specified that at least one control orifice is rotatable relative to the piston by the spring, and preferably the spring is firmly connected to at least one control orifice, and / or at least one control orifice is rotatable via compression of the spring.

[0090] Preferably, the damping device is specified to have an impeller that can rotate at least one control orifice relative to the piston, and preferably the impeller is particularly preferably arranged directly at least one control orifice, and / or is rotatable via the flow of the damping fluid, and / or is specified to have at least two, particularly preferably four blades.

[0091] Advantageously, it has been determined that the damping device preferably has at least one telescopic device which can rotate at least one control orifice relative to the piston, and preferably at least one telescopic device is rotatable, particularly preferably twisted and / or via a guide arranged in the cylinder, and / or has been determined to have a plurality of telescopic members which can be telescopically extended and retracted relative to and / or into each other.

[0092] Particularly preferably, in the embodiment, it has been determined that at least one adjusting piston acts parallel and / or in series with respect to any seal element present and / or at least one control orifice.

[0093] According to an advantageous configuration of the invention, at least one adjusting piston slides relative to at least one piston, in particular automatically, via at least one accumulator, and thus the speed of the piston relative to the cylinder is preferably linear and / or adapted to a speed reference curve defined via at least one further accumulator, and preferably it has been determined that at least one fluid outflow opening of at least one adjusting piston is slid relative to at least one outlet opening of the piston.

[0094] According to a preferred embodiment of the invention, - the speed of the piston relative to the cylinder during the damping stroke is adjusted by an overlap in the flow cross-section of at least one flow passage, preferably by an overlap between at least one fluid outflow opening which may be present and at least one outlet opening which may be present, the overlap defining the flow cross-section of the damping fluid and / or the flow cross-section being changed by the relative position of at least one adjusting piston relative to the piston, - the overlap and / or the change in the speed of the piston relative to the cylinder is continuously changed during the damping stroke, - At least one adjustment piston and the piston are formed as a pressure equalizer, and an overlap in the flow cross-section of at least one flow passage is decreased when the pressure of the damping fluid in the region of the overlap with respect to and / or for at least one adjustment piston is increased, and / or increased when the pressure in the region of the overlap with respect to and / or for at least one adjustment piston is decreased. - During the damping stroke of the damping device, at least one accumulator changes the overlap in the flow cross-section of at least one flow passage, and the speed of the piston relative to the cylinder is increased by an increase in the overlap and / or decreased by a decrease in the overlap. - The overlap in the flow cross-section of at least one flow passage is automatically reduced or eliminated via the speed difference of the piston relative to the cylinder with respect to the speed reference curve, and the speed difference is transmitted, optionally via at least one further accumulator and / or at least one accumulator that may be present, such that a relative position of at least one adjustment piston with respect to the piston occurs, and / or - The overlap is automatically changed by the speed difference of the piston relative to the cylinder with respect to the speed reference curve, which is transmitted, optionally via at least one further accumulator and / or at least one accumulator that may be present. It is specified that.

[0095] Generally, it is optional whether the expansion of the flow cross-section is effected by the expansion or relative positioning of at least one adjustment piston with respect to the piston, in which case the compression accumulator and the tension accumulator can be used in any orientation, in particular in front of or behind at least one adjustment piston in the direction of the damping stroke relative to at least one adjustment piston.

[0096] The features of the device claims are applicable in the method claims and vice versa. Further details and advantages of the present invention will be explained in detail below with respect to the embodiments shown in the drawings with reference to the description of the drawings.

Brief Description of the Drawings

[0097]

Figure 1a

Figure 1b

Figure 2a

Figure 2b

Figure 2c

Figure 2d

Figure 2e

Figure 3a

Figure 3b

Figure 3c

Figure 4a

Figure 4b

Figure 4c

Figure 4d

Figure 5a

Figure 5b

Figure 6a

Figure 6b

Figure 7a

Figure 7b

Figure 8a

Figure 8b

Figure 9

Figure 10

Figure 11a

Figure 11b

Figure 11c

Figure 11d

Figure 12a

Figure 12b

Figure 12c

Figure 13

Figure 14

Figure 15a

Figure 15b

Figure 16

Figure 17

Figure 18a

Figure 18b

Figure 18c

Figure 19

Figure 20a

Figure 20b

Figure 21a

Figure 21b

Figure 22a

Figure 22b

Figure 23a

Figure 23b

[0098] FIG. 1a shows a damping device 1 for damping the movement of a movable furniture part 2, which damping device comprises a cylinder 3, a piston 5 guided in the cylinder 3 and damped by a damping fluid 4, a piston rod 6 connected to the piston 5, and a fluid chamber 7 filled with the damping fluid 4 defined at least by the cylinder 3, the piston 5, and the piston rod 6.

[0099] The piston 5 has an inlet opening 9 facing the front region 8 of the fluid chamber 7, where the front region 8 is arranged on the side of the piston 5 opposite to the piston rod 6. The piston 5 has an outlet opening 11 facing the rear region 10 of the fluid chamber 7, where the rear region 10 is arranged on the side of the piston 5 facing the piston rod 6.

[0100] The damping device 1 is provided with an adjustment piston 12 disposed inside the piston 5, and the adjustment piston 12 is completely disposed inside the piston 5. In order to define and fix the adjustment piston 12 relative to the piston 5, a stopper 15 facing the front region 8 is disposed on the piston 5 for the adjustment piston 12.

[0101] The adjustment piston 12 includes a fluid inlet opening 13 facing the front region 8 of the fluid chamber 7 and a fluid outlet opening 14 facing the rear region 10 of the fluid chamber 7. The damping fluid 4 flows from the front region 8 of the fluid chamber 7 into the rear region 10 of the fluid chamber 7 through the fluid outlet opening 14 and the outlet opening 11 during the damping stroke of the damping device 1.

[0102] The speed of the piston 5 relative to the cylinder 3 during the damping stroke can be adjusted by the overlap 16 between the fluid outlet opening 14 and the outlet opening 11. The overlap 16 corresponds to the flow cross-section 17 of the damping fluid 4, and this flow cross-section 17 can be changed by the relative position of the adjustment piston 12 with respect to the piston 5 (see Fig. 3c).

[0103] A damping element can be disposed between the adjustment piston 12 and the piston 5 to block the direct flow of the damping fluid 4 from the front region 8 through the outlet opening 11. The outer peripheral surface of the adjustment piston 12 is generally adapted to the inner peripheral surface of the piston 5 such that the damping fluid 4 flows in without passing through the fluid outlet opening 14 from the front region 8 to the rear region 10. However, generally, when there is no overlap 16 between the fluid outlet opening 14 and the outlet opening 11, in order to also ensure the damping stroke distance of the piston 5, it is conceivable to allow a slight direct passage of the damping fluid 4 that does not pass through the fluid outlet opening 14 from the front region 8 to the rear region 10.

[0104] In the damping device 1, another energy storage device 18 in the form of a spring is arranged, and this energy storage device is arranged on the piston 5 inside the cylinder 3 in order to form the linear speed reference curve 19 of the damping device 1. Generally, another energy storage device 18 may also be arranged on the adjusting piston 12 alternatively or supplementarily. In this case, it is specified that preferably, another energy storage device 18 is arranged exclusively on the piston 5 with respect to the adjusting piston 12 and the piston 5.

[0105] In the damping device 1, an energy storage device 20 formed as a spring, which is completely arranged inside the piston 5, is arranged. The energy storage device 20 is arranged on the piston 5 and the adjusting piston 12. In this case, the energy storage device 20 acts between the piston 5 and the cylinder end face 21 of the adjusting piston 12. The energy storage device 20 functions to change the overlap 16 between the fluid outflow opening 14 and the outlet opening 11 in order to adjust the speed of the piston 5 relative to the cylinder.

[0106] The overlap 16 can be automatically changed by the speed difference 22 of the piston 5 relative to the cylinder 3 with respect to the speed reference curve 19, which is transmitted via another energy storage device 18 and by the energy storage device 20. The speed of the piston 5 during the damping stroke can be changed via the relative position of the adjusting piston 12 with respect to the piston 5, via another energy storage device 18 and by the energy storage device 20.

[0107] The parameter x represents the damping stroke distance of the piston 5, and the parameter z represents the relative movement between the adjusting piston 12 and the piston 5. Above the damping device 1, the pressure transition along the flow path of the damping fluid is shown, and this pressure transition includes the parameter p2 as the pressure in the front region 8, p1 as the pressure inside the piston 5 (between the fluid inflow opening 13 and the fluid outflow opening 14), p0 as the pressure in the rear region 10, and Δp2 as the difference between p2 and p1.

[0108] FIG. 1b shows the variation of the speed v of the piston 5 relative to the cylinder 3 with respect to the damping stroke distance x. In this case, another accumulator 18 defines a speed reference curve 19 for the movement of the piston 5 relative to the cylinder 3 when the movable furniture part 2 moves uniformly.

[0109] The speed curve of the piston 5 located above the speed reference curve 19 of the piston 5 is at least approximated to the desired speed reference curve 19 via the damping device 1. In this case, preferably, the assimilation of the speed curve to the speed reference curve 19 is performed.

[0110] When the speed difference 22 between the current speed of the piston 5 is large, the output valve realized by the adjustment piston 12 acts more powerfully than when the speed difference 22 is small. The current difference between the speed curve and the speed reference curve 19 forms a signal for the adjustment piston 12 in order to cause the approximation of the speed curve to the speed reference curve 19.

[0111] FIG. 2a shows the adjustment piston 12 used for the pressure equalizer. In this case, the parameter A represents the currently existing flow cross-section 17, which occurs, for example, in the output valve formed by the fluid outflow opening 14 and the outlet opening 11 with a 10% overlap 16 to adjust the speed of the piston 5.

[0112] The adjustment piston 12 and the piston 5 are formed as a pressure equalizer. The overlap 16 between the fluid outflow opening 14 and the outlet opening 11 can be decreased when the pressure of the damping fluid 4 with respect to the adjustment piston 12 or in the region of the overlap 16 is increased, and can be increased when the pressure with respect to the adjustment piston 12 or in the region of the overlap 16 is decreased.

[0113] The spring force F of the accumulator 20 c is a function of the parameter (z) of the relative position between the adjustment piston 12 and the piston 5. The spring force F0 of another accumulator 18 is a function of the parameter (x) of the damping stroke distance of the piston 5.

[0114] Δp2 is the difference between p2 and p1, and in this case, Δp2 * 's functional relationship is obtained by dividing Fc(z) - F0(x) by the area A of the flow cross-section 17 in the form of the overlap 16.

[0115] Figure 2b shows the relative positioning of the adjustment piston 12 with respect to the piston 5 during the damping stroke where the velocity of the piston 5 relative to the cylinder is located above the desired velocity reference curve 19. The parameter z is adjusted at the adjustment piston 12 such that the forces of both accumulators 18, 20 are balanced, and forms a control signal for the current velocity of the piston 5. This is because the volume flow of the damping fluid 4 and the associated piston velocity are proportional to Δp2.

[0116] Figure 2c shows a graph of the spring stress of another accumulator 18 as a function of the damping stroke distance x, and this other accumulator defines the velocity reference curve 19 of the piston 5, as indicated by v Ref The velocity reference curve 19 can be defined by the damping stroke distance x of the piston 5 according to the spring force F0. A control signal for the differential velocity for the damping output is transmitted to the adjustment piston 12 via the preload of the accumulator 20. The movement of the piston rod 6 is initiated, for example, by the angular velocity of the movable furniture part 2.

[0117] Figures 2d to 3b show usage examples where the velocity of the piston 5 relative to the cylinder 3 starting from the movable furniture part 2 is higher than the desired velocity according to the velocity reference curve 19 at the current damping stroke distance position x.

[0118] In Figure 2d, the damping stroke distance x is equal to 0 (indicated by the circle), and at this time, damping is initiated in the direction of the closed position of the movable furniture part 2, and there is a load case v > v Ref existing. In this case, the overlap 16 is 100%. The damping device 1 approximates the reference velocity curve 19 according to the existing velocity difference 22, thereby preventing the risk of collision.

[0119] In FIG. 2e, the pressure situation occurring in the damping device 1 is shown in comparison with the force of the accumulator present. In this case, F0 indicates the accumulator preload of another accumulator 18 in the case of a damping stroke distance x = 0.

[0120] FIG. 3a differs from FIG. 2d in that the damping stroke distance x (indicated by the circle) of 50% of the maximum damping stroke distance x of the damping device 1 is observed. In the region of the overlap 16 (see FIG. 3c) for changing the flow cross-section 17, the accumulator characteristic curve of another accumulator 18 by means of an outlet valve adjusted via an adjustment piston 12 changes as a function of the damping stroke distance x and F0 and F c as a function.

[0121] The speed reference curve 19 is a function of the damping stroke distance x. When the speed difference 22 is relatively small, as a result, the relative sliding of the adjustment piston 12 with respect to the piston 5 starting from the no-load position is relatively small, whereby the overlap 16 is enlarged and the flow cross-section 17 is increased. As a result, the pressure of the damping fluid 4 in the front region 8 is reduced.

[0122] FIG. 3b differs from FIG. 2e in that the pressure situation in the damping device 1 is shown in comparison with the force of the accumulator occurring at a damping stroke distance x of 50%.

[0123] FIG. 3c shows the damping device 1, in which case the damping device 1 is moved in the direction of the closed position of the movable furniture part with respect to FIG. 1a and is in the damping stroke.

[0124] Another accumulator 18 and an accumulator 20 are arranged parallel to each other in the damping stroke direction 23, and another accumulator 18 and an accumulator 20 are arranged coaxially.

[0125] The piston rod 6 is movable relative to the cylinder 3 directly by the movable furniture part 2 via a rotational or swiveling movement. In this case, the piston rod 6, together with the piston 5, performs a linear movement relative to the cylinder 3. In general, an indirect transmission of the movement path of the movable furniture part 2 to the damping device 1 is also conceivable - for example, in the form of a mechanical transmission mechanism with a gradient cam or a joint device.

[0126] The movable furniture part 2 is provided in the form of a furniture flap, but it could also be another form of movable furniture part 2 such as a drawer that performs a linear movement in the direction of the damping device 1.

[0127] In order to assimilate the speed of the piston 5 relative to the cylinder 3 to the speed reference curve 19, the overlap 16 is such that, and thereby, the speed change of the piston 5 relative to the cylinder 3 is continuously changed via the positioning of the adjustment piston 12 relative to the piston 5 during the damping stroke.

[0128] During the damping stroke of the damping device 1, the overlap 16 between the fluid outflow opening 14 and the outlet opening 11 can be changed via the accumulator 20. The speed of the piston 5 relative to the cylinder 3 can be increased by an increase in the overlap 16 and decreased by a decrease in the overlap 16.

[0129] Since the flow-through of the damping fluid 4 is adjusted, the overlap 16 can be automatically reduced and eliminated via the speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, depending on the position of the adjustment piston 12 relative to the piston 5. The speed difference 22 is transmitted to the relative position of the adjustment piston 12 with respect to the piston 5 via another accumulator 18 and by the accumulator 20.

[0130] For example, a method for adjusting the damping speed of the damping device 1 during the damping stroke by the damping device 1 can be implemented as follows: - Move a piston 5 guided within a cylinder 3 and damped by a damping fluid 4 relative to the cylinder 3 by loading a force via a piston rod 6 connected to the piston 5. - The damping fluid 4 flows from a front region 8 of a fluid chamber 7 through an inlet opening 9 of the piston 5 to an outlet opening 11 of the piston 5 facing a rear region 10 of the fluid chamber 7. - An adjustment piston 12 disposed inside the piston 5 automatically slides relative to the piston 5 by means of an accumulator 20. As a result, a fluid outflow opening 14 of the adjustment piston 12 facing the rear region 10 of the fluid chamber 7 is slid relative to the outlet opening 11 of the piston 5, and the speed of the piston 5 relative to the cylinder 3 is assimilated to a linear speed reference curve 19 dependent on another accumulator 18.

[0131] During adjustment of the damping speed of the damping device 1 via the adjustment piston 12, - The speed of the piston 5 relative to the cylinder 3 during the damping stroke can be adjusted by an overlap 16 between the fluid outflow opening 14 and the outlet opening 11. This overlap 16 defines a flow cross-section 17 of the damping fluid 4, and the flow cross-section 17 is continuously changed by the relative position of the adjustment piston 12 with respect to the piston 5 during the damping stroke for changing the speed of the piston 5. - The adjustment piston 12 and the piston 5 can be formed as a pressure equalizer. The overlap 16 between the fluid outflow opening 14 and the outlet opening 11 is decreased when the pressure of the damping fluid 4 with respect to the adjustment piston 12 or in the region of the overlap 16 is increased, and is increased when the pressure with respect to the adjustment piston 12 or in the region of the overlap 16 is decreased. - During the damping stroke of the damping device 1, via the accumulator 20, the overlap 16 between the fluid outflow opening 14 and the outlet opening 11 is changed, and the speed of the piston 5 relative to the cylinder 3 is increased by an enlargement of the overlap 16 and decreased by a reduction of the overlap 16. - The overlap 16 is automatically reduced or eliminated via the speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19. In this case, the speed difference 22 is transmitted by another accumulator 18 or accumulator 20 such that a relative position of the adjusting piston 12 with respect to the piston 5 occurs. - The overlap 16 is automatically changed by the speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, which is transmitted via another accumulator 18 or accumulator 20.

[0132] Figures 4a to 4d show another example of use of the damping device 1 when the speed of the piston 5 relative to the cylinder 3 is lower than the desired speed of the speed reference curve 19 at the current damping stroke distance position x.

[0133] In Figure 4a, the case where the damping stroke distance x = 0 is observed (indicated by a circle), and the speed difference 22 of the piston 5 relative to the speed reference curve 19 is negative. In this case, the overlap 16 is 100%.

[0134] Figure 4b shows the pressure behavior in the fluid chamber 7 and the force behavior of the accumulator 20 as a function of the relative positioning z of the adjusting piston 12 with respect to the piston 5 when the speed difference 22 occurs. In this case, F0 indicates the accumulator preload of another accumulator 18 when the damping stroke distance x = 0.

[0135] In such an arrangement of the parameters and position adjustment of the adjusting piston 12, the damping device 1 does not generate a damping output because the speed difference 22 is negative, whereby the speed of the piston 5 relative to the cylinder approximates the speed reference curve 19 by a speed increase.

[0136] If the overlap 16 is less than 100%, the overlap 16 is increased by the accumulator 20. If the speed difference 22 were positive, the piston speed would be reduced by reducing the overlap 16 via the accumulator 20.

[0137] FIG. 4c is different from FIG. 4a at the point where the damping stroke distance x of 50% of the maximum damping stroke distance x is observed. The speed difference 22 is the reference speed v of the speed reference curve 19 at the - damping stroke distance x, or due to the approximation of the piston speed to the speed reference curve 19 having already been performed. Even if it is reduced, since the speed difference 22 is still negative, the damping output by the damper 1 is not performed. Ref Even if it is reduced by the decrease of, or due to the approximation of the piston speed to the speed reference curve 19 having already been performed, since the speed difference 22 is still negative, the damping output by the damper 1 is not performed.

[0138] FIG. 4d is different from FIG. 4b in that the parameters regarding the pressure, accumulator preload, force of the accumulator, accumulator characteristic line, and the speed of the piston 5 relative to the cylinder 3 are shown when the damping stroke distance x is half.

[0139] FIG. 5a shows a damper 1 for a furniture fitting or a building fitting. This damper includes a cylinder 3 in which a damping fluid 4 is disposed inside, and a piston 5 operable via a piston rod 6. This piston is movable at the speed by the damping fluid 4 during the damping stroke.

[0140] A flow passage 42 having a flow cross-section 17 (penetrating the piston 5 and the adjustment piston 12, and generally, the flow passage 42 also passes near the brake element 25) is provided in the damper 1. Through this flow passage, the damping fluid 4 can pass through the piston 5 during the damping stroke. An adjustment piston 12 is provided to be slidably supported along the piston 5 (or within the piston, see FIGS. 22a - 23b). By the movement of the adjustment piston 12 relative to the piston 5, the flow cross-section 17 of the flow passage 42 can be changed.

[0141] The accumulator 20 is provided in the form of a return spring in the damper 1. This accumulator 20 loads a return force on the adjustment piston 12 relative to the piston 5. This return force counteracts at least one flow force that may be applied to the adjustment piston 12 by the damping fluid 4 during the damping stroke.

[0142] In the control orifice 29, a pressure drop proportional to the flow force and the speed of the piston 5 takes place, and at this time a target speed for the piston 5, which depends on the position of the piston 5 relative to the cylinder 3, is defined. At this time, when the speed of the piston 5 is higher than the target speed, the adjusting piston 12 is movable relative to the piston 5 so that the flow cross-section 17 of the flow passage 42 can be reduced against the return force.

[0143] The damping action is caused by the flow cross-section 17, and the damping device 1 can be automatically deactivated below the target speed. The target speed for the piston 5, which depends on the position of the piston 5 relative to the cylinder 3, is defined by another accumulator 18 (such as the spring 28) that loads a force against the return force on the adjusting piston 12 and by a groove 45 provided on the inner wall 46 of the cylinder, which has a changing groove cross-section. Generally, the target speed may alternatively or additionally be based on the adjustability of the orifice opening 44 of the control orifice 29.

[0144] Figure 5b shows the damping device 1 according to Figure 5a, simply viewed from a different angle.

[0145] Figures 6a and 6b differ from Figures 5a and 5b only in that, in order to adjust the damping output via the position between the piston 5 and the adjusting piston 12, the adjusting piston 12 is slid relative to the piston 5 during the damping stroke, thereby changing the overlap 16 in the flow cross-section 17 of the flow passage 42.

[0146] The adjusting piston 12 is completely arranged outside the piston 5, but may also be arranged inside the piston 5 at least in a predetermined region.

[0147] The adjusting piston 12 exists in the form of an output valve for the piston 5. The flow cross-section 17 of the flow passage 42 can be changed by the adjusting piston 12 via the control orifice 29, thereby adjusting the speed of the piston 5.

[0148] The adjustment piston 12 is preloaded relative to the piston 5 by another accumulator 18 and an accumulator 20, and the piston 5 is loaded with a force for forming a desired speed reference curve by another accumulator 18.

[0149] The flow passage 42 is closed or opened by the adjustment piston 12.

[0150] Fig. 7a shows the damping device 1, in which case the adjustment piston 12 has an opening that can overlap the opening of the piston 5 to enlarge or reduce the flow cross-section 17 of the flow passage 42.

[0151] In Fig. 7b, the damping fluid 4 can flow into the piston 5, while in Figs. 8a and 8b, the flow passage 42 for the damping fluid 4 is closed.

[0152] Generally, the speed of the piston 5 relative to the cylinder 3 during the damping stroke can be adjusted by an overlap 16 at the flow cross-section 17 of the flow passage 42 - for example, between the fluid outflow opening 14 and the outlet opening 11.

[0153] The overlap 16 defines the flow cross-section 17 of the damping fluid 4, which can be changed by the relative position of the adjustment piston 12 with respect to the piston 5. The flow cross-section 17 can also be adjusted by the control orifice 29 or can be used as a control signal for the adjustment piston 12. The overlap 16 and the change in the speed of the piston 5 relative to the cylinder 3 can be continuously changed during the damping stroke.

[0154] The adjustment piston 12 and the piston 5 are formed as a pressure equalizer, and the overlap 16 at the flow cross-section 17 of the flow passage 42 can be decreased when the pressure of the damping fluid 4 in the region of the adjustment piston 12 and the overlap 16 is increased, and can be increased when the pressure in the region of the adjustment piston 12 and the overlap 16 is decreased.

[0155] As shown in FIG. 8b, another accumulator 18 in the form of a spring 28 is provided, which contributes to forming an optionally definable speed reference curve 19 of the damping device 1 at the piston 5 and the adjustment piston 12 inside the cylinder 3.

[0156] During the damping stroke of the damping device 1, via the accumulator 20, the overlap 16 at the flow cross-section 17 of the flow passage 42 can be changed, and the speed of the piston 5 relative to the cylinder 3 can be increased by an increase in the overlap 16 and decreased by a decrease in the overlap 16. The functional relationships of the components are available in all the illustrated embodiments.

[0157] The overlap 16 at the flow cross-section 17 of the flow passage 42 can be automatically reduced or eliminated via the speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19. In this case, the speed difference 22 can be transmitted by another accumulator 18 or the accumulator 20 such that a relative position of the adjustment piston 12 with respect to the piston 5 occurs. The overlap 16 at the flow cross-section 17 of the flow passage 42 can be automatically changed by the speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, which is transmitted via another accumulator 18 and the accumulator 20. The speed of the piston 5 during the damping stroke can be changed by another accumulator 18 and the accumulator 20 via the relative position of the adjustment piston 12 with respect to the piston 5.

[0158] FIG. 9 shows the damping device 1, in which case the damping device 1 includes a magnet 35 formed in the form of a bar magnet as a permanent magnet, whereby, in order to rotate the control orifice 29 with respect to the piston 5 and thereby change the damping output, a changed amount of damping fluid 4 flows through the piston 5 and the adjustment piston 12.

[0159] By means of the magnet 35, the control orifice 29 is rotatable relative to the piston 5. In this case, the magnet 35 is directly arranged on the control orifice 29, and the magnet 35 is rotatable at least via the metal strip 36 in the form of a steel strip arranged on the cylinder 3.

[0160] FIG. 10 is different from FIG. 9 only in that the position of the control orifice 29 is changed relative to the piston.

[0161] Two metal strips 36 connected to each other are twisted and arranged on the cylinder 3.

[0162] The piston 5 includes exactly two flow passages 42. In this case, these flow passages 42 are symmetrically arranged with respect to the end face 30 of the piston 5.

[0163] The control orifice 29 is arranged on the end face 30 of the piston 5, and the piston 5 and the control orifice 29 are formed so as to be longitudinally kinematically connected to each other during the damping stroke and separated from each other in the rotational direction 32 during the damping stroke.

[0164] Due to the rotation of the piston 5 relative to the control orifice 29 and the rotation of the control orifice 29 relative to the piston 5, the flow cross-section 17 can be changed. In this case, the control orifice 29 and the piston 5 are formed to be rotatable relative to each other such that the flow cross-section 17 can be reduced (depending on the longitudinal distance and the speed) and generally can also be enlarged during the damping stroke.

[0165] Figure 11a shows the control orifice 29 in an exploded view and in an assembled state, and Figures 11b to 11d show three different rotational positions of the control orifice 29 transmitted via the -magnet 35. Depending on the degree of rotation of the control orifice 29, the orifice opening 44 is enlarged or reduced along the flow passage 42, whereby the amount or pressure of the inflowing damping fluid 4 can be adapted so that the adjusting piston 12 can be operated to a desired position relative to the piston 5.

[0166] The angle of rotation or the degree of change of the orifice opening 44 can be caused depending on the position and / or depending on the piston speed.

[0167] Figures 12a to 12c differ from Figures 11b to 11d only in that cross-sectional views in three changed flow cross-sections 17 are added.

[0168] Figure 13 shows the damping device 1, which has a spring 28 for loading a force on the piston 5, which is arranged in the control orifice 29, and by means of this spring 28 the control orifice 29 is rotatable relative to the piston 5.

[0169] Generally, the spring 28 may be provided only for loading a force on the piston 5 or only for rotating the control orifice 29, and it has been found that a combined function of another accumulator 18 is particularly suitable for the damping device 1.

[0170] The spring 28 is firmly connected to the control orifice 29, and the control orifice 29 is rotatable via the compression of the spring 28.

[0171] Figure 14 differs from Figure 13 only in that the spring 28 in a compressed position after rotation during the damping stroke is shown.

[0172] Figures 15a and 15b show the piston 5 and the control orifice 29 in two different positions relative to each other. In Figure 15a, there is a flow cross-section 17 of the flow passage 42 for the damping fluid 4. In Figure 15b, the overlap 16 exists such that the damping fluid 4 cannot flow into the adjustment piston 12.

[0173] The rotation of the control orifice 29 can be caused, for example, by a hollow piston rod (not shown) that can rotate the piston 5 relative to the control orifice 29. For example, the hollow piston rod may be directly arranged on the piston 5 or arranged on the cylinder 3 and guided via a twisted slide track.

[0174] Figure 16 shows the damping device 1, which has a telescopic device 39 by which the control orifice 29 can rotate relative to the piston 5.

[0175] Figure 17 differs from Figure 16 only in the positions changed along the damping stroke. In this case, the telescopic device 39 is rotated via a guide 40 twisted along the telescopic device 39 and has a plurality of telescopic members 41 that can telescopically extend and contract relative to each other.

[0176] Figures 18a to 18c show the guide 40 of the telescopic device 39 and the telescopic members 41 in a telescopically extended position, a telescoped position, from the side, in an exploded view, in an assembled position, and in a compressed state, in perspective views.

[0177] Figure 19 shows the control orifice 29 for interacting with the piston 5 of the damping device 1. The damping device 1 has a vane wheel 37 by which the control orifice 29 can rotate relative to the piston 5.

[0178] FIG. 20a shows a damping device 1 equipped with an impeller 37 in a sectional view, and FIG. 20b is different from FIG. 20a only in that the position is changed in the damping stroke direction.

[0179] The impeller 37 is directly arranged in the control orifice 29 and is rotatable through the flow of the damping fluid 4. The impeller 37 has a plurality of blades 38 that can be pushed in the rotational direction by the flow of the damping fluid 4.

[0180] FIGS. 21a and 21b show the damping device 1 equipped with the impeller 37 in sectional views from the side, at the position during the damping stroke and at the position before the damping stroke. In this case, for the sake of clarity, the adjustment piston 12 is not shown.

[0181] In the embodiment according to FIGS. 9 to 21b, the piston 5 and the control orifice 29 are formed such that the piston 5 can rotate relative to the control orifice 29 and the control orifice 29 can rotate relative to the piston 5 through the longitudinal movement of the piston 5 during the damping stroke inside the cylinder 3.

[0182] FIGS. 22a and 22b show a damping device 1 similar to the damping device 1 according to FIGS. 5a to 8b. In this case, the adjustment piston 12 is arranged inside the piston 5 instead of outside the piston 5. Kinematically, by adjusting the overlap 16 between the adjustment piston 12 and the piston 5, a change in the flow passage 42 in the flow cross-section 17 can also be realized in the same way.

[0183] Figures 23a and 23b show the damping device 1 shown in Figures 22a and 22b in a position where the adjusting piston 12 is slid slightly relative to the piston 5. In this case, along the damping stroke, the movement of a movable furniture part (not shown) can be controlled via adjustment of the damping speed by the damping device 1. In this case, if the speed of the movable furniture part 2 relative to the damping device 1 or the speed of the piston 5 relative to the cylinder 3 is higher than the target speed, the adjusting piston 12 is moved relative to the piston 5 against the return force (generated by the accumulator 20) such that the flow cross-section 17 of the flow passage 42 is reduced, and the movable furniture part 2 or the piston 5 is braked to reach the target speed.

[0184] The target speed is defined via the force loading by another accumulator 18 and the position of the control orifice 29 along the cylinder.

[0185] If the speed is lower than the target speed, the damping device 1 is automatically switched off.

[0186] For adjustment of the damping intensity, the adjusting piston 12 is automatically slid relative to the piston 5 via the accumulator 20, whereby the speed of the piston 5 relative to the cylinder 3 is adapted, for example, to a linear or another speed reference curve 19 defined via another accumulator 18. The fluid outflow opening 14 of the adjusting piston 12 can in this case be slid depending on the relative positioning of the adjusting piston 12 and the piston 5 relative to the outlet opening 11 of the piston 5.

[0187] The sealing element 24 of the damping device 1 is formed as a brake element 25 and acts in the flow direction of the damping fluid 4 parallel to the flow passage 42 in the adjusting piston 12. In embodiments with a rotationally controlled control orifice 29, the adjusting piston 12 is generally arranged to act in series with the control orifice 29.

[0188] The damping device 1 is defined by a cylinder 3, a seal element 24, a piston 5 and a piston rod 6 and includes a fluid chamber 7 filled with a damping fluid 4. In this case, the damping device 1 includes a constant volume holding element 26 which constantly holds the volume provided for the damping fluid 4 in the fluid chamber 7 at any position of the piston 5 including the piston rod 6 and which is loaded with force by an additional accumulator 18.

[0189] The adjustment piston 12 is movable translationally relative to the piston 5 and the control orifice 29 during the damping stroke as a function of the longitudinal distance and the speed of the piston 5.

Claims

1. A damping device (1) for furniture fittings or building fittings, comprising a cylinder (3) with a damping fluid (4) arranged therein and a piston (5) operable via a piston rod (6), wherein the piston is movable at a speed by the damping fluid (4) during a damping stroke, and at least one flow passage (42) with a flow cross-section (17) is provided, through which the damping fluid (4) can pass through the piston (5) during the damping stroke. In the damping device (1), at least one adjusting piston (12) is provided, movably, preferably slidably supported within and / or on the piston (5), and by the movement of the at least one adjusting piston (12) relative to the piston (5), the flow cross-section (17) of the at least one flow passage (42) can be changed, and at least one accumulator (20), preferably a return spring, is provided to load a return force on the at least one adjusting piston (12) relative to the piston (5), and the return force counteracts at least one flow force that can be applied to the at least one adjusting piston (12) by the damping fluid (4) during the damping stroke, and at least one control orifice (29) is provided for a pressure drop proportional to the flow force and the speed of the piston (5), and a target speed for the piston (5) is defined depending on the position of the piston (5) relative to the cylinder (3), and the at least one adjusting piston (12) is movable relative to the piston (5) such that the flow cross-section (17) of the at least one flow passage (42) can be reduced against the return force when the speed of the piston (5) is higher than the target speed, and preferably, the target speed for the piston (5) depends on - at least one another accumulator (18), particularly preferably a spring (28), loading a force against the return force on the at least one adjusting piston (12), and / or - by the adjustability of the orifice opening (44) of the at least one control orifice (29), and / or - at least one groove (45) provided in the cylinder inner wall (46) with a changing groove cross-section, characterized in that it is defined, damping device (1). **Claim 2** The at least one adjustment piston (12) is arranged outside the piston (5) and / or inside the piston (5), and / or exists in the form of an output valve of the piston (5), preferably via the at least one control orifice (29) and / or by the at least one adjustment piston (12), the flow cross-section (17) of the at least one flow passage (42) can be changed, whereby the speed of the piston (5) can be adjusted, the damping device (1) according to claim 1. **Claim 3** The at least one adjustment piston (12) is preloaded relative to the piston (5) by at least one another accumulator (18) and / or the at least one accumulator (20), and / or a force can be applied to the piston (5) by at least one another accumulator (18), the damping device (1) according to claim 1 or 2. **Claim 4** The piston (5) includes at least one inlet opening (9) facing the front region (8) of the fluid chamber (7) arranged on the side of the piston (5) opposite to the piston rod (6), and at least one outlet opening (11) facing the rear region (10) of the fluid chamber (7) arranged on the side of the piston (5) facing the piston rod (6), the at least one adjustment piston (12) includes at least one fluid inlet opening (13) facing the front region (8) of the fluid chamber (7) and at least one fluid outlet opening (14) facing the rear region (10) of the fluid chamber (7), the damping fluid (4) can flow through the at least one fluid outlet opening (14) and the at least one outlet opening (11) from the front region (8) of the fluid chamber (7) into the rear region (10) of the fluid chamber (7) during the damping stroke of the damping device (1), the damping device (1) according to any one of claims 1 to 3. **Claim 5** The at least one adjustment piston (12) is arranged completely inside or completely outside the piston (5), and preferably, at least one stopper (15) for the at least one adjustment piston (12) is arranged on the piston (5), preferably facing the front region (8). The damping device (1) according to any one of claims 1 to 4, wherein it is specified that

6. The speed of the piston (5) relative to the cylinder (3) during the damping stroke is adjustable by an overlap (16) in the flow cross-section (17) of the at least one flow passage (42), preferably by an overlap (16) between a fluid outflow opening (14) that may be present and an outlet opening (11) that may be present in some cases. Preferably, the overlap (16) defines the flow cross-section (17) of the damping fluid (4), and / or it is specified that the flow cross-section (17) can be changed by the relative position of the at least one adjustment piston (12) with respect to the piston (5). The damping device (1) according to any one of claims 1 to 5, wherein

7. The overlap (16), and / or the change in the speed of the piston (5) relative to the cylinder (3) can be continuously changed during the damping stroke. The damping device (1) according to claim 6, wherein

8. The at least one adjustment piston (12) and the piston (5) are formed as a pressure equalizer. The overlap (16) in the flow cross-section (17) of the at least one flow passage (42), preferably the overlap (16) between a fluid outflow opening (14) that may be present and an outlet opening (11) that may be present in some cases, can be decreased when the pressure of the damping fluid (4) in the region of the at least one adjustment piston (12) and / or in the region of the overlap (16) is increased, and / or can be increased when the pressure in the region of the at least one adjustment piston (12) and / or in the region of the overlap (16) is decreased. The damping device (1) according to any one of claims 1 to 7, wherein

9. At least one further energy storage device (18), preferably a spring (28), is provided, said energy storage device being arranged inside the cylinder (3) on the piston (5) and / or on said at least one adjusting piston (12) in order to form a preferably linear speed reference curve (19) of said damping device (1), damping device (1) according to any one of claims 1 to 8.

10. Said at least one energy storage device (20), preferably a spring, is provided and is arranged inside the piston (5) and / or on the piston (5) and on said at least one adjusting piston (12), preferably, said at least one energy storage device (20) acts between the piston (5) and the cylinder end face (21) of said at least one adjusting piston (12) and / or it has been determined that said at least one further energy storage device (18) acts between the piston (5) and the inner wall (46) of the cylinder, damping device (1) according to any one of claims 1 to 9.

11. During the damping stroke of said damping device (1), via said at least one energy storage device (20), the overlap (16) at the flow cross-section (17) of said at least one flow passage (42), preferably the overlap (16) between a fluid outflow opening (14) which may be present in some cases and an outlet opening (11) which may be present in some cases, can be changed, the speed of said piston (5) relative to the cylinder (3) can be increased by an increase in said overlap (16) and / or can be decreased by a decrease in said overlap (16), damping device (1) according to any one of claims 1 to 10.

12. The overlap (16) at the flow cross-section (17) of said at least one flow passage (42) can be automatically reduced or cancelled via a speed difference (22) of said piston (5) relative to the cylinder (3) relative to the speed reference curve (19), said speed difference (22) can be transmitted by means of at least one further energy storage device (18) which may be present in some cases and / or said at least one energy storage device (20) such that a relative position of said at least one adjusting piston (12) relative to the piston (5) occurs, damping device (1) according to any one of claims 1 to 11.

13. The overlap (16) in the flow cross-section (17) of the at least one flow passage (42) is automatically variable by a velocity difference (22) relative to a velocity reference curve (19) of the piston (5) relative to the cylinder (3), which is transmitted via at least one further accumulator (18) which may be present and / or the at least one accumulator (20), of the damping device (1) according to any one of claims 1 to 12.

14. The velocity of the piston (5) during the damping stroke is variable by the relative position of the at least one adjusting piston (12) relative to the piston (5) and by at least one further accumulator (18) which may be present and / or the at least one accumulator (20) of the damping device (1) according to any one of claims 1 to 13.

15. The at least one further accumulator (18) and the at least one accumulator (20) are preferably arranged parallel to one another in the direction of the damping stroke (23), and in particular it is specified that the at least one further accumulator (18) and the at least one accumulator (20) are arranged coaxially, of the damping device (1) according to any one of claims 1 to 14.

16. The at least one piston rod (6) is movable relative to the cylinder (3) directly or indirectly by the movable furniture part (2), preferably via a linear movement, a rotational movement and / or a swivelling movement, of the damping device (1) according to any one of claims 1 to 15.

17. The damping device (1) has a sealing element (24) through which the piston rod (6) is movable, and the sealing element (24) - is formed as a brake element (25) and / or - acts parallel to the at least one flow passage (42) and / or the at least one control orifice (29) in the flow direction of the damping fluid (4) and / or - acts in series with the at least one flow passage (42) and / or the at least one control orifice (29) in the flow direction of the damping fluid (4), of the damping device (1) according to any one of claims 1 to 16.

18. The damping device (1) includes a fluid chamber (7) filled with a damping fluid (4), and the fluid chamber is defined at least by the cylinder (3), optionally an existing sealing element (24), the piston (5), and / or the piston rod (6). The damping device (1) according to any one of claims 1 to 17.

19. The damping device (1) includes a constant volume holding element (26) that keeps the volume provided for the damping fluid (4) in the fluid chamber (7) constant at any position of the piston (5) including the piston rod (6), and / or the sealing element (24) forms the constant volume holding element (26) together, is movable relative to the cylinder (3), and is loaded with a force on the side opposite to the fluid chamber, preferably by another accumulator (18) that may exist in some cases. The damping device (1) according to claims 17 and 18.

20. The at least one adjustment piston (12) is translatable relative to the piston (5) and / or the at least one control orifice (29) during the damping stroke, preferably in accordance with the longitudinal distance and / or speed of the piston (5). The damping device (1) according to any one of claims 1 to 19.

21. The piston (5) and / or the at least one control orifice (29) are formed such that the piston (5) is rotatable relative to the at least one control orifice (29) and / or the at least one control orifice (29) is rotatable relative to the piston (5) through the longitudinal movement of the piston (5) inside the cylinder (3) during the damping stroke. The damping device (1) according to any one of claims 1 to 20.

22. - The piston (5) includes at least two, preferably exactly two flow passages (42), and preferably, the at least two flow passages (42) are specifically arranged symmetrically with respect to the end face (30) of the piston (5), and / or - the at least one flow passage (42) is arranged on the end face (30) of the piston (5) and / or the at least one control orifice (29) is arranged on the end face (30) of the piston (5) and / or - the piston (5) and the at least one control orifice (29) are formed so as to be longitudinally kinematically connected to each other during the damping stroke and / or to be separated from each other in the rotational direction (32) during the damping stroke and / or - the flow cross-section (17) can be changed by rotation of the piston (5) relative to the at least one control orifice (29) and / or by rotation of the at least one control orifice (29) relative to the piston (5) and / or - the at least one control orifice (29) and the piston (5) are formed to be rotatable relative to each other such that during the damping stroke, the flow cross-section (17) can preferably be reduced according to the longitudinal distance of the piston (5) and / or according to the speed, The damping device (1) according to claim 21.

23. The damping device (1) has a hollow piston rod that can rotate the piston (5) relative to the at least one control orifice (29), preferably the hollow piston rod is particularly preferably arranged directly on the piston (5) and / or the hollow piston rod is particularly preferably arranged on the cylinder (3) and / or is specified to be guided via a twisted slide track. The damping device (1) according to claim 21 or 22.

24. The damping device (1) has a magnet (35) that can rotate the at least one control orifice (29) relative to the piston (5), preferably a bar magnet and / or a permanent magnet. Preferably, the magnet (35) is particularly preferably arranged directly on the at least one control orifice (29) and / or the magnet (35) is particularly preferably rotatable via at least one metal strip (36) arranged on the cylinder (3), particularly preferably a steel strip. The damping device (1) according to any one of claims 21 to 23.

25. The damping device (1) according to claim 24, wherein at least two metal strips (36) are provided and / or at least one of the metal strips (36) is twisted and arranged on the cylinder (3).

26. The damping device (1) has a spring (28) for loading a force on the piston (5), which is arranged in the at least one control orifice (29), and the at least one control orifice (29) is rotatable relative to the piston (5) by the spring (28). Preferably, the spring (28) is firmly coupled to the at least one control orifice (29) and / or the at least one control orifice (29) is specified to be rotatable via compression of the spring (28). The damping device (1) according to any one of claims 21 to 25.

27. The damping device (1) has a turbine (37) capable of rotating the at least one control orifice (29) relative to the piston (5). Preferably, the turbine (37) is particularly preferably arranged directly on the at least one control orifice (29) and / or is rotatable via the flow of the damping fluid (4), and / or is specified to have at least two, particularly preferably four blades (38). The damping device (1) according to any one of claims 21 to 26.

28. The damping device (1) has at least one telescopic device (39) capable of rotating the at least one control orifice (29) relative to the piston (5). Preferably, the at least one telescopic device (39) is particularly preferably twisted and / or rotatable via a guide (40) arranged on the cylinder (3), and / or is specified to have a plurality of telescopic members (41) that can expand and contract inwardly and outwardly and / or relative to each other. The damping device (1) according to any one of claims 21 to 27.

29. The at least one adjustment piston (12) of the damping device (1) according to any one of claims 1 to 28 acts parallel to and / or in series with an optionally present sealing element (24) and / or the at least one control orifice (29).

30. A method of controlling the movement of a movable furniture part (2) by adjusting a damping rate by means of at least one damping device (1) according to any one of claims 1 to 29, wherein when the speed of the movable furniture part (2) relative to the at least one damping device (1) and / or the speed of the piston (5) relative to the cylinder (3) is higher than a target speed, at least one adjustment piston (12) is moved relative to the piston (5) against the return force, and the flow cross-section (17) of at least one flow passage (42) is reduced so that the movable furniture part (2) and / or the piston (5) is braked to reach the target speed, and in particular, when the speed is lower than the target speed, it is specified that the at least one damping device (1) is inoperative. Method, characterized in that.

31. The at least one adjustment piston (12) slides relative to at least one of the pistons (5) in particular automatically via at least one accumulator (20), whereby the speed of the piston (5) relative to the cylinder (3) is preferably linear and / or assimilated to a speed reference curve (19) defined via at least one further accumulator (18), and preferably at least one fluid outflow opening (14) of the at least one adjustment piston (12) is specified to be slid relative to at least one outlet opening (11) of the piston (5). The method according to claim 30.

32. - Adjust the speed of the piston (5) relative to the cylinder (3) during the damping stroke by means of an overlap (16) in the flow cross-section (17) of at least one of the flow passages (42), preferably by means of an overlap (16) between at least one fluid outflow opening (14) which may be present and at least one outlet opening (11) which may be present, said overlap (16) defining the flow cross-section (17) of the damping fluid (4), and / or said flow cross-section (17) being changed by the relative position of at least one adjusting piston (12) with respect to the piston (5), - Continuously change the overlap (16) and / or the change in the speed of the piston (5) relative to the cylinder (3) during the damping stroke, - The at least one adjusting piston (12) and the piston (5) are formed as a pressure equalizer, and the overlap (16) in the flow cross-section (17) of the at least one flow passage (42) is decreased when the pressure of the damping fluid (4) with respect to the at least one adjusting piston (12) and / or in the region of the overlap (16) is increased, and / or increased when the pressure with respect to the at least one adjusting piston (12) and / or in the region of the overlap (16) is decreased, - During the damping stroke of the damping device (1), change the overlap (16) in the flow cross-section (17) of the at least one flow passage (42) by means of the at least one accumulator (20), and increase the speed of the piston (5) relative to the cylinder (3) by an enlargement of the overlap (16), and / or decrease it by a reduction of the overlap (16), - The overlap (16) in the flow cross-section (17) of the at least one flow passage (42) is automatically reduced or eliminated via a speed difference (22) of the piston (5) relative to the cylinder (3) relative to a speed reference curve (19), the speed difference (22) being transmitted, optionally via at least one further accumulator (18) and / or the at least one accumulator (20) which may be present, such that a relative position of the at least one adjusting piston (12) relative to the piston (5) results, and / or - the overlap (16) is automatically changed by a speed difference (22) of the piston (5) relative to the cylinder (3) relative to a speed reference curve (19), which is transmitted via at least one further accumulator (18) and / or the at least one accumulator (20) which may be present. The method according to claim 30 or 31.

33. Use of the damping device (1) according to any one of claims 1 to 29 in a movable furniture part (2), a door and / or a window.

34. Furniture comprising at least one damping device (1) according to any one of claims 1 to 29, wherein at least one movable furniture part (2) is damped between an open position and a closed position relative to a furniture cabinet by the at least one damping device (1).

35. A door comprising at least one damping device (1) according to any one of claims 1 to 29, wherein the door is damped between an open position and a closed position relative to a door frame by the at least one damping device (1).

36. A window comprising at least one damping device (1) according to any one of claims 1 to 29, wherein the window is damped between an open position and a closed position relative to a window frame by the at least one damping device (1).

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