Damper device for furniture or building fittings

Abstract

The invention relates to a damping device (1) for furniture or building fittings, comprising a cylinder (3), in which a damping fluid (4) is arranged, and a piston (5), which can be actuated by means of a piston rod (6) and can be moved at a speed through the damping fluid (4) during a damping stroke, in which at least one flow channel (42) having a through-flow cross-section (17) is provided, the damping fluid (4) can pass through the piston (5) through a flow cross section during a damping stroke, at least one adjusting piston (12) is provided, which is mounted in and / or on the piston (5) in a movable, preferably displaceable manner, and a flow cross section (17) of the at least one flow channel (42) can be changed by a movement of the at least one adjusting piston (12) relative to the piston (5), wherein at least one force accumulator (20), preferably a return spring, is provided, which applies a return force to the at least one actuating piston (12) against the piston (5), which return force counteracts at least one flow force, which can be applied to the at least one actuating piston (12) by means of the damping fluid (4) during a damping stroke, and wherein at least one control diaphragm (29) is provided, a pressure drop proportional to the flow force and to the speed of the piston (5) is achieved at the control plate, a target speed dependent on the position of the piston (5) relative to the cylinder (3) is specified for the piston (5), and when the speed of the piston (5) is greater than the target speed, at least one adjusting piston (12) can be moved relative to the piston (5) against a restoring force, a flow cross-section (17) of the at least one flow channel (42) can be made smaller.

Description

Technical Field

[0001] The invention relates to a damping device according to the preamble of claim 1. The invention also relates to a method for controlling the movement of a movable furniture part by adjusting the damping speed by at least one such damping device. The invention also relates to the use of such a damping device and to furniture, doors and windows having at least one such damping device. Background Art

[0002] DE 20 2011 108 658 U1 already discloses a damping device which utilizes a volume constant-keeping element in the form of a floating seal with a groove control device in the return flow region of the damping fluid in order to achieve a groove design adapted to the volume change caused by the sealing element and uniform damping properties.

[0003] A disadvantage of the prior art is that the damping device cannot be adjusted flexibly to the changing actual conditions of the furniture, since different sizes of the movable furniture parts, different movement paths and / or movement processes lead to varying damping properties. In particular, the damping device must be individually adjusted to each specific requirement in use and each specific piece of furniture by means of the structural design, for example the geometry of the groove. Since the damping device always adjusts the speed of the movable furniture part to zero, a constant damping behavior does not result in different movable furniture parts and / or when the speed of the movable furniture parts changes, since the damping device is size-dependent (and / or speed-dependent) to the movable furniture part. Summary of the invention

[0004] The objective technical object of the present invention is therefore to provide a damping device and a method for controlling the movement of a movable furniture part which are improved compared to the prior art, wherein the disadvantages of the prior art are at least partially eliminated and which are characterized in particular by a constant damping behavior or constant damping characteristics, regardless of the size and / or speed of the movable furniture part.

[0005] This object is achieved by the features of claim 1 .

[0006] According to the present invention, at least one regulating piston is provided, which is movably, preferably displaceably supported in and / or on the piston, wherein the flow cross section of at least one flow channel can be changed by the movement of the at least one regulating piston relative to the piston, wherein at least one force accumulator, preferably a return spring, is provided, which applies a return force to the at least one regulating piston relative to the piston, the return force counteracting at least one flow force, which can be applied to the at least one regulating piston by the damping fluid during the damping stroke, wherein at least one control diaphragm is provided, at which a pressure drop is achieved that is proportional to the flow force and the speed of the piston, wherein a rated speed is preset for the piston that is related to the position of the piston relative to the cylinder, wherein when the speed of the piston is greater than the rated speed, the at least one regulating piston can move relative to the piston against the return force so that the flow cross section of the at least one flow channel can be reduced, wherein it is preferably provided that the rated speed for the piston that is related to the position of the piston relative to the cylinder

[0007] - presetting by at least one further force accumulator, particularly preferably a spring, which acts on the at least one control piston against a restoring force, and / or

[0008] - presetting by means of the adjustability of the partition opening of at least one control partition, and / or

[0009] The provision is made by at least one groove in the inner wall of the cylinder having a varying groove cross section.

[0010] It is thus possible that the damping device comprises an automatic adjustment by means of the at least one adjusting piston, which is caused in particular by a pressure profile and / or a force profile and / or is triggered by a control signal for the at least one adjusting piston at the at least one control plate and / or at the at least one brake element, by means of which adjustment a stronger or weaker damping effect can be produced individually depending on the force acting on the piston rod, which damping effect leads to a particularly coordinated damping operation of the movable furniture part even if the forces acting on the movable furniture part and / or the damping device vary greatly. The speed of the movable furniture part thus constantly or continuously approaches a desired speed characteristic, which is defined, for example, by at least one additional force accumulator acting between the cylinder and the piston, wherein this is independent of the mass of the movable furniture part and / or the force transmission to the damping device via the tensioning mechanism.

[0011] Furthermore, in particular in the case of changes in the piston speed and / or in the size of the movable furniture part, an adaptation to an (arbitrarily defined) desired speed profile of the damping device can be achieved in the sense of a uniform damping characteristic or a constant damping behavior.

[0012] Thus, at a changing piston speed relative to the cylinder, the differential speed can be automatically adapted to the desired speed characteristic curve of the piston relative to the cylinder, so as to ensure that the same and / or coordinated damping force is maintained during the damping stroke, both when the piston speed is too high and when it is unexpectedly low.

[0013] Particularly preferably, the damping is adjusted in a speed-dependent manner on the piston relative to the cylinder, wherein, alternatively or additionally, a displacement-dependent adjustment can also be provided in order in particular to automatically adapt the damping behavior to changing dimensions and / or speeds of the movable part.

[0014] When the speed of the piston or the movable furniture part (or window or door) falls below the rated speed defined by the structural design of the buffer device, the buffer device can automatically switch to an inactive state so that no braking of the piston and / or the movable furniture part is performed until the speed increases above the rated speed.

[0015] Furthermore, the speed reference curve can be adapted both in the case of excessively high and low piston speeds, thereby ensuring that the operation of furniture with such a damping device is particularly user-friendly by means of coordinated and identical motion sequences.

[0016] In addition, the damping device can be used in a wider range of movable furniture parts without structural modifications. For example, the damping device according to the invention can be used for a wider power range and / or can be flexibly adapted to new demand ranges by suitable selection of the force accumulator in the damping device.

[0017] Furthermore, the damping device exhibits a more favorable crash behavior, wherein damage to components is particularly effectively suppressed, since in the closed position region of the movable furniture part, when a desired reference speed of the piston relative to the cylinder is reached, there is substantially no damping power, and / or the collision region of the damping device is usually arranged at a safe distance from the operating region of the damping device. Damage can thus be prevented or suppressed even in the event of erroneous operation of the furniture. Furthermore, the damping device makes the tensioning time from the at least partially open position of the movable furniture part to the closed position of the movable furniture part more constant, since below a reference speed of the piston relative to the cylinder, the damping device produces substantially no damping, and the movable furniture part can therefore compensate for the available time in the temporal progression of the movement of the movable furniture part.

[0018] Furthermore, in the case of an assembly consisting of at least one damping device and a tensioning device, the tensioning force of the tensioning device can be reduced, thereby improving the tactile feel for a user of the assembly.

[0019] The flow of damping fluid through the piston inlet is dependent on the speed of the piston relative to the cylinder and generates a pressure drop in the front region. This pressure drop can be converted into a movement of at least one regulating piston by means of a pressure balance, for example, wherein the spring prestress of at least one further force accumulator that loads the piston can be used as a reference speed. Depending on the position of the at least one regulating piston along the movement displacement of the at least one regulating piston relative to the piston, a power valve can be obtained that determines the flow cross section of the damping fluid flowing through the outlet of the piston.

[0020] Depending on the flow cross section, a pressure of the damping fluid is generated in the front region, wherein this pressure determines the damping force and thus the damping performance of the damping device.

[0021] In other words, via a force / pressure ratio (which is determined by the amount of fluid flowing through at least one control diaphragm, a spring force, etc.), a control signal can be obtained for a power signal at at least one power valve in the form of a regulating piston that interacts with a piston (arranged on the outside or inside) (for example, via a fluid flow through a braking element and / or at least one control diaphragm), wherein a change in the flow cross-section is generated, for example, by an overlap or a change in the cross-section of at least one flow channel.

[0022] Advantageous properties are also that the damping device can be designed compactly by means of the at least one adjusting piston, has a particularly long service life while remaining low-maintenance, can be flexibly adapted to different requirements, does not require complex components and is economically viable and allows user-friendly assembly.

[0023] The advantage of this design is that the damping capacity is achieved by the at least one adjusting piston in the sense of a controlled throttle (function of speed or pressure difference), in contrast to a pure position dependency of the piston in the cylinder (e.g., achieved by a groove in the damper) and a pure speed dependency of the piston in the cylinder (e.g., achieved by a throttle that interacts with the piston). The speed dependency of the damping capacity can be dependent on the position of the at least one adjusting piston in the cylinder, whereby the speed characteristic can be changed as a function of the displacement of the at least one adjusting piston. If an increased pressure is present, the damping force acts in such a way that a further reduced pressure is present. The speed dependency can be converted into a pressure dependency, wherein the piston speed can result in a cross section being obtained by the at least one adjusting piston, which cross section is variable. Preferably, a pressure-dependent control diaphragm is taken into account and / or a displacement-dependent reaction force is generated.

[0024] The power valve can usually be implemented in parallel and / or in series with at least one control diaphragm and / or brake element. Usually, the outlet opening and / or the inlet opening or the flow cross section can involve at least one regulating piston, at least one control diaphragm and / or piston (in the sense of kinematic reversal).

[0025] As mentioned at the outset, protection is also claimed for a method for controlling the movement of a movable furniture part by adjusting a damping speed with the aid of at least one damping device according to any of the preceding claims, characterized in that, when a speed of the movable furniture part relative to at least one damping device and / or a speed of the piston relative to the cylinder is greater than a rated speed, the at least one regulating piston is moved relative to the piston against a restoring force in such a way that a flow cross section of the at least one flow channel is reduced and the movable furniture part and / or the piston is braked to a rated speed, wherein, in particular, it is provided that the at least one damping device is inactive at a speed less than the rated speed.

[0026] The basic idea of ​​the invention is to adjust a predefined desired speed characteristic curve of the damping device as a function of the damping travel of the movable furniture part. This can be achieved in that the damping device generates a damping force as a function of the speed difference from the desired speed characteristic curve, wherein the desired speed characteristic curve particularly preferably constitutes a linear speed curve with a constant slope. In other words, it can be ensured that the damping device automatically and / or continuously approaches or adapts to the predefined speed characteristic curve. If the speed difference is negative, so that the current speed of the piston relative to the cylinder is below the desired speed, the damping device can prevent the damping force.

[0027] For example, the at least one regulating piston can be moved against the force applied by the at least one further force accumulator (caused by the pressure of the damping fluid on the at least one regulating piston) into a relative position relative to the piston in which the damping fluid can flow through the piston substantially without resistance. A maximum damping effect with respect to the damping stroke section can be achieved in a relative position in which there is no overlap between the at least one fluid discharge opening and the at least one outlet, so that the movement of the piston in the cylinder is determined solely by the compressibility of the damping fluid.

[0028] In the context of the present invention, an overlap is to be understood as an overlap of the discharge area of ​​at least one fluid discharge opening of at least one regulating piston with the entry area of ​​at least one outlet of the piston (or vice versa), which defines the flow cross section of the damping fluid between the at least one regulating piston and the piston. However, the cross section of the fluid discharge opening and / or the outlet can vary from the entry area of ​​the at least one fluid discharge opening or up to the discharge area of ​​the at least one outlet, wherein this can be controlled by the specifically present pressure behavior of the damping device in the regulation by the positioning of the at least one regulating piston relative to the piston. The cross section of the discharge area of ​​the at least one fluid discharge opening and the cross section of the entry area of ​​the at least one outlet can generally be different; however, it is particularly preferred that they are designed to be of the same size and / or are constructed in the form of cylindrical openings or holes.

[0029] The damping fluid can generally be present in gaseous and / or liquid form, wherein particularly preferably the damping fluid is used in the liquid phase. The damping device can be designed as a pneumatic and / or hydraulic device.

[0030] At least one control diaphragm and / or at least one regulating piston can have a fixed, position-dependent and / or speed-dependent flow cross section. For example, the flow cross section can be adjusted by rotating at least one control diaphragm relative to the piston.

[0031] As mentioned at the outset, protection is also claimed for the use of such a damping device in movable furniture parts, doors and / or windows.

[0032] As mentioned at the outset, protection is also claimed for a piece of furniture having at least one such damping device, wherein at least one movable furniture part can be damped relative to the furniture carcass between an open position and a closed position by means of the at least one damping device.

[0033] As mentioned at the outset, protection is also claimed for a door having at least one such damping device, wherein the door can be damped relative to the door frame between an open position and a closed position by means of the at least one damping device.

[0034] As mentioned at the outset, protection is also claimed for a window having at least one such damping device, wherein the window can be damped relative to the window frame between an open position and a closed position by means of the at least one damping device.

[0035] Generally, the damping effect can act towards the closed position and / or towards the open position. The damping device offers the advantage that a damping stroke can be obtained over a large angular range of the component to be damped. Conventional damping devices are designed for damping an area not long in front of the closed position within a range of about 20°. In contrast, the damping device according to the invention can damp an angular range of more than 90°, wherein the increased forces required for moving the component can be reduced, in particular by interaction between at least one control partition and at least one flow channel, and / or the damping device can be rendered essentially inactive by means of a damping cross section. As a result, the user of the component generally preferably does not have to operate the damping device within a defined angular range, wherein the area in front of the closed position can preferably be effectively damped depending on the speed of the piston.

[0036] Advantageous embodiments of the invention are defined in the dependent claims.

[0037] It is particularly preferred that at least one regulating piston is arranged on the outside of the piston and / or is arranged inside the piston and / or exists in the form of a power valve of the piston, wherein it is preferably provided that the flow cross-section of at least one flow channel can be changed by at least one control partition and / or by at least one regulating piston, so that the speed of the piston can be adjusted.

[0038] The at least one regulating piston is movable in translation relative to the piston and / or is actuated by at least one control plate which is movable in translation and / or rotation relative to the cylinder.

[0039] In a preferred embodiment of the invention, it is provided that at least one control piston is preloaded relative to the piston by at least one further force accumulator and / or at least one force accumulator is preloaded relative to the piston and / or the piston can be acted upon by force by at least one further force accumulator.

[0040] By means of at least one further force accumulator, a speed reference curve for a desired setpoint speed curve of the piston and / or the movable furniture part can be adjusted by means of the force relationships acting on the piston. Alternatively or additionally, the speed reference curve can also be adapted in another way, for example by means of a position-dependent groove cross section in the cylinder or a spring constant of a force accumulator interacting with the at least one adjusting piston.

[0041] It is preferably provided that the piston includes at least one inlet facing a front area of ​​the fluid chamber, the front area being arranged on the side of the piston facing away from the piston rod, and the piston includes at least one outlet facing a rear area of ​​the fluid chamber, the rear area being arranged on the side of the piston facing the piston rod, wherein at least one regulating piston includes at least one fluid inlet opening facing the front area of ​​the fluid chamber and at least one fluid outlet opening facing the rear area of ​​the fluid chamber, wherein, during the buffer stroke of the buffer device, the buffer fluid can flow from the front area of ​​the fluid chamber through the at least one fluid outlet opening and the at least one outlet to the rear area of ​​the fluid chamber.

[0042] By changing the positioning of the piston and / or at least one adjusting piston in the cylinder, the inlet opening and the outlet opening can usually be exchanged. It is usually relevant here that the fluid flow in the throughflow cross section of at least one flow channel is regulated by a differential speed, in particular by the interaction between at least one adjusting piston and at least one control partition.

[0043] According to an advantageous embodiment of the invention, the at least one regulating piston is arranged completely inside or completely outside the piston, wherein preferably at least one stop for the at least one regulating piston is arranged on the piston, preferably toward the front region.

[0044] Arrangement completely inside the piston facilitates a compact damping device, wherein, particularly advantageously, a relative pressure difference between the exterior of the piston and / or the exterior of the at least one regulating piston can be used to adjust the relative positioning of the at least one regulating piston relative to the piston. In the case of arrangement completely outside the piston, a particularly advantageous force transmission can be achieved in order to bring about an overlap of the openings along the flow cross section that is required for a desired speed of the piston.

[0045] The at least one stop ensures that the at least one adjusting piston does not come out of the piston unintentionally and / or limits the movement displacement of the at least one adjusting piston relative to the piston. For example, the at least one stop can be arranged on the piston in a displaceable and / or rotatable manner to simplify the assembly of the at least one adjusting piston. However, a stop that is materially connected to the piston is also conceivable.

[0046] Typically, at least one regulating piston can also be arranged locally on the outside / inside of the piston. Displacement-dependent grooves, such as flow grooves, are also conceivable. For example, a reduced / increased flow cross section for a reduced / increased damping power can be generated by rotation or compression.

[0047] Advantageously, it is provided that the speed of the piston relative to the cylinder during the damping stroke can be adjusted by an overlap in the flow cross-section of at least one flow channel, preferably an overlap of a possible fluid discharge opening and a possible outlet, wherein it is preferably provided that the overlap limits the flow cross-section of the damping fluid and / or the flow cross-section can be changed by the relative position of at least one adjusting piston relative to the piston.

[0048] The overlap and the resulting flow cross section of the damping fluid (typically, for example, from the front area to the rear area of ​​the fluid chamber) can define a power valve that enables automatic and continuous variation of the damping force and / or the speed of the piston relative to the cylinder in order to adjust the damping device.

[0049] It has proven to be advantageous if the overlap and / or the speed change of the piston relative to the cylinder can be varied continuously during the damping stroke.

[0050] According to an advantageous embodiment of the invention, at least one regulating piston and the piston are constructed as a pressure balance, wherein the overlap on the flow cross section of at least one flow channel, preferably the overlap of a possible fluid outlet opening and a possible outlet, can be reduced when the buffer fluid pressure on at least one regulating piston and / or in the overlapping area increases, and / or can be increased when the pressure on at least one regulating piston (12) and / or in the overlapping area decreases.

[0051] The embodiment as a pressure balance provides a particularly effective means of adjusting the damping properties, wherein a particularly compact damping device can be ensured and / or no complex components are required.

[0052] In order to ensure a constant speed, the excess delivery flow can be conducted, for example, via an adjustable measuring diaphragm to which a pressure balance is connected downstream and / or with a bypass non-return valve, which is arranged on a pressure balance slider, wherein the volume flow causes the pressure balance slider to move in the direction of the outlet. The task of the pressure balance is to keep the difference between the pressures existing before and after the measuring diaphragm at a constant level preset by a spring force, so that a constant volume flow can be generated at the outlet. The pressure existing before the throttling point acts on the end side of the pressure balance slider, and the pressure at the outlet acts on its back side. By means of a continuously performed force balance, the position of the pressure balance is changed with each pressure fluctuation before or after the measuring diaphragm, wherein the volume flow cross section at the outlet is reduced or enlarged. Starting from the inlet, the flow through to the outlet can be carried out with low losses in the sense of a non-return valve.

[0053] The pressure balance may include the following tasks, that is, to keep the volume flow constant as much as possible independent of pressure and / or temperature. The volume flow may be constant and related to the volume flow cross section of the throttling diaphragm. The pressure balance may be used for input and / or output control. Typically, the throttling diaphragm may be arranged in combination with the pressure balance and a spring, wherein throttling may be performed on the throttling cross section from the inlet toward the outlet direction. In order to keep the volume flow constant independent of pressure, the pressure balance may include a control edge, which is arranged downstream of the throttling diaphragm. The pressure balance may be moved by a spring. If the pressure balance is flowed through, the input pressure acts on the pressure balance and moves it. Here, the volume flow cross section at the control edge of the pressure balance is reduced, and the pressure difference at the throttling diaphragm may be kept constant as a result. When there is a force balance, the movement of the pressure balance may stop. The pressure balance may continuously compare the pressure difference on the throttling diaphragm with the value given by the spring parameter and / or prestress. By continuous readjustment, a constant volume flow may be achieved. Usually, an adjusting device, such as an adjusting screw, can be provided, by which the amount of the volume flow can be varied within adjustable limits. The volume flow starting from the outlet in the direction of the inlet can depend on the cross section of the throttling diaphragm, wherein the function of the pressure balance can be switched off in this case. The pressure balance can be connected upstream and / or downstream of the throttling diaphragm.

[0054] The volume flow valve can be used as a pressure balance, wherein the pressure balance is designed to be displacement-dependent, thereby forming a displacement-dependent reference speed. In contrast to a damping device whose goal is to damp to a speed that no longer exists, a damping device is thus achieved that damps to a desired reference speed.

[0055] The pressure balance can be implemented in such a way that the piston is preloaded with a first spring force by at least one further accumulator and at least one regulating piston is preloaded with a further spring force by at least one accumulator and that in the event of a pressure drop (caused by 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 regulating piston), the first spring force and the second spring force remain in constant balance. As a result, a specific position of the regulating piston is generated based on the defined further spring force. Since the volume flow of the buffer fluid, which can be related to the speed of the piston relative to the cylinder, is proportional to the pressure drop, the position of the at least one regulating piston represents a control signal for the current speed of the piston relative to the cylinder. In other words, the pressure balance causes a control signal in the form of a position of the regulating piston, which is proportional to the speed of the piston relative to the cylinder.

[0056] The overlap between the fluid discharge opening and the outlet can be adjusted by a corresponding position of at least one adjusting piston, wherein a variable flow cross section for the buffer fluid can be continuously changed, so that the overlap serves as a regulated power valve of the buffer device so that the flow cross section can always be adapted to the desired speed reference curve.

[0057] It has proven to be advantageous to provide at least one further force accumulator, preferably a spring, which is arranged inside the cylinder on the piston and / or at least one regulating piston in order to form a preferably linear speed reference curve of the damping device.

[0058] The accumulator prestress of the at least one further accumulator associated with the piston can define a reference speed of the piston relative to the cylinder. A speed reference characteristic curve can be defined as a function of the accumulator force over the piston stroke.

[0059] An advantageous variant is that at least one force accumulator, preferably a spring, is provided and arranged inside the piston and / or on the piston and at least one regulating piston, wherein preferably at least one force accumulator acts between the piston and the cylinder end side of at least one regulating piston and / or at least one further force accumulator acts between the piston and the inner wall of the cylinder.

[0060] In the prior art, the control signal for the damping power depends in principle on the absolute speed of the piston relative to the cylinder, whereby the speed regulation cannot be adequately guaranteed.

[0061] The spring prestress of the at least one force accumulator associated with the at least one regulating piston has the effect that the control signal associated with the damping power is dependent on the differential speed of the piston relative to the cylinder with respect to a reference speed of the piston relative to the cylinder via the at least one regulating piston. It can thereby be ensured that the damping device keeps the speed of the piston in the cylinder close to the speed reference curve both in terms of excess and lack of regulating speed, so that the value of the speed difference of the damping device without the at least one regulating piston is reduced or eliminated.

[0062] At least one accumulator can be used to set the extent to which the damping fluid can flow from the front area through the piston into the rear area, and / or the pressure at which the flow cross-section can be increased or decreased by changing the overlap through the damping fluid, and / or the extent to which an increase or decrease in the overlap is produced by at least one adjusting piston.

[0063] It is particularly preferred that during the damping stroke of the damping device through at least one accumulator, the overlap of a preferably possible fluid outlet opening and a possible outlet at a flow cross-section of at least one flow channel can be changed, wherein the speed of the piston relative to the cylinder can be increased by increasing the overlap and / or can be reduced by reducing the overlap.

[0064] In one embodiment of the present invention, it is provided that the overlapping portion on the flow cross-section of at least one flow channel can be automatically reduced or eliminated by a speed difference between the piston and the cylinder relative to a speed reference curve, wherein the speed difference can be caused to cause the relative position of at least one regulating piston relative to the piston via at least one possible additional accumulator and / or the at least one accumulator.

[0065] The overlap may be defined by two separate components and / or openings that at least partially overlap one another.

[0066] The speed difference between the desired speed of the piston relative to the cylinder (the speed of the piston relative to the speed reference curve in the absence of at least one adjusting piston) forms a speed difference curve to be adapted, which is caused by a movement or force action of the movable furniture part on at least one further force accumulator, wherein, in a combination of two force accumulators, the speed curve (accumulated by the speed difference curve and the speed reference curve) can be adapted to the speed reference curve determined by the at least one further force accumulator.

[0067] The speed difference of the pistons to be reduced or eliminated defines both an input variable and an output variable to be adjusted as a control signal for a power valve formed by the at least one regulating piston.

[0068] According to a preferred embodiment of the invention, it is provided that the overlap at the flow cross section of at least one flow channel can be automatically changed by a speed difference of the piston relative to the cylinder relative to a speed reference curve, which speed difference is caused by at least one possible additional accumulator and / or at least one accumulator.

[0069] It has proven to be advantageous if the speed of the piston during the damping stroke can be varied by means of the relative position of at least one adjusting piston relative to the piston, by means of at least one further force accumulator which may be present and / or by means of at least one force accumulator.

[0070] Since the adaptation to the speed reference curve can be achieved solely by a changed positioning of the at least one control piston relative to the piston, no additional components or electronic control modules are required, apart from the mechanically determined movement of the at least one control piston by the at least one force accumulator.

[0071] Furthermore, it is preferably provided that the at least one further force accumulator and the at least one force accumulator are arranged parallel to one another, preferably in the damping stroke direction, wherein it is preferably provided that the at least one further force accumulator and the at least one force accumulator are arranged coaxially.

[0072] As a result, the force transmission between the piston and the at least one adjusting piston is facilitated, a tilting of the at least one adjusting piston relative to the piston is prevented, and a particularly precise setting of the damping force or the piston speed over the damping stroke path can be ensured.

[0073] In a further embodiment of the invention, it can be provided that at least one sealing element is provided, wherein the fluid chamber is at least partially delimited by the at least one sealing element, wherein it is preferably provided that the piston rod can move through the at least one sealing element.

[0074] In general, further sealing elements may also be provided, for example on the outer circumference of the piston and / or on the upper circumference of the cylinder.

[0075] The at least one sealing element can be present, for example, in the form of a segment on a brake element or at least one control partition, wherein a complete or partial sealing on the inner wall of the cylinder is possible. For example, a small fluid flow through the brake element can be useful for the functionality of the damping device, which fluid flow serves as a control signal for a power signal (configured as a pressure balance) on at least one regulating piston as a power valve. However, such a sealing element is generally not absolutely necessary.

[0076] According to an advantageous embodiment of the invention, it is provided that at least one piston rod can be moved relative to the cylinder drum directly or indirectly via the movable furniture part, preferably via a linear movement, a rotational movement and / or a pivoting movement.

[0077] In general, the damping device can be used in any structural design of furniture and / or movable furniture parts in which damping of movement processes is required. It is particularly preferred that the rotation-induced oscillating movement of the movable furniture part, preferably a furniture flap or the like, is directly converted into a linear movement of the piston rod. In the case of an indirect conversion to the piston rod, sliding elements, coated surfaces, transmission devices and / or control cams are conceivable, but generally not necessary.

[0078] Preferably, the sealing element is configured as a braking element and / or acts in parallel to at least one flow channel and / or at least one control diaphragm along the flow direction of the buffer fluid and / or acts in series with at least one flow channel and / or at least one control diaphragm along the flow direction of the buffer fluid.

[0079] The at least one control partition can also be connected in series and / or in parallel with the at least one regulating piston.

[0080] It is preferably provided that the damping device comprises a fluid chamber which is filled with a damping fluid and which is delimited at least by the cylinder, by a possibly present sealing element, by the piston and / or by the piston rod.

[0081] It is particularly preferably proposed that the damping device comprises a volume constant maintaining element which constantly maintains the volume provided for the damping fluid in the fluid chamber in any position of the piston together with the piston rod, and / or wherein the sealing element together forms the volume constant maintaining element and is movable relative to the cylinder body and is loaded with force on its side facing away from the fluid chamber, preferably by means of a possible additional force accumulator.

[0082] According to a preferred embodiment of the present invention, a groove is formed on the inner wall of the cylinder body, and during the buffer stroke, the buffer fluid can flow from the front area of ​​the fluid chamber to the rear area of ​​the fluid chamber through the groove.

[0083] Particularly preferably, in an embodiment of the invention, it is provided that at least one control piston is movable translationally relative to the piston and / or at least one control partition during the damping stroke, preferably in the longitudinal direction, dependent on the piston travel and / or speed.

[0084] Alternatively or additionally, it can be provided that the piston and / or the at least one control partition are designed such that the piston can be rotated relative to the at least one control partition and / or the at least one control partition can be rotated relative to the piston within the cylinder during the damping stroke by a longitudinal movement of the piston.

[0085] This makes it possible to adapt the damping capacity to the piston speed without requiring grooves or other force accumulators in the cylinder which, in certain applications, could undesirably influence the damping properties over the damping stroke.

[0086] By rotating, at least one control partition can partially cover at least one flow channel in order to reduce the flow cross section. For example, at least one partition opening and at least one flow channel completely overlap at the beginning of the damping stroke, wherein the damping cross section is reduced, preferably to zero, during the damping stroke, in particular in order to adjust the damping power during the damping process.

[0087] Furthermore, advantageous properties are produced, namely that by the interaction of the at least one control diaphragm with the at least one flow channel of the piston, the passage cross section or flow cross section for the damping fluid is adapted to the desired damping properties and the passage of the damping fluid can be adjusted during the damping stroke. For example, the at least one control diaphragm can cover the at least one flow channel to a greater extent from the beginning of the damping stroke, in which a high speed of the piston is usually present, to an operating position in the end region of the damping stroke, in which a low speed of the piston is usually expected, so that the passage cross section for the damping is preferably reduced gradually and / or, for example, by a diaphragm opening.

[0088] It is particularly preferred to provide:

[0089] The piston comprises at least, preferably exactly, two flow channels, wherein it is preferably provided that the at least two flow channels are arranged symmetrically on the end side of the piston, and / or

[0090] The at least one flow channel is arranged on the end side of the piston and / or the at least one control partition is arranged on the end side of the piston and / or

[0091] The piston and the at least one control partition are designed to be coupled to each other in motion in the longitudinal direction during the damping stroke and / or to be decoupled from each other in the rotational direction during the damping stroke, and / or

[0092] - the flow cross section can be varied by a rotation of the piston relative to at least one control partition and / or a rotation of at least one control partition relative to the piston, and / or

[0093] The at least one control partition and the piston are designed to be rotatable relative to one another so that during the damping stroke the flow cross section (17) can be reduced, preferably in the longitudinal direction, as a function of the piston (5) displacement and / or speed.

[0094] It is preferably provided that the buffer device comprises a hollow piston rod, via which the piston can be rotated relative to at least one control partition, wherein it is preferably provided that the hollow piston rod is particularly preferably arranged directly on the piston and / or the hollow piston rod is guided via a guide rail which is particularly preferably arranged on the cylinder body and / or is twisted.

[0095] It is preferably provided that the buffer device comprises a magnet, preferably a rod magnet and / or a permanent magnet, by which at least one control baffle can be rotated relative to the piston, wherein it is preferably provided that the magnet is particularly preferably arranged directly on at least one control baffle and / or the magnet can be rotated by at least one metal belt, particularly preferably a steel belt, which is particularly preferably arranged on the cylinder body.

[0096] It is preferably provided that at least two metal strips are provided and / or that at least one metal strip is arranged in a twisted manner on the cylinder.

[0097] It is preferably provided that the buffer device comprises a spring for applying a loading force to the piston, the spring being arranged on at least one control diaphragm, wherein, via the spring, the at least one control diaphragm is capable of rotating relative to the piston, wherein, it is preferably provided that the spring is fixedly connected to the at least one control diaphragm, and / or the at least one control diaphragm is capable of rotating by compression of the spring.

[0098] It is preferably provided that the buffer device comprises an impeller, through which at least one control baffle can rotate relative to the piston, wherein it is preferably provided that the impeller is particularly preferably arranged directly on at least one control baffle and / or can be rotated by the passage of a buffer fluid and / or comprises at least two, particularly preferably four, blades.

[0099] It is preferably provided that the buffer device comprises at least one telescopic device, by means of which at least one control partition can be rotated relative to the piston, wherein it is preferably provided that at least one telescopic device can be rotated by a guide part which is particularly preferably twisted and / or arranged on the cylinder body, and / or comprises a plurality of telescopic parts which can be telescopic within each other and / or relative to each other.

[0100] Particularly preferably, in one embodiment, it is provided that at least one control piston acts in parallel and / or in series with a sealing element which may be present and / or with at least one control partition.

[0101] According to an advantageous design of the present invention, it can be provided that at least one regulating piston is displaced relative to at least one piston, in particular automatically, via at least one accumulator, whereby the speed of the piston relative to the cylinder adapts to a speed reference curve which is preferably linear and / or defined by at least one further accumulator, wherein it is preferably provided that at least one fluid outlet opening of at least one regulating piston is moved relative to at least one outlet of the piston.

[0102] According to a preferred embodiment of the present invention, it is provided that:

[0103] - adjusting the speed of the adjusting piston relative to the cylinder during the damping stroke by means of an overlap of at least one possible fluid outlet opening and at least one possible outlet at the flow cross section of at least one flow channel, wherein the overlap defines the flow cross section for the damping fluid and / or the flow cross section is varied by means of the relative position of at least one adjusting piston relative to the piston,

[0104] - continuously varying the overlap and / or the speed of the piston relative to the cylinder during the damping stroke,

[0105] at least one regulating piston and the piston are designed as a pressure balance, wherein, in the event of an increase in the pressure of the damping fluid at the at least one regulating piston and / or in the overlap region, the overlap at the flow cross section of the at least one flow channel is reduced, and / or in the event of a decrease in the pressure at the at least one regulating piston and / or in the overlap region, the overlap at the flow cross section of the at least one flow channel is increased,

[0106] - during a damping stroke of the damping device, the overlap in the flow cross section of at least one flow channel is varied by means of at least one force accumulator, wherein the speed of the piston relative to the cylinder is increased by increasing the overlap and / or reduced by reducing the overlap,

[0107] - the overlap at the flow cross section of at least one flow channel is automatically reduced or eliminated by a speed difference of the piston relative to the cylinder relative to a speed reference curve, wherein the speed difference is brought about by at least one possibly present further force accumulator and / or at least one force accumulator in a relative position of at least one regulating piston relative to the piston, and / or

[0108] The overlap is automatically varied by a speed difference of the piston relative to the cylinder relative to a speed reference curve, which speed difference is brought about via at least one possibly present further force accumulator and / or at least one force accumulator.

[0109] It is generally arbitrary whether the increase in the flow cross section is achieved by increasing or by the relative positioning of the at least one regulating piston with respect to the piston, wherein pressure accumulators and tension accumulators can be considered to be arranged in any orientation, in particular in the direction of the damping stroke, before or after the at least one regulating piston relative to the at least one regulating piston. BRIEF DESCRIPTION OF THE DRAWINGS

[0110] Features of the device claim may be applied to the method claim and vice versa. Further details and advantages of the invention are described in detail below with the aid of the accompanying drawings and with reference to the embodiments shown in the drawings. It is shown that:

[0111] Figure 1aA damping device according to a particularly preferred embodiment is shown in a schematically illustrated section through a control piston.

[0112] Figure 1b The diagram is used to illustrate the Figure 1a A diagram of the change in speed of the piston of the buffer device of an embodiment,

[0113] Figure 2a to Figure 2e Preferred embodiments of the regulating piston are shown alone and in a relative position to the piston, as well as diagrams for illustrating forces, speeds and pressures on the piston or regulating piston,

[0114] Figure 3a to Figure 3c shows the buffer stroke according to Figure 1a A damping device of an embodiment of the invention, with a diagram for illustrating the speed adaptation and the relationship between the pressure and the force on the piston or regulating piston,

[0115] Figures 4a to 4d shows a diagram for illustrating the adaptation of the speed of the piston to a reference speed, as well as the forces and pressures acting on the piston or regulating piston,

[0116] Figure 5a , Figure 5b A damping device with a regulating piston arranged outside the piston according to a preferred embodiment is shown in a sectional view from the side and in a perspective sectional view,

[0117] Figure 6a , Figure 6b Shown according to Figure 5a A damping device of an embodiment wherein the relative position of the adjusting piston with respect to the piston is changed,

[0118] Figure 7a , Figure 7b A damping device with a regulating piston arranged within a piston according to a further preferred embodiment is shown in a sectional view from the side and in a perspective sectional view,

[0119] Figure 8a , Figure 8b Shown according to Figure 7a A damping device of an embodiment wherein the relative position of the adjusting piston with respect to the piston is changed,

[0120] Fig. 9 A damping device according to a further preferred embodiment is shown in perspective, sectional and enlarged detail sections, wherein the relative rotation between the control diaphragm and the piston is produced by a rod magnet.

[0121] Fig.10 shows the buffer stroke according to Fig. 9 A buffer device of an embodiment,

[0122] Figures 11a to 11d The exploded view, perspective view and front view show the Fig. 9 The control partition and the rod-shaped magnet of the buffer device of the embodiment of the present invention are shown in the front view, wherein the rod-shaped magnet is hidden in three different positions along the buffer stroke.

[0123] Figures 12a to 12c The three-dimensional view, front view and cross-sectional view at different positions along the buffer stroke are respectively shown according to Fig.11a A control partition of a buffer device of an embodiment,

[0124] Fig.13 A damping device according to a further preferred embodiment is shown in a perspective sectional view with an enlarged detail section and in a sectional view from the side with an enlarged detail section, wherein the rotation is generated by a spring,

[0125] Fig.14 shows the buffer stroke according to Fig.13 A buffer device of an embodiment,

[0126] Fig.15a , Fig.15b Shown according to Fig.13 A buffer device in two different positions during the buffer stroke of an embodiment of the present invention, wherein the spring is hidden (or the telescopic device is hidden),

[0127] Fig.16 A perspective sectional view with enlarged detail sections and a sectional view from the side with enlarged detail sections show a damping device according to a further preferred embodiment, wherein the rotation is generated by the telescopic device,

[0128] Fig.17 shows the buffer stroke according to Fig.16 A buffer device of an embodiment,

[0129] Figures 18a to 18c The embodiment according to the invention is shown in a view from the side before and after the damping stroke, in an exploded view and a perspective view before the damping stroke, and in a perspective view after the damping stroke. Fig.16 The embodiment of the telescopic device of the buffer device,

[0130] Fig.19 A damping device according to a further preferred embodiment is shown in a perspective view and in an exploded view, wherein the rotation is generated by an impeller.

[0131] Fig.20a , Fig.20b The three-dimensional cross-sectional view before and during the buffer stroke shows the Fig.19 A buffer device of an embodiment,

[0132] Fig.21a , Figure 21b The cross-sectional view from the side before and during the damping stroke shows the Fig.19 A buffer device of an embodiment,

[0133] Fig.22a , Figure 22b A damping device with a regulating piston arranged inside the piston according to a further preferred embodiment is shown in a sectional view from the side and in a perspective sectional view,

[0134] Fig.23a , Figure 23b Shown according to Fig.22a A damping device of an embodiment wherein the relative position of the adjusting piston with respect to the piston is changed. DETAILED DESCRIPTION

[0135] Figure 1a A damping device 1 for damping the movement of a movable furniture part 2 is shown, which 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, which is limited by at least the cylinder 3, the piston 5 and the piston rod 6.

[0136] The piston 5 comprises an inlet 9 towards a front region 8 of the fluid chamber 7, wherein the front region 8 is arranged at the side of the piston 5 facing away from the piston rod 6. The piston 5 comprises an outlet 11 towards a rear region 10 of the fluid chamber 7, wherein the rear region 10 is arranged at the side of the piston 5 facing the piston rod 6.

[0137] In the damping device 1, a regulating piston 12 is arranged inside the piston 5, wherein the regulating piston 12 is arranged completely inside the piston 5. To limit and fix the regulating piston 12 relative to the piston 5, a stop 15 for the regulating piston 12 is arranged on the piston 5 toward the front region 8.

[0138] The regulating piston 12 comprises a fluid inlet opening 13 towards the front region 8 of the fluid chamber 7 and a fluid outlet opening 14 towards the rear region 10 of the fluid chamber 7. During the damping stroke of the damping device 1, the damping fluid 4 flows from the front region 8 of the fluid chamber 7 through the fluid outlet opening 14 and the outlet 11 into the rear region 10 of the fluid chamber 7.

[0139] The speed of the piston 5 relative to the cylinder 3 during the damping stroke can be adjusted by the overlap 16 of the fluid outlet opening 14 and the outlet 11. The overlap 16 corresponds to a flow cross section 17 of the damping fluid 4, wherein the flow cross section 17 can be changed by adjusting the relative position of the piston 12 relative to the piston 5 (see Figure 3c ).

[0140] A damping element may be arranged between the regulating piston 12 and the piston 5 in order to prevent the damping fluid 4 from flowing directly from the front region 8 through the outlet 11. The outer circumference of the regulating piston 12 is usually adapted to the inner circumference of the piston 5 in such a way that the damping fluid 4 flows from the front region 8 into the rear region 10 without passing through the fluid outlet opening 14. However, it is generally conceivable that the damping fluid 4 can flow slightly directly from the front region 8 into the rear region 10 without passing through the fluid outlet opening 14, so as to ensure a damping stroke displacement of the piston 5 even when there is no overlap 16 between the fluid outlet opening 14 and the outlet 11.

[0141] Arranged on the damping device 1 is a further force accumulator 18 in the form of a spring, which is arranged on the piston 5 in the cylinder 3 for forming a linear speed reference curve 19 of the damping device 1. Generally, the further force accumulator 18 can also be arranged on the regulating piston 12 as an alternative or in addition, wherein it is preferably provided that the further force accumulator 18 is arranged only on the piston 5 with respect to the regulating piston 12 and the piston 5.

[0142] Arranged on the damping device 1 is a force accumulator 20 designed as a spring, which is arranged completely inside the piston 5. The force accumulator 20 is arranged on the piston 5 and the regulating piston 12, wherein the force accumulator 20 acts between the piston 5 and the cylinder end face 21 of the regulating piston 12. The force accumulator 20 ensures that the overlap 16 between the fluid outlet opening 14 and the outlet 11 is changed in order to adjust the speed of the piston 5 relative to the cylinder.

[0143] The overlap 16 can be varied automatically by a speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, which speed difference 22 is brought about by the further force accumulator 18 and by the force accumulator 20. The speed of the piston 5 during the damping stroke can be varied by adjusting the relative position of the piston 12 relative to the piston 5 via the further force accumulator 18 and by the force accumulator 20.

[0144] The parameter x represents the damping stroke displacement of the piston 5, and the parameter z represents the relative movement between the regulating piston 12 and the piston 5. Above the damping device 1 is the pressure variation curve along the flow path of the damping fluid, wherein the parameter p2 is the pressure in the front area 8, p1 is the pressure inside the piston 5 (between the fluid inlet opening 13 and the fluid outlet opening 14), p0 is the pressure in the rear area 10, and Δp2 is the difference between p2 and p1.

[0145] Figure 1b The curve of the speed v of the piston 5 relative to the cylinder 3 over the damping stroke x is shown, wherein a speed reference curve 19 for the movement of the piston 5 relative to the cylinder 3 is defined by the further force accumulator 18 in the case of a uniform movement of the movable furniture part 2 .

[0146] The speed curve of the piston 5 which lies above the speed reference curve 19 of the piston 5 is at least approached to the desired speed reference curve 19 by the damping device 1 , wherein an adaptation of the speed curve to the speed reference curve 19 preferably takes place.

[0147] If the speed difference 22 between the current speeds of the piston 5 is high, the action of the power valve caused by the control piston 12 is stronger than in the case of a small speed difference 22. The current difference between the speed curve and the speed reference curve 19 forms a signal for the control piston 12 in order to bring about an approach of the speed curve to the speed reference curve 22.

[0148] Figure 2a The regulating piston 12 for a pressure balance is shown, wherein the parameter A represents the currently existing flow cross section 17 which is set, for example, to an overlap 16 of 10% in the power valve produced by the fluid outlet opening 14 and the outlet 11 for regulating the speed of the piston 5 .

[0149] The regulating piston 12 and the piston 5 are constructed as a pressure balance, wherein the overlap 16 of the fluid outlet opening 14 and the outlet 11 can be reduced when the pressure of the buffer fluid 4 on the regulating piston 12 or in the region of the overlap 16 increases, and can be increased when the pressure on the regulating piston 12 or in the region of the overlap 16 decreases.

[0150] Spring force F of force accumulator 20 c The spring force F0 of the additional force accumulator 18 is a function of the parameter (x) of the damping stroke displacement of the piston 5 .

[0151] Δp2 represents the difference between p2 and p1, where F c (z)-F0(x) divided by the area A of the flow cross section 17 in the form of the overlap 16 results in the functional relationship of Δp2*.

[0152] Figure 2b The relative positioning of the control piston 12 relative to the piston 5 is shown during a damping stroke, in which the speed of the piston 5 relative to the cylinder is above the desired speed reference curve 19. The parameter z is set at the control piston 12 in such a way that the forces of the two accumulators 18, 20 are balanced and form a control signal for the current speed of the piston 5, since the volume flow of the damping fluid 4 and the associated piston speed are proportional to Δp2.

[0153] Figure 2cThe diagram shows the spring stress of the further force accumulator 18 as a function of the damping stroke displacement x, which defines the speed reference curve 19 of the piston 5 and is determined by v Ref denoted by . Depending on the spring force F0, a speed reference curve 19 can be defined with respect to the damping stroke displacement x of the piston 5. By means of the prestressing of the force accumulator 20, a control signal for the differential of the damping power is transmitted to the regulating piston 12. The movement of the piston rod 6 is initiated, for example, by the angular velocity of the movable furniture part 2.

[0154] Figure 2d to Figure 3b An example of application is shown in which the speed of the piston 5 , proceeding from the movable furniture part 2 relative to the cylinder 3 , is higher than the speed expected according to the speed reference curve 19 at the current damping stroke displacement position x.

[0155] exist Figure 2d In the example, the damping travel displacement x is equal to 0 (indicated by a circle), wherein the damping starts in the direction of the closed position of the movable furniture part 2 and there is v>v Ref The overlap 16 is 100% here. The damping device 1 approaches the reference speed profile 19 as a function of the existing speed difference 22, thereby suppressing the risk of a violent collision.

[0156] Figure 2e F0 represents the current pressure situation in the damping device 1 compared to the existing accumulator force. F0 represents the accumulator prestressing force of the further accumulator 18 at the damping stroke displacement x=0.

[0157] Figure 3a and Figure 2d The difference is that a damping stroke displacement x (indicated by a circle) of 50% of the maximum damping stroke displacement x of the damping device 1 is observed. By means of a power valve in the region of the overlap 16 for changing the flow cross section 17, which is adjusted via the regulating piston 12 (see Figure 3c ), the accumulator characteristic curve of the other accumulator 18 is used as F0 and F c function, changes according to the buffer stroke displacement x.

[0158] The speed reference curve 19 is a function of the damping stroke displacement x, wherein a smaller speed difference 22 leads to a smaller relative movement of the control piston 12 relative to the piston 5 starting from the unloaded position, thereby increasing the overlap 16 and increasing the flow cross section 17. As a result, the pressure of the damping fluid 4 decreases in the front region 8.

[0159] Figure 3b and Figure 2e The difference is that at a damping stroke travel x of 50%, the pressure conditions in the damping device 1 are shown in comparison with the existing accumulator force.

[0160] Figure 3c A buffer device 1 is shown, wherein the buffer device 1 is relative to Figure 1a The movable furniture part has already been moved in the direction of the closed position and is within the damping stroke.

[0161] The further force accumulator 18 and the force accumulator 20 are arranged parallel to one another in the damping stroke direction 23 , wherein the further force accumulator 18 and the force accumulator 20 are arranged coaxially.

[0162] The piston rod 6 can be moved directly via the movable furniture part 2 by means of a rotational movement or a pivoting movement relative to the cylinder 3, wherein the piston rod 6 together with the piston 5 executes a linear movement relative to the cylinder 3. In general, it is also conceivable to indirectly transmit the movement path of the movable furniture part 2 to the damping device 1, for example in the form of a mechanical transmission with an adjustment curve or an articulation.

[0163] The movable furniture part 2 is in the form of a furniture flap, but other movable furniture parts 2 , such as a drawer which is linearly movable in the direction of the damping device 1 , are also possible.

[0164] In order to adapt the speed of the piston 5 relative to the cylinder 3 to the speed reference curve 19 , the overlap 16 and thus the speed change of the piston 5 relative to the cylinder 3 are continuously varied during the damping stroke by adjusting the positioning of the piston 12 relative to the piston 5 .

[0165] During a damping stroke of the damping device 1 , the overlap 16 of the fluid outlet opening 14 and the outlet 11 can be varied by the force accumulator 20 , wherein the speed of the piston 5 relative to the cylinder 3 can be increased by increasing the overlap 16 and can be reduced by reducing the overlap 16 .

[0166] The overlap 16 can be reduced and eliminated automatically by a 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, because the flow of the buffer fluid 4 is adjusted. The speed difference 22 is brought about by the further accumulator 18 and by the accumulator 20 to adjust the relative position of the adjustment piston 12 relative to the piston 5.

[0167] Exemplarily, the method for adjusting the damping speed of the damping device 1 during a damping stroke may be performed by the damping device 1 as follows:

[0168] a piston 5 guided in the cylinder 3 and damped by the damping fluid 4 is moved relative to the cylinder 3 by applying a force via a piston rod 6 connected to the piston 5,

[0169] the damping fluid 4 flows from the front region 8 of the fluid chamber 7 via the inlet 9 of the piston 5 into the outlet 11 of the piston 5 facing the rear region 10 of the fluid chamber 7,

[0170] - The regulating piston 12 arranged in the piston 5 is automatically moved relative to the piston 5 via the accumulator 20, whereby the fluid outlet opening 14 of the regulating piston 12 in the rear area 10 facing the fluid chamber 7 is moved relative to the outlet 11 of the piston 5, and the speed of the piston 5 relative to the cylinder 3 is adapted to a linear speed reference curve 19 related to the further accumulator 18.

[0171] During the adjustment of the damping speed of the damping device 1 by means of the adjusting piston 12, it is possible

[0172] - during the damping stroke, the speed of the piston 5 relative to the cylinder 3 is adjusted by the overlap 16 of the fluid outlet opening 14 and the outlet 11, wherein the overlap 16 defines a flow cross section 17 for the damping fluid 4, and the flow cross section 17 is continuously changed during the damping stroke by adjusting the relative position of the piston 12 relative to the piston 5 to change the speed of the piston 5,

[0173] the regulating piston 12 and the piston 5 are designed as a pressure balance, wherein the overlap 16 of the fluid outlet opening 14 and the outlet 11 decreases when the pressure of the damping fluid 4 on the regulating piston 12 or in the region of the overlap 16 increases and increases when the pressure on the regulating piston 12 or in the region of the overlap 16 decreases,

[0174] - during the damping stroke of the damping device 1 , the overlap 16 of the fluid outlet opening 14 and the outlet 11 is varied by the force accumulator 20 , wherein the speed of the piston 5 relative to the cylinder 3 is increased by an increase in the overlap 16 and is reduced by a decrease in the overlap 16 ,

[0175] the overlap 16 is automatically reduced or eliminated by a speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19 , wherein the speed difference 22 causes the relative position of the adjustment piston 12 relative to the piston 5 to be adjusted by means of the further force accumulator 18 or the force accumulator 20 ,

[0176] The overlap 16 is changed automatically by a speed difference 22 of the piston 5 relative to the cylinder 3 relative to a speed reference curve 19 , which is brought about by means of the further force accumulator 18 or the force accumulator 20 .

[0177] Figures 4a to 4d A further example of application of the damping device 1 is shown, in which 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 displacement position x.

[0178] exist Figure 4aIn FIG. 1 , the damping stroke x=0 (indicated by a circle) is observed, wherein the speed difference 22 of the piston 5 relative to the speed reference curve 19 is negative. The overlap 16 is 100% in this case.

[0179] Figure 4b The pressure behavior in the fluid chamber 7 and the force behavior of the force accumulator 20 are shown as a function of the relative position z of the control piston 12 relative to the piston 5 when a speed difference 22 is present. F0 here denotes the force accumulator prestress of the further force accumulator 18 at the damping stroke x=0.

[0180] In this configuration of the parameters and positioning of the adjustment piston 12 , the damping device 1 generates no damping power, since the speed difference 22 is negative, whereby the speed of the piston 5 relative to the cylinder approaches the speed reference curve 19 due to the speed increase.

[0181] In the case of an overlap 16 of less than 100%, the overlap 16 will be increased by the accumulator 20. If the speed difference 22 is positive, a reduction in the piston speed occurs due to the reduction of the overlap 16 by the accumulator 20.

[0182] Figure 4c and Figure 4a The difference is that a damping stroke displacement x of 50% of the maximum damping stroke displacement x is observed. Although the speed difference 22 is lower, this is due to the smaller reference speed v of the speed reference curve 19 at the damping stroke displacement x. Ref Or the piston speed has successfully approached the speed reference curve 19, but the damping power is not achieved by the damping device 1, because the speed difference 22 is still negative.

[0183] Figure 4d and Figure 4b The difference is that in the case of half the damping stroke displacement x, parameters which are dependent on the pressure, the accumulator prestress, the accumulator force, the accumulator characteristic curve and the speed of the piston 5 relative to the cylinder 3 are observed.

[0184] Figure 5a A damping device 1 for a furniture or building fitting is shown, comprising a cylinder 3 and a piston 5 which can be actuated via a piston rod 6 , in which a damping fluid 4 is arranged, through which the piston can be moved at a certain speed during a damping stroke.

[0185] In the damping device 1, a flow channel 42 with a flow cross section 17 is provided (which passes through the piston 5 and the regulating piston 12, wherein the flow channel 42 usually also passes past the brake element 25), through which the damping fluid 4 can pass through the piston 5 during the damping stroke. A regulating piston 12 is provided, which is movably supported on the piston 5 (or in the piston, see Figures 22a to 23b), wherein the flow cross section 17 of the flow channel 42 can be varied by a movement of the adjusting piston 12 relative to the piston 5 .

[0186] A force accumulator 20 in the form of a return spring is provided on the damping device 1 , wherein the force accumulator 20 acts on the regulating piston 12 with a return force relative to the piston 5 , which counteracts at least one flow force that can be applied to the regulating piston 12 by the damping fluid 4 during the damping stroke.

[0187] A pressure reduction is performed on the control diaphragm 29 in proportion to the flow force and the speed of the piston 5, wherein a rated speed for the piston 5 is predetermined and is related to the position of the piston 5 relative to the cylinder 3, wherein, when the speed of the piston 5 is greater than the rated speed, the regulating piston 12 can move relative to the piston 5 against the restoring force, so that the flow cross section 17 of the flow channel 42 can be reduced.

[0188] The damping effect is determined by the flow cross section 17, wherein the damping device 1 can automatically fail below a set speed, and the set speed for the piston 5, which is dependent on the position of the piston 5 relative to the cylinder 3, is preset by a further force accumulator 18, such as a spring 28, and by a groove 45 with a variable groove cross section in the cylinder inner wall 46, which loads the adjustment piston 12 with force against the restoring force. In general, the set speed can also be determined alternatively or additionally by the adjustability of the diaphragm opening 44 of the control diaphragm 29.

[0189] Figure 5b Only from the perspective of change is shown according to Figure 5a Buffer device 1.

[0190] Figure 6a and Figure 6b and Figure 5a and Figure 5b The only difference is that the regulating piston 12 is displaced relative to the piston 5 during the damping stroke, so that the overlap 16 on the flow cross section 17 of the flow channel 42 is changed, in order to adjust the damping power via the position between the piston 5 and the regulating piston 12 .

[0191] The regulating piston 12 is arranged completely outside the piston 5 , but may also be arranged at least partially inside the piston 5 .

[0192] The regulating piston 12 is in the form of a power valve for the piston 5 , wherein the flow cross section 17 of the flow channel 42 can be varied by means of a control partition 29 and by means of the regulating piston 12 , so that the speed of the piston 5 can be adjusted.

[0193] The adjusting piston 12 is preloaded relative to the piston 5 via the further force accumulator 18 and the force accumulator 20 , and the piston 5 is acted upon by force via the further force accumulator 18 in order to form a desired speed reference curve.

[0194] The flow channel 42 is closed or opened by the adjusting piston 12 .

[0195] exist Figure 7a , a damping device 1 is shown, wherein the adjusting piston 12 comprises an opening which can overlap with an opening of the piston 5 in order to increase or reduce the throughflow cross section 17 of the flow channel 42 .

[0196] exist Figure 7b In the embodiment, the buffer fluid 4 can flow into the piston 5, while in Figure 8a and Figure 8b In this case, the flow channel 42 is closed to the buffer fluid 4 .

[0197] Generally, the speed of the piston 5 relative to the cylinder 3 during the damping stroke can be adjusted by the overlap 16 at the flow cross section 17 of the flow channel 42 , for example between the fluid outlet opening 14 and the outlet 11 .

[0198] The overlap 16 defines a flow cross section 17 for the damping fluid 4, and the flow cross section 17 can be varied by adjusting the relative position of the piston 12 relative to the piston 5, wherein the flow cross section 17 can also be adjusted at the control partition 29 or used as a control signal for the adjusting piston 12. The overlap 16 and the speed change of the piston 5 relative to the cylinder 3 can be varied continuously during the damping stroke.

[0199] The regulating piston 12 and the piston 5 are designed as a pressure balance, wherein the overlap 16 on the flow cross section 17 of the flow channel 42 can be reduced when the pressure of the damping fluid 4 on the regulating piston 12 and in the region of the overlap 16 increases, and can be increased when the pressure on the regulating piston 12 and in the region of the overlap 16 decreases.

[0200] like Figure 8b As shown, a further force accumulator 18 is provided in the form of a spring 28 in order to facilitate the formation of a arbitrarily definable speed reference curve 19 for the damping device 1 within the cylinder 3 at the piston 5 and the regulating piston 12 .

[0201] During a damping stroke of the damping device 1, the overlap 16 on the flow cross section 17 of the flow channel 42 can be varied by the force accumulator 20, wherein the speed of the piston 5 relative to the cylinder 3 can be increased by increasing the overlap 16 and can be reduced by reducing the overlap 16. The functional connection of the components can be applied in all the illustrated exemplary embodiments.

[0202] The overlap 16 in the flow cross section 17 of the flow channel 42 can be automatically reduced or eliminated by a speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, wherein the speed difference 22 can be brought about by the further force accumulator 18 and the force accumulator 20 to adjust the relative position of the piston 12 relative to the piston 5. The overlap 16 in the flow cross section 17 of the flow channel 42 can be automatically changed by a speed difference 22 of the piston 5 relative to the cylinder 3 relative to the speed reference curve 19, which speed difference 22 is brought about by the further force accumulator 18 and the force accumulator 20. The speed of the piston 5 during the damping stroke can be changed by adjusting the relative position of the piston 12 relative to the piston 5, by the further force accumulator 18 and the force accumulator 20.

[0203] Fig. 9 A damping device 1 is shown, wherein the damping device 1 includes a magnet 35 in the form of a rod magnet, which is designed as a permanent magnet, in order to rotate the control diaphragm 29 relative to the piston 5 so that a varying amount of damping fluid 4 flows through the piston 5 and the regulating piston 12 in order to vary the damping power.

[0204] The control diaphragm 29 can be rotated relative to the piston 5 by means of a magnet 35 , wherein the magnet 35 is arranged directly on the control diaphragm 29 and the magnet 35 can be rotated by means of a metal belt 36 in the form of a steel belt arranged at least on the cylinder 3 .

[0205] Fig.10 and Fig. 9 The only difference is the changed position of the control diaphragm 29 relative to the piston.

[0206] Two metal strips 36 connected to one another are arranged in a twisted manner on the cylinder 3 .

[0207] The piston 5 comprises exactly two flow channels 42 , wherein the flow channels 42 are arranged symmetrically on the end side 30 of the piston 5 .

[0208] The control plate 29 is arranged on this end side 30 of the piston 5 , and the piston 5 and the control plate 29 are designed to be coupled to each other in motion in the longitudinal direction during the damping stroke and to be decoupled from each other in the rotational direction 32 during the damping stroke.

[0209] The flow cross section 17 can be changed by rotating the piston 5 relative to the control diaphragm 29 and by rotating the control diaphragm 29 relative to the piston 5, wherein the control diaphragm 29 and the piston 5 are designed to be rotatable relative to each other, so that during the damping stroke, the flow cross section 17 (longitudinally depending on the displacement and depending on the speed) can be reduced and usually also increased.

[0210] Fig.11a The control panel 29 is shown in an exploded view and in the assembled state, wherein Figure 11b to Figure 11dThree different rotational positions of the control diaphragm 29 are shown, which are brought about by the magnet 35. Depending on the degree of rotation of the control diaphragm 29, the diaphragm opening 44 is enlarged or reduced along the flow channel 42 in order to adapt the amount or pressure of the flowing damping fluid 4 in such a way that the regulating piston 29 is actuated into the desired position relative to the piston 5.

[0211] The changed rotation angle or amount of the partition opening 44 can be produced in a position-dependent and / or piston-speed-dependent manner.

[0212] Figures 12a to 12c and Figure 11b to Figure 11d The difference lies only in the additional sectional views in the three varying flow cross sections 17 .

[0213] Fig.13 A damping device 1 is shown, wherein the damping device 1 comprises a spring 28 for applying a force to the piston 5 , which spring 28 is arranged on a control plate 29 , wherein the control plate 29 can be rotated relative to the piston 5 by means of the spring 28 .

[0214] In general, the spring 28 can also be used only for the force loading of the piston 5 or only for controlling the rotation of the intermediate plate 29 , wherein the combined function of the additional force accumulator 18 has proven to be particularly advantageous for the damping device 1 .

[0215] The spring 28 is fixedly connected to the control diaphragm 29 , and the control diaphragm 29 can be rotated by compression of the spring 28 .

[0216] Fig.14 and Fig.13 The only difference is that the spring 28 is in the compressed position during the damping stroke after the rotation has taken place.

[0217] Fig.15a and Fig.15b Two different positions of the piston 5 and the control diaphragm 29 relative to each other are shown, wherein Fig.15a There is a flow cross section 17 for the flow channel 42 of the buffer fluid 4, and Fig.15b In the embodiment of the present invention, the overlap 16 is present in such a way that the damping fluid 4 cannot flow into the regulating piston 12 .

[0218] The rotation of the control diaphragm 29 can be caused, for example, by a hollow piston rod (not shown), by which the piston 5 can be rotated relative to the control diaphragm 29. For example, the hollow piston rod can be arranged directly on the piston 5 or can be guided via a twisted sliding guide rail arranged on the cylinder 3.

[0219] Fig.16 A damping device 1 is shown, wherein the damping device 1 comprises a telescopic device 39 , by means of which the control plate 29 can be rotated relative to the piston 5 .

[0220] Fig.17 and Fig.16 The difference lies only in the position that changes along the damping stroke, wherein the telescopic device 39 is rotated by a guide 40 that twists along the telescopic device 39 and comprises a plurality of telescopic elements 41 that can be telescoped into each other and can be telescoped relative to each other.

[0221] Figures 18a to 18c The guide 40 and the telescope 41 of the telescopic device 39 are shown separately in a side view in the extended position and in the retracted position, as well as in an exploded view, in a perspective view in the assembled position and in the compressed state.

[0222] Fig.19 A control diaphragm 29 is shown for interaction with a piston 5 of the damping device 1 , wherein the damping device 1 comprises an impeller 37 , by which the control diaphragm 29 can be rotated relative to the piston 5 .

[0223] Fig.20a The damping device 1 with the impeller 37 is shown in cross section, wherein Fig.20b and Fig.20a The difference lies only in the position changed along the direction of the buffer stroke.

[0224] The impeller 37 is arranged directly at the control partition 29, and can be rotated by the passage of the buffer fluid 4. The impeller 37 includes a plurality of blades 38 which can be pushed in the rotation direction by the flow of the buffer fluid 4.

[0225] Fig.21a and Figure 21b The damping device 1 with the impeller 37 is shown in a sectional view from the side in a position during a damping stroke and in a position before the damping stroke, wherein the control piston 12 is not shown in detail for reasons of clarity.

[0226] according to Figures 9 to 21b The exemplary embodiment is designed in such a way that the piston 5 and the control partition 29 are designed in such a way that during the damping stroke in the cylinder 3 the piston 5 can rotate relative to the control partition 29 and the control partition 29 relative to the piston 5 due to the longitudinal movement of the piston 5.

[0227] Fig.22a and Figure 22b The buffer device 1 shown is similar to the one according to Figures 5a to 8b A damping device 1 in which the adjusting piston 12 is not arranged outside the piston 5 but inside the piston 5. Kinematically, a change in the flow cross section 17 of the flow channel 42 can be achieved in a similar manner by adjusting the overlap 16 between the adjusting piston 12 and the piston 5.

[0228] Fig.23a and Figure 23b The diagram shows a position in which the regulating piston 12 is slightly displaced relative to the piston 5 according to Fig.22a and Figure 22b A damping device 1 is provided, wherein along the damping stroke, the movement of a movable furniture part (not shown) can be controlled by the damping device 1 via adjustment of the damping speed. In this case, when 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 greater than the rated speed, the regulating piston 12 moves relative to the piston 5 against the restoring force (which is generated by the accumulator 20), so that the flow cross section 17 of the flow channel 42 is reduced and the movable furniture part 2 or the piston 5 is braked to the rated speed.

[0229] The setpoint speed is predetermined by the force application of the further force accumulator 18 and the position of the control partition 29 along the cylinder.

[0230] At speeds below the rated speed, the damping device 1 is automatically switched to inactive.

[0231] For damping strength adjustment, the regulating piston 12 is automatically moved relative to the piston 5 via the force accumulator 20, thereby adapting the speed of the piston 5 relative to the cylinder 3 to a speed reference curve 19, for example linearly or defined via a further force accumulator 18. Depending on the relative position of the regulating piston 12 and the piston 5, the fluid outlet opening 14 of the regulating piston 12 can be moved relative to the outlet 11 of the piston 5.

[0232] The sealing element 24 of the damping device 1 is designed as a brake element 25 and acts in parallel with the flow channel 42 on the regulating piston 12 in the flow direction of the damping fluid 4. In the embodiment with a rotationally controlled control diaphragm 29, the regulating piston 12 is usually arranged in series with the control diaphragm 29.

[0233] The buffer device 1 includes a fluid chamber 7 filled with a buffer fluid 4, which is bounded by a cylinder 3, a sealing element 24, a piston 5 and a piston rod 6, wherein the buffer device 1 includes a constant-volume retaining element 26, which constantly maintains the volume available for the buffer fluid 4 in the fluid chamber 7 in each position of the piston 5 together with the piston rod 6 and loads force via an additional further accumulator 18.

[0234] During the damping stroke, the control piston 12 can be moved translationally in the longitudinal direction relative to the piston 5 and the control plate 29 as a function of the displacement and speed of the piston 5 .

Claims

1. A damping device (1) for a furniture or building fitting, comprising a cylinder (3) and a piston (5) which can be actuated by a piston rod (6), a damping fluid (4) being arranged in the cylinder, the piston being able to move through the damping fluid (4) at a speed during a damping stroke, wherein: At least one flow channel (42) having a flow cross section (17) is provided, through which a damping fluid (4) can pass through the piston (5) during the damping stroke, characterized in that at least one regulating piston (12) is provided, which is supported in and / or on the piston (5) in a movable, preferably displaceable manner, wherein the flow cross section (17) of the at least one flow channel (42) can be changed by movement of the at least one regulating piston (12) relative to the piston (5), wherein at least one force accumulator (20), preferably a return spring, is provided, which acts on the at least one regulating piston (12) with a return force relative to the piston (5), the return force counteracting at least one flow force, the at least one A flow force can be applied to the at least one regulating piston (12) during the damping stroke by means of a damping fluid (4), wherein at least one control diaphragm (29) is provided, at which a pressure drop is achieved which is proportional to the flow force and the speed of the piston (5), wherein a rated speed related to the position of the piston (5) relative to the cylinder (3) is preset for the piston (5), wherein when the speed of the piston (5) is greater than the rated speed, the at least one regulating piston (12) can move relative to the piston (5) against a restoring force so that a flow cross section (17) of the at least one flow channel (42) can be reduced, preferably wherein the rated speed for the piston (5) related to the position of the piston (5) relative to the cylinder (3) is - presetting by at least one further force accumulator (18), particularly preferably a spring (28), which applies a force to the at least one regulating piston (12) counter to the restoring force, and / or - presetting by means of the adjustability of the partition opening (14) of the at least one control partition (29), and / or - Presetting is carried out by at least one groove (45) with a varying groove cross section in the cylinder inner wall (46).

2. The buffer device (1) according to claim 1, wherein: The at least one regulating piston (12) is arranged on the outside of the piston (5) and / or inside the piston (5) and / or is present in the form of a power valve for the piston (5), wherein it is preferably provided that the flow cross section (17) of the at least one flow channel (42) can be varied by means of the at least one control partition (29) and / or by means of the at least one regulating piston (12), so that the speed of the piston (5) can be adjusted.

3. The buffer device (1) according to claim 1 or 2, wherein: The at least one regulating piston (12) is preloaded relative to the piston (5) by at least one further force accumulator (18) and / or by the at least one force accumulator (20), and / or the piston (5) can be acted upon by force by at least one further force accumulator (18).

4. The buffer device (1) according to any one of the preceding claims, wherein: The piston (5) comprises at least one inlet (9) which faces a front region (8) of a fluid chamber (7), the front region being arranged on a side of the piston (5) facing away from the piston rod (6), and the piston comprises at least one outlet (11) which faces a rear region (10) of the fluid chamber (7), the rear region being arranged on a side of the piston (5) facing the piston rod (6), wherein the at least one regulating piston (12) comprises 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), wherein the buffer fluid (4) can flow from the front region (8) of the fluid chamber (7) through the at least one fluid outlet opening (14) and the at least one outlet (11) into the rear region (10) of the fluid chamber (7) during the buffer stroke of the buffer device (1).

5. The buffer device (1) according to any one of the preceding claims, wherein: The at least one regulating piston (12) is arranged completely inside the piston (5) or completely outside the piston (5), wherein it is preferably provided that at least one stop (15) for the at least one regulating piston (12) is arranged on the piston (5), preferably toward the front area (8).

6. A buffer device (1) according to any one of the preceding claims, wherein: 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 at least one flow channel (42), preferably an overlap (16) of a possible fluid outlet opening (14) and a possible outlet opening (11), wherein it is preferably provided that the overlap (16) defines the flow cross section (17) of the damping fluid (4), and / or the flow cross section (17) can be changed by the relative position of the at least one regulating piston (12) relative to the piston (5).

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

8. The buffer device (1) according to any one of the preceding claims, wherein: The at least one regulating piston (12) and the piston (5) are constructed as a pressure balance, wherein an overlap (16) at a flow cross section (17) of the at least one flow channel (42), preferably an overlap (16) of a possible fluid outlet opening (14) and a possible outlet (11) can decrease when the pressure of the buffer fluid (4) on the at least one regulating piston (12) and / or in the region of the overlap (16) increases, and / or can increase when the pressure on the at least one regulating piston (12) and / or in the region of the overlap (16) decreases.

9. The buffer device (1) according to any one of the preceding claims, wherein: At least one further force accumulator (18), preferably a spring (28), is provided, which is arranged in the cylinder (3) at the piston (5) and / or at least one regulating piston (12) in order to form a preferably linear speed reference curve (19) of the damping device (1).

10. The buffer device (1) according to any one of the preceding claims, wherein: At least one force accumulator (20), preferably a spring, is provided and is arranged in the piston (5) and / or on the piston (5) and the at least one regulating piston (12), wherein it is preferably provided that the at least one force accumulator (20) acts between the piston (5) and the cylinder end face (21) of the at least one regulating piston (12), and / or the at least one further force accumulator (18) acts between the piston (5) and the cylinder inner wall (46).

11. The buffer device (1) according to any one of the preceding claims, wherein: During a damping stroke of the damping device (1), the overlap (16) at the flow cross section (17) of the at least one flow channel (42), preferably the overlap (16) of a possible fluid outlet opening (14) and a possible outlet (11) can be varied by the at least one force accumulator (20), wherein the speed of the piston (5) relative to the cylinder (3) can be increased by increasing the overlap (16) and / or can be reduced by reducing the overlap (16).

12. The buffer device (1) according to any one of the preceding claims, wherein: The overlap (16) at the flow cross section (17) of the at least one flow channel (42) can be automatically reduced or eliminated by a speed difference (22) between the piston (5) and the cylinder (3) and a speed reference curve (19), wherein the speed difference (22) can be brought about by at least one possibly present further accumulator (18) and / or the at least one accumulator (20) to effect a relative position of the at least one regulating piston (12) relative to the piston (5).

13. The buffer device (1) according to any one of the preceding claims, wherein: The overlap (16) at the flow cross section (17) of the at least one flow channel (42) can be automatically changed by a speed difference (22) of the piston (5) relative to the cylinder (3) relative to a speed reference curve (19), the speed difference being brought about via at least one possibly present further force accumulator (18) and / or the at least one force accumulator (20).

14. The buffer device (1) according to any one of the preceding claims, wherein: During the damping stroke, the speed of the piston (5) can be varied via the relative position of the at least one regulating piston (12) relative to the piston (5) by at least one possibly present further force accumulator (18) and / or the at least one force accumulator (20).

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

16. The buffer device (1) according to any one of the preceding claims, wherein: The at least one piston rod (6) is moved relative to the cylinder (3) directly or indirectly via the movable furniture part (2), preferably via a linear movement, a rotational movement and / or a pivoting movement.

17. The buffer device (1) according to any one of the preceding claims, wherein: The damping device (1) comprises a sealing element (24) through which the piston rod (6) can move, wherein the sealing element (24) - is configured as a brake element (25), and / or - acts in parallel with the at least one flow channel (42) and / or the at least one control partition (29) in the direction of passage of the buffer fluid (4), and / or - acting in series with the at least one flow channel (42) and / or the at least one control partition (29) in the direction of passage of the buffer fluid (4).

18. The buffer device (1) according to any one of the preceding claims, wherein The damping device (1) comprises a fluid chamber (7) filled with a damping fluid (4), which is bounded at least by the cylinder (3), by a possibly present sealing element (24), by the piston (5) and / or by the piston rod (6).

19. The buffer device (1) according to claims 17 and 18, wherein: The buffer device (1) comprises a constant volume maintaining element (26), which maintains the volume provided for the buffer fluid (4) in the fluid chamber (7) constant in any position of the piston (5) together with the piston rod (6), and / or wherein the sealing element (24) together forms the constant volume maintaining element (26) and is movable relative to the cylinder (3) and is loaded with force on the side of the sealing element facing away from the fluid chamber, preferably by means of a possible additional accumulator (18).

20. The buffer device (1) according to any one of the preceding claims, wherein: The at least one regulating piston (12) is movable in a translational manner relative to the piston (5) and / or the at least one control partition (29) during a damping stroke, preferably in the longitudinal direction, dependent on the displacement of the piston (5) and / or dependent on the speed.

21. The buffer device (1) according to any one of the preceding claims, wherein: The piston (5) and / or the at least one control diaphragm (29) are constructed so that, during the buffer stroke, through the longitudinal movement of the piston (5), the piston (5) can rotate relative to the at least one control diaphragm (29) in the cylinder (3), and / or the at least one control diaphragm (29) can rotate relative to the piston (5).

22. The buffer device (1) according to claim 21, wherein The piston (5) comprises at least two, preferably exactly two, flow channels (42), wherein it is preferably provided that the at least two flow channels (42) are arranged symmetrically on the end side (30) of the piston (5), and / or The at least one flow channel (42) is arranged at the end side (30) of the piston (5), and / or the at least one control partition (29) is arranged at the end side (30) of the piston (5), and / or The piston (5) and the at least one control partition (29) are designed to be coupled to each other in motion in the longitudinal direction during the damping stroke and / or to be decoupled from each other in the rotational direction (32) during the damping stroke, and / or - the flow cross section (17) can be varied by a rotation of the piston (5) relative to the at least one control partition (29) and / or a rotation of the at least one control partition (29) relative to the piston (5), and / or The at least one control partition (29) and the piston (5) are designed to be rotatable relative to one another so that during the damping stroke the flow cross section (17) can preferably be reduced in the longitudinal direction in a manner dependent on the displacement of the piston (5) and / or in a manner dependent on the speed.

23. The buffer device (1) according to claim 21 or 22, wherein: The damping device (1) comprises a hollow piston rod, via which the piston (5) can be rotated relative to the at least one control partition (29), wherein it is preferably provided that the hollow piston rod is particularly preferably arranged directly on the piston (5) and / or that the hollow piston rod is guided by a sliding guide rail which is particularly preferably arranged on the cylinder body (3) and / or is twisted.

24. The buffer device (1) according to any one of claims 21 to 23, wherein: The buffer device (1) comprises a magnet (35), preferably a rod magnet and / or a permanent magnet, by means of which the at least one control diaphragm (29) can be rotated relative to the piston (5), wherein it is preferably provided that the magnet (35) is particularly preferably arranged directly on the at least one control diaphragm (29) and / or the magnet (35) can be rotated via at least one metal belt (36), particularly preferably a steel belt, which is particularly preferably arranged on the cylinder (3).

25. The buffer device (1) according to claim 24, characterized in that At least two metal strips (36) are provided, and / or the at least one metal strip (36) is arranged in a twisted manner on the cylinder (3).

26. The buffer device (1) according to any one of claims 21 to 25, wherein: The buffer device (1) comprises a spring (28) for applying a force to the piston (5), wherein the spring is arranged at the at least one control diaphragm (29), wherein the at least one control diaphragm (29) can rotate relative to the piston (5) via the spring (28), wherein it is preferably arranged that the spring (28) is fixedly connected to the at least one control diaphragm (29), and / or the at least one control diaphragm (29) can rotate by compression of the spring (28).

27. The buffer device (1) according to any one of claims 21 to 26, wherein: The buffer device (1) comprises an impeller (37), and the at least one control baffle (29) can be rotated relative to the piston (5) by means of the impeller, wherein it is preferably arranged that the impeller (37) is particularly preferably directly arranged at the at least one control baffle (29), and / or can be rotated by the passage of the buffer fluid (4), and / or comprises at least two, particularly preferably four blades (38).

28. The buffer device (1) according to any one of claims 21 to 27, wherein: The buffer device (1) comprises at least one telescopic device (39), by means of which the at least one control partition (29) can be rotated relative to the piston (5), wherein it is preferably provided that the at least one telescopic device (39) can be rotated via a guide (40) which is particularly preferably twisted and / or arranged on the cylinder body (3), and / or comprises a plurality of telescopic parts (41) which can be telescopic within each other and / or can be telescopic relative to each other.

29. The buffer device (1) according to any one of the preceding claims, wherein: The at least one regulating piston (12) acts in parallel and / or in series with a sealing element (24) which may be present and / or the at least one control partition (29).

30. A method for controlling the movement of a movable furniture part (2) by adjusting the damping speed via a damping device (1) according to any one of the preceding claims, characterized in that When the speed of the movable furniture part (2) relative to at least one damping device (1) and / or the speed of the piston (5) relative to the cylinder (3) is greater than a rated speed, at least one regulating piston (12) is moved relative to the piston (5) against a restoring force, so that the flow cross section (17) of at least one flow channel (42) is reduced and the movable furniture part (2) and / or the piston (5) are braked to the rated speed, wherein in particular it is provided that the at least one damping device (1) is inactivated when the speed is less than the rated speed.

31. The method according to claim 30, wherein: The at least one regulating piston (12) is moved relative to the at least one piston (5), in particular automatically, via at least one force accumulator (20), whereby the speed of the piston (5) relative to the cylinder (3) is adapted to a speed reference curve (19) which is preferably linear and / or defined via at least one further force accumulator (18), wherein it is preferably provided that at least one fluid outlet opening (14) of the at least one regulating piston (12) is moved relative to at least one outlet (11) of the piston (5).

32. The method according to claim 30 or 31, wherein: - adjusting the speed of the piston (5) relative to the cylinder (3) during the damping stroke by means of an overlap (16) at the flow cross section (17) of the at least one flow channel (42), preferably an overlap (16) of at least one possible fluid outlet opening (14) and at least one possible outlet (11), wherein the overlap (16) defines the flow cross section (17) of the damping fluid (4) and / or the flow cross section (17) is changed by the relative position of the at least one regulating piston (12) relative to the piston (5), - continuously varying the overlap (16) and / or the speed variation of the piston (5) relative to the cylinder (3) during the damping stroke, - the at least one regulating piston (12) and the piston (5) are designed as a pressure balance, wherein, when the pressure of the buffer fluid (4) on the at least one regulating piston (12) and / or in the region of the overlap (16) increases, the overlap (16) at the flow cross section (17) of the at least one flow channel (42) decreases, and / or when the pressure on the at least one regulating piston (12) and / or in the region of the overlap (16) decreases, the overlap (16) at the flow cross section (17) of the at least one flow channel (42) increases, - during a damping stroke of the damping device (1), the overlap (16) at the flow cross section (17) of the at least one flow channel (42) is varied by means of the at least one force accumulator (20), wherein the speed of the piston (5) relative to the cylinder (3) is increased by increasing the overlap (16) and / or is reduced by reducing the overlap (16), - the overlap (16) at the flow cross section (17) of the at least one flow channel (42) is automatically reduced or eliminated by a speed difference (22) of the piston (5) relative to the cylinder (3) relative to a speed reference curve (19), wherein the speed difference (22) is brought about by at least one possibly present further force accumulator (18) and / or the at least one force accumulator (20) to adjust the relative position of the at least one regulating piston (12) relative to the piston (5), and / or The overlap (16) is automatically varied by a speed difference (22) of the piston (5) relative to the cylinder (3) relative to a speed reference curve (19), the speed difference being brought about via at least one possibly present further force accumulator (18) and / or the at least one force accumulator (20).

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

34. A piece of furniture having at least one cushioning device (1) according to any one of claims 1 to 29, wherein: At least one movable furniture part (2) can be damped relative to the furniture carcass between an open position and a closed position by means of the at least one damping device (1).

35. A door having at least one buffer device (1) according to any one of claims 1 to 29, wherein: The door can be damped relative to the door frame between an open position and a closed position by means of the at least one damping device (1).

36. A window having at least one buffer device (1) according to any one of claims 1 to 29, wherein: The window is capable of being cushioned relative to the window frame between an open position and a closed position by means of the at least one cushioning device (1).

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