WO2024020608A1

WO2024020608A1 - Damping device for damping a movement of a movable part, in particular furniture part, window and/or door

Info

Publication number: WO2024020608A1
Application number: PCT/AT2023/060215
Authority: WO
Inventors: Philip SCHLUGE
Original assignee: Julius Blum Gmbh
Priority date: 2022-07-26
Filing date: 2023-07-05
Publication date: 2024-02-01
Also published as: AT526392A1

Abstract

The invention relates to a damping device (1) for damping a movement of a movable part, more particularly furniture part, window and/or door, having – a cylinder (3), - a piston (5) guided, in particular linearly, in the cylinder (3) and damped by a damping fluid (4), and – a piston rod (6) connected to the piston (5), wherein the damping device (1), preferably the piston (5), comprises at least one flow channel (9) for the passage of the damping fluid (4), wherein the flow channel (9) has a passage cross section (11), and the damping device (1) comprises at least one diaphragm (10) for adjusting the passage cross section (11) for the passage of the damping fluid (4) in a damping stroke, wherein the piston (5) and/or the at least one diaphragm (10) is/are designed such that during a damping stroke, the piston (5) can be rotated relative to the at least one diaphragm (10) and/or the at least one diaphragm (10) can be rotated relative to the piston (5) and/or the at least one diaphragm (10) can be rotated within the cylinder (3) via a longitudinal movement of the piston (5).

Description

Damping device for damping a movement of a movable

Part, especially furniture part, window and/or door

The invention relates to a damping device for damping a movement of a movable part, in particular a furniture part, window and/or door, with a cylinder, a piston guided in the cylinder, in particular linearly, and damped by a damping fluid, and a piston connected to the piston Piston rod, wherein the damping device, preferably the piston, comprises at least one flow channel for the passage of the damping fluid, the flow channel having a passage cross section, and the damping device comprises at least one aperture for adjusting the passage cross section for the passage of the damping fluid in a damping stroke. Furthermore, the invention relates to the use of such a damping device. Furthermore, the invention relates to a piece of furniture, a door or a window with at least one such damping device.

A damping device is already known from DE 20 2011 108 658 Ul, which uses a volume constant element in the form of a floating seal with a groove control in a return flow area of a damping fluid in order to achieve a configuration of the groove that is adapted to the volume change caused by a sealing element and a uniform damping To enable characteristics. Through the groove, varying volume flows can be generated for different operating positions, so that a level of damping force provided by the damping device can be achieved, depending on the distance from the piston, at the start of damping, which is higher than at the end of damping.

The disadvantage of the state of the art is that in the course of

Damping stroke, the sealing element is also moved over the groove with a variable cross section, so that in the area of the groove With a large cross-section, only a low braking performance is required. In addition, the damping device is given

Groove cross section cannot be flexibly adjusted to changing furniture conditions, since different dimensions of the movable furniture part, different movement trajectories and/or movement sequences lead to varying damping characteristics. The damping device must be individually adapted to each specific requirement in use and each specific piece of furniture via the structural design, such as the geometry of the groove. Furthermore, apart from a uniform damping characteristic, no adjustment to a desired speed profile of the damping device can take place - especially when piston speeds change.

The objective technical task of the present invention is therefore to provide a damping device that is improved compared to the prior art, in which the disadvantages of the prior art are at least partially eliminated, and which is characterized in particular by a high and / or constant damping performance over the entire damping stroke.

This task is solved by the features of claim 1.

It is therefore provided according to the invention that the piston and/or the at least one aperture is designed such that the piston is relative to the at least one aperture and/or the at least one aperture is relative to the piston and/or the at least one aperture within the cylinder can be rotated in the course of a damping stroke via a longitudinal movement of the piston.

This makes it possible for the damping performance to be adapted to the speed of the piston without the need for grooves are required in the cylinder, which undesirably affect a damping characteristic over a damping stroke.

Due to the rotation, the at least one aperture can partially cover the at least one flow channel to reduce a passage cross section. For example, at least one aperture opening and the at least one flow channel are congruent at the beginning of the damping stroke, with the damping cross section being reduced, preferably to 0, in the course of the damping stroke - in particular in order to set a damping performance in the course of the damping.

In addition, there is the positive property that through the interaction of the at least one aperture with the at least one flow channel of the piston, the passage cross section for the damping fluid can be adapted to a desired damping characteristic and/or a passage of the damping fluid can be adjusted in the course of the damping stroke. For example, the at least one aperture can have the at least one flow channel starting from a start of a damping stroke - in which there is generally a high speed of the piston - to an operating position in the area of the end of the damping stroke - in which a low speed of the piston is generally desired - cover to a greater extent, so that the passage cross-section is preferably successively reduced for damping purposes.

Particularly preferably it is provided that the piston relative to the at least one aperture and/or the at least one aperture relative to the piston and/or the at least one aperture within the cylinder in the course of a damping stroke via a longitudinal movement of the piston and by one of the at least one aperture and means separate from the damping fluid for rotating the at least one aperture can be rotated, so that the passage cross section can be reduced. Preferably, the at least one aperture comprises an aperture opening for the passage of the damping fluid. However, this is generally not absolutely necessary. The at least one aperture can completely, partially and/or not cover the at least one flow channel during the course of the damping stroke in order to regulate the amount of passage of the damping fluid through the piston.

Preferably, the at least one aperture is arranged in front of the piston in the direction of passage of the damping fluid during a damping stroke, particularly preferably on an end face of the piston.

Particularly preferably, the piston comprises the at least one flow channel, it being generally also conceivable that the at least one flow channel is formed by an area between the piston and the cylinder and is partially covered by the at least one aperture during the course of a damping stroke.

For example, a groove in the cylinder can also be reduced and/or enlarged in cross section by the at least one aperture in the course of the damping stroke. In general, the groove can also be present in addition to a flow channel within the piston, which is partially covered by the at least one aperture in the course of the damping stroke.

The flow channel is preferably designed in such a way that the damping fluid passes or flows through in the course of a damping stroke from an area in front of the piston into an area in the flow direction behind the piston or within the piston. The damping fluid may generally be in the form of a liquid or a gas. As stated at the beginning, protection is also desired for the use of such a damping device on a piece of furniture, a door and/or a window.

The damping device offers the advantage that a damping stroke can be achieved over a large angular range of the part to be damped. Conventional damping devices are designed to dampen the area just before a closed position in the range of approximately 20°. The damping device according to the invention, on the other hand, can dampen angular ranges over 90 °, whereby an increased effort required to move the part can be reduced, in particular through the interaction between the at least one aperture and the at least one flow channel; for example by essentially rendering the damping device inactive through the damping cross section. The user of the part therefore generally does not have to work against the damping device, preferably over defined angular ranges, with an area in front of the closed position being effectively dampenable, preferably depending on a speed of the piston.

As stated at the beginning, protection is also sought after for a piece of furniture with at least one such damping device, a door with at least one such damping device and a window with at least one such damping device, with a movable furniture part relative to a furniture body, the door relative to a door frame or that Window can be dampened relative to a window frame by the at least one damping device between an open position and a closed position.

The at least one damping device can be used externally as an additional component for retrofitting and/or used as an integrated component. The at least one damping device can be integrated, for example, in a furniture fitting, a window fitting or a door fitting. Advantageous embodiments of the invention are defined in the dependent claims.

It is preferably provided that the damping device is suitable for furniture or building fittings and comprises a cylinder in which a damping fluid is arranged, the piston being movable at a speed through the damping fluid in the course of a damping stroke, at least one flow channel with a flow cross section being provided is, through which the damping fluid can pass through the piston during the damping stroke, with at least one control piston being provided, which is movably, preferably displaceably, mounted in and/or on the piston, the flow cross section of the flow channel being determined by a movement of the control piston relative to the piston can be changed, with at least one force accumulator, preferably a restoring spring, being provided, which applies a restoring force to the control piston relative to the piston, which counteracts at least one flow force that can be exerted on the control piston by the damping fluid during the damping stroke.

It is preferably provided that at least one flow channel with a flow cross section is provided, through which the damping fluid can pass through the piston during the damping stroke, characterized in that at least one control piston is provided, which is movably, preferably displaceably, mounted in and/or on the piston , wherein the flow cross section of the at least one flow channel can be changed by moving the at least one control piston relative to the piston, with at least one force accumulator, preferably a restoring spring, being provided, which applies a restoring force to the at least one control piston relative to the piston, which is at least counteracts a flow force that can be exerted on the at least one control piston by the damping fluid during the damping stroke, with at least one control panel being provided on which a Flow force and pressure drop proportional to the speed of the piston takes place, a target speed for the piston (5) depending on a position of the piston relative to the cylinder being predetermined, with the at least one control piston counteracting at a speed of the piston which is greater than the target speed the restoring force can be moved relative to the piston in such a way that the flow cross section of the at least one flow channel can be reduced, preferably the target speed for the piston, which is dependent on a position of the piston relative to the cylinder, by at least one further force accumulator, particularly preferably a spring, which has the at least a control piston is subjected to a force counter to the restoring force, and/or is predetermined by an adjustability of a diaphragm opening of the at least one control diaphragm and/or by at least one groove in an inner cylinder wall with a changing groove cross section.

Particularly preferably, it is provided that at least one control orifice is provided, at which a pressure drop proportional to the flow force and the speed of the piston occurs, with a target speed for the piston dependent on a position of the piston relative to the cylinder being predetermined, the control piston being at a speed of the piston, which is greater than the target speed, can be moved relative to the piston against the restoring force in such a way that the flow cross section of the flow channel can be reduced, preferably whereby the target speed for the piston, which is dependent on a position of the piston relative to the cylinder, by at least a spring which applies a force to the control piston counter to the restoring force, and/or through an adjustability of an aperture opening of the at least one control aperture, and/or through at least one groove in one Cylinder inner wall is specified with a changing groove cross section.

According to an advantageous embodiment of the invention, it is provided that the piston comprises at least, preferably precisely, two flow channels, it being preferably provided that the at least two flow channels are arranged symmetrically on an end face of the piston.

A symmetrical arrangement means that component components such as the piston are loaded symmetrically, whereby the service life of the damping device can be increased and/or tilting of component components such as the piston in the cylinder can be prevented. If there is a large number of flow channels, these can be arranged at the front of the piston at a distance from an axis of symmetry of the piston and the passage cross section can be closed and / or opened in a defined manner by the at least one aperture when the piston or the at least one aperture rotates fnet.

It is advantageously provided that the at least one flow channel is arranged on an end face of the piston and/or the at least one aperture is arranged on the end face of the piston.

This allows damping fluid to flow directly centrally into the piston, with no lateral openings on the piston being required, over which damping fluid flows from an area in front of the piston into an area behind the piston and/or, if necessary, via a sealing element. In general, a fluid space in the area in front of the piston is reduced in the course of the damping stroke by the movement of the piston and the fluid space in the area behind the piston is increased accordingly. Particularly preferably, it is provided that the piston and the at least one diaphragm are designed to be movement-coupled to one another in the longitudinal direction during the damping stroke and/or to be decoupled from one another in the rotational direction during the damping stroke.

The longitudinal movement of the piston and/or the at least one aperture, which occurs along an axis of the damping device, can mediate the rotational movement of the piston and/or the at least one aperture.

According to an advantageous embodiment of the invention, it is provided that the passage cross section can be changed by rotating the piston relative to the at least one aperture and/or the at least one aperture relative to the piston.

It has proven to be advantageous that the damping device comprises a hollow piston rod, preferably separate from the piston rod, through which the piston can be rotated relative to the at least one aperture, it preferably being provided that the hollow piston rod, particularly preferably directly, on the Piston is arranged and / or the hollow piston rod is guided over a, particularly preferably arranged and / or twisted, slide track on the cylinder.

In general, the piston can be guided in the cylinder without moving in the direction of rotation during the damping stroke and the at least one diaphragm is rotated or the at least one diaphragm can be guided in the cylinder without moving in the direction of rotation during the damping stroke and the piston is rotated, with an overlap of both rotational movements also being conceivable is .

The hollow piston rod is preferably arranged on the side of the piston facing away from the end face of the piston between the cylinder and the piston, with the hollow piston rod during the Damping stroke is guided along the link path in order to move the piston relative to the aperture. The slide track can, for example, be designed as a groove in the cylinder, along which the hollow piston rod is moved, whereby twisting can cause a rotational movement when the piston moves longitudinally.

In general, the piston and the at least one aperture can be designed to be movement-coupled to one another in the longitudinal direction, so that the at least one aperture is moved together with the piston longitudinally along an axis of the damping device in the course of a damping stroke.

An advantageous variant of the present invention is that the damping device comprises a magnet, preferably a bar magnet and/or permanent magnet, through which the at least one aperture can be rotated relative to the piston, it preferably being provided that the magnet, particularly preferably directly, is arranged on the at least one aperture and / or the magnet can be rotated via at least one metallic band, particularly preferably steel band, particularly preferably arranged on the cylinder.

Through a magnetic interaction between the magnet and the metallic band located on the cylinder, the at least one aperture can be rotated within the cylinder during a longitudinal movement of the at least one aperture in order to reduce (during damping) and/or increase the passage cross section ( during a reset of the damping device).

It is particularly preferred that at least two metallic bands are provided and/or that at least one metallic band is arranged twisted on the cylinder. Two metallic bands have proven to be particularly cheap

Rotation of a bar magnet has been proven, which can be guided along the metallic bands on the cylinder along the twist (on an inner surface of the cylinder with a changed angular range in the longitudinal direction for the rotation of the at least one aperture).

In one exemplary embodiment of the invention it is provided that the damping device comprises a spring for applying force to the piston, which is arranged on the at least one aperture, the at least one aperture being rotatable relative to the piston by the spring, it being preferably provided that the spring is firmly connected to the at least one aperture and/or the at least one aperture can be rotated via compression of the spring.

If a spring is compressed with a fixed free end, this compression automatically causes a rotation of another free end of the spring. This inherent rotation in the compression process can be used to rotate the at least one diaphragm arranged on the spring during the damping stroke. A degree of rotation can be adjusted to a desired dimension, for example via a spring length, a spring cross section or a diameter of the spring.

According to a preferred exemplary embodiment of the invention, it is provided that the damping device comprises an impeller, through which the at least one aperture can be rotated relative to the piston, it being preferably provided that the impeller is arranged, particularly preferably directly, on the at least one aperture and / or can be rotated via a passage of damping fluid and / or comprises at least two, particularly preferably four, wings. Particularly preferably, the vanes are inclined in the longitudinal direction of the damping device, so that a rotation of the at least one aperture arranged on the impeller can be generated by the passage of the damping fluid via the at least one aperture into the piston and/or vice versa.

Furthermore, it is preferably provided that the damping device comprises at least one telescopic device, through which the at least one aperture can be rotated relative to the piston, it preferably being provided that the at least one telescopic device has a, particularly preferably twisted and/or arranged on the cylinder, Guide is rotatable and / or comprises several telescopic parts that can be telescoped into one another and / or to one another.

The telescopic device is preferably arranged between the side facing the end face of the piston and the cylinder on the at least one aperture. The guide can, for example, be designed as a twisted link on the cylinder and/or the telescopic device in order to rotate the diaphragm via the telescopic device in the course of the damping stroke. During the damping stroke, the telescopic device can be compressed in the longitudinal direction and moved into the starting position while the damping device is being reset.

The arrangement and structural designs as well as the positioning of the hollow telescopic rod can be used in the telescopic device and vice versa.

In a further embodiment, it can be provided that the damping device comprises a sealing element, wherein the sealing element is designed as a braking element and/or acts parallel to the at least one flow channel in the passage direction and/or acts in series with the at least one flow channel in the passage direction . In principle, the sealing element can be provided to prevent the passage of damping fluid between the cylinder and the outside of the piston, so that the damping device is completely blocked when the flow channel is completely covered by the at least one aperture. However, the sealing element can also allow a small amount of damping fluid to pass through, so that the sealing element acts as a braking element and/or damping is generated even when the flow channel is completely closed.

According to an advantageous embodiment of the invention, it is provided that the piston comprises a power valve in the form of a control piston, wherein the passage cross section and/or a further passage cross section of a fluid outlet opening of the piston can be changed by the power valve, it being preferably provided that the power valve is parallel and / or acts in series with an optionally present sealing element and / or the at least one aperture.

If the power valve is connected in parallel to the at least one orifice and/or the braking element, a passage via the braking element and/or the at least one orifice can act as a control pressure for the power valve, with a damping device being provided in the sense of a bypass line, which is connected to the damping device can preferably switch between two operating positions - an active and a suppressed damping via the at least one flow channel.

The power valve can adjust a damping effect of the damping device in such a way that the speed of the piston is adapted to a desired reference speed, with an increased damping effect being generated at the beginning of a damping stroke, where high piston speeds occur, which continues until the end of the damping stroke, where low piston speeds desired are, reduced. The desired reference speed can represent a linear curve of a speed over a damping path, although other reference speed curves are generally also possible. This means that the damping effect can be generated in a distance-dependent and speed-dependent manner as a function of the desired reference speed in the course of the damping stroke.

Particularly preferably, it is provided that the control piston is arranged on the outside of the piston and/or inside the piston, wherein it is preferably provided that the at least one control piston is prestressed relative to the piston by a control piston spring and/or the piston by an optionally present spring can be acted upon with force and/or the power valve is designed as a pressure compensator.

The control piston can convey a pressure difference on the piston via the function as a pressure compensator, with the passage cross section and/or the further passage cross section at the at least one flow channel and/or the fluid outlet opening being reduced or increased depending on the pressure differences present on the piston. The control piston can therefore act as a pressure compensator, with damping fluid preferably constantly flowing through the piston during the damping stroke.

It is particularly preferably provided that the damping device comprises a fluid space filled with damping fluid, which is delimited at least by the cylinder, by an optionally present sealing element, by the piston and/or by the piston rod.

According to a preferred embodiment, it is provided that the damping device comprises a volume-constant element which keeps the volume available for the damping fluid in the fluid space constant in every position of the piston including the piston rod holds, and/or wherein the sealing element also forms the volume constant holding element and is movable relative to the cylinder and is subjected to force on its side facing away from the fluid space, preferably by an optionally present spring.

According to a particularly preferred exemplary embodiment, it is provided that the at least one diaphragm and the piston are designed to be rotatable relative to one another in such a way that, in the course of the damping stroke, the passage cross section can be reduced, preferably longitudinally as a function of the path and/or as a function of the speed of the piston.

As a result, the damping performance during the damping stroke is adapted to a desired damping effect, whereby the damping performance can be regulated depending on an axial position of the piston and/or on the speed of the piston within the cylinder in order to automatically adjust the speed of the movable part to be able to achieve a desired reference speed - in particular via a power valve that may be present.

Further details and advantages of the present invention are explained in more detail below using the description of the figures with reference to the exemplary embodiments shown in the drawings. Show in it:

Fig. 1 a damping device according to a preferred one

From the embodiment, in which a relative rotation between the diaphragm and the piston is generated via a bar magnet, in a perspective view with a sectional view and an enlarged detailed section,

Fig. 2 the damping device according to the exemplary embodiment according to FIG. 1 during a damping stroke, Fig. 3a-3d the aperture and the bar magnet of the damping device according to the exemplary embodiment according to FIG. 1 in an exploded view, a perspective view and a view from the front with the bar magnet hidden in three different positions along the

damping strokes,

Fig. 4a-4c the aperture of the damping device according to the exemplary embodiment according to FIG. 3a each in a perspective view, a view from the front and a sectional view in different positions along the damping stroke,

Fig. 5 a damping device according to a further preferred embodiment, wherein a rotation is generated via a spring, in a perspective sectional view with an enlarged detail section and a sectional view from the side with an enlarged detail section,

Fig. 6 the damping device according to the exemplary embodiment according to FIG. 5 during the damping stroke,

Fig. 7a, 7b the damping device according to the exemplary embodiment according to FIG. 5 in two different positions during the damping stroke with the spring hidden,

Fig. 8 a damping device according to a further preferred embodiment, wherein a rotation is generated via a telescopic device, in a perspective sectional view with an enlarged detail and a sectional view from the side with an enlarged detail,

Fig. 9 the damping device according to the exemplary embodiment according to FIG. 8 during a damping stroke,

Fig. 10a-10c the telescopic device of the damping device according to the exemplary embodiment according to FIG. 8 in one View from the side before and after a damping stroke, in an exploded view and perspective view before the damping stroke and in a perspective view after the damping stroke,

Fig. 11 a damping device according to a further preferred embodiment, with rotation being generated via an impeller, in a perspective view and one

exploded view,

Fig. 12a, 12b the damping device according to the exemplary embodiment according to FIG. 11 in a perspective

Sectional view before and during one

damping strokes,

Fig. 13a, 13b the damping device according to the exemplary embodiment according to FIG. 11 in a sectional view from the side before and during a damping stroke,

Fig. 14 a damping device with a power valve in

Shape of a translationally movable control piston in a perspective view with an enlarged detail.

Fig. 1 shows a damping device 1 for damping a movement of a movable part such as a furniture part, window or a door with a cylinder 3, a piston 5 which is linearly guided in the cylinder 3 and dampened by a damping fluid 4 and a piston rod 6 connected to the piston 5 .

The piston 5 and the diaphragm 10 are designed in such a way that when the piston 5 moves relative within the cylinder 3, the diaphragm 10 can be rotated relative to the piston 5 (in the course of a damping stroke via a longitudinal movement of the piston 5 and) within the cylinder 3 is . Fig. 2 differs from Fig. 1 only to the effect that the piston rod 6 has penetrated further into the cylinder 3 for damping, as a result of which the diaphragm 10 has been rotated relative to the piston 5.

To rotate the diaphragm 10, the damping device 1 comprises a magnet 15 in the form of a bar magnet designed as a permanent magnet, through which the diaphragm 10 can be rotated relative to the piston 5 in the course of the damping stroke.

The magnet 15 is arranged directly on the aperture 10, the magnet 15 being rotatable via two metallic bands 16 arranged on the cylinder 3 in the form of twisted steel bands. The bands 16 are arranged on the outside of the cylinder 3 , whereby the bands 16 can generally also be arranged on an inner surface of the cylinder 3 . The number of bands 16 is generally arbitrary - the number preferably being identical to a number of free ends of the magnet 15.

In general, a kinematic reversal of the rotation is also possible, with the piston 5 being rotated relative to the aperture 10 when the piston 5 moves in the cylinder 3. This can be provided, for example, in a preferred exemplary embodiment, wherein the rotation of the damping device 1 is generated by a hollow piston rod, the piston 5 being rotatable relative to the diaphragm 10 through the hollow piston rod. The hollow piston rod can be arranged directly on the piston 5 and guided, for example, via a twisted slide track arranged on the cylinder 3 (an analogous movement mechanism to the twisted bands 16 with a positive guidance along the slide track).

Fig. 3a shows an exploded view of component components in interaction with the aperture 10 of the damping device of the embodiment with a magnet 15. A damping performance, which is given as a function of a difference speed between an actual speed of the piston 5 and a desired reference speed of the piston 5, is generated in the damping device 1 via an interaction between the diaphragm 10 and the piston 5. For this purpose, the piston 5 comprises at least one flow channel 9 for the passage of the damping fluid 4, the flow channel 9 having a passage cross section 11, and the damping device 1 the aperture 10 for adjusting the passage cross section 11 for the passage of the damping fluid 4 in a damping stroke via relative rotation between aperture 10 and piston 5.

Fig. 3b to Fig. 3d visualize different diaphragm positions along the damping stroke, with the passage cross section 11 being changed by the magnet 15, which is hidden in the illustrations. By rotating the diaphragm 10 relative to the piston 15, the passage cross section 11 can be enlarged and reduced, whereby a damping performance can be adjusted.

The piston 5 comprises exactly two flow channels 9, the two flow channels 9 being arranged symmetrically on an end face 12 of the piston 5. The number of flow channels 9 is generally arbitrary.

The diaphragm 10 is arranged on the end face 12 of the piston 5 , although this does not necessarily have to be necessary even with flow channels 9 arranged on the end faces 12 .

The piston 5 and the at least one diaphragm 10 are designed to be coupled to one another for movement in the longitudinal direction 32 during the course of the damping stroke and to be decoupled from one another in the direction of rotation 33 during the course of the damping stroke. Fig. 4a to Fig. 4c illustrate a movement coupling between aperture 10 and piston 5 in the longitudinal direction with simultaneous relative rotation orthogonal to the longitudinal direction of the damping device 1.

Based on the relative positioning in Fig. 4b shows the passage cross section 11 in FIG. 4 a changed by the rotation of the piston 5 relative to the aperture 10 (with active movement of the aperture 10 in the direction of rotation). In Fig. 4c is the passage cross section 11 for the damping fluid 4 compared to FIG. 4b greatly reduced.

Fig. 5 shows a further possibility for rotation between the diaphragm 10 and the piston 5 in order to change the passage cross section 11 by rotation, with a spring 17a being provided for the rotation. The spring 17a can, for example, represent an already existing return spring of the damping device 1, which is used in the sense of a double function to adjust the passage cross section 11 via the aperture 10.

In the two enlarged details of the sectional views it can be seen that the damping device 1 includes a spring 17a for applying force to the piston 5, which is arranged directly (indirectly is also conceivable) on the diaphragm 10. By compressing the spring 17a, a free end of the spring 17a arranged on the panel 10 automatically rotates, the panel 10 being rotated relative to the piston 5 by the spring 17a in order to adapt the passage cross section 11 to a desired damping performance.

In this exemplary embodiment, the spring 17a is fixed to the aperture

10 is connected and the aperture 10 is about the compression of the

Spring 17a rotatable, generally alternatively or in In addition, a spring 17a for rotation of the piston 5 can also be arranged on the piston 5.

Fig. 6 differs from Fig. 5 only to the effect that the piston 5 was moved in the direction of the damping stroke within the cylinder 3, whereby the passage cross section 11 changed via the spring 17a.

To illustrate the rotation of the diaphragm 10 relative to the piston 5 - initiated by the spring 17a - are shown in Fig. 7a and Fig. 7b shows two varying rotational positions of the aperture 10 with the spring 17a hidden with different passage cross sections 11.

The spring 17a provided for the rotation of the diaphragm 10 is securely fastened with a free end to the inside of the cylinder 3, so that when the spring 17a is compressed, a rotational movement (through a connection of the spring 17a to the diaphragm 10) is imparted to the diaphragm 10 is used to adjust the passage cross section 11 of the flow channel 9 for the piston 9.

Fig. 8 shows a further exemplary embodiment of the damping device 1, wherein the damping device 1 comprises a telescopic device 20, through which the diaphragm 10 can be rotated relative to the piston 5.

The telescopic device 20 is supported on the front side on the inside of the cylinder 3, with a guide 21 twisted along a lateral surface being used for rotation in interaction with a guide pin. The telescopic device 20 is arranged within a restoring spring 17 , with both an arrangement outside the spring 17 and a damping device 1 without a spring 17 being possible. By attaching the telescopic device 20 to one end of the cylinder 3 (analogous to the rotation of the aperture 10 via the spring 17), a fixed point for the rotation of the aperture 10 (due to the movement coupling between the aperture 10 and the telescopic device 20) in the course of the damping stroke given during the telescoping movement.

Fig. 9 differs from Fig. 8 only to the effect that the damping device 1 was moved along the damping stroke, whereby the telescopic device 20 is in a telescoped position with a changed passage cross section 11.

Fig. 10a shows that the telescopic device 20 for rotating the diaphragm 10 via the telescopic device 20 comprises three telescopic parts 22 which can be telescoped into one another and towards one another, which are shown in the telescoped out and telescoped in state.

In Fig. 10b, the components of the telescopic device 20 are shown in an exploded view and in the assembled state, with a spring 17 supporting the telescoping process - but is generally not absolutely necessary.

In Fig. 10c, the telescopic device 20 is in a fully telescoped state, in which the aperture 10 has generally been rotated maximally relative to the piston 5 relative to an initial position.

Fig. 11 shows a further embodiment of the damping device 1 in an exploded view and in an assembled state, with an impeller 18 being used to rotate the aperture 10.

In the two positions along a damping stroke according to FIG. 12a and Fig. 12b it can be seen that the aperture 10 is rotated relative to the piston 5 by the impeller 18 in the course of the damping movement. The impeller 18 is directly in this example arranged on the panel 10 and rotatable via a passage of damping fluid 4, with a large number of wings 19 being provided, which cause the panel 10 to rotate due to the damping fluid 4 flowing past.

The impeller 18 acts analogously to a turbine, with a meshing movement being generated between the damping fluid 1 and the vanes 19 to rotate the diaphragm.

Fig. 13a and Fig. 13b differ from Fig. 12a/12b simply by changing the perspective of the sectional view. In general, a sealing element 7 can be provided, through which the piston rod 6 moves. This damping device 1 comprises a sealing element 7, wherein the sealing element 7 is designed as a braking element 23 and acts in series with the flow channel 9 in the direction of passage of the damping fluid 4.

In general, it can also be provided that the sealing element 7 acts in the form of a braking element 23 in the direction of passage parallel to the flow channels 9.

As in Fig. 14 can be seen, in addition to the rotation of the aperture 10 (all embodiments) of the piston 3 can also include a power valve 24 in the form of a control piston 25, the passage cross section 11 or a further passage cross section of a fluid outlet opening of the piston 5 passing through the power valve 24 can be changed, with the power valve 24 acting in parallel or in series with the sealing element 7 or the aperture 10.

The control piston 25 can be arranged on the outside of the piston 5, the control piston 25 in this embodiment being arranged inside the piston 5, the control piston 25 being biased relative to the piston 5 by a control piston spring 28 and the piston 5 by a spring 17 can be acted upon with force. As a result, the power valve 24 is designed as a pressure compensator 29. A power valve 24 can be provided on the damping device 1 through a rotatably movable diaphragm 10 and a further power valve 24 via the control piston 25.

The damping device 1 comprises a fluid space 8 filled with damping fluid 4, which is delimited by the cylinder 3, the sealing element 7, the piston 5 and the piston rod 6.

The damping device 1 comprises a volume-constant element 30, which keeps the volume available for the damping fluid 4 in the fluid space 8 constant in every position of the piston 5 including the piston rod 6 and is acted upon by a spring 17 on its side 31 facing away from the fluid space. A sealing element 7 can be designed to be movable relative to the cylinder 3 and/or can also form the volume-constant element 30 - however, this is generally not necessary.

With an aperture of the apertures 10 presented above, the piston 5 can be designed to be rotatable relative to the aperture 10 in such a way that in the course of the damping stroke, the passage cross section 11 can be reduced longitudinally depending on the path or speed of the piston 5.

According to the invention, the damping devices 1 can be used on a movable furniture part, a door or a window, for example a piece of furniture, a door or a window can be equipped with the damping device 1 in order to move the movable furniture part, the door or the window relative to a furniture body , a door frame or a window frame via the damping device 1 between an open position and a closed position.

The damping device 1 is suitable for furniture or building fittings, the piston 5 can be moved at a speed through the damping fluid during a damping stroke, a flow channel with a flow cross section being provided, through which the damping fluid can pass the piston 5 during the damping stroke. The control piston 25 is generally provided in all exemplary embodiments, which is slidably mounted in or on the piston 5, the flow cross section of the flow channel being changeable by a movement of the control piston 25 relative to the piston 5.

The force accumulator 28 in the form of a restoring spring applies a restoring force to the control piston 25 relative to the piston 5, which counteracts at least one flow force that can be exerted on the control piston 25 by the damping fluid during the damping stroke.

A control orifice is provided, at which a pressure drop proportional to the flow force and the speed of the piston 5 occurs, with a target speed for the piston 5 depending on a position of the piston 5 relative to the cylinder 3 being predetermined, with the control piston 25 at a speed of the piston 5, which is greater than the target speed, can be moved relative to the piston 5 against the restoring force in such a way that the flow cross section of the flow channel can be reduced.

The target speed for the piston 5, which depends on a position of the piston 5 relative to the cylinder 3, can be achieved, for example, by a spring, which applies a force to the control piston 25 against the restoring force, by adjusting an aperture opening in the control panel or by a groove in one Cylinder inner wall can be specified with a changing groove cross section.

Claims

Claims Damping device (1) for damping a movement of a movable part, in particular a furniture part, window and/or door

- a cylinder (3),

- a piston (5) guided in the cylinder (3), in particular linearly, and damped by a damping fluid (4) and

- a piston rod (6) connected to the piston (5), the damping device (1), preferably the piston (5), comprising at least one flow channel (9) for the passage of the damping fluid (4), the flow channel (9) having a Has a passage cross section (11), and the damping device (1) has at least one aperture (10) for adjusting the

Passage cross section (11) for the passage of the

Damping fluid (4) in a damping stroke, characterized in that the piston (5) and / or the at least one aperture (10) is designed such that the piston (5) relative to the at least one aperture (10) and / or the at least one aperture (10) can be rotated relative to the piston (5) and/or the at least one aperture (10) within the cylinder (3) in the course of a damping stroke via a longitudinal movement of the piston (5). Damping device (1) according to claim 1, wherein the piston (5) comprises at least, preferably exactly, two flow channels (9), it being preferably provided that the at least two flow channels (9) are symmetrical on an end face (12) of the piston ( 5) are arranged. Damping device (1) according to claim 1 or 2, wherein the at least one flow channel (9) on an end face (12) of the piston (5) is arranged and / or the at least one aperture (10) is arranged on the end face (12) of the piston (5).

4. Damping device (1) according to one of the preceding claims, wherein the piston (5) and the at least one aperture (10) are coupled to one another in the longitudinal direction (32) in the course of the damping stroke and / or in the direction of rotation

(33) are designed to be decoupled from one another in the course of the damping stroke.

5. Damping device (1) according to one of the preceding claims, wherein the passage cross section ( 11) can be changed.

6. Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises a hollow piston rod through which the piston (5) can be rotated relative to the at least one aperture (10), it being preferably provided that the hollow Piston rod, particularly preferably directly, is arranged on the piston (5) and / or the hollow piston rod is guided over a gate track, particularly preferably arranged and / or twisted on the cylinder (3).

7. Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises a magnet (15), preferably bar magnets and / or permanent magnets, through which the at least one aperture (10) can be rotated relative to the piston (5). is, wherein it is preferably provided that the magnet (15), particularly preferably directly, is arranged on the at least one aperture (10) and / or the magnet (15) via at least one, particularly preferably on the cylinder (3) arranged metallic band (16), particularly preferred

Steel band, can be rotated. Damping device (1) according to claim 7, wherein at least two metallic bands (16) are provided and/or the at least one metallic band (16) is arranged twisted on the cylinder (3). Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises a spring (17a) for applying force to the piston (5), which is arranged on the at least one aperture (10), the spring (17a) at least one aperture (10) can be rotated relative to the piston (5), it being preferably provided that the spring (17a) is firmly connected to the at least one aperture (10) and/or the at least one aperture (10) via a Compression of the spring (17a) is rotatable. Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises an impeller (18), through which the at least one aperture (10) can be rotated relative to the piston (5), it is preferably provided that the impeller (18), particularly preferably directly, is arranged on the at least one aperture (10) and/or can be rotated via a passage of damping fluid (4) and/or comprises at least two, particularly preferably four, wings (19). Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises at least one telescopic device (20), through which the at least one aperture (10) can be rotated relative to the piston (5), it being preferably provided that the at least one telescopic device (20) via a guide, particularly preferably twisted and/or arranged on the cylinder (3). (21) is rotatable and/or comprises a plurality of telescopic parts (22) which can be telescoped into one another and/or towards one another. Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises a sealing element (7), wherein the sealing element (7)

- Is designed as a braking element (23) and/or

- acts in the direction of passage parallel to the at least one flow channel (9) and/or

- Acts in the direction of passage in series with the at least one flow channel (9). Damping device (1) according to one of the preceding claims, wherein the piston (3) comprises a power valve (24) in the form of a control piston (25), the passage cross section (11) and/or a further passage cross section of a fluid outlet opening passing through the power valve (24). of the piston (5) can be changed, it being preferably provided that the power valve (24) acts parallel and/or in series to an optionally present sealing element (7) and/or the at least one aperture (10). Damping device (1) according to claim 13, wherein the control piston (25) is arranged on the outside of the piston (5) and / or inside the piston (5), it is preferably provided that the at least one control piston (25) is controlled by a control piston spring ( 28) is biased relative to the piston (5) and/or the piston (5) can be acted upon with force by an optionally present spring (17) and/or the power valve (24) is designed as a pressure compensator (29). Damping device (1) according to one of the preceding claims, wherein the damping device (1) comprises a fluid space (8) filled with damping fluid (4), which is at least from the cylinder (3), from an optionally present Sealing element (7), limited by the piston (5) and/or by the piston rod (6).

16. Damping device (1) according to one of claims 12 to 14 and

15, wherein the damping device (1).

Volume constant holding element (30), which controls the volume available for the damping fluid (4) in the fluid space (8) in every position of the piston (5) including the piston rod

(6) is kept constant, and/or wherein the sealing element (7) forms the constant volume element (30) and is movable relative to the cylinder (3) and is subjected to force on its side (31) facing away from the fluid space, preferably by an optionally present spring (17). is.

17. Damping device (1) according to one of the preceding claims, wherein the at least one aperture (10) and the piston (5) are designed to be rotatable relative to one another in such a way that in the course of the damping stroke the passage cross section (11), preferably longitudinally path-dependent and / or can be reduced depending on the speed of the piston (5).

18. Damping device (1) according to one of the preceding claims, wherein the piston (5) relative to the at least one aperture (10) and / or the at least one aperture (10) relative to the piston (5) and / or the at least one Aperture (10) within the cylinder (3) in the course of a damping stroke via a longitudinal movement of the piston (5) and by a means for rotating the at least one aperture (10) separate from the at least one aperture (10) and the damping fluid (4). ) can be rotated so that the passage cross section (11) can be reduced.

19. Use of a damping device (1) according to one of the preceding claims on a piece of furniture, a door and/or a window. Furniture with at least one damping device (1) according to one of claims 1 to 18, wherein a furniture part that is movable relative to a furniture body can be damped by the at least one damping device (1) between an open position and a closed position. Door with at least one damping device (1) according to one of claims 1 to 18, wherein the door can be damped relative to a door frame, the at least one damping device (1) between an open position and a closed position. Window with at least one damping device (1) according to one of claims 1 to 18, wherein the window can be damped relative to a window frame between an open position and a closed position by the at least one damping device (1).