WO2006029421A1

WO2006029421A1 - Fluid damper

Info

Publication number: WO2006029421A1
Application number: PCT/AT2005/000037
Authority: WO
Inventors: Marco Rücker; Claus HÄMMERLE
Original assignee: Julius Blum Gmbh
Priority date: 2004-09-17
Filing date: 2005-02-04
Publication date: 2006-03-23
Also published as: DE202005020820U1; AT10342U1; CN201021704Y

Abstract

A fluid damper(19), particularly for mobile furniture parts, comprising a displaceable piston (2, 2') which is guided in a cylinder (1) and which can be displaced in relation to the cylinder (1), wherein at least one through-flow opening (4, 4') for a through-flowing fluid is provided inside the piston (2, 2') and/or between the piston (2, 2') and cylinder (1), wherein at least one overload opening (10) can be opened inside the piston (2, 2') and/or between the piston (2, 2') and/or between the piston and cylinder (1) if the pressure impingement on the fluid damper (19) exceeds a threshold.

Description

fluid damper

The present invention relates to a fluid damper, in particular for movable furniture parts, with a guided in a cylinder relative to the cylinder displaceable piston, wherein in the piston and / or between the piston and cylinder at least one through-flow for fluid flowing through is provided.

Fluid dampers are known in the prior art in a variety of forms and applications. Among other things, they are used in conjunction with moving furniture parts. Thus, with corresponding fluid dampers, e.g. the closing movement of furniture doors are damped, whereby a loud slamming and possible damage to the doors are prevented. The damping effect of the fluid damper is based essentially on the flow resistance of a fluid present in the cylinder. When pressure is applied to the piston, the latter is displaced relative to the cylinder, the fluid flowing through flow passages through the piston or between the piston and cylinder from one cylinder chamber to another. Instead of or in addition to the damping effect by means of flow resistance, an energy reduction by friction can also be provided.

In the known in the prior art Fluiddämpfem it comes when they are subjected to excessive pressure, so-called damper bouncing. In this situation, the fluid can no longer flow sufficiently past the piston or through the piston. The increased pressure is then no longer dissipated by the damper, so that the piston or the attached piston rod abruptly stops or springs back.

Object of the present invention is to improve a fluid damper to the effect that the described damper bounce is effectively prevented in case of overload.

This is achieved according to the invention in that at least one overload opening in the piston and / or between the piston and cylinder is apparent above a threshold value of a pressurization on the fluid damper.

It is thus provided that, starting from a certain threshold value of a pressurization on the fluid damper or on its piston rod or the piston overload openings are opened by the addition of and / or instead of the flow openings Fluid through the piston and / or can flow past the piston, whereby an excessive increase in the braking force and thus the unwanted damper bouncing is prevented. In such an abuse or overload situation, a strong pressure reduction is possible through the open overload openings. The respective threshold value of the pressurization can be determined by the skilled person depending on the field of application by appropriate choice of the shape and size of the overload openings, the wall thicknesses and the materials used.

It is favorable for an optimum pressure reduction in the event of overload if the overload opening is further apparent from the threshold value of the pressurization with further increasing pressurization on the fluid damper, preferably continuously. The fluid dampers according to the invention are preferably designed as linear dampers. The inventive type of protection against overload in fluid dampers can be used particularly favorably, the damping effect of which is based essentially on the flow resistance of the fluid. The fluids include both gases, e.g. Air, as well as liquids or hydraulic fluids, such. oils, in question. Preferred embodiments provide for the use of the fluid damper according to the invention in movable furniture parts such as doors, drawer inserts or hinges, in particular furniture hinges.

Further advantages and details of the present invention will become apparent from the following description of the figures. Showing:

Figs. 1 to 3 a first embodiment according to the invention, Figs. 2a and 3a detailed views of Figs. 2 and 3, Figs. 4 and 5 are plan views of the piston of the first embodiment from the direction

AA (see FIGS. 2 and 3), FIGS. 6 to 8 a second embodiment according to the invention, FIGS. 7 a and 8 a details from FIGS. 7 and 8, FIG. 9 the second embodiment in an overload situation, FIG. 11 is a schematic representation of the sequence of the closing movement of a furniture door with fluid damper according to the invention, FIGS. 12 and 12a and 12b show a third embodiment according to the invention, FIGS. 13 and 13a and 13b Fourth embodiment of the invention, Fig. 14 and Fig. 14a to 14d a fifth embodiment of the invention, Fig. 15 and Fig. 15a to 15d, a sixth embodiment of the invention and FIGS. 16 to 18 a show a special shape and design of flow-through openings.

When fluid damper 19 according to the embodiments of the piston 2, as is known, slidably guided in a cylinder 1. The pressurization of the piston 2 by means of the piston rod 5. The return spring 6 is used essentially for returning the piston 2 following a damping process. In the latter case, the piston is pushed into the cylinder 1 by pressurizing the piston rod 5 in the direction 23.

The absorber 7 is made of a slightly compressible material, e.g. Sponge rubber, made. It serves to balance the volume of the piston rod 5 when it is pushed in direction 23 into the cylinder 1. The seals 8 and 9 can be designed in any manner known in the art. They only prevent the unwanted outflow of the fluid arranged inside the cylinder 1 and thus an undesired pressure drop. On the piston 2, in the first embodiment according to FIGS. 1 to 5, a ring-shaped or tubular closure element 3 is arranged. This is longitudinally extending and mounted on the piston 2 relative to this displaceable. The closure element 3 fulfills in the present embodiment as well as in the variant according to FIGS. 6 to 9 a double function. On the one hand, when the pressure is applied to the fluid damper 19 or its piston rod 5, the flow-through opening 4 is reduced in its flow cross-section. On the other hand, the closure element 3, as shown in detail with reference to FIGS. 3, 3 a, 4 and 5, opens the overload openings 10 in the event of an overload, which are arranged in the piston 2. In order to exercise this dual function, the closure element 3 is formed radially expandable. When pressurized, the closure element 3 can thereby expand in the direction of the wall of the cylinder 1, whereby the annular and disposed between the closure element 3 and the inner wall of the cylinder 1 through-flow opening 4 is reduced in cross section and thus the flow resistance of the fluid is increased.

To explain the overload protection according to the invention, reference is made to FIGS. 3, 3a, 4 and 5 with respect to this embodiment in particular. FIG. 4 shows a view from direction AA on the piston 2 in the normal operating situation illustrated in FIG. 2, in which the pressurization is below the threshold value and the fluid can flow through the annular gap 4. Fig. 5 shows the view of the piston 2 from direction AA in the overload situation shown in Fig. 3. FIG. 3 a shows the region marked with a circle in FIG. 3 in an enlarged view. in the Normal operation, in which the pressurization is less than the predetermined threshold value, fluid can flow between the closure element 3 and the wall of the cylinder 1 through the flow-through opening 4, whereby the piston 2 is displaceable within the cylinder 1. By increasing the pressurization, the annular closure element 3 is radially expanded, whereby the flow-through opening 4 is reduced in its cross-section. The dimensioning of the piston 2 with the tapered from the piston exterior to the piston interior overload openings 10 and the inner diameter of the cylinder 1 as well as the wall thickness and the material properties of the closure element 3 are chosen so that upon reaching the intended application of the fluid damper threshold by increasing Elongation of the closure element 3, the overload openings 10 are opened in the region 12, so that fluid can flow through them. As a result, blocking or bouncing of the piston is prevented in the case of excessive pressurization. The Überlastsituatioπ shown in Fig. 5 is shown again in Fig. 3a in a sectional view.

In addition to the druckabhäπgigen control of the flow cross-section and thus the flow resistance of the fluid by stretching the closure element 3 in all embodiments additionally a path-dependent control of the flow resistance is realized. For this purpose, it is provided that the inner diameter of the cylinder in the region in which the piston is displaceable, e.g. in the areas 11a, 11b, 11c and 11d, is different in size. By thus achieved taper of the inner cylinder diameter in the direction of the cap 8, the flow-through 4 is reduced with increasing depression of the piston 2 in the cylinder 1 in the direction 23. As a result, the flow resistance of the fluid is automatically higher the further the piston rod 5 or the piston 2 is pushed into the cylinder 1. Fig. 1 shows the first embodiment in the situation in which the piston rod 5 substantially no pressure is exerted. Fig. 1 also shows the relative position of the piston 2 and the closure element 3 in the return of the piston by means of the spring 6 counter to the direction 23. In the shown restoring situation, a relatively large gap between the closure element 3 and the piston 2 is free. This allows a good flow through the fluid and thus a quick return. In Fig. 2, the reduction of the cross section of the flow-through opening takes place in the transition between the regions 11b and 11c.

In the second embodiment according to the invention according to FIGS. 6 to 9, additional throughflow openings 4 'are arranged in the piston 2'. The annular closure element 3 'is not displaceable relative to the piston 2' in this embodiment, but engages in a groove 18 in the piston. As in the first exemplary embodiment, the closure element 3 'is radially expandable so that the flow-through openings 4, as already described, can be controlled in their opening cross-section as a function of pressure by the closure element 3'. Another pressure-dependent control of the total flow cross-section is given in this example by the interaction of the brake plate 15 with the Abdecklamelle 16. Both lamellae are displaceable relative to one another and are mounted to the piston 2 'on a connecting rod 14, which connects the piston 2' to the connecting element 13. The piston 2 'is supported via said connecting rod 14 and the connecting element 13 against the spring 6, which performs the same function as in the first embodiment.

The pressure-dependent control takes place in this embodiment in the interaction of the slats 15 and 16 with the pressure-dependent expansion of the closure element 3 '. As a result, a constant control of the braking force or damping of the fluid damper 19 for different closing forces is thereby achieved. These change, e.g. by aging the closure mechanisms, e.g. hinges, or vary by using different hinge types. The fins 15 and 16 can be made so fine or smooth that they react to low pressures, which particularly well changes in the closing force can be compensated. The closure element 3 'is then conveniently designed so that it can respond to larger pressure changes.

Fig. 6 shows the second embodiment, when the piston rod 5 has been fully extended by means of the spring 6. The overflow 4 'and 4 are open in this situation maximum. If pressure is now exerted on the piston rod 5 in the direction 23, then the brake plate 17 initially lays against the piston 2 'by displacement along the connecting rod 14 and at least partially closes the flow openings 4'. The brake disk 15 has at least one fin opening 17, which is arranged so that fluid can still flow through the fin opening 17 and at least part of the flow opening 4 '. As the pressure builds up further, the covering lamella 16 is likewise displaced in the direction of the piston 2 'and deformed at the corresponding pressure, as shown in FIGS. 7, 7a, 8 and 8a. Depending on the degree of deformation while the fin opening 17 is partially or completely closed. At the same time takes place by the pressure buildup and an elongation of the annular closure element 3 ', which in turn the outer annular flow opening 4 is tapered in its opening cross-section. If the pressurization increases over a threshold value provided for the respective area of application of the damper, the overload protection according to the invention also occurs in this exemplary embodiment by opening the overload opening 10, which in the exemplary embodiment is designed in the region of the groove 18. The overload situation is shown in FIG. 9. The closure element 3 'is stretched by appropriate pressure build-up in the region of the groove 18 so far that the overload opening 10 is opened, whereby the fluid is again given a possibility to bypass the piston 2'. In this case, the closure member 3 ^{1 is held} by a not visible in Fig. 9 support so in its position relative to the piston 2 ', that no relative displacement between closure element 3' and piston 2 'is possible, and the closure element after completion of the overload situation back into the Groove 18 engages.

In the first two embodiments according to FIGS. 1 to 9, the closure element 3 or 3 'fulfills a dual function. On the one hand, it controls the opening and closing of the overload opening (s) 10. On the other hand, the closure element also controls the flow cross section of the throughflow openings 4.

In the further exemplary embodiments according to the invention according to FIGS. 12 to 15d, which are described below, these two functionalities are separated from one another. For opening and closing the overload opening (s) 10, at least one overload control device 28 is provided. To change the flow cross-section of the flow-through openings 4, the fluid damper 19 has a flow-through opening control element 24. The overload control device 28 and the Durchströmöffnungskontrollelement 24 are separate from each other - different - components of the fluid damper 19th

The Durchströmöffnungskontrollelement 24 has substantially the features of the closure element 3, 3 'of the first two embodiments, or may be formed accordingly. Thus, it is provided in particular that said element 24 is stretchable, so that the passage cross-section of the flow-through 4 is reduced in size with the increase acting on the fluid damper 19 pressurization by the flow control. Conveniently, this as the closure elements 3, 3 'ring-shaped or tubular and radially expandable. In addition, it can also be provided that the flow-through opening control element 24 extends longitudinally and preferably has different wall thicknesses along its longitudinal extent. In the embodiments of FIGS. 12 to 15d is the Element 24 also slidably mounted between a stop 27 on the piston 2 and a stop of the respective connecting element 13 in the cylinder longitudinal direction.

FIGS. 12 to 12 b show a first variant of an overload control device 28 separated from the flow-through opening control element 24, in which it essentially has a spring-loaded ball 25. This is intended to close the overload opening 10 as long as the pressurization in the fluid is below a predefinable threshold value. If this is exceeded by the properties of the ball loading spring 26 predeterminable threshold, it comes to the deflection, preferably for compression, the spring 26, whereby the overload opening 10 is released and the fluid is opened a path through the piston 2 therethrough. FIG. 12 a shows the cutout 34 from FIG. 12 in the event of an overload, in which the ball 25 releases the overload opening 10. Fig. 12b shows the same detail in the normal state in which the ball 25 is acted upon by the spring 26, the overload opening 10 closes. In this embodiment, the ball 25 loading spring 26 is parallel to the direction of movement of the piston 2 displaceable in the cylinder deflectable.

In the exemplary embodiment according to FIGS. 13 to 13b, a resilient variant of the overload control device 28 is likewise provided. However, this is deflected in the radial direction. In embodiments of this type, the overload control device for opening and closing the overload opening 10 on a resilient ring or a, preferably c-shaped, resilient ring segment 29. This closes in normal operation with the cap 30, the overload opening 10 in the piston 2. Only when a predetermined by the elastic properties of the ring segment 29 (or ring) predetermined threshold of pressurization, the ring segment 29 is stretched so far that the overflow 10 released and fluid can flow past and past the piston 2. This situation is shown in the section 35 in Fig. 13a. 13b indicates in an exploded view that the resilient ring segment 29 partially surrounds the piston 2, wherein the overload opening 10 is arranged in the lateral surface of the piston 2.

In the fifth embodiment of the invention according to FIGS. 14 to 14 d, the overload control device 28 has an eccentrically expandable ring 31. This is in the illustrated embodiment, as can be seen particularly well in Fig. 14b, equipped with a locking lug 32, which is intended to be anchored in the receptacle 33 of the piston 2. As a result, the eccentrically stretchable ring 31 is only partially or fixed only in a small portion of the piston 2. When pressure is applied, this unilateral fixation results in eccentric expansion of the ring 31. If the predefinable threshold value is exceeded, the overload opening 10 in the piston 2 shown in FIG. 14d is released by corresponding expansion, whereby fluid can once again flow past the piston 2. Fig. 14c shows the same view from direction 37 on the piston 2, but in the situation in which the pressurization of the eccentrically expandable ring 31 is below the threshold and the overload opening 10 is closed by the ring 31. 14a shows the detail 36 from the sectional view 14. In the situation shown here, the overflow opening 10 is closed by the eccentrically expandable ring 31.

FIGS. 15 to 15 d show a further exemplary embodiment according to the invention, in which the overload control device 28 has a preferably disc-shaped overload lamella 38 which has at least one elastically deformable region 39 for opening and closing overload openings 10 provided in the piston 2. The region or regions 39 are partially surrounded by preferably substantially V-shaped or U-shaped recesses 41. The tabs thus formed can be bent with appropriate pressurization and thus open the overload openings 10, which in turn fluid can flow through the piston 2. As can be seen from the detailed illustrations 15b to 15d of the cutout 40, the overload lamella 38 is mounted on the latter in an axially displaceable manner parallel to the direction of movement of the piston 2. Fig. 15b shows the situation in which the overload plate 38 is removed from its stop on the piston 2. Fig. 15c shows the situation in which, although it rests on the piston 2 but the overload opening 10 is not yet released. In Fig. 15d, the deformable portions 39 are bent after exceeding the threshold value of the pressure load and the overload opening (s) 10 is (are) released.

For path-dependent damping in the already shown and discussed embodiments, the interaction of the closure element 3, 3 'and the Durchströmöffnungskontrollelementes 24 is provided with the preferably variable inner diameter of the cylinder 1. FIGS. 16 to 18 furthermore show a variant in which, for the purpose of controlling the flow cross-section, substantially groove-shaped throughflow openings extending in addition to and extending essentially parallel to the direction of movement of the piston are provided. This can be arranged both in the inner wall of the cylinder 1 facing the piston 2 and in the piston 2 and / or in the flow-through opening control element 24 or in the closure element 3, 3 '. As shown in FIGS. 16 to 18 a, it is also preferably provided in the case of the essentially groove-shaped throughflow openings 42 that they vary their flow cross section in the longitudinal direction of the cylinder. Thus, Fig. 16a shows the cross section in the position shown in Fig. 16, in which the piston is at the beginning of the damping movement. If the piston rod 5 and thus the piston are pushed further, in the situation illustrated in FIGS. 17 and 17a there is already a change in both the groove-shaped throughflow openings 42 and the annular throughflow opening 4. In the situation illustrated in FIGS. 18 and 18a , in which the piston rod 5 is almost completely inserted into the cylinder, the annular flow openings 4 are completely closed. In this area, no groove-shaped flow openings 42 are more provided in the cylinder inner wall. Only the groove-shaped throughflow openings 42 in the flow-through opening control element 24 remain open. The variant shown with the additional groove-shaped throughflow openings 42 is possible in all exemplary embodiments shown and previously discussed. It makes it possible to vary the curvature cross-section available in the respective position of the piston particularly strongly over the longitudinal extent of the cylinder 1. So this is a cheap further variant of the damping properties of the fluid damper path-dependent to make.

The relationship between pressurization and elongation can by material selection and appropriate dimensioning of the closure element 3 and 3 'and

Overload control device 28 and the Durchströmöffnungskontrollelementes 24 can be achieved. Preferred is e.g. a quadratic context in which the

Strain change per pressure change decreases with increasing pressure.

Cheap materials for the manufacture of the closure element are thermoplastics and / or elastomers, such as e.g. TPE's (thermoplastic elastomers). By varying or varying wall thicknesses of said components, a desired variation of the expansion behavior can additionally be achieved. Thus, it can be provided both that the components expand in some areas more than in others or evenly over their entire longitudinal extent.

Fig. 10 shows a furniture hinge 20 as an application form on which a fluid damper 19 according to the invention is arranged. This is placed here on the hinge arm 22. The piston rod is supported on the opposite side.

Fig. 11 shows schematically the closing behavior of a door which is equipped with a furniture hinge with inventive fluid damper 19. In the diagram shown is the Movement velocity v of the door against the opening angle α applied. The phases I to IV of the closing process are differentiated. In phase I (up to a closing angle of approx. 20 °), the fluid damper is not in action. In phase II, there is a gentle first braking and interception of the door. In phase III, the essential braking process is ensured by an interaction of the above-described pressure-dependent and path-dependent damping. In area IV, the door speed is already slowed to almost zero. There is a gentle closing.

Claims

claims:

1. fluid damper, in particular for movable furniture parts, with a guided in a cylinder relative to the cylinder movable piston, wherein in the piston and / or between the piston and cylinder at least one flow opening is provided for fluid flowing through, characterized in that above a threshold value of pressurization the fluid damper (19) at least one overload opening (10) in the piston (2, 2 ') and / or between the piston (2, 2') and cylinder (1) is apparent.

2. fluid damper according to claim 1, characterized in that the overload opening (10) from the threshold value of the pressurization with further increasing pressurization of the fluid damper, preferably continuously, is further apparent.

3. fluid damper according to claim 1 or 2, characterized in that its damping effect is based essentially on the flow resistance of the fluid.

4. fluid damper according to one of claims 1 to 3, characterized in that it is a linear damper.

5. fluid damper according to one of claims 1 to 4, characterized in that the cylinder (1) has at least two different inner diameter in the region in which the piston (2, 2 ') is displaceable.

6. fluid damper according to one of claims 1 to 5, characterized in that the flow-through (4, 4 ') in its flow cross-section with increase in the fluid damper (19) acting pressurization by at least one closure element (3, 3') is reduced in size.

7. fluid damper according to claim 6, characterized in that the closure element (3, 3 ') is annular or tubular.

8. fluid damper according to one of claims 6 or 7, characterized in that the closure element (3, 3 ') is radially expandable.

9. fluid damper according to one of claims 6 to 8, characterized in that the closure element (3, 3 ') extends longitudinally and preferably along its longitudinal extent has different wall thicknesses.

10. fluid damper according to one of claims 6 to 9, characterized in that the increasing with increasing pressurization in its cross-section throughflow opening (4, 4 ') at least partially between the closure element (3, 3') and the inner wall of the cylinder (1) is arranged ,

11. Fluid damper according to one of claims 6 to 10, characterized in that the

Throughflow (4) at least partially between the piston (2) and closure element (3, 3 ') is arranged.

12. fluid damper according to one of claims 6 to 11, characterized in that the closure element (3, 3 '), preferably on the piston (2), relative to the piston (2) is displaceably mounted.

13. Fluid damper according to one of claims 6 to 11, characterized in that the overload opening (10) in the form of a, preferably circumferential, groove (18) in the outer surface of the piston (2 ') is formed and the closure element (3') in this groove (18) engages.

14. Fluid damper according to one of claims 1 to 13, characterized in that the overload opening (10) in the piston (2) is formed with the piston interior to the piston interior tapering opening cross-section.

15. Fluid damper according to one of claims 1 to 14, characterized in that at least one, preferably additional, flow-through opening (4 ¹ ) in the piston (2 ') is provided, which by at least one brake disc (15) when pressure is applied to the fluid damper (19 ) is partially closed.

16. A fluid damper according to claim 15, characterized in that the brake disc (15) has at least one louver opening (17) which is arranged so that fluid through the slat opening (17) of the brake plate (15) and the flow-through opening (4 ') flow can.

17. Fluid damper according to one of claims 15 or 16, characterized in that a Abdecklamelle (16) is provided, which closes the slat opening (17) of the brake plate (15) in response to the pressurization of the fluid damper (19) different degrees.

18. Fluid damper according to one of claims 15 to 17, characterized in that the brake plate (15) with the slat opening (17) relative to the piston (2 ') is movably mounted.

19. Fluid damper according to one of claims 15 to 18, characterized in that the Abdecklamelle (16) relative to the piston (2 ^! ) And / or to the brake plate (15) is movably mounted.

20. Fluid damper according to one of claims 6 to 19, characterized in that the closure element (3, 3 ') the overload opening (10) above the predetermined

Pressurization opens.

21. Fluid damper according to one of claims 1 to 5, characterized in that it is for opening and closing the overload opening (10) at least one overload control device (28) and for changing the flow cross-section of

Throughflow (4, 4 ') at least one flow-through control element (24).

22. A fluid damper according to claim 21, characterized in that the overload control device (28) and the flow-through control element (24) are different components of the fluid damper.

23. Fluid damper according to claim 21 or 22, characterized in that the flow-through control element (24) has the features of the closure element (3, 3 ') according to at least one of claims 6 to 12.

24. Fluid damper according to one of claims 21 to 23, characterized in that the overload control device (28) comprises a spring-loaded ball (25), wherein the ball (25) is provided to close the overload opening (10) and the ball ( 25) loading spring (26) from reaching the threshold of a Pressures so deflectable, preferably compressible, is that the ball (25) the overload opening (10) releases.

25. Fluid damper according to claim 24, characterized in that the ball (25) loading spring (26) parallel to the direction of movement of the piston displaceable in the cylinder (2) is deflectable.

26. Fluid damper according to one of claims 21 to 23, characterized in that the overload control device (28) for opening and closing the overload opening (10) has a resilient ring or a, preferably c-shaped, resilient ring segment (29).

27. A fluid damper according to claim 26, characterized in that the resilient ring or the resilient ring segment (29) optionally partially surrounds the piston (2), and preferably the overload opening (10) in the lateral surface of the piston

(2) is arranged.

28. Fluid damper according to one of claims 21 to 23, characterized in that the overload control device (28) has an eccentrically expandable ring (31).

29. Fluid damper according to claim 28, characterized in that the eccentrically expandable ring (31), preferably by means of a latching lug (32), only in sections, preferably only in a small portion, on the piston (2) is fixable.

30. Fluid damper according to one of claims 21 to 23, characterized in that the overload control device (28) has a, preferably disc-shaped, overload plate (38), which has at least one elastically deformable region (29) for opening and closing the overload opening (10) ,

31. Fluid damper according to claim 30, characterized in that the elastically deformable region (39) is partially surrounded by a, preferably substantially V-shaped or U-shaped, recess in the overload plate (38).

32. fluid damper according to claim 30 or 31, characterized in that the overload plate (38) parallel to the direction of movement of the piston (2) is displaceably mounted.

33. Fluid damper according to one of claims 1 to 32, characterized in that an optionally present closure element (3, 3 ') or an optionally present Durchströmöffnungcontrollelement (24) and / or the piston (2), preferably in the respective outer surface facing the cylinder , at least one, preferably substantially parallel to the direction of movement of the piston (2) extending, substantially groove-shaped flow opening (42).

34. fluid damper according to one of claims 1 to 33, characterized in that in the piston (2) facing inner wall of the cylinder (1) at least one, preferably substantially parallel to the direction of movement of the piston (2) extending, substantially groove-shaped Durchströmöffπung ( 42) is provided.

35. Fluid damper according to claim 33 or 34, characterized in that the substantially groove-shaped throughflow opening (42) has at least two areas with different opening cross-sections (have).

36. Hinge, in particular furniture hinge (20), with a fluid damper (19) according to one of claims 1 to 35.