ROTATIONAL DAMPER AND SEATING ARRANGEMENT

Abstract

The present invention relates to, among other things, a rotational damper comprising a fluid-filled damper housing and within the damper housing a piston rotatably accommodated by a rotation axis of the rotational damper in a first direction and an opposite second direction with a piston rod extending in the direction of the rotation axis; whereby the piston has at least one opening with a flow cross-section which allows for the flow of fluid through the piston, whereby a total flow cross-section is calculated as the sum of the flow cross-sections of the at least one opening. A blocking device can be furthermore assigned to the piston which is capable of reducing the flow cross-section of at least one of the openings during a rotation of the piston in a first direction relative to a rotation of the piston in the second direction.

Claims

1. Rotational damper, comprising: a fluid-filled damper housing and a piston rotatably accommodated in the damper housing by a rotation axis of the rotational damper in a first direction and an opposite second direction with a piston rod extending in the direction of the rotation axis; whereby the piston has at least one opening with a flow cross-section, which allows for the flow of fluid through the piston, whereby a total flow cross-section is calculated as the sum of the flow cross-sections of the at least one opening, wherein a blocking device can be furthermore assigned to the piston, which is capable of reducing the flow cross-section of at least one of the openings during a rotation of the piston in a first direction relative to a rotation of the piston in the second direction.

2. Rotational damper according to claim 1, wherein the total flow cross-section is greater than zero at a rotation of the piston in the first direction.

3. Rotational damper according to claim 1, wherein the blocking device through which at least one elastic plate is formed which is assigned to the piston in such a way that it at least partially covers at least one of the openings during a rotation of the piston in the first direction and substantially exposes the at least one opening during a rotation in the second direction.

4. Rotational damper according to claim 3, wherein the elastic plate comprises at least one opening which overlaps at least partially with one of the openings during the rotation of the piston in the first direction.

5. Rotational damper, comprising: a fluid-filled damper housing; and a piston rotatably accommodated in the damper housing by a rotation axis of the rotational damper in a first direction and an opposite second direction with a piston rod extending in the direction of the rotation axis, wherein at least one bypass channel is provided at the inside of the damper housing across at least one rotation angle section which facilitates in the area of its extension the flow of fluid around the piston in the direction against the rotation of the piston.

6. Rotational damper according to claim 5, wherein the at least one bypass channel is provided in a plate which extends vertically to the rotation axis, for example a floor of the damper housing.

7. Rotational damper according to claim 5, wherein the least one bypass channel comprises a variable cross-section in a circumference direction, for example a linearly increasing cross-section.

8. Rotational damper, comprising: a fluid-filled damper housing; and a piston rotatably accommodated in the damper housing by a rotation axis of the rotational damper in a first direction and an opposite second direction with a piston rod extending in the direction of the rotation axis, if applicable, comprising further features of claim 1, wherein a floor is provided within the damper housing that is movable along the rotation axis.

9. Rotational damper according to claim 8, wherein the movable floor is preloaded in the direction of the piston by means of an elastic member, for example a mechanical spring, and in particular a disk spring.

10. Rotational damper according to claim 9, wherein an axial sealing member is assigned to the piston, whereby the movable floor abuts against the axial sealing member due to the effect of the elastic member.

11. Rotational damper according to claim 8, wherein it comprises a thermal expansion member which is configured and arranged in such a way that it moves the movable floor further in the direction of the piston as the temperature increases.

12. Rotational damper according to claim 1, wherein the piston is formed point symmetrically or rotation symmetrically relative to the rotation axis.

13. Rotational damper according to claim 1, wherein at least one stop is provided at the inner wall of the damper housing which limits a rotation of the piston at a predetermined angle position.

14. Rotational damper according to claim 1, whereby at least one sealing member is provided between the piston and the inner wall of the damper housing.

15. Rotational damper according to claim 1, wherein the piston comprises a substantially circular hub area in the area of the rotation axis from which at least one wing area extends in the direction of the inner wall of the damper housing, whereby furthermore at least one protrusion extends in the direction of the hub area from the inner wall of the damper housing, whereby a gap ring is preferably provided between the protrusion and the hub area.

16. (canceled)

17. Seating arrangement with a fixed seat and a tiltable backrest for a vehicle, wherein the damper of claim 1 is provided between the fixed seat and the tiltable backrest which, when the backrest is tilted from the substantially vertical position to the substantially horizontal position, has a greater damping force than during an opposite movement of the backrest, in particular a rotational damper.

18. Seating arrangement according to claim 17, wherein the damper has an increasing damping force when the backrest is tilted from the substantially vertical position in the substantially horizontal position, and wherein at least one bypass channel is provided at the inside of the damper housing across at least one rotation angle section which facilitates in the area of its extension the flow of fluid around the piston in the direction against the rotation of the piston.

19. Seating arrangement according to claim 18, wherein the backrest and the damper are adapted to each other in such a way that a substantially constant force must be applied when the backrest is tilted from the substantially vertical position to the substantially horizontal position.

20. Rotational damper according to claim 1 wherein the rotational damper is provided between a seat of a vehicle and the vehicle and/or between the seat and a tiltable backrest of the vehicle, whereby the seat is rotatable from its horizontal position relative to the vehicle and/or the backrest, tiltable from a substantially horizontal position to a substantially vertical position, and whereby one of the damper housings and the piston rod are assigned to the seat and the other of the two to the backrest and/or the vehicle.

Description

[0034] Further properties and advantages of the present invention become clear from the description of embodiments below when these are considered together with the enclosed figures. These figures show in detail:

[0035] FIG. 1 shows a rotational damper according to the invention in the mounted state from the outside in a side view;

[0036] FIG. 2 shows the rotational damper from FIG. 1 in a sectional view along a section plane vertical to its rotational axis;

[0037] FIG. 3 shows the rotational damper from FIGS. 1 and 2 in a cross-sectional view along a section plane parallel to the rotational axis;

[0038] FIGS. 4a and 4b show detail views of possible embodiments of the piston of the rotational damper from FIGS. 1 to 3;

[0039] FIGS. 5a and 5b show the piston from FIG. 4a in a sectional view during rotation in opposite directions; and

[0040] FIG. 6 shows a schematic side view of a seating arrangement according to the invention.

[0041] FIG. 1 shows a rotational damper according to the invention in the mounted state in a side view, which is identified in general with the reference number 10. It comprises a cylindrical damper housing 12 with an end cap 14 attached to it, which is fastened in the known manner for example by being screwed on or by means of a bayonet closure. A piston rod 16 extends through this end cap 14, whereby sealing members are arranged respectively between the damper housing 12, the end cap 14, and the piston rod 16 so that a tight interior is created in the damper housing 12 in which damping fluid is received.

[0042] The damper housing 12 and the end cap 14 attached thereto on the one hand and the piston rod 16 on the other are rotatable against each other by an axis of rotation R, whereby a cut is indicated vertical to this axis of rotation R by the plane II, along which the view from FIG. 2 is shown.

[0043] This FIG. 2 shows, in addition to the already mentioned damper housing 12, the interior space 18 provided therein which, as mentioned, is filled with a damping fluid such as hydraulic oil. Furthermore, a piston 20 is arranged in the damper housing 12, which represents an axial extension of the piston rod 16 from FIG. 1. This piston 20 is, just as the damper housing 12, formed point symmetrically around the axis of rotation R and comprises a substantially circular hub area 22, which extends around the axis of rotation R, two wing areas 24 radially extending outward from this hub area 22, as well as two radial ends 26. Between the radial ends 26 of the piston 20 and the inner wall 12a of the damper housing 12, sealing members may be provided that are assigned to the piston 20 so that flow around the piston 20 is prevented at its radial outside.

[0044] Furthermore, FIG. 2 shows stops 12b that protrude from the inner wall 12a of the damper housing 12, which restrict the possible rotation angle area between the piston 20 and the damper housing 12, when the piston 20 abuts to the respective stops 12b with its radial outer ends 26, as this is specifically shown in FIG. 2 as well. Even further from the inner wall 12a of the damper housing 12 than the stops 12b extend two protrusions 12c in a symmetrical manner as well until they reach the hub area 22 of the piston 20. Sealing members may be provided between these protrusions 12c and the hub area 22 of the piston 20 so that, on the one hand, flow around the piston 20 is prevented in this area and, on the other, that a transfer of the shearing forces acting on the piston 20 to the damper housing 12 are permitted at this location.

[0045] It should be pointed out in this context that, even though the protrusions 12c could perform the function of the stops 12b as well, the angle distance between the protrusions 12c and the stops 12b shown in FIG. 2 can avoid nonlinear damping effects which would occur, for example, if large surfaces of the piston 20 were to abut against the protrusions 12c, whereby then a suction effect would occur when the piston 20 is detached from the protrusions 12c again.

[0046] Furthermore, FIG. 2 shows in the substantially even floor 12d of the damper housing two point-symmetrically configured bypass channels 27 which both extend counterclockwise from one of the projections 12c in the circumference direction with a decreasing cross-section and which facilitate, in the area of their extension, the flow of the damping fluid around the piston 20. These bypass channels 27 achieve a progressively increasing, angle-dependent damping force which increases counterclockwise during a movement of the piston 20 away from the corresponding protrusion 12c.

[0047] Lastly, reference should be made in connection with FIG. 2 to the two rivets 28 in the wing areas 24 of the piston 20, which pass through the holes provided in the wing areas 24 and which each retain an elastic plate 30, which extends substantially parallel to the axis of rotation R and therefore parallel to the wing area 24 of the piston 20 in this direction. Furthermore, a cutting line III is shown in FIG. 2 along which the cross-section from FIG. 3 is taken.

[0048] This FIG. 3 shows, in addition to the components damper housing 12, end cap 14, piston rod 16, piston 20, rivet 28, and elastic plate 30 already described above, a floor 40 that is movable in the direction of the axis of rotation R which is sealed from the damper housing 12 as well as the axis of rotation 16 by means of two seals 42 and 44 configured as O-rings, so that no fluid can escape from the inner space 18. Furthermore, an elastic member configured as a disk spring 46 is provided between the movable floor 40 and the end cap 14, which preloads the movable floor 40 in the direction of the piston 20. Here, the assembly formed from the movable floor 40 and the disk spring 46 serve as an overload safety, because the movable floor 40 is raised by the displacement effect of the fluid received in the inner space 18 in the event of an external moment of force acting on the piston rod 16, if the fluid can no longer flow through or around the piston 20 with a sufficient flow rate, whereby the fluid can flow additionally between the piston 20 and the movable floor 40. This way, a bypass of the piston 20 is created so that the damping force of the damper 10 suddenly decreases and the external moment of force can be accommodated in that the piston 20 rotates in the corresponding direction with much less resistance until it abuts against one of the stops 12b.

[0049] FIGS. 4a and 4b show two variations in which a damping that depends on the direction of rotation can be achieved by the interaction of the piston 20 with the elastic plate 30 and 30. Here, the two pistons 20 and 20 are each shown from a front view, i.e., in a top view on an elastic plate 30 and 30, whereby a further plate that is not shown is arranged symmetrically on the back of the pistons 20 and 20.

[0050] In the first variation shown in FIG. 4a, a further hole 32 is provided in the two wings 24 of the piston 20 in addition to the hole provided for the rivet 28, through which fluid can flow through the piston 20. These openings 32 are, however, initially covered by the elastic plates 30, which, however, each have an opening 34 with a smaller cross-section and which coincides in FIG. 4a with the opening 32 of the piston. Thus, the fluid can first only have the cross-section of the opening 34 of the elastic plate 30 available to flow through the piston 20, as will later be explained with the help of FIG. 5a as well.

[0051] On the other hand, the variation shown in FIG. 4b shows two pairs of openings 32a and 32b at the piston wings 24 of the piston 20 whose respective cross-section forms an overall flow-through cross-section for the fluid through the piston 20. Here as well, however, the elastic plate 30 initially covers one of the two openings, while the other opening 32a remains exposed in every state and can act as a flow channel through the piston 20.

[0052] Another variation not shown here would be a piston/plate assembly in which all holes of the piston are completely covered by the plate during a rotation in the first direction so that fluid can only flow around the piston in this state. Expressed differently, the flow-through cross-section of the piston in this variation is zero during the rotation in the first direction.

[0053] FIGS. 5a and 5b, which actually show the variation from FIG. 4a, whose theory of operation can, however, be easily applied to the variation from FIG. 4b, now show, however, that a lifting of the elastic plate 30 due to the dynamic pressure acting on it causes the available flow cross-section for fluid through the piston 20 to be increased. While during a movement of the piston in direction B1, which corresponds in FIG. 2 to a clockwise rotation, the piston 20 is pressed against the wing area 24 of the piston 20 due to the dynamic pressure K1 of the fluid and therefore only the cross-section of the opening 34 of the elastic plate 30 is available as a flow path S1 for the fluid, the elastic plate 30 is lifted from the wing area 24 of the piston 20 during an opposite movement of the piston 20 in the direction B2 due to the pressure K2 of the fluid, so that, in addition to the flow path S1 through the opening 34 of the elastic plate 30, the second flow path S2 through the opening 32 of the piston 20 and between the piston wing 24 and the plate 30 is available. Consequently, a higher damping force acts during a movement of the piston 20 in the direction of rotation B1 than during a movement in the direction B2, whereby, through a suitable selection of the viscosity of the damping fluid and the cross-sections of the openings 32 and 34, various levels of damping hardness can be adjusted in both directions B1 and B2.

[0054] Lastly, FIG. 6 shows a diagram of a seating arrangement according to the invention from a side view, which is identified with the reference number 100 and which comprises a fixed seat 110 and a tiltable backrest 112. These kinds of seating arrangements are used in motor vehicles, for example, to create a continuous loading surface when the seats are not in use, and while, in the case shown, a tilting of the backrest from its substantially vertical position to its substantially horizontal position occurs backward away from the seat, arrangements of this type are known as well in which the backrest 112 can be tilted forward in the direction of the seat 110. Here, the rotatable attachment of the backrest 112 relative to the seat 110 is provided by a rotational damper 10 according to the invention, whereby in this case, the axis of rotation R represents the axis of rotation between the backrest 112 and the seat 110 and the damper housing 12 of the damper 10 is assigned to the backrest 112, while the piston rod 16 is assigned to the seat 110.

[0055] During a tilting of the backrest 112 in the direction of the circular arc K, a differently large component applies its weight in the vertical direction, depending on the current angle of the backrest 112, as indicated by the arrows G1, G2, and G3 in three possible positions of the backrest 112. The rotational damper 10 according to the invention makes it now possible that a tilting of the backrest 112 is dampened more than a return of the backrest 112 to the upright position in order to avoid a sudden backward drop of the backrest 112, on the one hand, or to not make it unnecessarily more difficult for a user to bring the backrest 112 again in a vertical position against its weight. On the other hand, the damping progressively increases during a movement from the vertical to the horizontal position to create a compensation for the also increasing vertically acting components of the weight G1-G3. Last but not least, the rotational damper 10 provides an overload safety as well which prevents the damper and other components from being damaged.