DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT

专利摘要:
A device for damping the movement of a movably mounted component (1) comprises a first, mechanically acting brake device which has at least one friction pair, in which a driven friction surface (14) about an axis (6) of the first brake device opposes to generate a braking force a braking device which is coupled to the first brake device, wherein the mutual contact pressure of the friction surfaces (14,15) of the friction pair or of at least one of the friction pairings in dependence on a braking force exerted by the second brake device. The second brake device has at least one driven damper surface (21) rotatable about an axis (6) of the second brake device and including at least one retained damper surface (22) at least one gap containing a viscous damping medium (23) which, when the at least one driven damper surface (21) is rotated relative to the at least one retained damper surface (22), causes a braking force of the second brake device.
公开号:AT512306A4
申请号:T84/2012
申请日:2012-01-25
公开日:2013-07-15
发明作者:Wolfgang Mueller；Edwin Gruebel
申请人:Fulterer Gmbh；
IPC主号:

专利说明:

patent attorneys
HofmanSeFechner
6δδό FelSkirch, Austria Egelseestr 65a, PO Box 61 T +43 (0) 5522 73137 F +43 (0) 5522 73 359 M office@vpat.at I www.vpat.at 24353/33 / ss 111117
The invention relates to a device for damping the movement of a movably mounted component, comprising a first, mechanically acting brake device having at least one friction pair, in which for generating a braking force a driven friction surface about an axis of the first braking device against a voltage applied to it fixed friction surface is rotatable, and a second brake device which is coupled to the first brake device, wherein the mutual contact of the friction surfaces of the friction pair or at least one of the friction pairings of the first brake device in response to a force exerted by the second brake device braking force. Damping devices, such as those used for damping of movably mounted furniture parts, such as drawers, are known in different embodiments. Thus, for example, piston-cylinder units are known in which at least one flow-through opening for a fluid flowing through, for example a hydraulic fluid, is provided in the piston and / or between the piston and the cylinder. Such dampers can be seen for example from DE 20 2005 020 820 U1 and DE 10 213 726 A1. Known are further rotational damper, in which a highly viscous damping medium is arranged in a gap between a fixed damper part and a rotatably mounted damper part. The braking force is caused by this sheared damping medium. Dampers of this type are described for example in DE 10 210 917 C1, US Pat. No. 5,277,282 A, JP 59222631 A and US Pat. No. 5,143,432 A.
It is advantageous in the case of these previously known pneumatic, hydraulic and shear friction dampers that the braking force produced depends on the speed of movement of the component to be damped, so that a component moving more rapidly is more strongly damped, which is the case in many applications.
wishes. Disadvantages are the relatively low achievable braking forces (in particular with purely pneumatic dampers and shear friction dampers), the required seals (in particular with hydraulic dampers) and the relatively high frictional forces which are to be overcome at low speeds of actuation of the damper. These are frictional forces which act independently of the braking effect of the damper medium (= idling friction).
Furthermore, the use of purely mechanically acting friction dampers is known. Thus, for example, DE 19938 626 A1, DE 201 16 1 97 U1 and JP 01266331 A disclose loop parts which surround an inner friction part and form a friction pair with it. Friction dampers have the disadvantage that the braking force you exert is basically independent of speed
DE 10 313 659 B3, DE 10 214 596 A1, DE 19 717 937 A1, AT 503 877 B1 and EP 1 260 159 A2 show piston-cylinder units in which an air pressure difference forming between the two piston sides points to a elastically deformable piston part acts, which is pressed depending on the pressure difference more or less strongly to the cylinder inside. The frictional force acting between the elastic piston part and the cylinder inner wall thus depends on the pressure difference and thus on the speed of movement of the component to be damped. There are thus provided linear dampers, in which a mechanically acting braking device is coupled with a pneumatically acting braking device which controls the braking force of the mechanically acting braking device. A disadvantage of these previously known dampers is, inter alia, that first a pressure difference must build up until the braking force of the friction damper begins, which is associated with a more or less large time delay of the onset of the damping effect. Also, the damping characteristic is unfavorable for many applications or difficult to adapt to different applications. A linear damper is also limited to a limited range of operation. • • • • • t «9 ·· ·· · *
limited extent or it must correspond to the dimensions of a linear damper of the desired operating distance.
A device of the type mentioned, which is designed as a vehicle shock absorber, it is apparent from DE 601 293 C. A flexibly formed loop part rubingly abuts against an inner friction part formed by a friction drum. One end of the belt part is connected to the vehicle axle to be damped. The other end of the belt part is in communication with a hydraulic damping device. This is arranged within the rubbing drum and comprises wings which are rotatably mounted and arranged in a chamber containing a liquid. Through holes in the wings, the liquid can pass from one side to the other side of the wing. Alternatively, the holes may also be arranged in chamber walls which connect two chambers with each other. The friction force of the rotary friction damper is thus controlled by the hydraulic damper, thereby achieving an overall speed-dependent braking characteristic. The disadvantage of this device is that it has a relatively large size. Also, due to the high pressures occurring in the fluid, high quality seals must be present. Such seals also cause friction, so that the ease of movement at low speeds is limited (= increased idleness).
As mentioned damping devices are often used to dampen the retraction of extendable furniture parts, such as drawers and pull-out tall cabinets. These extendable furniture parts are then usually equipped with a self-closing device. This pulls the extendable furniture part over a last portion of the Einfahrstrecke in its closed state, wherein the retraction movement is damped by the damping device. Self-closing devices have become known in various embodiments. In a conventional embodiment, a spring-loaded tilting slide is provided, which cooperates with a driver attached to the extendable furniture part and from the driver between a basic position and * 4 · · • · • • · · ·. Is adjusted to a waiting position which the tilting slide occupies in the extended state of the pull-out furniture part. An example of such a self-retracting device, here in combination with a Ausziehsperreinrichtung, is apparent from EP 1 500 763 A2. From GB 1 117 071 a locking device is shown in which a spring-loaded catch arm is pivotally mounted about an axis and is pivoted by the driver between the base position and the waiting position about this axis. The spring is moved over a dead center.
If several extendable Möbelteife are present, which are only extendable alternately, for example, several superimposed drawers, so Ausziehsperrvorrichtungen be used. A central locking can be realized via such Ausziehsperrvorrichtungen. In a common embodiment locking rods are present, which have only a limited space for their displacement. For each extendable furniture part an actuating part is provided, which cooperates with at least one of the locking rods. When you take off one of the extendable furniture parts at least one of the locking rods is moved so that the space for the displacement of the locking rods is used up and another extendable furniture part thus can not be pulled out at the same time. Such a pull-out device can be seen, for example, from the already mentioned EP 1 500 763 A2. From GB 2 376043 A a pull-out locking device emerges in which the actuating parts are pivoted about axes which are parallel to the longitudinal extent of the locking bars and have cams cooperating with the locking bars.
Ausziehsperrvorrichtungen with locking rods are known in various other embodiments. For example, DE 29 620 152 U1, EP 1 336 709 A1 and WO 2008/107499 A1 show an actuation of the locking rods by actuating parts, which are pivoted about an axis perpendicular to the locking rods when pulling out of the respective extendable furniture part. For example, GB 2 376 043 A discloses a pull-out locking device in which the operating parts are pivoted about axes parallel to the longitudinal extent of the locking bars and cams cooperating with the locking bars. The object of the invention is to provide a damping device of the type mentioned, which has a speed-dependent braking force, a compact design of the device is made possible and at low speeds of movement of the component to be damped to be overcome 5 friction of the device should be kept low. According to the invention, this is achieved by a device having the features of claim 1.
In the device according to the invention, a viscous damping medium is arranged in at least one gap of the second brake device, which is formed between a driven damper surface rotatable about an axis of the second brake device and a damper surface fixed relative to rotation about the axis. This, preferably the at least one gap completely fills, damping medium, during rotation of the at least one driven by the movement of the component to be damped damper surface against-15 on the at least one recorded damper surface, a braking force of the second brake device.
The braking force produced by the second braking device influences via the coupling the braking force of the first, mechanically acting braking device, which could also be referred to as a rotational friction damper. For this purpose, the mutual contact pressure (= pressing force) of the friction surfaces of the friction pair or of at least one of the friction pairings is changed as a function of the braking force of the second brake device, wherein the contact pressure increases with increasing braking force of the second brake device. As a result of the coupling, an active connection acting between the second and the first brake device is produced, directly or via at least one coupling part lying therebetween. By the invention, a compact, cost-effective damper can be provided with an advantageous braking characteristic, wherein the amount of braking force depends on the speed of the component to be damped. A small amount of empty friction can be achieved. Since the first and second brake devices are designed in the form of rotational dampers, it is optionally possible to achieve damping via a basically unlimited path. Μ * «%» t · ♦ • »V · ·
If the first brake device comprises more than one friction pair, these are preferably all rotatable about the same axis (ie coaxial). If the second brake device comprises more than one driven damper surface, these are preferably all rotatable about the same axis (ie coaxial).
Advantageously, the axis of the first brake device about which the at least one driven friction surface of the first brake device is rotatable coincides with (coincides with) the axis of the second brake device about which the at least one driven damper surface of the second brake device is rotatable, i. the at least one driven friction surface of the first brake device and the at least one driven damper surface of the second brake device are thus rotatable about the same axis or coaxial. It is achieved by a simple, compact design. The friction pairing or at least one of the friction pairings of the first brake device expediently has a sliding friction coefficient of at least 0.2, preferably at least 0.3.
The viscosity of the viscous damping medium of the second braking device is advantageously more than 20,000 Pa s, preferably more than 50,000 Pa s, with values in the range of 100,000 to 1,000,000 Pa s are particularly preferred.
The gap width of the gap or at least one of the gaps, preferably all gaps, in which or in which the damping medium is arranged, is advantageously in the range of 0.1 mm to 0.5 mm, i. the damping medium has such a layer thickness.
The damping force is caused by the arranged in at least one gap damping medium in that this is loaded on shear. The damping medium having gap or these gaps preferably extend annularly about the axis of the second brake device. ·· * · ♦ · fr «t ·» * -7 * · * Λ β
For retaining the damping medium in the gap or in the respective gap, relatively simple seals can be used, if at all.
For non-flowable greases, gaskets may be omitted altogether. With 5 flowable oils, seals that prevent the oil from leaking are required, with no high pressures on the seals.
In an advantageous embodiment of the invention, the first brake device comprises a flexible, preferably elastically bendable, formed loop part or a loop unit which comprises at least two jaw parts connected to one another in an articulated manner. The wrap-around part or the wrap-around unit surrounds an inner brake part over a part of its circumference, which is at least more than 90 °, preferably at least 180 °, particularly preferably at least 250 °. Preferably, the wrap-around part or the wrap-around unit extends over at most 500 °, particularly preferably over at most 330 °, around the inner brake part. The loop part or the belt unit and the inner brake part form the friction pair or at least one of the friction pairings of the first brake device. In this case, the coupling with the second brake device can favorably be effected by a rear end of the belt part or the belt unit being directly or indirectly connected to a part of the second brake device which applies a braking force caused by the second brake device to the belt part! or transmits the Umschlingungseinheit. This part of the second brake device may in particular be designed in the form of a damper sleeve which has at least one of the damper surfaces of the second brake device. The term "rear end" refers to the relative movement between the wrapping part or the wrapping unit and the inner brake part. In this case, either the loop part or the loop unit can be driven by the component to be damped and rotate in a direction of rotation relative to the inner brake part or the inner brake
* -8 • · ♦ · ♦ · • ·
Part can be driven and opposite to the belt part or the
Turn the belt unit in an opposite direction of rotation.
In another possible embodiment, at least one friction member rotatably driven about the axis of the braking device comprises the driven friction surface or at least one of the driven friction surfaces and at least one friction member retained against rotation about the axis holds the retained friction surface or at least one of the retained friction surfaces a driven damper part rotatable about the axis of the second brake device comprises the driven damper surface or at least one of the driven damper surfaces and at least one damper part retained against rotation about the axis, the captured damper surface or at least one of the damper surfaces being retained, the driven damper part or one of the driven damper surfaces Damper parts by a connection with the driven friction part or one of the driven friction parts or a rotationally fixed hereby connected part via a coupling spring angetri is even or wherein the detained damper part or one of the detained damper parts is held by a connection with the detained friction member or one of the detained friction parts or a part rotatably connected thereto via a coupling spring. It comes thereby, if a damping of the movement of the movably mounted component is carried out, to a more or less large angular offset between the two parts connected by the coupling spring, depending on the speed of movement of the component to be damped. Cooperating control surfaces adjust the contact pressure of the friction surfaces of the friction pairing or at least one of the friction pairings as a function of this angular offset, or in other words, the cooperating control surfaces convert this angular offset into a contact pressure of the friction surfaces that depends on the angular offset.
A device according to the invention is suitable for damping different types of movably mounted components, in other words for exerting a braking force on different types of movably mounted components. Thus, the movement of a linearly movably mounted component, e.g. a linear motion «β ♦ ···« *
such as a drawer or a cabinet drawer, or the movement of a rotatably mounted component, e.g. a door or a flap in the form of a furniture part or as part of or be damped in a vehicle. Different other types of linearly or rotatably movably mounted parts, such as machine parts, can also be damped by a device according to the invention.
By a device according to the invention, high damping forces can be applied, so that the device can be used, for example, to dampen the insertion movement of heavy duty pull-outs. For heavy-duty pull-out furniture parts are provided, of which one, several or all are loaded with more than 150kg.
Further advantages and details of the invention are explained below with reference to the accompanying drawings. In this show:
1 shows an oblique view of a first embodiment of a device according to the invention;
Fig. 2 is an oblique view corresponding to Figure 1 of the cross-cut device. Fig. 3 is an exploded view;
4 is an oblique view of devices according to the invention according to a second embodiment in use for damping the insertion movement of extendable furniture parts;
5 shows an oblique view of one of the devices of FIG. 4, in the waiting position of the tentacle taken in the extended state of the extendable furniture part, with a fastening rail;
Fig. 6 is an oblique view corresponding to Figure 5 in the state which is present in the retracted state of the extendable furniture part.
Fig. 7 is an oblique view corresponding to Figure 6 but from a different angle.
8 shows a view of the device fastened to the rail, with the tentacle in the waiting position; ♦ · · • · · · ·
8a is a representation corresponding to FIG. 8, but in the longitudinal center section of the device;
Fig. 9 is a section along the line AA of Fig. 8 and 8a;
FIGS. 10 and 11 are sections corresponding to FIG. 9, but in an intermediate position and in FIG. 5 the basic position of the catching arm taken in the retracted state of the extendable furniture part;
Fig. 12 is a section along the line BB of Fig. 8 and 8a;
Fig. 13 is an exploded view;
FIG. 14 shows an oblique view of the device cut open in a section parallel to the axis and passing through the axis; FIG.
Fig. 15 is an illustration for explaining the retraction movement of the tentacle of the device in the slot of the driver;
16 is a slightly modified embodiment of the device with additional elements for forming a pull-out device; Fig. 17 is an exploded view of this modified embodiment; 17a shows an oblique view of the wrap-around part engaging with the damper sleeve from a different viewing direction from FIG. 17;
Figures 18 and 19 are schematic representations of an alternative embodiment for the actuation of the locking rods. Figures 20 and 21 are illustrations corresponding to Figures 18 and 19 but without the actuating sleeve.
Fig. 22 is an oblique view corresponding to Fig. 5 of a further modification of the second embodiment;
23a and 23b show a modified embodiment of the first embodiment described with reference to FIGS. 1 to 3 25, in oblique view and in an exploded view;
Fig. 24 is an oblique view of a third embodiment of the invention, the device cut in the longitudinal center section;
FIGS. 25 and 26 show two different positions of the control surfaces; Fig. 27 shows the device of Fig. 24 in the exploded condition of the parts. U * '• · ι »
A first embodiment of a device according to the invention is shown in FIGS. 1 to 3.
The device serves to damp the movement of a movably mounted component 5, which is indicated only schematically in FIG. On the component 1 of the likewise only schematically indicated driver 2 is arranged, which has a Kuißenbahn 3 formed by a depression. To dampen the movement of the component 1 in the direction of movement 44, a projection 4 arranged on a catching arm 5 (= catching lever) enters the slide track 3, wherein the catching arm 5 is rotated about the axis 6 in the direction of the arrow 26 and is thereby braked and thus the movement of the component 1 brakes. The projection 4 is formed in the embodiment of a pin, but could for example also be formed by a roller. A reverse training (projection on the driver, recess on the tentacle) is possible. Also designed in other form driving-15 compounds, for example, a substantially V-shaped recess into which a projection runs to rotate the tentacle 5 from the oncoming driver 2, are possible. Different types of possible driving connections are known, for example, from conventional pull-out furniture parts with self-closing devices ago. 20
The tentacle 5 is attached to a front jaw member 7 or formed integrally therewith. The front jaw part 7 is pivotally connected to a rear jaw part 8, so that the jaw parts 7, 8 are at least limited to each other about a pivot axis 9 against each other, which is parallel to the axis 6. 25
The front and rear jaw members 7, 8 together form a belt unit surrounding an inner brake member 10 over most of its circumference. The wrap unit surrounds the inner brake member 10 in the embodiment over its entire circumference, except for a gap between the 30 of the articulated connection with the rear jaw remote front end 11 of the front jaw member 7 and the articulated connection with the front jaw part. 7 remote rear end 12 of the back jaw part 8 12- ♦ ····································································································. · • • · • • • ·* • · · · lies. This gap preferably extends over less than 45 ° with respect to the angle about the axis 6.
A basicist! of the front jaw part 7 has on its inside a recess in which a brake pad 13 is arranged. Its inner (= directed to the axis 6) surface forms a driven friction surface 14 which abuts against the outer (= away from the axis 6) surface of the inner brake member 10, which forms a fixed friction surface 15. The inner brake member 10 is held against rotation about the axis 6, in the embodiment by a rotationally fixed connection with the rotatably mounted shaft 24th
The friction surfaces 14, 15 form a friction pair, whereby the rotation of the driven friction surface 14 about the axis 6 is opposed to a braking force whose magnitude depends on the mutual contact force of the friction surfaces 14,15. The brake pad 13 is pressed by a pressure spring 16 to the inner brake member 10, wherein in the illustrated embodiment, a bent leaf spring is provided for this purpose, which is held on the outside of the front jaw part of this and the brake pad 13 through an opening 17 in the base part of acted upon front jaw part 7 therethrough.
The device thus has a first, mechanically acting braking device, which is designed as a rotational damper and which comprises the front and the rear jaw part 7, 8 comprising the belt unit and the inner brake part 10. The braking force of this first brake device is set by a second brake device as a function of the movement speed of the component to be damped 1 (= controlled), as will be explained below.
The rear jaw member 8 is connected to a damper sleeve 18, so that when the rear jaw member 8 is rotated about the axis 6, the damper sleeve 18 is also rotated about the axis 6 by the rear jaw member 8. In the exemplary embodiment, the damper sleeve 18 for this purpose has a driving lug, which projects outwardly through a window recess 20 in the inner brake member 10 and in a recess of the back
*. A reverse training (driving lug on the rear jaw part 8, recess in the damper sleeve 18), for example, possible. The damper sleeve 18 is about the predetermined by the window recess 20 angle range relative to the inner brake member 10verdrehbar, in the embodiment shown about 45 °, with larger or smaller hints Iberei che are possible.
The outer surface (directed away from the axis 6) of the damper sleeve 18 forms a driven damper surface 21. The inner surface (of the axis 6) of the inner brake member 10 forms a retained damper surface 22. The damper surfaces 21,22, in particular at least one portion their circumference are cylindrical (in the embodiment shown over its entire circumference, apart from the areas of the driving lug 19 and the window recess 20), between them a gap, in which a viscous damping medium is arranged, which is here in the form of a non-flowable fat is. During the rotation of the driven damper surface 21 with respect to the retained damper surface 22, a braking force occurs due to the shear friction acting on the damping medium 23.
The device thus comprises a second braking device, which is designed as a rotary damper and the damper sleeve 18 and the inner brake member 10 and arranged in the gap between them damping medium 23 comprises.
Instead, the damping medium 23 could be arranged in the gap between the damper sleeve 18 and the fixed shaft 24. The driven damper surface would then be formed by the inner surface of the damper sleeve 18 and the retained damper surface would then be formed by the outer surface of the shaft 24 and the second brake device would then comprise the damper sleeve 18 and the fixed shaft 24. It could also be arranged both in the gap between the damper sleeve 18 and the inner brake member 10 and in the gap between the damper sleeve 18 and the shaft 24, a viscous damping medium 23, so in this case, the second brake device comprise all these parts * 14 * *. There would be two driven damper surfaces and two retained damper surfaces.
The braking force exerted by the second brake device brakes the rotation 5 of the damper sleeve 18 about the axis 6. On the rear jaw part 8 is thereby exerted on the rotation of the belt unit about the axis 6, a restraining force, and more so, the greater the rotational speed of the Wrapping unit about the axis 6 is. The front and the rear jaw part 7, 8 are thereby more or less strongly compressed, the brake pad 13 10 is more or less displaced outwardly against the pressure spring 16, thereby the pressure spring 16 biases and thus the mutual pressure force of the friction surfaces is increased. The braking force of the first brake device increases as the speed of the component 1 increases. 15 When a maximum pressing force of the brake pad 13 is reached on the inner brake member 10, it comes with a further compression of the jaw members 7,8 to rest the adjacent to the brake pad 13 areas of the inner surface of the front jaw member 7 to the inner brake member 10. The mutual However, the friction coefficient of these interacting surfaces is much smaller than the friction coefficient of the friction pair. The pressing force of the brake pad 13 on the inner brake member 10 is thereby limited, whereby at a further increase in the speed of the component 1, the total braking force of the device is no longer or only slightly increased. 25 is located between the ends 11,12 of the Umschlingungseinheit an open-holding spring 25. If starting from the idle state, the front jaw part 7 is rotated about the axis 6 with increasing speed, the force of the hold-open spring 25 must first be overcome until it to a Compression of the jaw parts 7.8 comes. The hold-open spring 25 can be prestressed for this purpose (a limitation of the pushing apart of the ends 11, 12 is not shown in the figures for the sake of simplicity). At low speeds of the component 1 Μ Η ·· • · * ♦ * * * * * · · * | This allows the braking force exerted by the device to be kept to a minimum.
At rest, the pressure spring 16 presses the brake pad 13 preferably only 5 with a small force or not at the detained friction surface 15 at.
The rear jaw part 8 could likewise be equipped with a brake lining which, for example, could be spring-loaded analogously to the brake lining 13 of the front jaw part 7. 10
In modified embodiments, the spring loading of the at least one brake pad could also be omitted.
In the embodiment shown, the front and rear jaw members 7, 15 8 have relatively low friction coefficients away from the region of the friction surface 14 formed by the at least one brake pad 13 on their inner surfaces relative to the outer surface of the inner brake member 10, so that these Surface areas hardly contribute to the braking force exerted by the first braking device (less than 10%). In modified Ausführungsfor-20 men separate pads could also be omitted and one-piece jaw members 7,8 or at least one of these could directly form at least one friction surface of the first brake device. Suitable materials of the respective baking element and of the inner braking part could be selected for this purpose and / or a coating of the respective baking part and / or the inner braking part could be provided. An embodiment of the inner brake part with at least one brake pad formed by a separate part is also possible.
The wrapping unit could also comprise more than two axes of jaws which are articulated to each other about axes lying parallel to the axis 6.
In a modification of the first embodiment, the wrapping unit having the jaw parts 7, 8 could also be prevented from rotating about the axis 6. FIG. • ··· • • • • • ·· c ··· ·· ** • tt * · «• · * be. One can imagine for this purpose that the tentacle 5 is held against rotation about the axis 6. In fact, one will be able to omit the tentacle 5 in such an embodiment and form the support against rotation about the axis 6 by a modified design. In this modified embodiment, the component to be damped would rotate the shaft 24 in a direction opposite to the arrow 26. The friction surface 15 of the inner brake member 10 would then be the driven friction surface, and the friction surface 14 of the wrap unit would then be the retained friction surface. A second embodiment of a device according to the invention is shown in FIGS. 4 to 15. The device we are here used to dampen the insertion movement of movably mounted components 1, which are formed by drawers, the drawer guides for the drawers are not shown. Also for damping the insertion movement of other extendable furniture parts 15, the device can be used in an analogous manner. In the device here a pull-in spring 27 is additionally integrated to provide a self-closing for the pull-out furniture part over the last part of the Einfahrweges.
Substantially equivalent or at least analogous parts are denoted largely by the same reference numerals as in the first embodiment. At the back of a respective component to be damped 1, a driver 2 is mounted, which has slide tracks 3, which can be formed as shown by wells or through openings. A tentacle 5 of the device has projections 4, which are formed here of roles and with the coolies-25 senbahnen 3 interaction. A U-shaped design of the driver 2 with opposing slide tracks 3, each cooperating with a projection 4, is preferred, whereby a single co-operating with a projection 4 slide track 3 could be provided. A reverse training is possible in which at least one slide track on the tentacle and mindes-30 least a projection on the driver is provided. 17 • · 4 4 4 4 4 4 4 4 4
44 44 I
In the inserted state of the pull-out furniture part (cf., the three lower drawers in Fig. 4 and Figs. 6, 7 and 11) of the tentacle 5 assumes its basic position. When the pull-out furniture part is pulled out in the pull-out direction 68, the catching arm 5 is pivoted about the axis 6 until it assumes its waiting position (see the upper drawer in FIG. 4 and FIGS. 5, 8, 9 and 12). In this position of the tentacle 5, the driver 2 decoupled from the tentacle 5. When inserting the pull-out furniture part (movement in the direction of arrow 44), the driver 2 connects to the waiting in his waiting position fishing arm 5, whereupon the fishing arm 5 rotates back about the axis 6 until he returns to the basic position -10 and the extendable Furniture part is completely inserted.
Other embodiments of the driver 2 and the tentacle 5 are possible to allow such coupling and uncoupling with the pivoting of the tentacle between its basic position and its waiting position. Different types 15 of possible driving compounds are known, for example, from conventional pull-out furniture parts with Selbsteinzüge (= Einziehmechaniken) ago.
The operating principle of the device is similar to the first embodiment described above, with the extensions described below and 20 differences.
The inner brake member 10 and a mounted on this housing part 28 are rotatably connected to the rail 29, which in turn is attached to the furniture body 30.
The attachment to the rail 29 is preferably carried out by latching projections of the inner braking member 10 and the housing part 28, which engage in recesses in the rail 29. An attachment of the device directly to the furniture body 30 is conceivable and possible.
The unit formed by the inner brake part 10 and by the housing part 28 preferably has an inner cavity penetrating it completely axially (see FIG. 14). This can accommodate parts of a Ausziehsperrvorrichtung, as will be described below with reference to FIGS. 16 and 17. 18 • ♦ · »# # # # Φ Φ ΦΦ ΦΦ Φ Φ Φ Φ Φ« «« «« «I I I · ·
The tentacle 5 is rotatably mounted on the unit formed by the inner brake member 10 and the housing part 28 about the axis 6.
The tentacle 5 is connected to a preformed, but flexible by its elasticity Umschlingungsteil 31, so that the Umschlingungsteil 31 is also rotated upon rotation of the tentacle 5 about the axis 6 in the direction of arrow 26 about the axis 6. The wrap member 31 is formed in the embodiment of a band and extends around a majority of the circumference of the inner brake member 10 around this. The inner (= the axis 6 facing) surface of the Umschlingungsteils 31 forms a driven friction surface 14, which cooperates to generate a braking force with the outer (= 6 away from the axis) surface of the inner brake member 10 which forms a fixed friction surface 15 (im Embodiment, this is the lower portion of the wall 40). The driven friction surface 14 and the retained friction surface 15 form the friction pairing of the first, mechanically acting brake device, which comprises the loop part 31 and the inner brake part 10.
The connection of the catching arm 5 with the wrap-around part 31 takes place via an overload spring 32, which is formed integrally with the wrap-around part 31 in the embodiment shown and is formed by a bow-shaped or loop-shaped section of the band forming both the wrap-around part 31 and the overload spring 32 , The geometry of this arcuate or loop-shaped course and the elasticity of this portion of the band are designed so that there is a spring element with the desired spring characteristic. In modified embodiments, the overload spring 32 can also be formed by a separate part which is arranged in the transmission path between the catching arm 5 and the at least one driven friction surface 14 of the first braking device. Instead or in addition, an overload spring could also be arranged at a different point in the transmission path of the force transmitted to the device to be damped from the device and the device driving force, at the same time. For example, between the inner brake member 10 and the rail 29. In other embodiments, an overload spring can also be omitted.
The transition between the wrap-around part 31 and the overload spring 32 can be regarded as the front connection point 33 of the wrap-around part 31, at which the movement of the component 1 to be damped is introduced into the wrap-around part 31.
At a rear connection point 34, the wrap-around part 31 is connected to a damper sleeve 18. Here, in the illustrated embodiment, an axial projection of the loop portion 31, which has a slot 35, inserted into a recess in the region of the lying in Fig. 13 bottom side of a radial projection 36 of the damper sleeve 18, wherein the slot 35 arranged in a recess in this Web engages (the recess of the radial projection 36 and the web disposed therein are not visible in Fig. 13).
Between the front connection point 33 and the rear connection point 34, the wrap-around part 31 extends over more than 90 °, preferably over more than 180 °, particularly preferably over more than 250 ° in a first (opposite to the arrow 26) rotational direction with respect to the axis 6 around the inner brake member 10. In the illustrated embodiment, this extension is less than 360 °. An extension of more than 360 ° is possible, i. the wrap-around part then has more than one complete turn, wherein it runs helically around the inner brake part 10.
The rear connection point 34 of the wrap-around part 31 is connected to the catching arm 5 via an open-necked spring 25. This hold-open spring 25 is formed integrally with the wrap-around part 31 in this exemplary embodiment and is formed by an arc-shaped or loop-shaped section of the strap, which also forms the wrap-around part 31 and optionally the overload spring 32. The geometry of the arcuate course and the elasticity of this section of the band are adapted to a desired spring characteristic. The function of the open spring spring 25, which, when damping the movement of the component 1, is the rear connection point of the belt part opposite the front connection point of the belt part in the direction of rotation 26 (this is the opposite direction of rotation in which the belt part from the front connection point to the rear connection point applied to the axis 6), is at least largely analogous to the open-holding spring described in the first embodiment and will be described in more detail below.
The hold-open spring 25 could also be formed by a separate part or omitted.
The overload spring 32 is substantially harder, preferably more than 10 times harder than the hold-open spring 25th
The damper sleeve 18 has in this embodiment, a wall 37 which engages in a slot between an inner and an outer wall 39,40 of the inner brake member 10. Furthermore, the damper sleeve 18 has a wall 38 which engages over an upper portion of the outer wall 40 of the inner brake member 10. The inner and outer surfaces of the wall 37 of the damper sleeve 18 and the inner surface of the wall 38 of the damper sleeve 18 form driven damper surfaces 21. The outer surface of the wall 39 of the inner brake member 10, the inner surface of the wall 40 of the inner brake member 10 and the upper portion of the outer surface the wall 40 of the inner brake member 10 form retained damper surfaces (the lower portion of the wall 40 forms the retained friction surface 15). Between the driven damper surfaces 21 and the retained damper surfaces 22 is in each case an annular gap, in which a viscous damping medium 23 is arranged. Sealing rings 41, 42 define the gap between the outer surface of the wall 39 and the inner surface of the wall 37 at the upper end and the gap between the upper portion of the outer surface of the wall 40 and the inner surface of the wall 38 at its lower end, so that a sealed space is trained. As a damping medium, therefore, a flowable oil can be used. The use of a non-flowable fat is also possible. The sealing rings 41, 42 could then be omitted in principle.
The second brake device thus comprises the damper sleeve 18, the inner brake part 10 and the damping medium 23.
By the rotation of the catching arm 5 about the axis 6 in the direction corresponding to the arrow 26, the looping part 31 is rotated about the axis 6, which is rotated by the connection of the wrapper 31 with the damper sleeve 18 10 about the axis 6. The axis 6 thus forms both the axis of rotation of the first and the axis of rotation of the second brake device. Depending on the speed of rotation of the damper sleeve 18 about the axis 6, the second braking device exerts a more or less large braking force, whereby between the front joint 33 and the rear connection point 34 of the um-15 schlingungsteils 31 a more or less large tensile force acts. Depending on the size of this tensile force is a more or less strong contact pressure of the driven friction surface 14 to the fixed friction surface 15th
In the rest state of the device, the wrap-around part 31 advantageously at least partially has a distance from the retained friction surface 15. Preferably, the wrapping member 31, due to its preforming at rest, has over at least substantially the entire course of a friction surface 14, i. at least over 90% of its extent in the circumferential direction, a distance from the friction surface 15 of the inner brake member 10. 25
Due to the elasticity of the wrap-around part 31 and / or the preferably present hold-open spring 25, the friction surface 14 of the wrap-around part 31 is then up to a limit value of the speed of the component 1 or a limit value of the rotational speed of the catching arm 5 from the friction surface 15 of the inner 30 brake part 10 spaced (at least in sections) and the first brake device is substantially ineffective (ie their braking effect is in any case less than 22 22 * * * * the braking effect of the second brake device). Only when exceeding this limit, the first braking device is effective.
At a high speed, with which the component 1 impinges on the catching arm 5, 5 it would come without the overload spring 32 to a suddenly occurring high braking force of the device, whereby undesirably high loads and an undesirably strong braking of the component 1 would result. By the overload spring 32, the peak of the braking force is cushioned by the catching arm 5 with respect to the loop member 31 under deformation of the overload spring 32 twist 10 can. in the illustrated embodiment is further, as already mentioned, a pull-in spring 27 is present, which, if only the damping function is desired, could also be omitted. The pull-in spring 27 extends between the catching arm 5 and the unit formed by the housing part 28 and the inner brake part 10. In particular, latching arms 43 are arranged on the housing part 28, between which the inner (= closer to the axis 6 located) end of the catch spring 27 can be engaged.
When pivoting the tentacle 5, starting from its normal position in Rich-20 tion of its waiting position, the collection spring 27 is first stretched, see. Fig. 11 and Fig. 10. Shortly before reaching the waiting position, a dead center is crossed (this is the position shown in FIG. 10), as a result, the catch spring is a little relaxed again until reaching the holding position shown in FIG. preferably less than one fifth of the previous compression stroke). 25
If, when inserting the pull-out furniture part, the carrier 2 starts against the catching arm 5, then these two parts couple to one another and the catch 2 pivots the catching arm 5 over its dead center. As a result, the extendable furniture part is retracted by the catching arm 5 by the force of the pull-in spring 27, until 30 the basic position of the catching arm shown in Fig. 11 is reached. The further pivoting is in the waiting position and the basic position by appropriate »· · · · · · · · ♦
Limited stops (in the basic position, this can also be achieved by a stop for the insertion movement of the pull-out furniture part).
The retraction of the extendable furniture part takes place here against the force exerted by the device braking force. Since the speed of retraction, if necessary after damping of the initially faster speed when starting against the tentacle, is relatively low, this is essentially only the relatively low braking force of the second brake device to overcome. The force of the pull-in spring 27 can thus be designed relatively low, which facilitates the removal of the pull-out furniture part.
If the pull-in spring 27 can be connected at different distances from the axis 6 to the housing part 28, for example by a plurality of latching arms 43 are provided, the strength of the pull-in force can be changed by different biases of the pull-in spring 27. Also connection possibilities at different locations of the tentacle 5 may be provided or a continuous change of the distance from the axis, e.g. by an eccentric element, can be provided.
In the embodiment, a bent leaf spring is provided as a pull-in spring. Also trained in other ways feed springs may be provided. By way of example, an embodiment variant with a leg spring is shown in FIG. 23. For example, a bent leaf spring could also be provided which optionally has a greater width in a central region than in the end-side connection regions and can also be bent upward or downward, for example.
The shrinkage of one of the projections 4 of the Einziehhebels 5 in the associated slide track 3 of the driver 2 when moving the component 1 in the direction of movement 44 is shown in Fig. 15. The curved slide track 3 (the course of both cam tracks 3 is identical) has an inlet section 3a, at the beginning of the projection 4 from outside the slide track 3 in the slide track 3 24 * · • #
retracts. Via the inlet section 3a, the slide track 3 guides the projection 4 in a direction 69 which encloses an angle d of less than 30 ° with the pull-out direction 68 directed counter to the direction of movement 44. In this case, the angle α increases continuously from the beginning of the inlet section 3a, in which this angle α is preferably less than 20 °, particularly preferably less than 15 °, to the end of the inlet section 3 a. The end of the inlet section 3a and the beginning of a continuation section 3b of the slide track 3 are therefore where this angle α reaches the value of 30 °. This angle α continues to increase over the continuation section 3b until it is more than 45 °, in the illustrated embodiment between 80 ° and 90 °, in FIG. 15 the angle α for a position of the projection 4 is drawn within the continuation section 3b, in which the angle α is slightly more than 45 °.
In the illustrated embodiment, the angle α, once it has reached its maximum value, to the end of the continuation section 3b constant. Also, a curved configuration of the link 3 to the remote from the inlet section 3a end of the continuation section 3b is possible in other embodiments.
The projection 4 is thus guided by the slide track 3 at least over a subsequent to the beginning of the inlet section 3a part of the inlet section of the slide track 3 at an angle of less than 20 °, preferably less than 15 ° to the pull-68. At least over part of the continuation section 3b, the projection 4 is preferably guided by the slide track 3 in a direction which, with the pull-out direction 68, forms an angle of more than 70 °, preferably more than 80 °.
In Fig. 15, three positions of the projection 4 when entering the slide track 3 are shown with dashed lines. The first position shows just the first start of the projection 4 to the side wall 45 of the slide track 3, through which the Einziehhebel 5 is pivoted over the dead center (this side wall 45 is then in the continuation section 3b with respect to the direction of movement 44 of the component 1 rear side wall the slide track 3). The angle α is here 25 • # less than 20 °, preferably less than 10 °. In the second position, the projection 4 is already in the continuation section 3b, in which case the angle α is just greater than 45 °. In the third position shown, the projection 4 is located in the continuation section 3b at the point that it occupies in the fully inserted state of the extendable furniture part, wherein the angle α is here in the embodiment between 80 ° and 90 °. The side wall 45 extends in each case in the direction in which the projection 4 is guided by the slide track 3, so that the angle which the side wall 45 includes in each case with the pull-out direction 68, the angle α between the direction of the guidance of the projection 4 and the pull-out direction 68 corresponds.
Due to the described curved course of the at least one slide track 3, the force required to actuate the catching arm 5 during insertion of the component 1 can be influenced. In particular, results from the course of the inlet section 3a a kind of translation. The damping force acting on the component 1 is thereby reduced, when the component 1 starts at a certain speed against the catching arm 5, at the beginning of starting when the projection 4 is located in the region of the inlet portion 3a of the guide track 3. Furthermore, the dead center of the pull-in spring 27 (if present) can thereby be overcome by a smaller force to be applied by the component 1.
When turning back the tentacle 5 in the direction opposite to the arrow 26 is rotated by the tentacle 5 on the open ha Itefeder 25, the damper sleeve 18 so that the force to be overcome in this case is exercised. This force is comparatively low, since the first brake device is not effective in this direction of rotation. If the application of such a force is not desired, however, it is possible to provide a freewheel between a part connected to the loop part 31, optionally via the hold-open spring 25 and / or the overload spring 32, and the catch arm 5, which in the direction of rotation corresponding to the arrow 26 is closed and opens in the opposite direction of rotation. Such freewheel are known, also in connection with dampers. 26 • * 26 • * • * • • «* *
From Fig. 15 also shows a self-healing section 3c of the slide track 3 shows. Through this, the respective projection 4 can enter into the continuation section 3b, when the driver 2 should start when inserting the component 1 to the retraction lever 5 located in its basic position. The self-healing portion ver-5 is at least substantially (i.e., deviating less than 15 °) parallel to the withdrawal direction 68. The self-healing portions 3c are widened towards their open ends by lead-in slopes. Thus, a retraction of the projections 4 is made possible by the self-healing sections 3c, the projections 4 but not by the self-healing sections 3c from the continuation sections 3b leak 10, the elasticities of the components can be exploited (so that the jump before 4 as shown in FIG 15 is in the retracted state of the component 1 offset from the self-healing section 3c). For example, it would also be possible to drive over the steps when retracting the projections 4 by the self-healing sections 3c, wherein the side cheeks 2a, 2b having the slide tracks 3 are pressed apart. Additionally or instead could be provided on the driver 2 arranged, additional resilient locking elements.
In a modified embodiment in relation to the illustrated embodiment, the catching arm 5 could also be pivotally mounted on the damper sleeve 18 and indeed about an axis 6 parallel to the axis of rotation. The connection of the wrap-around part 31 or the overload spring 32 connected to the wrap-around part 31 could then take place on the catching arm radially outside this pivoting axis. By a return spring of the tentacle 5 could be acted upon in an initial position with respect to its pivot axis relative to the damper sleeve 18. When 25 damping the movement of the component 1, when the tentacle arm 5 is pivoted against the force of the return spring acting on it about the pivot axis more or less, since the rotation of the pivot axis about the axis 6 is braked by the braking force of the second brake device, is the wrap-around part 31 is tightened more or less and pressed against the retained friction surface 15. 30
Other linearly displaceably mounted components as extendable furniture parts can be damped by the braking device. Furthermore there is a damping • * ♦ * »♦ *« »* * * *» ·· «· · ι *« «· * ·· *» tm 07 ······· · »£ / * · * From rotatably mounted components, depending on the application, a pull-in spring 27 may be provided or may be omitted. A connection of the component to be damped to the device may optionally also be carried out in a manner other than via a radially projecting arm (= catch lever) rotatably mounted about the axis 6, for example a pinion rotatably mounted about the axis 6 and connected to the loop portion 31, optionally over overload spring 32 is connected.
The wrap-around part 31 can also be formed by a wire, in particular a spring wire, or a cord instead of a band. The angle of wrap of the wire or cord is favorably between 90 ° and 530 °, preferably between 180 ° and 500 °, wherein a wrap angle between 250 ° and 330 ° is particularly preferred.
Also, a kinematic reversal is possible, wherein the inner brake member 10 and the inner brake member 10 and possibly also the housing part 28 comprehensive unit is driven by the component to be damped 1 and the wrap member 31 at its front junction 33 and held on this damper sleeve 18 becomes. The driven friction surface 14 described above and shown in the drawing then becomes the gripped friction surface and vice versa. The driven damper surface 21 described above and shown in the drawing then becomes the retained damper surface and vice versa. The holding of the belt part could then also be done by a part other than a protruding from the axis 6 arm (corresponding to the tentacle 5).
FIGS. 16, 17 and 17a show a modification of the second embodiment of the invention, which illustrates the integration of a pull-out locking device into a device according to the invention. Apart from the differences described below, the device according to the invention is the same as the embodiment of the device according to the invention described with reference to FIGS. 4 to 15.
Ausziehsperrvorrichtungen serve that of several on the Ausziehsperrvorrichtung coupled extendable furniture parts only one is simultaneously extendable. Only after the insertion of this pull-out furniture part another can be pulled out. Furthermore, via such a pull-out locking device, if desired, a central locking can be provided.
In the embodiment of the Ausziehsperrvorrichtung shown in the embodiment extend between actuators, which are assigned to the individual extendable furniture parts, locking bars, which have only a limited space (= etn limited game) for their displacement. If one of the pull-out furniture parts pulled out, so are the two (if it is a middle extendable furniture part, the operating part on both sides locking bars are arranged) with the actuating part cooperating locking rods moved apart from the operating part. As a result, the existing space is used up, so that a movement apart of cooperating with another of the operating parts locking rods is no longer possible and thus no more extendable furniture part can be pulled out more. The operating part of an end-side extendable furniture part can also interact only with a locking bar, which shifts it when removing this extendable furniture part. The basic design of Ausziehsperrvorrichtung corresponds to the extent of the prior art, for example, according to the aforementioned writings to Ausziehsperrvorrichtungen.
The unit formed by the inner brake part 10 and the housing part 28 has a floating space 46 extending in the direction of the axis 6 and fully penetrating the unit. From this parts of the Ausziehsperrvorrichtung can be added.
By a, when removing and inserting the extendable furniture part rotated about the axis 6 part, in the illustrated embodiment by the tentacle 5, a this extendable furniture part associated actuating member 47 is adjusted. If further extendable furniture parts are arranged above and below the pull-out furniture part, then the actuating part 47 displaces an upper locking bar 48 upwards and / or one lower locking bar 49 down. If it is the lowest extendable furniture part, only an upper locking bar 48 could be moved upwards. If it is the top pull-out furniture part, only a lower locking bar 49 could be moved down.
The actuating member 47 is formed in this embodiment as rotatable about the axis 6 cam. A cam follower part 50, 51 is attached to the locking rods 48, 49 actuated by the actuating part 47, the cam follower parts 50, 51 being secured against rotation about the axis 6.
Upon rotation of the actuating member 47 about the axis 6 in a first direction of rotation, the two cam follower parts 50, 51 are pressed apart (by a displacement of at least one of the locking rods parallel to the axis 6) and at a rotation in the opposite direction of rotation (corresponding to the arrow 26) they approach each other again.
The actuating member 47 can be moved relative to the tentacle 5 in the direction of the axis 6 by a limited distance, while still remaining in rotationally fixed connection with the tentacle 5. In the exemplary embodiment, for this purpose, the tentacle 5 in the direction of the axis 6 extending claws 52, which engage in recesses 53 of the actuating member 47.
A displacement of at least one of the locking rods 48, 49 by a one of the extendable furniture parts associated actuating part, without the rotationally fixed connection of the remaining actuating parts is repealed with the respective associated tentacle, is made possible.
The cam follower part 50 has an axial extension 50a with latching tongues 50b. The cam follower 51 has an axial extension 51a with latching tongues 51b. 30 30 »* * * • • • • • • • • Ι • 4 '••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••
The cam follower 51 is inserted with the extension 51 a in the cavity 46 and the cam follower part 50 can be inserted with the extension 50 a through a central opening of the actuating member 47 in a central opening of the cam follower 51. By the locking tongues 50b, 51b, the parts are held together for ease of assembly before assembly of the device, wherein after installation, the required range of motion is maintained.
The entrainment between the Umschlingungsteil 31 and the damping sleeve 18 is here indicated by an axial projection 35 'of the Umschlingungsteils 31 and a receiving this recess 36' in the damper sleeve 18, see. in particular Fig. 17a.
The actuation of the locking rods 48, 49 could also be done in other ways. Such another possible embodiment is shown in FIGS. 18 to 21. Here, the actuating member 47 is formed in the form of a cam member which is pivotable about a pivot axis 54 perpendicular to the axis 6. The actuating member 47 cooperates with the end of the at least one adjacent locking bar 48, 49 or a part connected to this locking bar to move the locking bar 48, 49 in its respective direction parallel to the axis 6 when pivoting about the pivot axis 54.
The actuating part 47 has an actuating arm 47a, which projects radially from the pivot axis 54 and is in communication with a sleeve 55 rotatable about the axis 6. Upon rotation of the sleeve 55 about the axis 6, the actuating member 47 is pivoted about the pivot axis 45. Between the sleeve 55 and the actuating arm 47a a limited shift in the direction of the axis 6 is possible, for example, by a fork-shaped configuration of the end of the actuating arm 47a, in which a sleeve 55 attached to the pin 56 engages.
The sleeve 55 may be connected to the catching arm 5 or another part which rotates about the axis 6 when the catching arm is rotated about the axis 6, for example with the damper sleeve 18. Also a one-piece design with the * * · * ♦ ♦ · ♦ ♦ · «« ·· «· t« · · < •••• 4 ··· «♦ ···« · · ♦
Ol ··· »·· i · # ····
Catch 5 or the rotated about the axis 6 part, for example, the damper sleeve 18 is possible.
The telescoping furniture parts coupled together by the pull-out locking device could also be arranged side by side rather than vertically one above the other. The locking bars 48, 49 and the axis 6 would then be arranged horizontally. The terms "top" used in the preceding description and "below" would then have to be replaced by "left" and "right" be replaced. In principle conceivable and possible are inclined relative to the horizontal arrangements of the locking rods 48,49 and the axis. 6
FIGS. 23a and 23b show a modification of the first embodiment described with reference to FIGS. 1 to 3 in order to equip the first embodiment with a pull-in spring 27. This is for example as shown formed as a leg spring (also training in another form, for example in the form of a leaf spring as shown in the second embodiment could be provided) and engages on the one hand on the tentacle 5 and on the other hand on a housing part 28, the rotationally fixed with respect to a rotation held about the axis 6, for example by a rotationally fixed connection with the shaft 24. Also a rotationally fixed connection with the inner brake member 10 could be provided.
The function of the pull-in spring 27 is completely analogous as described in connection with the second embodiment. When pivoting the tentacle 5 from its basic position to its waiting position, the pull-in spring 27 is tensioned, being traversed before reaching the waiting position over a dead center and thus holds the tentacle pivoted into the waiting position 5 in this.
A third embodiment of the invention is shown in FIGS. 24 to 27. To dampen here is in a rotatable about an axis 6 shaft 57 introduced rotary motion. For example, for this purpose, a fixed to a shaft portion 57a, projecting from the axis 6 tentacle 5 with a driver 2 interaction, which has a slide track 3, in soft a projection 4 of the tentacle 5 enters. • «« «
The driver 2 is attached to an only schematically indicated component 1, wherein the shaft 57 is rotated by the component 1.
For example, the shaft 57 could also be rotated by a pivotable component, for example a flap, wherein the component is, for example, rigidly connected to the shaft 57 and is thus pivotably mounted about the axis 6. A separate pivotable mounting of the component is possible.
The shaft 57 further comprises a shaft part 57b, which is rigidly connected to the shaft part 57a and which is designed as a hollow shaft and has a receiving space for receiving further parts of the device.
In the receiving space of the shaft portion 57b projects in the axial direction of the shaft 57 extending detained damper part 58 which is rigidly connected to a fixed base member 59. With a portion of the captured damper part 58 disc-shaped, held friction parts 60 are rotatably connected. With the detained friction parts driven friction members 61 cooperate, which are rotatably connected to the shaft portion 57b. For rotationally fixed connection with the shaft part 57b, the shaft part 57b has inwardly projecting webs 57c, which engage in depressions 61a on the outer edge of the disk-shaped driven friction parts 61.
The detained and driven friction members 60, 61 are alternately stacked in the manner of a multi-plate clutch. The facing surfaces form retained and driven friction surfaces 15, 14.
The first mechanically acting brake device thus comprises the retained and driven friction parts 60, 61.
The gripped friction parts 60 which are located between driven friction parts 61 can be displaced in the direction of the axis 6 relative to the retained damper part 58. FIG. The driven friction parts 61 are displaceable in the direction of the axis 6 relative to the shaft part 57b.
In the receiving space of the shaft part 57b a driven damper part 62 is further arranged. This is driven by the movement of the component to be damped 1 via the shaft 57 and the coupling member 64 and is for this purpose connected via the coupling spring 63 with the coupling part 64, which in turn is non-rotatably connected to the shaft part 57b. For the rotationally fixed connection with the shaft part 57b, the coupling part 64 on the outer edge of an annular federal depressions 64a, in which engage the webs 57c of the shaft portion 57b. The coupling part 64 is in this case displaceable in the direction of the axis 6 relative to the shaft part 57b.
A portion of the outer surface of the retained damper portion 58 forms a captured damper surface 22. An inner surface of the driven damper portion 62 forms a driven damper surface 21. In the gap between the driven damper surface 21 and the retained damper surface 22 is a viscous damping medium 23. The second brake device thus comprises the retained damper part 58, the driven damper part 62 and the damper medium 23 arranged between them.
If no braking force was exerted by the second brake device, the driven damper part 62 would be taken over the coupling spring 63 from the coupling part 64 without changing the angular position between the coupling part 64 and the driven damper part 62. However, the greater the rotational speed of the shaft 57, the greater will be the braking force produced by the second braking device. This leads to a speed-dependent angular offset against the restoring force of the coupling spring 63 between the rotational position of the driven damper part 62 and the coupling part 64 and thus also with respect to the angular position of the shaft 57th
The driven damper part 62 and the coupling part 64 have cooperating control surfaces 65, 66. The control surfaces 65, 66 have one around the axis 6 lou- • · »··· ·« t · * · «· **. ····························································································································································································································································
The driven damper part 62 is supported against an axial displacement directed away from the friction parts 60, 61. With increasing angular displacement between the driven damper part 62 and the coupling member 64, the coupling member 64 is displaced by the cooperating control surfaces in the axial direction against the friction members 60, 61, wherein the furthest from the coupling member 64 remote friction member (here a detained friction member 60) against an axial Displacement is supported in this direction Rich-10, for example, by the head of a detent member 58 connected to the retaining pin 67th
With increasing speed of the shaft 57, the driven and retained friction surfaces 14,15 are thus increasingly pressed against each other, whereby the braking force of the first braking device increases with increasing speed of the shaft 57.
The first brake device could also be designed differently than in the manner of a multi-disc brake. For example, a retained friction member 60 could be provided which includes a conical retained friction surface 15 extending about the axis 6 which cooperates with a conically driven friction surface 14 of the driven friction member 61.
The driven damper part 62 could also be connected via the coupling spring 63 to the shaft part 57b, one of the driven friction parts 61 or another part driven by the shaft 57.
To cushion load peaks, an overload spring could be arranged in the transmission path of the component 1 to be damped transmitted to the device and the device 30 driving force. For example, the shaft parts 57a, 57b could be rotated against each other against the restoring force of this overload spring. Another possibility would be, for example, that the retained damper part 58 is above 35 9 9 9 9 9 9 9 9 9 · 9 9 9 9 9 9 9 9 9 9 9 • 9 9 9 9 9 9 99 99 9 • 9 «to connect an overload spring with the ßasisteil 59, so that upon occurrence of a load peak, a rotation of the detained damper part 58 relative to the base member 59 can be made against the restoring force of the overload spring. The captured damper portion 58 is then held by the overload spring against a continuous rotation about the axis 6, such that it despite a certain rotation of the retained damper 58 when a load peak occurs in the course of damping the movement of the component 1 yet to a rotation of the driven At least in the steady state, when a steady balance has been established, the angular position of the festgehaitenen damper part 58 remains unchanged.
The design of the device could also be reversed to the effect that the shaft 57 is fixed and to damp the movement of the component 1 from the component 1, the base part 59 (which may be modified here) is rotated about the axis 6. The at least one driven friction member then becomes the retained friction member and the at least one retained friction member then becomes the driven friction member. Furthermore, then the detained damper part to the driven damper part and the driven damper part is the detained damper part. The captured damper part is then held by the coupling spring 63 against rotation about the axis 6, wherein a certain rotation of the detained damper part is possible, whereby the control surfaces 65,66 are actuated. At least in the stationary state of the device, if there is a constant balance (with the same drive of the device), the angular position of the detained damper part remains unchanged.
In the above-described embodiments, the axis of the first brake device coincides with the axis of the second brake device, respectively, as is preferred. But there are also conceivable and possible training in which these axes are, for example, parallel to each other, but at a distance from each other. Even angular alignments between these axes are possible in principle. Between the first and the second brake device, it is necessary to be able to move between the first and the second brake device. 36 36... 36. · #·· then appropriate transmission elements, for example, gears may be provided.
In the described embodiments, in each case a first mechanically acting brake device with two parts rotatable relative to one another about an axis (= first rotational damper) and a second braking device coupled with this first braking device, the braking force of which is at least one gap between two opposite one another about an axis rotatable parts arranged viscous damping medium is caused (= second rotary 10 damper). In this case, modified embodiments of such a device are possible in different ways. • · ································· * * * * * * * * * * * * * * * * * * * * *
Key to the reference numbers: 1 component 26 arrow 5 2 driver 27 intake spring 3 slide track 28 housing part 3a inlet section 35 29 rail 3b continuation section 30 furniture carcass 3c self-healing section 31 wrap 10 4 projection 32 Überiastfeder 5 tentacle 33 front junction 6 axis 40 34 rear junction 7 front jaw part 35 slot 8 rear jaw part 35 'projection 15 9 pivot axis 36 projection 10 inner brake part 36' recess 11 end 45 37 wall 12 end 38 wall 13 brake lining 39 wall 20 14 driven friction surface 40 wall 15 detained friction surface 41 sealing ring 16 pressure spring 50 42 sealing ring 17 opening 43 locking arm 18 damper sleeve 44 direction of movement 25 19 driving lug 45 side wall 20 window recess 46 cavity 21 driven damper surface 55 47 actuating member 22 recorded damper surface 47a operating arm 23 damping medium 48 locking rod 30 24 shaft 49 locking rod 25 retaining spring 50 cam follower part 50a extension 15 58 retained damper part 50b latching tongue 59 base part 51 cam follower part 60 retained friction part 51a extension 61 driven friction part 51b latching tongue 61a recess 52 jaw 20 62 driven damper part 53 recess 63 coupling spring 54 pivot axis 64 coupling part 55 sleeve 64a recess 56 Pin 65 Control surface 57 Shaft 25 66 Control surface 57a Wellentei! 67 retaining bolt 57b shaft part 68 extension direction 57c bridge 69 direction

权利要求:
Claims (15)
[1]
Patent Attorneys • "Hofmann SeFechner Dr. med. Ralf HofrQam · 'Dr. Thomas liecfwer 6806 Feldkirch, Austria · j / * J.143 (fifc522 73 137 • 1 ': f =. 43ie) 6522 73 359 M office@vpat.at Egelseestr 65a, PO Box 61 61 f www.vpat.at 24353 33 / ss 111117 39 Claims 1. A device for damping the movement of a movably mounted component (1), comprising a first, mechanically acting braking device which has at least one friction pair, in which for generating a braking force a driven friction surface (14) about an axis (6) of the first brake device is rotatable relative to a detent friction surface (15) resting against it, and a second brake device coupled to the first brake device, wherein the mutual contact pressure of the friction surfaces (14,15) of the friction pair or of at least one of Friction pairing of the first brake device in response to a force exerted by the second brake device braking force, characterized in that the second brake device at least ei ne about a shaft (6) of the second brake device rotatable, driven damper surface (21), which includes at least one detained damper surface (22) at least one gap in which a viscous damping medium (23) is located, which upon rotation of the at least one driven damper surface (21) relative to the at least one detained damper surface (22) causes a braking force of the second brake device.
[2]
2. Device according to claim 1, characterized in that the axis (6) of the first braking device about which the driven friction surface (14) of the friction pair or a respective one of the friction pairings of the first braking device is rotatable with the axis (6) of the second braking device around which the at least one driven damper surface (21) of the second brake device is rotatable.
[3]
3. Apparatus according to claim 1 or 2, characterized in that a flexibly formed loop part (31) an inner brake part (10) at least 40 ······ * a more than 90 °, preferably at least 180 °, amounting amount of the circumference the inner brake member (10) surrounds, wherein the wrap member (31) and the inner brake member (10) form the friction pair or at least one of the friction pairings of the first brake device.
[4]
4. The device according to claim 1 or 2, characterized in that at least two articulated mutually interconnected jaw parts (7, 8) together form a Umschlingungseinheit the first braking device having an inner brake member (10) at least over a more than 90 °, preferably at least 180th ° amounting portion of the circumference of the inner brake part (10) surrounds, wherein the belt unit and the inner Bremstei! (10) the friction surfaces (14,15) of the friction pair or at least one of the friction pairings of the first brake device.
[5]
5. Apparatus according to claim 3 or 4, characterized in that the transmission of the movement of the component to be damped (1) on a front connection point (33) of the Umschlingungsteils (31) or on a front of the jaw parts (7) of the Umschlingungseinheit, wherein the inner brake member (10) is retained, or the movement of the component (1) to be damped is transmitted to the inner brake member (10), the front joint (33) of the wrap member (31) or the front jaw member (7) being retained is, and that a rear connection point (34) of the Umschlingungsteilils or a rear of the jaw parts (8) of the Umschlingungseinheit is connected to a damper sleeve (18) having at least one of the damper surfaces (21,22) of the second brake device.
[6]
6. The device according to claim 5, characterized in that extending the Umschlingungsteil (31) from the front connection point (33) to the rear connection point (34) in a first rotational direction about the axis (6) of the first braking device or the Umschlingungseinheit from the end of the front jaw part (7) remote from the articulated connection of the front jaw part (7) to the end of the rear jaw part (8) lying away from the articulated connection of the rear jaw part (8) in a first direction of rotation Axle (6) of the first brake device extends.
[7]
7. The device according to claim 6, characterized in that an Offenhaltefe the {25) at least in the state of the device in which it dampens the movement of the component (1), the rear connection point of the Umschlingungsteils (31) opposite the front connection point of the Umschlingungsteils (31) or the rear jaw part (8) opposite the front jaw part (7) in a first direction of rotation opposite second direction of rotation about the axis (6) of the first braking device acted upon.
[8]
8. Device according to one of claims 5 to 7, characterized in that the inner brake member (10) or a herewith, preferably non-rotatably connected part having at least one damper surface (22,21) with the at least one damper surface (21, 22) of the damper sleeve (18) forms the gap or at least one of the gaps in which or in which the viscous damping medium (23) is located.
[9]
9. Apparatus according to claim 1 or 2, characterized in that at least one about the axis (6) of the first braking device rotatable driven friction member (61) the driven friction surface (14) or at least one of the driven friction surfaces (14) and at least one against a friction member (60) retained about the axis (6) comprises the retained friction surface (15) or at least one of the retained friction surfaces (15) and at least one driven damper portion (62) rotatable about the axis (6) of the second brake assembly the driven damper surface (21) or at least one of the driven damper surfaces (21) and at least one against a rotation about the axis (6) held damper part (58) the detained damper surface (22) or at least one of the recorded damper surfaces (22) that the driven Damper part (62) or one of the driven Dämpferterle (62) by a connection with the driven n friction member (61) or one of the driven friction parts (61) or a non-rotatably connected thereto part via a coupling spring (63) is driven or the detained damper! (58) or one of the retained damper parts (58) is held in place via a coupling spring (63) by connection to the retained friction member (60) or one of the retained friction members (60) or a member rotatably connected therewith; and cooperating control surfaces (65, 65); 66) depending on a by the braking force of the second braking device adjusting angular offset between the two by the coupling spring (63) connected parts adjust the contact pressure of the friction surfaces (14,15) of the friction pair or at least one of the friction pairings.
[10]
10. Device according to one of claims 1 to 9, characterized in that the device comprises an overload spring (32), which in the transmission path of the component to be damped (1) transmitted to the device, the device driving force is arranged.
[11]
11. Device according to one of claims 1 to 10, characterized in that the component to be damped (1) is a pull-out furniture part, which couples when inserted into a tentacle (5) of the device, which is about the axis (6) of the first braking device can be pivoted from a waiting position into a basic position and in this case the at least one driven friction surface (14) of the first brake device is rotated about the axis (6) of the first brake device.
[12]
12. The apparatus of claim 10 and 11, characterized in that the overload spring (32) in the transmission path between the catching arm (5) and the at least one driven friction surface (14) of the first braking device is arranged.
[13]
13. The apparatus of claim 11 or 12, characterized in that the tentacle (5) is acted upon by a pull-in spring (27), wherein the pull-in spring in the waiting position of the tentacle (5) is stretched more than in the basic position of the tentacle (5) and in the adjustment of the tentacle (5) from the basic 43 ···· position in the waiting position, a dead center of the intake spring (27) is overcome.
[14]
14. Device according to one of claims 1 to 13, characterized in that on the component to be damped (1) or on a part to be damped by the component (1) about an axis (6) pivotable part of the device, a driver (2) is arranged, the at least one slide track (3) and at the other of these two parts at least one projection (4) is arranged, which retracts during damping of the component (1) in the at least one slide track (3), wherein the slide track (3) has an inlet section ( 3a), over which the projection (4) is guided in a direction (69) which, with the direction of movement (44) of the component (1) opposite direction (68) forms an angle (a) of less than 45 °, and a continuation section (3b) which adjoins the inlet section (3a) and over which the projection (4) is guided in a direction (69) which forms an angle with the direction (68) opposite to the direction of movement (44) of the component (1) of more than 45 ° includes.
[15]
15. The apparatus according to claim 14, characterized in that the projection (4) at least over part of the inlet section (3a), which connects to the continuation section (3b) facing away from the beginning of the inlet section (3a), guided in one direction (69) is that with the direction of movement (44) of the component (1) opposite direction (68) forms an angle of less than 30 °, preferably less than 20 °

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同族专利:

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公开号 | 公开日

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EP2807394A1|2014-12-03|

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CN104081080A|2014-10-01|

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WO2013110101A1|2013-08-01|

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ES2589462T3|2016-11-14|

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PL2807394T3|2016-12-30|

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AT512306B1|2013-07-15|

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US20140339031A1|2014-11-20|

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CN104081080B|2016-10-12|

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US9945440B2|2018-04-17|

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EP2807394B1|2016-06-08|

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法律状态:
2018-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20180125 |

优先权:

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申请号 | 申请日 | 专利标题

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ATA84/2012A|AT512306B1|2012-01-25|2012-01-25|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|ATA84/2012A| AT512306B1|2012-01-25|2012-01-25|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|

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CN201280068190.XA| CN104081080B|2012-01-25|2012-12-13|For buffering the device of the motion of the parts of mobile-bearing|

---

PL12815610.6T| PL2807394T3|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|

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US14/374,087| US9945440B2|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|

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EP12815610.6A| EP2807394B1|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|

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PCT/AT2012/000316| WO2013110101A1|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|

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ES12815610.6T| ES2589462T3|2012-01-25|2012-12-13|Device for damping the movement of a component mounted in a mobile way|