• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A device for damping the movement of a movably mounted component (1) comprises a braking device having a driven damper surface (21) with a retained damper surface (22) includes a gap in which a viscous damping medium (23) is located upon rotation of the driven damper surface (21) with respect to the retained damper surface (22) causes a brake force of the brake device, the braking force depending on the rotational speed of the driven damper surface (21). The device further comprises an auxiliary brake device and a clutch in the closed position thereof Condition at least one by the movement of the component (1) about an axis (6) of the additional brake device driven additional damper surface (19) of the additional brake device against at least one detained additional damper surface (20) about the axis (6) Additional brake device rotates, with the additional Bremsvorri tion an additional braking force exerts, and in the open state, the additional brake device is inactive. The actuation of the clutch is effected by the braking force exerted by the braking device.
    公开号:AT512300A4
    申请号:T83/2012
    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:

    PatentanwälteHofmann Sc Fechner * * · ♦ ♦ ψ · φ; Dr; fSalfl5 <imapn. · · "; * Ä * 6806 Feldkirch, 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 24470/33 / ss 120119 1
    The invention relates to a device for damping the movement of a movably mounted component, comprising a braking device which has at least one damper surface driven by the movement of the component and at least one slit rotatable about an axis of the brake device, which includes at least one gap with at least one retained damper surface. in which a viscous damping medium is located, which causes the rotation of the at least one driven damper surface about its axis braking braking force of the braking device when rotating the at least one driven damper surface relative to the at least one damper surface, wherein the braking force exerted by the braking device of the rotational speed of depends at least one driven damper surface. 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 is different from the movement force ". I &lt; · 4 4 A4 4 «444 4 9 Vi · 4 4 4 4 4 · 44 ^ 44 4 4 4 44 444 speed of the component to be damped, so that a faster moving component is more strongly damped, which is desirable in many applications 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 19 938 626 A1, DE 201 16197 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 1 59 A2 disclose piston-cylinder units in which an air pressure difference forming between the two piston sides arises an 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 is difficult to adapt to different conditions. • I # ···································································
    Adapt applications. A linear damper is also limited to a limited operating distance or it must correspond to the dimensions of a linear damper of the desired operating distance.
    A device with two brake devices coupled together, which is designed as a vehicle shock absorber, it is apparent from DE 601 293 C. A flexibly formed loop part rubs against a friction flow. 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 telescopic mowing part and from the driver between a basic position and 4 4 4 4 4 4 4 44 4 44 444 4 4444 44 4 4 4 44 44 44 444 4 # 4.4 4 4 4 4 4 4 4 · £ 44 44 44 44 44 «is adjusted to a waiting position, which occupies the tilting slide 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 furniture parts are present, which should only be alternately extendable, for example, several superimposed drawers, so Ausziehsperrvorrichtungen be used also a central locking can be realized on 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 2 376 043 A there is shown an extraction locking device in which the operating parts are pivoted about axes parallel to the longitudinal extent of the locking bars and having 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 actuating parts are pivoted about axes which are parallel to the longitudinal extension of the... 4 *. 4 4 4 4 44
    4 4 4 4 4 4 4 4 4 I • * · | · · · · · · · · ·. ·· "·· 4 4 • · · · Κ * · · · 444
    Locking rods lie and have cooperating with the locking rods cams.
    The object of the invention is to provide a damping device of the type mentioned above, 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 the friction of the device to be overcome should be kept low. According to the invention, this is achieved by a device having the features of claim 1. 10
    In the device according to the invention, in addition to the braking device, in which a braking force can be exerted by a arranged in at least one gap viscous damping medium, an additional braking device is present, from which also a braking force can be exercised. In addition, the device comprises a coupling 15 for coupling and uncoupling the additional brake device. In the closed state of the clutch, at least one additional damper surface of the additional brake device which is rotatable about an axis of the additional brake device is driven about the axis of the additional brake device by the movement of the component. In this case, the additional brake device exerts an additional braking force. In the open state 20 of the clutch, the at least one additional damper surface is uncoupled from the movement of the component, that is not driven, and the additional brake device is inactive, so exerts no braking force on the component. The closing and opening of the clutch takes place as a function of the rotational speed of the at least one driven damper surface of the brake device about the axis of the brake device, the actuation of the clutch being effected automatically by the braking force exerted by the brake device. Conveniently, the clutch is open at a below-threshold rotational speed of the at least one driven damper surface and closed at a rotational speed above the threshold of the at least one driven damper surface. The rotational speed of the at least one driven damper surface depends on the speed or rotational speed of the movement of the movably mounted component, so that therefore the additional "44 44 4444 44 · 4 · 4 4 4 4 4 ··· 4 4 4 4 4 4 * 44 4 • * 4 * 4 44 444 4 4 ^ 4 4 4 4 4 4 4 44Q 44 44 4 * 4 444
    Braking device is switched on at higher speeds of movement of the component. It can thus be achieved at higher speeds, an increase in the total force exerted by the device braking force, which exceeds the speed-dependent increase in the braking force exerted by the braking device.
    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 friction can be achieved. Since the brake device and additional brake device are designed in the form of rotational dampers, it is optionally possible to achieve damping via a basically unlimited path.
    If the brake device comprises more than one driven damper surface, these are preferably all rotatable about the same axis (ie coaxial). If the additional brake device comprises more than one additional driven damper surface, these are preferably all rotatable about the same axis (ie coaxial).
    Advantageously, the axis of the brake device around which the at least one driven damper surface of the brake device is rotatable coincides with the axis of the additional brake device (= coincides therewith) about which the at least one driven auxiliary damper surface of the auxiliary brake device at least in closed state of the clutch is rotatable, ie the at least one driven damper surface of the brake device and the at least one driven additional damper surface of the additional brake device are thus rotatable about the same axis or coaxial. It is achieved by a simple, compact design.
    In an advantageous embodiment of the invention, the at least one driven additional damper surface of the additional brake device with at least one detained additional damper surface includes at least one gap in which a viscous damping medium is located, which upon rotation of the ·· »i *» » * * * »* * *» * At least one driven auxiliary damper surface opposite to the at least one retained auxiliary damper surface causes a brake force of the additional brake device to brake the rotation of the at least one driven additional damper surface about its axis. The braking force of the additional brake device thus depends on the rotational speed of the at least one driven additional damper surface.
    In another possible embodiment, the additional braking device could also be designed purely mechanically and have at least one friction pair in which a driven friction surface is rotatable about an axis of the additional brake device to generate a braking force against a friction surface resting against it. Conveniently, a speed dependency of the braking force exerted by the additional braking device could be effected by pressing the friction surfaces of at least one of the friction pairings more or less strongly in dependence on the braking force exerted by the braking device, that is, depending on the movement speed of the component. An advantage of such a mechanically acting braking device is that in a compact design, a high frictional force can be achieved.
    In an embodiment of the additional brake device with a arranged in at least one gap viscous damping medium, which causes a braking force, in contrast, there are advantages that occurs during mechanical braking wear due to friction and that operating noise that may occur in mechanical brakes (such as chattering or squeaking) can be avoided. In addition, the braking force of such an additional braking device is speed-dependent.
    A combination of a mechanically acting brake device with a brake device having a damping medium loaded in a gap and having a shear load could also be provided in principle. · Φ φφ φφφφ «φ« * t * φ φ ι φ φ · ♦ · * · * φ φ φ · · · * # # · φ φφφ φ φφφφφφφ φ # φ · φ φφ φφ φ φφ φφφ
    The viscosity of the viscous damping medium arranged in at least one gap of the brake device and optionally in at least one gap of the additional brake 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 being particularly are 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 of the braking device and optionally the additional braking device is arranged, is advantageously in the range of 0.1mm to 0.5mm, i. the damping medium has such a layer thickness.
    The damping force is caused by the arranged in at least one gap of the brake device and optionally in at least one gap of the additional braking device damping medium which advantageously completely fills the gap or respective gap, characterized in that this is loaded on shear. The damping medium having gap or these gaps preferably extend annularly around the axis of the braking device.
    For retaining the damping medium in the gap or in the respective gap of the braking device and optionally the additional braking device can, if any, relatively simple seals are used. For non-flowable greases, gaskets may be omitted altogether. For 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 coupling comprises a flexible, preferably elastically bendable, trained wrap-around part. The loop part surrounds a coupling 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 wrapping part extends over at most 500 °, more preferably over less than 360 ° around the Ankuppelteil around. The ·· 4 «Μ« «· * Μ • · · · · · ·« ««
    Umschlingungsteil is directly or indirectly connected to a damper sleeve of the brake device having at least one of the damper surfaces of the brake device. When the rotational speed of the at least one driven damper surface of the brake device is above the threshold value, the rotationally fixed connection of the belt part to the coupling part occurs, while at a rotational speed below the threshold of the at least one driven damper surface of the brake device, the two parts are rotatable relative to one another Conveniently, the axis about which the loop part and the coupling part in the opened state of the coupling are mutually rotatable coincides with the axis of the brake device and / or with the axis of the additional brake device.
    The non-rotatable connection between the loop part and the Ankuppelteil in the closed state of the coupling can be done by friction and / or positive engagement. 20
    For automatically closing and opening the clutch, a rear end of the strap member is conveniently connected directly or indirectly to the damper sleeve, which transmits a braking force caused by the brake device to the strap member, the damper sleeve surrounding an inner brake member and 25 the damper sleeve and the inner brake member against each other are rotatable. The term "rear end" refers to the relative movement between the strap member and the inner brake member or between the strap member and the Ankuppelteil in the open state of the clutch. In this case, either the belt part can be driven by the component to be damped and rotate in a direction of rotation with respect to the fixed inside brake part or the coupling part fixed in the opened state of the clutch, or the inner brake part can be driven and move in relation to the belt part. 44 4 ·· »9 * 9 • · 4 9 t 9 # 4 4 # 4 444444 444 4 4 44 4 * 4 4 444 4 4 4 4 4 4 4 4 4 4 ** ΙΓ) ·· ** · 44 444 rotate in an opposite direction of rotation, wherein in the open state of the coupling, the Ankuppelteil rotates with the inner brake member.
    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 linearly mounted furniture part, 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, in which a cascade-like connection of at least one additional braking device takes place in dependence on the braking force exerted by the braking device, 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:
    Figure 1 is an oblique view of devices according to the invention according to an advantageous embodiment in use for damping the insertion movement of extendable furniture parts.
    Fig. 2 is an oblique view of one of the devices of Figure 1, in the retracted in the extended state of the extendable furniture part waiting position of the tentacle, with a mounting rail. * Μ Μ * ··· Μ Φ • t · Φ Φ I φ Φ · Φ Φ Φ Φ Φ Φ Φ Φ Φ Φ • i t. · Ψ m * ·· φ t ··· φ ·· # φ φφ · φ φ φφ φφφ
    Fig. 3 is an oblique view corresponding to Figure 2 in the state which is present in the retracted state of the extendable furniture part.
    Fig. 4 is an oblique view corresponding to Figure 3 but from a different angle.
    5 shows a view of the device attached to the rail, with the tentacle in the waiting position;
    Fig. 5a is a view corresponding to Figure 5, but in the longitudinal center section of the device.
    Fig. 6 is a section along the line AA of Fig. 5 and 5a;
    Fig. 7 and 8 sections corresponding to Figure 6, but in an intermediate position and in the retracted state of the extendable furniture part occupied basic position of the tentacle;
    FIG. 9 shows a section along the line BB of FIG. 5 or 5a; FIG.
    Fig. 10 is an exploded view;
    Figure 11 is an oblique view of the cut in a plane parallel to the axis and through the axis section device.
    12 is an illustration for explaining the retraction movement of the tentacle of the device in the slot of the driver.
    Figure 13 is a slightly modified embodiment of the device with additional elements for forming a Ausziehsperrvorrichtung.
    Fig. 14 is an exploded view of the locking bars with the attached cam follower parts and the intermediate actuating part of this modified embodiment.
    A first embodiment of a device according to the invention is shown in FIGS. 1 to 12. 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, the device can be used in an analogous manner.
    In the device here a pull-in spring 27 is integrated, in addition to the damping to provide a self-closing for the pull-out furniture part over the last part of the Einfahrweges. A catch spring could basically be omitted.
    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 interact with the slide tracks 3. 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 at least one projection on the driver is provided. The at least one projection 4 could also be formed in the form of a pin.
    In the retracted state of the pull-out furniture part (cf., the three lower drawers in Fig. 1 and Figs. 3, 4 and 8) of the tentacle 5 assumes its basic position. When pulling out the pull-out furniture part in the pull-out 68 of the tentacle 5 is pivoted about the axis 6 until it assumes its waiting position (see, the upper drawer jade in Fig. 1 and Figs. 2, 5, 6 and 9). 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 tentacle 5, whereupon the tentacle 5 rotates back about the axis 6 until he resumes the basic position and fully pushed the extendable furniture part is.
    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. For example, a substantially V-shaped recess could be provided, into which a projection runs in order to move the catch arm from the catch 2 between its
    Position and his basic position and back to create. Different types of possible driving connections are known, for example, from conventional pull-out furniture parts with Selbsteinzüge (= Einziehmechaniken) ago.
    In the coupled state of the tentacle 5 with the driver 2 there is a positive connection between these two parts in the direction of movement 44 and the opposite pull-out direction.
    The inner brake member 10 and a mounted on this housing part 28 are rotatably connected to the mounting rail 29, which in turn is attached to the furniture body 30. The attachment to the mounting rail 29 is preferably carried out by latching projections of the inner brake member 10 and the housing part 28, which engage in recesses in the mounting rail 29. An attachment of the device directly to the furniture body 30 is conceivable and possible.
    The inner Bremstei! 10 and formed by the housing part 28 unit preferably has an axially completely passing through this inner cavity {see FIG. Fig. 10). This can accommodate parts of a Ausziehsperrvorrichtung, as will be described below with reference to FIGS. 13 and 14.
    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 about the axis 6 upon rotation of the tentacle 5 about the axis 6 in the direction of F * 26. The wrap-around part 31 is formed in the embodiment of a band and extends around a major part of the circumference of the inner brake member 10 and a coupling member 11 disposed thereon about the inner brake member 10 and the Ankuppelteil 11 around. The loop part 31 and the coupling part 11 form parts of a coupling whose function will be described below. The inner (= the axis 6 facing) surface of the Umschlin- • I «14 ♦ · Φ ♦ ♦ • ♦ # · ·« · · · · «♦ ♦ · · ···· 1 · + · · · · · · 31 forms a first coupling surface 14, which cooperates in the closed state of the coupling with the outer (= away from the axis 6) surface of the coupling part 11, which forms a second coupling surface 15.
    The connection of the tentacle 5 with the belt portion 31 via an overload spring 32, the function will be explained below. The overload spring 32 is integrally formed in the embodiment shown with the wrap member 31 and is formed by an arcuate or loop-shaped portion of both the wrap member 31 and the overload spring 32 forming band. The geometry of this arcuate or looped course and the elasticity of this portion of the band are designed so that a spring element with the desired spring characteristic results In modified embodiments, the overload spring 32 can also be formed by a separate part, in the transmission path between the tentacle 5 and the at least one driven additional damper surface 19 of the additional brake device is arranged. Instead of or in addition, an overload spring could also be arranged at a different location in the transmission path of the force to be damped component transmitted to the device and the Vor-direction driving force, for example, between the inner brake member 10 and the mounting rail 29. In others 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. In this case, in the embodiment shown, an axial projection of the loop part 31, which has a slot 35, is inserted into a recess in the region of the lower side of a radial projection 36 of the damper sleeve 18, as shown in FIG. * · • 4
    The web arranged in the recess (the recess of the radial projection 36 and the web arranged therein are not visible in FIG. 10).
    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 Ankuppelteil 11. 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 coupling part 11.
    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 bow or loop-shaped course and the elasticity of this section of the band are adapted to a desired spring characteristic. The function of the hold-open spring 25, which, when dampening the movement of the component 1, is the rear connection point of the belt part with respect to 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 around) Axis 6 extends) is described below.
    The hold-open spring 25 could also be formed by a separate part or possibly omitted.
    The overload spring 32 is much harder, preferably more than 10 times harder than the hold-open spring 25. 16 »»: ι
    * * * * * Ι
    4 4 * • ·: • * 4
    The damper sleeve 18 surrounds a portion of the inner brake member 10. The inner brake member 10 opposite surface of the damper sleeve 18 forms a driven damper surface 21. The damper sleeve 18 opposite outer surface of the inner brake member 10 forms a recorded damper surface 22. Between the driven damper surface 21 and the retained damper surface 22 is an annular gap in which a viscous damping medium 23 is arranged. Sealing rings 41, 42 define the gap at both of its ends, so that a sealed space is formed. 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 brake device thus comprises the damper sleeve 18, the inner brake member 10 and the damping medium 23rd
    The annular coupling part 11 surrounds a portion of the inner brake member 10. The inner, the inner brake member 10 opposite surface of the Ankuppelteils 11 forms a driven additional damper surface 19 in the closed state of the clutch. The Ankuppelteil 11 opposite outer surface of the inner brake member 10 forms a retained auxiliary damper surface 20. Between the driven additional damper surface 19 and the held additional damper surface 20 is an annular gap in which a viscous damping medium 23 is arranged. Sealing rings 39, 40 define the gap at both ends, so that a sealed space is formed. As a damping medium, therefore, a flowable oil can be set. The use of a non-flowable fat is also possible. The sealing rings 39, 40 could then be omitted.
    The additional brake device thus comprises the Ankuppelteil 11, the inner brake member 10 and the damping medium 23. 17 17
    • · · ♦ · · · φ «· · · · · ·
    By rotating 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 about the axis 6. The axis 6 forms both the axis of rotation of the brake device 5 and the axis of rotation of the additional brake device. Depending on the speed of rotation of the damper sleeve 18 about the axis 6, the braking device exerts a more or less large braking force, whereby a more or less large tensile force acts between the front joint 33 and the rear connection point 34 of the wrap 31. 10
    In the rest state of the device, the first coupling surface 14 of the wrap-around part 31 at least in sections at a distance from the second coupling surface 15 of the Ankuppelteils 11. Preferably, because of its preforming at rest, the wrap-around portion 31 has at least substantially the entire course of its dome area 14, i. at least over 90% of its extent in the
    Circumferential direction, a distance from the coupling surface 15 of the inner brake member 10.
    Due to the elasticity of the loop part 31 and / or the preferably present 20 hold open spring 25, the coupling surface 14 of the wrap 31 is then up to a threshold speed of the component 1 or a threshold value of the rotational speed of the tentacle 5 of the dome surface 15 of the inner brake member 10th spaced (at least in sections) and the clutch is open, ie the rotational movement of the wrap 31 is not transferred to the Ankuppelteil 11. The additional brake device is thus inactive, so does not exert any braking force.
    Only when the threshold is exceeded, the clutch closes by the braking force exerted by the braking device by the wrap member 30 31 is applied to the Ankuppelteil 11 such that a driving connection is formed, i. During a rotation of the Umschiingungs-part 31 about the axis 6, the Ankuppelteil 11 is also rotated by the Umschlingungsteil 31 about the axis 6. The driving connection is frictionally formed in the embodiment. Positive locking cooperating elements could be provided instead or in addition. In the closed state of the clutch, the additional brake device is active, thus exerts a braking force. In the exemplary embodiment in which the additional brake device has the viscous damping medium 23 arranged in the at least one gap, the braking force exerted by the additional brake device is speed-dependent.
    In order to achieve an appropriate increase in the total braking force when the auxiliary brake device is engaged by closing the clutch, the braking force exerted by the additional brake device is favorably at least one third of the braking force exerted by the brake device, preferably the braking force exerted by the auxiliary brake device greater than the brake force exerted by the braking device, more preferably more than twice as large. For the sizes of the braking force of the brake device and the braking force of the additional brake device desired values can be achieved by selecting appropriate lengths and / or widths for the column filled with the damping medium and / or damping media having different viscosities.
    At a high speed, with which the component 1 impinges on the catching arm 5, it would come without the overload spring 32 to a suddenly occurring high braking force of the device, whereby undesirable high loads and an undesirably strong braking of the component 1 would be the result. By the overload spring 32, the peak of the braking force is cushioned by the catching arm 5 can rotate relative to the loop member 31 under deformation of the overload spring 32.
    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 catching arm 5, starting from its basic position in the direction of its waiting position, the pull-in spring 27 is initially tensioned, cf. Fig. 8 and Fig. 7. Shortly before reaching the waiting position, a dead center is crossed (this is the position shown in Fig. 7), as a result, the catch spring is a little relaxed again until reaching the holding position shown in Fig. 6 ( preferably less than one fifth of the previous compression stroke).
    If, when inserting the pull-out furniture part of the driver 2 accumulates on the tentacle 5, so these two parts couple together and the driver 2 pivots the tentacle 5 over its dead center. As a result, the extendable furniture part is retracted by the tentacle 5 by the force of the pull-in spring 27 until the basic position of the tentacle shown in Fig. 8 is reached. The further pivoting is limited in the waiting position and the basic position by corresponding stops (in the normal 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, possibly after damping the initially faster speed when starting against the tentacle, is relatively low, so that the clutch is opened, in this case only the braking force of the braking device is to overcome, while the additional braking device is inactive. 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 to the housing part 28 at different distances from the axis 6, for example by providing a plurality of latching arms 43, the strength of the pull-in force can be determined by different feedforward φΦ φφφφ ♦ · φφ φφ • φ φ * * »» t ···························································································································································································································································································· 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. For example, a leg spring could be used, one leg of which is connected to the catching arm 5 and the other leg is connected to the housing part 28. For example, a bent leaf spring could also be provided, which optionally has a greater width in a middle region than in the end-side attachment regions and can also run 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. 12. The curved extending link track 3 (the course of both slide tracks 3 is identical) has an inlet section 3 a, at the beginning of the projection 4 from outside of the slide track 3 enters the slide track 3. Via the inlet section 3 a, the slide track 3 guides the projection 4 in a direction 69 which encloses an angle α of less than 30 ° with the direction of withdrawal 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 °. By way of the continuation section 3b, this angle α continues to increase until, in any case, it is more than 45 °, in the embodiment shown between 80 ° and 90 °. In Fig. 12, the angle α is plotted for a position of the projection 4 within the continuation portion 3b, in which the angle α is slightly more than 45 °. «4 * 4 44 444« «4 4 4 * 4 4« 4 «4 4 44 4 44 44 4 # 44 4 ··· 4 4 4 4 444 4 444444« «4 21 ** 4« «4 4 44 444
    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. 12, three positions of the projection 4 when entering the slide track 3 are shown by 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 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.
    As a result of the described curved course of the at least one slide track 3, the force required to actuate the catching arm 5 can be increased during the insertion of the ♦ ♦ · · # # # · · · · · · · · · ·. · • • • • • • • * * • t ·· • · · · · ··
    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.
    From Fig. 12 is further 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 extends at least substantially (i.e., a deviation of less than 15 °) parallel to the withdrawal direction 68. The self-healing portions 3c are widened towards their open ends by lead-in slopes. In order to allow retraction of the projections 4 by the self-healing portions 3c, but the projections 4 can not leak from the continuation portions 3b through the self-healing portions 3c, the elasticities of the components can be utilized (so that the projection 4 as shown in FIG in the retracted state of the component 1 offset from the self-healing section 3c is). For example, it would also be possible to drive over the steps when retracting the projections 4 through the self-healing sections 3c, wherein the side cheeks 2a, 2b having the slide tracks 3 are pushed apart from one another. Additionally or instead could be provided on the driver 2 arranged, additional resilient locking elements.
    When turning back the tentacle 5 in the opposite direction of the arrow 26 is rotated by the tentacle 5 on the Offenhaitefeder 25, the damper sleeve 18 so that the force to be overcome in this case is exercised. This force is comparatively low because the additional brake device is not effective in this direction of rotation. However, if it is not desired to apply such a force, a part connected to the loop part 31, possibly via the open-end spring 25 and / or the overload spring 32, and the catch arm 5 can be used · · · · 4 · I ft · 4 ·· II * # * * «ft * ft * ft * ft * ft ftftftft ftftftft # ft ft ft 2 ft ft ft ft # # "·
    Freewheel be provided, which is closed in the direction opposite to the arrow 26 direction of rotation and opens in the opposite direction of rotation. Such freewheel are known, also in connection with dampers. In an embodiment modified from the illustrated embodiment, the catching arm 5 could also be pivotably mounted on the damper sleeve 18, namely about an axis of rotation parallel to the axis 6. 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 damping the movement of the component 1, when the tentacle arm 5 is more or less pivoted against the force of the return spring acting on it about the pivot axis, since the rotation of the pivot axis about the axis 6 is braked by the braking force of the braking device is on the Umschlingungsteil 31 exerted a more or less large tensile force, whereby at a sufficiently high rotational speed of the damper sleeve 18, the clutch is closed.
    Other linearly displaceably mounted components as extendable furniture parts can be damped by the braking device. Furthermore, a damping of rotatably mounted components is possible, depending on the application, a collection spring 27 may be provided or may be omitted. A connection of the component to be damped to the device may optionally also take place in a different way than via a rotatably mounted about the axis 6, radially projecting catch arm (= catch lever), for example via a rotatably mounted about the axis 6 pinion, which with the wrap 31st , optionally connected via an overload spring 32.
    The Umschiingungsteil 31 may be formed instead of a band of a wire, in particular spring wire, or a string. The wrap angle of the wire or cord is favorably between 250 ° and 720 °. * · «# Fr fr fr fr» »» »» »» »» »» »» »» »» »• • •. ♦♦ * · · ά.Η tt # · «· ♦ ··« · #
    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 damper surface 21 described above and shown in the drawing then becomes the retained damper surface and vice versa. The previously described and shown in the drawing driven additional damper surface 19 is then fixed to the additional damper surface and vice versa. Here, the driven additional damper surface is independent of whether the clutch is closed or opened, driven by the movement of the component, while the detained additional damper surface is held only in the closed state of the clutch (and in the open state of the clutch with the driven Additional damper surface rotates). 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. 13 and 14 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. 1 to 12.
    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. Further, if desired, a central locking can be provided via such a pull-out locking device.
    In the embodiment of the Ausziehsperrvorrichtung shown in the embodiment extend between actuators, which are assigned to the individual extendable furniture parts, locking rods, the limited space (= a limited ** * * 4 * * ··· · «· * · ·« · · · ·
    • * * «« «« I 25 * * ft ft ft ft ······· * * · * · Φ ft ft ·
    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 cavity 46 extending in the direction of the axis 6 and passing completely through 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, the actuating part 47 moves an upper locking bar 48 upwards and / or a lower locking bar 49 downwards. 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. To the lock actuated by the actuation part 47 ·······················································································. ·· • *
    Rods 48, 49 are each a cam follower part 50, 51 mounted with cam follower parts 50, 51 are 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 operating 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.
    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 prior to assembly of the device, wherein after assembly, the required range of motion is maintained.
    The operation of the locking rods 48, 49 could also be done in other ways. For example, the actuating part could be in the form of a cam part, 27.
    Φ ··· «· 4 M« I »· ♦ *» * »I · * · Μ ·· φ φ | ΦΦΦ which is pivotable about a pivot axis perpendicular to the axis 6. The actuating member cooperates with the end of the at least one adjacent locking bar 48, 49 or a part connected to this locking rod, in order to displace the locking bar 48, 49 in its respective direction parallel to the axis 6 during its pivoting about the pivot axis. The actuating part is in this case coupled to the catching arm 5 in such a way (for example via a fork-shaped driver part and a pin) that it is pivoted about the axis 6 during the rotation of the catching arm 5.
    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
    In the embodiments described above, the axis of the brake device coincides with the axis of the additional brake device, 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 brake device and the additional brake device then appropriate transmission elements would be provided, for example gears. The clutch would then preferably be formed coaxially with the brake device or with the additional brake device. 28 ····································································································. • * * * • • «ft ft ft ft ft *
    Key to the reference numbers: 1 component 32 overload spring 2 driver 33 front connection point 3 slide track 35 34 rear connection point 3a inlet section 35 slot 3b continuation section 36 projection 3c self-healing section 39 sealing ring 4 projection 40 sealing ring 5 catching arm 40 41 sealing ring 6 axis 42 sealing ring 10 inner brake part 43 Latch arm 11 Coupling part 44 Direction of movement 14 First coupling surface 45 Side wall 15 Second coupling surface 45 46 Cavity 18 Damper sleeve 47 Actuating member 19 Driven auxiliary 47a Actuating arm Damper surface 48 Locking rod 20 Retained additional locking bar Damper surface 50 50 Cam follower 21 Driven damper surface 50a Extension 22 Damper surface 50b retained Catching tongue 23 Damping medium 51 Cam follower part 25 Holding-open spring 51a Extension 26 Arrow 55 51b Catching tongue 27 Retraction spring 52 Claw 28 Housing part 53 Recess 29 Mounting rail 68 Pull-out Direction 30 Furniture carcass 69 Direction 31 Loop part 60
    权利要求:
    Claims (14)
    [1]
    Patent Attorneys: :: :: Hofmann Sc Fechftgf ·· &quot; Dr »RaIf * Hc5ma * n · • · · · · ßr Tlfimas F ^ Shn ^ J 6806 Feldkirch, Austria Egelseestr 65a, PO Box 61 T +43 (0) 5522 73 137 F +43 (0) 5522 73 359 M office@vpat.at I www.vpat.at 24470/33 / ss 1. A device for damping the movement of a movably mounted component (1), comprising a braking device which weds at least one damper surface (21) which is rotatable about an axis (6) of the braking device and is driven by the movement of the component (1), with at least one retained damper surface (22) including 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 retained damper surface (22) rotation of at least a braking damper surface (21) causing braking force of the braking device about its axis (6), the braking force exerted by the braking device being at least the rotational speed of the braking device s a driven damper surface (21), characterized in that the device comprises an additional braking device and a clutch, in its closed state at least one by the movement of the component (1) about an axis (6) of the additional brake device driven addition Damper surface (19) of the auxiliary brake device rotates relative to at least one retained additional damper surface (20) about the axis (6) of the additional brake device, wherein the additional brake device exerts an additional braking force, and in the open state, the addition -Bremsvorrichtung is inactive, wherein the actuation of the clutch is effected by the braking force exerted by the braking device.
    [2]
    2. Apparatus according to claim 1, characterized in that the clutch is open at a below a threshold rotational speed of the at least one driven damper surface (21) and closed at a rotational speed above the threshold of the at least one driven damper surface (21). , 3Q
    [3]
    3. Apparatus according to claim 1 or 2, characterized in that the at least one driven damper surface (21) and the at least one driven in the closed state of the clutch additional damper surface (19) are coaxial. 10 15 Device according to one of claims 1 to 3, characterized in that the at least one driven additional damper surface (19) with at least one detained additional damper surface (20) includes at least one gap in which a viscous damping medium (23) is located in that, upon rotation of the at least one driven additional damper surface (19) relative to the at least one retained auxiliary damper surface (20), a braking force of the additional brake device which brakes the rotation of the at least one driven additional damper surface (19) about its axis (6) causes, wherein the braking force of the auxiliary brake device on the rotational speed of the at least one specified additional damper surface (19) depends. 20 25
    [4]
    5. Device according to one of claims 2 to 4, characterized in that the coupling has a flexibly formed Umschlingungsteil (31), which a Ankuppelteil (11) at least by more than 90 °, preferably at least 180 °, amounting angle about an axis (6) of the clutch surrounds, wherein the Umschlingungsteil (31) is connected to a damper sleeve (18) having at least one of the damper surfaces (21,22) of the braking device and wherein the Umschlingungsteil (31) and the Ankuppelteil (11) at a below the threshold rotational speed of the at least one driven damper surface (21) are rotated against each other and at a rotational speed above the threshold of the at least one driven damper surface (21) are rotatably connected to each other.
    [5]
    6. The device according to claim 5, characterized in that the wrap-around part (31) from the front connection point (33) to the rear connection 30 31 '♦ »♦ · ♦ +» »· • · i * · · ♦ * ♦ · ······························································· (34) extends in a first rotational direction about the axis (6 31) is connected to the damper sleeve (18) and that the transmission of the movement of the component to be damped (1) on the front connection point (33) of the Um-5 schlingungsteils (31), wherein the Ankuppelteil (11) in the closed state the clutch driven auxiliary damper surface (19) or at least one of the driven additional damper surfaces (19) and a cooperating with this held damper surface on a detained inner brake member (10) is arranged, or the transmission of the movement of the damping to 10 B. Autuns (1) on the inner brake member (10), wherein the inner brake member (10) has the driven additional damper surface or at least one of the driven additional damper surfaces which held with the on Ankuppelteil (11) held in the closed state of the clutch Additional damper surface cooperates, and the strap member (31) at the front 15 connection point (33) is held.
    [6]
    7. Apparatus according to claim 5 or 6, characterized in that the axis (6) of the coupling with the axis (6) of the braking device and / or coincides with the axis (6) of the additional brake device. 20
    [7]
    8. The device according to claim 7, characterized in that a Offenhaltefe- (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 wrap member (31) opposite the front connection point of the wrapper (31) in a first direction of rotation opposite to the second direction of rotation about the axis (6) of the first braking device acted upon.
    [8]
    9. Device according to one of claims 5 to 8, characterized in that the damper sleeve (18) has the driven damper surface (21) or at least one of the driven damper surfaces ne (21) and the drive of the specified damper surface (21) or at least one of the driven damper surfaces (21) via the looped part takes place and that the Ankuppelteil (11) or a part rotated by this the driven in the closed state of the clutch additional damper surface or at least one of the closed state of the clutch driven additional damper surfaces (21) having.
    [9]
    10. Device according to one of claims 5 to 9, characterized in that the looping part (31) at a rotational speed above the threshold of the at least one driven damper surface (21) is frictionally connected to the Ankuppelteil (11).
    [10]
    11. Device according to one of claims 1 to 10, 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]
    12. The device according to claim 11, characterized in that the overload spring (32) is arranged in the transmission path between the component (1) and the wrap-around part (31).
    [12]
    13. Device according to one of claims 1 to 12, 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 preferably about an axis (6) coincident with the axis (6) of the braking device and / or the axis (6) of the additional braking device is pivotable from a waiting position to a basic position and in this case the at least one driven damper surface (21) of the braking device is rotated about the axis (6) of the braking device ,
    [13]
    14. The apparatus according to claim 13, characterized in that the catching arm (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 at the adjustment of the tentacle (5) from the basic position to the waiting position a dead center of the intake spring (27) is overcome.
    [14]
    15. Device according to one of claims 1 to 14, characterized in that on the component to be damped (1) or on one of the component to be damped (1) about an axis (6) pivotable part of the device, a driver (2) ange-5 is arranged, which has at least one slide track (3) and at the other of these two parts at least one projection (4) is arranged, which retracts when damping the component (1) in the at least one slide track (3), wherein the slide track (3) an inlet section (3a) over which the projection (4) is guided in a direction (69) which, with the direction (68) of the component (1) 10 opposite the direction of movement (44), has an angle (a) of less than 45 ° includes, and a subsequent to the inlet portion (3a) continuation portion (3b) over which the projection (4) in a direction (69) is guided, with the direction of movement (44) of the component (1) opposite direction (68) an angle of more than a ls 45 °. 15
    类似技术:
    公开号 | 公开日 | 专利标题
    EP2807320B1|2018-02-21|Pull-out device for at least two pull-out furniture parts
    AT509923B1|2013-12-15|FEEDING DEVICE FOR PULLING A MOVABLE FURNITURE PART
    AT512415B1|2013-08-15|Catching device for a movably mounted furniture part
    DE112009001940T5|2011-06-16|Synchronization / stabilization system and self-moving mechanism for drawer applications
    AT506903B1|2013-09-15|DAMPING DEVICE FOR FURNITURE OR FURNITURE FITTINGS
    DE19717937A1|1998-05-20|Braking and damping element for moving furniture parts
    DE20306195U1|2004-08-26|Damping device for movable furniture parts
    EP2807395B1|2016-03-23|Device for damping the movement of a movably mounted component
    EP2807394B1|2016-06-08|Device for damping the movement of a movably mounted component
    AT512299B1|2013-07-15|FEEDING DEVICE FOR AT LEAST TWO EXTENDABLE FURNITURE PARTS
    EP2000691B1|2009-12-09|Disengaging device
    DE102007059575A1|2009-06-18|Damping and moving device for sliding element i.e. sliding door, has damping cylinders arranged one above other, where tension springs and damping cylinders are arranged in series connection with one behind other
    EP2806769B1|2015-10-07|Pull-in system for multiple pull-out furniture parts
    DE10100014B4|2006-09-21|Steaming and braking device for furniture parts
    DE10343928B3|2004-11-11|Ventilator spring for opening a flap, especially a trunk lid of a motor vehicle, comprises a propeller spring with both ends formed as hooks which interact in corresponding receivers on the free end of a piston rod
    EP1785061A1|2007-05-16|Detachable coupling for linear power transmission, in particular for drawer rails
    DE102010029579A1|2011-12-01|Refrigerating appliance with a door adjusting device
    DE4107041C2|1993-02-11|
    DE202011106253U1|2013-01-07|Door unit, in particular motor vehicle door unit
    EP2910283B1|2018-06-06|Fire protection flap
    EP2781864B1|2020-06-24|Refrigeration and/or freezer device
    DE1650387C|1971-05-27|Program valve actuated by counted pressure pulses
    DE202006001668U1|2006-04-06|Damping device for movable parts, especially doors, flaps, or drawers, has compression chambers of cylinders interconnected, and stop acting in extension direction is provided on spring piston for main piston
    同族专利:
    公开号 | 公开日
    EP2807395B1|2016-03-23|
    CN104067023A|2014-09-24|
    CN104067023B|2017-10-17|
    AT512300B1|2013-07-15|
    PL2807395T3|2016-09-30|
    EP2807395A1|2014-12-03|
    US20140353096A1|2014-12-04|
    WO2013110100A1|2013-08-01|
    US9777789B2|2017-10-03|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE20021956U1|2000-12-23|2001-03-15|Schwarz Verbindungs Sys Gmbh|Spring-loaded hinge and damping arrangement, in particular for a spring-loaded hinge|
    DE102005056132A1|2004-11-30|2006-06-22|Nifco Inc., Yokohama|rotary damper|
    WO2009140706A1|2008-05-19|2009-11-26|Julius Blum Gmbh|Damping device for furniture components or furniture fitting components|
    BE400181A|1933-01-03|
    DE654017C|1935-12-17|1937-12-08|Ardeltwerke G M B H|Shock absorbers|
    US2653043A|1951-03-19|1953-09-22|Boyd N Carlson|Door closer|
    GB1117071A|1966-02-21|1968-06-12|G K N Sankey Proprietary Ltd|Improvements in or relating to drawers and cabinet assemblies|
    DE2911772A1|1978-03-30|1979-10-04|Blum Gmbh Julius|Extending drawer guide rail system - has rotatable tilt segment interacting with rail on chassis for precise control of rails |
    JPS6243153Y2|1980-06-16|1987-11-09|
    JPH0532606B2|1983-06-01|1993-05-17|Nifco Inc|
    JPS6124850A|1984-07-16|1986-02-03|Nifco Inc|One way damper|
    DE3431386C2|1984-08-25|1989-09-14|Fa. Anton Kessel, 7945 Andelfingen, De|
    US4603239A|1985-07-05|1986-07-29|M-S Cash Drawer|Cash drawer assembly having a compulsory switch activating drawer latch|
    US4732434A|1986-09-29|1988-03-22|Metalworks, Inc.|Horizontal file drawer interlock assembly|
    JPS63171736U|1987-04-30|1988-11-08|
    JPH01266331A|1988-04-14|1989-10-24|Aisin Chem Co Ltd|Damper|
    AT393948B|1989-04-03|1992-01-10|Blum Gmbh Julius|LOCKING DEVICE FOR DRAWERS|
    JPH057005B2|1990-05-23|1993-01-27|Sugatsune Kogyo|
    AT401334B|1990-07-31|1996-08-26|Blum Gmbh Julius|LOCKING DEVICE FOR DRAWERS|
    DE9012423U1|1990-08-30|1990-10-31|Gebr. Willach Gmbh Fabrik Fuer Beschlag-Technik, 5207 Ruppichteroth, De|
    DE9013161U1|1990-09-17|1990-11-22|Paul Hettich Gmbh & Co, 4983 Kirchlengern, De|
    JPH04321825A|1991-04-23|1992-11-11|Mita Ind Co Ltd|Shock absorber|
    KR100251977B1|1991-10-29|2000-04-15|구로이시 이쿠오|Foot-operated parking brakes for cars and one-way dampers for use therein|
    US5303994A|1992-06-05|1994-04-19|Steelcase Inc.|Drawer interlock|
    US5277282A|1992-10-20|1994-01-11|Kato Hatsujo Kaisha, Ltd.|Rotary oil damper|
    DE9311534U1|1993-08-02|1993-12-09|Romagnoni Mauro|Pull-out lock for furniture pull-outs|
    DE4325920C2|1993-08-02|1997-12-18|Mauro Romagnoni|Pull-out lock for pull-outs|
    DE4427026C2|1994-02-03|1996-04-18|Porte Soehne D La|Drawer locking device|
    JP3304188B2|1994-02-23|2002-07-22|株式会社ニフコ|One-way rotary damper|
    JP3292790B2|1995-04-26|2002-06-17|株式会社ニフコ|Variable speed rotary damper|
    GB2302906B|1995-06-30|1999-07-07|Maine Engineering Limited|Interlock meachanism for slidable units|
    DE29518173U1|1995-11-16|1996-01-11|Itw Ateco Gmbh|Device for damping the movement of a movably mounted component, in particular a flap in an automobile or the like.|
    DE29622864U1|1995-11-23|1997-09-04|Lautenschlaeger Mepla Werke|Underfloor pull-out guide for drawers etc.|
    DE19634581A1|1996-07-05|1998-01-08|Lautenschlaeger Mepla Werke|Flush-mounted guide rail for drawer|
    DE19717937A1|1996-11-08|1998-05-20|Grass Ag|Braking and damping element for moving furniture parts|
    DE29620152U1|1996-11-20|1997-04-03|Hekna Hermann Knapp Gmbh & Co|Central locking for furniture|
    AT406181B|1998-02-09|2000-03-27|Blum Gmbh Julius|FASTENING DEVICE FOR FASTENING SEVERAL FURNITURE FITTINGS ON ONE FURNITURE PART|
    EP0951848A1|1998-03-27|1999-10-27|Julius Blum Gesellschaft m.b.H.|Catch device for a door wing or a drawer|
    US6095262A|1998-08-31|2000-08-01|Halliburton Energy Services, Inc.|Roller-cone bits, systems, drilling methods, and design methods with optimization of tooth orientation|
    DE19938626A1|1999-08-14|2001-07-19|Bruno Gruber|Collision impact damping device, with movement device to receive impact movement to be damped|
    JP3900767B2|1999-12-22|2007-04-04|三菱自動車工業株式会社|Automotive pedal equipment|
    JP4524771B2|2001-01-26|2010-08-18|株式会社ニフコ|Rotating damper and assist grip device|
    DE20107426U1|2001-04-30|2001-08-30|Zimmer Guenther Stephan|Brake controller with air or liquid damping, in particular for damping the end position of drawers, doors or the like. Facilities|
    ES2238516T3|2001-05-17|2005-09-01|Julius Blum Gmbh|SHOCK ABSORBER, ESPECIALLY FOR FURNITURE.|
    US6568771B2|2001-06-01|2003-05-27|Tk Canada Limited|Drawer interlock|
    DE20116197U1|2001-10-02|2003-02-13|Lautenschlaeger Mepla Werke|Furniture hinge for e.g. cupboard doors, has friction damper as damping device|
    DE20202520U1|2002-02-18|2002-06-13|Anton Schneider Gmbh & Co|Self-closing for drawers or the like.|
    DE10206854C1|2002-02-18|2003-08-21|Huwil Werke Gmbh|Pull-out lock for drawers arranged one above the other|
    DE10210917C1|2002-03-13|2003-11-13|Itw Automotive Prod Gmbh & Co|Braking device with freewheel|
    DE10213726B4|2002-03-26|2005-11-03|Weforma Dämpfungstechnik GmbH|shock absorber|
    US6866588B2|2002-06-11|2005-03-15|Illinois Tool Works Inc.|One-way damper|
    AT5674U3|2002-07-22|2003-05-26|Fulterer Gmbh|STEAMED SELF-FEEDING DEVICE|
    JP4056906B2|2003-03-03|2008-03-05|株式会社パイオラックス|Heart cam-damper unit and opening / closing control device using the same|
    DE10313659B3|2003-03-26|2004-09-30|Zimmer, Günther Stephan|Pneumatic retarding device for braking movable furniture parts|
    AT502574B1|2003-05-19|2007-08-15|Blum Gmbh Julius|FURNITURE WITH A MOVABLE FURNITURE|
    DE20308218U1|2003-05-22|2004-09-23|Paul Hettich Gmbh & Co.|Closing and damping device for a moving furniture parts, e.g. drawer or door comprises a rotating damper having a brake disc with a blocking element|
    AT413630B|2003-07-24|2006-04-15|Fulterer Gmbh|AUSZIEHSPERREINRICHTUNG|
    AT413473B|2003-11-21|2006-03-15|Fulterer Gmbh|SELF FEED DEVICE|
    DE102004006092A1|2004-02-07|2005-08-25|Schock Metallwerk Gmbh|pull-out guide|
    AT500722B1|2004-08-16|2009-06-15|Blum Gmbh Julius|BEARING ELEMENT FOR FASTENING IN A FURNITURE BASKET|
    DE202005020820U1|2004-09-17|2006-08-17|Julius Blum Gmbh|fluid damper|
    DE102005021591A1|2005-05-10|2006-11-16|BSH Bosch und Siemens Hausgeräte GmbH|Household appliance with telescopic extension|
    AT503139B1|2006-02-08|2009-02-15|Blum Gmbh Julius|OUTBOARD WITH SLIP COUPLING|
    DE102006022563B4|2006-05-15|2018-11-08|Trw Automotive Gmbh|rotary damper|
    US7815267B1|2006-09-15|2010-10-19|Gus Frousiakis|Drawer slide closure apparatus|
    DE102006051688B4|2006-10-30|2008-08-21|Sidler Gmbh & Co. Kg|rotary damper|
    ES2304214B1|2007-03-07|2009-08-03|Ojmar, S.A.|DRAWER SELECTIVE EXTRACTION SYSTEM.|
    AT505053B1|2007-04-02|2009-02-15|Fulterer Gmbh|ROLLER Differential extension|
    AT505970B1|2007-11-07|2012-10-15|Blum Gmbh Julius|WEARING CONSTRUCTION FOR AT LEAST ONE FURNITURE DRIVE|
    DE102008011481A1|2008-02-21|2009-08-27|Schock Metallwerk Gmbh|pull-out guide|
    US8393693B2|2008-12-30|2013-03-12|Sun Chain Metal Industry Co., Ltd.|Return device for a drawer|
    DE102009012921A1|2009-03-12|2010-09-16|Gronbach Forschungs- Und Entwicklungs Gmbh & Co. Kg|Device or furniture has body, drawer which is pulled out from body, and move-in mechanism for moving-in drawer in body, where guide path is provided at body or at drawer|
    DE102009012922A1|2009-03-12|2010-09-16|Gronbach Forschungs- Und Entwicklungs Gmbh & Co. Kg|Device or furniture has body, drawer, which is pulled out from body, and move-in mechanism for moving-in drawer in body, where move-in mechanism has bolt, lever with guide for bolt and spring|
    DE202009002035U1|2009-04-03|2010-08-19|Paul Hettich Gmbh & Co. Kg|pull-out guide|
    US8317277B2|2009-04-21|2012-11-27|Accuride International, Inc.|Dampened assisted-motion systems and methods|
    US7987555B2|2009-07-03|2011-08-02|Martas Precision Slide Co., Ltd.|Hinged slide rail with buffering function|
    US20110043087A1|2009-08-19|2011-02-24|Hui-Chu Shih|Slide rail buffering structure|
    US8205951B2|2009-11-04|2012-06-26|Knape & Vogt Manufacturing Company|Closing device for drawers|
    AT508905B1|2009-12-07|2011-05-15|Fulterer Gmbh|AUSZIEHSPERRVORRICHTUNG|
    US8220879B2|2010-01-19|2012-07-17|Martas Precision Slide Co., Ltd.|Interlocking device for slide rail|
    US8459758B2|2010-01-21|2013-06-11|Actron Manufacturing, Inc.|Drawer slide auto-close dampening system with reset feature|
    JP5632645B2|2010-05-07|2014-11-26|株式会社ニフコ|Pull-in device and pull-in body used therefor|
    JP5613502B2|2010-05-19|2014-10-22|株式会社ニフコ|Damper|
    DE102011051907A1|2011-07-18|2013-01-24|Horst Lautenschläger|Retraction device for movable furniture components, particularly drawers, comprises movable carrier brought into releasable engagement with furniture component, where damping unit and spring unit stand in operative connection with carrier|
    AT512306B1|2012-01-25|2013-07-15|Fulterer Gmbh|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|
    NO2807320T3|2012-01-25|2018-07-21|
    AT512299B1|2012-01-25|2013-07-15|Fulterer Gmbh|FEEDING DEVICE FOR AT LEAST TWO EXTENDABLE FURNITURE PARTS|
    WO2013110099A1|2012-01-25|2013-08-01|Fulterer Gesellschaft Mbh|Pull-in system for multiple pull-out furniture parts|
    AT512415B1|2012-03-20|2013-08-15|Fulterer Gmbh|Catching device for a movably mounted furniture part|
    AT512509B1|2012-07-10|2013-09-15|Blum Gmbh Julius|Ejecting device for a movable furniture part|NO2807320T3|2012-01-25|2018-07-21|
    AT512306B1|2012-01-25|2013-07-15|Fulterer Gmbh|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|
    AT512415B1|2012-03-20|2013-08-15|Fulterer Gmbh|Catching device for a movably mounted furniture part|
    CN112982202B|2021-03-02|2022-03-04|中国建筑第八工程局有限公司|Shed tunnel structure capable of effectively resisting falling stone impact|
    法律状态:
    2018-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20180125 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA83/2012A|AT512300B1|2012-01-25|2012-01-25|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|ATA83/2012A| AT512300B1|2012-01-25|2012-01-25|DEVICE FOR CONTROLLING MOVEMENT OF A MOVABLE COMPONENT|
    CN201280068206.7A| CN104067023B|2012-01-25|2012-12-13|Device for the motion of the part that buffers mobile-bearing|
    PCT/AT2012/000315| WO2013110100A1|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|
    US14/373,758| US9777789B2|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|
    EP12816641.0A| EP2807395B1|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|
    PL12816641.0T| PL2807395T3|2012-01-25|2012-12-13|Device for damping the movement of a movably mounted component|
    [返回顶部]