EP2777432B1 - Commande d'extraction pour un élément de meuble pouvant être extrait d'un corps de meuble - Google Patents

Commande d'extraction pour un élément de meuble pouvant être extrait d'un corps de meuble Download PDF

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Publication number
EP2777432B1
EP2777432B1 EP14000485.4A EP14000485A EP2777432B1 EP 2777432 B1 EP2777432 B1 EP 2777432B1 EP 14000485 A EP14000485 A EP 14000485A EP 2777432 B1 EP2777432 B1 EP 2777432B1
Authority
EP
European Patent Office
Prior art keywords
lever arm
stop
guide rail
pull
pivot axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14000485.4A
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German (de)
English (en)
Other versions
EP2777432A1 (fr
Inventor
Wolfgang Müller
Edwin Grübel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fulterer GmbH
Original Assignee
Fulterer GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Priority to PL14000485T priority Critical patent/PL2777432T3/pl
Publication of EP2777432A1 publication Critical patent/EP2777432A1/fr
Application granted granted Critical
Publication of EP2777432B1 publication Critical patent/EP2777432B1/fr
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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47B—TABLES; DESKS; OFFICE FURNITURE; CABINETS; DRAWERS; GENERAL DETAILS OF FURNITURE
    • A47B88/00—Drawers for tables, cabinets or like furniture; Guides for drawers
    • A47B88/40—Sliding drawers; Slides or guides therefor
    • A47B88/49—Sliding drawers; Slides or guides therefor with double extensible guides or parts
    • A47B88/493—Sliding drawers; Slides or guides therefor with double extensible guides or parts with rollers, ball bearings, wheels, or the like
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47B—TABLES; DESKS; OFFICE FURNITURE; CABINETS; DRAWERS; GENERAL DETAILS OF FURNITURE
    • A47B88/00—Drawers for tables, cabinets or like furniture; Guides for drawers
    • A47B88/40—Sliding drawers; Slides or guides therefor
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47B—TABLES; DESKS; OFFICE FURNITURE; CABINETS; DRAWERS; GENERAL DETAILS OF FURNITURE
    • A47B88/00—Drawers for tables, cabinets or like furniture; Guides for drawers
    • A47B88/40—Sliding drawers; Slides or guides therefor
    • A47B88/473—Braking devices, e.g. linear or rotational dampers or friction brakes; Buffers; End stops
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47B—TABLES; DESKS; OFFICE FURNITURE; CABINETS; DRAWERS; GENERAL DETAILS OF FURNITURE
    • A47B2210/00—General construction of drawers, guides and guide devices
    • A47B2210/0091—Drawer movement damping
    • A47B2210/0094—Drawer damping device with 2 relatively movable parts to convert kinetic energy

Definitions

  • the invention relates to a pull-out for a pull-out of a furniture body furniture part comprising a first guide rail and a second guide rail which is slidably mounted relative to the first guide rail in and against a displacement direction via a displacement, wherein the braking of the second guide rail at least at one end of the displacement path is damped by a arranged on one of the guide rails stop damper, to which a arranged on the other guide rail counter-stop element starts.
  • Pull-out guides are known, for example, in the form of roller pull-out guides, in which the rollers serving for the displacement are rotatably mounted on the rails about axes which are stationary relative to them.
  • Differential-type roller pull-out guides have a load-transmitting differential roller rotatably mounted on the center rail, thereby achieving synchronized or differential travel of the rails.
  • the middle rail only covers half the path of the pull-out rail with respect to the carcass rail.
  • Such role differential extension guides are for example from the AT 391 603 B and EP 1 360 914 A1 known.
  • the role-pull guides are known as another type telescopic extension guides in which on all rails load-transmitting rollers are rotatably mounted and in which the pull-out and the center rail are pulled out of the carcass rail successively.
  • load-transmitting rollers are rotatably mounted and in which the pull-out and the center rail are pulled out of the carcass rail successively.
  • Such a telescopic extension with differential effect is for example in the AT 392 883 B described.
  • roller extension guides which have equipped with rolling elements carriage, eg ball pull-out.
  • rolling elements carriage eg ball pull-out.
  • the object of the invention is to provide a pull-out of the type mentioned, which has an advantageous damping device, which can be integrated with relatively little space in the pull-out, with a durable damping device can be realized even at higher payloads provided for pull-out. According to the invention, this is achieved by a pull-out guide with the features of claim 1.
  • a stop damper is used, which is designed as a lever.
  • This lever is mounted on the first guide rail, against which the braked second guide rail is slidably mounted, or on the braked second guide rail pivotable about a pivot axis.
  • a counter-stop element is arranged at the other of the two guide rails.
  • the lever has a first lever arm with a stop surface against which the counter-stop element for braking the second guide rail starts, and a second lever arm with a support surface with which the second lever arm is supported relative to that guide rail on which the lever is pivotably mounted about the pivot axis ,
  • the second lever arm is elastically bendable in such a way that the second lever arm dampens the deceleration of the second guide rail due to its bending.
  • the second lever arm thus acts like a leaf spring.
  • the first lever arm is in this case preferably not bendable or at least much less bendable (by a factor of at least 5), so that the first lever arm not or much less contributes to the damping of the deceleration of the second guide rail.
  • an overload stop device is available.
  • the overload stop device When the first lever arm during braking of the second guide rail, starting from a starting position, which it occupies when the counter-stop element is spaced from the stop surface is increasingly pivoted, the overload stop device is effective upon reaching a limit of the pivoting of the first lever arm about the pivot axis.
  • the pivoting of the first lever arm about the pivot axis is limited to a maximum value, so that the force exerted by the counter-stop element on the second lever arm is limited by this overload stop device.
  • the overload stop device thus becomes effective upon reaching a maximum bending of the second lever arm and prevents further bending of the second lever arm.
  • the abutment surface of the first lever arm alone by the bending of the second lever arm via one on the direction of displacement of the second Guide rail relative to the first guide rail related, distance of at least 1 mm, preferably at least 2mm are moved before the overload stop device is effective.
  • the overload stop device is a fixed stop.
  • two inflexible elements preferably made of metal, to each other.
  • the pull-out guide according to the invention has at least one damping device which acts between two guide rails of the pull-out guide in a displacement direction at the end of the displacement path.
  • a pull-out guide according to the invention can also have two or more such damping devices, with a respective damping device acting between two respective guide rails in a respective displacement direction. If such damping devices are present in both displacement directions for two mutually displaceable guide rails, these damping devices may desirably have partially the same parts, e.g. a common stop damper in the form of a lever, wherein for the two displacement directions separate counter-stop elements are present, which pivot the first lever arm at the end of the displacement in the respective displacement direction in opposite directions, so that the second lever arm is bent in opposite directions.
  • the overload stop device of a damping device may include in a possible embodiment, the counter-stop element and an end stop, which is arranged on that guide rail on which the stop damper is pivotally mounted. If the first lever arm is pivoted by the start of the counter-stop element about the pivot axis until the limit value of the pivoting is reached, the counter-stop element runs against the end stop.
  • the end stop in a space between two legs of the first lever arm be arranged.
  • the overload stop device may have a first overload stop element arranged on the first guide rail, which cooperates with a second overload stop element arranged on the second guide rail.
  • the first and second overload stop elements are separate parts from the counter-stop element and the stop damper. For example, these can be formed by lobes bent out of the guide rails.
  • a limit value of the force exerted by the counter-stop element on the stop damper when exceeding which the overload stop device is effective is, for example, in the range from 150 to 300 N.
  • the unwound length of the first lever arm in a straight-line course of the second lever arm, at least that Threefold of the length of the first lever arm measured along the course of the longitudinal extent of the first lever arm from the pivot axis to the stop surface (ie the length measured along the neutral fiber), which may also be referred to as unwound length or extended length of the first lever arm.
  • the unwound length thus corresponds to the distance of the support surface from the pivot axis.
  • the unwound length of the first lever arm thus corresponds to the distance of the abutment surface from the pivot axis.
  • a damping device designed in the manner described above can advantageously be integrated into the pull-out guide.
  • a first connecting line extending between the abutment surface of the first lever arm and the pivot axis, an angle with a second connecting line extending between the support surface of the second lever arm and the pivot axis , an angle that is less than 135 °, preferably less than 110 °. Particularly preferably, this angle is in the range of 70 ° to 90 °.
  • the lever forming the stopper damper preferably comprises a base material which is a plastic having a modulus of elasticity in the range of 6,000 to 30,000, preferably 10,000 to 25,000, with a value in the range of 15,000 to 20,000 being particularly preferred.
  • a smaller proportion of other materials of preferably less than 10% by volume of the total stop damper may be present or the stop damper may be entirely formed entirely of this base material, d. H. have no other materials.
  • the base material desirably has a tensile and compressive strength of more than 100 megapascals, preferably more than 150 megapascals.
  • the base material is a plastic filled with strength-increasing fillers.
  • filler for example, glass fibers, aramid fibers, carbon fibers or glass beads can be used.
  • the filler content is favorably in the range of 20% to 60%.
  • the plastic may be, for example, polyamide, PEEK or polyamide imide.
  • FIG. 1 to 35 An embodiment of a trained in accordance with the invention pull-out is in the Fig. 1 to 35 shown.
  • the pull-out guide is used to pull out a pull-out furniture part 1 from a furniture body 2, the only in Fig. 8 are indicated by dashed lines.
  • the indicated pull-out furniture part 1 is a drawer.
  • a pull-out guide according to the invention can also be designed, for example, to pull out cabinet extensions.
  • pull-out furniture part 1 On both sides of the pull-out furniture part 1 such pull-out guides are attached, of which only one is shown and are formed in mirror image.
  • a pull-out guide according to the invention can be designed for relatively high load-bearing forces.
  • the load capacity of both sides of the extendable furniture part arranged pull-out guides together amount to more than 100kg.
  • the pull-out guide comprises a body-fixed guide rail 3 to be attached to the furniture body 2, a middle guide rail 4 and an extendable guide rail 5 to be attached to the extendable furniture part 1.
  • the guide rails 3 and 4 and the guide rails 4 and 5 are each mounted displaceable relative to one another.
  • rollers are rotatably mounted on the central guide rail 4 in the illustrated embodiment. It is formed in a known manner, a differential extension, in which when pulling out the extendable guide rail 5, the middle guide rail 4 moves at half the speed of the extendable guide rail 5.
  • the rollers comprise a front roller 8 rotatably mounted relative to the displacement direction 6 of the extension in the region of the front end of the guide rail 4, a rear roller 9 rotatably mounted in the region of the rear end of the guide rail 4, one rotatably mounted in a central region of the guide rail 4 middle roller 10, arranged next to the central roller 10, rotatably mounted with game differential roller 11 and a rotatably mounted above the differential roller 11 support roller 12.
  • a game rotatably mounted auxiliary roller 13 is conveniently present, which in a region of the longitudinal extent of the central guide rail 4 is rotatably mounted, which lies between the rear roller 9 and the middle roller 10.
  • the extendable guide rail 5 includes a support web 14 for supporting the extendable furniture part 1, a catwalk 15 and a connecting web with the catwalk 15 connecting connecting web 16.
  • the catwalk 15 has on its underside a track for the front roller 8 and the differential roller 11 and its top a raceway for the support roller 12.
  • the support bar 14 could also be omitted and made the connection with the pull-out furniture part 1 via the connecting web 16.
  • the corpusfest guide rail 3 comprises an upper catwalk 17 and a lower catwalk 18, which are interconnected by a connecting web 19.
  • the upper catwalk 17 has on its underside a track for the rear roller 9.
  • the lower catwalk 18 has on its upper side a track for the differential roller 11, the middle roller 10 and the auxiliary roller 13.
  • rollers 8-13 are rotatably mounted about horizontal axes and the catwalks 15, 17 and 18 aligned horizontally.
  • the rear guide rail has a vertical web 20, from the upper and at the lower end of an upper and a lower horizontal web 23, 21 go out.
  • the lower horizontal web 23 is provided with an upwardly directed beading 22 extending parallel to the vertical web 20.
  • the rear roller 9 and support roller 12 are rotatably mounted around the vertical web 20 fixed axes.
  • the front roller 8, middle roller 10, differential roller 11 and auxiliary roller 13 are rotatably mounted about axes which extend between the vertical web 20 and the bead 22.
  • the mutual sliding support of the guide rails 3, 4, 5 could also be done in other ways, for example, by a trained in other ways roller extension, wherein the guide rails through Casters are mutually displaceable, wherein the rollers are rotatably mounted to the respective guide rails stationary axes.
  • roller extension wherein the guide rails through Casters are mutually displaceable, wherein the rollers are rotatably mounted to the respective guide rails stationary axes.
  • Another such Rollenauszieh entry example is a telescopic extension, in which on all guide rails rollers are rotatably mounted and the guide rails are pulled out successively.
  • the invention can also be used in other types of pull-out guides than in roller pull-out guides with castors having fixed axes to the guide rails be, especially in pullout guides, which have fitted with rolling elements carriage, eg Kugelauszieh arrangementen.
  • the mutual displacement of the central guide rail 4 relative to the body-fixed guide rail 3 and the extendable guide rail 5 relative to the central guide rail 4 is limited in the direction of displacement of the extension 6 and in the opposite direction of displacement 7 of the insertion respectively by stops, wherein the rails between the attacks each about a displacement are mutually displaceable.
  • the counter-stop element 24 is here formed by a punched out of the upper horizontal web 23 and bent down lobe, but could also be formed in other ways.
  • the rear stop damper 25 is designed in the form of a two-armed lever and rotatably mounted on the central guide rail 4 about a horizontal pivot axis 26.
  • the first lever arm 27 cooperates with the counter-stop member 24 and the second lever arm 28 is supported on a support surface 29 on the central guide rail 4, in the embodiment on the underside of the upper horizontal web 23.
  • the upper horizontal web 23 in this case has a slot-like opening 30, in which engages over the support surface 29 protruding pin 31 of the second lever arm 28, whereby a guide for the end of the second lever arm 28 is formed in the direction of displacement 6.
  • the rear stop damper 25 is shown in its relaxed state. In fact, the stop damper is slightly biased when installed in the middle guide rail.
  • the support of the end of the second lever arm 28 on the guide rail 4, on which the stop damper 25 is rotatably mounted could also be done in other ways, for example via an attached to the profile of the guide rail 4 part.
  • journal 32 For mounting the rear stop damper 25 on the central guide rail 4 is a journal 32 with a downwardly projecting projection 33 (see. Fig. 33 ) in a keyhole-shaped opening 34 (see. Fig. 30 ) and guided down until the projection 33 engages over the edge of the opening 34.
  • a journal 32 For mounting the rear stop damper 25 on the central guide rail 4 is a journal 32 with a downwardly projecting projection 33 (see. Fig. 33 ) in a keyhole-shaped opening 34 (see. Fig. 30 ) and guided down until the projection 33 engages over the edge of the opening 34.
  • a journal 32 For mounting the rear stop damper 25 on the central guide rail 4 is a journal 32 with a downwardly projecting projection 33 (see. Fig. 33 ) in a keyhole-shaped opening 34 (see. Fig. 30 ) and guided down until the projection 33 engages over the edge of the opening 34.
  • the first lever arm 27 at the upper end of the vertical web 20 of the central guide rail 4 arranged
  • the second lever arm 28 is guided in a central region of its longitudinal extension relative to the guide rail 4 by a pin 67 arranged on the second lever arm 28 (cf. FIGS. 32 and 34 ) in a slot 68 (see. Fig. 2 and 30 ) engages in the guide rail 4.
  • the first lever arm 27 has from a base portion of the first lever arm 27 by a slot spaced stop tabs 39, 40. These each have a stop member surface to which the counter-stop member 24 starts at the end of Ausziehweges. These stop faces together form a stop surface 41 of the first lever arm 27 for cooperation with the counter-stop element 24.
  • Fig. 7 to 13 show the position of the middle guide rail 4, in which the counter-stop element 24 just starts in the displacement direction of the extension guide 6 in the displacement direction 6 to the stop surface 41 of the first lever arm 27 of the rear stop damper 25. From this position, the rear stop damper 25 is effective.
  • the stop tongues 39, 40 are bent in the direction of the base part of the first lever arm 27 until they rest against a contact surface 42 of the base part of the first lever arm 27.
  • the gap between the stop tongues 39, 40 and the base part of the first lever arm 27 is thus closed.
  • a pivoting of the first lever arm 27 takes place about the pivot axis 26, wherein the second lever arm 28 bends increasingly.
  • This bend is in Fig. 10 is indicated by a dashed line 43 (the line 43 can be regarded as a neutral fiber in the bent state of the second lever arm 28.
  • the bending thus takes place about an imaginary bending axis parallel to the pivot axis 26.
  • the first lever arm 27 is at least substantially rigid.
  • At least the spring rate of the bend of the second lever arm 28 is less than 10% of the spring rate of bending of the base part of the first lever arm 27.
  • the stop tongues 39, 40 are much easier bendable than the second lever arm 28. In the bending of the stop tabs 39, 40 until their contact with the contact surface 42 thus hardly comes to a bend of the second lever arm 28.
  • the spring rate of bending the stop tongues 39 Preferably, 40 is less than 10% of the spring rate of the bend of the second lever arm.
  • stop tongues 39, 40 there is a significant reduction of the impact noise of the counter-stop element 24 on the rear stop damper 25. It is conceivable and possible, however, that the stop tongues 39, 40 accounts or only one stop tongue is present.
  • overload stopper which becomes effective when a threshold value of pivoting of the first lever arm 27 from its initial position (which the first lever arm 27 occupies as long as the counter-abutment member 24 is spaced from the stopper face 41) is achieved.
  • This overload stop means here comprises the counter-stop element 24 and the end stop 36.
  • the counter-stop element 24 and the end stop 36 at the moment of the counter-stop member 24 against the stop surface 41 have a distance a.
  • the distance traveled by the counter-stop element 24 in the displacement direction 6 is preferably in the range from 0.2 mm to 1 mm, particularly preferably in the range from 0.3 mm to 0.6 mm. Furthermore, from the counter-stop element 24 to the effectiveness of the overload stop means, a path can be covered in the direction of displacement 6, which is made possible by an increasing bending of the second lever arm 28.
  • a distance in the displacement direction 6 can be covered, which is in the range of 1 mm to 7mm, preferably in the range of 1.5mm to 5mm, more preferably in the range of 3mm to 4mm.
  • the stop surface 41 can thus be moved only by virtue of this bending of the second lever arm 28 by this distance relative to the displacement direction 6.
  • the rear stop damper 25 is formed in the embodiment centrein Divisionig from a plastic containing fillers.
  • the second lever arm 28 extends, as long as the counter-stop member 24 is spaced from the stop surface 41, except for a relatively short, adjoining the support surface 29 end portion straight.
  • a more or less curved design and / or at least largely folded training (in which the second lever arm 28 has two or more between them bends of nearly 90 ° having portions) is conceivable and possible.
  • the first lever arm 27 is also formed substantially straight in the embodiment. Again, a more or less curved or even folded training would be conceivable and possible.
  • the length of the second lever arm 28 measured along the course of the longitudinal extent of the second lever arm 28 from the pivot axis 26 to the support surface 29 is at least three times the length of the first measured along the course of the longitudinal extent of the first lever arm 27 from the pivot axis 26 to the stop surface 41 lever arm. It is thereby provided an advantageous length of the second lever arm 28 for its bending.
  • first connecting line 44 which extends between the stop surface 41 of the first lever arm 27 and the pivot axis 26 and a second connecting line 45 is considered, extending between the support surface 29 of the second lever arm 28th and the pivot axis 26 extends, so they close two connecting lines 44, 45 an angle 46, which is less than 135 °, preferably less than 110 °, see. Fig. 23 , Conveniently, this angle 46 is in the range of 70 ° to 100 °.
  • the area moment of inertia of the second lever arm 28 against a bend in the direction perpendicular to the longitudinal extent of the second lever arm 28 at the respectively considered location and at right angles to the pivot axis 26 decreases with increasing, along the course of the longitudinal extent of the second lever arm 28 measured distance from the pivot axis 26.
  • the decrease in the area moment of inertia is continuous, at least over much of the length of the second lever arm 28.
  • the second lever arm 28 may be like a leaf spring with a parabolic design or act as a carrier with the same tension.
  • the displacement of the extendable guide rail 5 relative to the central guide rail 4 in the direction of displacement 6 of the extraction is damped by means of a front stop damper 47 to which a arranged on the extendable guide rail 5 counter stop element 48 starts.
  • the function is largely analogous to that of the interaction of the counter-stop element 48 arranged on the body-fixed guide rail 3 with the rear stop damper 25, as described above.
  • the preceding description thus also applies to the front stop damper 47 and its interaction with the counter-stop element 48, unless differences are described in the following.
  • the counter stop element 48 is arranged here on the relative to the central guide rail 4 in the direction of displacement 6 moving extendable guide rail 5 and formed in the form of a two-armed lever front stop damper 47 is pivotable on the central guide rail 4 about the pivot axis 49 stored.
  • an arcuate lower edge of the front stop damper 47 rests on the lower horizontal web 22 of the middle guide rail 4.
  • a hook-shaped extension 50 of the front stop damper 47 extends through an opening in the lower horizontal web 22 of the central guide rail 4 and is thereby suspended in the lower horizontal web 21.
  • the first lever arm 51 Analogous to the stop tongues 39, 40 of the first lever arm 27 of the rear stop damper 25, the first lever arm 51 has a stop tongue 52 (here only individual) whose function corresponds to that of the stop tongues 39, 40 and which has the stop surface 54 for the counter stop element 48.
  • the second lever arm 55 has at its end a hook-shaped extension 56 which extends through an opening in the lower horizontal web 21 and is thereby hooked into the lower horizontal web 21.
  • the extension 56 At its side facing the lower horizontal web 22, the extension 56 has a support surface 57, with which the second lever arm 55 is supported on the underside of the lower horizontal web 22.
  • the Fig. 7 to 13 show the position of the extendable guide rail 5, in which it just comes to the support surface 57 when pulling the extendable guide rail 5 in the direction of displacement 6 for starting the counter-stop member 48.
  • essentially only the bending of the stop tongue 52 initially occurs until it comes to rest on the base part of the first lever arm 51.
  • the first lever arm 51 is pivoted under bending of the second lever arm 55.
  • the bend of the second lever arm 55 is shown schematically in FIG Fig. 13 indicated by a dashed line 53.
  • the overload stop device is here formed by a first overload stop element 58, which is arranged on the central guide rail 4, and a second overload stop element 59, which is arranged on the extendable guide rail 5.
  • the overload stop elements 58, 59 are formed in the embodiment of punched out of the profiles of the rails and bent out lobes.
  • the first overload stop element 58 projects horizontally from the lower end of the middle guide rail 4.
  • the second overload stop element 59 projects from the underside of the support web 14 of the extendable guide rail 5 downwards.
  • a further displacement of the extendable guide rail 5 against the middle guide rail 4 in the direction of displacement 6 is thereby blocked, so that the pivoting of the first lever arm 51 is blocked at the limit and thus the force exerted by the counter-stop member 48 on the second lever arm 55 and thus the deflection of the second lever arm 55 is limited.
  • a mounting arm 69 is provided in the embodiment.
  • the hook-shaped extension 50 is suspended in the opening in the lower horizontal web 22 and hooked at the end of the second lever arm 55 hook-shaped extension 56 hooked into the further breakthrough in the lower horizontal web 21.
  • the second lever arm 55 is slightly bent in the direction away from the vertical web 20 to perform the hook-shaped extension 56 through a widened area in this opening of the lower horizontal web 21, after which the second lever arm 55 is released and the extension thereby in a narrower area in Breakthrough arrives, in which the hook-shaped extension 56 can not be pulled out of this breakthrough.
  • the Fig. 1 to 6 show just the position in which the counter-stop member 60 comes to the stop surface 61 to the plant.
  • the first lever arm 51 is pivoted by the counter-stop member 60 about the pivot axis 49, in the opposite pivoting direction as when pivoting the first lever arm 51 by the counter-stop member 48 when braking the extendable Guide rail 5 at the end of Ausziehweges.
  • the second lever arm 55 which is now supported with a voltage applied to the upper side of the lower horizontal web 22 support surface 62 at the lower horizontal web 22 of the central guide rail 4, is bent thereby.
  • the bending of the second lever arm 55 is in Fig. 5 indicated by a dashed line 66.
  • an overload stop device is again provided.
  • this comprises the first overload stop element 58 arranged on the central guide rail 4 and a third overload stop element 63 arranged on the extendable guide rail 5.
  • the third overload stop element 63 is formed in the illustrated exemplary embodiment by a tab punched out and bent out of the profile of the guide rail. This extends from the support web 14 down.
  • the third overload stop member 63 In the in the Fig. 1 to 6 illustrated position, the third overload stop member 63 a distance c from the first overload stop member 58, see. Fig. 4 , In the further displacement of the extendable guide rail 5 in the direction of displacement 7, wherein the first lever arm 51 is pivoted about the pivot axis 49, the third overload stop member 63 increasingly approaches the first overload stop member 58 until it comes to rest. The further displacement of the extendable guide rail 5 relative to the central guide rail 4 in the direction of displacement 7 is thereby blocked, so that a pivoting of the first lever arm 51 is limited to a limit and thus the force exerted by the counter-stop member 60 on the second lever arm 55 force is limited.
  • the insertion of the middle guide rail 4 in the corpusfeste guide rail 3 is formed in the embodiment shown by a fixed stop between the stop member 64 of the corpus fixed guide rail 3 and an end stop 65 of the middle guide rail 4.
  • the stop member 64 is formed by a stamped out of the connecting web 16 and bent tabs and the end stop 65 is formed by a rear end face of the vertical web 20 of the central guide rail 4.
  • a stop damper for braking the central guide rail 4 could be provided at the end of the displacement. This could in turn be formed in the manner of the stop damper 25 or 47.
  • the rear stop damper 25 has its second lever arm 28 rearwardly instead of forwardly extending (from the pivot axis 26 to its free end) configured.
  • the rear stop damper 25 would then be arranged further forward pivotally on the central guide rail. Angle and function are the same, but then the support surface is loaded on train instead of pressure.
  • the second lever arm 28 at the end could have a hook at the front stop damper 47, with which it interacts with the central guide rail 4.
  • a loadable on train contact point could also be designed in other ways.
  • front stop damper 47 could be formed and pivotally mounted so that its second lever arm 55 extends forward.
  • the rear and / or front stop damper 25, 47 could also be provided that extends the first lever arm 27 and 51 down instead of upwards.
  • the counter-stop elements should be arranged accordingly.
  • Embodiments are also conceivable and possible in which only one rear stop damper 25 designed in the manner described or only one front stop damper 47 designed in the manner described is present.
  • a stop damper 47 designed according to the corresponding stop damper could also be provided.
  • a stop damper 47 designed according to the corresponding stop damper could also be provided.
  • the invention can also be used with pull-out guides which have only two guide rails which can be displaced relative to one another or which have more than three guide rails which can be displaced relative to one another.
  • ⁇ b> Legend to the numbers: ⁇ / b> 1 extendable furniture part 38 side leg 2 furniture body 39 stop tongue 3 corpus fixed guide rail 40 stop tongue 4 middle guide rail 41 stop surface 5 extendable guide rail 42 contact surface 6 displacement direction 43 line 7 displacement direction 44 first connecting line 8th front caster 45 second connecting line 9 rear caster 46 angle 10 middle roller 47 front stop damper 11 differential roller 48
  • Counter-stop element 12 support roller 49 swivel axis 13 auxiliary role 50 extension 14 support web 51 first lever arm 15 catwalk 52 stop tongue 16 connecting web 53 line 17 upper catwalk 54 stop surface 18 lower catwalk 55 second lever arm 19 connecting web 56 extension 20 vertical web 57 supporting 21 lower horizontal bridge 58
  • Overload stop element 23 Upper horizontal bar 60
  • Counter-stop element 24 Counter-stop element 61 stop surface 25 rear

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  • Drawers Of Furniture (AREA)
  • Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)

Claims (15)

  1. Guidage d'extraction destiné à une partie de meuble (1) pouvant être extraite d'un corps de meuble (2) comprenant un premier rail de guidage (3, 4) et un second rail de guidage (4, 5) qui est monté coulissant par rapport au premier rail de guidage (3, 4) dans et dans la direction opposée à une direction de coulissement (6, 7) sur une course de coulissement, le freinage du second rail de guidage (4, 5) étant amorti au moins à une extrémité de la course de coulissement par un amortisseur de butée (25, 47) situé sur l'un des rails de guidage (3, 4, 5), et sur lequel bute un élément de butée antagoniste (24, 48, 60) monté sur l'autre rail de guidage (3, 4, 5),
    caractérisé en ce que
    l'amortisseur de butée (25, 47) est réalisé sous la forme d'un levier qui est monté pivotant autour d'un axe de pivotement (26, 49) sur le rail de guidage (3, 4, 5) sur lequel est monté l'amortisseur de butée (25, 47), et qui comporte un premier bras de levier (27, 51) muni d'une surface de butée (41, 54, 61) sur laquelle bute l'élément de butée antagoniste (24, 48, 60) en cas de freinage du second rail de guidage (4, 5), et un second bras de levier (28, 55) élastiquement flexible pour permettre d'amortir le freinage du second rail de guidage (4, 5) et ayant une surface d'appui (29, 57, 62) par laquelle s'appuie ce second bras de levier (28, 55) contre le rail de guidage (3, 4, 5) sur lequel est monté pivotant l'amortisseur de butée (25, 47), et en ce que pour une valeur limite du pivotement du premier bras de levier (27, 51) autour de l'axe de pivotement (26, 49) un dispositif de butée antisurcharge (24, 36, 58, 59, 58, 63) qui limite le pivotement du premier bras de levier (27, 51) autour de l'axe de pivotement (26, 49) devient actif.
  2. Guidage d'extraction conforme à la revendication 1,
    caractérisé en ce que
    la surface de butée (41, 54, 61) du premier bras de levier (27, 51) peut être déplacée par la seule flexion du second bras de levier (28, 55) sur une course d'au moins 1 mm, de préférence sur une course d'au moins 2 mm avant que le dispositif de butée antisurcharge (24, 36, 58, 59, 58, 63) ne devienne actif.
  3. Guidage d'extraction conforme à la revendication 1 ou 2,
    caractérisé en ce que
    le second bras de levier (28, 55) est orienté au moins sur un segment de son extension longitudinale selon un angle de moins de 45° par rapport à la direction de coulissement (6, 7).
  4. Guidage d'extraction conforme à l'une des revendications 1 à 3,
    caractérisé en ce que
    la longueur du second bras de levier (28, 55) mesurée le long de l'étendue longitudinale de ce second bras de levier (28, 55) de l'axe de pivotement (26, 49) à la surface d'appui (29, 57, 62) est égale à au moins le triple de la longueur du premier bras de levier (27, 51) mesurée le long de l'étendue longitudinale de ce premier bras de levier (27, 51) de l'axe de pivotement (26, 49) à la surface de butée (41, 54).
  5. Guidage d'extraction conforme à l'une des revendications 1 à 4,
    caractérisé en ce qu'
    en vue latérale en direction de l'axe de pivotement (26, 49) une première droite de liaison (44) qui s'étend entre la surface de butée (41, 54) du premier bras de levier (27, 51) et l'axe de pivotement (26, 49) définit avec une seconde droite de liaison (45) qui s'étend entre la surface d'appui (29, 57, 62) du second bras de levier (28, 55) et l'axe de pivotement (26, 49) un angle qui est inférieur à 135°, de préférence inférieur à 110°.
  6. Guidage d'extraction conforme à l'une des revendications 1 à 5,
    caractérisé en ce que
    le dispositif de butée anti-surcharge comprend l'élément de butée antagoniste (24) et une butée d'extrémité (36) qui est située sur le rail de guidage (3, 4) sur lequel est monté pivotant l'amortisseur de butée (25) et sur laquelle bute l'élément de butée antagoniste (24) lorsqu'a été atteinte la valeur limite du pivotement du premier bras de levier (27) autour de l'axe de pivotement (26).
  7. Guidage d'extraction conforme à la revendication 6,
    caractérisé en ce que
    la butée d'extrémité (36) est située entre deux branches latérales (37, 38) du premier bras de levier (27).
  8. Guidage d'extraction conforme à l'une des revendications 1 à 5,
    caractérisé en ce que
    le dispositif de butée antisurcharge comprend un premier élément de butée antisurcharge (58) situé sur le premier rail de guidage (3, 4) et un second élément de butée antisurcharge (59, 63) situé sur le second rail de guidage (4, 5) et sur lequel bute le premier élément de butée antisurcharge (58) lorsqu'a été atteinte la valeur limite du pivotement du premier bras de levier (51) autour de l'ace de pivotement (49).
  9. Guidage d'extraction conforme à l'une des revendications 1 à 8,
    caractérisé en ce que
    le premier bras de levier (27, 51) comprend au moins une languette de butée (39, 40, 52), cette languette de butée (39, 40, 52) comportant la surface de butée (41, 54), étant élastiquement flexible lors de la mise en butée de l'élément de butée antagoniste (24, 48), et s'appliquant lorsqu'a été atteinte la valeur maximum de cette flexion contre une surface d'appui (42) du premier bras de levier (27, 51).
  10. Guidage d'extraction conforme à la revendication 9,
    caractérisé en ce que
    le coefficient d'élasticité de la flexion de la languette de butée (39, 40, 52) est égal à moins de 10% du coefficient d'élasticité de la flexion du second bras de levier (28, 55).
  11. Guidage d'extraction conforme à l'une des revendications 1 à 10,
    caractérisé en ce que
    le premier bras de levier (27, 51) comprend une partie de base s'étendant sur la longueur de ce premier bras de levier (27, 51), et le coefficient d'élasticité de la flexion du second bras de levier (28, 55) est égal à moins de 10% du coefficient d'élasticité de la flexion de la partie de base du premier bras de levier (27, 51).
  12. Guidage d'extraction conforme à l'une des revendications 1 à 11,
    caractérisé en ce que
    le moment d'inertie géométrique agissant à l'encontre d'une flexion dans la direction perpendiculaire à l'étendue longitudinale du second bras de levier (28, 55) au point respectivement considéré de ce second bras de levier (28, 55) et perpendiculairement à l'axe de pivotement (26, 49) diminue avec l'augmentation de la distance à l'axe de pivotement (26, 49) mesurée le long de l'étendue longitudinale du second bras de levier (28, 55).
  13. Guidage d'extraction conforme à l'une des revendications 1 à 12,
    caractérisé en ce que
    l'amortisseur de butée (25, 47) renferme un matériau de base constitué par un matériau synthétique qui présente un module d'élasticité situé dans la plage de 6.000 à 30.000, de préférence dans la plage de 10.000 à 25.000.
  14. Guidage d'extraction conforme à la revendication 13,
    caractérisé en ce que
    l'amortisseur de butée (25, 47) est réalisé en un seul matériau et globalement dans le matériau de base.
  15. Guidage d'extraction conforme à l'une des revendications 1 à 14,
    caractérisé en ce qu'
    au moins l'un des rails de guidage est équipé de galets (8, 13) qui sont montés mobiles, en rotation autour d'axes solidaires du rail de guidage (3, 4, 5).
EP14000485.4A 2013-03-12 2014-02-11 Commande d'extraction pour un élément de meuble pouvant être extrait d'un corps de meuble Active EP2777432B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL14000485T PL2777432T3 (pl) 2013-03-12 2014-02-11 Prowadnica wysuwana do części mebla wysuwanej z korpusu mebla

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA189/2013A AT513608B1 (de) 2013-03-12 2013-03-12 Ausziehführung für ein aus einem Möbelkorpus ausziehbares Möbelteil

Publications (2)

Publication Number Publication Date
EP2777432A1 EP2777432A1 (fr) 2014-09-17
EP2777432B1 true EP2777432B1 (fr) 2015-07-15

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ID=50072848

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14000485.4A Active EP2777432B1 (fr) 2013-03-12 2014-02-11 Commande d'extraction pour un élément de meuble pouvant être extrait d'un corps de meuble

Country Status (5)

Country Link
US (1) US9301609B2 (fr)
EP (1) EP2777432B1 (fr)
AT (1) AT513608B1 (fr)
ES (1) ES2548230T3 (fr)
PL (1) PL2777432T3 (fr)

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US9642460B2 (en) * 2014-06-23 2017-05-09 King Slide Works Co., Ltd. Self-closing slide rail assembly and self-closing mechanism thereof
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CN105640089B (zh) * 2016-03-03 2018-02-23 李浩典 伸缩滑轨的缓冲自关器
US9854909B1 (en) * 2016-07-30 2018-01-02 Nan Juen International Co., Ltd. Bi-directional positioning sliding rail assembly
TWI621415B (zh) * 2016-09-13 2018-04-21 川湖科技股份有限公司 滑軌總成及其滑軌套件
TWI584761B (zh) * 2016-09-13 2017-06-01 川湖科技股份有限公司 滑軌總成
CN107836869B (zh) * 2016-09-20 2019-11-15 川湖科技股份有限公司 滑轨总成及其滑轨套件
TWI642386B (zh) 2017-08-10 2018-12-01 川湖科技股份有限公司 滑軌總成及其滑軌套件
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Also Published As

Publication number Publication date
US9301609B2 (en) 2016-04-05
US20140265795A1 (en) 2014-09-18
AT513608A4 (de) 2014-06-15
ES2548230T3 (es) 2015-10-15
AT513608B1 (de) 2014-06-15
EP2777432A1 (fr) 2014-09-17
PL2777432T3 (pl) 2015-12-31

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