EP2777432B1 - Extension guide for a furniture component which can be pulled out from a furniture body - Google Patents

Description

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.

It is known to provide at Ausziehführungen for extendable furniture parts, especially drawers or cabinet drawer, damping devices, whereby the braking is damped at least at one end of the displacement. For example, linear dampers in the form of piston-cylinder units and rotary dampers are known, which dampen the insertion of the guide rail over a last portion of the displacement, such damping devices are often combined with self-closing devices. A disadvantage of such cylinder or rotary damper is their space requirement. An installation in the pull-out is not possible in many configurations of pull-out and an arrangement outside the pull-out is often disturbing. In addition, such cylinder or rotary damper increase the pull-out.

Also known is a use of elements made of elastomeric materials, in particular rubber elements on parts in contact with each other. Due to the design, however, the abutting abutment surfaces are often relatively small and straightforward in pull-out guides which are designed for a higher load-bearing capacity; During operation, relatively rapid wear of such rubber impact elements occurs.

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. In this case, 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.

In 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. In order to achieve a simultaneous extension of the guide rails, it is further known to use on the center rail a rotatably mounted and a window recess of the center rail passing through elastic drive roller, but does not represent a load-transmitting role. Such a telescopic extension with differential effect is for example in the AT 392 883 B described.

In addition to roller extension guides pullout guides are known, which have equipped with rolling elements carriage, eg ball pull-out. For example, goes from the EP 1 561 398 A1 a bullet telescopic pull out.

Another example of such pull-out guides is from the EP 1 817 984 A1 known.

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.

In the pull-out according to the invention, 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. At the other of the two guide rails, a counter-stop element is arranged. 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. In addition, an overload stop device is available. 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. By means of this overload stop device, 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.

Preferably, 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.

In particular, the overload stop device is a fixed stop. There are thus 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 according to the invention 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. Advantageously, in this case, the end stop in a space between two legs of the first lever arm be arranged. As a result, a central load of the counter-stop element can be achieved so that no tilting moments occur.

In another possible embodiment, 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.

Advantageously, along the course of the longitudinal extension of the second lever arm from the pivot axis to the support surface measured length of the second lever arm (ie the measured along the neutral fiber length), which may also be referred to as unwound length or extended length 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. In a straight-line course of the second lever arm, the unwound length thus corresponds to the distance of the support surface from the pivot axis. In a straight-line course of the first lever arm, the unwound length of the first lever arm thus corresponds to the distance of the abutment surface from the pivot axis. For the course of the respective lever arm whose neutral fiber is used.

The second lever arm is preferably at least over a portion of its longitudinal extent at an angle of less than 45 ° to the direction of the second guide rail relative to the first guide rail. Preferably, this portion is at least the majority of the total longitudinal extent (= the unwound or extended length) of the second lever arm.

A damping device designed in the manner described above can advantageously be integrated into the pull-out guide.

In an advantageous embodiment it is provided that viewed in a side view in the direction of the pivot axis 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. In this case, 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.

Preferably, the base material is a plastic filled with strength-increasing fillers. As 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.

If in this document from "front" and "back" is mentioned, this is related to the direction of displacement of the extension of the pull-out.

• Fig. 1 eine Schrägsicht einer Ausziehführung gemäß einem Ausführungsbeispiel der Erfindung im zusammengeschobenen Zustand;
• Fig. 2 eine Ansicht der Ausziehführung;
• Fig. 3 eine Ansicht entsprechend Fig. 2, die Schienen im Bereich des vorderen Anschlagdämpfers teilweise aufgebrochen dargestellt;
• Fig. 4 ein vergrößertes Detail A von Fig. 2;
• Fig. 5 ein vergrößertes Detail B von Fig. 3;
• Fig. 6 ein vergrößertes Detail C von Fig. 5;
• Fig. 7 eine Schrägsicht der Ausziehführung im ausgezogenen Zustand;
• Fig. 8 eine Ansicht der Ausziehführung im ausgezogenen Zustand;
• Fig. 9 ein vergrößertes Detail D von Fig. 8;
• Fig. 10 einen vergrößerten Ausschnitt der Ansicht von Fig. 8 im Bereich des hinteren
• Anschlagdämpfers;
• Fig. 11 eine Ansicht entsprechend Fig. 10, der hintere Anschlagdämpfer weggelassen;
• Fig. 12 eine Ansicht entsprechend Fig. 8, die ausziehbare Führungsschiene im Bereich des vorderen Anschlagdämpfers teilweise aufgebrochen dargestellt;
• Fig. 13 ein vergrößertes Detail E von Fig. 12;
• Fig. 14 eine Schrägsicht der ausziehbaren Führungsschiene;
• Fig. 15 eine Ansicht der ausziehbaren Führungsschiene;
• Fig. 16 und 17 stirnseitige Ansichten der ausziehbaren Führungsschiene von vorne und hinten;
• Fig. 18 eine Schrägsicht der korpusfesten Führungsschiene;
• Fig. 19 eine Ansicht der korpusfesten Führungsschiene;
• Fig. 20 und 21 stirnseitige Ansichten der korpusfesten Führungsschiene von vorne und hinten;
• Fig. 22 eine Schrägsicht der mittleren Führungsschiene;
• Fig. 23 eine Ansicht der mittleren Führungsschiene;
• Fig. 24 eine Unteransicht der mittleren Führungsschiene;
• Fig. 25 eine Draufsicht auf die mittlere Führungsschiene;
• Fig. 26 ein vergrößertes Detail F von Fig. 22;
• Fig. 27 ein vergrößertes Detail G von Fig. 24;
• Fig. 28 ein vergrößertes Detail H von Fig. 24;
• Fig. 29 ein Schnitt entlang der Linie II von Fig. 25;
• Fig. 30 eine Schrägsicht der mittleren Führungsschiene mit nach Art einer Explosionsdarstellung herausgenommenem vorderen und hinteren Anschlagdämpfer;
• Fig. 31 eine Schrägsicht des vorderen Anschlagdämpfers aus einem gegenüber Fig. 30 unterschiedlichen Blickwinkel;
• Fig. 32 bis 34 Schrägsichten des hinteren Anschlagdämpfers aus unterschiedlichen Blickwinkeln;
• Fig. 35 ein vergrößertes Detail J von Fig. 32.

Further advantages and details of the invention are explained below with reference to the accompanying drawings. In this show:

• Fig. 1 an oblique view of a pull-out according to an embodiment of the invention in the collapsed state;
• Fig. 2 a view of the pull-out guide;
• Fig. 3 a view accordingly Fig. 2 , The rails shown partially broken in the area of the front stop damper;
• Fig. 4 an enlarged detail A of Fig. 2 ;
• Fig. 5 an enlarged detail B of Fig. 3 ;
• Fig. 6 an enlarged detail C of Fig. 5 ;
• Fig. 7 an oblique view of the pull-out in the extended state;
• Fig. 8 a view of the pull-out in the extended state;
• Fig. 9 an enlarged detail D of Fig. 8 ;
• Fig. 10 an enlarged section of the view from Fig. 8 in the area of the rear
• Stop damper;
• Fig. 11 a view accordingly Fig. 10 Having omitted the rear stop damper;
• Fig. 12 a view accordingly Fig. 8 , The extendable guide rail in the area of the front stopper damper partially broken shown;
• Fig. 13 an enlarged detail E of Fig. 12 ;
• Fig. 14 an oblique view of the extendable guide rail;
• Fig. 15 a view of the extendable guide rail;
• FIGS. 16 and 17 front views of the extendable guide rail from the front and rear;
• Fig. 18 an oblique view of the corpus fixed guide rail;
• Fig. 19 a view of the corpus fixed guide rail;
• FIGS. 20 and 21 frontal views of the corpus fixed guide rail from the front and rear;
• Fig. 22 an oblique view of the middle guide rail;
• Fig. 23 a view of the middle guide rail;
• Fig. 24 a bottom view of the middle guide rail;
• Fig. 25 a plan view of the middle guide rail;
• Fig. 26 an enlarged detail F of Fig. 22 ;
• Fig. 27 an enlarged detail G of Fig. 24 ;
• Fig. 28 an enlarged detail H of Fig. 24 ;
• Fig. 29 a section along the line II of Fig. 25 ;
• Fig. 30 an oblique view of the middle guide rail with taken out in the manner of an exploded front and rear stop damper;
• Fig. 31 an oblique view of the front stop damper from one opposite Fig. 30 different perspectives;
• FIGS. 32 to 34 Oblique views of the rear stop damper from different angles;
• Fig. 35 an enlarged detail J of Fig. 32 ,

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.

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.

Advantageously, a pull-out guide according to the invention can be designed for relatively high load-bearing forces. In particular, the load capacity of both sides of the extendable furniture part arranged pull-out guides together amount to more than 100kg.

In the exemplary embodiment shown, 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.

For mutually displaceable mounting of the rails 3, 4, 5 all 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. Furthermore, 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.

Preferably, the 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.

Instead of in the form of a differential drawer, which has a rotatably mounted on the center rail load-bearing differential roller 11, 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. Another such Rollenausziehführung 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 Kugelausziehführungen.

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.

When the middle guide rail 4 is displaced relative to the corpus-fixed guide rail 3 in the displacement direction 6 of the extension, so runs at the end of the displacement in the direction of pulling a arranged on the corpus fixed guide rail 3 counter-stop member 24 against a arranged on the central guide rail 4 rear stop damper 25th at. 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. In the figures, 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. Therefore, the end of the second lever arm 28 is not shown in its correct position in the figures, cf. especially Fig. 23 and 29 , In the actually installed, preloaded and thus slightly bent state of the rear stop damper, the support surface 29 as stated on the underside of the upper horizontal web 23 and the pin 31 protrudes into the opening 30th

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.

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. Here, at the upper end of the vertical web 20 of the central guide rail 4 arranged extension by an opening 35 in the first lever arm 27 (see. Fig. 35 ) inserted. The front end surface of this extension forms an end stop 36, as will be described below. This end stop is between side legs 37, 38 of the first lever arm 27th

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.

The 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. First, 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. As a result, 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.

Here, the first lever arm 27 is at least substantially rigid. The first lever arm 27 as a whole, i. its base part does not flex, or at least to a much lesser extent, than the second lever arm 28. 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, however, 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.

By the 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.

In addition, there is an 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. In particular from Fig. 11 in which the rear stop damper 25 is hidden, it can be seen that 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. In the increasing bending of the stop tabs 39, 40, if any, and then with the increasing pivoting of the first lever arm 27 and bending of the second lever arm 28, there is a reduction in the distance a, until the limit of the pivoting of the first lever arm 27 the Counter-stop element 24 starts at the end stop 36. Thus, the damping distance for the braking of the central guide rail 4 relative to the body-fixed guide rail 3 is completely traversed and a further displacement of the middle guide rail 4 relative to the corpus fixed guide rail 3 in the direction of displacement 6 of the extension and thus further pivoting of the first lever arm 27 about the pivot axis 26th is blocked. A possible overload of the rear stop damper 25 is prevented.

From the moment the counter-stop element 24 starts to run against the stop surface 41 until the overload stop device becomes effective, a bend of the at least one stop tongue 39, 40, if such exists, until it rests against the contact surface 42. 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. Preferably, it is provided that solely by the Bending of the second lever arm 28 from the counter-stop member 24 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. Also, 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 materialeinstückig from a plastic containing fillers.

In this embodiment, 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.

When viewed in a side view in the direction of the pivot axis 26 seen a 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. Preferably, 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.

In order to achieve this decrease in the area moment of inertia, a corresponding decrease in the cross-sectional area of the second lever arm 28 is provided in the exemplary embodiment.

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. For this purpose, 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. 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. 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. During the further movement in the direction of displacement 6, in which the braking of the extendable guide rail 5 takes place, 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. As a result, 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.

In the in the Fig. 7 to 13 illustrated position of the extendable guide rail 5, in which the counter-stop element 48 just starts against the stop surface 54 of the first lever arm 51 of the front stop damper 47, the overload stop elements 58, 59 a distance b from each other, see. Fig. 9 , If during braking of the extendable guide rail 5 and the increasing pivoting of the first lever arm 51, a limit of this pivoting of the lever arm 51 is achieved about the pivot axis 49, it comes to stop the second overload stop member 59 on the first overload stop member 58. 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.

To facilitate the assembly of the front stop damper 47, a mounting arm 69 is provided in the embodiment. During assembly, 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. For this purpose, 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.

When the pull-out guide is pushed together, it comes in the in the Fig. 1 to 6 illustrated position to a start of another counter-stop element 60, which is arranged on the extendable guide rail 5, to a further stop surface 61 of the first lever arm 51 of the front stop damper 47. This stop surface 61 is the stop surface 54 opposite, ie, the stop surface 54 is in the direction of displacement 7 of the insertion and the stop surface 61 is directed in the direction of displacement 6 of the extension. The stop surface 61 is arranged here directly on the base part of the first lever arm 51. In principle, however, it would be conceivable and possible to provide at least one bendable stop tongue on this side of the first lever arm, which, like the stop tongue 52, is spaced from the base part of the first lever arm 51 by a slot and has the stop face 61.

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. In the further displacement of the extendable guide rail 5 in the sliding direction corresponding to the insertion 7, 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. The illustrated bending is exaggerated for clarity. In fact, after an already smaller deflection, the second lever arm 55 comes to rest in a middle region of its longitudinal extent on the upper side of the lower horizontal web 22. In a further pivoting of the first lever arm 51, the second lever arm 55 deflects in the region between this contact point middle region of its longitudinal extent at the lower horizontal web 22 of the central guide rail 4 and the pivot axis 49. The spring rate increases thereby considerably opposite the deflection, before the middle region of the longitudinal extent of the second lever arm 55 comes to bear against the lower horizontal web 22.

To limit the pivoting of the first lever arm 51 about the pivot axis 49, an overload stop device is again provided. In the exemplary embodiment, 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.

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.

Also for the insertion of the middle guide rail 4 in the body fixed guide rail 3, 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.

It is also conceivable and possible that 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. For this purpose, as in the exemplary embodiment shown, 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.

Also, the 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.

For damping between the middle guide rail and the body-fixed guide rail, a stop damper 47 designed according to the corresponding stop damper could also be provided. Conversely, could be provided for damping between the middle guide rail and the extendable guide rail and the rear stop damper 25 appropriately trained stop damper.

Of course, 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 22 beading 59 Overload stop element 23 Upper horizontal bar 60 Counter-stop element 24 Counter-stop element 61 stop surface 25 rear stop damper 62 supporting 26 swivel axis 63 Overload stop element 27 first lever arm 64 stop part 28 second lever arm 65 end stop 29 supporting 66 line 30 breakthrough 67 spigot 31 spigot 68 Long hole 32 journal 69 mounting arm 33 head Start 34 opening 35 opening 36 end stop 37 side leg

Claims (15)

1. A pull-out guide for a furniture part (1) which can be pulled out of a furniture carcass (2), comprising a first guide rail (3, 4) and a second guide rail (4, 5) which is mounted displaceably over a path of displacement in and counter to a direction of displacement (6, 7) relative to the first guide rail (3, 4), wherein the braking of the second guide rail (4, 5) at least at one end of the path of displacement is damped by a stop damper (25, 47) arranged on one of the guide rails (3, 4, 5), against which damper a mating stop element (24, 48, 60) arranged on the other guide rail (3, 4, 5) runs up, characterised in that the stop damper (25, 47) is in the form of a lever which is arranged mounted pivotably about a pivot axis (26, 49) on the guide rail (3, 4, 5) on which the stop damper (25, 47) is arranged, and which comprises a first lever arm (27, 51) with a stop surface (41, 54, 61), against which surface the mating stop element (24, 48, 60) runs up upon braking of the second guide rail (4, 5), and an elastically flexible second lever arm (28, 55) for damping the braking of the second guide rail (4, 5), with a supporting surface (29, 57, 62) with which the second lever arm (28, 55) is supported relative to the guide rail (3, 4, 5) on which the stop damper (25, 47) is pivotably mounted, and in that at a limit value of the pivoting of the first lever arm (27, 51) about the pivot axis (26, 49) an overload stop means (24, 36; 58, 59; 58, 63) takes effect which limits the pivoting of the first lever arm (27, 51) about the pivot axis (26, 49).
2. A pull-out guide according to Claim 1, characterised in that the stop surface (41, 54, 61) of the first lever arm (27, 51) is movable over a distance of at least 1 mm, preferably over a distance of at least 2 mm, solely due to the flexing of the second lever arm (28, 55), before the overload stop means (24, 36; 58, 59; 58, 63) takes effect.
3. A pull-out guide according to Claim 1 or 2, characterised in that the second lever arm (28, 55), at least over a portion of its longitudinal extent, is oriented at an angle of less than 45° to the direction of displacement (6, 7).
4. A pull-out guide according to one of Claims 1 to 3, characterised in that the length of the second lever arm (28, 55), measured along the course of the longitudinal extent of the second lever arm (28, 55) from the pivot axis (26, 49) to the supporting surface (29, 57, 62), is at least three times the length of the first lever arm (27, 51), measured along the course of the longitudinal extent of the first lever arm (27, 51) from the pivot axis (26, 49) to the stop surface (41, 54).
5. A pull-out guide according to one of Claims 1 to 4, characterised in that, viewed in a side view in the direction of the pivot axis (26, 49), a first straight connecting line (44), which extends between the stop surface (41, 54) of the first lever arm (27, 51) and the pivot axis (26, 49), encloses an angle (46) which is less than 135°, preferably less than 110°, with a second straight connecting line (45) which extends between the supporting surface (29, 57, 62) of the second lever arm (28, 55) and the pivot axis (26, 49).
6. A pull-out guide according to one of Claims 1 to 5, characterised in that the overload stop means comprises the mating stop element (24) and an end stop (36) which is arranged on the guide rail (3, 4) on which the stop damper (25) is pivotably mounted, and onto which the mating stop element (24) runs upon reaching the limit value of the pivoting of the first lever arm (27) about the pivot axis (26).
7. A pull-out guide according to Claim 6, characterised in that the end stop (36) is arranged between two side arms (37, 38) of the first lever arm (27).
8. A pull-out guide according to one of Claims 1 to 5, characterised in that the overload stop means comprises a first stop element (58) arranged on the first guide rail (3, 4) and a second overload stop element (59, 63) arranged on the second guide rail (4, 5), against which second element the first overload stop element (58) runs up upon reaching the limit value of the pivoting of the first lever arm (51) about the pivot axis (49).
9. A pull-out guide according to one of Claims 1 to 8, characterised in that the first lever arm (27, 51) has at least one stop tongue (39, 40; 52), the at least one stop tongue (39, 40; 52) having the stop surface (41, 54) and being elastically flexible when the mating stop element (24, 48) runs up and, upon reaching a maximum value of its flexing, coming to lie against a supporting surface (42) of the first lever arm (27, 51).
10. A pull-out guide according to Claim 9, characterised in that the spring rate of the flexing of the at least one stop tongue (39, 40; 52) is less than 10% of the spring rate of the flexing of the second lever arm (28, 55).
11. A pull-out guide according to one of Claims 1 to 10, characterised in that the first lever arm (27, 51) has a base part which extends over the length of the first lever arm (27, 51) and the spring rate of the flexing of the second lever arm (28, 55) is less than 10% of the spring rate of the flexing of the base part of the first lever arm (27, 51).
12. A pull-out guide according to one of Claims 1 to 11, characterised in that the second moment of area which acts counter to flexing in the direction at right-angles to the longitudinal extent of the second lever arm (28, 55) at the location in question in each case of the second lever arm (28, 55) and at right-angles to the pivot axis (26, 49) decreases with increasing distance from the pivot axis (26, 49) measured along the course of the longitudinal extent of the second lever arm (28, 55).
13. A pull-out guide according to one of Claims 1 to 12, characterised in that the stop damper (25, 47) has a base material which is a plastics material which has a modulus of elasticity which lies in the range of 6,000 to 30,000, preferably in the range of 10,000 to 25,000.
14. A pull-out guide according to Claim 13, characterised in that the stop damper (25, 47) is designed to be of one piece in terms of material and consists overall of the base material.
15. A pull-out guide according to one of Claims 1 to 14, characterised in that at least one of the guide rails is provided with rollers (8-13) which are rotatably mounted about spindles which are located fixed relative to the guide rail (3, 4, 5).

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