EP3253255A1 - Mecanisme synchrone - Google Patents

Mecanisme synchrone

Info

Publication number
EP3253255A1
EP3253255A1 EP16703255.6A EP16703255A EP3253255A1 EP 3253255 A1 EP3253255 A1 EP 3253255A1 EP 16703255 A EP16703255 A EP 16703255A EP 3253255 A1 EP3253255 A1 EP 3253255A1
Authority
EP
European Patent Office
Prior art keywords
spring
support
backrest
coupling element
movement
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.)
Granted
Application number
EP16703255.6A
Other languages
German (de)
English (en)
Other versions
EP3253255B1 (fr
Inventor
Hermann Bock
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.)
Bock 1 GmbH and Co KG
Original Assignee
Bock 1 GmbH and Co KG
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
Priority claimed from DE102015101546.3A external-priority patent/DE102015101546B4/de
Application filed by Bock 1 GmbH and Co KG filed Critical Bock 1 GmbH and Co KG
Publication of EP3253255A1 publication Critical patent/EP3253255A1/fr
Application granted granted Critical
Publication of EP3253255B1 publication Critical patent/EP3253255B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C1/00—Chairs adapted for special purposes
    • A47C1/02—Reclining or easy chairs
    • A47C1/031—Reclining or easy chairs having coupled concurrently adjustable supporting parts
    • A47C1/032—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest
    • A47C1/03261—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest characterised by elastic means
    • A47C1/03272—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest characterised by elastic means with coil springs
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C1/00—Chairs adapted for special purposes
    • A47C1/02—Reclining or easy chairs
    • A47C1/031—Reclining or easy chairs having coupled concurrently adjustable supporting parts
    • A47C1/032—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest
    • A47C1/03261—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest characterised by elastic means
    • A47C1/03266—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest characterised by elastic means with adjustable elasticity

Definitions

  • the invention relates to a synchronous mechanism for a
  • synchronous mechanism is understood to mean assemblies in the seat substructure of an office chair which provide kinematics which are coupled to one another and provide a specific relative movement of the seat and backrest Office chair mounted
  • Backrest support which extends in a conventional manner from the actual synchronizing mechanism to the rear, carries on an upwardly extending arm, the backrest of the office chair.
  • An object of the present invention is to provide a structurally simple self-adjusting synchronous mechanism, which requires a small space, yet the
  • Swing resistance of the backrest is adjustable. This object is achieved by a synchronous mechanism according to claim 1.
  • Backrest support is pivotally connected to both pivotable about a first transverse axis with the base support and with the seat support and wherein the seat support is pivotally connected via a coupling element with the base support, wherein the coupling element pivotable about both a second transverse axis pivotally connected to the base support and the seat support is connected, wherein a spring mechanism is provided for adjusting the pivoting resistance of the backrest, which spring mechanism comprises at least one spring element, wherein the at least one
  • Spring element is supported with its one spring end on the coupling element.
  • the number of coupling elements in particular the number of seat support and backrest support connecting elements, reduced, thereby achieving a particularly simple structural design of the mechanism, without sacrificing the desired functionality of a synchronous mechanism.
  • a deviating from the usual lifting movement of the seat seat movement can be provided, in which nevertheless the so-called
  • Backrest support pivotable about a transverse axis and thus defining the main pivot axis of the mechanism with the
  • Base support as well as with the seat support directly, ie directly and without the interposition of an additional component, articulated such that a pivotal movement of the backrest from a basic position into a pivoted backward position an immediate lowering movement of the chair longitudinal direction seen rear portion of the seat carrier to the rear induced below and the seat support is pivotally connected to the base support via a hinged to the seat support and the base support coupling element such that during the pivotal movement of the backrest from the basic position in the pivoted back position immediate lifting movement of seen in chair longitudinal direction front portion of the seat support back to the top.
  • the rear portion of the seat is lowered at a pivoting of the backrest in its rearwardly pivoted position, while the front portion of the seat is raised.
  • the lowering of the rear seating area takes place directly at each leaving the basic position, without about initially a lifting movement of the rear seating area takes place.
  • the basic position is considered that position in which the backrest is not pivoted to the rear.
  • the user's weight directly affects the swing resistance felt by the user.
  • a light user must be a significantly lower when pivoting
  • the special synchronous movement of the mechanism according to the invention is preferably achieved in a particularly simple manner by the positions of the articulation points of
  • Backrest support on the base support on the one hand and on the seat support on the other hand a rigidly connected to the backrest support or as an integral part of the
  • Backrest support trained coupling element is defined. In other words, between backrest support and Seat support no mutually freely pivotable coupling element longer required. Instead, the backrest support itself serves as a coupling element.
  • a particularly suitable coupling geometry and a resulting synchronous movement is achieved in a preferred embodiment of the invention in that the
  • Coupling element on the base support and the articulation point of the front coupling element on the seat support seen in the seat longitudinal direction in each position of the backrest support in front of the articulation point of the front coupling element is located on the base support.
  • the present synchronous mechanism is characterized in that it is particularly flat, so that a corresponding assembly requires very little space. This is true even if, for
  • a spring mechanism with one or more Spring elements is provided, since the spring mechanism can be designed such that the at least one spring element connects the coupling element with the base support or with the backrest support, without the addition of the already provided housing volume of the base support addition further additional space required. This is especially true when the spring element with the coupling element on the one hand and with the rear region of the base support or connected to the backrest support and thereby
  • the spring mechanism comprises means for adjusting the spring force of the at least one spring element such that the distance of the seen in chair longitudinal direction front end of the spring to the front transverse axis, ie to the connecting axis of the base support and coupling element , is changeable.
  • the effective lever arm which determines the action of the spring end and thus influences the pivoting resistance of the backrest support, namely the distance between the articulation point of the spring and the lever arm can be determined
  • Coupling element and the front transverse axis be extended or shortened.
  • the position of the spring element in the mechanics, in particular their inclination is changed, resulting in the result of the bias of
  • the adjustment of the spring force is preferably carried out such that no work against the spring force must be performed.
  • a "powerless" spring force adjustment are the
  • Adjusting means designed such that the variable-position front end of the spring is movable on a circular path with a substantially constant radius about the other, rear end of the spring. The bias of the spring element remains unchanged.
  • the adjusting means comprise a cam drive, which cooperates with a cam carrier cam follower with the variable-position spring end of the at least one
  • Spring element is connected and by a manual or motorized by the user movement of the cam carrier in Positions of different spring force is movable.
  • the use of a cam drive as adjusting means is advantageous because of the precisely defined by the predetermined curve slope movement curve of the spring end.
  • the adjusting means comprise a movement thread with a threaded spindle and with a threaded nut movably guided on the threaded nut, wherein the threaded nut is connected to the coupling element supported on the spring end of the at least one spring element and said spring end by a movement of the threaded nut in positions of different spring force is movable.
  • Fig. 1 is a side view of the synchronous mechanism (first
  • Fig. 2 is a partially sectioned side view of
  • Synchronous mechanism in the basic position ("hard” setting
  • Fig. 3 is a partially sectioned side view of
  • Synchronous mechanism in a maximum rearwardly pivoted position ("hard” setting
  • Fig. 4 is a partially sectioned side view of
  • Synchronous mechanism in the basic position ("soft" setting), a partially sectioned side view of
  • Synchronous mechanism in a maximum rearwardly pivoted position ("soft setting)
  • Fig. 6 is a first sectional side view of
  • Fig. 7 is a second sectional side view of
  • Fig. 8 is a first sectional side view of
  • Fig. 9 is a second sectional side view of
  • Synchronous mechanism in a plan view in the direction of the spindle axis.
  • the synchronous mechanism; 100 has a base support 1, which is set by means of a cone seat 2 on the upper end of a chair column 10 (see Fig. 1).
  • the synchronous mechanism comprises: 100 a substantially frame-shaped seat support 3 and a bifurcated in plan view
  • the cheeks 5 are arranged on both sides of the base support 1.
  • the seat support 3 is provided for receiving or mounting a preferably padded seat (not shown). The assembly takes place with the help of not shown
  • Backrest support 4 is not shown in detail
  • the backrest can with the
  • Backrest support 4 also be integrally connected.
  • the entire synchronous mechanism 100 is with respect to their
  • Synchronous mechanism 100 in a maximum rearwardly pivoted position of the backrest support 4th In the seen in chair longitudinal direction 14 rear portion 6 of the mechanics of a main pivot axis 11 of the
  • Synchronous mechanism 100 defining first transverse axis in
  • Pivoting direction 7 pivoting backrest support 4 on the one hand with the rear portion 9 of the base support 1 and on the other hand connected directly to the rear portion 25 of the seat support 3 hinged.
  • the backrest support 4 is hinged with its extending in the direction of the front seat area 8 cheek 5 directly to the base support 1 and thus about a fixed main pivot axis of the synchronous mechanism 100 defining the first (rear) transverse axis 11 in the pivoting direction 7 pivotally. With an upwardly extending driver 12 of the cheek 5 of the backrest support 4 is connected to the seat support 3 directly articulated.
  • Backrest support 4 from the basic position in a pivoted backward position is therefore always connected to a lowering S of the rear portion 25 of the seat support 3.
  • both axes of articulation 13, 15 are seen in the chair longitudinal direction 14 in front of the center of the cone seat 2.
  • the second hinge axis 15 seen in the chair longitudinal direction 14 behind the center of the cone seat 2, while the position of the first hinge axis 13 relative to the cone seat. 2
  • a rigidly connected to the backrest support 4, formed as an integral part of the backrest support 4 coupling element 16 is defined as symbolically represented in Fig. 1 with dotted line is.
  • the arrangement of the coupling element 16 immediately above the cone seat 2 contributes to an advantageous sequence of movement of the synchronous mechanism 100 at.
  • the front region 18 of the base support 1 is articulated to the front region 8 of the seat support 3.
  • a coupling element 21 is provided, on the one hand directly to the base support 1, namely about a second (front) transverse axis 19 pivotally, and on the other hand directly hinged to the seat support 3.
  • the rear coupling element 16 shows in the chair longitudinal direction 14 seen from the first transverse axis 11 in each case obliquely upwards and to the rear and the front coupling element 21 shows seen in chair longitudinal direction 14, starting from the second transverse axis 19 in each case obliquely upwards and forwards.
  • the joint axes 15, 23 at the articulation points of the seat support 3 in the vertical direction always extend above the articulation axes 13, 22, which are defined by the articulation on the base support 1.
  • the coupling elements 16, 21 are arranged in a V-shape with each other, with the imaginary extension lines of the coupling elements 16, 21 intersecting below the base support 1.
  • the relative movement of seat support 3 and backrest support 4 to each other is determined by the position of the four total by the ends of the two
  • Coupling elements 16, 21 extending, defined by the articulation points hinge axes 13, 15, 22, 23 determined.
  • the described pivoting mechanism ensures that the backrest support 4 can be pivoted with the backrest about the rear transverse axis 11 serving as the main pivot axis, in this case the first articulation axis 13, in the pivoting direction 7.
  • the pivoting movement of the backrest to the rear induces an immediate lowering S of the rear portion 25 of the seat support 3 back down and the front portion 8 of the seat support 3 performs a lifting movement H back to the top (see Fig. 1).
  • the mechanism has a spring mechanism for adjusting the pivoting resistance of the backrest. This comprises at least one spring element 30, see Fig. 2.
  • the spring element 30 exerts a spring force against the rearward Pivoting movement 7 of the backrest. This is the
  • Spring element 30 acted upon pivoting of the backrest support 4. Depending on the "hardness" of the spring element 30 so the synchronous movement (seat and backrest) takes place against a more or less large spring resistance.
  • a spring assembly provided with a centrally disposed helical compression spring 30, which on the one hand on a front abutment 31 and on the other hand on a rear abutment 37 by means of spring plates 32, 34 is supported (not shown in detail in all figures).
  • the spring 30, which is shown in detail alone in Fig. 2, surrounds it
  • the spring 30 on one side namely at its front end of the spring 28, charged. More specifically, the at least one spring element 30 with its one, viewed in the chair longitudinal direction 14 rear spring end 27 is directly connected to the backrest support 4 or the base support 1, namely at the pivot point 40 at or near the position of connecting these two components
  • Main pivot axis 11 of the mechanism 100 With its other, seen in the chair longitudinal direction 14 front spring end 28, the spring element 30 is connected to the coupling element 21 such that a movement of the backrest from a basic position in a pivoted backward position, an application of this front spring end 28 causes.
  • the front end of the spring 28 is to form a
  • the spring element 30 is a compression spring.
  • the connection point 42 of the spring end 28 with the coupling element 21 is located above the front transverse axis 19 and thus between the front transverse axis 19 and the articulation point 23 of the coupling element 21 on the seat support 3.
  • the connection point 42 of the spring 30 with the coupling element 21 is then seen in chair longitudinal direction 14 is always above and in front of the front transverse axis 19.
  • the coupling element 21 performs as a kind of link during a pivoting movement of the backrest or the seat hinged thereto a directed towards the backrest support 4 towards
  • Backrest support 4 or the base support 1 and the coupling element 21 clamped compression spring 30 is acted upon from the front.
  • the position of the front articulation point 42 of the spring element 30 on the coupling element 21 defines the length of a lever arm 36 to the front transverse axis 19 of the mechanism 100.
  • the spring mechanism comprises means for adjusting the spring force of the at least one spring element 30 by changing the position of the front spring end 28. For this purpose, the distance of the front spring end 28 is changed to the front transverse axis 19.
  • the adjustment means are configured such that the front spring end 28 is movable in a circular path of substantially constant radius about the rearward spring end 27 of the spring element 30.
  • the rearward spring end 27 remains positionally immutable during this adjustment.
  • the change in the position of the front spring end 28 takes place in the first embodiment of the invention described in connection with FIGS. 1 to 5 by means of a cam drive 43.
  • the cam drive 43 has a manually and / or motor-actuated, movably mounted on the coupling element 21, in particular rotatably mounted, preferably eccentric cam carrier 44, which cooperates with a scanning element serving as a cam roller 45, which coincides with the curve 46 of
  • Cam carrier 44 cooperates or is engaged.
  • the cam roller 45 runs on one side on the curve 46, to which it is pressed by the at least one spring element 30.
  • the cam roller 45 is connected to the front spring end 28.
  • the cam roller 45 is provided in the illustrated embodiment of the invention with a sliding block 51 and is guided on an open link 47 provided in the coupling element 21 (see FIG. 2) or is connected in another way to the coupling element 21.
  • the gate 47 is bent, namely circular executed such that the cam roller 45 and thus the front end of the spring 28 is movable on a circular path with a substantially constant radius about the other spring end 27.
  • the front end of the spring 28 of the spring element 30 is connected to the coupling element 21 by a bolt or other suitable for scanning the curve component to which the spring end 28 attached, for example, is mounted, guided in the coupling element 21 and stored.
  • a bolt or other suitable for scanning the curve component to which the spring end 28 attached for example, is mounted, guided in the coupling element 21 and stored.
  • the scanning component for example, the cam roller 45, in particular in a guide groove, a curved link or the like and is based on a defined, dependent on its position on the curve 46, the spring force of the spring element 30 determining position of the coupling element 21, wherein it from the Coupling element 21 associated front transverse axis 19 is spaced.
  • a suitable component for example in the form of a bolt, is used, on the one hand with an adjustable cam carrier 44, for example, the cam to cooperate and as cam follower 45 to scan the cam 46 of the cam 44, and at the same time on the other hand as a kind of sliding block act or cooperate with a shoe 51 or the like, which is supported on a sliding track, for example in the form of a curved link 47 on the coupling element 21.
  • an adjustable cam carrier 44 for example, the cam to cooperate and as cam follower 45 to scan the cam 46 of the cam 44, and at the same time on the other hand as a kind of sliding block act or cooperate with a shoe 51 or the like, which is supported on a sliding track, for example in the form of a curved link 47 on the coupling element 21.
  • Cams 44 are the local course of the curve 46 defining troughs 48, 49 are provided which at defined points of the curve 46 a sufficiently large self-locking, ie a sufficient resistance against slippage of the cam roller 45 on the curve 46, ensure. Thus, the cam roller 45 remains in place, even if to achieve the shortest possible adjustment in the setting of
  • Spring force of the spring element 30 is a cam carrier 44 is used, which has a curve 46 as steep as possible, ie a steep curve angle.
  • An advantage of the wells 48, 49 is that thereby a stepped adjustment of the spring force is possible, which is often considered advantageous from a user perspective, since the adjustment of the spring end with a more or less strong engagement of the cam roller 45 in the respective trough 48, 49 connected is, whereby the user receives a tactile feedback on a successfully completed adjustment.
  • it is also a version with continuous smooth edge of the curve possible. From the "hard” to the "soft” setting can be reached when the mounted in the coupling element 21 eccentric cam 44 is rotated in the direction of actuation 50.
  • the cam plate 44 is rotatably mounted about an axis of rotation 52 in the coupling element 21, wherein the axis of rotation 52 is located approximately centrally between the front transverse axis 19 and the articulation point 23 of the coupling element 21 on the seat support 3.
  • Linkage point 42 of the spring 30 at the same pivot angle of the backrest support 4 cover a greater distance. In other words, the spring travel is longer. For this reason, the spring 30 is compressed more. The swing resistance is harder. In this case, the spring 30 already at the beginning of the pivoting the greatest hardness, without the need for pivoting the backrest support 4 is necessary. At the same time starting from the transverse axis 19 perpendicular to the spring line of action 38 pointing effective lever arm 35 is the longest. The restoring torque acting on the mechanism in this setting with a pivoting of the backrest is maximum.
  • the cam follower 45 is located in the foremost well 49 of the curve 46.
  • the effective lever arm 35 is shorter, the spring travel and thus the pivoting resistance correspondingly lower.
  • the rotation of the cam carrier 44 in the actuating direction 50 takes place, for example, by means of a manually operable handle, for example with a rotary handle or a handwheel (not shown).
  • This handle is mounted on the coupling element 21 and moves with the coupling element 21, so performs as well as the coupling element 21 during pivoting of the backrest support 4, a pivoting movement 41 to the rear.
  • the cam carrier 44 can also be driven via levers, Bowden cables, etc.
  • a (electric) motor drive can be provided instead of a manual operation.
  • the cam carrier 44 is designed such that the cam roller 45 is forcibly guided on or in the curve 46 of the cam carrier 44.
  • the cam carrier 44 is designed such that the cam roller 45 is forcibly guided on or in the curve 46 of the cam carrier 44.
  • a trained as a spiral curve guide groove for the cam roller 45 Preferably, a trained as a spiral curve guide groove for the cam roller 45.
  • the adjustment can be made stepless in any case.
  • a large or small cam 46 can be used.
  • curve 46 can be used with a low or a steep slope.
  • the adjustment characteristic of the pivoting resistance can be set.
  • Adjusting means for adjusting the spring force instead of a Curve drive 43 now comes a movement thread 53 used.
  • the two embodiments do not differ or only insignificantly. Both embodiments have, as is clear, inter alia, by reference numerals, identical or in their function corresponding elements, so that is largely dispensed with by a completely repeated description of the interaction of the components.
  • not all elements are shown in FIGS. 6 to 9. For example, that part of the cheek 5 of the backrest support, which is connected to the main pivot axis 11 of the mechanism, not shown. The position of the main pivot axis 11 itself, however, is located.
  • Synchronous mechanism 101 in a maximum rearwardly pivoted position of the backrest support. It is again provided a spring arrangement with a centrally disposed helical compression spring 30 which is supported on the one hand on a front abutment 31 and on the other hand on a rear abutment 37 by means of spring plates 32, 34.
  • the spring 30 (only indicated in FIG. 6) encompasses guide rods 33 which have the spring plates 32, 34 at their respective ends.
  • the spring 30 Upon pivoting of the backrest support 4, the spring 30 on one side, namely at its front end of the spring 28, charged.
  • the rear spring end 27 is directly connected to the base support 1.
  • the spring element 30 With its front spring end 28, the spring element 30 is connected to the coupling element 21 such that a movement of the backrest from a basic position to a rearward pivoted position causes an actuation of this front spring end 28.
  • the front end of the spring 28 is again connected to the formation of a lever arm 36 spaced from the front transverse axis 19 with the coupling element 21.
  • the coupling element 21 performs as a kind of link during a pivoting movement of the backrest or the seat hinged thereto a directed towards the backrest support 4 towards
  • the spring force adjustment means are configured such that the forward spring end 28 is movable in a substantially constant radius circular path about the rearward spring end 27 of the spring element 30.
  • the rearward spring end 27 remains there during Adjustment positionally changeable.
  • the movement of the position of the front spring end 28 takes place here by means of a movement thread 53.
  • the movement thread 53 comprises a threaded spindle 55 and a threaded spindle 55 movably guided on the threaded nut 56.
  • the threaded nut 56 is with the spring end 28 of the at least one spring element 30 supported on the coupling element 21 is connected directly or indirectly.
  • the front spring end 28 is movable by a movement of the threaded nut 56 on the threaded spindle 55 in positions relative to the front transverse axis 19, which result in a different spring force.
  • the threaded spindle 55 is mounted on both sides at fixed bearing points 57, 58 within the coupling element 21, so that the threaded spindle 55 pivots with the coupling element 21. Even in the rearwardly pivoted state, as shown in FIGS. 8 and 9, the threaded nut 56 remains at its respective place on the threaded spindle 55, since a self-locking thread (trapezoidal thread) is used.
  • the threaded spindle 55 is rotatably mounted in the bearing points 57, 58. Upon rotation of the threaded spindle 55 (rotational movement), the threaded nut 56 on the threaded spindle 55 is moved up and down (linear movement). The threaded spindle 55 is manually and / or motor actuated.
  • the threaded nut 56 is connected in the illustrated embodiment of the invention with a shoe 54 and is guided on an opening provided in the coupling element 21 open link 47.
  • the gate 47 is bent, namely executed circular.
  • the threaded nut 56 on both sides in the transverse direction of the threaded nut 56 outstanding Bearing journals 60, on which the sliding shoe 54 is mounted, see Fig. 10.
  • the shoe 54 has for this purpose suitable bearings 61 for receiving the bearing pin 60.
  • the shoe 54 is hereby given an additional rotational degree of freedom.
  • the sliding shoe 54 can thus about the pivot axis 59 in the pivoting direction 63 relative to the
  • Threaded nut 56 can be pivoted to its sliding surface
  • the shoe 54 is decoupled from the threaded nut 56 with respect to this degree of freedom.
  • the sliding on the slide 47 sliding surface 62 of the shoe 54 opposite is a bearing surface
  • one at the lower end of the threaded spindle 55 with the spindle 55 is rotatably connected drive wheel 62, for example, gear
  • the drive wheel 62 can for this purpose, if necessary with the interposition of one or more suitable transmission or
  • cam carrier cam disc

Abstract

L'invention concerne un mécanisme synchrone; (100, 101) pour un mouvement interdépendant de l'assise et du dossier d'un siège de bureau, comportant un support de base (1) pouvant être monté sur une colonne du siège (10), un support d'assise (3) et un support de dossier (4), le support de dossier (4) pouvant aussi bien pivoter autour d'un premier axe transversal (11) avec le support de base (1) qu'être relié de manière articulée au support d'assise (3), et ledit support d'assise (3) étant relié de manière articulée au support de base (1) par un élément d'accouplement (21), l'élément d'accouplement (21) pouvant aussi bien pivoter autour d'un deuxième axe transversal (19) avec le support de base (1) qu'être relié de manière articulée au support d'assise (3), un mécanisme à ressort étant présent pour régler la résistance de pivotement du dossier, lequel mécanisme à ressort comprend au moins un élément élastique (30), et ledit au moins un élément élastique (30) s'appuyant, par une de ses extrémités (27) sur l'élément d'accouplement (21).
EP16703255.6A 2015-02-03 2016-02-03 Mecanisme synchrone Active EP3253255B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015101546.3A DE102015101546B4 (de) 2015-02-03 2015-02-03 Synchronmechanik
PCT/EP2016/000170 WO2016124328A1 (fr) 2015-02-03 2016-02-03 Mecanisme synchrone

Publications (2)

Publication Number Publication Date
EP3253255A1 true EP3253255A1 (fr) 2017-12-13
EP3253255B1 EP3253255B1 (fr) 2019-05-08

Family

ID=60239705

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16703255.6A Active EP3253255B1 (fr) 2015-02-03 2016-02-03 Mecanisme synchrone

Country Status (1)

Country Link
EP (1) EP3253255B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3741256A1 (fr) * 2019-05-21 2020-11-25 BOCK 1 GmbH & Co. KG Mécanique synchrone

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3741256A1 (fr) * 2019-05-21 2020-11-25 BOCK 1 GmbH & Co. KG Mécanique synchrone

Also Published As

Publication number Publication date
EP3253255B1 (fr) 2019-05-08

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