EP3253254B1 - Synchronized mechanism - Google Patents

Synchronized mechanism Download PDF

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Publication number
EP3253254B1
EP3253254B1 EP16702659.0A EP16702659A EP3253254B1 EP 3253254 B1 EP3253254 B1 EP 3253254B1 EP 16702659 A EP16702659 A EP 16702659A EP 3253254 B1 EP3253254 B1 EP 3253254B1
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EP
European Patent Office
Prior art keywords
spring
support
backrest
seat
cam
Prior art date
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Active
Application number
EP16702659.0A
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German (de)
French (fr)
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EP3253254A1 (en
Inventor
Hermann Bock
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Bock 1 GmbH and Co KG
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Bock 1 GmbH and Co KG
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Publication date
Priority claimed from DE102015101545.5A external-priority patent/DE102015101545A1/en
Application filed by Bock 1 GmbH and Co KG filed Critical Bock 1 GmbH and Co KG
Publication of EP3253254A1 publication Critical patent/EP3253254A1/en
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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 correlated seat-backrest movement of an office chair, with a base support that can be placed on a chair column, a seat support and a backrest support.
  • synchronous mechanism is understood to mean assemblies in the seat substructure of an office chair, which ensure kinematics that are coupled to one another and bring about a specific relative movement of the seat and backrest to one another.
  • the seat of the office chair which is usually provided with an upholstered seat, is mounted on the seat support.
  • the backrest support which extends backwards in the usual way from the actual synchronous mechanism, carries the backrest of the office chair on an outrigger that runs upwards.
  • Such self-adjusting synchro-mechanisms are not only often constructed in a comparatively complicated manner, they consist of a large number of interacting components and/or are complex in terms of
  • One object of the present invention is to provide a structurally simple, self-adjusting synchro-mechanism that requires little installation space. This problem is solved by a synchronous mechanism according to claim 1.
  • Advantageous embodiments of the invention are specified in the dependent claims.
  • a synchronous mechanism for a correlated seat-backrest movement of an office chair with a base support that can be placed on a chair column, a seat support and a backrest support, with the backrest support being pivotably connected to the base support and to the seat support both in a pivotable manner about a first transverse axis and wherein the seat support is articulated to the base support via a coupling element, wherein the coupling element is pivotally connected to the base support both about a second transverse axis and to the seat support at an articulation point, wherein a spring mechanism is provided for adjusting the pivoting resistance of the backrest, which spring mechanism has at least one spring element, wherein the at least one spring element is connected with its one spring end to the backrest support and with its other spring end not to the seat support but to the coupling element at a distance from the second transverse axis is such that movement of the backrest causes movement of both spring ends.
  • the at least one spring element is acted upon on both sides, only a very short spring deflection is required in order to achieve the desired spring effect. As a result, particularly little space is required for the construction of the mechanics. the The structural elements required can be accommodated in a comparatively small space, in particular by achieving a particularly low overall height of the mechanism.
  • the desired action on both sides of the at least one spring element is preferably achieved in that one spring end is connected to the backrest support at a distance from the first transverse axis.
  • the at least one spring element is preferably connected to the corresponding structural elements of the mechanism in such a way that the loading on both sides causes the distance between the two spring ends to change.
  • the loading on both sides preferably causes either a reduction or an increase in the distance between the two spring ends.
  • the spring mechanism preferably has means for adjusting the spring force of the at least one spring element such that the distance of one spring end from the first transverse axis and/or the distance of one spring end from the second transverse axis can be changed.
  • the effective lever arm which determines the loading of the spring ends and thus influences the pivoting resistance of the backrest support, can be lengthened or shortened.
  • the spring force is preferably adjusted in such a way that no work has to be performed against the spring force.
  • the setting means are designed in such a way that the position-changeable end of the spring can be moved around the other end of the spring on a circular path with a substantially constant radius. The bias of the spring element remains unchanged.
  • the adjustment means preferably comprise a cam drive whose cam roller interacting with a cam carrier is connected to a positionable spring end of the at least one spring element and can be moved into positions of different spring force by the user manually or motor-driven movement of the cam carrier.
  • a cam drive as the adjustment means is advantageous because the movement curve of the spring end can be precisely defined by the predetermined curve slope.
  • the present invention also reduces the number of coupling elements, in particular the number of elements connecting the seat support and backrest support, in order to achieve a particularly simple structural design of the mechanism without sacrificing the desired functionality of a synchronous mechanism.
  • the backrest support can be pivoted about a transverse axis and thus defines the main pivot axis of the mechanism with the base support as well as with the seat support, preferably directly, ie directly and without the interposition of an additional component, articulated.
  • the three main mechanical components, base support, seat support and backrest support are preferably connected to one another in such a way that a pivoting movement of the backrest from a basic position to a rearwardly pivoted position results in an immediate lowering movement of the rear area of the seat support, viewed in the longitudinal direction of the chair, backwards and downwards also an immediate lifting movement of the front area of the seat support seen in the longitudinal direction of the chair backwards and upwards is induced.
  • the rear area of the seat is lowered when the backrest is pivoted into its rearwardly pivoted position, while the front area of the seat is raised.
  • the lowering of the rear seat area takes place immediately each time the basic position is left, without the rear seat area initially being lifted.
  • the basic position is that position in which the backrest is not pivoted backwards.
  • the seat support is lowered in its rear area and at the same time the front area of the seat support is raised, the seat is carried synchronously in a defined relationship to the backrest and the seat surface is tilted. This results in the desired synchronous effect, in which the angle of the seat support changes to the backrest support.
  • the weight of the user has a direct impact on the pivoting resistance felt by the user.
  • pivoting a light user has to overcome a significantly lower pivoting resistance than a heavy user.
  • every user experiences the same "felt" resistance when pivoting the backrest.
  • the special synchronous movement of the mechanism according to the invention is preferably achieved in a particularly simple manner in that a coupling element designed as an integral part of the backrest support is defined by the positions of the pivot points of the backrest support on the base support on the one hand and on the seat support on the other hand.
  • a coupling element that can be freely pivoted on both sides is no longer required between the backrest support and the seat support.
  • the backrest support itself serves as a coupling element.
  • a particularly suitable coupling geometry and a synchronous movement resulting therefrom is achieved in a preferred embodiment of the invention in that the pivot point of the backrest support on the seat support seen in the longitudinal direction of the seat in every position of the backrest support behind the pivot point of the backrest support on the base support and the pivot point of the front coupling element on the seat support is seen in the longitudinal direction of the seat in every position of the backrest support in front of the pivot point of the front coupling element on the base support.
  • This is preferably supported in that the front coupling element is connected to the seat support via a pure rotary joint and not via a combined rotary/sliding joint.
  • the present synchronous mechanism is characterized in that it is particularly flat, so that a corresponding assembly requires very little space.
  • a particularly high level of seating comfort is achieved in an elegant way in the smallest of spaces without the so-called "shirt pulling effect" and without having to resort to complex and expensive constructive solutions.
  • the synchronous mechanism 100 has a base support 1, which is attached to the upper end of a chair column 10 by means of a cone mount 2 (see 1 ) is set.
  • the synchronizing mechanism 100 comprises an essentially frame-shaped seat support 3 and a backrest support 4 which is fork-shaped in plan view and whose cheeks 5 are arranged on both sides of the base support 1 .
  • the seat support 3 is provided for receiving or mounting a preferably upholstered seat (not shown).
  • the assembly is done with the help of fasteners not shown in the usual way.
  • a backrest not shown in detail, is attached to the backrest support 4, the height of which is adjustable in modern office chairs.
  • the backrest can also be connected in one piece to the backrest support 4 .
  • the entire synchronizing mechanism 100 has a mirror-symmetrical structure with respect to its central longitudinal plane. In this respect, the following description is always based on construction elements of the actual pivoting mechanism that are present in pairs on both sides.
  • the backrest support 4 is directly articulated to the rear area 9 of the base support 1 and to the rear area 25 of the seat support 3 .
  • the backrest support 4 is hinged directly to the base support 1 with its cheek 5 extending in the direction of the front seat area 8 and can therefore be pivoted in the pivoting direction 7 about a first (rear) transverse axis 11 that defines the fixed main pivoting axis of the synchronous mechanism 100.
  • the backrest support 4 is directly articulated to the seat support 3 with an upwardly extending driver 12 of the cheek 5 .
  • the first articulation axis 13 defined by the articulation of the backrest support 4 on the base support 1 is arranged in front of the second articulation axis 15 defined by the articulation of the backrest support 4 on the seat support 3 in the longitudinal direction 14 of the chair.
  • the second joint axis 15 is offset only slightly to the rear.
  • a zenith position directly above the first hinge axis 13 cannot be achieved. Pivoting the backrest support 4 out of the basic position into a rearwardly pivoted position is therefore always associated with a lowering movement S of the rear area 25 of the seat support 3 .
  • both joint axes 13, 15 are located in front of the center of the cone mount 2, seen in the longitudinal direction 14 of the chair.
  • the second joint axis 15 is located behind the center of the cone mount 2, seen in the longitudinal direction 14 of the chair, while the position of the first Joint axis 13 relative to the cone mount 2 is unchangeable.
  • the positions of the pivot points of the backrest support 4 on the base support 1 on the one hand and on the seat support 3 on the other hand define a coupling element 16 which is rigidly connected to the backrest support 4 and is designed as an integral part of the backrest support 4, as is shown in Fig 1 is shown symbolically with a dot-dash line.
  • the coupling element 16 consists exclusively of a part of the cheek 5.
  • the arrangement of the coupling element 16 directly above the cone receptacle 2 contributes to an advantageous sequence of movements of the synchronous mechanism 100.
  • the front area 18 of the base support 1 is connected in an articulated manner to the front area 8 of the seat support 3 .
  • a coupling element 21 is provided, which on the one hand is articulated directly on the base support 1, specifically about a second (front) transverse axis 19, and on the other hand is articulated directly on the seat support 3.
  • the front transverse axis 19, like the rear transverse axis 11, is stationary with respect to the base support 1 and is therefore fixed, and is therefore not moved when the backrest support 4 is pivoted.
  • the articulation point of the coupling element 21 on the base support 1 and thus the third articulation axis 22 is located behind the articulation point of the coupling element 21 on the seat support 3 and thus behind the fourth articulation axis 23, viewed in the longitudinal direction 14 of the chair.
  • the rear coupling element 16, viewed in the longitudinal direction 14 of the chair always points obliquely upwards and backwards, starting from the first transverse axis 11, and the front coupling element 21, viewed in the longitudinal direction 14 of the chair, starting from the second transverse axis 19, always points obliquely upwards and forwards.
  • the coupling elements 16, 21 are arranged in a V-shape relative to one another, 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 one another is determined by the position of the four joint axes 13, 15, 22, 23 that run through the ends of the two coupling elements 16, 21 and are defined by the pivot points.
  • the pivoting mechanism described ensures that the backrest support 4 with the backrest can be pivoted in the pivoting direction 7 about the rear transverse axis 11 serving as the main pivoting axis, here the first joint axis 13 .
  • the backwards pivoting movement of the backrest induces an immediate lowering movement S of the rear area 25 of the seat support 3 backwards and downwards and the front area 8 of the seat support 3 performs a lifting movement H backwards and upwards (see Fig 1 ).
  • the seat support 3 is simultaneously displaced backwards, while the base support 1 with the pivot bearings 13, 22 and their transverse axes 11 remains fixed in position.
  • the mechanism 100 has a spring mechanism for adjusting the pivoting resistance of the backrest.
  • This includes at least one spring element 30, see 2 .
  • the spring element 30 exerts a spring force against the backward pivoting movement 7 of the backrest.
  • the spring element 30 is acted upon when the backrest support 4 pivots.
  • the synchronous movement (seat and backrest) takes place against a greater or lesser spring resistance.
  • a spring arrangement is provided with a centrally arranged helical compression spring 30, which is supported on one side on a front abutment 31 and on the other side on a rear abutment 37 with the aid of spring plates 32, 34 (not shown in detail in all figures).
  • the spring 30, which is in detail alone in 2 is shown, encompasses guide rods 33, which have the spring plates 32, 34 at their respective ends.
  • the spring 30 When the backrest support 4 pivots, the spring 30 is loaded on both sides. More precisely, the at least one spring element 30 is connected with its one rear spring end 27, seen in the longitudinal direction 14 of the chair, directly to the backrest support 4 and with its other, front spring end 28, seen in the longitudinal direction 14 of the chair, either directly with the seat support 3 or directly with the coupling element 21 that a movement of the backrest from a basic position to a rearwardly pivoted position causes a simultaneous movement of both spring ends 27, 28.
  • the rear end of the spring 27 is used to form a rear end that is variable in length in the illustrated embodiment
  • Lever arm 35 is connected to the backrest support 4 at a distance from the first transverse axis 11 .
  • the spring element 30 is a compression spring, as shown in the figures, this connection point 40 is located below the first transverse axis 11.
  • the rear end 27 of the spring element 30 is connected to the base support 2 via the pivot point 11 also extending arm 20 of the cheek 5 is articulated.
  • the cheek 5 extending in the direction of the front edge 8 of the seat is lengthened obliquely forwards and downwards beyond the pivot point 11, as a result of which a lever arm 35 pivoting with the backrest support 4 is formed.
  • the connection point 40 of the spring 30 with the backrest support 4 is then always seen in the longitudinal direction 14 of the chair below and in front of the rear transverse axis 11.
  • connection point 40 would be located above the first transverse axis 11, namely between the two pivot points 13, 15 of the backrest support 4 on the base support 1 and seat support 3.
  • the front spring end 28 is positioned at a distance from the front transverse axis 19 to form a front lever arm 36, which is of constant length in the illustrated embodiment, namely either connected to the seat support 3, in particular to the front region 8 of the seat support 3, preferably at the pivot point 23 of the coupling element 21 on the seat support 3, or, as shown, with the coupling element 21.
  • the spring element 30 is a compression spring, as shown in the figures, this connection point 42 is located above the second transverse axis 19, namely between the two pivot points 22, 23 of the coupling element 21 to the base support 1 and seat support 3, so that the connection point 42 of the spring 30 with the coupling element 21 seen in the longitudinal direction 14 of the chair is always above and in front of the front transverse axis 19 .
  • Coupling element 21, acting as a kind of link performs a pivoting movement 29 directed towards backrest support 4 when the backrest or the seat articulated thereon pivots, which interacts with pivoting movement 41 of lever arm 20 of the backrest support in such a way that a gap between backrest support 4 and the Coupling element 21 clamped compression spring 30 is simultaneously compressed from both sides.
  • connection point of the spring with the coupling element 21 would have to be below and behind the second transverse axis 19 seen in the longitudinal direction 14 of the chair, for which purpose the coupling element 21 should be downwards, over the pivot point 22 of the coupling element 21 on the base support 1 addition, would have to be extended.
  • the two spring ends 27, 28 are acted upon in such a way that the distance between the two spring ends 27, 28 from one another changes. If the spring element used is a compression spring 30, the distance between the two spring ends 27, 28 is reduced from one another. In the case of a tension spring (not shown), the loading of both spring ends 27, 28 leads to an increase in the distance between the two spring ends 27, 28.
  • the position of the rear pivot point 40 of the spring element 30 on the backrest support 4 thus defines the length of a lever arm 35 up to the main pivot axis 11 of the mechanism 100.
  • the arm 35 is pivoted forward in the pivoting direction 41, whereby the rear end of the spring 27 is acted upon.
  • the position of the front end of the spring 28, which is articulated on the coupling 21 or on the seat support 3 also changes. Since this seat support 3 also performs a horizontal displacement backwards in addition to a tilting movement backwards and downwards, the result is that the compression spring 30 is acted upon on both sides.
  • the spring ends 27, 28 are connected to components, more precisely articulated to components which, when the backrest support 4 is pivoted, pivot in relation to one another in such a way that the spring ends 27, 28 move in opposite directions, but in any case move in such a way that their Movement to change the distance between the spring ends 27, 28 contribute to each other, whereby a greater spring effect can be achieved.
  • the spring 30 is preferably arranged in such a way and the connection of the spring 30 to the backrest support 4 is preferably carried out in such a way that the line of action of the spring 30 is essentially perpendicular to the lever arm 35 in the basic position.
  • the spring mechanism includes means for adjusting the spring force of the at least one spring element 30 by changing the position of at least one of the two spring ends 27, 28 and thus the distance between the two spring ends 27, 28.
  • the figures show an adjustment of the rear end of the spring 27. For this purpose, the removal of the rear end of the spring 27 changed to the first transverse axis 11. If the front end of the spring 28 (not shown) is adjusted, the distance between the front end of the spring 28 and the second transverse axis 19 would be changed accordingly. Also possible is a preferably simultaneous adjustment of the position of both spring ends 27, 28 in order to increase the adjustment effect with the same adjustment path.
  • the setting means are designed in such a way that the positionable spring end 27 to be adjusted can be moved around the other spring end 28 of the spring element 30 on a circular path with a substantially constant radius. If both spring ends 27, 28 are not adjusted at the same time, the other spring end 28 remains in a fixed position during this adjustment.
  • the position of the spring end 27, 28 is preferably changed by means of a cam drive 43.
  • the cam drive 43 has a manually and/or motor-operated, movably mounted, in particular rotatably mounted, preferably eccentric cam carrier 44 on the backrest support 4, which is equipped with a scanning element
  • Cam roller 45 cooperates, which cooperates with the curve 46 of the cam carrier 44 or is in engagement.
  • the cam carrier 44 is designed as a cam disc
  • the cam roller 45 runs on one side, as shown, on the cam 46 against which it is pressed by the at least one spring element 30 .
  • the cam roller 45 is connected to the rear end of the spring 27 or, if the front end of the spring 28 (not shown) is adjusted, to the latter.
  • the cam roller 45 and thus the spring end 27, 28 attached there can be moved into positions relative to the first transverse axis 11 which have different spring forces have as a consequence.
  • the cam roller 45 is provided with a sliding shoe 51 and lies in a slot 47 provided in the backrest support 4 or in the coupling element 21 or is connected in some other way to the backrest support 4 or when the front spring end is adjusted 28 (not shown) connected to the coupling element 21.
  • the elongated hole 47 is curved, namely circular in shape, in such a way that the cam roller 45 and thus the rear end of the spring 27 can be moved around the other end of the spring 28 on a circular path with a substantially constant radius.
  • variable-position spring end 27, 28 of the spring element 30 is connected to the relevant structural element (backrest support 4 or coupling element 21) by a bolt or another component suitable for scanning the curve 46, to which the spring end 27, 28 is fastened, e.g. is guided or stored directly or indirectly in this structural element 4, 21.
  • the scanning component for example the cam roller 45, lies in particular in a curved guide groove, a guide slot or the like and is supported at a defined position of the structural element 4 that depends on its position on the cam 46 and determines the spring force of the spring element 30. 21, wherein it is spaced apart from the fixed transverse axis 11, 19 associated with this structural element 4, 21.
  • a suitable component for example in the form of a bolt, is used in order on the one hand to interact with an adjustable cam carrier 44, for example the cam disc, and to scan the cam 46 of cam disc 44 as cam roller 45, and on the other hand to act as a type of sliding shoe 51 to act or interact with a shoe or the like, which is on a slide, for example in the form of a guide groove or a curved Slot 47 on the backrest support 4 (with an adjustability of the rear spring end 27) or on the coupling element 21 (with an adjustability of the front spring end 28).
  • an adjustable cam carrier 44 for example the cam disc
  • cam 46 of cam disc 44 as cam roller 45
  • a type of sliding shoe 51 to act or interact with a shoe or the like, which is on a slide, for example in the form of a guide groove or a curved Slot 47 on the backrest support 4 (with an adjustability of the rear spring end 27) or on the coupling element 21 (with an adjustability of the front spring end 28).
  • cam roller 45 On the edge of the cam disk 44 that defines the course of the curve 46, there are troughs 48, 49 that determine the local course of the curve 46 curve 46, ensure.
  • the cam roller 45 thus remains in place, even if, in order to achieve the shortest possible adjustment path when setting the spring force of the spring element 30, a cam carrier 44 is used which has a curve 46 with the steepest possible rise, i.e. a steep curve angle.
  • troughs 48, 49 allow the spring force to be adjusted in stages, which is often seen as advantageous from the user's point of view, since the adjustment of the spring end involves the cam roller 45 engaging to a greater or lesser extent in the respective trough 48, 49 is connected, whereby the user receives tactile feedback about a successfully completed adjustment process.
  • an embodiment with a continuously smooth curve edge is also possible.
  • the cam carrier 44 is rotated in the actuation direction 50, for example, by means of a manually operable handle, for example a rotary handle or a handwheel (not shown).
  • This handle is mounted on the backrest support 4, with the axis of rotation of the handwheel coinciding with the rear transverse axis 11.
  • the cam carrier 44 can also be driven via levers, Bowden cables, etc.
  • An (electric) motor drive can also be provided instead of manual actuation.
  • the cam carrier 44 is designed in such a way that the cam roller 45 is positively guided on or in the cam 46 of the cam carrier 44 .
  • the cam carrier 44 preferably has a guide groove designed as a spiral cam for the cam roller 45 . In this case, the adjustment can always be stepless.
  • a large or small cam disk 44 can be used. Also may vary desired size, a curve 46 can be used with a low or a steep slope. Likewise, the adjustment characteristic of the pivoting resistance can be adjusted by the selection of the curve 46, in particular by the decision as to whether a curve 46 with a constant or variable slope is used.
  • the spring force setting described by changing the position of the rear spring end 27 can also be used accordingly for the front spring end 28 .
  • a suitable guide for example an arcuate slot, is provided in the coupling element 21 for a cam roller 45 connected to the front spring end 28 .

Description

Die Erfindung betrifft eine Synchronmechanik für eine korrelierte Sitz-Rückenlehnen-Bewegung eines Bürostuhles, mit einem auf einer Stuhlsäule plazierbaren Basisträger, einem Sitzträger und einem Rückenlehnenträger.The invention relates to a synchronous mechanism for a correlated seat-backrest movement of an office chair, with a base support that can be placed on a chair column, a seat support and a backrest support.

Unter der Bezeichnung "Synchronmechanik" werden Baugruppen im Sitzunterbau eines Bürostuhles verstanden, die für eine miteinander gekoppelte, eine bestimmte Relativbewegung von Sitz- und Rückenlehne zueinander mit sich bringende Kinematik sorgen. Auf dem Sitzträger ist der in aller Regel mit einer gepolsterten Sitzfläche versehene Sitz des Bürostuhles montiert. Der Rückenlehnenträger, der sich in gängiger Weise von der eigentlichen Synchronmechanik nach hinten erstreckt, trägt an einem nach oben verlaufenden Ausleger die Rückenlehne des Bürostuhles.The term "synchronous mechanism" is understood to mean assemblies in the seat substructure of an office chair, which ensure kinematics that are coupled to one another and bring about a specific relative movement of the seat and backrest to one another. The seat of the office chair, which is usually provided with an upholstered seat, is mounted on the seat support. The backrest support, which extends backwards in the usual way from the actual synchronous mechanism, carries the backrest of the office chair on an outrigger that runs upwards.

Es ist bekannt, bestimmte Arten von Synchronmechaniken derart aufzubauen, daß der Benutzer des Bürostuhles sich durch eine Belastung der Rückenlehne selbst nach oben hebt. Mit anderen Worten arbeitet der Benutzer beim Betätigen der Synchronmechanik durch Zurückdrücken der Rückenlehne gegen sein eigenes, auf dem Sitz aufliegendes Gewicht. Der gewünschte Schwenkwiderstand stellt sich somit quasi selbsttätig aufgrund des Gewichtes des Benutzers ein. Eine bekannnte Synchronmechanik ist beispielsweise in der GB2068717 beschrieben.It is known to construct certain types of synchronous mechanisms in such a way that the user of the office chair lifts himself up by loading the backrest. In other words, when the synchronous mechanism is actuated, the user works by pushing back the backrest against his own weight resting on the seat. The desired pivoting resistance is thus adjusted almost automatically based on the weight of the user. A well-known synchronous mechanism is, for example, in GB2068717 described.

Solche selbsteinstellenden Synchronmechaniken sind nicht nur oft vergleichsweise kompliziert aufgebaut, bestehen aus einer Vielzahl zusammenwirkender Bauteile und/oder sind aufwendig inSuch self-adjusting synchro-mechanisms are not only often constructed in a comparatively complicated manner, they consist of a large number of interacting components and/or are complex in terms of

BESTÄTIGUNGSKOPIECONFIRMATION COPY

ihrer Montage, sondern beanspruchen oft auch einen vergleichsweise großen Bauraum.their assembly, but often also require a comparatively large amount of space.

Eine Aufgabe der vorliegenden Erfindung ist es, eine konstruktiv einfache selbsteinstellende Synchronmechanik bereitzustellen, die einen geringen Bauraum benötigt. Diese Aufgabe wird durch eine Synchronmechanik nach Anspruch 1 gelöst. Vorteilhafte Ausführungen der Erfindung sind in den Unteransprüchen angegeben.One object of the present invention is to provide a structurally simple, self-adjusting synchro-mechanism that requires little installation space. This problem is solved by a synchronous mechanism according to claim 1. Advantageous embodiments of the invention are specified in the dependent claims.

Danach ist eine Synchronmechanik für eine korrelierte Sitz-Rückenlehnen-Bewegung eines Bürostuhles vorgesehen, mit einem auf einer Stuhlsäule plazierbaren Basisträger, einem Sitzträger und einem Rückenlehnenträger, wobei der Rückenlehnenträger sowohl um eine erste Querachse schwenkbar mit dem Basisträger als auch mit dem Sitzträger gelenkig verbunden ist und wobei der Sitzträger über ein Koppelelement mit dem Basisträger gelenkig verbunden ist, wobei das Koppelelement sowohl um eine zweite Querachse schwenkbar mit dem Basisträger als auch an einem Anlenkpunkt mit dem Sitzträger gelenkig verbunden ist, wobei ein Federmechanismus zum Einstellen des Schwenkwiderstandes der Rückenlehne vorgesehen ist, welcher Federmechanismus wenigstens ein Federelement aufweist, wobei das wenigstens eine Federelement mit seinem einen Federende mit dem Rückenlehnenträger und mit seinem anderen Federende nicht mit dem Sitzträger, sondern mit dem Koppelelement beabstandet von der zweiten Querachse verbunden ist derart, daß eine Bewegung der Rückenlehne eine Bewegung beider Federenden hervorruft.Accordingly, a synchronous mechanism for a correlated seat-backrest movement of an office chair is provided, with a base support that can be placed on a chair column, a seat support and a backrest support, with the backrest support being pivotably connected to the base support and to the seat support both in a pivotable manner about a first transverse axis and wherein the seat support is articulated to the base support via a coupling element, wherein the coupling element is pivotally connected to the base support both about a second transverse axis and to the seat support at an articulation point, wherein a spring mechanism is provided for adjusting the pivoting resistance of the backrest, which spring mechanism has at least one spring element, wherein the at least one spring element is connected with its one spring end to the backrest support and with its other spring end not to the seat support but to the coupling element at a distance from the second transverse axis is such that movement of the backrest causes movement of both spring ends.

Wegen der beidseitigen Beaufschlagung des wenigstens einen Federelements wird nur ein sehr kurzer Federweg benötigt, um die gewünschte Federwirkung zu erzielen. Hierdurch wird für den Aufbau der Mechanik besonders wenig Platz benötigt. Die erforderlichen Konstruktionselemente können auf vergleichsweise kleinem Raum, insbesondere unter Verwirklichung einer besonders geringen Bauhöhe der Mechanik, untergebracht werden.Because the at least one spring element is acted upon on both sides, only a very short spring deflection is required in order to achieve the desired spring effect. As a result, particularly little space is required for the construction of the mechanics. the The structural elements required can be accommodated in a comparatively small space, in particular by achieving a particularly low overall height of the mechanism.

Die gewünschte beidseitige Beaufschlagung des wenigstens einen Federelements wird vorzugsweise dadurch erreicht, daß das eine Federende beabstandet von der ersten Querachse mit dem Rückenlehnenträger verbunden ist.The desired action on both sides of the at least one spring element is preferably achieved in that one spring end is connected to the backrest support at a distance from the first transverse axis.

Dies dient zur Ausbildung einer Anzahl Hebelarme, mit deren Hilfe bei einer Verschwenkung des Rückenlehnenträgers nach hinten, wie sie durch ein Anlehnen des Benutzers an die Rückenlehne hervorgerufen wird, die beidseitige Beaufschlagung hervorgerufen wird.This serves to form a number of lever arms, with the help of which, when the backrest support is pivoted backwards, as is caused by the user leaning against the backrest, the loading on both sides is brought about.

Vorzugsweise ist das wenigstens eine Federelement derart mit den entsprechenden Konstruktionselementen der Mechanik verbunden, daß die beidseitige Beaufschlagung dazu führt, daß sich der Abstand der beiden Federenden zueinander verändert. Vorzugsweise bewirkt dabei die beidseitige Beaufschlagung, je nachdem, ob es sich bei dem wenigstens einen Federelement um eine Druckfeder oder eine Zugfeder handelt, entweder eine Verringerung oder eine Vergrößerung des Abstandes der beiden Federenden zueinander. Vorzugsweise weist der Federmechanismus Mittel zur Einstellung der Federkraft des wenigstens einen Federelements auf derart, daß die Entfernung eines Federendes zu der ersten Querachse und/oder die Entfernung eines Federendes zu der zweiten Querachse veränderbar ist. Hierdurch kann der die Beaufschlagung der Federenden bestimmende und damit den Schwenkwiderstand des Rückenlehnenträgers beeinflussende wirksame Hebelarm verlängert oder verkürzt werden. Bei der Einstellung der Federkraft wird die Lage des Federelements in der Mechanik, insbesondere deren Neigung verändert, wodurch sich im Ergebnis die Vorspannung der Gesamtmechanik ändert.The at least one spring element is preferably connected to the corresponding structural elements of the mechanism in such a way that the loading on both sides causes the distance between the two spring ends to change. Depending on whether the at least one spring element is a compression spring or a tension spring, the loading on both sides preferably causes either a reduction or an increase in the distance between the two spring ends. The spring mechanism preferably has means for adjusting the spring force of the at least one spring element such that the distance of one spring end from the first transverse axis and/or the distance of one spring end from the second transverse axis can be changed. As a result, the effective lever arm, which determines the loading of the spring ends and thus influences the pivoting resistance of the backrest support, can be lengthened or shortened. When adjusting the spring force, the position of the spring element in the mechanism, in particular their Inclination changes, which changes the preload of the overall mechanics as a result.

Das Einstellen der Federkraft erfolgt dabei vorzugsweise derart, daß keine Arbeit gegen die Federkraft verrichtet werden muß. Für eine solche "kraftlose" Federkrafteinstellung sind die Einstellmittel derart ausgebildet, daß das lageveränderliche Federende auf einer Kreisbahn mit im wesentlichen konstanten Radius um das andere Federende bewegbar ist. Die Vorspannung des Federelements bleibt dabei unverändert.The spring force is preferably adjusted in such a way that no work has to be performed against the spring force. For such a "forceless" spring force setting, the setting means are designed in such a way that the position-changeable end of the spring can be moved around the other end of the spring on a circular path with a substantially constant radius. The bias of the spring element remains unchanged.

Vorzugsweise umfassen die Einstellmittel einen Kurventrieb, dessen mit einem Kurventräger zusammenwirkende Kurvenrolle mit einem lageveränderlichen Federende des wenigstens einen Federelements verbunden ist und durch eine durch den Benutzer manuell oder motorisch bewirkte Bewegung des Kurventrägers in Positionen unterschiedlicher Federkraft bewegbar ist. Die Verwendung eines Kurventriebs als Einstellmittel ist wegen der durch die vorgegebene Kurvensteigung exakt definierbaren Bewegungskurve des Federendes vorteilhaft.The adjustment means preferably comprise a cam drive whose cam roller interacting with a cam carrier is connected to a positionable spring end of the at least one spring element and can be moved into positions of different spring force by the user manually or motor-driven movement of the cam carrier. The use of a cam drive as the adjustment means is advantageous because the movement curve of the spring end can be precisely defined by the predetermined curve slope.

Mit der vorliegenden Erfindung wird außerdem die Anzahl der Koppelelemente, insbesondere die Anzahl der Sitzträger und Rückenlehnenträger verbindenden Elemente, verringert, um dadurch einen besonders einfachen konstruktiven Aufbau der Mechanik zu erreichen, ohne auf die gewünschte Funktionalität einer Synchronmechanik zu verzichten. Aus diesem Grund ist der Rückenlehnenträger sowohl um eine Querachse schwenkbar und damit die Hauptschwenkachse der Mechanik definierend mit dem Basisträger als auch mit dem Sitzträger vorzugsweise unmittelbar, d.h. direkt und ohne Zwischenschaltung eines zusätzlichen Bauteils, gelenkig verbunden.The present invention also reduces the number of coupling elements, in particular the number of elements connecting the seat support and backrest support, in order to achieve a particularly simple structural design of the mechanism without sacrificing the desired functionality of a synchronous mechanism. For this reason, the backrest support can be pivoted about a transverse axis and thus defines the main pivot axis of the mechanism with the base support as well as with the seat support, preferably directly, ie directly and without the interposition of an additional component, articulated.

Die Anbindung der drei Hauptkomponenten der Mechanik, Basisträger, Sitzträger und Rückenlehnenträger, untereinander ist vorzugsweise derart ausgeführt, daß eine Schwenkbewegung der Rückenlehne von einer Grundstellung sowohl in eine nach hinten verschwenkte Stellung eine sofortige Absenkbewegung des in Stuhllängsrichtung gesehen hinteren Bereichs des Sitzträgers nach hinten unten als auch eine sofortige Anhebebewegung des in Stuhllängsrichtung gesehen vorderen Bereichs des Sitzträgers nach hinten oben induziert.The three main mechanical components, base support, seat support and backrest support, are preferably connected to one another in such a way that a pivoting movement of the backrest from a basic position to a rearwardly pivoted position results in an immediate lowering movement of the rear area of the seat support, viewed in the longitudinal direction of the chair, backwards and downwards also an immediate lifting movement of the front area of the seat support seen in the longitudinal direction of the chair backwards and upwards is induced.

Anstelle des sonst üblichen Anhebens des gesamten Sitzes wird also der hintere Bereich des Sitzes bei einem Verschwenken der Rückenlehne in ihre nach hinten verschwenkte Stellung abgesenkt, während der vordere Bereich des Sitzes angehoben wird. Das Absenken des hinteren Sitzbereiches erfolgt dabei unmittelbar bei jedem Verlassen der Grundstellung, ohne daß etwa zunächst eine Anhebebewegung des hinteren Sitzbereiches erfolgt. Als Grundstellung wird dabei diejenige Stellung angesehen, in der die Rückenlehne nicht nach hinten verschwenkt ist.Instead of the otherwise customary raising of the entire seat, the rear area of the seat is lowered when the backrest is pivoted into its rearwardly pivoted position, while the front area of the seat is raised. The lowering of the rear seat area takes place immediately each time the basic position is left, without the rear seat area initially being lifted. The basic position is that position in which the backrest is not pivoted backwards.

Dadurch, daß der Sitzträger in seinem rückwärtigen Bereich abgesenkt wird und gleichzeitig ein Anheben des vorderen Bereichs des Sitzträgers erfolgt, erfolgt ein synchrones Mitführen des Sitzes in einem definierten Verhältnis zur Rückenlehne sowie ein Neigen der Sitzfläche. Hierdurch gibt sich der gewünschte Synchroneffekt, bei dem sich der Winkel des Sitzträgers zum Rückenlehnenträger ändert.Because the seat support is lowered in its rear area and at the same time the front area of the seat support is raised, the seat is carried synchronously in a defined relationship to the backrest and the seat surface is tilted. This results in the desired synchronous effect, in which the angle of the seat support changes to the backrest support.

Das Gewicht des Benutzers wirkt sich direkt auf den von dem Benutzer spürbaren Schwenkwiderstand aus. Ein leichter Benutzer muß bei einem Verschwenken einen deutlich geringeren Schwenkwiderstand überwinden, als ein schwerer Benutzer. Subjektiv ergibt sich für jeden Benutzer der gleiche "gefühlte" Widerstand beim Verschwenken der Rückenlehne.The weight of the user has a direct impact on the pivoting resistance felt by the user. When pivoting, a light user has to overcome a significantly lower pivoting resistance than a heavy user. Subjectively, every user experiences the same "felt" resistance when pivoting the backrest.

Die spezielle Synchronbewegung der erfindungsgemäßen Mechanik wird vorzugsweise auf besonders einfache Art und Weise dadurch erreicht, daß durch die Positionen der Anlenkpunkte des Rückenlehnenträgers an dem Basisträger einerseits und an dem Sitzträger andererseits ein als integraler Bestandteil des Rückenlehnenträgers ausgebildetes Koppelelement definiert ist. Anders ausgedrückt ist zwischen Rückenlehnenträger und Sitzträger kein beidseitig frei verschwenkbares Koppelelement mehr erforderlich. Statt dessen dient der Rückenlehnenträger selbst als Koppelelement.The special synchronous movement of the mechanism according to the invention is preferably achieved in a particularly simple manner in that a coupling element designed as an integral part of the backrest support is defined by the positions of the pivot points of the backrest support on the base support on the one hand and on the seat support on the other hand. In other words, a coupling element that can be freely pivoted on both sides is no longer required between the backrest support and the seat support. Instead, the backrest support itself serves as a coupling element.

Eine besonders geeignete Koppelgeometrie und eine daraus resultierende Synchronbewegung wird in einer bevorzugten Ausführungsform der Erfindung dadurch erzielt, daß der Anlenkpunkt des Rückenlehnenträgers an dem Sitzträger in Sitzlängsrichtung gesehen in jeder Stellung des Rückenlehnenträgers hinter dem Anlenkpunkt des Rückenlehnenträgers an dem Basisträger und der Anlenkpunkt des vorderen Koppelelementes an dem Sitzträger in Sitzlängsrichtung gesehen in jeder Stellung des Rückenlehnenträgers vor dem Anlenkpunkt des vorderen Koppelelementes an dem Basisträger liegt. Vorzugsweise wird dies dadurch unterstützt, daß das vordere Koppelelement mit dem Sitzträger über ein reines Drehgelenk und nicht etwa über in kombiniertes Dreh-/Schiebegelenk verbunden ist.A particularly suitable coupling geometry and a synchronous movement resulting therefrom is achieved in a preferred embodiment of the invention in that the pivot point of the backrest support on the seat support seen in the longitudinal direction of the seat in every position of the backrest support behind the pivot point of the backrest support on the base support and the pivot point of the front coupling element on the seat support is seen in the longitudinal direction of the seat in every position of the backrest support in front of the pivot point of the front coupling element on the base support. This is preferably supported in that the front coupling element is connected to the seat support via a pure rotary joint and not via a combined rotary/sliding joint.

Gegenüber anderen selbsteinstellenden Mechaniken zeichnet sich die vorliegende Synchronmechanik dadurch aus, daß sie besonders flachbauend ist, so daß eine entsprechende Baugruppe nur sehr wenig Bauraum benötigt. Mit anderen Worten wird mit der Erfindung auf elegante Weise auf kleinstem Raum ein besonders hoher Sitzkomfort ohne den sogenannten "Hemdauszieheffekt" erreicht, ohne daß auf aufwendige und teure konstruktive Lösungen zurückgegriffen werden muß.Compared to other self-adjusting mechanisms, the present synchronous mechanism is characterized in that it is particularly flat, so that a corresponding assembly requires very little space. In other words, with the invention A particularly high level of seating comfort is achieved in an elegant way in the smallest of spaces without the so-called "shirt pulling effect" and without having to resort to complex and expensive constructive solutions.

Diese und weitere Vorteile der Erfindung werden im Zusammenhang mit den Ausführungsbeispielen der Erfindung nachfolgend anhand der Zeichnungen erläutert. Hierbei zeigen:

Fig. 1
eine Seitenansicht der Synchronmechanik in der Grundstellung ("harte" Einstellung),
Fig. 2
eine teilweise geschnittene Seitenansicht der Synchronmechanik in der Grundstellung ("harte" Einstellung),
Fig. 3
eine Seitenansicht der Synchronmechanik in einer maximal nach hinten verschwenkten Stellung ("harte" Einstellung),
Fig. 4
eine Seitenansicht der Synchronmechanik in der Grundstellung ("weiche" Einstellung),
Fig. 5
eine teilweise geschnittene Seitenansicht der Synchronmechanik in der Grundstellung ("weiche" Einstellung),
Fig. 6
eine Seitenansicht der Synchronmechanik in einer maximal nach hinten verschwenkten Stellung ("weiche" Einstellung).
These and other advantages of the invention are explained below in connection with the exemplary embodiments of the invention with reference to the drawings. Here show:
1
a side view of the synchronous mechanism in the basic position ("hard" setting),
2
a partially sectioned side view of the synchronous mechanism in the basic position ("hard" setting),
3
a side view of the synchronizing mechanism in a position pivoted to the rear as far as possible ("hard" setting),
4
a side view of the synchronous mechanism in the basic position ("soft" setting),
figure 5
a partially sectioned side view of the synchronous mechanism in the basic position ("soft" setting),
6
a side view of the synchronous mechanism in a maximally pivoted backwards position ("soft" setting).

Sämtliche Figuren zeigen die Erfindung nicht maßstabsgerecht, dabei lediglich schematisch und nur mit ihren wesentlichen Bestandteilen. Gleiche Bezugszeichen entsprechen dabei Elementen gleicher oder vergleichbarer Funktion.None of the figures show the invention to scale, but only schematically and only with its essential components. The same reference symbols correspond to elements with the same or comparable function.

Zunächst wird der allgemeine Aufbau und Bewegungsablauf der Mechanik erläutert.First, the general structure and movement of the mechanics are explained.

Die Synchronmechanik 100 weist einen Basisträger 1 auf, der mittels einer Konusaufnahme 2 auf das obere Ende einer Stuhlsäule 10 (siehe Fig. 1) gesetzt ist. Darüber hinaus umfaßt die Synchronmechanik 100 einen im wesentlichen rahmenförmigen Sitzträger 3 und einen in Draufsicht gabelförmigen Rückenlehnenträger 4, dessen Wangen 5 zu beiden Seiten des Basisträgers 1 angeordnet sind.The synchronous mechanism 100 has a base support 1, which is attached to the upper end of a chair column 10 by means of a cone mount 2 (see 1 ) is set. In addition, the synchronizing mechanism 100 comprises an essentially frame-shaped seat support 3 and a backrest support 4 which is fork-shaped in plan view and whose cheeks 5 are arranged on both sides of the base support 1 .

Der Sitzträger 3 ist zur Aufnahme oder Montage einer vorzugsweise gepolsterten Sitzfläche (nicht abgebildet) vorgesehen. Die Montage erfolgt mit Hilfe nicht näher dargestellter Befestigungselemente auf übliche Art und Weise. Am Rückenlehnenträger 4 ist eine nicht näher dargestellte Rückenlehne angebracht, die bei modernen Bürostühlen höhenverstellbar ist. Die Rückenlehne kann mit dem Rückenlehnenträger 4 auch einstückig verbunden sein.The seat support 3 is provided for receiving or mounting a preferably upholstered seat (not shown). The assembly is done with the help of fasteners not shown in the usual way. A backrest, not shown in detail, is attached to the backrest support 4, the height of which is adjustable in modern office chairs. The backrest can also be connected in one piece to the backrest support 4 .

Die gesamte Synchronmechanik 100 ist bezüglich ihrer Mittellängsebene, was die eigentliche Kinematik betrifft, spiegelsymmetrisch aufgebaut. Insoweit ist bei der folgenden Beschreibung immer von beiderseits paarweise vorhanden Konstruktionselementen der eigentlichen Schwenkmechanik auszugehen.As far as the actual kinematics are concerned, the entire synchronizing mechanism 100 has a mirror-symmetrical structure with respect to its central longitudinal plane. In this respect, the following description is always based on construction elements of the actual pivoting mechanism that are present in pairs on both sides.

In den Fig. 1 und 2 sowie den Fig. 4 und 5 ist die Grundposition der Synchronmechanik 100 gezeigt, bei welcher der Sitzträger 3 eine im wesentlichen waagerechte Lage einnimmt. Fig. 3 und 6 zeigen die Synchronmechanik 100 in einer maximal nach hinten geschwenkten Stellung des Rückenlehnenträgers 4.In the 1 and 2 as well as the 4 and 5 the basic position of the synchronous mechanism 100 is shown, in which the seat support 3 assumes a substantially horizontal position. 3 and 6 show the synchro-mechanism 100 in a position of the backrest support 4 pivoted to the maximum rearward.

In dem in Stuhllängsrichtung 14 gesehen hinteren Bereich 6 der Mechanik ist der Rückenlehnenträger 4 einerseits mit dem hinteren Bereich 9 des Basisträgers 1 und andererseits mit dem hinteren Bereich 25 des Sitzträgers 3 unmittelbar gelenkig verbunden.In the rear area 6 of the mechanism seen in the longitudinal direction 14 of the chair, the backrest support 4 is directly articulated to the rear area 9 of the base support 1 and to the rear area 25 of the seat support 3 .

Der Rückenlehnenträger 4 ist dabei mit seiner sich in Richtung des vorderen Sitzbereiches 8 erstreckenden Wange 5 unmittelbar an dem Basisträger 1 angelenkt und somit um eine die feststehende Hauptschwenkachse der Synchronmechanik 100 definierende erste (hintere) Querachse 11 in Schwenkrichtung 7 schwenkbar. Mit einem sich nach oben erstreckenden Mitnehmer 12 der Wange 5 ist der Rückenlehnenträger 4 mit dem Sitzträger 3 unmittelbar gelenkig verbunden.The backrest support 4 is hinged directly to the base support 1 with its cheek 5 extending in the direction of the front seat area 8 and can therefore be pivoted in the pivoting direction 7 about a first (rear) transverse axis 11 that defines the fixed main pivoting axis of the synchronous mechanism 100. The backrest support 4 is directly articulated to the seat support 3 with an upwardly extending driver 12 of the cheek 5 .

Die durch die Anlenkung des Rückenlehnenträgers 4 an dem Basisträger 1 definierte erste Gelenkachse 13 ist in Stuhllängsrichtung 14 gesehen vor der durch die Anlenkung des Rückenlehnenträgers 4 an dem Sitzträger 3 definierten zweite Gelenkachse 15 angeordnet. Gegenüber der Senkrechten auf der Hauptschwenkachse der Synchronmechanik 100 ist die zweite Gelenkachse 15 zwar nur leicht nach hinten versetzt. Eine Zenith-Stellung unmittelbar über der ersten Gelenkachse 13 kann jedoch nicht erreicht werden. Ein Herausschwenken des Rückenlehnenträgers 4 aus der Grundstellung in eine nach hinten verschwenkte Stellung ist daher stets mit einer Absenkbewegung S des hinteren Bereiches 25 des Sitzträgers 3 verbunden.The first articulation axis 13 defined by the articulation of the backrest support 4 on the base support 1 is arranged in front of the second articulation axis 15 defined by the articulation of the backrest support 4 on the seat support 3 in the longitudinal direction 14 of the chair. Compared to the vertical on the main pivot axis of the synchronous mechanism 100, the second joint axis 15 is offset only slightly to the rear. However, a zenith position directly above the first hinge axis 13 cannot be achieved. Pivoting the backrest support 4 out of the basic position into a rearwardly pivoted position is therefore always associated with a lowering movement S of the rear area 25 of the seat support 3 .

In der Grundstellung befinden sich beide Gelenkachsen 13, 15 in Stuhllängsrichtung 14 gesehen vor dem Zentrum der Konusaufnahme 2. In der maximal nach hinten verschwenkten Stellung befindet sich die zweite Gelenkachse 15 in Stuhllängsrichtung 14 gesehen hinter dem Zentrum der Konusaufnahme 2, während die Position der ersten Gelenkachse 13 gegenüber der Konusaufnahme 2 unveränderlich ist.In the basic position, both joint axes 13, 15 are located in front of the center of the cone mount 2, seen in the longitudinal direction 14 of the chair. In the position pivoted to the maximum backwards, the second joint axis 15 is located behind the center of the cone mount 2, seen in the longitudinal direction 14 of the chair, while the position of the first Joint axis 13 relative to the cone mount 2 is unchangeable.

Durch die Positionen der Anlenkpunkte des Rückenlehnenträgers 4 an dem Basisträger 1 einerseits und an dem Sitzträger 3 andererseits wird ein starr mit dem Rückenlehnenträger 4 verbundenes, als integraler Bestandteil des Rückenlehnenträgers 4 ausgebildetes Koppelelement 16 definiert, wie es in Fig. 1 mit strichpunktierter Linie symbolisch dargestellt ist. Das Koppelelement 16 besteht konstruktiv ausschließlich aus einem Teil der Wange 5. Die Anordnung des Koppelelements 16 unmittelbar oberhalb der Konusaufnahme 2 trägt zu einem vorteilhaften Bewegungsablauf der Synchronmechanik 100 bei.The positions of the pivot points of the backrest support 4 on the base support 1 on the one hand and on the seat support 3 on the other hand define a coupling element 16 which is rigidly connected to the backrest support 4 and is designed as an integral part of the backrest support 4, as is shown in Fig 1 is shown symbolically with a dot-dash line. In terms of construction, the coupling element 16 consists exclusively of a part of the cheek 5. The arrangement of the coupling element 16 directly above the cone receptacle 2 contributes to an advantageous sequence of movements of the synchronous mechanism 100.

In dem vorderen Bereich 17 der Mechanik ist der vordere Bereich 18 des Basisträgers 1 mit dem vorderen Bereich 8 des Sitzträgers 3 gelenkig verbunden. Hierzu ist ein Koppelelement 21 vorgesehen, das einerseits unmittelbar an dem Basisträger 1, nämlich um eine zweite (vordere) Querachse 19 schwenkbar, und andererseits unmittelbar an dem Sitzträger 3 angelenkt ist. Die vordere Querachse 19 ist, ebenso wie die hintere Querachse 11 ortsfest zu dem Basisträger 1 und damit feststehend, wird also bei einem Verschwenken des Rückenlehnenträgers 4 nicht mitbewegt. Der Anlenkpunkt des Koppelelements 21 an dem Basisträger 1 und damit die dritte Gelenkachse 22 befindet sich in Stuhllängsrichtung 14 gesehen hinter dem Anlenkpunkt des Koppelelements 21 an dem Sitzträger 3 und damit hinter der vierten Gelenkachse 23. Auch in einer maximal nach hinten verschwenkten Stellung der Synchronmechanik 100 ändert sich die Reihenfolge der Anordnung der Gelenkachsen 13, 15, 22, 23 nicht. Das hintere Koppelelement 16 zeigt in Stuhllängsrichtung 14 gesehen ausgehend von der ersten Querachse 11 in jedem Fall schräg nach oben und nach hinten und das vordere Koppelelement 21 zeigt in Stuhllängsrichtung 14 gesehen ausgehend von der zweiten Querachse 19 in jedem Fall schräg nach oben und nach vorn. Dabei verlaufen die Gelenkachsen 15, 23 an den Anlenkpunkten des Sitzträgers 3 in vertikaler Richtung gesehen stets oberhalb der Gelenkachsen 13, 22, die durch die Anlenkung an dem Basisträger 1 definiert werden. Die Koppelelemente 16, 21 sind zueinander V-förmig angeordnet, wobei sich die gedachten Verlängerungslinien der Koppelelemente 16, 21 unterhalb des Basisträgers 1 schneiden. Die relative Bewegung von Sitzträger 3 und Rückenlehnenträger 4 zueinander wird durch die Position der insgesamt vier durch die Enden der beiden Koppelelemente 16, 21 verlaufenden, durch die Anlenkpunkte definierten Gelenkachsen 13, 15, 22, 23 bestimmt.In the front area 17 of the mechanism, the front area 18 of the base support 1 is connected in an articulated manner to the front area 8 of the seat support 3 . For this purpose, a coupling element 21 is provided, which on the one hand is articulated directly on the base support 1, specifically about a second (front) transverse axis 19, and on the other hand is articulated directly on the seat support 3. The front transverse axis 19, like the rear transverse axis 11, is stationary with respect to the base support 1 and is therefore fixed, and is therefore not moved when the backrest support 4 is pivoted. The articulation point of the coupling element 21 on the base support 1 and thus the third articulation axis 22 is located behind the articulation point of the coupling element 21 on the seat support 3 and thus behind the fourth articulation axis 23, viewed in the longitudinal direction 14 of the chair. Even when the synchronous mechanism 100 is pivoted to the maximum rearward position, the order in which the joint axes 13, 15, 22, 23 are arranged does not change. The rear coupling element 16, viewed in the longitudinal direction 14 of the chair, always points obliquely upwards and backwards, starting from the first transverse axis 11, and the front coupling element 21, viewed in the longitudinal direction 14 of the chair, starting from the second transverse axis 19, always points obliquely upwards and forwards. The joint axes 15, 23 at the pivot points of the seat support 3, viewed in the vertical direction, always run above the joint axes 13, 22, which are defined by the linkage to the base support 1. The coupling elements 16, 21 are arranged in a V-shape relative to one another, 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 one another is determined by the position of the four joint axes 13, 15, 22, 23 that run through the ends of the two coupling elements 16, 21 and are defined by the pivot points.

Durch den beschriebenen Schwenkmechanismus wird gewährleistet, daß der Rückenlehnenträger 4 mit der Rückenlehne um die als Hauptschwenkachse dienende hintere Querachse 11, hier die erste Gelenkachse 13, in Schwenkrichtung 7 verschwenkt werden kann. Zugleich induziert die Schwenkbewegung der Rückenlehne nach hinten eine sofortige Absenkbewegung S des hinteren Bereiches 25 des Sitzträgers 3 nach hinten unten und der vordere Bereich 8 des Sitzträgers 3 vollführt eine Anhebebewegung H nach hinten oben (siehe Fig. 1). Bei einer Verschwenkung der Rückenlehne erfolgt also zugleich eine Verschiebung des Sitzträgers 3 nach hinten, während der Basisträger 1 mit den Schwenklagern 13, 22 und ihren Querachsen 11 positionsfest bleibt.The pivoting mechanism described ensures that the backrest support 4 with the backrest can be pivoted in the pivoting direction 7 about the rear transverse axis 11 serving as the main pivoting axis, here the first joint axis 13 . At the same time, the backwards pivoting movement of the backrest induces an immediate lowering movement S of the rear area 25 of the seat support 3 backwards and downwards and the front area 8 of the seat support 3 performs a lifting movement H backwards and upwards (see Fig 1 ). When the backrest is pivoted, the seat support 3 is simultaneously displaced backwards, while the base support 1 with the pivot bearings 13, 22 and their transverse axes 11 remains fixed in position.

Die Mechanik 100 weist einen Federmechanismus zum Einstellen des Schwenkwiderstandes der Rückenlehne auf. Dieser umfaßt wenigstens ein Federelement 30, siehe Fig. 2. Das Federelement 30 übt dabei eine Federkraft entgegen der nach hinten gerichteten Schwenkbewegung 7 der Rückenlehne aus. Dabei wird das Federelement 30 bei einem Verschwenken des Rückenlehnenträgers 4 beaufschlagt. Je nach "Härte" des Federelements 30 erfolgt also die Synchronbewegung (Sitz- und Rückenlehne) gegen einen mehr oder weniger großen Federwiderstand.The mechanism 100 has a spring mechanism for adjusting the pivoting resistance of the backrest. This includes at least one spring element 30, see 2 . The spring element 30 exerts a spring force against the backward pivoting movement 7 of the backrest. The spring element 30 is acted upon when the backrest support 4 pivots. Depending on the "hardness" of the spring element 30, the synchronous movement (seat and backrest) takes place against a greater or lesser spring resistance.

Es ist eine Federanordnung mit einer zentral angeordneten Schraubendruckfeder 30 vorgesehen, welche sich einerseits an einem vorderen Widerlager 31 und andererseits an einem hinteren Widerlager 37 mit Hilfe von Federtellern 32, 34 abstützt (nicht in allen Figuren im Detail abgebildet). Die Feder 30, die im Detail allein in Fig. 2 dargestellt ist, umgreift dabei Führungsstangen 33, die an ihren jeweiligen Enden die Federteller 32, 34 aufweisen.A spring arrangement is provided with a centrally arranged helical compression spring 30, which is supported on one side on a front abutment 31 and on the other side on a rear abutment 37 with the aid of spring plates 32, 34 (not shown in detail in all figures). The spring 30, which is in detail alone in 2 is shown, encompasses guide rods 33, which have the spring plates 32, 34 at their respective ends.

Bei einem Verschwenken des Rückenlehnenträgers 4 wird die Feder 30 beidseitig belastet. Genauer gesagt ist das wenigstens eine Federelement 30 mit seinem einen, in Stuhllängsrichtung 14 gesehen hinteren Federende 27 unmittelbar mit dem Rückenlehnenträger 4 und mit seinem anderen, in Stuhllängsrichtung 14 gesehen vorderen Federende 28 entweder unmittelbar mit dem Sitzträger 3 oder unmittelbar mit dem Koppelelement 21 verbunden derart, daß eine Bewegung der Rückenlehne von einer Grundstellung in eine nach hinten verschwenkte Stellung eine gleichzeitige Bewegung beider Federenden 27, 28 hervorruft.When the backrest support 4 pivots, the spring 30 is loaded on both sides. More precisely, the at least one spring element 30 is connected with its one rear spring end 27, seen in the longitudinal direction 14 of the chair, directly to the backrest support 4 and with its other, front spring end 28, seen in the longitudinal direction 14 of the chair, either directly with the seat support 3 or directly with the coupling element 21 that a movement of the backrest from a basic position to a rearwardly pivoted position causes a simultaneous movement of both spring ends 27, 28.

Das hintere Federende 27 ist dabei zur Ausbildung eines in der dargestellten Ausführungsform längenveränderlichen hinteren Hebelarmes 35 beabstandet von der ersten Querachse 11 mit dem Rückenlehnenträger 4 verbunden. Handelt es sich bei dem Federelement 30 um eine Druckfeder, wie in den Figuren dargestellt, befindet sich dieser Verbindungspunkt 40 unterhalb der ersten Querachse 11. Das bedeutet, daß das hintere Ende 27 des Federelements 30 an einem sich über den Anlenkpunkt 11 mit dem Basisträger 2 hinaus erstreckenden Arm 20 der Wange 5 angelenkt ist. Zu diesem Zweck ist die sich in Richtung Sitzvorderkante 8 erstreckenden Wange 5 schräg nach vorn unten hin über den Anlenkpunkt 11 hinaus verlängert, wodurch ein mit dem Rückenlehnenträger 4 schwenkender Hebelarm 35 gebildet wird. Der Verbindungspunkt 40 der Feder 30 mit dem Rückenlehnenträger 4 liegt dann in Stuhllängsrichtung 14 gesehen stets unterhalb sowie vor der hinteren Querachse 11.The rear end of the spring 27 is used to form a rear end that is variable in length in the illustrated embodiment Lever arm 35 is connected to the backrest support 4 at a distance from the first transverse axis 11 . If the spring element 30 is a compression spring, as shown in the figures, this connection point 40 is located below the first transverse axis 11. This means that the rear end 27 of the spring element 30 is connected to the base support 2 via the pivot point 11 also extending arm 20 of the cheek 5 is articulated. For this purpose, the cheek 5 extending in the direction of the front edge 8 of the seat is lengthened obliquely forwards and downwards beyond the pivot point 11, as a result of which a lever arm 35 pivoting with the backrest support 4 is formed. The connection point 40 of the spring 30 with the backrest support 4 is then always seen in the longitudinal direction 14 of the chair below and in front of the rear transverse axis 11.

In dem Fall, daß eine Zugfeder eingesetzt werden würde (nicht dargestellt), würde sich der Verbindungspunkt 40 oberhalb der ersten Querachse 11 befinden, nämlich zwischen den beiden Anlenkpunkten 13, 15 des Rückenlehnenträgers 4 an Basisträger 1 und Sitzträger 3.If a tension spring were to be used (not shown), the connection point 40 would be located above the first transverse axis 11, namely between the two pivot points 13, 15 of the backrest support 4 on the base support 1 and seat support 3.

Das vordere Federende 28 ist zur Ausbildung eines in der dargestellten Ausführungsform konstant langen vorderen Hebelarmes 36 von der vorderen Querachse 19 beabstandet positioniert, nämlich entweder mit dem Sitzträger 3 verbunden, insbesondere mit dem vorderen Bereich 8 des Sitzträgers 3, vorzugsweise an dem Anlenkpunkt 23 des Koppelelements 21 an dem Sitzträger 3, oder aber, wie dargestellt, mit dem Koppelelement 21. Handelt es sich bei dem Federelement 30 um eine Druckfeder, wie in den Figuren dargestellt, befindet sich dieser Verbindungspunkt 42 oberhalb der zweiten Querachse 19, nämlich zwischen den beiden Anlenkpunkten 22, 23 des Koppelelements 21 an Basisträger 1 und Sitzträger 3, so daß der Verbindungspunkt 42 der Feder 30 mit dem Koppelelement 21 in Stuhllängsrichtung 14 gesehen stets oberhalb sowie vor der vorderen Querachse 19 liegt.The front spring end 28 is positioned at a distance from the front transverse axis 19 to form a front lever arm 36, which is of constant length in the illustrated embodiment, namely either connected to the seat support 3, in particular to the front region 8 of the seat support 3, preferably at the pivot point 23 of the coupling element 21 on the seat support 3, or, as shown, with the coupling element 21. If the spring element 30 is a compression spring, as shown in the figures, this connection point 42 is located above the second transverse axis 19, namely between the two pivot points 22, 23 of the coupling element 21 to the base support 1 and seat support 3, so that the connection point 42 of the spring 30 with the coupling element 21 seen in the longitudinal direction 14 of the chair is always above and in front of the front transverse axis 19 .

Das Koppelelement 21 führt als eine Art Lenker bei einer Schwenkbewegung der Rückenlehne bzw. des daran angelenkten Sitzes eine zum Rückenlehnenträger 4 hin gerichtete Schwenkbewegung 29 aus, die derart mit der Schwenkbewegung 41 des Hebelarmes 20 des Rückenlehnenträgers zusammenwirkt, daß eine zwischen dem Rückenlehnenträger 4 und dem Koppelelement 21 eingespannte Druckfeder 30 zugleich von beiden Seiten her zusammengedrückt wird.Coupling element 21, acting as a kind of link, performs a pivoting movement 29 directed towards backrest support 4 when the backrest or the seat articulated thereon pivots, which interacts with pivoting movement 41 of lever arm 20 of the backrest support in such a way that a gap between backrest support 4 and the Coupling element 21 clamped compression spring 30 is simultaneously compressed from both sides.

Für den Fall, daß eine Zugfeder eingesetzt werden würde (nicht dargestellt), müßte sich der Verbindungspunkt der Feder mit dem Koppelelement 21 unterhalb und in Stuhllängsrichtung 14 gesehen hinter der zweiten Querachse 19 befinden, wofür erforderlichenfalls das Koppelelement 21 nach unten hin, über den Anlenkpunkt 22 des Koppelelements 21 an dem Basisträger 1 hinaus, verlängert werden müßte.In the event that a tension spring would be used (not shown), the connection point of the spring with the coupling element 21 would have to be below and behind the second transverse axis 19 seen in the longitudinal direction 14 of the chair, for which purpose the coupling element 21 should be downwards, over the pivot point 22 of the coupling element 21 on the base support 1 addition, would have to be extended.

Die beiden Federenden 27, 28 werden bei einer Verschwenkung des Rückenlehnenträgers 4 derart beaufschlagt, daß sich der Abstand der beiden Federenden 27, 28 zueinander verändert. Handelt es sich bei dem verwendeten Federelement um eine Druckfeder 30, wird dabei der Abstand der beiden Federenden 27, 28 zueinander verringert. Im Fall einer Zugfeder (nicht dargestellt) führt die Beaufschlagung beider Federenden 27, 28 zu einer Vergrößerung des Abstandes der beiden Federenden 27, 28.When the backrest support 4 pivots, the two spring ends 27, 28 are acted upon in such a way that the distance between the two spring ends 27, 28 from one another changes. If the spring element used is a compression spring 30, the distance between the two spring ends 27, 28 is reduced from one another. In the case of a tension spring (not shown), the loading of both spring ends 27, 28 leads to an increase in the distance between the two spring ends 27, 28.

Die Position des hinteren Anlenkpunktes 40 des Federelements 30 an dem Rückenlehnenträger 4 definiert also die Länge eines Hebelarmes 35 bis zur Hauptschwenkachse 11 der Mechanik 100. Bei einem Verschwenken des Rückenlehnenträgers 4 wird der Arm 35 nach vorn in Schwenkrichtung 41 verschwenkt, wodurch das hintere Federende 27 beaufschlagt wird. Zugleich ändert sich bei einem Verschwenken des Rückenlehnenträgers 4 auch die Position des vorderen Federendes 28, das an der Koppel 21 bzw. am Sitzträger 3 angelenkt ist. Da dieser Sitzträger 3 zusätzlich zu einer Kippbewegung nach hinten unten auch eine horizontale Verschiebung nach hinten vollführt, wird im Ergebnis eine beidseitige Beaufschlagung der Druckfeder 30 erreicht.The position of the rear pivot point 40 of the spring element 30 on the backrest support 4 thus defines the length of a lever arm 35 up to the main pivot axis 11 of the mechanism 100. At a pivoting of the backrest support 4, the arm 35 is pivoted forward in the pivoting direction 41, whereby the rear end of the spring 27 is acted upon. At the same time, when the backrest support 4 is pivoted, the position of the front end of the spring 28, which is articulated on the coupling 21 or on the seat support 3, also changes. Since this seat support 3 also performs a horizontal displacement backwards in addition to a tilting movement backwards and downwards, the result is that the compression spring 30 is acted upon on both sides.

Erfindungsgemäß sind die Federenden 27, 28 mit Bauteilen verbunden, genauer gesagt an Bauteile angelenkt, die sich bei einem Verschwenken des Rückenlehnenträgers 4 auf eine Weise zueinander verschwenken, daß sich die Federenden 27, 28 in entgegengesetzte Richtungen bewegen, jedenfalls aber derart bewegen, daß deren Bewegung zu einer Veränderung des Abstandes der Federenden 27, 28 zueinander beitragen, wodurch eine größere Federwirkung erzielbar ist.According to the invention, the spring ends 27, 28 are connected to components, more precisely articulated to components which, when the backrest support 4 is pivoted, pivot in relation to one another in such a way that the spring ends 27, 28 move in opposite directions, but in any case move in such a way that their Movement to change the distance between the spring ends 27, 28 contribute to each other, whereby a greater spring effect can be achieved.

Die Feder 30 ist vorzugsweise derart angeordnet und die Verbindung der Feder 30 mit dem Rückenlehnenträger 4 vorzugsweise derart ausgeführt, daß in der Grundstellung die Wirklinie der Feder 30 im wesentlichen senkrecht zu dem Hebelarm 35 steht.The spring 30 is preferably arranged in such a way and the connection of the spring 30 to the backrest support 4 is preferably carried out in such a way that the line of action of the spring 30 is essentially perpendicular to the lever arm 35 in the basic position.

Nachfolgend wird die Änderung des Schwenkwiderstandes näher beschrieben.The change in the swing resistance is described in more detail below.

Der Federmechanismus umfaßt Mittel zum Einstellen der Federkraft des wenigstens einen Federelements 30, indem die Position wenigstens eines der beiden Federenden 27, 28 und damit der Abstand zwischen den beiden Federenden 27, 28 verändert wird. In den Figuren dargestellt ist eine Verstellung des hinteren Federendes 27. Hierzu wird die Entfernung des hinteren Federendes 27 zu der ersten Querachse 11 verändert. Bei einer Verstellung des vorderen Federendes 28 (nicht abgebildet) würde entsprechend die Entfernung des vorderen Federendes 28 zu der zweiten Querachse 19 verändert werden. Ebenfalls möglich ist eine vorzugsweise gleichzeitige Verstellung der Position beider Federenden 27, 28, um den Verstelleffekt bei gleichem Verstellweg zu verstärken.The spring mechanism includes means for adjusting the spring force of the at least one spring element 30 by changing the position of at least one of the two spring ends 27, 28 and thus the distance between the two spring ends 27, 28. The figures show an adjustment of the rear end of the spring 27. For this purpose, the removal of the rear end of the spring 27 changed to the first transverse axis 11. If the front end of the spring 28 (not shown) is adjusted, the distance between the front end of the spring 28 and the second transverse axis 19 would be changed accordingly. Also possible is a preferably simultaneous adjustment of the position of both spring ends 27, 28 in order to increase the adjustment effect with the same adjustment path.

Um eine "kraftlose" Federkrafteinstellung zu erreichen, sind die Einstellmittel derart ausgebildet, daß das zu verstellende, lageveränderliche Federende 27 auf einer Kreisbahn mit im wesentlichen konstanten Radius um das andere Federende 28 des Federelements 30 bewegbar ist. Sofern keine gleichzeitige Verstellung beider Federenden 27, 28 erfolgt, bleibt das andere Federende 28 während dieser Verstellung lageunveränderlich.In order to achieve a "forceless" spring force setting, the setting means are designed in such a way that the positionable spring end 27 to be adjusted can be moved around the other spring end 28 of the spring element 30 on a circular path with a substantially constant radius. If both spring ends 27, 28 are not adjusted at the same time, the other spring end 28 remains in a fixed position during this adjustment.

Die Veränderung der Position des Federendes 27, 28 erfolgt vorzugsweise mittels eines Kurventriebes 43. Der Kurventrieb 43 weist einen manuell und/oder motorisch betätigbaren, beweglich am Rückenlehnenträger 4 gelagerten, insbesondere drehbar gelagert, vorzugsweise exzentrischen Kurventräger 44 auf, der mit einer als Abtastelement dienenden Kurvenrolle 45 zusammenwirkt, die mit der Kurve 46 des Kurventrägers 44 zusammenwirkt bzw. in Eingriff steht. In einem einfachen Fall, in dem der Kurventräger 44 als Kurvenscheibe ausgeführt ist, läuft, wie dargestellt, die Kurvenrolle 45 einseitig auf der Kurve 46, an die sie durch das wenigstens eine Federelement 30 gedrückt wird. Die Kurvenrolle 45 ist dabei mit dem hinteren Federende 27 bzw. bei einer Verstellung des vorderen Federendes 28 (nicht dargestellt) mit diesem verbunden. Durch eine Bewegung des Kurventrägers 21 kann die Kurvenrolle 45 und damit das dort angebrachte Federende 27, 28 in Positionen relativ zu der ersten Querachse 11 bewegt werden, welche unterschiedliche Federkräfte zur Folge haben. Dabei ist die Kurvenrolle 45 bei der abgebildeten Ausführungsform der Erfindung mit einem Gleitschuh 51 versehen und liegt in einem in dem Rückenlehnenträger 4 oder in dem Koppelelement 21 vorgesehenen Langloch 47 ein oder ist auf andere Weise mit dem Rückenlehnenträger 4 bzw. bei einer Verstellung des vorderen Federendes 28 (nicht dargestellt) mit dem Koppelelement 21 verbunden. Das Langloch 47 ist gebogen, nämlich kreisförmig ausgeführt derart, daß die Kurvenrolle 45 und damit das hintere Federende 27 auf einer Kreisbahn mit im wesentlichen konstanten Radius um das andere Federende 28 bewegbar ist.The position of the spring end 27, 28 is preferably changed by means of a cam drive 43. The cam drive 43 has a manually and/or motor-operated, movably mounted, in particular rotatably mounted, preferably eccentric cam carrier 44 on the backrest support 4, which is equipped with a scanning element Cam roller 45 cooperates, which cooperates with the curve 46 of the cam carrier 44 or is in engagement. In a simple case, in which the cam carrier 44 is designed as a cam disc, the cam roller 45 runs on one side, as shown, on the cam 46 against which it is pressed by the at least one spring element 30 . The cam roller 45 is connected to the rear end of the spring 27 or, if the front end of the spring 28 (not shown) is adjusted, to the latter. By moving the cam carrier 21, the cam roller 45 and thus the spring end 27, 28 attached there can be moved into positions relative to the first transverse axis 11 which have different spring forces have as a consequence. In the illustrated embodiment of the invention, the cam roller 45 is provided with a sliding shoe 51 and lies in a slot 47 provided in the backrest support 4 or in the coupling element 21 or is connected in some other way to the backrest support 4 or when the front spring end is adjusted 28 (not shown) connected to the coupling element 21. The elongated hole 47 is curved, namely circular in shape, in such a way that the cam roller 45 and thus the rear end of the spring 27 can be moved around the other end of the spring 28 on a circular path with a substantially constant radius.

Das lageveränderliche Federende 27, 28 des Federelements 30 ist mit dem betreffenden Konstruktionselement (Rückenlehnenträger 4 oder Koppelelement 21) verbunden, indem ein Bolzen oder ein anderes zur Abtastung der Kurve 46 geeignetes Bauteil, an dem das Federende 27, 28 befestigt, beispielsweise eingehängt ist, in diesem Konstruktionselement 4, 21 mittelbar oder unmittelbar geführt bzw. gelagert ist. Dabei liegt das abtastende Bauteil, also beispielsweise die Kurvenrolle 45, insbesondere in einer gebogenen Führungsnut, einem Führungsschlitz oder dergleichen ein und stützt sich an einer definierten, von seiner Position auf der Kurve 46 abhängigen, die Federkraft des Federelements 30 bestimmenden Position des Konstruktionselements 4, 21 ab, wobei es von der diesem Konstruktionselement 4, 21 zugeordneten, feststehenden Querachse 11, 19 beabstandet ist. Mit anderen Worten wird ein geeignetes Bauteil, beispielsweise in Form eines Bolzens, verwendet, um einerseits mit einem verstellbaren Kurventräger 44, beispielsweise der Kurvenscheibe, zusammenzuwirken und als Kurvenrolle 45 die Kurve 46 der Kurvenscheibe 44 abzutasten, und um zugleich andererseits als eine Art Gleitschuh 51 zu wirken oder mit einem Gleitschuh oder dergleichen zusammenwirken, der sich auf einer Gleitbahn, beispielsweise in Form einer Führungsnut oder eines gebogenen Langloches 47, an dem Rückenlehnenträger 4 (bei einer Verstellbarkeit des hinteren Federendes 27) oder an dem Koppelelement 21 (bei einer Verstellbarkeit des vorderen Federendes 28) abstützt.The variable-position spring end 27, 28 of the spring element 30 is connected to the relevant structural element (backrest support 4 or coupling element 21) by a bolt or another component suitable for scanning the curve 46, to which the spring end 27, 28 is fastened, e.g. is guided or stored directly or indirectly in this structural element 4, 21. The scanning component, for example the cam roller 45, lies in particular in a curved guide groove, a guide slot or the like and is supported at a defined position of the structural element 4 that depends on its position on the cam 46 and determines the spring force of the spring element 30. 21, wherein it is spaced apart from the fixed transverse axis 11, 19 associated with this structural element 4, 21. In other words, a suitable component, for example in the form of a bolt, is used in order on the one hand to interact with an adjustable cam carrier 44, for example the cam disc, and to scan the cam 46 of cam disc 44 as cam roller 45, and on the other hand to act as a type of sliding shoe 51 to act or interact with a shoe or the like, which is on a slide, for example in the form of a guide groove or a curved Slot 47 on the backrest support 4 (with an adjustability of the rear spring end 27) or on the coupling element 21 (with an adjustability of the front spring end 28).

Auf dem den Verlauf der Kurve 46 definierenden Rand der Kurvenscheibe 44 sind den lokalen Verlauf der Kurve 46 bestimmende Mulden 48, 49 vorgesehen, welche an definierten Stellen der Kurve 46 eine ausreichend große Selbsthemmung, also einen hinreichenden Widerstand gegen ein Verrutschen der Kurvenrolle 45 auf der Kurve 46, gewährleisten. Damit bleibt die Kurvenrolle 45 an ihrem Platz, auch wenn zum Erreichen eines möglichst kurzen Verstellweges bei der Einstellung der Federkraft des Federelements 30 ein Kurventräger 44 zum Einsatz kommt, der eine Kurve 46 mit möglichst steilem Anstieg, also einem steilen Kurvenwinkel, aufweist.On the edge of the cam disk 44 that defines the course of the curve 46, there are troughs 48, 49 that determine the local course of the curve 46 curve 46, ensure. The cam roller 45 thus remains in place, even if, in order to achieve the shortest possible adjustment path when setting the spring force of the spring element 30, a cam carrier 44 is used which has a curve 46 with the steepest possible rise, i.e. a steep curve angle.

Ein Vorteil der Mulden 48, 49 ist, daß dadurch eine gestufte Einstellung der Federkraft möglich ist, was aus Benutzersicht oftmals als vorteilhaft angesehen wird, da das Verstellen des Federendes mit einem mehr oder weniger starken Einrasten der Kurvenrolle 45 in der jeweiligen Mulde 48, 49 verbunden ist, wodurch der Benutzer eine taktile Rückmeldung über einen erfolgreich vollzogenen Einstellvorgang erhält. Es ist jedoch auch eine Ausführung mit durchgehend glattem Kurvenrand möglich.One advantage of the troughs 48, 49 is that they allow the spring force to be adjusted in stages, which is often seen as advantageous from the user's point of view, since the adjustment of the spring end involves the cam roller 45 engaging to a greater or lesser extent in the respective trough 48, 49 is connected, whereby the user receives tactile feedback about a successfully completed adjustment process. However, an embodiment with a continuously smooth curve edge is also possible.

Von der "harten" in die "weiche" Einstellung und zurück gelangt man, wenn die an der hinteren Querachse 11 gelagerte exzentrische Kurvenscheibe 44 in Betätigungsrichtung 50 gedreht wird. In der in den Fig. 1 bis 3 abgebildeten härtesten Einstellung liegt die Kurvenrolle 45 in der hintersten Mulde 48 der Kurve 46 ein. Der wirksame Hebelarm 35 vom Angriffspunkt 40 der Feder 30 bis zur Hauptschwenkachse 11 ist am größten. In dieser Stellung muß der Anlenkpunkt 40 der Feder 30 bei gleichem Verschwenkwinkel des Rückenlehnenträgers 4 eine größere Strecke zurücklegen. Mit anderen Worten ist der Federweg länger. Aus diesem Grund wird die Feder 30 stärker komprimiert. Der Schwenkwiderstand ist härter. Dabei weist die Feder 30 bereits zu Beginn des Verschwenkvorgangs die größte Härte auf, ohne daß dazu ein Verschwenken des Rückenlehnenträgers 4 notwendig ist.You get from the "hard" to the "soft" setting and back if the eccentric cam disk 44 mounted on the rear transverse axis 11 is rotated in the direction of actuation 50 . In the in the Figures 1 to 3 illustrated hardest setting is the cam roller 45 in the rearmost trough 48 of the curve 46. The effective lever arm 35 from the point of application 40 of the spring 30 to the main pivot axis 11 is at its greatest. In this position must Pivot point 40 of the spring 30 cover a greater distance with the same pivoting angle of the backrest support 4 . In other words, the suspension travel is longer. For this reason, the spring 30 is compressed more. The swing resistance is harder. The spring 30 already has the greatest hardness at the beginning of the pivoting process, without the backrest support 4 having to be pivoted for this purpose.

In der in Fig. 5 abgebildeten weichsten Einstellung liegt die Kurvenrolle 45 in der vordersten Mulde 49 der Kurve 46 ein. Der effektive Hebelarm 35 ist kürzer, der Federweg und damit der Schwenkwiderstand entsprechend geringer.in the in figure 5 shown softest setting is the cam roller 45 in the foremost trough 49 of the curve 46. The effective lever arm 35 is shorter, the spring deflection and thus the pivoting resistance is correspondingly lower.

Die Drehung des Kurventrägers 44 in Betätigungsrichtung 50 erfolgt beispielsweise mittels einer manuell betätigbaren Handhabe, beispielsweise mit einem Drehgriff oder einem Handrad (nicht abgebildet). Diese Handhabe ist an dem Rückenlehnenträger 4 gelagert, wobei die Drehachse des Handrades mit der hintere Querachse 11 übereinstimmt. Alternativ kann der Kurventräger 44 auch über Hebel, Bowdenzüge usw. angetrieben werden. Auch kann anstelle einer manuellen Betätigung ein (elektro)motorischer Antrieb vorgesehen sein.The cam carrier 44 is rotated in the actuation direction 50, for example, by means of a manually operable handle, for example a rotary handle or a handwheel (not shown). This handle is mounted on the backrest support 4, with the axis of rotation of the handwheel coinciding with the rear transverse axis 11. Alternatively, the cam carrier 44 can also be driven via levers, Bowden cables, etc. An (electric) motor drive can also be provided instead of manual actuation.

In einer alternativen Ausführung der Erfindung (nicht dargestellt) ist der Kurventräger 44 derart ausgeführt, daß die Kurvenrolle 45 an bzw. in der Kurve 46 des Kurventrägers 44 zwangsgeführt wird. Hierzu weist der Kurventräger 44 vorzugsweise eine als Spiralkurve ausgebildete Führungsnut für die Kurvenrolle 45 auf. In diesem Fall kann die Verstellung in jedem Fall stufenlos erfolgen.In an alternative embodiment of the invention (not shown), the cam carrier 44 is designed in such a way that the cam roller 45 is positively guided on or in the cam 46 of the cam carrier 44 . For this purpose, the cam carrier 44 preferably has a guide groove designed as a spiral cam for the cam roller 45 . In this case, the adjustment can always be stepless.

Je nach zur Verfügung stehendem Bauraum kann eine große oder kleine Kurvenscheibe 44 zum Einsatz kommen. Auch kann je nach gewünschter Baugröße eine Kurve 46 mit einer geringen oder einer starken Steigung verwendet werden. Ebenso kann durch die Wahl der Kurve 46, insbesondere durch die Entscheidung, ob eine Kurve 46 mit konstanter oder variabler Steigung eingesetzt wird, die Verstellcharakteristik des Schwenkwiderstandes eingestellt werden.Depending on the space available, a large or small cam disk 44 can be used. Also may vary desired size, a curve 46 can be used with a low or a steep slope. Likewise, the adjustment characteristic of the pivoting resistance can be adjusted by the selection of the curve 46, in particular by the decision as to whether a curve 46 with a constant or variable slope is used.

Die beschriebene Federkrafteinstellung durch Veränderung der Position des hinteren Federendes 27 kann entsprechend auch für das vordere Federende 28 verwendet werden. In diesem Fall ist in dem Koppelelement 21 eine geeignete Führung, beispielsweise ein bogenförmiges Langloch, für eine mit dem vorderen Federende 28 verbundene Kurvenrolle 45 vorgesehen.The spring force setting described by changing the position of the rear spring end 27 can also be used accordingly for the front spring end 28 . In this case, a suitable guide, for example an arcuate slot, is provided in the coupling element 21 for a cam roller 45 connected to the front spring end 28 .

Insgesamt ergibt sich somit eine mit wenigen Bauteilen realisierbare und besonders wenig Bauraum benötigende Federkrafteinstellung.Overall, this results in a spring force setting that can be implemented with few components and requires particularly little installation space.

Alle in der Beschreibung, den nachfolgenden Ansprüchen und den Zeichnungen dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein, wobei der Gegenstand der Erfindung durch den unabhängigen Patentanspruch definiert wird.All of the features presented in the description, the following claims and the drawings can be essential to the invention both individually and in any combination with one another, the subject matter of the invention being defined by the independent patent claim.

BezugszeichenlisteReference List

11
Basisträgerbase carrier
22
Konusaufnahmecone mount
33
Sitzträgerseat carrier
44
Rückenlehnenträgerbackrest support
55
Wangecheek
66
hinterer Mechanikbereichrear mechanics area
77
Schwenkrichtungpan direction
88th
vorderer Bereich des Sitzträgersfront area of the seat carrier
99
hinterer Bereich des Basisträgersrear area of the base carrier
1010
Stuhlsäulechair column
1111
Hauptschwenkachse, erste (hintere) QuerachseMain pivot axis, first (rear) transverse axis
1212
Mitnehmerdriver
1313
erste Gelenkachsefirst joint axis
1414
Stuhllängsrichtungchair longitudinal direction
1515
zweite Gelenkachsesecond joint axis
1616
hinteres Koppelelementrear coupling element
1717
vorderer Mechanikbereichfront mechanics area
1818
vorderer Bereich des Basisträgersfront area of the base carrier
1919
zweite (vordere) Querachsesecond (front) transverse axis
2020
Armpoor
2121
Koppelelementcoupling element
2222
dritte Gelenkachsethird axis of articulation
2323
vierte Gelenkachsefourth axis of articulation
2424
(frei)(free)
2525
hinterer Bereich des Sitzträgersrear area of the seat carrier
2626
(frei)(free)
2727
hinteres Federenderear spring end
2828
vorderes Federendefront end of the spring
2929
Schwenkbewegung des KoppelelementsPivoting movement of the coupling element
3030
Schraubendruckfeder, FederelementHelical compression spring, spring element
3131
vorderes Widerlagerfront abutment
3232
vorderer Federtellerfront spring plate
3333
Führungsstangeguide rod
3434
hinterer Federtellerrear spring plate
3535
hinterer Hebelarmrear lever arm
3636
vorderer Hebelarmfront lever arm
3737
hinteres Widerlagerrear abutment
3838
(frei)(free)
3939
(frei)(free)
4040
Verbindungs-/Angriffspunkt des hinteren FederendesConnection/application point of the rear end of the spring
4141
Schwenkbewegung des hinteren HebelarmsPivoting movement of the rear lever arm
4242
Verbindungs-/Angriffspunkt des vorderen FederendesConnection/application point of the front end of the spring
4343
Kurventriebcam drive
4444
Kurventräger, KurvenscheibeCam carrier, cam disc
4545
Kurvenrolle, Abtastercam roller, tracer
4646
KurveCurve
4747
LanglochLong hole
4848
hintere Mulderear hollow
4949
vordere Muldefront hollow
5050
Betätigungsrichtungoperating direction
5151
Gleitschuhsliding shoe
100100
Synchronmechaniksynchronous mechanism
HH
Anhebebewegunglifting motion
SS
Absenkbewegunglowering movement

Claims (9)

  1. Synchronous mechanism (100) for a correlated seat/backrest movement of an office chair, having a base support (1) which is placeable on a chair column (10), a seat support (3) and a backrest support (4),
    wherein the backrest support (4) is connected to the base support (1) so as to be pivotable about a first transverse axis (11) and is also connected to the seat support (3) in an articulated manner,
    and
    wherein the seat support (3) is connected to the base support (1) in an articulated manner via a coupling element (21),
    wherein the coupling element (21) is connected to the base support (1) so as to be pivotable about a second transverse axis (19) and is also connected to the seat support (3) in an articulated manner at an articulation point (23),
    wherein a spring mechanism for setting the pivoting resistance of the backrest is provided, which spring mechanism has at least one spring element (30),
    characterized in that
    the at least one spring element (30) is connected by its one spring end (27) to the backrest support (4) and by its other spring end (28) not to the seat support (3) but to the coupling element (21) at a distance from the second transverse axis (19), such that a movement of the backrest brings about a movement of both spring ends (27, 28).
  2. Synchronous mechanism (100) according to Claim 1, wherein the one spring end (27) is connected to the backrest support (4) at a distance from the first transverse axis (11).
  3. Synchronous mechanism (100) according to Claim 1 or 2, wherein the spring ends (27, 28) of the at least one spring element (30) are connected to the backrest support (4) on the one hand and to the seat support (3) or to the coupling element (21) on the other hand such that a movement of the backrest brings about a change in the distance of the two spring ends (27, 28) from one another.
  4. Synchronous mechanism (100) according to Claim 3, wherein the spring ends (27, 28) of the at least one spring element (30) are connected to the backrest support (4) on the one hand and to the seat support (3) or to the coupling element (21) on the other hand such that a movement of the backrest brings about a decrease in the distance of the two spring ends (27, 28) from one another.
  5. Synchronous mechanism (100) according to Claim 3, wherein the spring ends of the at least one spring element (30) are connected to the backrest support (4) on the one hand and to the seat support (3) or to the coupling element (21) on the other hand such that a movement of the backrest brings about an increase in the distance of the two spring ends (27, 28) from one another.
  6. Synchronous mechanism (100) according to one of Claims 1 to 5, wherein the spring mechanism has means (43) for setting the spring force of the at least one spring element (30) such that the distance of at least one of the spring ends (27) of the at least one spring element (30) from the first transverse axis (11) and/or the distance of at least one of the spring ends (28) of the at least one spring element (30) from the second transverse axis (19) is variable.
  7. Synchronous mechanism (100) according to Claim 6, wherein the setting means (43) are configured such that the at least one positionally variable spring end (27) of the at least one spring element (30) is movable on a circular path with a substantially constant radius about the other spring end (28) of this spring element (30).
  8. Synchronous mechanism (100) according to Claim 6 or 7, wherein the setting means (43) have a cam mechanism, having a movably mounted cam carrier (44) and having a cam roller (45) which cooperates with the cam (46) of the cam carrier (44), wherein the cam roller (45) is connected to the at least one positionally variable spring end (27) of the at least one spring element (30) and is movable into positions with different spring forces by a movement of the cam carrier (44).
  9. Synchronous mechanism (100) according to Claim 8, wherein the cam roller (45) runs unilaterally on the cam (46) against which it is pressed by the at least one spring element (30).
EP16702659.0A 2015-02-03 2016-01-28 Synchronized mechanism Active EP3253254B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015101545.5A DE102015101545A1 (en) 2015-02-03 2015-02-03 synchronous mechanism
PCT/EP2016/000140 WO2016124317A1 (en) 2015-02-03 2016-01-28 Synchronized mechanism

Publications (2)

Publication Number Publication Date
EP3253254A1 EP3253254A1 (en) 2017-12-13
EP3253254B1 true EP3253254B1 (en) 2022-08-03

Family

ID=60239700

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16702659.0A Active EP3253254B1 (en) 2015-02-03 2016-01-28 Synchronized mechanism

Country Status (1)

Country Link
EP (1) EP3253254B1 (en)

Also Published As

Publication number Publication date
EP3253254A1 (en) 2017-12-13

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