WO2009007002A1 - Chaise, en particulier chaise de bureau - Google Patents

Chaise, en particulier chaise de bureau Download PDF

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Publication number
WO2009007002A1
WO2009007002A1 PCT/EP2008/005100 EP2008005100W WO2009007002A1 WO 2009007002 A1 WO2009007002 A1 WO 2009007002A1 EP 2008005100 W EP2008005100 W EP 2008005100W WO 2009007002 A1 WO2009007002 A1 WO 2009007002A1
Authority
WO
WIPO (PCT)
Prior art keywords
backrest
chair according
support
backrest support
restoring force
Prior art date
Application number
PCT/EP2008/005100
Other languages
German (de)
English (en)
Inventor
Armin Sander
Christopher Schmidt
Martin Potrykus
Original Assignee
König + Neurath AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by König + Neurath AG filed Critical König + Neurath AG
Priority to DE502008002234T priority Critical patent/DE502008002234D1/de
Priority to AT08773610T priority patent/ATE493910T1/de
Priority to EP08773610A priority patent/EP2173218B1/fr
Publication of WO2009007002A1 publication Critical patent/WO2009007002A1/fr

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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
    • A47C1/03255—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest with a central column, e.g. rocking office chairs
    • 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
    • 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
    • A47C1/03294—Reclining or easy chairs having coupled concurrently adjustable supporting parts the parts being movably-coupled seat and back-rest slidingly movable in the base frame, e.g. by rollers
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C31/00—Details or accessories for chairs, beds, or the like, not provided for in other groups of this subclass, e.g. upholstery fasteners, mattress protectors, stretching devices for mattress nets
    • A47C31/12—Means, e.g. measuring means for adapting chairs, beds or mattresses to the shape or weight of persons
    • A47C31/126—Means, e.g. measuring means for adapting chairs, beds or mattresses to the shape or weight of persons for chairs

Definitions

  • the invention relates to a chair, in particular an office chair with a Synchronme- s chanik with the features of the preamble of claim 1.
  • Modern office chairs are usually provided with a synchronous mechanism, which ensures that the seat moves synchronously with the backrest.
  • the synchronizing mechanism is usually formed by a seat support and a backrest support as well as sliding guide devices and / or pivot arrangements, with which these two parts are connected to one another and to the seat and / or the backrest.
  • the synchronous mechanism is designed such that a movement of the backrest 15 also leads to a change in the position of the seat. And indeed, the seat is tilted backwards down at a tilt of the backrest.
  • Office chairs with synchronous mechanism can be seen for example from DE 101 22 946 C1 or DE 101 22 948 C1. 0
  • an automatic adjustment of the restoring force exerted on the backrest support is provided by varying a lever arm length as a function of the current weight load.
  • a hinge element designed as a roller is provided on the backrest support, which is supported on a counteracting surface of a lever. The role is in vertical direction guided under a load of the seat support in the manner of a sliding guide along the reaction surface. The force exerted by a return spring restoring force is transmitted via the lever on the roller and thus the backrest support.
  • the invention has for its object to improve the automatic weight adjustment.
  • the object is achieved according to the invention by a chair having the features of claim 1.
  • the office chair which is designed in particular with a synchronous mechanism, comprises a seat support and a backrest support which can be tilted about a backrest and a weight mechanism for automatic weight-dependent adjustment of a restoring force acting on the backrest support.
  • the seat carrier and the backrest support are in this case suitably connected to one another via a synchronous mechanism in order to ensure the desired coupled movement between the backrest support and the seat support.
  • the weight mechanism comprises in particular a so-called Einwiegefederelement.
  • the restoring force is preferably provided an additional, independent of the Einwiegefederelement return spring.
  • the restoring force is transmitted to the backrest carrier via a hinged element.
  • An effective lever length is defined between the articulation element and the backrest pivot axis.
  • the weight mechanism is in this case designed such that automatically sets a larger lever length with increasing weight load.
  • the effective lever length is greater, the greater the current weight load, so the heavier the person who uses the chair. Since the restoring force is exerted via the return spring, the return spring engages in heavy people with a very large lever length with a torque. Due to the large lever length, the total load of heavy mechanical parts of the individual mechanical parts is kept comparatively low. In contrast to the solution to be taken from WO 2006/103000 A1, the mechanism can therefore be made lighter and therefore more cost-effective as a whole. According to an expedient development in this case the hinge element is guided relatively displaceable on the backrest support.
  • the backrest support itself moves with a weight load of the seat support together with this substantially in the vertical direction downwards and is thereby guided along the in the vertical direction substantially locally fixedly positioned articulation element. This increases the distance between the backrest pivot axis and the articulation element.
  • the backrest support is therefore part of a weighing unit, which is preferably moved linearly in a weight load down.
  • the back support comprises a leg, or generally an attack or counteracting surface on which the hinge element engages.
  • the entire weighing unit is preferably guided linearly parallel to this leg.
  • a weighing process, ie a weight load, therefore has no effect on angular orientation between the coupling element and the counteracting surface on the backrest carrier.
  • the orientation of the power transmission that is, the direction of the force application between the articulation element and the counteracting surface is therefore preferably independent of the current weight load.
  • the restoring force transmitted by the articulation element to the counteracting surface therefore acts on it at the same angle, irrespective of the weighing position.
  • the angular orientation between the articulation element or between the direction of the restoring force transmitted by the articulation element and the counteracting surface does not change during the weighing process.
  • the orientation of the force acting on the counteracting surface therefore remains the same, so that the amount of force in a predetermined direction remains the same.
  • neither the counteracting surface nor the direction of the restoring force transmitted by the articulation element change their orientation.
  • the position and orientation of the restoring force performing restoring element is not affected by Einwiegevorgang.
  • weighing only results in a linear adjustment of the counteracting surface, in particular in the vertical direction.
  • this is the introduction of force regardless of the weight load in terms of design optimized adjustable.
  • the backrest support and thus the counteracting surface is preferably rotated about the backrest axis of rotation.
  • the articulation element is arranged in the non-inclined initial state of the backrest support and, in particular in the direction of a rear end of the backrest support, slightly behind a vertical plane passing through the backrest pivot axis.
  • the engagement surface for the power transmission from the Anlanke- lement on the backrest support is arranged offset approximately in the vertical direction in alignment with the axis of rotation or slightly backwards in the direction of the backrest.
  • This arrangement of the engagement element "behind" the backrest axis of rotation positively influences the movement process with an inclination adjustment with respect to the force transmission, in particular a relatively perpendicular force application between the restoring force exerted by a return spring and the backrest support. that in the case of an inclination of the backrest support the articulation element at its attack surface on the backrest support quasi “wanders" upwards. This is for the desired right-angled force application advantage.
  • a substantially perpendicular deviation is understood as meaning a maximum deviation of up to 15 °, in particular of up to 10 °, in the non-tilted starting position. Even in the inclined position, the deviation is only in the range of a maximum of 15 ° to 20 ° relative to a right-angled force application.
  • the fulcrum axis of rotation is at the level and, in particular, below the lower end of the region of the backrest carrier against which the articulation element rests.
  • the coupling element is guided in a sliding guide designed in particular as a slot. This ensures safe guidance in a defined trajectory. At the same time the mobility within the slot allows a necessary freedom of movement in the operation of the synchronous mechanism, such as the backrest tilt adjustment.
  • the sliding guide is formed in a carrier unit which receives the seat support and the backrest support.
  • the carrier unit is therefore essentially the connection to a pedestal of the office chair.
  • the carrier unit is usually connected to the pedestal via a telescopic rod which can be extended to adjust the seat height.
  • the hinge element is therefore mounted in the carrier unit, in such a way that it is held substantially stationary in the axial direction.
  • the sliding guide is in this case preferably oriented approximately in a horizontal or slightly inclined direction, so that when the inclination of the backrest support the articulation element can escape against the spring force of the return element guided within the slot.
  • the sliding guide is formed on the backrest carrier and oriented substantially in the vertical direction.
  • the coupling element is guided in the backrest support itself and the slot allows the Relatiwerschiebung between hinge element and backrest support.
  • the coupling element preferably engages with guide pins in the respective slot.
  • the backrest support is formed in a side view in an approximately L-shaped, wherein abuts the one L-leg, the hinge element. This is in particular the shorter leg, whereas the seat back is attached to the longer L-leg.
  • the L-limb on which the articulation element ripens, in this case extends essentially approximately in the vertical direction.
  • the backrest support seen in cross-section, is preferably designed in the manner of a U-profile.
  • Slotted holes for the slat are provided in the side bolsters.
  • the hinge element is rotatable about a bearing axis, so that it rolls on a relative movement to the backrest carrier on this.
  • a comfortable and low-friction as possible relative movement between the hinge element and backrest support is possible even under load.
  • the articulation element is designed in particular in the manner of a roller or roller rotatable about a bearing axis. It is arranged between the two side cheeks of the U-profile. The bearing axis is guided at both ends each in the respective slot.
  • the power transmission takes place exclusively or at least for the most part via the roller in interaction with a counteracting surface on the backrest carrier.
  • the slot itself is therefore unencumbered by force.
  • the return spring engages in the region of the coupling element. Conveniently, it engages directly on the articulation element itself, for example on the laterally projecting end pieces of the bearing axis.
  • the return spring is stationary with respect to the Weighing process, ie their two ends take part in Einwiegevorgang at any movement. Rather, the return spring is arranged with its two ends on the carrier unit, which in turn is fixedly connected to the chair tube.
  • the weighing process ie the vertical adjustment of the weighing unit, which comprises the seat support and the backrest support, therefore have no influence on neither the vertical position nor on the tilting position of the return spring. Due to the fixed return spring, the direction of the introduction of force on the backrest carrier is decoupled from the current weight load in an advantageous manner.
  • the return spring can and is therefore oriented as low as possible with regard to the introduction of force into the backrest support with regard to a desired right-angled force application.
  • Such a rectangular force application generally has the advantage that in the region of the coupling element no or only small forces in vertical Direction occur that want to displace the backrest support from its vertical position up or down.
  • a mechanically complex locking of the once set restoring force is provided.
  • two mutually rotatably arranged locking elements are arranged, which can engage with each other.
  • the invention is therefore based on the object to enable an improved locking of the once set restoring force.
  • the weighting mechanism as Einwiegefederele- ment includes a particular against relaxing lockable gas spring.
  • the locking or blocking function is therefore integrated directly in the Einwiegefederelement.
  • Weighing in here means the preferably vertical adjustment of the seat carrier and the backrest support comprehensive weighing unit relative to a support unit which receives the Einwiegefederelement. During weighing, the weighing spring element is compressed due to the weight load.
  • the gas spring is therefore clamped between the seat support and the carrier unit and is compressed in a vertical load direction and blocked in this compressed position.
  • the effective lever length ie the distance between the hinge element and the fulcrum axis, fixed unchangeable.
  • the gas pressure spring preferably comprises a control element designed in particular as a control pin, which automatically transitions from a release position into a blocking position for a given load of the backrest or seat support, and vice versa. In the release position is
  • the control is arranged according to an expedient development and cooperates with the seat support such that it is already in the locked position before the compression of the gas spring takes place. This means that even before the actual weighing process, the gas spring is blocked, but only against a relaxation to allow a further Komprimie-o ren of the gas spring when weighing. Even a small load of the seat support therefore leads to a blockage of the gas spring, so that it is only in one direction, namely in the clamping direction, is functional until the blocking is released again.
  • a gas spring is used, which is blocked in a block both in the relaxation direction and in the clamping direction, in this an adjustment after blocking is no longer possible borrowed.
  • gas spring is preferably provided that the blocking takes place automatically in response to a defined inclination position of the backrest support. Since a tilt adjustment of the backrest support already presupposes a load on the seat support and thus a completed weighing-in operation, the gas pressure spring is blocked in this way only after the weighing process.
  • the blocking takes place here, for example, when the backrest support reaches a tilt adjustment of a few degrees, for example 10 °, starting from an upright starting position of the backrest. Conversely, the blocking is exactly solved again at this defined tilt position of the backrest carrier.
  • the blocking element is in a depressed, so acted upon with force, in its release position.
  • the blocking element is thus actively held in the release position.
  • the gas spring automatically switches to the blocked state.
  • the weighing unit comprising the backrest carrier and the seat carrier has an actuating lever acting on the control element.
  • This is designed according to a preferred embodiment as a first lever arm of a rocker element, wherein a second lever arm of the rocker element cooperates with the weighing unit.
  • the two arms in this case run approximately parallel to the plane of the seat, that is approximately horizontally.
  • a tilting movement At a defined load of the seat mechanism is a tilting movement, so that the operating lever releases the control and this passes from its depressed release position in its upwardly extended locking position and the gas spring is blocked.
  • For the transmission of the exerted weight force when weighing a connected to the seat support driver element is provided, which is mechanically connected to an extendable part of the gas spring.
  • the Einwiegevorgang so the burden of the seat support, therefore, does not lead to a tilting movement. This is triggered only when a tilt adjustment of the backrest carrier.
  • the driver element is preferably arranged relative to the latter in a guide element of the rocker element designed in particular as a slot-like recess for transmitting the applied weight force to the gas pressure spring.
  • the driver element is mounted displaceably in the vertical direction within the guide element. This makes it possible that already a displacement of the seat support in the vertical direction can be done without the gas spring is compressed. Rather, this creates a certain freedom and latitude, so that it is certainly ensured that initially the tilting movement to block the gas spring takes place before the gas spring is compressed.
  • FIGS. Each shows in schematic, partially simplified representations:
  • 1A is a side view of an office chair with synchronous mechanism
  • FIG. 1B shows the office chair according to FIG. 1A in the loaded state when the synchronous mechanism with inclined backrest is actuated
  • FIG. 2A shows a perspective view of a seat mechanism
  • FIG. 2B shows the illustration according to FIG. 2A in section
  • FIG. 1B shows the office chair according to FIG. 1A in the loaded state when the synchronous mechanism with inclined backrest is actuated
  • FIG. 2A shows a perspective view of a seat mechanism
  • FIG. 2B shows the illustration according to FIG. 2A in section
  • Fig. 3A is a side view in section of the seat mechanism of FIG. 2A in the unloaded, non-weighed state in the upright position of the backrest
  • FIG. 3B shows a representation according to FIG. 3A in the maximally loaded, in-loaded state
  • FIG. 4A is a side view in section of the seat mechanism according to FIG. 2A in the unloaded, non-weighed-in state in the inclined position of the backrest
  • Fig. 4B is a view according to FIG. 4A in the maximum loaded, weighed state
  • Fig. 5 is a side view in section of the seat mechanism of FIG. 2A in the unloaded, non-weighed state at an inclined intermediate position of the backrest between the positions shown in FIGS. 3A and 4A
  • FIG. 6 is a fragmentary perspective views of the seat mechanism of a first alternative embodiment
  • Fig. 7 is a side view of the seat mechanism of a second alternative embodiment
  • FIG. 1A.1B office swivel chair with synchronous mechanism comprises a back 2, a seat 4, a arranged below the seat 4 seat mechanism 6, in which the individual mechanical components for forming a synchronous mechanism and a weight mechanism are at least partially integrated, and a Standpipe 8, which is connected to a foot part, not shown here.
  • the standpipe 8 is usually formed as a telescopic tube over which a height adjustment can be made.
  • the office swivel chair is equipped with a synchronous mechanism, so that the movement of the seat 4 and the back 2 are coupled together. Namely, when the backrest 2 is moved from the position shown in FIG. 1A to the position shown in FIG. 1B, the seat 4 is transferred from the substantially horizontal orientation of FIG. 1A to the obliquely rearward inclined position.
  • the synchronous mechanism in particular comprises a backrest support 12, via which the backrest 2 is fastened. Furthermore, the synchronizing mechanism comprises a seat support 14 which carries the seat 4.
  • the seat support 14 and the backrest support 12 articulated or mutually displaceable interconnected.
  • the connection of the individual elements takes place at so-called articulation points.
  • the seat mechanism 6 comprises a cup-like design in the embodiment support unit 16, which is connected to the Fig. 1A.1 B entsecuredem standpipe 8.
  • the seat mechanism 6 further comprises the backrest support 12 and the seat support 14, which are rotatably connected to one another to form the coupled synchronous movement, inter alia via a rear armature axis 18.
  • the backrest support 12 is viewed from the side approximately L-shaped, wherein the shorter L-leg 12A in the upright position of the backrest in the embodiment extends in the vertical direction, whereas the longer L-leg 12B is approximately horizontal.
  • the longer L leg 12B is bent downwards in its rearward region oriented towards the backrest 2.
  • the backrest support 12 in each case has side cheeks, that is, when viewed in cross-section, it is approximately U-shaped. As can be seen in particular from the sectional views, for example from FIG. 2B, the center part connecting the two side cheeks, in particular for reasons of stability, has a different curved course in its rear part than the side cheeks.
  • the shorter L-leg 12A is rotatably mounted via a arranged at its lower end armature pivot axis 20, so that upon tilt adjustment of the backrest support 12, a rotation about the arm pivot axis 20 takes place.
  • the roller 22 is rotatable about a bearing axis 24.
  • the bearing axis 24 protrudes on both sides of the roller 22 and extends substantially horizontally, only slightly obliquely inclined backward slots 26 which are formed in side cheeks of the support unit 16.
  • At the outer ends of the bearing shaft 24 engages in each case one in the embodiment designed as a tension coil spring return spring 28, which is coupled with its front end to an abutment of the support unit 16.
  • a restoring force is generated, which counteracts a tilt adjustment of the backrest support 12, so this pulls in its upright position.
  • the return spring 28 is slightly backwards relative to the horizontal on the backrest support.
  • roller 22 is also fixedly mounted within the carrier unit 16, as defined by its mounting in the elongated holes 26, vertical movement of the seat carrier 14 has no effect on the position of the return spring 28 in a so-called weighing-in process.
  • the elongated holes 26 are in this case Oriented substantially in the longitudinal direction of the return spring 28, thus have approximately the same inclination with respect to the horizontal as the return spring 28th
  • This restoring force is automatically adjusted depending on the current weight load of the seat support 14 such that at a high weight load, a high restoring force and at a low weight load, a lower restoring force is exerted.
  • a so-called weighing-in process is provided in which a weighing unit comprising the seat support 14 and the backrest support 12 is moved differently in the axial direction as a function of the current weight load relative to the support unit 16.
  • This weighing process takes place here against the spring force of a spring element, which is formed in the embodiment as a lockable gas spring 30.
  • the gas spring is further attached to the support unit 16.
  • an elastic restoring force exerting element can be provided.
  • the backrest axis 20 is mounted in a central support part 31 (cf., for example, FIG. 2B, FIG. 3A).
  • the central support part 31 is part of the seat support 14 and the Leh- nenany 12 forming weighing unit and is guided with these in the vertical direction relative to the carrier unit 16 slidably.
  • the entire weighing unit is in this case guided in a linear guide on the carrier unit 16.
  • the linear guide is formed by a tube receiving the gas pressure spring 30, which is encompassed by a sleeve of the weighing unit which is arranged on the carrier part 31 in the exemplary embodiment (see Fig. 2B).
  • the roller 22 and the return spring 28 are held stationary with respect to the Weighing process.
  • the vertical adjustment of the weighing unit during the weighing operation therefore has no effect on the position of the roller 22 and the return spring 28.
  • the end of the return spring 28 acting on the roller 22 is guided obliquely backwards only at a tilt adjustment, so that the return spring is tensioned ,
  • the support part 31 is connected at its upper end to the seat support 14 via a pin 32 which is slidably guided in a slot-like recess 33 in a cheek of the seat support 14.
  • the support member 31 is connected to the backrest support 12, via the backrest pivot 20th
  • This mechanism of the weight-dependent weighing-in operation can best be deduced from a comparison of FIGS. 3A and 3B or a comparison of FIG. 4A.4B.
  • the entire weighing unit, comprising in particular the seat support 14, the back support 12 and the central support member 31 is moved from the unloaded or slightly loaded initial position shown in FIG. 3A in the vertical direction down to the support unit 16. This is done against the spring force of the gas spring 30.
  • the central support member 31 is connected via a driver element with the extendable piston 34.
  • the driver element is arranged at the upper end of the piston 34 and surrounds this in the manner of a perforated disc.
  • the weight mechanism is designed so that in heavy people as long a lever length is set so that the force exerted on the return spring 28 force is transmitted over as long a lever arm on the backrest support 12.
  • the load on the mechanical components of the weight mechanism is kept comparatively low, as a result of which the components can be made comparatively light or the risk of mechanical failure of the components is low.
  • the vertical L-leg 12A rotates about the backrest pivot 20 to the right, as can be seen from the comparison of Fig. 3A, 3B with Figs. 4A.4B. Due to this movement takes place at the same time a compensating movement of the roller 22 in approximately horizontal direction, which is made possible by the storage of the bearing axis 24 in the slots 26 of the support unit 16. At the same time, the roller 22 rolls slightly off the vertical L-leg 12A when tilted. For a possible noise and low friction rolling the roller 22 is provided for example with a rubber coating or other suitable surface, which is mounted on a metallic base body.
  • the vertical L-leg 12B is substantially aligned with the backrest pivot axis 20, i.
  • the backrest pivot axis 20 and the short L-leg 12B are at least approximately in a vertical plane.
  • the articulation element 22 is likewise arranged approximately offset in this vertical plane or slightly to the rear. Only in the case of an inclination adjustment does the roller 22 move out of the area of this vertical plane to the rear. Of particular importance here is that the bearing axis 24 of the roller 22 is at least not arranged in front of the vertical plane in the initial state. In this way, in fact, it is achieved that during the tilting process, the roller 22 as a compensating movement quasi rolls on the vertical L-leg 12B upwards and not downwards, which has a favorable effect on the introduction of force.
  • a blocking of this effective lever length is additionally provided in the exemplary embodiment, so that the restoring force exerted on the backrest support 12 does not occur for example, adjusted during a movement of the person on the seat.
  • the gas pressure spring 30 has an extendable piston 34, at the upper end of which in turn is designed as a control pin 35 control is provided.
  • the control pin 35 is biased toward its extended position, which occupies the control pin 35 in the embodiment from a defined inclination of the backrest support 12.
  • This extended position of the control pin 35 in which it passes automatically due to the bias voltage, unless it is pressed down by force actuation, corresponds to a blocking position in which the blocking of the gas spring 30 is active. Conversely, the depressed position of the control pin 35 corresponds to a release position in which the blockage is canceled.
  • the position of the piston 34 In a blocking of the gas spring 30, the position of the piston 34 is fixed, ie it is in the embodiment, neither compressing nor relaxing the gas spring 30 possible.
  • an actuating lever 36 For actuating the control pin 35, an actuating lever 36 is provided which presses the control pin 35 in a starting position in a force-actuated manner downwards.
  • the actuating lever 36 is in the exemplary embodiment, a lever arm of a two-armed rocker element 38.
  • the rocker element 38 therefore has a second lever arm 40 which is connected in the illustrated embodiment with the backrest support 12. It is supported, in particular, on the upper side of the horizontally extending L-leg 12B.
  • a tilting axis 42 about which the rocking element 38 can tilt is mounted on the central support part 31 of the seat mechanism 6.
  • the tilting axis 42 is now substantially in alignment with the Lehnenfitachse 20, at best slightly offset to this aligned. It is essential that the second lever arm 40 can perform a tilting movement at an inclination of the backrest support 12.
  • the sequence of movement and the blocking of the gas spring 30 can best be seen from a comparison of FIGS. 3A, 4A and 5.
  • FIG. 5 shows an intermediate position in which the backrest support 12 assumes an inclination, from which the gas pressure spring 30 is blocked. With an inclination of the backrest support 12, the horizontally extending L-leg 12 B lowers slightly downwards. Due to the bias of the control pin 35, therefore, the left lever arm (operating lever 36) can be pushed upwards.
  • the second right lever arm 40 can also be coupled via a positive guide to the backrest support 12, so that it is actively pulled downwards.
  • the rocker element 38 is now designed and positioned such that from a certain angle of inclination in an intermediate position, as shown in Fig. 5, the control pin 35 is extended and the gas spring 30 is blocked. In the embodiment, this is approximately in the range of an inclination angle between 5 ° and 10 ° of the backrest support 12, based on an originally particular vertical orientation in the upright backrest position. Conversely, when the backrest support 12 is returned to the upright position, the control pin 35 is forcibly pressed again and the blocking of the gas pressure spring 30 is canceled.
  • a large lever length is automatically set at a high weight load.
  • the bearing axis 24 of the roller 22 is guided in slots 26 of the backrest support 12.
  • the bearing axle 24 is connected to the carrier unit 16 via a connecting lever 50.
  • the connecting lever 50 has a bolt receptacle 51.
  • the return springs 28 engage a bolt 52, which is guided by the connecting lever 50 and the slots 26.
  • the bolt 52 is hereby positioned slightly below the bearing axis 24.
  • the backrest support 12 is pushed down in the vertical direction, so that the roller 22 rolls on the vertical L-leg 12A.
  • the effective lever length is in turn defined by the bearing axis 24 and the backrest pivot axis 20, which in turn is formed in the lower region of the backrest support 12.
  • the force exerted on the restoring spring 28 is applied to the inside of the vertical arm via the articulation element designed as a roller 22.
  • Leg 12A transferred, which forms a counteracting surface.
  • the slots 26 are only used to guide the bearing axis 24, but otherwise are unloaded.
  • Fig. 7 shows an alternative embodiment for the operation of the lockable gas spring 30.
  • a special form of a lockable gas spring 30 is provided, namely one which is only blockable against relaxation.
  • the rocker element 38 is arranged on the seat support 14 instead of the backrest support 12.
  • the second lever arm 40 is mounted on the seat support 14.
  • the rocker element 38 has an approximately triangular recess 54 in the exemplary embodiment, in which an actuating pin 56 of the central support part 31 engages. In the starting position shown in FIG. 7, the actuating pin 56 due to the recess 54 has an alternative possibility in the vertical direction, so it can move upwardly within the recess 54.
  • a helical spring 58 which additionally supports the gas pressure spring 30 is additionally provided.
  • the weight mechanism for varying the effective lever length is similar to the embodiment of FIGS. 2 to 5 formed.

Landscapes

  • Health & Medical Sciences (AREA)
  • Dentistry (AREA)
  • General Health & Medical Sciences (AREA)
  • Chairs Characterized By Structure (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Hydrogenated Pyridines (AREA)

Abstract

L'invention concerne une chaise, en particulier une chaise de bureau avec un mécanisme de synchronisation. Pour réaliser un ajustement automatique en fonction du poids d'une force de rappel exercée sur un dossier (2), la force de rappel est transmise selon l'invention par un élément de liaison (22) au support (12) du dossier, et une longueur de levier est définie entre l'élément de liaison (22) et un axe de rotation (24) du dossier, une plus grande longueur de levier étant ajustée avec l'augmentation de la contrainte de poids. Avantageusement, pour la fixation de la longueur de levier active ajustée, on utilise un ressort de pression à gaz (30) pouvant être bloqué, qui, dans la position bloquée, empêche toute modification de la longueur de levier efficace.
PCT/EP2008/005100 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau WO2009007002A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE502008002234T DE502008002234D1 (de) 2007-07-07 2008-06-24 Stuhl, insbesondere bürostuhl
AT08773610T ATE493910T1 (de) 2007-07-07 2008-06-24 Stuhl, insbesondere bürostuhl
EP08773610A EP2173218B1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007031790.7 2007-07-07
DE102007031790 2007-07-07

Publications (1)

Publication Number Publication Date
WO2009007002A1 true WO2009007002A1 (fr) 2009-01-15

Family

ID=39758738

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/005100 WO2009007002A1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau

Country Status (5)

Country Link
EP (2) EP2173218B1 (fr)
AT (2) ATE493910T1 (fr)
DE (1) DE502008002234D1 (fr)
ES (2) ES2382726T3 (fr)
WO (1) WO2009007002A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022125681A1 (de) 2022-10-05 2024-04-11 Amir Anvarovich Fatkullin Stuhl

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2844109B1 (fr) 2012-05-04 2017-08-30 Itoki Corporation Chaise, en particulier chaise de bureau

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5308144A (en) * 1989-05-20 1994-05-03 Roeder Gmbh Chair, in particular work or office chair
US20050140183A1 (en) * 2003-12-01 2005-06-30 J. Robert Britton & Associates, Inc. Reclining chair with foot and leg rest
DE202005004880U1 (de) * 2005-03-26 2006-08-03 Sander, Armin Stuhl, insbesondere Bürostuhl
DE202005011725U1 (de) * 2005-07-27 2006-12-07 Sander, Armin Stuhl, insbesondere Bürostuhl

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH659179A5 (en) * 1983-05-06 1987-01-15 Provenda Marketing Ag Working chair, especially an office chair
DE4020868C1 (fr) * 1990-05-01 1992-02-06 Roeder Gmbh Sitzmoebelwerke, 6000 Frankfurt, De
DE10215285A1 (de) * 2002-04-07 2003-10-16 Christian Erker Sitzschale mit Neigungs-Konturkoppelungsmechanismus
DE102004053965B4 (de) * 2004-11-09 2006-10-12 Girsberger Holding Ag Stuhl

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5308144A (en) * 1989-05-20 1994-05-03 Roeder Gmbh Chair, in particular work or office chair
US20050140183A1 (en) * 2003-12-01 2005-06-30 J. Robert Britton & Associates, Inc. Reclining chair with foot and leg rest
DE202005004880U1 (de) * 2005-03-26 2006-08-03 Sander, Armin Stuhl, insbesondere Bürostuhl
DE202005011725U1 (de) * 2005-07-27 2006-12-07 Sander, Armin Stuhl, insbesondere Bürostuhl

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022125681A1 (de) 2022-10-05 2024-04-11 Amir Anvarovich Fatkullin Stuhl

Also Published As

Publication number Publication date
ATE493910T1 (de) 2011-01-15
EP2173218B1 (fr) 2011-01-05
EP2301390B1 (fr) 2012-03-28
DE502008002234D1 (de) 2011-02-17
EP2301390A1 (fr) 2011-03-30
ES2382726T3 (es) 2012-06-12
ATE550971T1 (de) 2012-04-15
EP2173218A1 (fr) 2010-04-14
ES2359678T3 (es) 2011-05-25

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