EP2301390A1 - Siège, en particulier chaise de bureau - Google Patents

Siège, en particulier chaise de bureau Download PDF

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Publication number
EP2301390A1
EP2301390A1 EP10014355A EP10014355A EP2301390A1 EP 2301390 A1 EP2301390 A1 EP 2301390A1 EP 10014355 A EP10014355 A EP 10014355A EP 10014355 A EP10014355 A EP 10014355A EP 2301390 A1 EP2301390 A1 EP 2301390A1
Authority
EP
European Patent Office
Prior art keywords
backrest
support
chair according
backrest support
seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10014355A
Other languages
German (de)
English (en)
Other versions
EP2301390B1 (fr
Inventor
Armin Sander
Christopher Schmidt
Martin Potrykus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koenig and Neurath AG
Original Assignee
Koenig and 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 Koenig and Neurath AG filed Critical Koenig and Neurath AG
Publication of EP2301390A1 publication Critical patent/EP2301390A1/fr
Application granted granted Critical
Publication of EP2301390B1 publication Critical patent/EP2301390B1/fr
Active legal-status Critical Current
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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 synchronous mechanism having the features of the preamble of claim 1.
  • Such a chair is from the WO 2006/193000 A1 known.
  • 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 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 are for example from the DE 101 22 946 C1 or the DE 101 22 948 C1 refer to.
  • an automatic adjustment of the force exerted on the backrest support restoring force by a lever arm length is varied depending on 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 restoring force automatically adjusts depending on the currently exerted weight load, there is the problem that with a short-term variation of the weight load - for example, by a movement of the person sitting on the chair - the restoring force sets to a new value.
  • the WO 2006/103000 A1 provided a mechanically complex locking the once set restoring force.
  • 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 weight mechanism comprises as Einwiegefederelement 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.
  • When weighing the Einwiegefederelement is compressed due to the weight load.
  • the automatic weight-dependent adjustment of the restoring force acting on the backrest support which is dependent on the relative position of the weighing unit to the carrier unit. Namely, by this relative position, an effective lever length between a hinge element, on which the restoring force engages, and the lean axis of rotation set.
  • the restoring force is exerted by an additional, indirectly or directly acting on the articulation return spring.
  • the gas spring is therefore clamped between the seat support and the carrier unit and is compressed at a weight load in the vertical 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.
  • the release position in this case the blocking of the gas spring is canceled, whereas it is active in the locked position. It is therefore no manual actuation required, but there is an automatic transfer between the release and the locked position.
  • This automatic actuation takes place here optionally as a function of a weight load of the seat or backrest support or a tilt adjustment of the backrest support.
  • the control acts in this case generally on a valve which prevents the overflow of a fluid between two pressure chambers of the gas spring in the locked position or releases.
  • 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 further compression 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 they only still 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.
  • 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 process, the gas 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 formed 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.
  • the driver element is preferably arranged relative to this in a particular designed as a slot-like recess guide element of the rocker element for transmitting the exerted weight force on the gas 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.
  • the office chair designed in particular with a synchronous mechanism generally comprises a seat support and a backrest support that can be tilted about a backrest axis, and a weight mechanism for the automatic weight-dependent adjustment of a restoring force acting on the backrest support.
  • the seat support and the backrest support are in this case connected to each other in a suitable manner via a synchronous mechanism in order to ensure the desired coupled movement between the backrest support and the seat support.
  • the weight mechanism includes the Einwiegefederelement.
  • the restoring force is preferably provided an additional, independent of the Einwiegefederelement return spring.
  • the restoring force is transmitted via a coupling element on the backrest carrier.
  • An effective lever length is defined between the articulation element and the backrest pivot axis.
  • the weight mechanism here is preferably designed such that with increasing weight load automatically sets a longer lever length.
  • 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 occurring in heavy people total burden of the individual mechanical parts is kept relatively low. Unlike the one from the WO 2006/103000 A1 To be taken solution, the mechanism can therefore be made easier and thus more cost-effective.
  • 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 substantially vertically positioned in the vertical direction of the pivoting element. This increases the distance between the backrest pivot axis and the articulation element.
  • the backrest support is therefore part of the 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 coupling element to the counteracting surface therefore acts on it - regardless of the weighing state - at the same angle.
  • 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 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.
  • only a linear adjustment of the counteracting surface takes place, especially in the vertical direction, when weighing.
  • this is the introduction of force regardless of the weight load in terms of design optimized adjustable.
  • only the backrest support and thus the counteracting surface is preferably rotated about the backrest axis of rotation.
  • the restoring force exerted by the articulation element remains unchanged with respect to the direction. This is achieved in that the restoring element and the articulation element do not change their angular position, ie the articulation points of the restoring element only move linearly relative to one another.
  • 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 attack surface for the transmission of force from the coupling element to the backrest support is arranged to be offset approximately in the vertical direction in alignment with the axis of rotation or somewhat backwards in the direction of the backrest.
  • the restoring force transmitted by the articulation element engages in the non-inclined initial state essentially at right angles to the backrest carrier.
  • 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 relative displacement between the 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-leg on which the coupling element engages 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.
  • elongated holes are provided for the hinge element in the side cheeks.
  • 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 articulation 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
  • the weighing unit comprising the seat support and the backrest support, therefore, have no influence on neither the vertical position nor 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 respective 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 no or only small forces occur in the vertical direction in the region of the coupling element, which want to displace the backrest carrier from its vertical position upwards or downwards.
  • FIG. 1A, 1B illustrated office swivel chair with synchronous mechanism comprises a backrest 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 not one here represented foot part is connected.
  • 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. And that is in an adjustment of the back 2 of the in Fig. 1A shown position in the Fig. 1B shown position of the seat 4 of the substantially horizontal orientation according to Fig. 1A transferred to the obliquely backward 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 are hinged or mutually displaceable with each other.
  • the connection of the individual elements takes place at so-called articulation points.
  • the basic structure of the in the Fig. 2A to 5 shown seat mechanism 6 results in particular from the illustration according to the Fig. 2A . 2 B , Thereafter, the seat mechanism 6 comprises a cup-like design in the embodiment carrier unit 16, with the from the Fig. 1A, 1B is connected to entmanneddem standpipe 8.
  • the seat mechanism 6 further comprises the backrest support 12 and the seat support 14, which are rotatably connected to each other via a rear pivot axis 18 to form the coupled synchronous movement, inter alia.
  • 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 12 B is formed bent downwards in its rear, oriented towards the back 2 area.
  • the backrest support 12 in each case has side cheeks, that is, when viewed in cross-section, it is approximately U-shaped.
  • the shorter L-leg 12A is rotatably mounted via a arranged at its lower end armature pivot axis 20, so that in a 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 inclined relative to the horizontal slightly to the rear on the backrest support 12, and at an angle of about 5 ° to 15 °. Since the roller 22 is also fixedly mounted within the carrier unit 16 as defined by its bearing in the elongated holes 26, a 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 operation is provided, in which a weighing unit which comprises 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 lean axis 20 is for this purpose mounted in a central support member 31 (see, eg Fig. 2B . Fig. 3A ).
  • the central support part 31 is part of the weighing unit 14 forming the seat support 14 and the backrest support 12 and is displaceably guided with the latter in the vertical direction relative to the support unit 16.
  • 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 gas spring 30 receiving tube, which is encompassed by a arranged in the embodiment of the support member 31 sleeve of the weighing unit (see. Fig. 2B ).
  • the roller 22 and the return spring 28 are held stationary with respect to the Weighing process.
  • the weighing process Vertical adjustment of the weighing unit therefore has no effect on the position of the roller 22 and the return spring 28.
  • the acting on the roller 22 end of the return spring 28 is performed only at a tilt adjustment obliquely backwards, so that the return spring is tensioned.
  • the support member 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. At its lower portion, the support member 31 is connected to the backrest support 12, via the backrest pivot 20th
  • This mechanism of weight-based weighing-in process is best based on a comparison of the Fig. 3A and 3B or a comparison of Fig. 4A . 4B remove.
  • the entire weighing unit, comprising in particular the seat support 14, the backrest support 12 and the central support member 31 is of the in the Fig. 3A shown unloaded or slightly loaded starting position in the vertical direction down to the carrier unit 16 moves. 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 the lever length is set as long as possible for heavy persons, so that the force exerted on the return spring 28 Force is transmitted to the backrest support 12 over as long a lever arm as possible.
  • the load on the mechanical components of the weight mechanism is kept comparatively low.
  • the components can be made relatively easy 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 the Fig. 4A . 4B results. 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 fulcrum 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 with a tilt adjustment, the roller 22 moves out of the region 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 adjust, for example, during 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.
  • control pin 35 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 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-shaped ice 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 movement and the blocking of the gas spring 30 is best from a comparison of Fig. 3A . 4A and 5 refer to.
  • the Fig. 5 shows here an intermediate position in which the backrest support 12 assumes an inclination, from which the gas spring 30 is blocked.
  • the horizontally extending L-leg 12 B 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. As an alternative to the loose support of the second right lever arm 40, it 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 in Fig. 5 is shown, the control pin 35 extended and the gas spring 30 is blocked is. 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 arm pivot axis 20, which in turn is formed in the lower region of the backrest support 12.
  • the force exerted on the return spring 28 force is transmitted via the coupling element 22 formed as a roller on the inside of the vertical L-leg 12 A, which forms a counteracting surface.
  • the slots 26 are only used to guide the bearing axis 24, but otherwise are unloaded.
  • the Fig. 7 shows an alternative embodiment for the actuation 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.
  • Another difference to the one to the Fig. 2 to 5 described embodiment is the fact that the rocking element 38 on the seat support 14 is arranged 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.
  • an actuating pin 56 of the central support part 31 engages.
  • Fig. 7 is in addition to the gas spring 30 in addition to a gas spring 30 supporting coil spring 58 is provided.
  • the weight mechanism for varying the effective lever length is similar to the embodiment of the Fig. 2 to 5 educated.
EP10014355A 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau Active EP2301390B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007031790 2007-07-07
EP08773610A EP2173218B1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP08773610.4 Division 2008-06-24

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EP2301390A1 true EP2301390A1 (fr) 2011-03-30
EP2301390B1 EP2301390B1 (fr) 2012-03-28

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EP08773610A Active EP2173218B1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau
EP10014355A Active EP2301390B1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau

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EP08773610A Active EP2173218B1 (fr) 2007-07-07 2008-06-24 Chaise, en particulier chaise de bureau

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EP (2) EP2173218B1 (fr)
AT (2) ATE493910T1 (fr)
DE (1) DE502008002234D1 (fr)
ES (2) ES2359678T3 (fr)
WO (1) WO2009007002A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104470404B (zh) 2012-05-04 2019-07-05 株式会社伊藤喜 办公椅
DE102022125681A1 (de) 2022-10-05 2024-04-11 Amir Anvarovich Fatkullin Stuhl

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4682814A (en) * 1983-05-06 1987-07-28 Provenda Marketing Ag Tilting seat and back chair, particularly tilting desk chair
DE4020868C1 (fr) * 1990-05-01 1992-02-06 Roeder Gmbh Sitzmoebelwerke, 6000 Frankfurt, De
EP1352595A2 (fr) * 2002-04-07 2003-10-15 Christian Erker Coque de siège avec dispositif de réglage de l'inclinaison et du contour
EP1654959A1 (fr) * 2004-11-09 2006-05-10 Girsberger Holding AG Chaise

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3916474A1 (de) * 1989-05-20 1990-11-22 Roeder Soehne Sitzmoebelfab Stuhl, insbesondere arbeits- oder buerostuhl
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4682814A (en) * 1983-05-06 1987-07-28 Provenda Marketing Ag Tilting seat and back chair, particularly tilting desk chair
DE4020868C1 (fr) * 1990-05-01 1992-02-06 Roeder Gmbh Sitzmoebelwerke, 6000 Frankfurt, De
EP1352595A2 (fr) * 2002-04-07 2003-10-15 Christian Erker Coque de siège avec dispositif de réglage de l'inclinaison et du contour
EP1654959A1 (fr) * 2004-11-09 2006-05-10 Girsberger Holding AG Chaise

Also Published As

Publication number Publication date
EP2173218B1 (fr) 2011-01-05
EP2301390B1 (fr) 2012-03-28
ATE550971T1 (de) 2012-04-15
DE502008002234D1 (de) 2011-02-17
WO2009007002A1 (fr) 2009-01-15
ATE493910T1 (de) 2011-01-15
EP2173218A1 (fr) 2010-04-14
ES2359678T3 (es) 2011-05-25
ES2382726T3 (es) 2012-06-12

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