EP2313291A1 - Ferrure d'articulation de basculement pour un siège de véhicule - Google Patents

Ferrure d'articulation de basculement pour un siège de véhicule

Info

Publication number
EP2313291A1
EP2313291A1 EP09780724A EP09780724A EP2313291A1 EP 2313291 A1 EP2313291 A1 EP 2313291A1 EP 09780724 A EP09780724 A EP 09780724A EP 09780724 A EP09780724 A EP 09780724A EP 2313291 A1 EP2313291 A1 EP 2313291A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
bearing surface
clamping
taumelgelenkbeschlag
degrees
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.)
Withdrawn
Application number
EP09780724A
Other languages
German (de)
English (en)
Inventor
Thomas Thiel
Reinhard Vogel
Burckhard Becker
Wilfried Beneker
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.)
Johnson Controls Metals and Mechanisms GmbH and Co KG
Original Assignee
C Rob Hammerstein GmbH
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 C Rob Hammerstein GmbH filed Critical C Rob Hammerstein GmbH
Publication of EP2313291A1 publication Critical patent/EP2313291A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
    • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
    • B60N2/2252—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms in which the central axis of the gearing lies inside the periphery of an orbital gear, e.g. one gear without sun gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
    • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
    • B60N2/2254—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms provided with braking systems

Definitions

  • the invention relates to a Taumelgelenkbeschlag for a vehicle seat with a first articulated arm, which a) carries an internal gear and b) forms a first bearing surface, wherein the internal gear and the first bearing surface are central to a main axis, with a second articulated arm, which is associated with an eccentric a) has an externally toothed pinion which is located within and is in engagement with the internal gear, and b) has a second bearing surface, wherein pinion and second bearing surface are centered to an eccentric axis, with an eccentric driving part, which in the area between the first Bearing surface and second bearing surface is arranged, and with clamping parts which move in a clamping state, the eccentric axis relative to the main axis, whereby the Taumelgelenkbeschlag is made possible backlash.
  • Such a Taumelgelenkbeschlag also referred to as Getriebegelenkbeschlag is known from DE 10 2004 007 043 B3.
  • Taumelgelenkbeschlag are the clamping parts, which are formed as wedge segments, within the Exzenter dealt with the Exzenter facedeil, more precisely between the Exzenter facedeil and the first bearing surface.
  • the wedge segments are part of the eccentric, together with the Exzenter facedeil they define the eccentric.
  • the Exzenter consideredeil is designed as a complete ring.
  • the second articulated arm may be rigidly connected to the eccentric wheel, but it may also be another wobble mechanism between the second articulated arm and the eccentric, whereby the tumbling motion is not felt outside the driving handwheel or motor.
  • a disadvantage of the Taumelgelenkbeschlag the particular type mentioned is that the clamping parts must be designed as wedge elements or wedge segments and in particular that they define the eccentric. As a result, you are limited both in the geometric design of the clamping parts and in their arrangement within the Taumelgelenkbeschlags.
  • the wedge segments in the Taumelgelenkbeschlag of the aforementioned type have a dual function, they are both the means that balances the play and the means that defines the eccentric. Thus their position within the fitting also determines the location at which the eccentrically acting forces actually act on a drive.
  • the inventive design has the advantage that the clamping parts can be arranged at their optimum position within the hinge fitting. They can be optimally designed for a clamping function. They do not have to be designed as wedges, they can for example be designed as rollers, balls, clamping stilts, eccentric parts. Their shape is no longer determined by the crescent-shaped course between the eccentric drive part and either first bearing surface or second bearing surface as in the prior art, but the clamping parts can also be supported on non-round parts. This applies in particular to the geometric design of the support of the clamping parts on Exzenter capitaeil. The clamping parts are now designed exclusively for the clamping function. Their design does not have to take account of the eccentric function.
  • the clamping parts preferably cooperate with the first bearing surface. This forms a support surface for the clamping parts.
  • the other, more outer support surface of the clamping parts is formed on the Exzenterilloneil and does not necessarily have to be round, they can run arbitrarily within wide limits. This achieves more favorable clamping conditions.
  • the clamping parts can also interact with the second bearing surface.
  • the other, more inboard support surface is formed on the eccentric drive and also does not necessarily have to be round, they can run arbitrarily within wide limits.
  • An eccentric vector is defined by a root located on the major axis, a peak pointing to the eccentric axis, and a direction perpendicular to the major axis.
  • an eccentric region is provided, which extends in an angular range of ⁇ 30 °, preferably ⁇ 45 ° and in particular ⁇ 60 ° to the eccentric vector.
  • the eccentric area is in contact with the first bearing surface or the second bearing surface.
  • the clamping parts can be arranged at an angular distance from the eccentric vector, which is substantially larger than in the prior art.
  • the angular distance is chosen so that its support function is optimized in terms of clearance compensation.
  • the clamping parts are associated with the Exzenter facedeil. In this way, the clamping parts inevitably make the movement of the Exzenter consideredeils.
  • the first bearing surface and / or the second bearing surface can be cylindrical. Special guide areas or supporting flanks for the clamping parts are provided in the eccentric drive part.
  • the clamping parts themselves may have any shape, for example, be wedge-shaped. They can extend over a relatively large angular range, for example up to 90 °.
  • the decisive factor is where they actually have contact on the one hand with the first bearing surface or the second bearing surface and on the other hand with the Exzenter facedeil.
  • the location of these contact points means the location of the actual support. It is this actual support that positions arbitrarily can be.
  • the support is such that it is optimally designed for backlash compensation when absorbing high forces.
  • the shape of the clamping parts outside the contact points can be adapted to the respective requirements. This concerns, inter alia, the control of the clamping parts between a clamping state and a neutral state.
  • the invention Taumelgelenkbeschlag is the inclusion of high, accidental forces.
  • the clamping parts play virtually no role.
  • FIG. 1 is a perspective view in the form of a mounting pattern of a first embodiment of the Taumelgeschbeschlags, but without spring,
  • FIG. 2 is a perspective view from the front, in Figure 1 from the right, on the assembled Taumelgelenkbeschlag, but without control part and without drive,
  • Fig. 3 a perspective view as Figure 2, but now with
  • FIG. 4 shows a plan view similar to FIG. 3 of a second exemplary embodiment that largely corresponds to the first exemplary embodiment
  • FIG. 5 shows a view as in FIG. 4, for a third embodiment, in which the eccentric drive part is an enclosed ring,
  • FIG. 6 shows a view similar to Figure 4 for a fourth embodiment, in which the clamping bodies are designed as rolling elements
  • Fig. 7 a view as Figure 4 for a fifth embodiment, now the clamping body between the first bearing surface and the second bearing surface are now arranged, the Exzenter capitaeil is designed as a ring and has a step.
  • the wobble joint fitting has a first link arm 20 and a second link arm 22 cooperating therewith.
  • the first link arm 20 has an internal gear 24 and a first annular bearing surface 26. Internal gear 24 and first bearing surface 26 are central to a major axis 28.
  • the second link arm 22 is an eccentric 30 assigned. Assignment is understood here to mean that the eccentric wheel 30 is either rigidly connected to the second articulated arm 22 or is connected to the second articulated arm 22 via a wobble mechanism similar to the illustrated wobble mechanism.
  • the eccentric 30 proves an externally toothed pinion 32 which is in engagement with the internal gear 24 and can rotate in this tumbling. Furthermore, the eccentric 30 on a second bearing surface 34, which is also cylindrical.
  • the second bearing surface 34 is an inner surface.
  • the eccentric wheel 30 and thus its pinion 32 and the second bearing surface 34 are centered to an eccentric axis 36.
  • the Taumelgeschbeschlag an eccentric drive member 38 which is located in a crescent-shaped annular gap between the second bearing surface 34 and the first bearing surface 26.
  • This Exzenter technicallyeil 38 has an eccentric region 40, which is responsible for the actual eccentric function. It is in abutment both on the first bearing surface 26 and on the second bearing surface 34. The rest of the region of the Exzenter technicallyeils 38, ie outside of the eccentric region 40, may be in contact with one of the bearing surfaces 26 or 34, but is usually not in contact with both bearing surfaces 26, 34. He is not responsible for the actual drive function.
  • the Taumelgeschbeschlag clamping parts 42 In this case, a clamping part is sufficient, for symmetry reasons are usually two clamping parts, as shown.
  • the task of the clamping parts is to move in a clamping state, the eccentric axis 36 so relative to the main axis 28 that the Taumelgelenkbeschlag is possible without play.
  • the clamping state of the clamping members 42 Before the Taumelgelenkbeschlag can be adjusted, so the first articulated arm 20 can be pivoted relative to the second articulated arm 22 about the main axis 28, the clamping state of the clamping members 42 must be repealed, this is true for at least one of the clamping members 42.
  • Such a procedure is state of the art ,
  • the eccentric drive part 38 defines the eccentric.
  • the clamping members 42 are not part of the eccentric. Without clamping members 42 of the Taumelgeschbetsch works, but there is not just the described clamping state, the Taumelgelenkbeschlag is therefore not backlash.
  • the clamping members 42 are solely for maintaining the clamping condition under control. They have no part in the eccentric function.
  • an eccentric vector 44 is defined. It has its base on the major axis 28. Its tip falls on the eccentric axis 30. It has a direction which is perpendicular to both axes 28, 36. Clearly speaking, it points to the thickest point of the crescent-shaped gap between the two bearing surfaces 26, 34.
  • the eccentric vector 44 is also suitable for defining a plane of symmetry of the Taumelgelenkbeschlages. All embodiments shown are symmetrical to a plane defined by the eccentric vector 44 and one of the axles 28 and 36, respectively. This symmetry is in the clamping state, as shown in the figures. In a drive state, there is no such symmetry.
  • the eccentric region extends over an angle of at least ⁇ 10 °, preferably at least ⁇ 25 ° and in particular at least ⁇ 30 °.
  • the eccentric region 40 extends over 360 °, ie over the entire course of the annular eccentric friction part 38.
  • the control part 46 is assigned a drive 48. which is rotatably mated with the control part.
  • the drive has a stub axle which engages in a bore of the first articulated arm 20, which is located within the first bearing surface 26.
  • the Exzenter consideredeil 38 is substantially C-shaped, it extends over approximately 270 °. Diametrically opposite the eccentric region 40 is an air gap between the two bearing surfaces 26, 34, in this air gap engages a control lug of the control part 46 and causes the drive in a known manner.
  • the clamping members 42 are wedge segments in the first embodiment. They are pressed by a spring 50, which is designed in a known manner as omega spring in the clamping position.
  • the two clamping parts 42 are identical. They extend about 100 °. They rest with an inner surface on the first bearing surface 26. With an outer surface they face an inner wall of an arm 41 of the ExzenterInstituteils 38 and in Appendix.
  • the system is preferably linear, parallel to the axes 28, 36.
  • the clamping members 42 are designed so that the described contact and thus the support at an angle of 60 ° ⁇ 15 ° relative to the eccentric vector 44 takes place.
  • a drive operation proceeds as follows: The control part 46 is rotated and abuts with a flank of its control nose to a narrow end of the lying in the direction of rotation of the flank clamping member 42, for example, the left in Figure 4 terminal 42. This is now moved against the force of the spring 50 in a clockwise direction and abuts with its wide end to the eccentric region 40. In the further drive movement, the eccentric drive member 38 is now moved along. As a result, the two articulated arms 20, 22 are adjusted against each other, so changed their angular position. Ends the drive, the spring 50 moves the clamping members 42 back to the starting position, this is true at least for the left clamping member 42nd
  • the second embodiment of FIG. 4 works like the first embodiment.
  • the Exzenter consideredeil 38 forms a ring.
  • the clamping parts 42 are further located between the Exzenter consideredeil 38 and the first bearing surface 26.
  • the Exzenter consideredeil 38 is composed of an eccentric region 40, which extends as in the first embodiment about 45 °, and a ring segment extending over the remaining 315 ° extends, which are necessary for a full circulation.
  • the ring segment has contact only with the second bearing surface 34, from the first bearing surface 26 it has a distance of at least 1 to 2 mm.
  • the eccentric drive member 38 has two different thicknesses measured in the axial direction. It has a greater thickness in the area outside the gradation. It has a thinner thickness in the region of the gradation, that is to say in particular below the clamping parts 42 and between the narrow sides of the clamping parts 42.
  • the clamping members 42 are formed as balls or rolling elements. You are now not biased by an omega spring in the clamping position, but by one associated coil spring.
  • the Exzenter technicallyeil 38 is composed as in the first embodiment of an eccentric 40, which now but extends over almost 90 ° and two arms 41 together, which also extend over about 90 ° and rest only on the second bearing surface 34.
  • a clamping slope for the spherical clamping members 42 is provided on their inner surfaces in each case a clamping slope for the spherical clamping members 42 is provided. The clamping slope tapers in the direction of an expanding coil spring.
  • the balls, which form the clamping parts 42 lie between the arms 41 and the first bearing surface 26.
  • the control part fills substantially the rest of the gap between the bearing surfaces 26, 34 and engages with adjusting fingers in the vicinity of the balls, the clamping parts 42nd form. Furthermore, the control member 46 has a recess which can come into contact with the free ends of the arms 41 of the ExzenterInstituteils 38. During a rotational movement of the control part 46, first the finger 51 lying in the direction of movement first releases the adjacent ball from the clamping position, after which the eccentric drive part 38 is rotated. Accordingly, the distance between the finger 51 and the ball 42 is smaller than the distance between the recess and the free end of one of the arms 41.
  • the embodiment according to FIG. 7, that is to say the fifth exemplary embodiment, will be discussed.
  • the Exzenter consideredeil 38 is a closed ring, which is located below the clamping members 42.
  • the eccentric 40 extends over 360 °.
  • the Exzenter consideredeil 38 has a projecting into the plane of the clamping members 42 driver 52, which is located at the position of the eccentric portion 40 of the first embodiment. He has the same driving function as the latter.
  • the control part 46 is not shown, it is carried out similarly to the first embodiment, but extends over a larger angular range, so that it can interact with the narrow sides of the clamping members 42.
  • the clamping parts 42 extend over a smaller angle, for example about 60 °, and are thus shorter than in the first embodiment.
  • the clamping members 42 are in abutment both on the first bearing surface 26 and on the second bearing surface 34. So they act directly between these two bearing surfaces 26, 34, without participation of ExzenterInstituteils 38.
  • a sliding ring 54 is still provided is inserted into the first bearing surface 26 and assumes their function.

Abstract

L’invention concerne une ferrure d’articulation de basculement pour un siège de véhicule comprenant un premier bras articulé (20) qui a) comporte une roue dentée intérieure (24) et b) forme une première surface portante (26), lesquelles sont centrées par rapport à un axe principal (28), et un deuxième bras articulé (20) auquel est associée une roue excentrique (30) qui a) présente un pignon à denture extérieure (32) qui se trouve à l’intérieur de la roue dentée intérieure (24) et avec laquelle il est en prise et b) présente une deuxième surface portante (34). Le pignon (32) et la deuxième surface portante (34) sont centrés par rapport à un axe excentrique (36). Une partie motrice excentrique (38) est disposée dans la zone entre la première surface portante (26) et la deuxième surface portante (34). Des pièces de serrage (42), lorsqu’elles sont serrées, déplacent l’axe excentrique (36) par rapport à l’axe principal (28). La partie motrice excentrique (38) définit l’excentrique. Un mécanisme d’entraînement rotatif de la partie motrice excentrique (38) produit une rotation du pignon (32) par rapport à la roue dentée intérieure (24), même en l’absence des pièces de serrage (42). Selon l’invention, aucune compensation du jeu n’est obtenue en l’absence des pièces de serrage (42).
EP09780724A 2008-08-13 2009-07-16 Ferrure d'articulation de basculement pour un siège de véhicule Withdrawn EP2313291A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008041246 2008-08-13
PCT/EP2009/059169 WO2010018045A1 (fr) 2008-08-13 2009-07-16 Ferrure d’articulation de basculement pour un siège de véhicule

Publications (1)

Publication Number Publication Date
EP2313291A1 true EP2313291A1 (fr) 2011-04-27

Family

ID=41168433

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09780724A Withdrawn EP2313291A1 (fr) 2008-08-13 2009-07-16 Ferrure d'articulation de basculement pour un siège de véhicule

Country Status (4)

Country Link
US (1) US8336962B2 (fr)
EP (1) EP2313291A1 (fr)
CN (1) CN102149568A (fr)
WO (1) WO2010018045A1 (fr)

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DE102009052512A1 (de) * 2009-11-11 2011-05-12 Johnson Controls Gmbh Neigungsversteller für Fahrzeuge
DE102010062414B4 (de) * 2009-12-22 2022-06-23 Keiper Seating Mechanisms Co., Ltd. Taumelgelenkbeschlag für eine Verstellvorrichtung eines Kraftfahrzeugsitzes, insbesondere für einen Rückenlehnengelenkbeschlag
DE102010018952B4 (de) * 2010-04-28 2013-03-14 Keiper Gmbh & Co. Kg Beschlag für einen Fahrzeugsitz, Fahrzeugsitz und Verfahren zum Zusammenbau eines Beschlags
US9102248B2 (en) * 2011-09-08 2015-08-11 Magna Seating Inc. Quick adjust continuously engaged recliner
JP6067293B2 (ja) * 2012-09-19 2017-01-25 デルタ工業株式会社 シート用ブラケットの角度調整装置
US9475409B2 (en) * 2013-06-17 2016-10-25 Hubei Aviation Precision Machinery Technology Co., Ltd. Seat recliner and oil collecting element
WO2020094774A2 (fr) * 2018-11-07 2020-05-14 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Coburg Ferrure rotative avec sous-ensemble excentrique

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DE19517441C1 (de) 1995-05-12 1996-10-02 Keiper Recaro Gmbh Co Gelenkbeschlag für Sitze mit verstellbarer Rückenlehne, insbesondere Kraftfahrzeugsitze
DE19938666C5 (de) 1999-08-14 2008-01-03 Keiper Gmbh & Co.Kg Verstellbeschlag für Sitze mit neigungseinstellbarer Lehne, insbesondere für Kraftfahzeugsitze
WO2003024740A1 (fr) * 2001-09-06 2003-03-27 Keiper Gmbh & Co Ferrure destinee a un siege de vehicule
KR100549199B1 (ko) * 2003-11-26 2006-02-02 주식회사다스 컨티뉴즐리타입 자동차용 시트 리클라이닝장치
DE102004007043B3 (de) * 2004-02-12 2005-06-23 Keiper Gmbh & Co. Kg Beschlag für einen Fahrzeugsitz
DE202004004051U1 (de) 2004-03-12 2004-06-17 Kwm Entwicklungs-, Vertriebs- Und Service Gmbh Griffelement, insbesondere Haltegriff
DE102005026658B3 (de) * 2005-06-09 2006-11-02 Faurecia Autositze Gmbh & Co. Kg Neigungsverstellbeschlag für die Rückenlehne eines Kraftfahrzeugsitzes
US7285067B2 (en) * 2005-06-30 2007-10-23 Fisher Dynamics Corporation Rotary recliner
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Title
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Also Published As

Publication number Publication date
WO2010018045A1 (fr) 2010-02-18
US8336962B2 (en) 2012-12-25
US20110156463A1 (en) 2011-06-30
CN102149568A (zh) 2011-08-10

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