WO2009072943A1 - Installation de volant - Google Patents

Installation de volant Download PDF

Info

Publication number
WO2009072943A1
WO2009072943A1 PCT/SE2007/050940 SE2007050940W WO2009072943A1 WO 2009072943 A1 WO2009072943 A1 WO 2009072943A1 SE 2007050940 W SE2007050940 W SE 2007050940W WO 2009072943 A1 WO2009072943 A1 WO 2009072943A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
steering
rotation
steering wheel
axis
Prior art date
Application number
PCT/SE2007/050940
Other languages
English (en)
Inventor
Laurent Groleau
Original Assignee
Autoliv Development Ab
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 Autoliv Development Ab filed Critical Autoliv Development Ab
Priority to EP20070852212 priority Critical patent/EP2214948A4/fr
Priority to PCT/SE2007/050940 priority patent/WO2009072943A1/fr
Publication of WO2009072943A1 publication Critical patent/WO2009072943A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/04—Hand wheels
    • B62D1/10—Hubs; Connecting hubs to steering columns, e.g. adjustable
    • B62D1/105—Non-rotatable hubs, e.g. the central part of the steering wheel not rotating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R21/00—Arrangements or fittings on vehicles for protecting or preventing injuries to occupants or pedestrians in case of accidents or other traffic risks
    • B60R21/02—Occupant safety arrangements or fittings, e.g. crash pads
    • B60R21/16—Inflatable occupant restraints or confinements designed to inflate upon impact or impending impact, e.g. air bags
    • B60R21/20—Arrangements for storing inflatable members in their non-use or deflated condition; Arrangement or mounting of air bag modules or components
    • B60R21/203—Arrangements for storing inflatable members in their non-use or deflated condition; Arrangement or mounting of air bag modules or components in steering wheels or steering columns
    • B60R21/2032—Arrangements for storing inflatable members in their non-use or deflated condition; Arrangement or mounting of air bag modules or components in steering wheels or steering columns the inflator or inflatable member not being rotatable with the steering wheel; Arrangements using the steering column or steering wheel rim for storing, supplying or evacuating the inflation gas or for storing the inflatable member

Definitions

  • This invention relates to a steering wheel arrangement, and in particular concerns a steering wheel arrangement in which the steering whee! has a central, non-rotating hub, around which an outer peripheral part of the steering wheei may be rotated.
  • St has been proposed previously to provide a steering wheel unit for use in a motor vehicle in which the central hub of the arrangement remains stationary during rotation of the steering wheel.
  • Arrangements of this type are particularly advantageous when used with a steering wheel-mounted air-bag module of the type generally known as a "Driver's Air-Bag” (DAB) module because deployment of the air-bag can be more closely controlled if the air- bag is always in the same orientation relative to the cabin of the motor vehicle when it is activated.
  • DAB Driver's Air-Bag
  • This sort of arrangement also facilitates the mounting of controi buttons or the like on the upper surface of the air-bag unit in positions where they are always easily operable by the driver.
  • a fixed element 2 is generally in the disc, having an off-centre substantially circular aperture 3 therethrough, with a diverging skirt portion 2a extending away from the edges of the disc to allow the fixed element to be mounted to other components.
  • a steering wheel element 4 is mounted to the outer surface of the fixed element 2 by means of a first ring-bearing 6.
  • An engagement portion of the steering wheel element 4 extends away from the plane of the disc of the fixed element 2, and has a s ⁇ bstantiaiiy circular, inward-facing, toothed surface 7 provided thereon, forming a ring gear.
  • a steering coiumn eSement 8 is mounted to the inner surface of the aperture 3 which is provided in the fixed eiement 2 by means of a second ring bearing 9.
  • the steering coiumn element 8 also extends away from the plane of the disc of the fixed eiement 2, in the same direction as does the engagement portion of the steering wheel element 4, and is provided with a pinion gear 11 which lies paraiie! with the plane of the fixed element 2 and has a toothed outer periphery 12,
  • the arrangement is such that a part of the toothed periphery 12 of the pinion gear 11 engages with a part of the toothed inner surface 7 of the ring gear, so that rotation of the steering wheel eSement causes rotation of the steering column 8 in the same sense.
  • a support etement 13 protrudes from the fixed eiement 2 through a space between the ring gear and the pinion gear 11 , passing through the ring gear close to the side of the ring gear furthest from the point at which the pinion gear 11 engages with the ring gear.
  • the support eSement 13 that supports the non-rotating central hub of the steering wheei is the only support therefor.
  • the support eSement 13 must therefore necessarily be strong and have a large diameter. Because this relatively heavy-gauge support element 13 must pass through the ring gear, the amount of space within the ring gear that can be occupied by the pinion gear 11 is relatively small, to leave a sufficiently large gap within the ring gear for this occur, indeed, in some known designs, two bolts are provided to support the central hub, both of which pass through the space determined by the ring gear. This means that the ratio between the diameters of the ring gear and the pinion gear 11 must be relatively large, and in the case of the known steering wheel arrangement 1 illustrated, the ratio between these diameters is around 1/1.3. A steering ratio of this order is not always advantageous, and in many applications it is desirabie to achieve a steering ratio closer to, or preferably equal to, 1/1.
  • WO2007/080357 discloses a modified steering wheel arrangement of a type similar to that described above which seeks to address the above-mentioned technical probiems.
  • the resulting arrangement is nevertheless similar to that described above, in the sense that the central non-rotating hub, to which an air-bag module can be secured, is fixed directly to the steering column, thus requiring a particular interface to mount the steering wheel to the resulting structure.
  • This means that different interfaces are required for different motor vehicles and this can result in unnecessarily high manufacturing costs and Sow fiexibility.
  • US 4,729,254 discloses an arrangement in which there is no direct connection between the central non-rotating hub and the steering column housing, and uses a pair of interconnected satellite gears arranged for co-rotation about an axis substantially parallel to the axis of rotation of the steering column.
  • the present invention provides a steering wheel arrangement comprising: a steering wheel frame secured to a steering column for co- rotation with the steering column, and a central non-rotating hub provided within the periphery of the steering wheel frame, the steering column being rotatably mounted about a column-axis within a steering column housing; the housing having a first fixed gear, and the hub having a second fixed gear, the arrangement being characterised by a planetary gear arrangement provided on the steering wheel frame and comprising a first planetary gear arranged in mesh with the first fixed gear, and a second planetary gear arranged in mesh with the second fixed gear, wherein said planetary gears are each arranged for rotation relative to said frame about an axis of rotation which is inc ⁇ ned at an ang!e to the column-axis, the planetary gear arrangement being configured such that rotation of one of said planetary gears imparts rotational movement to the other planetary gear.
  • said pianetary gears are arranged for rotation at the same speed as one another during movement of the steering wheel frame.
  • said planetary gears are fixed to one-another for co-rotation about a common axis of
  • said planetary gears are releasabiy fixed to one another via breakable element.
  • said second pianetary gear is biased in to mesh fixed gear.
  • said pianetary gears are arranged for roi respective axes of rotation, and are in mesh with one another.
  • each said axis of rotation is inclined at a different angle to the column-axis.
  • said first pianetary gear is biased into mesh with said first fixed gear.
  • the or each said axis of rotation intersects said column axis at a point beyond the end of said steering column.
  • the or each said axis of rotation intersects said column axis at a point along the length of said steering column.
  • said first fixed gear is biased into mesh with said first planetary gear.
  • each said gear is a bevel gear.
  • each said gear is an external bevel gear.
  • the central non-rotating hub comprises a support element configured to support an airbag module.
  • Figure 1 shows components of a known steering wheel arrangement
  • Figure 2 shows components of a steering wheel arrangement in accordance with a first embodiment of the present invention
  • Figure 3 is an exploded perspective view showing part of the arrangement illustrated in Figure 2;
  • Figure 4 is a perspective view illustrating part of the arrangement illustrated in
  • Figure 5 is a transverse cross-sectiona! view through a steering wheel arrangement in accordance with a second embodiment of the present invention.
  • Figure 6 is a view corresponding generally to that of Figure 5, but showing a section radially offset relative to the section illustrated in Figure 5;
  • FIG 6 is a perspective view illustrating part of the assembled arrangement of the second embodiment. Referring snstiaSfy to Figure 2, a steering whee! arrangement 15, in accordance with a first embodiment of the present invention, is illustrated.
  • a generally elongate steering column 16 is provided which narrows at its free end so as to have a substantially frusto-conical end region 17, the outer surface of which is provided with a plurality of serrations or splines in a manner known perse.
  • the steering coiumn 16 is mounted for rotation within a steering column housing 18 which comprises a generally cylindrical steering tube 19 provided with one or more bearings 20 (only one illustrated in Figure 2) in order to rotatabiy receive the steering column 16.
  • the steering column 16 projects beyond the end of the steering tube 19.
  • An annular damp 21 is fitted around the steering tube 19, in the region of its free end, and is tightened around the steering tube in a clamping manner (for example, by tightening a clamping screw 22) so as to be fixed in position around the steering tube 19.
  • the clamp arrangement is illustrated in perspective view in Figure 4, from which it can be seen that a plurality of elongate spring elements 23 extend from the annular clamp 21 , at respective positions spaced radially around its periphery, so as to extend generally parallel to the axis of rotation A of the steering coiumn 16.
  • Each spring element 23 is secured to the annular clamp 21 by a pair of screws 24.
  • the gear element 26 fits around the steering column 16, to allow significant clearance between the steering column and the gear element.
  • the gear element 26 takes the form of an annular external beve! gear 27 having a series of peripheral gear teeth provided around a conical pitch surface 28.
  • the spring elements 23 are configured to allow for deflection in an axial direction (relative to the steering column axis A) 1 but are configured to resist torsional movement around the steering column axis A.
  • the spring elements 23 are configured to allow for deflection in an axial direction (relative to the steering column axis A) 1 but are configured to resist torsional movement around the steering column axis A.
  • the spring elements 23 thus provide a degree of bias to the gear element 26, in an axiai direction away from the annular damp 21.
  • the spring elements 23 form a substantially rigid connection between the annular clamp 21 and the gear element 26 in a rotational sense and so the bevel gear 27 is effectively a fixed gear in the sense that it is not allowed to rotate relative to the other components of the steering column housing 18.
  • the gear element 26 defines an inner circular bearing surface 29 having a diameter slightly larger than the aperture 30 provided through the uppermost part of the gear element 26. An inwardiy-directed lip 31 is thus formed adjacent the bearing surface 29.
  • the steering wheel arrangement 15 further comprises a steering wheel having a substantially rigid steering wheel frame 32 which defines a number of spokes
  • the spokes 33 can either be formed integrally with the rim of the steering wheel frame, or can be formed seperately and secured to the rim.
  • the steering wheel frame 32 is provided with a central mounting aperture 34 which is provided with a plurality of serrations or splines on its inner surface which are complimentary to those provided on the outer surface of the frusto-conical end region 17 of the steering column 16.
  • the steering wheel frame 32 can thus be mounted on the steering column 16 in a substantially conventional manner by engagement between the respective splines on the frusto-conical end regions 17 of the steering column 16 and on the inner surface of the mounting aperture 34.
  • the steering wheel frame 32 is secured to the end of the steering column 16 by a fixing bolt 35 in a substantially conventional manner. !n this way, the steering wheel frame is secured to the steering coiumn 16 for co-rotation with the steering coiumn, the connection being rigid.
  • the steering wheel frame 32 has a depending skirt 36 which is received within the end aperture 30 of the gear element 26, with clearance between the two.
  • the lower region of the steering whee! skirt 36 is supported for rotation relative to the fixed gear element 26 by an annular bearing 37 which bears against the bearing surface 29 of the fixed gear element 26.
  • An annular wave-spring (also sometimes called a wave-washer in the art) is provided in a space between the bearing 37 and the lip 31.
  • the wave-spring 38 serves to impart a degree of axial bias to the fixed gear element 26, in a direction towards the end of the steering column 16.
  • the centra! region of the steering wheel frame 32 supports a second annular bearing 39 around the free end of the steering column 16, and this bearing provides rotational support between the steering wheel frame 32 and a second gear element 40.
  • the second gear element 40 also takes the form of a bevel gear having a plurality of peripheral gear teeth provided around a conical pitch surface 41.
  • the second gear element 40 has a smaller diameter than the first gear element 26 provided on the steering coiumn housing 18, but both of these gear elements have their conical pitch surfaces inclined in the same direction relative to the axis A of the steering column, with both of the conical pitch surfaces 28, 41 narrowing with movement along the axis A in a direction towards the end of the steering column 16,
  • the second gear element 40 is formed integraiiy with, or is securely attached to, an annular skirt 42 which forms part of a central hub 43 of the steering wheel.
  • the annular skirt 42 carries a generally annular support plate 44 at its uppermost end, and it is intended support plate 44 serves as a support for an air-bag module 45 mounted the hub 43 in a manner known perse.
  • the steering wheel frame 32 carries a planetary gear arrangement indicated generally at 46 which extends generally through one of the spokes 33.
  • the planetary gear arrangement 46 comprises a pair of planetary gears which are mounted for co-rotation with one another.
  • a first planetary gear 47 is provided for rotation about an axis which is inclined at an angle ⁇ relative to the axis of rotation A of the steering coiumn 16.
  • the first planetary gear 47 takes the form of a bevel gear having a conical pitch surface 49 which is provided with a plurality of gear teeth in mesh with the gear teeth of the fixed bevel gear 27.
  • the wave-spring 38 thus serves to bias the first fixed gear 27 in to mesh with the first planetary gear 47.
  • the first planetary gear 47 is provided with a recess 50 within which an elongated neck portion 51 of the second planetary gear 52 is received.
  • the two planetary gears 57, 52 are secured to one another by a bolt 53 for co- rotation with one another, and are supported relative to the steering wheel frame 32 by a pair of annular bearings 54 (although it should be appreciated that the pair of bearings could be replaced with a single bearing).
  • the second planetary gear 52 also takes the form, at its uppermost end, of a bevel gear having a plurality of peripheral gear teeth provided around a conical pitch surface 55.
  • the periphera! gear teeth of the second planetary gear 52 mesh with the peripheral gear teeth of the second fixed gear 40 around the uppermost end of the steering column 16.
  • the first and second planetary gears 47, 52 are preferably biased in a direction aiong the inclined axis 48, towards the centra! axis A, under the action of the wave-spring 58. in this manner, the wave-spring 56 serves to bias the first planetary gear 47 in to mesh with the first fixed gear 27, and also serves to bias the second planetary gear 52 in to mesh with the second fixed gear 40.
  • the relative sizes of the two fixed gears 27, 40, and the two planetary gears 47, 52 are chosen carefully so that the ratio of the number of gear teeth provided around the periphery of the first fixed gear 27 relative to the number of gear teeth provided around the second fixed gear 40 is equal to the ratio between the number of peripheral gear teeth provided around the first planetary gear 47 relative to the number of peripheral gear teeth provided around the secondary planetary gear 52.
  • the effective gear ratio between the first planetary gear 47 and the first fixed gear 27 is equal to the gear ratio between the second planetary gear 52 and the second fixed gear 40.
  • the first fixed gear 27 remains stationary whilst the entire planetary gear arrangement 46 is moved around the steering column axis A. Due to the meshing engagement between the first planetary gear 47 and the first fixed gear 27, then this rotational movement of the steering wheel frame 32 causes the first and second planetary gears 47, 52 to rotate with one another around the inclined axis 48. Because the gear ratios between the two planetary gears and their respective fixed gears are equal, this rotational movement of the second planetary gear 52 is effective to cause rotation between the second fixed gear 40 and the steering wheel frame 42 which is exactly opposite in direction and speed to the rotation between the steering wheel frame 32 and the first fixed gear 27. This means that during rotation of the steering wheel frame 32, the second fixed gear 40 remains stationary relative to the first fixed gear 27 which means that the central hub 43 remains stationary during rotation of the steering wheel 32 and hence is a non-rotating central hub.
  • the steering wheel arrangement described above can be provided with a mechanism effective to break the meshing engagement between the above-mentioned gears, and hence allow the hub to rotate relative to the steering wheel frame, in the event that the gear mechanism becomes jammed, for example by debris falling between the gear teeth.
  • a breakable pin 57 extending between the two planetary gears 47, 52 and which, when intact, serves to prevent rotation between the two planetary gears. With the pin 57 intact, operation of the arrangement is thus exactly as described above.
  • Figures 5 to 7 and the first embodiment illustrated in Figure 2 to 4 is that in the second embodiment, the first and second fixed gears 27, 40 are of equal diameter and hence have an equal number of peripheral gear teeth; the planetary gear arrangement 46 comprises first and second planetary gears 47, 52 which are of equal size and hence have an equal number of peripheral gear teeth; and the first and second planetary gears 47, 52 are arranged in meshing relation to one another rather than for co-rotation with one another about the same axis.
  • the first gear element 26 has a substantially identical form to the first gear element of the embodiment iliustrated in Figures 2 to 4, and is formed as a fixed beve! gear 27 around the steering column 16.
  • the steering wheel frame 32 is again mounted to the top of the steering column 18 in the same, generally conventional, manner by the fixing bolt 35, and again has a downwardly-depending skirt 36 which is received for rotation within the aperture 30 formed through the top of the first fixed gear 27.
  • the first fixed gear is again provided with a similar annular bearing 37 and wave-spring 38.
  • the second fixed gear element 40 is larger than the second fixed gear element of the first embodiment.
  • the second fixed gear element 40 has a diameter substantially equal to that of the first fixed gear element 27, the two fixed gear elements having an equal number of peripheral teeth around their conical pitch surfaces 28, 41.
  • the conical pitch surface 41 of the second fixed gear 40 is inverted relative to that of the first embodiment such that the conical pitch surfaces of the two fixed gears 27, 40 are arranged to face one another.
  • the second fixed gear element 40 is again supported for rotation relative to the steering wheel frame 32 by a bearing 39 in a generally similar manner as in the arrangement of Figures 2 to 4.
  • the planetary gear arrangement 46 comprises a pair of planetary gears of substantially identical form to one another.
  • Figure 5 illustrates the first planetary gear 47 which again takes the form of a bevel gear having a conical pitch surface 49.
  • the first planetary gear 47 is mounted for rotation about an axis 57 which makes an angie ⁇ with the central axis of rotation A of the steering column 16.
  • the first planetary gear 47 is supported for rotation about a spigot 58 on a pair of bearings 59 although the pair of bearings can be replaced with a single bearing), and is biased along the axis 57, towards the central axis A 1 under the action of an annular wave- spring 60.
  • first planetary gear 47 illustrated in Figure 5 meshes with the first fixed gear 27, and is biased in to mesh with the fixed gear under the action of the annular wave-spring 60.
  • Figure 6 is a view similar to that of Figure 5, but is taken through a different section line, rotated relative to the section Sine of Figure 5, about the central axis 24.
  • Figure 6 illustrates the second planetary gear 52 and it can be seen that the second planetary gear 52 is substantially identical in form to the first planetary gear 47 illustrated in Figure 5.
  • the second planetary gear 52 is mounted for rotation relative to the steering wheel frame 32 about an axis 61 which makes an angle y to the steering column axis A, and which intersects the steering column axis A at the same point as the axis 57 about which the first planetary gear 47 rotates, where angie y equals (180° - ⁇ ).
  • the second planetary gear 52 is mounted for rotation in exactly the same manner as the first planetary gear 47 and hence is also mounted on a spigot 62 via a pair of bearings 63 (although a single bearing can be used instead) and is provided with a biasing wave-spring 64 effective to bias the second planetary gear 52 along its axis of rotation 61 , towards the central axis A of the steering column.
  • the second planetary gear 52 is provided in mesh with the second fixed gear 40, and the annular wave-spring 64 serves to bias the second planetary gear 52 in to firm mesh with the second fixed gear 40.
  • the two planetary gears 47, 52 are provided in mesh with one another.
  • the two planetary gears 47, 52 have an equal number of peripheral gear teeth, and the two fixed gears 27, 40 also have ar number of peripheral gear teeth.
  • the first fixed gear 27 remains stationary which means that the first planetary gear 47 is caused to rotate about its axis 57, with the axis 57 itself rotating around the main central axis A.
  • both of the embodiments d conventional form of connection between the steering wheel frame 32 and the steering column 16. Both arrangements also avoid the need for direction connection between the air-bag support p!ate 44 and the steering column housing, but aiso provide gear arrangements where backlash is minimised.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • Steering Controls (AREA)

Abstract

La présente invention se rapporte à une installation de volant qui comprend un cadre de volant (32) fixé à une colonne de direction (16) une co-rotation avec la colonne de direction (16). L'installation comporte un moyeu central non rotatif (43) situé dans la périphérie du cadre de volant et la colonne de direction (16) est montée de manière rotative autour d'un axe de colonne (A) dans un logement de colonne de direction (18). Le logement (18) comporte un premier engrenage fixe (27), et le moyeu (43) comporte un second engrenage fixe (40). L'installation comporte une installation d'engrenage planétaire (46) située sur le cadre de volant (32) et qui comprend un premier engrenage planétaire (47) emboîté dans le premier engrenage fixe (27) et un second engrenage planétaire (52) emboîté dans le second engrenage fixe (40). Les engrenages planétaires sont disposés pour tourner par rapport au cadre de volant (32) autour d'un axe de rotation qui est incliné selon un angle par rapport à l'axe de colonne (24). L'installation d'engrenage planétaire (46) est conçue de sorte que la rotation de l'un des engrenages planétaires transmette un déplacement rotatif à l'autre engrenage planétaire. Dans un mode de réalisation préféré, les deux engrenages planétaires (47, 52) sont fixés l'un à l'autre pour une co-rotation autour d'un axe de rotation commun.
PCT/SE2007/050940 2007-12-05 2007-12-05 Installation de volant WO2009072943A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20070852212 EP2214948A4 (fr) 2007-12-05 2007-12-05 Installation de volant
PCT/SE2007/050940 WO2009072943A1 (fr) 2007-12-05 2007-12-05 Installation de volant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SE2007/050940 WO2009072943A1 (fr) 2007-12-05 2007-12-05 Installation de volant

Publications (1)

Publication Number Publication Date
WO2009072943A1 true WO2009072943A1 (fr) 2009-06-11

Family

ID=40717948

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2007/050940 WO2009072943A1 (fr) 2007-12-05 2007-12-05 Installation de volant

Country Status (2)

Country Link
EP (1) EP2214948A4 (fr)
WO (1) WO2009072943A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10427705B2 (en) 2017-06-30 2019-10-01 GM Global Technology Operations LLC Steering wheel with fixed eccentric center hub

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6194851A (ja) * 1984-10-16 1986-05-13 Nippon Plast Co Ltd ステアリング装置
JPS6274764A (ja) * 1985-09-27 1987-04-06 Nissan Motor Co Ltd ステアリング装置
US4729254A (en) 1985-03-14 1988-03-08 Isumi Corporation Industries, Inc. Steering system
WO2005028263A2 (fr) 2003-09-16 2005-03-31 Inova Gmbh Dispositif sac gonflable et son mode de fonctionnement
WO2007080357A1 (fr) 2006-01-11 2007-07-19 Autoliv Development Ab Arrangement de volant de direction
WO2007108733A1 (fr) * 2006-03-17 2007-09-27 Autoliv Development Ab Disposition de volant de direction

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4759235A (en) * 1982-12-18 1988-07-26 Toyoda Gosei Co., Ltd. Planetary gear assembling structure for steering wheels
EP1843932B1 (fr) * 2005-02-04 2011-04-06 ThyssenKrupp Presta Aktiengesellschaft Direction dotee d'un dispositif de coussin gonflable et mode de fonctionnement associe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6194851A (ja) * 1984-10-16 1986-05-13 Nippon Plast Co Ltd ステアリング装置
US4729254A (en) 1985-03-14 1988-03-08 Isumi Corporation Industries, Inc. Steering system
JPS6274764A (ja) * 1985-09-27 1987-04-06 Nissan Motor Co Ltd ステアリング装置
WO2005028263A2 (fr) 2003-09-16 2005-03-31 Inova Gmbh Dispositif sac gonflable et son mode de fonctionnement
WO2007080357A1 (fr) 2006-01-11 2007-07-19 Autoliv Development Ab Arrangement de volant de direction
WO2007108733A1 (fr) * 2006-03-17 2007-09-27 Autoliv Development Ab Disposition de volant de direction

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2214948A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10427705B2 (en) 2017-06-30 2019-10-01 GM Global Technology Operations LLC Steering wheel with fixed eccentric center hub

Also Published As

Publication number Publication date
EP2214948A1 (fr) 2010-08-11
EP2214948A4 (fr) 2014-04-09

Similar Documents

Publication Publication Date Title
EP1084045B1 (fr) Moyeu destine a des bicyclettes
US8037782B2 (en) Steering column assembly
JP5770025B2 (ja) ブレーキペダル装置
US7562604B2 (en) Bicycle chain wheel structure
US4981329A (en) Non moving wheel cover
JP5708838B2 (ja) ステアリング装置
US7950318B2 (en) Driver for a twin cutting device with counter-rotating blades
US20060086559A1 (en) Steering device
CN1058456C (zh) 方向盘安装组件
US4371214A (en) Bearing hub and carrier assembly for a driven steering wheel unit
US6398308B1 (en) Adjusting device for a motor vehicle seat
JP4483931B2 (ja) ステアリング装置
US8079288B2 (en) Bicycle gear crank
US6726228B2 (en) Steering wheel alignment system
WO2009072943A1 (fr) Installation de volant
JP4858414B2 (ja) ステアリング装置
US6119546A (en) Apparatus for a steering wheel assembly
EP1971515B1 (fr) Arrangement de volant de direction
JP2006224895A (ja) 可変舵角機構の回転ガタ調節構造
CN100493966C (zh) 用于固定汽车雨刷机构的固定装置
WO2007108733A1 (fr) Disposition de volant de direction
KR20080084458A (ko) 자동차용 스티어링 컬럼의 레이크 브라켓 어셈블리
KR20050038163A (ko) 차량의 스티어링 휠
US3934488A (en) Steering control head with adjustable positioning means
JP2008307926A (ja) 車両用ステアリング装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07852212

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2007852212

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2007852212

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE