EP3541685A1 - Système de direction - Google Patents

Système de direction

Info

Publication number
EP3541685A1
EP3541685A1 EP17786877.5A EP17786877A EP3541685A1 EP 3541685 A1 EP3541685 A1 EP 3541685A1 EP 17786877 A EP17786877 A EP 17786877A EP 3541685 A1 EP3541685 A1 EP 3541685A1
Authority
EP
European Patent Office
Prior art keywords
bearing
gear
housing
steering
screw pinion
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Withdrawn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
EP17786877.5A
Other languages
German (de)
English (en)
Inventor
Jens-Uwe Hafermalz
Dennis Fuechsel
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3541685A1 publication Critical patent/EP3541685A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0409—Electric motor acting on the steering column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0685—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only
    • F16C32/0688—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only with floating bearing elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0457—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear characterised by control features of the drive means as such
    • B62D5/046—Controlling the motor
    • B62D5/0463—Controlling the motor calculating assisting torque from the motor based on driver input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
    • F16H55/24—Special devices for taking up backlash

Definitions

  • the invention relates to a steering system, in particular a power steering system, for a motor vehicle.
  • the known power steering systems are based on a steering gear that translates the drive power of a hydraulic or electric steering motor and transmits, for example, the steering column.
  • Such steering gear can be in the form of a fferablylzgetriebes and in particular as fferradgetriebe or
  • Worm gear be formed. These then comprise a gear wheel, which may be directly or indirectly connected to the steering column, as well as an intermeshing, driven by a shaft of the steering motor pinion.
  • the pinion shaft is pivotally mounted about an axis which is perpendicular to the longitudinal axis of the pinion shaft and at a distance from the toothing engagement of pinion and gear, and by means of one or more spring elements against the gear is pressed.
  • the pivotability of the pinion shaft is thereby regularly integrated in one of the two bearings over which the pinion shaft is mounted end.
  • the bearing in the area of the other end is then designed with a defined clearance (so-called "floating bearing", cf., for example, DE 10 2005 035 020 A1) in order to enable the deflection caused by the pivoting movement.
  • the camp is regular
  • the one or more spring elements for pressing the pinion to the gear can be integrated in both the floating bearing and in the fixed bearing.
  • Such a steering gear in which the spring force is generated for the springing by means of the fixed bearing for example, from DE 10 2009 054 655 A1 known.
  • the rolling bearing which receives the pinion shaft in the region of the fixed bearing to store outside in a pivot sleeve.
  • Swivel sleeve includes a bearing sleeve which receives the rolling bearing largely free of play, and an outer ring which is held largely free of play in a receptacle of a housing of the steering gear, wherein the outer ring and the bearing sleeve are connected via a plurality of torsion webs, upon rotation of the outer ring to the bearing sleeve be twisted. After assembly of the steering gear, the torsion bars are twisted in such a way that the elastic restoring effect generated thereby causes the springing of the pinion shaft.
  • Steering gear results.
  • relatively large translation which is provided regularly in the transmission of the drive power from the pinion to the gear.
  • Such a steering gear is in fact regularly designed for relatively high speeds of the steering motor and thus the pinion and pinion shaft comprising the pinion, wherein such relatively high speeds with correspondingly high local speeds in meshing engagement and serving in the storage of the pinion shaft pivot bearings and consequently with a correspondingly large noise development are connected.
  • the invention has for its object to improve a steering system, as it is basically known from DE 10 2009 054 655 A1, in terms of noise during operation.
  • the invention is based on the idea, the noise of a
  • a steering system for a motor vehicle which comprises a steering gear, wherein the steering gear comprises a housing, a gear, meshing with the gear screw pinion and the screw pinion
  • Screw pinion shaft has.
  • the fferritzelwelle is mounted on one side of the fferritzels in a fixed bearing, which includes a pivot bearing in which the pinion shaft is received.
  • the rotary bearing can this purpose at least one inner bearing ring, an outer bearing ring and, where appropriate, in a preferred embodiment as rolling and
  • the fixed bearing comprises a pivot ring, which has an outer ring and an inner ring, which has one or more torsion bars
  • Housing of the steering gear (with respect to at least one, preferably with respect to all directions, that is immovable) is fixed.
  • the fferritzelwelle a steering system according to the invention is mounted on the other side of the fferritzels in a floating bearing comprising a pivot bearing in which the pinion shaft is received and which is accommodated in a bearing bush mounted in the housing, wherein the bearing bush a radial mobility of the pivot bearing within of the housing.
  • the movable bearing can, for example, an embodiment according to DE 10 2005 035 020 A1 exhibit.
  • the bearing bush of the movable bearing has a rotary bearing receiving inner bushing and a surrounding the inner bushing and fixedly arranged in the housing outer bushing, wherein the outer bushing and the inner bushing define an annular gap and wherein the
  • Outer sleeve and the inner sleeve are connected to each other via a flexible connecting portion, that they are movable relative to each other in at least one radial direction.
  • a steering system furthermore comprises a steering motor, which is connected to the screw pinion shaft of the steering gear in a rotationally driving manner exclusively via a coupling element and which may be designed, in particular, as an electric motor.
  • Such a steering system is according to the basic idea of the invention characterized in that the outer ring of the swivel ring of the fixed bearing and / or the bearing bush (respectively) exclusively (ie without direct contact with the housing) with the interposition of a vibration damping Entkoppelungselements in the housing (1) fixed is.
  • the vibration-damping decoupling elements or the at least partially, preferably completely (at least) a vibration damping material, preferably a plastic, in particular a thermoplastic material, or an elastomer (for example, a rubber) is formed.
  • a vibration damping material preferably a plastic, in particular a thermoplastic material, or an elastomer (for example, a rubber) is formed.
  • it is also possible to design such an element by design measures with a vibration-damping functionality.
  • the pivot ring of the fixed bearing and / or the bearing bush of the floating bearing and / or the screw pinion and / or the gear and / or the coupling element is at least partially formed of (at least) a vibration damping material / are ,
  • the vibration damping material is a (thermoplastic) plastic or an elastomer, wherein it is assumed that each (thermoplastic) plastic and each elastomer compared to metals and in particular steel and
  • the steering system according to the invention can be designed, in particular, as a power steering system in which an assisting torque can be generated by means of the steering motor so that a steering torque to be applied by a driver of a motor vehicle comprising the power steering system to the steering column for steering the motor vehicle is reduced (possibly also temporarily) to zero).
  • a steering torque to be applied by a driver of a motor vehicle comprising the power steering system to the steering column for steering the motor vehicle is reduced (possibly also temporarily) to zero.
  • the steering system in such a way that the entire steering torque required for steering is generated by the steering motor (in particular for a so-called steer-by-wire functionality of the steering system or of the motor vehicle).
  • the invention also relates to a motor vehicle with an inventive
  • FIG. 2 shows a longitudinal section of a section of the steering gear according to FIG. 1 and a section of a steering motor of a steering system according to the invention connected to the steering gear;
  • FIG. 3 shows the fixed bearing of the steering gear according to FIG. 1 in a view from the front;
  • Fig. 4 the bearing bush of the movable bearing of the steering gear according to FIG. 1 in a
  • Fig. 1 shows the essential components of a steering gear of a
  • This comprises a housing 1, within which a gear 2 and a meshing with the gear 2 fferritzel 3 rotatable are arranged.
  • the screw pinion 3 and the screw pinion 3 comprehensive sterritzelwelle 4 are integrally formed in the form of a screw.
  • the gear 2 is fixedly mounted on an output shaft 5 (see Fig. 1) of the steering gear.
  • This output shaft 5 which has a toothing for a secure rotationally fixed connection with the gear 2 in the illustrated embodiment, for example, with a trained at least in one section as a rack handlebar, whereby the rack performs a translational movement in a known manner via Radlenkhebel (not shown) in a
  • Pivoting movement of steerable wheels (not shown) of the motor vehicle can be translated.
  • the output shaft 5 may also be a steering column of a power steering system, which is connected to a steering wheel and acts via a steering pinion on the handlebar.
  • the screw pinion shaft 4 has a drive-side end via which it can be connected to the output shaft 7 of a steering motor 6 (for example, an electric motor)
  • a steering motor 6 for example, an electric motor
  • the screw pinion shaft 4 is mounted in the housing 1 by means of a first bearing.
  • This storage is designed as a fixed bearing 8, which pivoting the
  • Screw pinion shaft 4 about a pivot axis 9 permits. This
  • This floating bearing 10 is designed so that it allows the resulting from the pivoting of the fferritzelwelle 4 deflection of this end.
  • Both the fixed bearing 8 and the floating bearing 10 each comprise a pivot bearing in the form of a ball bearing 1 1, 12.
  • the corresponding portions of the ringritzelwelle 4 are mounted, while outer
  • Bearing rings of the ball bearings n, 12 are mounted in a respective bearing device 13, 14, which in turn are received in corresponding receptacles of the housing 1.
  • the bearing devices 13, 14 are structurally designed so that they allow in the case of the fixed bearing 8, the pivoting of the fferritzelwelle 4 about the pivot axis 9 and in the case of the movable bearing 10, the deflection of the free end of the fferritzelwelle 4.
  • the bearing device 13 of the fixed bearing 8 comprises a bearing sleeve 15 with Vietnameseringförmigem cross-section, the inner side in a first longitudinal section, the ball bearing 1 1 and in a second longitudinal section an inner ring 17 of a
  • Swing ring 16 receives.
  • the inner ring 17 of the swivel ring 16 is under
  • the swivel ring 16 comprises, in addition to the inner ring 17, an outer ring 20.
  • the outer ring 20 is connected to the inner ring 17 via two torsion webs 21 (see FIG. The outer ring 12, the inner ring 17 and the
  • Torsionsstege 21 are preferably integrally formed, for example, spring steel.
  • the two torsion bars 17 define the position of the pivot axis 9, about which the outer ring 20 is pivotable relative to the inner ring 17.
  • the torsion bars 21 and thus the pivot axis 9 do not run through the center of the pivot ring 16 and thus not through the center of the cross section of the SSritzelwelle 4, but radially offset thereto (see Fig. 3).
  • the pivot axis 9 thus does not intersect the longitudinal axis 25 of the fferritzelwelle 4. Due to the radial offset of the torsion bars 21 to the center of the pivot ring 16 is the
  • Swivel axis 9 is displaced in the vicinity of the outer periphery of the SSritzelwelle 4, whereby the formation of reaction moments arising as a result of the
  • Reaction torques is provided that the pivot axis 9 is within that tangential plane, which is formed in the contact point of the two partial or rolling circles of gear 2 and screw 3.
  • the torsion bars 21 of the swivel ring 16 not only allow pivoting of the outer ring 20 to the inner ring 17 and thus the ringritzelwelle 4 relative to the gear 2 and the housing 1, but at the same time cause that spring force through which the fferritzel 3 of the ringritzelwelle 4 in the toothing of the gear 2 is pressed in order to achieve the lowest possible backlash and thus a low noise during operation of the steering gear, especially in the so-called Komlenken.
  • This spring force results from the fact that during assembly of the steering gear, the fferritzelwelle 4 is deflected so far as a result of contact with the gear 2 that a
  • the bearing device 14 of the movable bearing 10 is formed in the form of a bearing bush 14, which comprises an inner sleeve 26, which in an unloaded
  • External bushing 27 is arranged (see Fig. 4).
  • the inner bush 26 is connected to the outer bushing 27 via a connecting section 28.
  • the inner bush 26 and the outer bushing have a curved projection 29, 30 in the transverse or radial section (cf., FIG. 4), which-opposite one another-are formed in the between the inner bush 26 and the outer bush 27 Ring gap 31 protrude.
  • the tips of the two projections 29, 30 touch each other.
  • the inner sleeve 26 and the outer sleeve 27 are surrounded by an elastomer shell 32.
  • the design of the elastomer shell 32 is such that it does not protrude beyond the outer surfaces of the inner sleeve 26 and the outer sleeve 27.
  • the axial length of the inner sleeve 26 and the outer sleeve 27 in the projections 29, 30 forming peripheral portions smaller than in the other peripheral portions. As a result, recesses (not visible) are formed, in which the elastic material of the elastomer shell 32 is received.
  • the inner bush 26 on its inner side and the outer bush 27 on its outer side each have a further, extending in the axial direction recess 33, 34, wherein the material of the elastomer shell 32 is also received in these recesses 33, 34. Also in the region of the annular gap 31, the projections 29, 30 on both sides (in the circumferential direction) of the elastic Material of the elastomer shell 32 surrounded or embedded in this.
  • the elastomer shell 32 provides for the cohesion of the inner sleeve 26 and the
  • the connecting portion 28 forms a swivel joint with a low pivoting moment, which causes the outer bushing 27 to pivot about the inner bushing 26 about one in the area of the
  • Connection portion 28 located pivot axis allows. At this
  • Swivel movement slide or roll the projections 29, 30 of the inner sleeve 26 and the outer sleeve 27 from each other, while the elastomer shell 32 does not hinder this relative movement of the outer sleeve 27 and inner sleeve 26 to a relevant extent.
  • bearing bush 14 is integrated into the housing 1 of the steering gear such that pivoting of the screw pinion shaft 4 about the pivot axis 9 defined by the bearing 8 results in displacement of the inner bushing 26 relative to the outer bushing 27 in a direction indicated in FIG Is substantially perpendicular to the leading through the connecting portion 28 radial axis 35. In the directions defined by this radial axis 35, however, should not possible
  • Displacement of the inner sleeve 26 relative to the outer sleeve 27 may be possible to interlock the fferritzel 3 on the gear 2 in the operation of the
  • Limiting element 36 which is displaceable in the radial direction within the
  • the limiting element 36 has a radial width that is greater than the radial width of the outer sleeve 27, wherein the
  • Limiting element 36 of the not yet mounted in the housing 1 bearing bush 14 can move so far outward that this projects beyond the outer surface of the outer sleeve 27. This results in a relatively large distance between the outside of the inner sleeve 26 and the limiting element 36, which allows a relatively simple mounting of the bearing bush 14. This distance is under the
  • the outer bushing 27 of the bearing bush 14 further comprises an elastic stop member 37, the movement of the inner sleeve 26 in a
  • Vibration excitation and thus a sound radiation of the housing 1 can be kept low.
  • the entire gear 2 or at least its teeth are formed of plastic or at least coated with it.
  • bearing bush 14 of the movable bearing 10 is at least partially, in particular the inner sleeve 26 and / or the outer sleeve 27 is partially or completely formed of plastic / are.
  • the outer ring 20 of the swivel ring 16 exclusively with the interposition of a multi-part, vibration damping Entkoppelungselements 38 in the housing. 1 is arranged fixed, said decoupling element 38 is formed of plastic or an elastomer. And finally, it is provided that the output shaft 7 of the steering motor 6
  • the measures according to the invention are all ways of transmitting body vibrations resulting from the rotations of the SSritzelwelle 4 and the gear 2, formed on the housing 1 in at least a portion of vibration-damping plastic or elastomer, so that a consequent vibration excitation of the housing. 1 and a sound radiation of the housing 1 due to this can be kept low.
  • the best possible effect in terms of noise behavior of the steering system can be achieved if all of these measures are implemented. But it is also possible to implement only some of these measures, in which case a possibly not optimal effect is realized.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Steering Mechanism (AREA)
  • Support Of The Bearing (AREA)
  • Gear Transmission (AREA)

Abstract

La présente invention concerne un système de direction pour un véhicule à moteur comprenant : un mécanisme de direction, lequel comprend un boîtier (1), une roue dentée (2), un pignon à denture hélicoïdale (3) s'engrenant avec la roue dentée (2) et un arbre de pignon à denture hélicoïdale (4) comprenant le pignon à denture hélicoïdale (3), l'arbre de pignon à denture hélicoïdale (4) étant monté sur un côté du pignon à denture hélicoïdale (3) dans un palier fixe (8), lequel comprend un palier rotatif, dans lequel l'arbre de pignon à denture hélicoïdale (4) est logé et lequel est logé dans une douille de palier (15), et le palier fixe (8) comprenant en outre un anneau pivotant (16), lequel comprend un anneau extérieur (20) et un anneau intérieur (17), lesquels sont raccordés pivotants à l'aide d'une ou de plusieurs axes de torsion (21), l'anneau intérieur (17) étant raccordé à la douille de palier (15) ou étant intégré dans ladite douille de palier et l'anneau extérieur (20) étant disposé fixe dans le boîtier (1) et l'arbre de pignon à denture hélicoïdale (4) étant monté de l'autre côté du pignon à denture hélicoïdale (3) dans un palier libre (10), lequel comprend un palier pivotant, dans lequel l'arbre de pignon à denture hélicoïdale (4) est logé et lequel est logé dans un coussinet (14) disposé dans le boîtier (1), le coussinet (14) assurant une mobilité radiale du palier pivotant à l'intérieur du boîtier (1) ; et un moteur de direction (6), entraîné en rotation uniquement à l'aide d'un élément d'accouplement (40), raccordé à l'arbre de pignon à denture hélicoïdale (4) du mécanisme de direction, ledit système de direction est caractérisé en ce que l'anneau extérieur (20) de l'anneau pivotant (16) du palier fixe (8) et/ou le coussinet (14) du palier libre (10) sont disposés fixes uniquement avec interposition d'un élément d'accouplement (38) d'amortissement des oscillations dans le boîtier (1) et/ou que l'anneau pivotant (16) du palier fixe (8), le coussinet (14) du palier libre (10), le pignon à denture hélicoïdale (3), la roue dentée (2) et/ou l'élément d'accouplement (40), au moins partiellement, sont formés d'un matériau d'amortissement des oscillations. Dans le système de direction selon l'invention, une stimulation des oscillations et un rayonnement acoustique du boîtier (1) en raison des oscillations, lesquelles résultent de la rotation de l'arbre de pignon à denture hélicoïdale (4) et de la roue dentée (2), sont maintenus aussi basses que possible, ce qui influe de manière positive le comportement anti-bruit du système de direction lors du fonctionnement.
EP17786877.5A 2016-11-21 2017-10-06 Système de direction Withdrawn EP3541685A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016122378.6A DE102016122378A1 (de) 2016-11-21 2016-11-21 Lenksystem
PCT/EP2017/075503 WO2018091200A1 (fr) 2016-11-21 2017-10-06 Système de direction

Publications (1)

Publication Number Publication Date
EP3541685A1 true EP3541685A1 (fr) 2019-09-25

Family

ID=60138356

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17786877.5A Withdrawn EP3541685A1 (fr) 2016-11-21 2017-10-06 Système de direction

Country Status (6)

Country Link
US (1) US20200063796A1 (fr)
EP (1) EP3541685A1 (fr)
JP (1) JP2019536684A (fr)
CN (1) CN109963769A (fr)
DE (1) DE102016122378A1 (fr)
WO (1) WO2018091200A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11814116B2 (en) 2018-09-11 2023-11-14 Nsk Ltd. Assist mechanism and electric power steering device
CN109780054A (zh) * 2019-01-28 2019-05-21 宁波易锐汽车零部件有限公司 一种塑料轴承衬套及其制造方法
CN110905919A (zh) * 2019-12-23 2020-03-24 至玥腾风科技集团有限公司 一种并联轴承
DE102020201761A1 (de) * 2020-02-12 2021-08-12 Thyssenkrupp Ag Lageranordnung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005035020A1 (de) 2005-07-27 2007-02-01 Zf Lenksysteme Gmbh Radialbewegliches Loslager für eine Welle eines Lenksystems
KR100816401B1 (ko) * 2006-07-05 2008-03-27 주식회사 만도 전동식 조향장치
DE102007055814A1 (de) * 2007-12-14 2009-06-18 Zf Lenksysteme Gmbh Radialbewegliches Loslager
DE102009054655A1 (de) 2009-12-15 2011-06-16 Zf Lenksysteme Gmbh Lenkgetriebe mit Festlager und Loslager für Schraubritzel
US8905185B2 (en) * 2009-12-23 2014-12-09 Mando Corporation Reducer of electric power steering apparatus
DE102012103146A1 (de) * 2012-04-12 2013-10-17 Zf Lenksysteme Gmbh Lenkgetriebe
DE102012103147A1 (de) * 2012-04-12 2013-10-17 Zf Lenksysteme Gmbh Loslager für ein lenkgetriebe
DE102013104521A1 (de) * 2013-05-03 2014-11-20 Zf Lenksysteme Gmbh Lenkgetriebe

Also Published As

Publication number Publication date
WO2018091200A1 (fr) 2018-05-24
US20200063796A1 (en) 2020-02-27
CN109963769A (zh) 2019-07-02
JP2019536684A (ja) 2019-12-19
DE102016122378A1 (de) 2018-05-24

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