WO2017137186A1 - Essieu semi-rigide directeur - Google Patents

Essieu semi-rigide directeur Download PDF

Info

Publication number
WO2017137186A1
WO2017137186A1 PCT/EP2017/050296 EP2017050296W WO2017137186A1 WO 2017137186 A1 WO2017137186 A1 WO 2017137186A1 EP 2017050296 W EP2017050296 W EP 2017050296W WO 2017137186 A1 WO2017137186 A1 WO 2017137186A1
Authority
WO
WIPO (PCT)
Prior art keywords
cross member
actuator
trailing arm
torsion beam
beam axle
Prior art date
Application number
PCT/EP2017/050296
Other languages
German (de)
English (en)
Inventor
Benjamin Bäumer
Knut Heidsieck
Original Assignee
Zf Friedrichshafen 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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2017137186A1 publication Critical patent/WO2017137186A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
    • B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
    • B60G21/051—Trailing arm twist beam axles
    • B60G21/052—Mounting means therefor
    • B60G21/053—Mounting means therefor adjustable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/18—Steering knuckles; King pins
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/20—Semi-rigid axle suspensions
    • B60G2200/21—Trailing arms connected by a torsional beam, i.e. twist-beam axles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/40—Indexing codes relating to the wheels in the suspensions
    • B60G2200/44—Indexing codes relating to the wheels in the suspensions steerable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/13—Torsion spring
    • B60G2202/136—Twist-beam type arrangement
    • B60G2202/1362—Twist-beam type arrangement including a second torsional element, e.g. second beam, stabiliser bar or tube
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B60G2202/42—Electric actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/20—Constructional features of semi-rigid axles, e.g. twist beam type axles

Definitions

  • the invention relates to a steerable beam axle for a motor vehicle with a twistable cross member, which at its two ends in each case one
  • Trailing arm wherein with each trailing arm, a suspension is connected, which is mounted in each case about a steering axis pivotally mounted on the respective trailing arm, wherein the suspension is a wheel and a in
  • a rigid, but torsionally soft design of the cross member ensures that a mutual entanglement of the wheel carrier receiving trailing arm is defined allows.
  • the torsionally soft cross member assumes the function of a roll stabilizer with which a high roll stability, ie a desired inclination of the vehicle body when cornering, can be achieved.
  • Other advantages of the joint handlebar axle are a good straight-ahead and a slight toe-in changes during compression and rebound of the axle.
  • Twist-beam axles are the wheel carrier rigidly connected to the trailing arms, for example, welded.
  • motor vehicles are provided with active rear wheel steering, with which but also the maneuverability of the motor vehicle can be increased.
  • the rear-wheel steering based on the front-wheel steering with the same or gegensinnigem steering angle can be actuated.
  • WO 2013/037652 A1 is a steerable torsion beam axle for a
  • the steerable torsion beam axle has two trailing arms arranged at a distance from each other, one each with a steering lever provided wheel carrier is arranged pivotably about a respective steering axis.
  • An actuator is attached to one of the trailing arms and engages over
  • the tie rod is designed as a pendulum support
  • Coupling arrangement connected to the cross member. With the trailing arms flange-like links are formed together with which in turn upper and lower bearing elements are screwed to guide a steering knuckle.
  • a torsion beam axle with a decoupled wheel carrier is known from "Fahrwerkhandbuch” 3rd, revised and expanded edition 2011, pages 427 and 428.
  • This non-steerable torsion beam axle which is described on page 428 in Figure 4-27 as "Multi Compliance Twist Beam Axis" is to be replaced by three the steering wheel and the trailing arm arranged hinge points with rubber bearings the self-steering behavior can be improved.
  • This arrangement causes the corresponding wheel carrier to be subject to both longitudinal and lateral forces, e.g. when braking, can go into toe.
  • An object of the invention is to develop a steerable twist beam axle in such a way that the ride comfort is improved.
  • a steerable torsion beam axle according to the invention for a motor vehicle with a twistable cross member has provided at both ends
  • Trailing arm wherein with each of the trailing arm, a suspension is connected, which is mounted in each case about a longitudinal axis pivotally mounted on the respective trailing arm.
  • the suspension has a wheel and a in
  • the suspension of the wheel carrier and handlebar is preferably formed in one piece.
  • the steerable beam axle has an at least indirectly with the
  • Cross member connected actuator which pivotable by means of tie rods the wheel carrier serves around the steering axles.
  • the actuator acts in other words on the coupling links tie rods on the wheel.
  • each wheel suspension is articulated to the trailing arm via at least two bearings, preferably elastomer bearings, so that the steering axle, for example in the vehicle vertical direction, runs through the two bearings.
  • At least one bearing has in the vehicle longitudinal direction at least in comparison to the vehicle vertical direction different, preferably lower, stiffness.
  • the at least one bearing may preferably be softer than in the vehicle vertical direction. This results in an advantageous manner a defined compliance in the vehicle longitudinal direction, said connection of the respective arm to the trailing arm in the vertical direction should be relatively stiff.
  • At least one bearing should be designed as a sleeve bearing. It is further provided that the sleeve bearing in at least one, substantially horizontally emanating from the trailing arm, preferably in
  • Vehicle vertical direction projecting, receiving lug is received and the suspension has at least two each of the bearings, preferably an outer sleeve of the sleeve bearing, receiving support arms.
  • an elastic preferably made of a rubber, composite element arranged with respect to the axial stiffness higher radial stiffness.
  • the inner sleeve is positively connected to the receiving lugs, preferably screwed by aligned by one another
  • the outer sleeve is at its two end faces to the
  • the outer sleeves can be integrally formed with the support arms. Alternatively, the outer sleeves may be pressed into hollow cylindrical receptacles of the support arms, so that the
  • Elastomeric bearings are generally easy to assemble and can be exchanged.
  • the actuator may preferably be arranged centrally on the transverse profile.
  • the actuator is directly connected to two tie rods, so this can be moved linearly in the vehicle transverse direction.
  • the actuator can be designed as an electric motor with a gear, so that a spindle nut with a motor moves a linearly displaceable spindle. This results in a double-acting actuator, which is articulated directly to each of the tie rods. This allows both suspensions simultaneously and
  • Coupling elements in the form of levers, handlebars or the like must be used. For a direct and high positioning accuracy is achieved as possible, which is subject to lower tolerances due to the small number of components.
  • the actuator can in the case of a hydraulic actuation with a
  • Hydraulic cylinder housing provided, wherein in the hydraulic cylinder, a double-acting piston provided with two piston rods is arranged.
  • the two tie rods are each articulated at the end of one of the piston rods.
  • a further advantageous embodiment provides that the cross member is formed by a along its longitudinal extent inwardly formed tube and at least partially in cross-section U-shaped, wherein the actuator is attached via at least one fastening unit to the cross member having a shaped profile section of the cross member encloses and has a shape that is adapted to a shape of the deformed profile section.
  • the fastening unit encloses the profile section of the cross member Outside.
  • the fact that the shape of the fastening unit is adapted to the shape of the deformed profile section may mean that a cross-section of the fastening unit is an essentially to scale enlargement of the cross section of the deformed profile section.
  • the fastening unit can have two fastening elements that can be positively, positively and / or materially connected to one another.
  • the actuator may also be attached via two or more corresponding fastening units on the transverse profile, the
  • the fastening elements may be arranged immediately adjacent or spaced from each other. In order to influence the torsional rigidity of the transverse profile only minimally, the distance of the fastening elements is chosen as small as possible.
  • At least one, preferably elastomeric, damping element is arranged between the fastening unit and the deformed profile section.
  • the damping element may have a shape in cross section, which is also adapted to the shape of the cross section of the cross member and the fastening unit.
  • the damping element can form-fit the profile section in the region of the fastening unit, for example by means of clamps.
  • Damping elements thus results in a further advantage of a decoupling from the cross member, so that the actuator does not have to absorb torsional forces of the cross profile.
  • the actuator e.g. its housing, are not adapted to a torsional stress or does not affect the torsional stiffness of the cross member.
  • the cross member is at least partially V-shaped in cross-section, is opening in the direction of the actuator and has two in cross-section at an angle to each other arranged and interconnected legs, wherein the actuator via at least one fastening element attached to the thighs. Due to the at least partially V-shaped configuration of the transverse profile, the cross member has good torsional properties and a suitable flexural rigidity. Each fastener may be bolted to the respective leg, for example. The actuator may also be attached to at least one of the legs via two or more corresponding fastening elements.
  • At least one fastening element is supported at least partially via at least one elastic, preferably elastomeric,
  • the damping element can form a bearing point on the respective leg, so that the respective fastening element is mounted in a floating manner on the respective leg via the damping element.
  • Fig. 1 is a schematic representation in perspective view of a first
  • FIG. 2 shows a side view of the steerable beam axle shown in FIG. 1, FIG.
  • FIG. 3 is a perspective view of a sleeve bearing
  • Fig. 4 is a schematic partial view in perspective view of a second
  • Embodiment of a steerable trained twist beam axle 5 is a partial view of a torsion beam axle with double-walled cross member
  • Fig. 6 is a partial view of a torsion beam axle with open cross member.
  • a steerable torsion beam axle 1 is designated for a motor vehicle not shown in detail, which can be used as a steerable rear axle of the same.
  • the steerable torsion beam axle 1 has two spaced apart trailing arms 2, 3, which are each connected to the ends of a cross member 4 to form a torsion beam. At the respective trailing arm 2, 3 each have a suspension 8a and 10a pivotally mounted.
  • Wheel suspension 8a, 10a has an integrally from a wheel 8, 10 and in the vehicle longitudinal direction adjoining the handlebar 5, 6.
  • a steering axle 7, 9 is provided for the pivotable articulation of the wheel suspension 8a, 10a or ultimately of the wheel carrier 8, 10 with the handlebar 5, 6 on the trailing arm 2, 3.
  • the two steering axles 7, 9 have a spread at an angle to
  • the suspension 8a, 10a is articulated to the trailing arms 2 and 3 respectively via two elastomeric bearings, of which in FIG. 2, which, viewed in the direction of travel, shows the right end of the torsion beam axle 1, an upper elastomeric bearing 11 and a lower elastomeric bearing 12 are visible.
  • FIG. 2 which, viewed in the direction of travel, shows the right end of the torsion beam axle 1, an upper elastomeric bearing 11 and a lower elastomeric bearing 12 are visible.
  • the wheel carrier 8 and 10 are shown, so that the upper elastomeric bearings 11 and 13 can be seen.
  • the elastomeric bearings 11, 12 and 13 are on the one hand via fastening screws 14 in fork-shaped
  • each suspension 8a, 10a protrudes from each suspension 8a, 10a from a support arm 17 and 18, in which the respective sleeve-shaped elastomeric bearings 11, 12 and 13 is pressed to fix it.
  • the steerable torsion beam axle 1 according to FIG. 1 has a twistable connecting the two trailing arms 2, 3
  • Cross member 4 which also takes over the function of a roll stabilizer.
  • part of the steerable steering axle joint 1 is a with the
  • Wheel support 8, 10 about the steering axles 7, 9.
  • An unspecified actuator of the actuator 19 engages via tie rod joints on two tie rods 20, 21, whose other ends via tie rod ends 22 and 23 each articulated to the handlebars 5, 6 in the form of Steering levers 24 and 25 of the two wheel carrier 8, 10 are connected.
  • the actuator 19 is mounted centrally on the cross member 4.
  • the actuator 19 is attached via two fastening elements 26, 27 on the cross member 4, which enclose a deformed profile section of the cross member 4.
  • a pivot bearing 28 and 29 is provided, via which the torsion beam axle 1 is articulated to a vehicle body of the motor vehicle.
  • spring plate 30 and 31 are formed, by means of which the torsion beam axle 1 is supported via abutment springs, not shown, to abutments of the vehicle body.
  • Elastomeric bearings 11, 12 shown which are fixed on the fastening straps 15, 16 and the fastening screws 14 on the trailing arm 2.
  • the upper support arm 17 and a lower support arm 32 of the suspension 8a, 10a respectively engage the circumference of the elastomeric bearings 11 and 12.
  • the steering axis 7, 9 respectively passes through the upper and lower sleeve bearings 11, 12, so that by means of the tie rods 20, 21 and the steering lever 24, 25 ultimately the wheel carrier 8, 10 are pivotable.
  • FIG. 3 shows one of the elastomer bearings 11, 12 or 13, which is embodied as a sleeve bearing 33 designed as a rubber-metal composite component.
  • An inner sleeve 34 of this sleeve bearing 33 has a longitudinal bore 35 for one of the fastening screws 14 and is connected via a rubber element 36 with a Outer sleeve 37 connected.
  • This rubber element 36 can make a precise vote of the radial and axial stiffnesses to each other. in the
  • the sleeve bearing 33 should, with a corresponding arrangement according to FIGS. 1 and 2, have a lower axial rigidity than the radial rigidity.
  • the rubber element 36 may also project axially beyond the outer sleeve 37 and thus form an axial abutment ring on both sides.
  • the outer sleeve 37 may be conically formed on its outer shell and thereby fixed in correspondingly formed receiving bores of the support arms 17 and 18.
  • a cross member 43 at least in this section, seen in cross-section, designed as a one-sided in the direction of the wheel open V-shaped profile with a longitudinal opening 38.
  • the cross member 4 has two, seen in cross section, at an angle to each other
  • Flange sections running fasteners 41 and 42 are bolted to the legs 39 and 40.
  • Fig. 5 shows a further embodiment example with a central region of a cross member 4, wherein the attachment of the actuator 19 to the
  • Embodiment corresponds to FIG. 1.
  • the cross section of the cross member 4 is U-shaped. As can be seen from the illustration, a tube is at least partially pressed radially for this purpose, so that a doubled wall 48 is formed on the cross member 4.
  • the actuator 19 is secured by means of damping elements 44 and 45 by means of clamps 46 and 47, which enclose the cross member 4.
  • FIG. 6 shows, as a further exemplary embodiment, a middle region of a cross member 43.
  • the cross member 43 is designed as a V profile open on one side.
  • the actuator 19 is disposed away from the longitudinal opening 38.
  • On the legs 39 and 40 are secured by screws 49 and 50 holding elements 51 and 52, in which the actuator 19 via the
  • Fixing elements 41 and 42 is fixed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention concerne un essieu semi-rigide directeur (1) pour véhicule à moteur, comportant une traverse à torsion (4, 43) présentant sur ses deux extrémités respectivement un bras oscillant longitudinal (2, 3), une suspension de roue (8a, 10a) étant reliée à chaque bras oscillant longitudinal (2, 3) et étant logée sur le bras oscillant longitudinal respectif de manière à pivoter respectivement autour d'un axe de direction (7, 9). La suspension de roue présente une fusée (8, 10) et un bras (5, 6) joint à la fusée dans la direction longitudinale du véhicule. Chaque suspension de roue (8a, 10a) est articulée au bras oscillant longitudinal (2, 3) respectif au moyen d'au moins deux paliers (11, 12, 13), de préférence des paliers élastomères, au moins un palier (11, 12, 13) présentant, dans la direction longitudinale du véhicule, une raideur différente, de préférence inférieure, au moins par rapport à la direction verticale du véhicule.
PCT/EP2017/050296 2016-02-10 2017-01-09 Essieu semi-rigide directeur WO2017137186A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016201992.9 2016-02-10
DE102016201992.9A DE102016201992A1 (de) 2016-02-10 2016-02-10 Lenkbare Verbundlenkerachse

Publications (1)

Publication Number Publication Date
WO2017137186A1 true WO2017137186A1 (fr) 2017-08-17

Family

ID=57758635

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/050296 WO2017137186A1 (fr) 2016-02-10 2017-01-09 Essieu semi-rigide directeur

Country Status (2)

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DE (1) DE102016201992A1 (fr)
WO (1) WO2017137186A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017215140B4 (de) * 2017-08-30 2021-03-25 Zf Friedrichshafen Ag Bauteil zur Befestigung eines Aktuators und Anordnung des Aktuators
DE102019200214A1 (de) 2019-01-10 2020-07-16 Zf Friedrichshafen Ag Lenkbare Verbundlenkerachse für ein Kraftfahrzeug, Längslenker und Kraftfahrzeug

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3808490A1 (de) * 1987-03-25 1988-10-13 Volkswagen Ag Kraftfahrzeug-hinterradaufhaengung
JPH02299981A (ja) * 1989-05-15 1990-12-12 Mazda Motor Corp 車両の後輪操舵装置
JPH11170835A (ja) * 1997-12-11 1999-06-29 Suzuki Motor Corp トーションビーム式サスペンション
DE102007055353A1 (de) * 2007-11-19 2009-05-28 Zf Friedrichshafen Ag Verbundlenkerachse
JP2010052584A (ja) * 2008-08-28 2010-03-11 Honda Motor Co Ltd リヤサスペンション装置
EP2168789A1 (fr) * 2008-09-29 2010-03-31 Renault s.a.s. Essieu souple arrière à palonnier et traverse creuse et véhicule correspondant
WO2010069303A1 (fr) * 2008-12-18 2010-06-24 Zf Friedrichshafen Ag Essieu arrière à traverse déformable en torsion pour un véhicule
DE102009032644A1 (de) * 2009-07-10 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Halbstarrachse, insbesondere Koppellenker - oder Verbundlenkerachse eines mehrspurigen Kraftfahrzeuges
FR2950290A1 (fr) * 2009-09-24 2011-03-25 Renault Sa Essieu arriere directeur a support de palonnier et d'actionneur decouple
WO2011110788A1 (fr) * 2010-03-11 2011-09-15 Peugeot Citroën Automobiles SA Dispositif de direction pour le train arrière d'un véhicule a moteur
DE102010015710A1 (de) * 2010-04-21 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hinterachse von der Bauart einer Verbundlenkerachse oder Koppellenkerachse für ein Kraftfahrzeug mit einer Einrichtung zu einer aktiven Radwinkelverstellung
WO2012032259A1 (fr) * 2010-09-09 2012-03-15 Peugeot Citroën Automobiles SA Train arriere de vehicule automobile a roues directrices
FR2973734A1 (fr) * 2011-04-06 2012-10-12 Renault Sa Essieu arriere directeur de vehicule automobile
WO2013037652A1 (fr) 2011-09-15 2013-03-21 Zf Friedrichshafen Ag Essieu arrière à traverse de torsion, dirigeable
WO2015092174A1 (fr) * 2013-12-20 2015-06-25 Renault S.A.S. Train de suspension pour véhicule automobile, rotule de liaison pour le train et procédé de montage correspondant

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DE102007043121A1 (de) * 2007-09-10 2009-03-12 GM Global Technology Operations, Inc., Detroit Verbundlenkerachse mit elastisch aufgehängtem Radträger
FR2936182A3 (fr) * 2008-09-24 2010-03-26 Renault Sas Traverse en v a pointe verticale pourvue d'un palonnier et essieu et vehicule correspondant
DE102011003668A1 (de) * 2011-02-04 2012-08-09 Zf Friedrichshafen Ag Verfahren zur selektiven Achsmontage

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3808490A1 (de) * 1987-03-25 1988-10-13 Volkswagen Ag Kraftfahrzeug-hinterradaufhaengung
JPH02299981A (ja) * 1989-05-15 1990-12-12 Mazda Motor Corp 車両の後輪操舵装置
JPH11170835A (ja) * 1997-12-11 1999-06-29 Suzuki Motor Corp トーションビーム式サスペンション
DE102007055353A1 (de) * 2007-11-19 2009-05-28 Zf Friedrichshafen Ag Verbundlenkerachse
JP2010052584A (ja) * 2008-08-28 2010-03-11 Honda Motor Co Ltd リヤサスペンション装置
EP2168789A1 (fr) * 2008-09-29 2010-03-31 Renault s.a.s. Essieu souple arrière à palonnier et traverse creuse et véhicule correspondant
WO2010069303A1 (fr) * 2008-12-18 2010-06-24 Zf Friedrichshafen Ag Essieu arrière à traverse déformable en torsion pour un véhicule
DE102009032644A1 (de) * 2009-07-10 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Halbstarrachse, insbesondere Koppellenker - oder Verbundlenkerachse eines mehrspurigen Kraftfahrzeuges
FR2950290A1 (fr) * 2009-09-24 2011-03-25 Renault Sa Essieu arriere directeur a support de palonnier et d'actionneur decouple
WO2011110788A1 (fr) * 2010-03-11 2011-09-15 Peugeot Citroën Automobiles SA Dispositif de direction pour le train arrière d'un véhicule a moteur
DE102010015710A1 (de) * 2010-04-21 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hinterachse von der Bauart einer Verbundlenkerachse oder Koppellenkerachse für ein Kraftfahrzeug mit einer Einrichtung zu einer aktiven Radwinkelverstellung
WO2012032259A1 (fr) * 2010-09-09 2012-03-15 Peugeot Citroën Automobiles SA Train arriere de vehicule automobile a roues directrices
FR2973734A1 (fr) * 2011-04-06 2012-10-12 Renault Sa Essieu arriere directeur de vehicule automobile
WO2013037652A1 (fr) 2011-09-15 2013-03-21 Zf Friedrichshafen Ag Essieu arrière à traverse de torsion, dirigeable
WO2015092174A1 (fr) * 2013-12-20 2015-06-25 Renault S.A.S. Train de suspension pour véhicule automobile, rotule de liaison pour le train et procédé de montage correspondant

Non-Patent Citations (1)

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Title
BERND HEISSING; METIN ERSOY; STEFAN GIES: "Fahrwerkhandbuch", 2011, pages: 427,428

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