EP1720722A2 - Articulation de guidage de roue - Google Patents

Articulation de guidage de roue

Info

Publication number
EP1720722A2
EP1720722A2 EP05726401A EP05726401A EP1720722A2 EP 1720722 A2 EP1720722 A2 EP 1720722A2 EP 05726401 A EP05726401 A EP 05726401A EP 05726401 A EP05726401 A EP 05726401A EP 1720722 A2 EP1720722 A2 EP 1720722A2
Authority
EP
European Patent Office
Prior art keywords
bearing
joint
wheel
joint arrangement
toroidal roller
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Withdrawn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
EP05726401A
Other languages
German (de)
English (en)
Inventor
Matthias Gercke
Michael Mühl
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.)
ZF Friedrichshafen AG
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 EP1720722A2 publication Critical patent/EP1720722A2/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Withdrawn legal-status Critical Current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
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/18—Steering knuckles; King pins
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/32—Articulated members
    • Y10T403/32606—Pivoted
    • Y10T403/32631—Universal ball and socket
    • Y10T403/32681—Composite ball
    • Y10T403/32704—Stud extends into ball

Definitions

  • the invention relates to a joint arrangement for a wheel guide, in particular for a driven, steerable axle of a motor vehicle, according to the preamble of patent claim 1.
  • Joint arrangements of the type mentioned at the outset come, for example, from so-called dissolved wheel carriers of, among others. McPherson axles, shock absorber axles or double wishbone axles are used. Such resolved wheel carriers are characterized in that a pivotable insert, for example a steering knuckle, is arranged on a fixed, that is to say non-steerable, part of the wheel carrier, which carries out the actual steering movement of the wheel.
  • Such resolved wheel carriers have in particular the advantage that the steering axis, about which the wheel is pivoted during the steering movement, can be arranged with a smaller spreading angle and closer to the center plane of the wheel, even without thereby causing an undesirably large and / or positive steering roll radius arises.
  • This reduces disruptive influences of the drive or braking torque as well as the influences on the steering of the vehicle resulting from uneven road surfaces, wheel imbalances or centrifugal forces.
  • the entire axle geometry in particular the interaction of spreading, steering roll radius, track width and camber as well as caster, can be better optimized in this way in order to cope with all driving conditions and in to ensure optimal steering of the vehicle as large a steering angle range as possible, as well as sensitive and responsive steering.
  • Such resolved wheel carriers are known for example from the publications US 6,042,294 AI and US 6,010,272 AI. These known wheel carriers comprise two ball joints through which the steering axis or pivot axis of the steering knuckle is determined. According to the teaching of these documents, the steering knuckle can thus be pivoted relative to a fork-like joint arrangement arranged on the wheel carrier about the steering axis determined by the two ball joints, as a result of which the corresponding wheel of the vehicle experiences the steering movement.
  • the wheel guide joint formed by the two ball joints must always be designed as a fixed / floating bearing combination in order to be able to accommodate the inevitable manufacturing and assembly tolerances and the deformations of the joint and axle components that always occur during operation. This is all the more true since such wheel guide joints, particularly in the case of driven axles, have to be embodied essentially in the form of a fork in order to enable the necessary passage for the drive shaft of the wheel.
  • this open, fork-shaped design brings with it additional elasticities, which are manifested in deformations of the joint fork or the respective bearing bracket as soon as road influences as well as drive, braking and centrifugal forces act on the wheel guide joint.
  • This device for absorbing axial displacements means nothing more than the need for a further, essentially prismatic bearing surface, in addition to the spherical-shell bearing surface between the ball pin and the spherical shell.
  • the joint arrangement is intended in particular to simplify the structural measures required for simultaneous absorption of axial displacements and misalignments between the individual joint components. Furthermore, the joint arrangement should be as space-saving as possible, free of play and low-maintenance as well be inexpensive to carry out.
  • the joint arrangement according to the present invention comprises, in a manner known per se, an articulated fork which can be arranged on a vehicle axle or on a wheel carrier, and a steering knuckle which receives the wheel bearing.
  • the joint fork and steering knuckle are pivotally connected to one another by two axially aligned bearing points, as a result of which the corresponding wheel of the vehicle experiences the steering movement.
  • the joint arrangement is characterized in that at least one of the two bearing points to which the joint fork and steering knuckle are pivotally connected has a toroidal roller bearing.
  • Toroidal roller bearings have the unique property in the field of rolling bearings that they can only accommodate axial misalignment as well as angular misalignments by means of corresponding automatic relative movement of the inner ring, outer ring and rolling elements. Neither the usual loose bearings occur known friction forces or stick-slip effects in the case of axial displacements, which lead to undesirable vibrations or loads on the rolling surfaces. Also, the mentioned compensatory movements of the bearing components of the toroidal roller bearing are not associated with uneven surface pressure or even with the occurrence of harmful edge pressure in the area of the rolling elements.
  • the toroidal roller bearing also has an extremely high load-bearing capacity due to the constantly even line contact between the toroidal-concave bearing rings and the spherical rolling elements.
  • the toroidal roller bearing regardless of angular misalignment or regardless of the axial misalignment, is almost always free of play due to its special geometry, which complies with the smooth running of the wheel and the sensitive and non-reactive steering.
  • the great advantage of the use of a toroidal roller bearing as a floating bearing in a joint arrangement for a wheel guide according to the invention is that all angular misalignments and axial misalignments that occur in the area of the wheel guide joint, for example due to tolerances and due to force-induced deformations, in the operation of the vehicle are in the range of one single storage space arrangement can be included.
  • the additional prismatic bearing surface that has always been necessary according to the prior art to absorb the axial displacements in the area of the floating bearing can thus be omitted without replacement.
  • the design of the other bearing point of the joint arrangement forming the fixed bearing is as long as this other bearing point can absorb and transmit the entire forces acting in the articulated axial direction between the joint fork and the knuckle.
  • the other bearing point forming the fixed bearing is designed as a ball joint. Since this ball-and-socket joint as a fixed bearing does not have to accept any axial misalignment, it can be designed to be space-saving and robust, with little play and with a high load-bearing capacity.
  • the toroidal roller bearing is arranged in a cup-shaped recess in the joint fork or the steering knuckle, the cup-shaped recess preferably having a circumferential annular collar in the region of the bottom of the recess.
  • This arrangement is advantageous in that the toroidal roller bearing is thus only given a defined fit by being pressed into the cup-shaped recess, the toroidal roller bearing being completely closed off from the surroundings by the bottom of the recess.
  • the circumferential ring collar ensures a defined axial fit of the toroidal roller bearing in the cup-shaped recess.
  • this cavity can serve as an additional reservoir for receiving lubricant for the toroidal roller bearing.
  • at least one elastic body is arranged between the outer ring of the toroidal roller bearing and the essentially cylindrical wall of the cup-shaped recess.
  • This at least one elastic body which is preferably in the form of one or more elastic rings, each with an essentially circular cross section, leads to a certain vibration damping and decoupling between the steering knuckle and the joint fork. This also benefits the driving comfort and the noise reduction of the vehicle axle provided with the joint arrangement with advantage.
  • the elastic ring or the elastic rings can in particular be receivable in grooves which are introduced all around on the surface of the bearing outer ring and / or on the inner surface of the wall of the cup-shaped recess.
  • the toroidal roller bearing is covered with a seal on the side facing away from the bottom of the cup-shaped recess.
  • the seal closes both the rolling elements and rolling surfaces of the toroidal roller bearing and the gap between the bearing outer ring and the cup-shaped recess, as well as the gap between the bearing inner ring and the bearing journal with respect to environmental influences. This is advantageous because the entire floating bearing area can be completely protected and encapsulated with just one seal.
  • the seal particularly preferably has a first and a second edge or sealing lip in the region of its inner circumference.
  • the seal is supported radially on the journal with the first edge or sealing lip. With the second edge or sealing lip, the seal is supported axially on the collar of the bearing journal.
  • FIG. 1 shows a schematic representation of an embodiment of a joint arrangement according to the invention in a lateral, partially sectioned view.
  • FIG. 1 shows an embodiment of a joint arrangement according to the invention with a view along the direction of travel of an associated motor vehicle.
  • the articulated fork 1 is connected to a strut (not shown) on the left-hand side of the drawing, for example, while the steering knuckle 2 carries the bearing of the steered wheel, also not shown, at 3 on the right-hand side.
  • Articulated fork 1 and steering knuckle 2 have two common bearing points 4 and 5, one of the bearing points being designed as a ball joint 4 and the other bearing point being provided with a roller bearing 5.
  • the roller bearing 5 is designed as a toroidal roller bearing which, as already described at the outset, both tolerates a certain angular offset between its outer ring 6 and its inner ring 7 and can accommodate axial displacements of the inner ring 7 relative to the outer ring 6 without problems and without reaction forces.
  • the ball joint 4 forms the fixed bearing of the fixed / floating bearing combination shown and is responsible for absorbing and transmitting the forces acting in the joint-axial direction between the knuckle 2 and the joint fork 1.
  • Bearing surface arrangement of the toroidal roller bearing can be included.
  • the arrangement of the toroidal roller bearing in a cylindrical, pot-shaped recess 9 of the joint fork 1 also contributes to the space-saving design.
  • This arrangement has the particular advantage of high rigidity and also completely covers the lower side of the toroidal roller bearing facing away from the drawing, so that no further sealing measures are required on this side.
  • an elastic element 10 for example one or more elastic rings 10, can be arranged between the outer ring 6 of the toroidal roller bearing and the cylindrical wall of the cup-shaped recess 9.
  • the elastic element 10 can additionally improve the vibration decoupling between the steering knuckle 2 and the articulated fork 1 and thus ensure better absorption of force peaks.
  • this allows the transmission of rolling noise in the form of structure-borne noise via the joints of the wheel suspension reduce or dampen.
  • FIG. 1 also shows the type and design of the seal 11, which covers the entire bearing region of the floating bearing 5 on the axle side.
  • the seal 11 shown is particularly advantageous in that both the rolling surfaces and rolling elements of the toroidal roller bearing are completely protected in this way with only one sealing element 11, and also the gaps 12, 3, which tend to be susceptible to corrosion, between the bearing rings 6, 7 of the toroidal roller bearing and the respective press fit the bearing rings 6, 7 in the cup-shaped recess 9 or on the bearing journal 14 of the steering knuckle 2 are completely protected.
  • the seal 11 is supported in the region of the kingpin 14 both radially at 12 on the journal 14 and axially at 15 on the collar of the journal 14. On the one hand, this leads to a particularly secure sealing effect, and on the other hand ensures that the seal 11 rests securely on the respective sealing surfaces 12, 13, 15 under all operating conditions, in particular also in the event of deflections of the joint axis 8 and / or axial displacements between the journal 14 and the joint fork 2.
  • the invention thus makes an important contribution to improving the wheel guidance and optimizing the axle kinematics, which benefits safety, cost effectiveness, low maintenance and driving comfort of wheel suspensions on the motor vehicle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
  • Rolling Contact Bearings (AREA)
  • Vehicle Body Suspensions (AREA)
  • Steering Controls (AREA)
  • Pivots And Pivotal Connections (AREA)

Abstract

L'invention concerne un ensemble articulé pour un guidage de roue, notamment pour un essieu dirigeable entraîné d'un véhicule automobile. L'ensemble articulé selon l'invention comprend une fourchette d'articulation (1) à placer sur un essieu de véhicule ou sur un support de roue, ainsi qu'une fusée d'essieu (2) portant le palier de roue (3), la fourchette d'articulation (1) et la fusée d'essieu (2) étant reliées pivotantes l'une à l'autre au moyen de deux points d'appui (4, 5). L'ensemble articulé selon l'invention est caractérisé en ce qu'au moins un des deux points d'appui (4, 5) de l'ensemble articulé présente un palier à rouleaux toroïdal. L'ensemble articulé selon l'invention améliore notamment le guidage de roue et la géométrie d'essieux dirigés entraînés tout en réduisant à la fois les coûts de réalisation pour la suspension des roues et l'espace nécessaire au montage de l'ensemble articulé en améliorant les caractéristiques de palier. L'invention contribue ainsi à optimiser la cinématique d'essieu, la sécurité, l'efficacité en termes de coût et de maintenance de suspensions de roues, ainsi qu'à améliorer le confort de conduite.
EP05726401A 2004-02-12 2005-02-11 Articulation de guidage de roue Withdrawn EP1720722A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004007127A DE102004007127A1 (de) 2004-02-12 2004-02-12 Radführungsgelenk
PCT/DE2005/000243 WO2005077682A2 (fr) 2004-02-12 2005-02-11 Articulation de guidage de roue

Publications (1)

Publication Number Publication Date
EP1720722A2 true EP1720722A2 (fr) 2006-11-15

Family

ID=34853454

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05726401A Withdrawn EP1720722A2 (fr) 2004-02-12 2005-02-11 Articulation de guidage de roue

Country Status (7)

Country Link
US (1) US20070096419A1 (fr)
EP (1) EP1720722A2 (fr)
JP (1) JP2007526851A (fr)
CN (1) CN101072705A (fr)
AU (1) AU2005211874A1 (fr)
DE (1) DE102004007127A1 (fr)
WO (1) WO2005077682A2 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056877B4 (de) * 2005-11-28 2008-08-21 Zf Friedrichshafen Ag Montageverfahren für Gelenkanordnung sowie Gelenkanordnung für Kraftfahrzeugachse
DE102008022089B4 (de) * 2008-05-05 2010-03-18 Horiba Automotive Test Systems Gmbh Prüfstand mit Stehlager
US8828850B2 (en) 2010-05-20 2014-09-09 Taiwan Semiconductor Manufacturing Company, Ltd. Reducing variation by using combination epitaxy growth
US9064688B2 (en) 2010-05-20 2015-06-23 Taiwan Semiconductor Manufacturing Company, Ltd. Performing enhanced cleaning in the formation of MOS devices
US9263339B2 (en) * 2010-05-20 2016-02-16 Taiwan Semiconductor Manufacturing Company, Ltd. Selective etching in the formation of epitaxy regions in MOS devices
CN103717929B (zh) * 2011-05-17 2017-02-15 Skf公司 用于圆环滚子轴承的保持架
US8857833B2 (en) 2011-11-15 2014-10-14 Dana Heavy Vehicle Systems Group, Llc Vehicle knuckle with bolt-on steer arm
CN110386185B (zh) * 2018-04-19 2023-04-07 舍弗勒技术股份两合公司 用于轮毂驱动车辆的转向系统及轮毂驱动车辆

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US3129023A (en) * 1961-07-21 1964-04-14 Gen Motors Corp Suspension ball joint assembly
US4283833A (en) * 1979-03-16 1981-08-18 The Bendix Corporation Method of attaching a ball joint to a suspension member
JPH0540020U (ja) * 1991-11-01 1993-05-28 エヌ・オー・ケー・メグラステイツク株式会社 センターベアリングサポート
DE4141793A1 (de) * 1991-12-18 1993-06-24 Zahnradfabrik Friedrichshafen Starre angetriebene lenkachse
DE19704909A1 (de) * 1996-03-29 1998-08-13 Skf Gmbh Lagerung
DE19817140A1 (de) * 1998-04-17 1999-10-21 Bayerische Motoren Werke Ag Lagerung eines Stabilisators
US6010272A (en) * 1998-11-19 2000-01-04 Trw Inc. Ball joint with two-piece bearing and spring
US6042294A (en) * 1998-11-23 2000-03-28 Trw Inc. Ball joint having rotational and axial movement
DE20111647U1 (de) * 2001-07-12 2001-10-18 AB SKF, Göteborg Lagerelement
DE10202525B4 (de) * 2002-01-24 2013-01-10 Sms Siemag Aktiengesellschaft Drehlagerungen für Rollen zum Stützen, Führen und/oder Transportieren von heißen Metallsträngen, insbesondere von gegossenen Stahlsträngen
FR2837776B1 (fr) * 2002-03-26 2005-02-04 Skf Ab Dispositif de fixation de pivot de roue de vehicule automobile

Non-Patent Citations (1)

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Title
See references of WO2005077682A2 *

Also Published As

Publication number Publication date
WO2005077682A2 (fr) 2005-08-25
US20070096419A1 (en) 2007-05-03
AU2005211874A1 (en) 2005-08-25
CN101072705A (zh) 2007-11-14
JP2007526851A (ja) 2007-09-20
DE102004007127A1 (de) 2005-09-22
WO2005077682A3 (fr) 2007-04-26

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