WO2017211513A1 - Actionneur pour essieu arrière directeur - Google Patents

Actionneur pour essieu arrière directeur Download PDF

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Publication number
WO2017211513A1
WO2017211513A1 PCT/EP2017/060849 EP2017060849W WO2017211513A1 WO 2017211513 A1 WO2017211513 A1 WO 2017211513A1 EP 2017060849 W EP2017060849 W EP 2017060849W WO 2017211513 A1 WO2017211513 A1 WO 2017211513A1
Authority
WO
WIPO (PCT)
Prior art keywords
hub
actuator according
spindle
ring
profile
Prior art date
Application number
PCT/EP2017/060849
Other languages
German (de)
English (en)
Inventor
Matthias Moeller
Rene Schwarze
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 WO2017211513A1 publication Critical patent/WO2017211513A1/fr

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
    • B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
    • B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
    • B62D7/146—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering characterised by comprising means for steering by acting on the suspension system, e.g. on the mountings of the suspension arms

Definitions

  • the invention relates to an actuator for a rear axle, comprising a spindle drive having an axially displaceable spindle and a housing with at least one thrust bearing for the spindle.
  • a dual-acting actuator also known as servomotor or short actuator
  • the actuator is mounted centrally on the axle of the motor vehicle and at the same time acts on the steering of the two rear wheels.
  • the actuator has a spindle drive, consisting of spindle and spindle nut, which is rotatably mounted in the housing and axially fixed.
  • the spindle nut is driven by an electric motor and causes an axial displacement of the spindle, which is prevented from twisting, d. H. has a rotation.
  • the spindle has an approximately centrally disposed threaded portion with a movement thread, which is in engagement with the spindle nut, and two spindle ends, which are each connected to bearing sleeves, which in turn are slidably guided in the housing.
  • bearing sleeves also called Aufschraubzapfen
  • joint forks are arranged for connection to a steering linkage.
  • single-acting actuators also called individual actuators, which each act only on the steering of a rear wheel.
  • Anti-rotation devices for the spindle of a spindle drive are known in various embodiments. From DE 10 2013 107 827 A1 an actuator for a rear axle steering of a motor vehicle with an electrically driven spindle drive was known, wherein the spindle is connected to a push rod, which performs an axial movement and has an anti-rotation.
  • the rotation is designed as a housing side supported slide bearing which receives a trained as a polygon section of the push rod. Due to the polygonal profiles of the push rod and the bearing opening of the plain bearing a positive fit is achieved and prevents rotation of the push rod or the spindle; axial movement is permitted.
  • the invention comprises the features of independent claim 1. Advantageous embodiments will be apparent from the dependent claims.
  • the spindle has at least one section with a splined shaft profile and the thrust bearing has a bearing opening with a splined profile for receiving the spline profile, that the thrust bearing is formed as a split hub ring with a first and a second hub half, which, seen in the axial direction , arranged one behind the other and in the circumferential direction against each other are braced.
  • the bracing of the two hub halves results in a contact on both sides of the flanks of the splined shaft profile with respect to both hub halves, so that acoustic phenomena, e.g. due to a play of the components to each other, be avoided.
  • the two hub halves each have sawtooth profiles on their end faces, which engage in one another.
  • the sawtooth profile allows the conversion of an axial movement of the first hub half in a circumferential or rotational movement of the second hub half.
  • a tension of the two hub halves can be initiated by an axial movement of the first hub half.
  • the bracing of the two hub halves takes place against each other mechanically, for example by at least one acting in the axial or circumferential direction spring element. This causes a constant tension of both hub halves.
  • the bracing is carried out via at least one piezoelectric element, which causes a travel when applying an electrical voltage.
  • the tension of the two hub halves can be controlled by electrical or electronic means, ie only if necessary.
  • the bracing of the hub halves in the steady state of the spindle that is, if no actuating movement carried out becomes.
  • the tension is at least relaxed or completely dissolved, so that there is also a lower friction between the flanks of the spline and the spline profile with an axial displacement of the spindle. The adjustment of the spindle can thus be done with less effort.
  • the sawtooth profiles each have first short flanks and second long flanks, wherein the short flanks extend predominantly in the axial direction, d. H. are relatively steep, while the long edges extend predominantly in the circumferential direction, d. H. run relatively flat.
  • the short flanks are formed as inclined surfaces.
  • the inclination of the inclined surfaces determines the translation between the path in the axial direction and in the circumferential direction.
  • the slope of the inclined surfaces in the form of an involute, resulting in favorable sliding conditions.
  • the piezoelectric element is designed as a ring element, which is arranged on the front side of the hub half to be adjusted in the axial direction and exerts an axial force distributed over the circumference of the hub half. For a space-saving arrangement of the adjustment is achieved.
  • the piezo ring element is supported on its side facing away from the hub half opposite the housing, preferably by a securing ring which engages in a groove in the housing.
  • the hub halves are split and each have an inner and an outer ring.
  • an intermediate ring in the form of an elastomeric layer is disposed between the inner and the outer ring. This achieves the advantage that shocks transmitted from the outside via the steering linkage to the spindle or the splined shaft profile are attenuated. Inner and outer ring are thus decoupled with respect to a vibration stress.
  • the invention further relates to a rear axle steering system for a motor vehicle having an actuator according to the aforementioned embodiments.
  • 2b is a plan view of the split hub ring with sawtooth profiles
  • 3a shows the split hub ring in a tensioned position
  • Fig. 3b is a plan view of the hub ring gem. Fig. 3a,
  • Fig. 5b is a detail E of Fig. 5a and
  • Fig. 1 shows a partially illustrated actuator 1 for a rear axle with a housing 2 and a spindle 3, which is part of a spindle drive, not shown, also called screw, is.
  • the spindle 3 which has a threaded portion 3a and is drivable by a rotatable spindle nut, not shown, is displaceable in the axial direction and therefore has an anti-rotation, which is designed as a spline profile 4, so that the spindle can not rotate about its longitudinal axis during rotation of the spindle nut.
  • a thrust bearing 5 is inserted in a corresponding bore, which is designed as a split hub ring 5 and has a splined hub profile 6 for receiving the spline profile 4.
  • the spindle 3 is thus secured against rotation relative to the housing 2.
  • a piezo-ring element P is arranged, which on the one hand housing side, z. B. by a circlip (not numbered) is supported and on the other hand rests against the end face of the split hub ring 5.
  • the piezo ring element P exerts an axial force on the split hub ring 5.
  • the protruding from the housing 2 end of the spindle 3 is - which is not shown - connected to a steering linkage for articulation to a wheel of a rear wheel of a motor vehicle.
  • the thrust bearing 5 can be arranged on one or both sides of the actuator 1, depending on whether an individual actuator acting on a wheel or a actuator acting on both wheels simultaneously on both wheels of an axle is used.
  • FIGS. 2 a to 3b show the thrust bearing 5 designed as a split hub ring 5 as an individual part in different representations.
  • the split hub ring 5 has a first, in the axial direction front hub half 7 and a second, axially rear hub half 8.
  • Fig. 2a shows the split hub ring 5 in a perspective view, from which a splined hub profile 6a for the front hub half 7 and a splined hub profile 6b for the rear hub half 8 can be seen.
  • the front hub half 7 and the rear hub half 8 have, in the region of their parting line, a first sawtooth profile 9 and a second sawtooth profile 10 which engage in one another.
  • the front hub half 7 is divided and has an outer ring 7a, also called outer ring 7a, and an inner ring 7b, also called inner ring 7b, with the splined hub profile 6a.
  • an intermediate ring 11 formed as an annular layer of an elastomer disposed, which serves as a spring-damping element.
  • the rear hub half 8 is - what in the Drawing is not recognizable - also divided into an inner and an outer ring with intermediate ring in an analogous manner.
  • Fig. 2b shows a plan view of the circumference of the split hub ring 5 with the axis a, the interlocking sawtooth profiles 9, 10.
  • the sawtooth profiles 9, 10 each have short, predominantly in the axial direction a running, steep flanks 9a, 10a and mainly in Circumferentially extending, long or flat flanks 9b, 10b.
  • the illustration according to FIGS. 2 a and 2b shows the split hub ring 5 in a so-called design or initial position in which an axial gap s is left between the long flanks 9b, 10b. This axial gap s allows a relative axial displacement of both hub halves 7, 8 against each other, d. H. until the stop, so that the hub halves can not be moved closer to each other.
  • FIGS. 3a and 3b show the split hub ring 5 with sawtooth profiles 9, 10 located without gaps.
  • the slope of the short or steep sawtooth edges 9a, 10a can be seen as an acute angle to the axis a of the hub ring 5.
  • the size of the pitch angle is decisive for the transmission ratio between an axial path and a path in the circumferential direction in a mutual displacement of the two hub halves 7, 8.
  • the surfaces of the flanks 9a, 9b 10a, 10b preferably have the shape of involutes.
  • Fig. 4 shows the first or front hub half 7 as a single part in perspective view of the sawtooth profile 9, which is part of the outer ring 7a.
  • the inner ring 7b which has the splined hub profile 6a, is decoupled from the outer ring 7a by the elastic intermediate ring 11.
  • FIG. 5a, 5b and 5c show the outer ring 7a with a sawtooth profile 9 in various perspective views, FIG. 5b showing a detail E from FIG. 5a.
  • Fig. 5b shows an enlarged view of the short, steep flank 9a of the sawtooth profile 9.
  • the edges between the long flanks 9b and the short flank 9a are broken and appear as chamfers 9c.
  • Fig. 5c shows the outer ring 7a with a short edge 9a and the axis of rotation a.
  • the leading edge and the trailing edge of the short flank 9a are connected to the axis a by a first radius r1 and a second radius r2.
  • the two radii r1, r2 form a spatial angle a, which illustrates the relation between a displacement in the axial and in the tangential direction.
  • split hub ring 5 The function of the split hub ring 5 will be explained below with reference to FIGS. 1 and 2a to 3b.
  • a splined shaft profile 4 and a splined hub profile 6 was selected, which has a circumferential clearance between the flanks of the spline and the spline hub for manufacturing reasons.
  • Such a backlash is prevented by the device according to the invention in the form of a split hub ring 5, in which both hub halves, i. H. the front hub half 7 and the rear hub half 8 can be moved and clamped in the circumferential direction relative to each other.
  • the tension is caused by an axial movement of the front hub half 7, in that the piezo ring element P (FIG. 1) exerts an axial force on the front hub half 7.
  • the piezo ring element P is subjected to an electrical voltage, which leads to an expansion and a travel in the axial direction.
  • the front hub half 7 performs an axial movement under the influence of the axial force, which is possible due to the axial gap s (FIGS. 2a, 2b).
  • the front hub half 7 is rotated relative to the rear, fixed hub half 8 by a predetermined amount in the circumferential direction, with the result that the flanks of the front spline profile 6a are no longer in a plane with the flanks of the rear spline profile 6b, but rather the flanks are circumferentially offset from each other.
  • This achieves a contact on both sides of the flanks of the splined hub profiles 6a, 6b and the flanks of the splined shaft profile 4 (FIG. 1).
  • flanks F1, F2 are no longer in a plane, but they are in the circumferential direction, which is not apparent from the drawing, offset against each other. This offset eliminates the backlash.

Landscapes

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

Abstract

L'invention concerne un actionneur, comprenant une commande à broche comportant une broche (3) à déplacement axial, un logement (2) pourvu d'au moins un palier de butée (5) pour la broche (3), la broche (3) comprenant en extrémité au moins une partie comportant un profil d'arbre cannelé (4) et le palier de butée (5) comportant une ouverture présentant un profil de moyeu cannelé (6) pour recevoir le profil d'arbre cannelé (4). Selon l'invention, le palier de butée (5) est réalisé sous la forme d'une bague de moyeu (5) divisée pourvue d'une première moitié et d'une deuxième moitié, lesquelles - observées dans la direction axiale - sont agencées l'une derrière l'autre et peuvent être mises en tension l'une vis-à-vis de l'autre dans la direction périphérique.
PCT/EP2017/060849 2016-06-09 2017-05-08 Actionneur pour essieu arrière directeur WO2017211513A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016210227.3 2016-06-09
DE102016210227.3A DE102016210227A1 (de) 2016-06-09 2016-06-09 Aktuator für eine Hinterachslenkung

Publications (1)

Publication Number Publication Date
WO2017211513A1 true WO2017211513A1 (fr) 2017-12-14

Family

ID=58671688

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/060849 WO2017211513A1 (fr) 2016-06-09 2017-05-08 Actionneur pour essieu arrière directeur

Country Status (2)

Country Link
DE (1) DE102016210227A1 (fr)
WO (1) WO2017211513A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109572325B (zh) * 2018-12-20 2024-06-25 内蒙古北方重型汽车股份有限公司 矿用自卸车d形分体式后桥壳总成
DE102021125484A1 (de) 2021-10-01 2023-04-06 Schaeffler Technologies AG & Co. KG Schubgestänge für einen Linearaktuator und Linearaktuator mit einem Schubgestänge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009039164A1 (de) * 2008-12-09 2010-06-10 Continental Teves Ag & Co. Ohg Lenkvorrichtung, insbesondere für eine Hinterradlenkung
EP2457753A2 (fr) * 2010-11-30 2012-05-30 Schaeffler Technologies AG & Co. KG Dispositif de réglage
DE102013107827A1 (de) 2013-07-23 2015-01-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Getriebeanordnung im Kraftfahrzeugbereich sowie Hinterachslenkanordnung mit einer derartigen Getriebeanordnung
DE102014206934A1 (de) 2014-04-10 2015-10-15 Zf Friedrichshafen Ag Stellmotor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4445858B4 (de) * 1994-12-22 2008-05-08 Röhm Gmbh Bohrvorrichtung
DE29904028U1 (de) * 1999-03-05 1999-09-02 Klann Tools Ltd Sicherheitsspindelkopf für Spindelantriebe
EP2470807B1 (fr) * 2009-08-24 2013-11-27 Schaeffler Technologies AG & Co. KG Système de serrage, et procédé de serrage d'une liaison arbre-moyeu
EP2614268B1 (fr) * 2010-09-09 2016-10-12 Schaeffler Technologies AG & Co. KG Dispositif de mise en tension pour une chaîne cinématique d'un véhicule à moteur
FR2995959B1 (fr) * 2012-09-24 2014-09-12 Valeo Embrayages Ensemble de transmission de couple, en particulier pour vehicule automobile

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009039164A1 (de) * 2008-12-09 2010-06-10 Continental Teves Ag & Co. Ohg Lenkvorrichtung, insbesondere für eine Hinterradlenkung
EP2457753A2 (fr) * 2010-11-30 2012-05-30 Schaeffler Technologies AG & Co. KG Dispositif de réglage
DE102013107827A1 (de) 2013-07-23 2015-01-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Getriebeanordnung im Kraftfahrzeugbereich sowie Hinterachslenkanordnung mit einer derartigen Getriebeanordnung
DE102014206934A1 (de) 2014-04-10 2015-10-15 Zf Friedrichshafen Ag Stellmotor

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