WO2011069499A2 - Elément de palier ou de transmission de force présentant une transition de section transversale - Google Patents

Elément de palier ou de transmission de force présentant une transition de section transversale Download PDF

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Publication number
WO2011069499A2
WO2011069499A2 PCT/DE2010/050088 DE2010050088W WO2011069499A2 WO 2011069499 A2 WO2011069499 A2 WO 2011069499A2 DE 2010050088 W DE2010050088 W DE 2010050088W WO 2011069499 A2 WO2011069499 A2 WO 2011069499A2
Authority
WO
WIPO (PCT)
Prior art keywords
cross
component
hyperbolic
power transmission
storage
Prior art date
Application number
PCT/DE2010/050088
Other languages
German (de)
English (en)
Other versions
WO2011069499A3 (fr
Inventor
Frank Scheper
Jens Diekhoff
Michael Mühl
Klaus Warnken
Stefan Wenk
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 WO2011069499A2 publication Critical patent/WO2011069499A2/fr
Publication of WO2011069499A3 publication Critical patent/WO2011069499A3/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/005—Ball joints
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/008—Attaching arms to unsprung part of vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/14—Mounting of suspension arms
    • B60G2204/143—Mounting of suspension arms on the vehicle body or chassis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/14—Mounting of suspension arms
    • B60G2204/143—Mounting of suspension arms on the vehicle body or chassis
    • B60G2204/1431—Mounting of suspension arms on the vehicle body or chassis of an L-shaped arm
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/416—Ball or spherical joints

Definitions

  • the invention relates to a component with a load receiving area and with a rounded cross-sectional transition between the load receiving area and the remaining component, in particular for storage or for power transmission between components, according to the preamble of patent claim 1.
  • Tie rods, ball joint pin or can also act on shaft sections are often multiple component areas with different cross sections or
  • Such rounded cross-sectional transitions between component regions with differently sized cross-sections are, in principle, independent of the material used, in particular of cast parts, injection-molded parts, on components.
  • Circle segments are used as envelopes for the shaping of the cross-sectional transition. Often in the prior art also rounded interconnected line segments are used as an envelope for cross-sectional transitions.
  • the invention should make it possible to make cross-sectional transitions on highly loaded components so that the
  • the bearing or power transmission component according to the present invention comprises at least one load receiving area, wherein the load receiving area and the remaining building block are integrally formed. Furthermore, a rounded cross-sectional transition is arranged between the load receiving area and the remaining component. For this purpose, the cross-sectional transition has a variable between load receiving area and residual component
  • the bearing or power transmission component is characterized in that the course of the envelope of the cross-sectional transition between the load receiving area and residual component at least partially substantially with the positive branch of the arc tangent, the Areasinus hyperbolic, the
  • Cross-sectional transition between load receiving area and residual component may be included, which run between each two of said curves or are formed from combinations of such curves or their sub-areas.
  • the invention is realized irrespective of which region of the positive branch of the arc tangent, the hyperinolic area, the hyperbolic arachnoid, the hyperbolic cotangent, the hyperbolical hyperkolic, or the partial ellipse is actually used for shaping the envelope.
  • it may also be useful, in particular, not to let the envelope begin at the beginning of the positive branch of one of the named curves (ie in particular at x 0) but at another position of the positive branch of the respective function curve, in particular this way a smooth transition to another segment of the envelope of the
  • a particularly preferred embodiment of the invention provides that the envelope of the cross-sectional transition between the load receiving area and the rest of the component beyond the actual cross-sectional transition in the field of Remaining component tangentially extrapolated or point-mirrored at the point of transition into the residual component.
  • Extrapolation or point mirroring generated continuation of the envelope in the area of this continuation the outer boundary of the residual component.
  • Envelope lying areas of the remaining component can thus be removed without the load capacity of the component is significantly weakened thereby. In this way, material and space requirements and thus also weight and cost for a component constructed according to the invention can be further reduced.
  • the envelope comprises a plurality of continuous and smooth (ie tangentially, or in mathematical terms continuous and differentiable) merging into each other sections.
  • the envelope may in particular comprise a plurality of smoothly merging segments of the positive branch of the arc tangent, the hyperinolic area, the hyperbolic hyperbole, the hyperbolic cotangent, the hyperbolical hyperkolic, or the partial ellipse, or at least one of the segments of the envelope may be connected to a segment of the positive branch one of the mentioned function curves
  • the invention can be used in all types of components in which areas of different cross-section material-saving must be connected to each other so that an optimal line of force results while minimizing voltage increases or notch voltages in the cross-sectional transitions.
  • the component is the shaft or the ball pivot of a ball joint, a tie rod, or in another embodiment by a
  • Embodiment exported ball stud benefits.
  • significant weight reductions are also possible in that the shank of the ball stud has a smaller extent over most of its axial length
  • Cross section or diameter may have as the comparable conical pin shaft according to the prior art.
  • Elastomer bearing or hydraulic bearing is.
  • the advantages of the invention are particularly pronounced for use, since such took on eb he oak for storage - such as elastomeric bearings or hydraulic bearings - are constructive and narrow dimensions are set in terms of dimensions. Because in such cases, it is usually desirable to use elastomeric bearings or hydraulic bearings with the smallest possible inner sleeve diameter on the one hand to the largest possible space within the camp for the
  • Rad Onlyslenkers be reached, or it may be a lighter or
  • the inner sleeve of the elastomer or hydraulic bearing and the cross-sectional transition between Lagerpin and handlebar overlap at least partially.
  • the contour of the inner sleeve of the bearing is preferably adapted to the shape of the envelope of the cross-sectional transition.
  • Hydrolabs is designed so that it can absorb the cross-section üb transition between Lagerpin and residual component at least partially. This results in the field of bearing support on the Lagerpin a particularly uniform course of force especially with very low bending stresses, since the force or torque input from the bearing on the Lagerpin already partially within the cross-sectional transition to the rest of the component, and thus in a region of the bearing pin, the already has a slightly enlarged cross-section and thus increased resistance moments.
  • Load bearing portion or the bearing pins a stop element for limiting the spring travel for the elastomer or hydraulic bearing is arranged.
  • Federwegbegrenzungs are basically advantageous to protect in particular high-quality elastomer or hydraulic bearings from overloading, for example by heavy road shocks or by temporary, high driving or braking torques on the motor vehicle.
  • Aluminum Rad entryslenker acts.
  • the aluminum handlebar is designed so that it can replace a possibly existing steel Rad Entryslenker compatible.
  • Thanks to the invention can thus replace, for example, steel wishbones by compatible aluminum wishbones, which significantly reduce the unsprung masses of the suspension of a vehicle and the driving and
  • the invention even makes it possible, if necessary, to measure compatible interchangeability of a steel wheel control arm by means of an aluminum wheel control arm, without any significant effect
  • connection components in particular to the elastomer or
  • Hydraulic bearings of the handlebar must be done.
  • existing, completely forged aluminum handlebars can be switched to more cost-effective production processes, in particular to the use of castings, or of precast Blanks that are only forged once more to obtain the finished component.
  • Embodiment of a component according to the invention with load receiving area including cut shown hydraulic mount;
  • FIG. 2 in a schematic representation of a longitudinal section through the
  • FIG. 3 is a longitudinal section through the load receiving area of a further component according to the prior art in a representation corresponding to FIG. 2;
  • FIGS. 2 and 3 shows in a representation corresponding to FIGS. 2 and 3 a longitudinal section through the load receiving area of a component according to an embodiment of the invention
  • Fig. 5 is a schematic sectional view of
  • Hydro bearing according to Fig. 1; 7 shows an enlarged isometric view of the load-receiving area and the hydraulic bearing shown in section in accordance with FIG. 6;
  • FIG. 9 shows an exemplary embodiment of a ball stud of a
  • FIG. 11 is a further enlarged representation of the two mutually merging sections of the positive branch of the arc tangent course of the envelope of the cross-sectional transition of FIG. 10;
  • Fig. 12 shows another embodiment of a ball stud a
  • FIG. 14 is a further enlarged representation of the two merging sections of the positive branch of the arc tangent course of the envelope of the cross-sectional transition of FIG. 13;
  • FIG. 15 shows a schematic longitudinal section through a ball stud with a conical seat according to the prior art
  • Fig. 16 shows the ball stud of the prior art shown in FIG. 15 under radial load with schematically visualized
  • FIG. 17 in a representation corresponding to Fig. 15 a ball stud according to an embodiment of the invention
  • FIG. 18 shows the ball stud according to FIG. 17 under radial load with schematically visualized voltage curves
  • Fig. 19 shows a further embodiment of a ball stud a
  • FIG. 20 is an enlarged view of the cross-sectional transition between the shaft and the approach of the thread rolling diameter on the ball pin of FIG. 19.
  • Fig. 1 shows as an embodiment of a component according to the invention
  • Load receiving area in isometric view a wishbone 1 with a designed as Lagerpin 2 load receiving area and one in the area
  • the hydraulic bearing 3 is shown cut open to recognize the load receiving area in the form of the bearing pin 2 can.
  • the wishbone 1 is designed as a one-piece aluminum forging. It may in particular be a component produced as a cast blank and then overmolded. Such produced in the form of a combination of a casting process and a forging aluminum components are particularly inexpensive to produce and are the material properties and resilience ago between a pure casting and a classic forging.
  • Load receiving area 2 and remnant component 1 is with regard to the replacement of classic forgings by castings or cast and then overmoulded components of great importance, since the transition 6 between the load receiving area 2 and residual component 1 forms one of the most highly stressed areas, for example in a control arm 1. This is especially true when a previously forged wishbone made of aluminum - or even a
  • FIG. 2 shows a longitudinal section through the load receiving area or bearing pin 2 of a transverse link 1, the contour of the bearing pin 2 shown in FIG. 2 corresponding to the prior art. In the prior art are often still
  • cross-sectional transitions 4 lead to relatively high notch stresses and corresponding
  • the relative failure frequencies are assigned to the hatches, which in the longitudinal section through the bearing pin 2 according to FIG have been used. It can be seen that the failure frequencies in some areas of the cross-sectional transition 4 between bearing pin 2 and residual component 1 are up to ten times as high as in the other areas of the
  • Residual component 1 is shown in section by a further Lagerpin 2 of FIG. 3.
  • the envelope curve for the cross-sectional transition 5 shown in FIG. 3 is the simple circle segment 5 which is usually used as a cross-sectional transition in the prior art. Although the circle segment 5 according to FIG. 3 is already significantly better than the rounded ones with respect to the failure frequencies
  • Fig. 4 shows the load receiving area on an inventively designed wishbone component 1 with bearing pin 2.
  • Cross-sectional transition 6 between load receiving area 2 and residual component 1 does not exceed the relative value 10 ⁇ 2 .
  • Transverse arm 1 for example, a steel wishbone can replace without connecting components, especially hydraulic bearings 3, in the area of
  • Load receiving area 2 would have to be significantly different dimensions. It follows thanks to the invention thus a substantially compatible plug and play exchange option between steel wishbones and
  • Fig. 5 shows schematically again the cross-sectional transition between a Lagerpin or load receiving area 2 and the associated remainder component 1, as well as a selection of envelopes for possible cross-sectional transitions between load receiving area 2 and remainder component 1.
  • FIG. 5 two variants for known from the prior art circular segment-shaped envelopes 5, 7 for the cross-sectional transition, wherein it is the envelope 7 is a 90 ° -Kreissegment, while the envelope 5 is a 45 ° -Kreissegment. This corresponds to the envelope 5 in the
  • FIG. 5 Shown in dashed lines in FIG. 5 is the course of an envelope which essentially corresponds to the arc tangent 6 over the length of the cross-sectional transition, as has also been used in the cross-section transition 6 formed between load-receiving region 2 and remaining component 1 according to FIG. 4.
  • the course of the curve of the arc tangent 6 is also shown again next to the legend of FIG. It can be seen that the arc tangent 6 has a particularly gradual and uniform course of the envelope 6, which is virtually ideal with respect to the avoidance of notch stresses in the region 8 of the highest failure frequency in the case of a circular segment-shaped transition 5 forms for the cross-sectional transition between the load receiving area 2 and residual component 1.
  • Frequency of failure similarly advantageous course for the transition curve also forms the Areasinus hyperbolic, the latter, however, is not asymptotic at the outlet along the load receiving area 2 and thus is particularly suitable for transitions with an angle> 90 °.
  • Arkuskotangens 6 are point-mirrored with the surface 12 of the residual component 1.
  • this alternative curve 9 of the envelope corresponds to a quarter-ellipse, and is shown in FIG. 5 as a dotted line 9. you recognizes that the course of the quarter ellipse 9 almost exactly matches the course of the arc tangent 6, in particular in the section between 1 and 3 of the length units plotted along the load receiving area 2.
  • Load receiving portion 2 as the Arkuskotangens 6 to then seamlessly pass into a tangent 12 to the residual component surface when hitting the residual component 1.
  • the quarter ellipse 9 also forms a nearly perfectly uniform cross-sectional transition between load receiving area 2 and residual component 1, in particular for the case that the residual component 1 is a plane
  • FIGS. 6 to 8 show the arrangement of an elastomer bearing or hydraulic bearing 3 on the load receiving area or bearing pin 2 of a wishbone component 1 designed according to the invention.
  • FIG. 6 shows first the wishbone according to FIG. 1, which has a load receiving area or a bearing pin 2 , which by means of an inventively formed cross-sectional transition 6 with the
  • FIG. 6 shows the bearing pin 2 and 6 hydrostatic bearing arm of the control arm 1 according to FIGS. 1 and 6 again in an enlarged, isometric view. In a further enlarged view, the bearing pin 2 and the hydraulic bearing 3 arranged thereon are shown again in the plan view according to FIG. 8.
  • Inner sleeve 13 of the hydraulic bearing 3 is used.
  • the hydraulic bearing 3 shown in FIGS. 6 to 8 has at its
  • Drawing-related right end also a ring-shaped
  • Stop element 14 which limits the radial deflections of the hydraulic bearing 3 occurring during driving of the control arm 1 when strong lateral forces occur in order to avoid overloading of the hydraulic bearing 3.
  • FIGS. 9 to 14 show two exemplary embodiments of ball pins 15, 16 of ball joints as further examples of application of the invention.
  • the ball studs 15, 16 according to FIG. 9 and FIG. 12 are mounted in a basic component (21) and each have a number of cross-sectional transitions 6 between one of their load receiving areas (ball 17 or threaded shaft 18) and the respective remaining component. (As the ball studs looked at several here
  • Load receiving areas - in particular 17, 18 - have defined the
  • both the cross-sectional transition from the threaded shank 18 to the stud collar 19 and the cross-sectional transition from the ball 17 to the collar 19 have a course of the envelope coinciding with the arc tangent 6.
  • Fig. 10 shows the cross-sectional transition of the ball 17 of the ball pin 15 of FIG. 9 on the collar 19 of the pin 15 again in an enlarged view. you recognizes that this cross-sectional exodus from two smooth or
  • branches 6 of the arc tangent are in this embodiment at their intersection 20 with the y-axis joined together (the
  • drawing-related upper arc tangency branch was previously mirrored along the y-axis). Since the arc tangent 6 intersects the y-axis at an angle of 45 ° (see also Fig. 5), this combination gives the two
  • each quarter ellipses 9 (see Fig. 5) or generally Generalellipsen. As can be seen from Fig. 5, the quarter ellipse 9 has when used as
  • Load receiving range 2 almost exactly coincides with the course of the arc tangent 6. Therefore, by using the quarter-ellipse 9 instead of the arc tangent 6, in particular symmetrical cross-sectional transitions (cf., FIGS. 10 and 11) can also be realized with notch stress optimization, if an opening angle between 0 ° and 90 ° is required.
  • the ball stud 16 according to FIG. 12 again have both the cross-sectional transition of the threaded shaft 18 on the pin collar 19 and the cross-sectional transition of the ball 17 on the collar 19 with the Arkuskotangens 6 matching waveforms of the envelope.
  • FIG. 13 and Fig. 14 show an enlarged view again the
  • This embodiment is particularly advantageous for mainly bending-loaded, neck-shaped regions, as is the case also with the ball stud 16 according to FIG. 12.
  • FIG. 15 Such a known from the prior art ball stud 22 is also shown in Figs. 15 and 16.
  • Fig. 15 it can be seen that conventional ball pins from the prior art have a tapered shaft 23 and are retracted by a screw 24 in a correspondingly tapered seat bore in the base member 21.
  • Focus areas A and B In the area A, this is associated with a comparatively high probability of failure, in particular since the range of maximum compressive stresses C coincides exactly with the range of maximum tensile stresses at A when the force direction FR changes, which is the case in the ball studs in FIGS. 15 and 16, respectively Technology in the areas A and C leads to correspondingly high voltage amplitudes under dynamic load and thus high failure probabilities in these areas.
  • the areas of maximum tensile stress at A and maximum compressive stress at C when changing the force direction FR are not congruent, but are thanks to the inventive design of the ball stud 16 at different points of the neck of the ball stud ,
  • the voltage amplitude is considerably lower both at A and at C, whereby the dynamic load capacity or service life of the ball stud 16 according to FIG. 17 or 18 already correspondingly significantly higher than that of known ball stud 22 according to FIG. 15 or 16, with otherwise substantially identical dimensions of the ball studs 16 and 22 respectively.
  • ball stud 16 much more uniform over almost the entire length of the shaft 18 and extends, as this in the selectively concentrated tensile prestress in the area B in the ball stud 22 according to the prior art is the case.
  • Ball stud 22 at B to increased risk of failure of the ball stud 22 under dynamic load, but it also deteriorates the seat of the tapered shaft 23 of the ball stud 22 in the base member 21, since most of the
  • the ball pin 22 thus has to be specially designed during assembly an excessive bias by the
  • Screw 24 received because of the setting behavior and the so
  • Pre-tensioning during assembly reduces the fatigue life of the ball stud 22 available during operation and increases the risk of pin failure, particularly in the area of the thread transition at B, and also causes structural over-dimensioning of the ball stud 22.
  • the ball pin 16 according to the invention as shown in FIGS. 17 and 18, which has an arc cross-sectional cross-section transition between the pin collar 19 and shank 18 and a seat on the base member 21 only in the immediate sphere E, the problem of the preload force loss and the associated disadvantages is almost eliminated.
  • ball stud 16 according to FIG. 17 or 18 also lies in the fact that virtually the entire biasing force of the screw 24 after assembly of the
  • the ball stud 16 according to the invention as shown in FIG. 17 and 18 eliminates the fatigue strength of the ball stud 22 according to FIGS. 15 and 16
  • Basic component 21 in a ball pin 22 according to the prior art with conical shaft 23 due to the tolerances of the shaft diameter and the bore diameter of the base member 21 and in dependence on the amount of bias through the screw 24 vary considerably.
  • the further ball stud 25 shown in Figures 19 and 20 is formed in a base member 21 of a softer material, e.g. made of aluminum, mounted.
  • Basic component 21 additionally an annular force transmission element 26 made of a harder material, in particular steel, inserted. Also the outer one
  • Basic component 21 corresponds - as well as the adjacent cross-sectional transition of the pin collar 19 on the shaft 18 of the ball stud 25 - also in this
  • Cross-sectional transitions 6 thus achieve, for example, also on ball studs 15, 16, 25 decisive improvements in the service life and the load capacity.
  • ball pivot at the same
  • Ball studs and tie rods, or components for suspension can be realized, which are thanks to the invention either significantly higher load capacity, or which can be dimensioned correspondingly smaller and lighter with the same load capacity and life.
  • the invention thus makes a crucial contribution to the provision of lightweight, but heavy-duty power transmission parts, also to expand the

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un élément de palier ou de transmission de force présentant au moins une transition de section transversale entre une zone de support de charge de l'élément et le reste de l'élément, une transition de section transversale étant ménagée entre la zone de support de charge et le reste de l'élément. L'élément de palier ou de transmission de force se caractérise en ce que l'allure de l'enveloppante de la transition de section transversale coïncide au moins par endroits avec la branche positive de l'arc cotangente, de l'argument sinus hyperbolique, de l'argument cosinus hyperbolique, de la cotangente hyperbolique, de la cosécante hyperbolique ou avec une ellipse partielle. La transition de section transversale réalisée selon l'invention permet de réduire au minimum les contraintes d'entaille dans la zone de la transition de section transversale entre la zone de support de charge et le reste de l'élément. L'invention permet une augmentation, pouvant atteindre plus d'un ordre de grandeur, de la protection contre les défaillances de la zone de transition entre la zone de support de charge et le reste de l'élément. L'invention permet le prolongement de la durée de vie, la diminution des quantités de matériaux utilisés et/ou l'utilisation de procédés de fabrication ou de matériaux plus économiques, en particulier pour des éléments de palier ou de transmission de force.
PCT/DE2010/050088 2009-12-11 2010-12-08 Elément de palier ou de transmission de force présentant une transition de section transversale WO2011069499A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009054571.9 2009-12-11
DE200910054571 DE102009054571A1 (de) 2009-12-11 2009-12-11 Lagerungs- oder Kraftübertragungsbauteil mit Querschnittsübergang

Publications (2)

Publication Number Publication Date
WO2011069499A2 true WO2011069499A2 (fr) 2011-06-16
WO2011069499A3 WO2011069499A3 (fr) 2011-08-04

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PCT/DE2010/050088 WO2011069499A2 (fr) 2009-12-11 2010-12-08 Elément de palier ou de transmission de force présentant une transition de section transversale

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WO (1) WO2011069499A2 (fr)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
CN106114106A (zh) * 2016-08-31 2016-11-16 宁波永信汽车部件制造有限公司 前下摆臂总成
CN106183677A (zh) * 2016-08-31 2016-12-07 宁波永信汽车部件制造有限公司 一种汽车前下摆臂总成
CN106274326A (zh) * 2016-08-31 2017-01-04 宁波永信汽车部件制造有限公司 汽车前下摆臂总成

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Publication number Priority date Publication date Assignee Title
DE102010003008B4 (de) 2010-03-18 2017-05-24 Zf Friedrichshafen Ag Axialgelenk mit formschlüssigem Radialsitz
DE102011082243A1 (de) 2011-09-07 2013-03-07 Zf Friedrichshafen Ag Lagerungs- oder Kraftübertragungsbauteil mit Querschnittsübergang

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CA912202A (en) * 1969-03-13 1972-10-17 V. Chambers Harold Artificial hip joint
DE19812627B4 (de) * 1998-03-23 2004-04-15 Bayerische Motoren Werke Ag Anordnung eines Kugelgelenkes
JP3705157B2 (ja) * 2001-06-05 2005-10-12 日産自動車株式会社 サスペンションアームの取り付け構造
NO20031250L (no) * 2003-03-18 2004-09-20 Kongsberg Automotive Asa Anordning ved kuleledd
SE528801C2 (sv) * 2005-04-12 2007-02-20 Kongsberg Automotive Asa Förbindningsanordning för en fordonsram och en hjulaxel
DE102005025551C5 (de) * 2005-06-01 2016-06-23 Zf Friedrichshafen Ag Gelenk- und/oder Lageranordnung
DE102009006356B4 (de) * 2009-01-28 2012-04-26 Zf Friedrichshafen Ag Querlenker eines Kraftfahrzeuges

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106114106A (zh) * 2016-08-31 2016-11-16 宁波永信汽车部件制造有限公司 前下摆臂总成
CN106183677A (zh) * 2016-08-31 2016-12-07 宁波永信汽车部件制造有限公司 一种汽车前下摆臂总成
CN106274326A (zh) * 2016-08-31 2017-01-04 宁波永信汽车部件制造有限公司 汽车前下摆臂总成

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WO2011069499A3 (fr) 2011-08-04
DE102009054571A1 (de) 2011-06-16

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