EP1523627A1 - Coussinet sph rique zones diff remment renforc es - Google Patents

Coussinet sph rique zones diff remment renforc es

Info

Publication number
EP1523627A1
EP1523627A1 EP03787675A EP03787675A EP1523627A1 EP 1523627 A1 EP1523627 A1 EP 1523627A1 EP 03787675 A EP03787675 A EP 03787675A EP 03787675 A EP03787675 A EP 03787675A EP 1523627 A1 EP1523627 A1 EP 1523627A1
Authority
EP
European Patent Office
Prior art keywords
bearing shell
joint
ball
areas
reinforced
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Withdrawn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
EP03787675A
Other languages
German (de)
English (en)
Inventor
Frank Budde
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 Lemfoerder GmbH
Original Assignee
ZF Lemfoerder GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Lemfoerder GmbH filed Critical ZF Lemfoerder GmbH
Publication of EP1523627A1 publication Critical patent/EP1523627A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • F16C11/0623—Construction or details of the socket member
    • F16C11/0628—Construction or details of the socket member with linings
    • F16C11/0633—Construction or details of the socket member with linings the linings being made of plastics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • F16C11/0623—Construction or details of the socket member
    • F16C11/0628—Construction or details of the socket member with linings
    • F16C11/0633—Construction or details of the socket member with linings the linings being made of plastics
    • F16C11/0638—Construction or details of the socket member with linings the linings being made of plastics characterised by geometrical details
    • 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
    • Y10T403/32721—Elastomeric seat
    • 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
    • Y10T403/32737—Universal ball and socket including liner, shim, or discrete seat
    • 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
    • Y10T403/32786—Divided socket-type coupling
    • 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
    • Y10T403/32795—Bifurcated socket
    • 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
    • Y10T403/32803—Separable socket sections

Definitions

  • the present invention relates to a bearing shell for a ball joint, in particular for motor vehicles, and the ball joint itself according to the features of the preambles of independent claims 1 and 16.
  • a generic bearing shell for ball joints, in particular for motor vehicles, is known from DE 29722507 Ul.
  • DE 29722507 U1 discloses a bearing shell which has slits for resilient deflection when a joint ball is mounted in the bearing shell, said slots extending essentially in the direction of the central axis of the bearing shell.
  • the rear walls of the bearing shell have groove-shaped depressions that serve as grease deposits for the lubrication of the ball joint.
  • Spacer knobs are provided on the outer walls of the bearing shell, which specify the position of the bearing shell in the ball joint housing and, after insertion in the ball joint housing, generates a slight, if any, preload due to the additional material that presses the bearing shell against the joint ball by being supported on the ball joint housing. Preloading the bearing shell in certain areas is highly desirable, since this enables the joint ball not to lift off parts of the bearing shell, even under load, and thus the whole
  • the bearing shells of DE 19932789 AI and DE 29722507 Ul are produced homogeneously from a plastic by injection molding.
  • this construction gives rise to the problem that when an inexpensive plastic is used, it is either tribologically well suited in an unreinforced form, but then does not have sufficient strength, or has good strength properties due to fiber reinforcement.
  • good strength properties are equivalent to a loss of tribological properties in low-cost plastics.
  • no preloading of the bearing shell can be achieved with these plastics for the purpose of better power transmission.
  • the ball bearing according to the invention and thus also the bearing shell according to the invention can be subjected to greater radial or axial loads.
  • the area of the bearing shell against which the joint ball rests due to the load (load area) is compressed by the joint ball in the direction of the load. If the bearing shell yields, the joint ball also moves in the direction of loading by the amount by which the bearing shell yields.
  • the joint ball can thereby stand out from the area opposite the load area of the bearing shell (opposite here means lying in a direction opposite the load direction).
  • the areas of the bearing shell that are less heavily loaded are therefore made of an unreinforced or less reinforced plastic.
  • the bearing shell is pretensioned during assembly, which means that the joint ball can no longer lift off the bearing shell under normal loads, so that all bearing surfaces of the bearing shell are in engagement, even under greater load, for the transmission of forces.
  • the preload on the bearing shell that is achieved in this way reduces the risk of free play of the joint ball in the bearing shell, which can lead to knocking and thus failure of the joint.
  • Areas which are exposed to greater loads have, according to the invention, a reinforced core which counteracts deformation and wear which occur under load and thus reduces the amount by which the joint ball lowers under heavy load due to the compression of the plastic.
  • a bearing shell designed in this way advantageously makes it possible to design the bearing shell with a large contact area in one piece and at the same time from a highly fiber-reinforced material.
  • a further advantageous embodiment results from a bearing shell which is additionally provided with webs and slots.
  • the bearing shell according to the invention advantageously has reinforced and unreinforced or less reinforced areas, the reinforced areas being produced, for example, by means of a multi-component system.
  • the multi-component system consists of reinforced plastics and less reinforced or unreinforced plastics.
  • the reinforced area consists of a core component and a jacket component.
  • the core components form the reinforcement through appropriate additives such as fibers, mica, minerals, fillers or spheres, the degree of reinforcement of which can be variably adjusted by the type and amount of the reinforcement additives used.
  • the jacket component is made of a tribologically suitable plastic. It encloses the core component in the sections in which there is an increased risk of wear due to friction effects due to appropriate reinforcement additives, such as between the core component and the joint ball, thus reducing the susceptibility to wear of the ball joint.
  • Figure 1 and 2 side views of a one-piece bearing shell of a mainly radial ball joint with axial and radial tolerance compensation;
  • FIG. 3 cross section through the bearing shell according to FIGS. 1 and 2;
  • Figures 4 and 5 side views of a one-piece bearing shell of a mainly axially loaded ball joint with axial and radial tolerance compensation;
  • FIG. 6 Side view of a one-piece bearing shell of a mainly axially loaded ball joint in the form of a sleeve joint with axial and radial tolerance compensation;
  • FIG. 7 cross section through the bearing shell according to FIG. 6;
  • Figure 8 Side view of a multi-part bearing shell with axial and radial tolerance compensation
  • Figure 9 Cross section through a multi-part bearing shell of a mainly axially loaded ball joint in the form of a support joint with axial and radial tolerance compensation;
  • FIG. 10 cross section through a multi-part bearing shell of a ball joint of a ball joint in the form of an axial joint, which is mainly subjected to tension;
  • Figure 11 Cross section through a one-piece bearing shell with defined support areas
  • Figure 12 Enlargement of a necessary to vary the support areas
  • Figures 1 to 3 show a bearing shell 1 of a mainly radially loaded ball joint.
  • the bearing shell is made in one piece and has a base body 2, on which a bearing shell part 3 comprising an articulated ball is molded.
  • the bearing shell 1 is provided with elastic webs 4 and slots 5, which enable the bearing shell 1 to spring open during the assembly process.
  • the spring-back process counteracts an otherwise usual weakening of the plastic, which can lead to the bearing shell breaking due to the expansion of the plastic during the assembly process, even during the assembly process.
  • the bearing shell according to FIG. 1 is mainly intended for radially loaded ball joints.
  • the elastic web 4 is designed in such a way that the bearing shell can spring open during assembly in combination with a circumferential slot 5 without great effort (see also FIG. 3).
  • the webs also function 4 through their elastic behavior as tolerance compensation during assembly, whereby they compensate for housing and ball tolerances.
  • An increase in the axial tolerance compensation can be achieved by a rubber ring that is installed in the ball joint housing between the bearing shell and ball joint housing when the bearing shell is installed. This means that any differences in height that occur during assembly can be compensated for, which means that more uniform joints can be produced.
  • Figure 2 shows a further side view of the bearing shell 1 of the mainly radially loaded ball joint.
  • the bearing shell has a circumferential slot 5 along the bearing shell part 3.
  • a further web 6 shown in dashed lines
  • Crosspieces 7 in the base body 2 of the bearing shell 1, also drawn in dashed lines, can optionally be introduced in order to achieve radial tolerance compensation by appropriate prestressing.
  • FIG. 3 shows a cross section through the bearing shell 1 according to FIG. 1.
  • the bearing shell 1 can be reinforced on both sides depending on the type of load, less reinforced or unreinforced on both sides and reinforced on one side and at the same time less reinforced or unreinforced on the other side.
  • both the base body 2 and the bearing shell parts 3 have a two-component system on the right, which consists of a tribologically suitable outer surface 8, into which a core 9 reinforcing the plastic is inserted.
  • a first plastic is first injected into the correspondingly shaped cavity, the cavity being only partially filled. This material forms the outer surface of the two-component system.
  • the cavity is completely filled with a second plastic, which forms the reinforced core component.
  • the base body 2 of the bearing shell 1 can also be made non-reinforced or slightly reinforced by appropriate sprue technology, in order to achieve a greater preload on the joint ball, for example, and thereby increase the axial preload.
  • the bearing shell 1 is made less reinforced or unreinforced to increase the preload.
  • ribs 10 can optionally be formed on the base body.
  • the bearing shell also has recesses 4a on its inside and / or outside, which in particular makes it easier for the bearing shell to spring open during assembly.
  • Figures 4 and 5 show embodiments of a bearing shell 11 of a mainly axially loaded ball joint.
  • the bearing shell 11 can also be reinforced on both sides depending on the type of load, less reinforced or unreinforced on both sides and reinforced on one side and at the same time less reinforced or unreinforced on the other side.
  • the corresponding webs 14 are attached in the areas where the lowest loads have to be absorbed, in the exemplary embodiment this area lies at the level of the equatorial plane (FIG. 4). In this exemplary embodiment, too, the web 14 serves for easier assembly and for creating a preload on the bearing shell.
  • a further web 17 can additionally be provided on the base body 12 (FIG. 5).
  • the outer contour of the base body 12 can either be circular (figure 5 on the right) or oblique (figure 5 on the left) in accordance with the structural specifications.
  • FIGS. 6 and 7 show a one-piece bearing shell 21 of a ball joint, which is mainly axially loaded, in the form of a sleeve joint.
  • Both elastic webs (24, 27) and reinforcements of the plastic are arranged according to the load.
  • the right part of the bearing shell is designed with an elastic web for axial tolerance compensation, while the left part of the bearing shell is solid.
  • elastic webs 27 shown in broken lines in FIG. 6) can also be arranged for radial prestressing. Additional longitudinal slots can be made in the bearing shell 21 for a simple assembly process.
  • FIG. 7 shows a section through the bearing shell according to FIG. 6.
  • the bearing shell has a two-component system 28, 29 on one side (FIG.
  • Figure 8 shows a side view of a multi-part bearing shell with axial and radial tolerance compensation.
  • the axial tolerance compensation is achieved by means of material projections 34 in the form of projections, which are arranged such that they are compressed during assembly of the bearing shell in the ball joint housing and expand again in areas in which the joint ball is lowered in accordance with the load, and so the resulting one Balance the game again.
  • the material projections 34 are arranged, for example, on the one hand on the lower shell ( Figure 8 left) and on the other hand on the upper shell ( Figure 8 right).
  • the radial tolerance compensation, not shown, and a preloading of the bearing shell after assembly are made possible by a corresponding arrangement of webs (see also FIG. 2).
  • Figure 9 shows a cross section through a multi-part bearing shell 31 of a mainly axially loaded ball joint in the form of a support joint. Since pressure forces predominate in this embodiment, the plastic of the bearing shell lowers in the area of the contact surfaces of the joint ball on the base body 32. A correspondingly necessary, large axial tolerance compensation is achieved by a greater preloading of the bearing shell 31 by using bearing shell parts 33 with larger wall thicknesses. The increase in the wall thickness of the bearing shell parts 33 arranged opposite to the direction of force increases the preload in the bearing shell 31, which is synonymous with a stronger compression of the plastic during assembly.
  • the base body 32 of the bearing shell 31 can have a reinforcing core 39.
  • FIG. 10 shows a cross section through a multi-part bearing shell 41
  • Ball joint of a ball joint in the form of an axial joint which is mainly subjected to tension.
  • the area of the bearing shell parts 43 above the equatorial plane with a reinforcing core 49 is predominant fitted.
  • the base body 42 can also have a greater wall thickness than the bearing shell parts.
  • FIG. 11 shows a cross section through a bearing shell 51 reinforced with a core 59 and provided with elastic webs 54, which, in addition to the above-mentioned features, makes it possible by arranging projections 55 (see also FIG. 12) on the 1- ⁇ nen lake of the bearing shell, which adjust the engaged wing to the load size and thus achieve defined moments in the ball joint.
  • Both base body 52 and bearing shell parts 53 have, for example, a reinforcing core 59.
  • the projections 55 with the height ⁇ s alone form the contact surface of the joint ball on the bearing shell.
  • the joint ball displaces the plastic forming the projections, so that the entire surface 56 of the bearing shell 51 forms the contact surface of the joint ball and the entire surface of the ball socket for the transmission of the forces thereby comes into attack.
  • the forces are evenly transferred to the plastic and the effective surface pressures are kept low, so that the plastic is less loaded and crawls less.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Support Of The Bearing (AREA)

Abstract

Coquille (1) de coussinet pour une articulation sphérique en plastique, et articulation sphérique en elle-même. Ladite coquille (1) de coussinet comporte des premières zones qui sont soumises à des sollicitations mécaniques plus importantes que les sollicitations exercées sur les zones restantes de la coquille (1). La matière formant les premières zones de la coquille (1) de coussinet est constituée d'un plastique renforcé, tandis que les autres zones sont constituées de plastique à renforcement minime ou exempt de renforcement.
EP03787675A 2002-07-24 2003-07-16 Coussinet sph rique zones diff remment renforc es Withdrawn EP1523627A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10233489 2002-07-24
DE10233489A DE10233489B4 (de) 2002-07-24 2002-07-24 Hochleistungs-Kugelschale
PCT/DE2003/002387 WO2004016960A1 (fr) 2002-07-24 2003-07-16 Coussinet sphérique à zones différemment renforcées

Publications (1)

Publication Number Publication Date
EP1523627A1 true EP1523627A1 (fr) 2005-04-20

Family

ID=30010315

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03787675A Withdrawn EP1523627A1 (fr) 2002-07-24 2003-07-16 Coussinet sph rique zones diff remment renforc es

Country Status (7)

Country Link
US (2) US7318686B2 (fr)
EP (1) EP1523627A1 (fr)
JP (1) JP2005533990A (fr)
KR (1) KR20050028906A (fr)
CN (1) CN100416116C (fr)
DE (1) DE10233489B4 (fr)
WO (1) WO2004016960A1 (fr)

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DE102004022533B4 (de) 2004-05-05 2006-08-03 Zf Friedrichshafen Ag Lagerschale
DE102004048753A1 (de) * 2004-10-05 2006-04-06 Wulf Gaertner Autoparts Ag Kugelgelenk
DE102005044564A1 (de) * 2005-09-17 2007-03-29 Demag Cranes & Components Gmbh Vorrichtung zum Aufhängen einer Schiene, insbesondere einer Fahrschiene eines Hängeförderers oder eines Hebezeugs
DE102006045809B4 (de) * 2006-09-26 2015-06-18 Zf Friedrichshafen Ag Kugelgelenk
DE102007041356A1 (de) * 2007-08-30 2009-03-05 Zf Friedrichshafen Ag Gelenk- und/oder Lageranordnung
US9476447B2 (en) * 2008-05-21 2016-10-25 Federal-Mogul Powertrain, Inc. Ball joint assembly and method of making
JP5284018B2 (ja) * 2008-09-09 2013-09-11 日本発條株式会社 ボールジョイント
PL232039B1 (pl) * 2014-07-18 2019-05-31 Valeo Autosystemy Spolka Z Ograniczona Odpowiedzialnoscia Łożysko zapobiegające przeciążeniom, w szczególności do mechanizmu wycieraczek samochodowych, oraz mechanizm wycieraczek samochodowych zawierający takie łożysko
JP6768584B2 (ja) * 2017-03-31 2020-10-14 日本発條株式会社 ボールジョイントの製造方法、及びスタビリンクの製造方法
CN107053258A (zh) * 2017-05-26 2017-08-18 绵阳伦奇机器人有限公司 一种拖链的铰接结构
US10954995B2 (en) * 2018-03-06 2021-03-23 Federal-Mogul Motorparts Llc Socket assembly and method of making
US11859657B2 (en) 2020-03-02 2024-01-02 Federal-Mogul Motorparts Llc Socket assembly with a retention device

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US4076344A (en) * 1976-05-07 1978-02-28 Gulf & Western Manufacturing Company Bearing assembly for a ball and socket joint
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Title
See references of WO2004016960A1 *

Also Published As

Publication number Publication date
WO2004016960A1 (fr) 2004-02-26
KR20050028906A (ko) 2005-03-23
US7318686B2 (en) 2008-01-15
JP2005533990A (ja) 2005-11-10
CN100416116C (zh) 2008-09-03
DE10233489A1 (de) 2004-02-05
CN1623045A (zh) 2005-06-01
DE10233489B4 (de) 2004-08-12
US20040258462A1 (en) 2004-12-23
US20080063466A1 (en) 2008-03-13

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