EP0000325B1 - Palier de fixation pour barre d'attelage - Google Patents

Palier de fixation pour barre d'attelage Download PDF

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Publication number
EP0000325B1
EP0000325B1 EP19780100075 EP78100075A EP0000325B1 EP 0000325 B1 EP0000325 B1 EP 0000325B1 EP 19780100075 EP19780100075 EP 19780100075 EP 78100075 A EP78100075 A EP 78100075A EP 0000325 B1 EP0000325 B1 EP 0000325B1
Authority
EP
European Patent Office
Prior art keywords
bearing
rings
bearing rings
box
tongue
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.)
Expired
Application number
EP19780100075
Other languages
German (de)
English (en)
Other versions
EP0000325A1 (fr
Inventor
Georg Dr.-Ing. Rockinger
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.)
Rockinger Spezialfabrik fuer Anhangerkupplungen GmbH and Co
Original Assignee
Rockinger Spezialfabrik fuer Anhangerkupplungen GmbH and Co
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 Rockinger Spezialfabrik fuer Anhangerkupplungen GmbH and Co filed Critical Rockinger Spezialfabrik fuer Anhangerkupplungen GmbH and Co
Publication of EP0000325A1 publication Critical patent/EP0000325A1/fr
Application granted granted Critical
Publication of EP0000325B1 publication Critical patent/EP0000325B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60D—VEHICLE CONNECTIONS
    • B60D1/00—Traction couplings; Hitches; Draw-gear; Towing devices
    • B60D1/48—Traction couplings; Hitches; Draw-gear; Towing devices characterised by the mounting
    • B60D1/50—Traction couplings; Hitches; Draw-gear; Towing devices characterised by the mounting resiliently mounted

Definitions

  • the invention relates to a mounting for a tie rod carrying a coupling head of a trailer coupling to be attached in particular to trucks with a bearing housing surrounding the tie rod at a radial distance and immovably arranged on the truck, in which the tie rod can be rotated about its axis via bearing rings which bear against the inside of the bearing housing.
  • the bearing housing Slidable in the axial direction against spring pressure and immovably guided in the radial direction, the bearing housing having at its ends axially outwardly widening contact surfaces for complementary conical surfaces on the outer circumference of the bearing rings and the bearing rings being axially acting against the contact surfaces of the bearing housing by spring means are tensioned and are so elastically deformable under the axial preload that they substantially prevent radial play between the tie rod and the bearing housing.
  • Such storage is known for example from DT-OS 17 18 380.
  • the spring means are formed by rubber buffers which rest against the essentially axially normal outer end faces of the bearing rings via pressure plates and tension these against the contact surfaces of the bearing housing.
  • the invention has for its object to protect a tie rod bearing of the type mentioned above against the ingress of moisture and to prevent rusting on the tie rod.
  • the bearing rings made of plastic are each provided with a sealing ring on their end surface which is essentially axially normal and which is intended to bear against a pressure surface of the spring means, said sealing ring being designed as an edge bead rising above the end surface.
  • bearing rings are made of plastic and the sealing ring is designed as an edge bead rising above the end face, it is possible to produce bearing rings and sealing ring in one piece, whereby a sealing surface, namely the sealing surface between the sealing ring and the end face of the bearing ring, is eliminated.
  • the diameter of the pull rod is slightly smaller than the inner diameter of the bearing housing in order to prevent friction between the pull rod and the bearing housing. Since the axial extension of the bearing rings in the known embodiment is approximately equal to the axial extension of the conical contact surfaces on the bearing housing, there is an annular cavity in the bearing housing. Since it is not possible to hermetically seal this cavity, condensation water can form in it under certain conditions, which leads to rusting of the bearing housing and tie rod. To avoid this, the bearing rings according to the invention are connected on their side facing the inside of the bearing housing with a cylindrical sleeve, the outside diameter of which is substantially equal to the inside diameter of the bearing housing and the inside diameter of which is equal to the inside diameter of the bearing rings.
  • These sleeves essentially fill the annular cavity between the tie rod and the inner wall of the bearing housing, so that practically no condensed water can form here and, moreover, corrosion that is possible due to a certain residual moisture is avoided by the sleeves being on both the peripheral surface of the tie rod and rub on the inside wall of the bearing housing and prevent rust from forming on these surfaces.
  • the axial length of the sleeves is preferably somewhat less than half the axial length of the cylindrical bearing housing section lying between the conical contact surfaces.
  • the bearing rings with the respective cylindrical sleeve are preferably designed as a one-piece bearing bush, which can be produced simply and inexpensively and can be exchanged easily and quickly as a wearing part.
  • the inside diameter of the bearing rings or the bearing bushes is about 0.5 mm larger than the diameter of the tie rod at the bearing points. This allows the bearing rings to be easily pushed onto the pull rod.
  • the bearing rings are then pressed by the axial pressure of the spring means against the conical contact surfaces of the bearing housing in such a way that they are radially compressed in the area of these contact surfaces are, whereby the diameter difference between the inner diameter of the bearing rings and the outer diameter of the tie rod is reduced to about 0.1 to 0.2 mm.
  • Good maintenance of the tie rod surface within the bearing housing can also be achieved in that at least one flat groove running obliquely to the axis is formed on the inner circumferential surface of the bearing bush formed by the bearing ring and sleeve sliding surfaces of the tie rod and bearing bush.
  • a coupling head 10 which is attached to a tie rod 12.
  • the pull rod 12 passes through a bearing bore 14 of a bearing housing 16 and is rotatably and axially displaceably mounted therein via bearing bushes 18.
  • the bearing housing 16 is fastened via a flange 20 provided on its outer circumference to a fastening cross member 22 connected to a towing vehicle, not shown.
  • the bearing bore 14 has a cylindrical central portion, the inner diameter of which is greater than the outer diameter of the tie rod 12 in its part passing through the bearing housing 16, so that an annular space is formed between the peripheral wall of the bearing bore 14 and the peripheral surface of the tie rod 12.
  • the inner circumferential wall of the bearing bore 14 goes into an axially conically widening contact.
  • surfaces 24, which are intended for bearing on the bearing bushes 18 complementarily shaped conical surfaces 26.
  • Both bearing bushes 18 are of identical design.
  • Each bearing bush 18 consists of a ring part 28, on the outer circumference of which the conical surface 26 intended for bearing against the respective contact surface 24 of the bearing housing 16 is formed, and a cylindrical sleeve part 30.
  • the ring part 28 and the sleeve part 30 are made in one piece from one another from an elastically deformable material , preferably a plastic, such as polytetrafluoroethylene.
  • the outer diameter of the sleeve part 30 is selected so that the bearing bushes 18 can be pressed into the bearing bore 14 with a clamp fit.
  • the inner diameter of the bearing bush is approximately 0.5 mm larger than the outer diameter of the pull rod 12, so that the pull rod 12 can easily be pushed through the bearing bushes 18.
  • the axial length of the sleeve part 30 is slightly less than half the axial length of the cylindrical portion of the bearing bore 14, so that a distance of a few millimeters remains between the mutually facing end faces of the bearing bushes 18 inserted into the bearing housing 16, the function of which will be explained further below .
  • the conical surface 26 on the ring part 28 merges at its edge remote from the sleeve part 30 into a narrow cylindrical surface 32 in the axial direction, which in turn merges with the formation of an edge bead 34 into the essentially axially normal end face 36 of the ring part 28.
  • the edge bead 34 projects in the axial direction by a few tenths of a millimeter, preferably about 0.2 mm, over the annular end face 36.
  • a plurality of axially extending recesses or bores 38 are provided in the end face 36 at regular angular intervals (FIG. 3), which serve to save material and increase the deformability of the ring part 28.
  • grooves 42 which run obliquely to the axis, are arranged in a gun barrel, similar to the swirl trains, which are used to supply and distribute lubricants when the bearing bushes 18 are seated on the pull rod 12.
  • the bearing bushes 18 When mounting the bearing, the bearing bushes 18 are pressed with their cylindrical sleeve parts 30 into the bearing bore 14 of the bearing housing 16 until the conical surfaces 26 bear against the ring parts 28 on the contact surfaces 24 of the bearing housing 16. Then the pull rod 12 is pushed through the bores 40 of the two bearing bushes 18. The bearing rings are then clamped by a clamping nut 48, which can be screwed onto the free end 46 of the pull rod 12, which end is provided with a thread 44, via two axially acting spring devices 50 and 52.
  • the spring device 50 which is close to the coupling head 10, comprises a rubber buffer 54 which, on the one hand, bears against an axially normal flange 56 formed in one piece with the coupling head 10 and, on the other hand, against the bottom 58 of a protective cap 60 which overlaps the rubber buffer 54 and is essentially axially normal.
  • the other side of the bottom 58 of the protective cap 60 bears against the front end of the bearing bush 18 on the left in FIG. 1.
  • the suspension device 52 on the other side of the bearing housing 16 also comprises a rubber buffer 62 which is attached to the protective cap 64 via an identical protective cap 64 to the protective cap 60 axially outer end of the right in Fig. 1 bearing bush 18 abuts.
  • a pressure plate 66 is also mounted on the pull rod 12, the outer diameter of which corresponds approximately to the outer diameter of the rubber buffer 62.
  • the pressure plate 66 is seated on a conical section 68 of the tie rod 12 which widens towards the bearing housing 16, the through-hole 70 in the pressure plate 66 also being provided with a complementary conical surface at least in part, its axial extent, so that the pressure plate 66 is screwed on the nut 48 on the threaded end 46 of the pull rod 12 can only be pushed onto the pull rod 12 until the conical surface of the bore 70 in the pressure plate 66 bears against the conical surface 68 of the pull rod 12. This prevents the rubber buffers 54 and 62 from being squeezed together too much when the clamping nut 48 is tightened.
  • the length of the tie rod section between the flange 56 and the conical surface 68 and the axial dimensions of the parts mounted on the tie rod 12 are chosen so that when the clamping nut 48 is tightened, the bearing bushes 18 are pressed firmly into the bearing bore 14 of the bearing housing 16. Due to the conically tapering towards the inside of the bearing housing 16 towards the contact surfaces 24, at least the ring parts 28 of the bearing bushes 18 are also pressed together in the radial direction, so that the originally existing diameter difference of 0.5 mm between the inside diameter of the bearing bushes 18 and the outside diameter of the Drawbar 12 reduced to about 0.1 to 0.2 mm. As a result, the pull rod 12 can still slide axially in the bearing bushes 18, but has no possibility of radial movement in the bearing housing 16.
  • the bearing bushes 18 are always so in the event of gradual wear Bearing bore 14 of the bearing housing 16 pressed in that, on the one hand, the conical surfaces 26 abut the contact surfaces 24 and, on the other hand, play between the tie rod 12 and the bearing housing 16 is avoided.
  • the above-mentioned small space between the facing ends of the bearing bushes 18 must be provided in the bearing bore 14.
  • edge beads 34 When the protective caps 60 and 64 are pressed against the front ends of the bearing bushes 18, the edge beads 34 are first deformed until the protective caps lie flat against the end faces 36. As a result, the edge bead 34 acts as a sealing ring, which prevents water from penetrating into the bearing housing when the bearing ring is momentarily relieved when the pull rod 12 is axially displaced between this bearing ring and the protective cap in question.
  • the tie rod 12 is enclosed practically over its entire length within the bearing housing 16 by the bearing bushes 18, the friction of the bearing bushes on the pull rod 12 constantly polishes it, so that due to condensation in the remaining space between the bearing bushes 18 residual moisture cannot lead to rust formation on the pull rod 12.
  • a lubricant can be introduced through the grooves 42 on the inner peripheral surface of the bearing bushes 18.
  • the tie rod mounting according to the invention is practically maintenance-free and ensures reliable play-free guidance of the tie rod 12 until the bearing bushes 18 are worn out so that readjustment is no longer possible.
  • the clamping nut 48 is secured by a split pin 72.
  • the clamping nut itself can then still be covered by a protective cap 74, which engages with a bead-like edge 76 in the manner of a snap closure over an annular collar 78 on the protective cap 64.
  • the sleeve parts 30 not only protect the surface of the tie rod 12 against corrosion, but also cause an additional radial bearing for the tie rod 12 in the bearing housing 16. This effect is particularly evident when the conical ring parts 28 are subjected to very strong radial forces. In this case, the sleeve parts 18 limit the load on the conical ring parts 28.
  • the rubber buffers 54 and 62 lie so close to the surface of the tie rod that water cannot penetrate into the bearing housing 16 even at these points.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)

Claims (7)

1. Palier, pour la barre d'attelage (12), portant la tête d'accouplement (10), d'un dispositif d'attelage de remorque destiné notamment à être monté sur des camions, comportant un corps de palier (16), qui entoure la barre d'attelage (12) à une distance radiale, qui est immobilisé sur le camion et dans lequel la barre d'attelage (12) est guidée en rotation sur son axe par l'intermédiaire de bagues de palier (28) appliquées contre la face interne du corps (16), est déplaçable dans le sens axial contre une pression de ressort, et est immobile dans le sens radial, le corps de palier (16) présentant à ses extrémités des surfaces (24) qui s'élargissent coniquement vers l'extérieur dans le sens axial, pour l'appui de surfaces coniques (26) de configuration complémentaire de la face externe périphérique des bagues de palier (28) et ces bagues étant pressées contre les surfaces d'appui (24) du corps de palier (16) par des moyens à ressort (50, 52) agissant dans le sens axial et étant, sous l'effet de cette sollicitation axiale, déformables élastiquement de telle façon qu'elles empêchent, pour l'essentiel, un jeu radial entre la barre d'attelage (12) et le corps de palier (16), caractérisé en ce que chaque bague de palier (28) est munie, sur sa face en bout (36), sensiblement perpendiculaire à son axe et destinée à venir en appui contre une face de poussée (58, 64) des moyens à ressort (50, 52), d'un joint d'étanchéité annulaire (34) conformé en bourrelet périphérique (34) saillant sur la dite face en bout (36).
2. Palier selon la revendication 1, caractérisé en en ce que les bagues de palier (28) sont, par leur côté tourné vers t'intérieur du- corps de palier (16), assemblées avec un manchon cylindrique (30), dont le diamètre extérieur est sensiblement égal au diamètre intérieur du corps de palier (16) et dont le diamètre intérieur est égal à celui des bagues de palier (28).
3. Palier selon la revendication 2, caractérisé en ce que la longueur axiale des manchons (30) est légèrement inférieure à la moitié de la longuer axiale de la partie cylindrique du corps de palier, comprise entre les surfaces d'appui coniques (24).
4. Palier selon la revendication 2 ou la revendication 3, caractérisé en ce que chaque bague de palier (28) forme avec le manchon cylindrique associé (30) un coussinet (18) d'une seule pièce.
5. Palier selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le diamètre intérieur des bagues de palier (28) est supérieur d'environ 0,5 mm au diamètre de la barre d'attelage (12).
6. Palier selon l'une quelconque des revendications 2 à 5, caractérisé en ce qu'au moins un sillon plat (42), qui s'étend obliquement par rapport à l'axe, est formé sur la face de révolution interne de chaque coussinet (18) formé d'une bague de palier (28) et d'un manchon (30).
7. Palier selon l'une quelconque des revendications 1 à 6, caractérisé en ce que plusieurs trous (38), qui s'étendent axialement, sont prévus dans la face en bout (36) des bagues de palier coniques (28).
EP19780100075 1977-07-19 1978-06-01 Palier de fixation pour barre d'attelage Expired EP0000325B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2732610 1977-07-19
DE19772732610 DE2732610C3 (de) 1977-07-19 1977-07-19 Lagerung für eine Zugstange einer Anhängerkupplung

Publications (2)

Publication Number Publication Date
EP0000325A1 EP0000325A1 (fr) 1979-01-24
EP0000325B1 true EP0000325B1 (fr) 1981-08-05

Family

ID=6014300

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19780100075 Expired EP0000325B1 (fr) 1977-07-19 1978-06-01 Palier de fixation pour barre d'attelage

Country Status (2)

Country Link
EP (1) EP0000325B1 (fr)
DE (1) DE2732610C3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3530565C2 (de) * 1985-08-27 2002-03-07 Rockinger Spezial Fab Joh Längskraftabstützung des Kupplungskörpers einer Anhängerkupplung
GB8706647D0 (en) * 1987-03-20 1987-04-23 Fraser S Towing bracket
EP0433471B1 (fr) * 1989-12-18 1993-11-10 ROCKINGER Spezialfabrik für Anhängerkupplungen GmbH & Co. Dispositif d'attelage avec support d'attelage ayant un disque de butée nervuré
DE4015473A1 (de) * 1990-05-14 1991-11-21 Rockinger Spezial Fab Joh Anhaengerkupplung, stichwort: verliersicherung mit wackelabstand
EP1527910B1 (fr) * 2003-10-29 2007-03-21 Schnabl, Peter Attelage de remorque

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE849044C (de) * 1942-02-27 1952-09-11 Ehrenreich & Cie A Gestaenge mit Abfederung
NL197069A (fr) * 1952-02-08
US3169783A (en) * 1962-07-30 1965-02-16 Western Unit Corp Drawbar hitch assembly
DE1241278B (de) * 1962-08-16 1967-05-24 Ade Werk G M B H Federnd gelagerte Anhaengerkupplung
DE2206617A1 (de) * 1972-02-11 1973-08-23 Rockinger Spezial Fab Joh Anhaengerkupplung

Also Published As

Publication number Publication date
EP0000325A1 (fr) 1979-01-24
DE2732610C3 (de) 1980-12-04
DE2732610A1 (de) 1979-02-01
DE2732610B2 (de) 1980-04-10

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