EP0000325A1 - Tow bar bearing for a trailer coupling - Google Patents

Tow bar bearing for a trailer coupling Download PDF

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Publication number
EP0000325A1
EP0000325A1 EP78100075A EP78100075A EP0000325A1 EP 0000325 A1 EP0000325 A1 EP 0000325A1 EP 78100075 A EP78100075 A EP 78100075A EP 78100075 A EP78100075 A EP 78100075A EP 0000325 A1 EP0000325 A1 EP 0000325A1
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EP
European Patent Office
Prior art keywords
bearing
rings
bearing rings
bearing housing
tie rod
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.)
Granted
Application number
EP78100075A
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German (de)
French (fr)
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EP0000325B1 (en
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
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Rockinger Spezialfabrik fuer Anhangerkupplungen GmbH and Co
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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/en
Application granted granted Critical
Publication of EP0000325B1 publication Critical patent/EP0000325B1/en
Expired legal-status Critical Current

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    • 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 has at its ends axially outwardly widening contact surfaces for complementarily designed conical surfaces on the outer circumference of the bearing rings, and wherein the bearing rings are tensioned by axially acting spring means against the contact surfaces of the bearing housing and are so elastically deformable under the axial preload that they essentially 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 on pressure plates on the essentially axially normal outer end faces of the bearing rings 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 above type against penetrating moisture and to prevent rusting on the tie rod.
  • the bearing rings are provided with a sealing ring on their end surface which is essentially axially normal and intended for bearing against a pressure surface of the spring means.
  • the arrangement of sealing rings between the pressure plates and the bearing rings ensures that even if the surfaces of the pressure plates and the bearing rings which are intended to be in contact with one another are not absolutely flat, no water can penetrate between them into the interior of the bearing housing.
  • the sealing ring can be connected to the bearing ring in any way.
  • the bearing rings are made of plastic, the sealing ring being designed as an edge bead rising above the end face. This makes it possible to manufacture the bearing rings and the sealing ring from one piece, as a result of which 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 can cause rusting of the bearing housing and Drawbar leads.
  • 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 sleeves, the N achstell Koch not hinder the conical bearing rings
  • the axial length of the sleeves is preferably somewhat less than half the axial length of the lying between the conical bearing faces bearing housing cylindrical portion.
  • 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 replaced easily and quickly as a wearing part.
  • the inside diameter of the bearing rings or the bearing bushes is approximately 0.5 mm larger than the diameter of the pull rod at the bearing points. This allows the bearing rings to be easily pushed onto the pull rod.
  • the bearing rings are then in the installed state by the axial pressure of the spring means so pressed against the conical contact surfaces of the bearing housing that they are radially compressed in the area of these contact surfaces, 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 peripheral surface of the bearing bush formed by the bearing ring and sleeve.
  • This groove designed according to the type of a twist pull, allows lubricant to be introduced between the sliding surfaces of the pull 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 merges into axially outwardly widening contact surfaces 24 which are intended for contact with cone surfaces 26 which are complementarily shaped on the bearing bushes 18.
  • 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 outside 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 about 0.5 mm larger than the outer diameter of the pull rod 12, so that the pull rod 12 can be easily 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 facing end faces of the bearing bushes 18 inserted into the bearing housing 16, the function of which will be explained in the following .
  • the cone 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 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 which is 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 bears on the axially outer end face of the bearing bush 18 on the right in FIG. 1 via a protective cap 64 identical to the protective cap 60.
  • 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 over at least part of its axial extent, so that the pressure plate 66 is screwed on Nut 48 on the threaded end 46 of the tie rod 12 only so far can be pushed onto the tension 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 selected 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 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 a gradual wear and tear 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 mutually facing ends of the La gerbüchsen 18 can 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 friction of the bearing bushes on the pull rod 12 means that the latter is constantly polished, so that condensation water forms 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 cause a load limitation for 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.

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

Abstract

1. Mounting for a tongue (12), carrying a coupling head (10), of a trailer coupling to be attached particularly to heavy-goods vehicles, with a bearing box (16), which surrounds the tongue (12) with a radial spacing and which is located immovably on the heavy-goods vehicle, and in which the tongue (12) is guided, via bearing rings (28) lying in contact with the inside of the bearing box (16), rotatably about its axis, displaceably in an axial direction against spring pressure and immovably in a radial direction, the bearing box (16) having at its ends bearing faces (24), which extend conically outwards axially, for conical faces (26) made complementary to these on the outer periphery of the bearing rings (28), the bearing rings (28) being tensioned, by axially acting spring means (50, 52), against the bearing faces (24) of the bearing box (16) and being elastically deformable under the axial prestress, in such a way that these bearing rings substantially prevent a radial play between the tongue (12) and bearing box (16), characterised in that the bearing rings (28) made of plastic are each provided, on their end face (36), substantially normal to their axis, intended for bearing on a pressure face (58, 64) of the spring means (50, 52), with a packing ring (34), which is designed as a marginal bead (34) elevated above the end face (36).

Description

Die Erfindung betrifft eine Lagerung für eine einen Kupplungskopf tragende Zugstange einer insbesondere an Lastfahrzeugen anzubringenden Anhängerkupplung mit einem die Zugstange mit einem radialen Abstand umgebenden, am Lastfahrzeug unbeweglich angeordneten Lagergehäuse, in dem die Zugstange über an der Innenseite des Lagergehäuses anliegende Lagerringe um ihre Achse drehbar, in axialer Richtung gegen Federdruck verschiebbar und in radialer Richtung unbeweglich geführt ist, wobei das Lagergehäuse an seinen Enden sich nach axial außen hin konisch erweiternde Anlageflächen für am Außenumfang der Lagerringe komplementär ausgebildete Konusflächen aufweist und wobei die Lagerringe durch axial wirkende Federmittel gegen die Anlaqeflächen des Lagergehäuses gespannt und unter der axialen Vorspannung derart elastisch deformierbar sind, daß sie ein radiales Spiel zwischen Zugstange und Lagergehäuse im wesentlichen verhindern.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. Slidable in the axial direction against spring pressure and guided immovably in the radial direction is, the bearing housing has at its ends axially outwardly widening contact surfaces for complementarily designed conical surfaces on the outer circumference of the bearing rings, and wherein the bearing rings are tensioned by axially acting spring means against the contact surfaces of the bearing housing and are so elastically deformable under the axial preload that they essentially prevent radial play between the tie rod and the bearing housing.

Eine derartige Lagerung ist beispielsweise aus der DT-OS 17 18 380 bekannt. Bei der bekannten Lagerung sind die Federmittel von Gummipuffern gebildet, die über Druckplatten an den im wesentlichen achsnormal gerichteten äußeren Stirnflächen der Lagerringe anliegen und diese gegen die Anlageflächen des Lagergehäuses spannen. Es hat sich nun gezeigt, daß bei einem längeren Gebrauch der Lagerung und dem dabei auftretenden Verschleiß der Lagerringe dann, wenn die Kupplung auf Zug oder Druck belastet und damit einer der Lagerringe entlastet wird, zwischen dem Lagerring und der Druckplatte bzw. dem Lagerring und dem Lagergehäuse unter Umständen Feuchtigkeit in das Innere des Lagergehäuses eindringen kann, die zum Rosten der Zugstange führt. Eine Reibung zwischen einer verrosteten Zugstange und den Lagerringen jedoch führt zu einem schnelleren Verschleiß der letzteren.Such storage is known for example from DT-OS 17 18 380. In the known storage, the spring means are formed by rubber buffers which rest on pressure plates on the essentially axially normal outer end faces of the bearing rings and tension these against the contact surfaces of the bearing housing. It has now been shown that with prolonged use of the bearing and the wear of the bearing rings that occurs when the clutch is subjected to tension or pressure and thus one of the bearing rings is relieved, between the bearing ring and the pressure plate or the bearing ring and the Under certain circumstances, the bearing housing can penetrate moisture into the interior of the bearing housing, which causes the drawbar to rust. Friction between a rusted tie rod and the bearing rings, however, leads to faster wear of the latter.

Der Erfindung liegt die Aufgabe zugrunde, eine Zugstangenlagerung der oben genannten Art gegen eindringende Feuchtigkeit zu schützen und eine Rostbildung an der Zugstange zu verhindern.The invention has for its object to protect a tie rod bearing of the above type against penetrating moisture and to prevent rusting on the tie rod.

Zur Lösung dieser Aufgabe wird erfindungsgemäß vorgeschlagen, daß die Lagerringe an ihrer zur Anlage an einer Druckfläche der Federmittel bestimmten, im wesentlichen achsnormalen Stirnfläche mit einem Dichtungsring versehen sind. Durch die Anordnung von Dichtringen zwischen den Druckplatten und den Lagerringen ist gewährleistet, daß auch dann, wenn die zur Anlage aneinander bestimmten Flächen der Druckplatten und der Lagerringe nicht absolut plan aneinander anliegen, dennoch kein Wasser zwischen ihnen in das Innere des Lagergehäuses eindringen kann.To achieve this object, it is proposed according to the invention that the bearing rings are provided with a sealing ring on their end surface which is essentially axially normal and intended for bearing against a pressure surface of the spring means. The arrangement of sealing rings between the pressure plates and the bearing rings ensures that even if the surfaces of the pressure plates and the bearing rings which are intended to be in contact with one another are not absolutely flat, no water can penetrate between them into the interior of the bearing housing.

Der Dichtring kann im Prinzip auf beliebige Weise mit dem Lagerring verbunden sein. Gemäß einer besonders bevorzugten Ausführungsform sind jedoch die Lagerringe aus Kunststoff hergestellt, wobei der Dichtungsring als ein sich über die Stirnfläche erhebender Randwulst ausgebildet ist. Dadurch ist es möglich, Lagerringe und Dichtungsring aus einem Stück herzustellen, wodurch eine Dichtungsfläche, nämlich die Dichtungsfläche zwischen Dichtungsring und Stirnfläche des Lagerringes wegfällt.In principle, the sealing ring can be connected to the bearing ring in any way. According to a particularly preferred embodiment, however, the bearing rings are made of plastic, the sealing ring being designed as an edge bead rising above the end face. This makes it possible to manufacture the bearing rings and the sealing ring from one piece, as a result of which a sealing surface, namely the sealing surface between the sealing ring and the end face of the bearing ring, is eliminated.

Bei der bekannten Ausführungsform ist der Durchmesser der Zugstange etwas geringer als der Innendurchmesser des Lagergehäuses, um eine Reibung zwischen Zugstange und Lagergehäuse zu verhindern. Da die axiale Ausdehnung der Lagerringe bei der bekannten Ausführung etwa gleich der axialen Ausdehnung der konischen Anlageflächen am Lagergehäuse ist, befindet sich also im Lagergehäuse ein ringförmiger Hohlraum. Da es nicht möglich ist, diesen Hohlraum hermetisch abzuschließen, kann sich in ihm unter bestimmten Bedingungen Kondenswasser bilden, das zum Verrosten von Lagergehäuse und Zugstange führt. Um das zu vermeiden, sind die erfindungsgemäßen Lagerringe an ihrer dem Inneren des Lagergehäuseszugekehrten Seite mit einer zylindrischen Hülse verbunden, deren Außendurchmesser im wesentlichen gleich dem Innendurchmesser des Lagergehäuses und deren Innendurchmesser gleich dem Innendurchmesser der Lagerringe ist. Diese Hülsen füllen also den ringförmigen Hohlraum zwischen Zugstange und Innenwand des Lagergehäuses im wesentlichen aus, so daß sich hier praktisch kein Kondenswasser bilden kann und im übrigen eine durch eine gewisse Restfeuchtigkeit mögliche Korrosion dadurch vermieden wird, daß die Hülsen sowohl auf der Umfangsfläche der Zugstange als auch an der Innenwand des Lagergehäuses reiben und damit eine Rostbildung an diesen Flächen verhindern.In the known embodiment, 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 can cause rusting of the bearing housing and Drawbar leads. In order 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.

Damit die Hülsen die Nachstellwirkung der konisch geformten Lagerringe nicht behindern, ist die axiale Länge der Hülsen vorzugsweise etwas geringer als die halbe axiale Länge des zwischen den konischen Anlageflächen liegenden zylindrischen Lagergehäuseabschnittes.Thus, the sleeves, the N achstellwirkung not hinder the conical bearing rings, the axial length of the sleeves is preferably somewhat less than half the axial length of the lying between the conical bearing faces bearing housing cylindrical portion.

Vorzugsweise sind die Lagerringe mit der jeweiligen zylindrischen Hülse als einstückige Lagerbüchse ausgebildet, die einfach und preiswert hergestellt und als Verschleißteil leicht und schnell ausgewechselt werden kann.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 replaced easily and quickly as a wearing part.

Der Innendurchmesser der Lagerringe bzw. der Lagerbüchsen ist etwa 0,5 mm größer als der Durchmesser der Zugstange an den Lagerstellen. Dadurch können die Lagerringe leicht auf die Zugstange aufgeschoben werden. Im eingebauten Zustand werden dann die Lagerringe durch den axialen Druck der Federmittel so gegen die konischen Anlageflächen des Lagergehäüses gepreßt, daß sie im Bereich dieser Anlageflächen radial zusammengepreßt werden, wodurch sich die Durchmesserdifferenz zwischen Innendurchmesser der Lagerringe und Aussendurchmesser der Zugstange auf etwa 0,1 bis 0,2 mm verringert. Damit ist nach wie vor eine axiale Bewe- gung der Zugstange gegenüber den Lagerringen bzw. Lagerbüchsen möglich, während eine radiale Bewegung der Zugstange gegenüber dem Lagergehäuse verhindert wird.The inside diameter of the bearing rings or the bearing bushes is approximately 0.5 mm larger than the diameter of the pull rod at the bearing points. This allows the bearing rings to be easily pushed onto the pull rod. The bearing rings are then in the installed state by the axial pressure of the spring means so pressed against the conical contact surfaces of the bearing housing that they are radially compressed in the area of these contact surfaces, 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. Thus, according as possible before an axial movement of the drawbar relative to the bearing rings or bearing bushes, while radial movement of the pull rod relative to the bearing housing is prevented.

Eine gute Pflege der Zugstangenoberfläche innerhalb des Lagergehäuses läßt sich noch dadurch erreichen, daß an der Innenumfangsfläche der von Lagerring und Hülse gebildeten Lagerbüchse mindestens eine schräg zur Achse verlaufende flache Rinne ausgebildet ist. Diese nach Art.eines Drallzuges ausgebildete Rinne ermöglicht das Einführen von Schmiermittel zwischen die aufeinander gleitenden Flächen von Zugstange und Lagerbüchse.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 peripheral surface of the bearing bush formed by the bearing ring and sleeve. This groove, designed according to the type of a twist pull, allows lubricant to be introduced between the sliding surfaces of the pull rod and bearing bush.

Die beiliegenden Figuren erläutern die Erfindung anhand eines Ausführungsbeispieles. Es stellen dar:

  • Fig. 1 eine teilweise schematische Seitenansicht mit einem axialen Schnitt durch die erfindungsgemäße Zugstangenlagerung,
  • Fig. 2 eine teilweise geschnittene Seitenansicht der erfindungsgemäßen Lagerbüchse in vergrößertem Maßstab, und
  • Fig. 3 eine Endansicht der erfindungsgemäßen Lagerbüchse in Richtung des Pfeiles-A in Fig. 2.
The accompanying figures explain the invention using an exemplary embodiment. They represent:
  • 1 is a partially schematic side view with an axial section through the tie rod bearing according to the invention,
  • Fig. 2 is a partially sectioned side view of the bearing bush according to the invention on an enlarged scale, and
  • 3 shows an end view of the bearing bush according to the invention in the direction of arrow-A in FIG. 2.

In Fig. 1 erkennt man einen Kupplungskopf 10, der an einer Zugstange 12 befestigt ist. Die Zugstange 12 durchsetzt eine Lagerbohrung 14 eines Lagergehäuses 16 und ist in diesem über Lagerbüchsen 18 drehbar und axial verschiebbar gelagert. Das Lagergehäuse 16 ist über einen an seinem Außenumfang vorgesehenen Flansch 20 an einer mit einem nicht dargestellten Zugfahrzeug verbundenen Befestigungstraverse 22 befestigt.In Fig. 1 you can see 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.

Die Lagerbohrung 14 weist einen zylindrischen Mittelabschnitt auf, dessen Innendurchmesser größer ist als der Außendurchmesser der Zugstange 12 in ihrem das Lagergehäuse 16 durchsetzenden Teil, so daß ein Ringraum zwischen der Umfangswand der Lagerbohrung 14 und der Umfangsfläche der Zugstange 12 gebildet wird. An den axialen Enden des Lagergehäuses 16-geht die Innenumfangswand der Lagerbohrung 14 in sich nach axial außen konisch erweiternde Anlageflächen 24 über, die zur Anlage von an den Lagerbüchsen 18 komplementär ausgeformten Konusflächen 26 bestimmt sind.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. At the axial ends of the bearing housing 16 - the inner circumferential wall of the bearing bore 14 merges into axially outwardly widening contact surfaces 24 which are intended for contact with cone surfaces 26 which are complementarily shaped on the bearing bushes 18.

Beide Lagerbüchsen 18 sind identisch ausgebildet. Jede Lagerbüchse 18 besteht aus einem Ringteil 28, an dessen Außenumfang die zur Anlage an der jeweiligen Anlagefläche 24 des Lagergehäuses 16 bestimmte Konusfläche 26 ausgebildet ist, und einem zylindrischen Hülsenteil 30. Der Ringteil 28 und der Hülsenteil 30 sind einstückig miteinander aus einem elastisch deformierbaren Material, vorzugsweise einem Kunststoff, wie etwa Polytetrafluoräthylen, hergestellt. Der Außendurchmesser des Hülsenteils 30 ist so gewählt, daß die Lagerbüchsen 18 mit Klemmsitz in die Lagerbohrung 14 eingepreßt werden können. Dagegen ist der Innendurchmesser der Lagerbüchse um etwa 0,5 mm größer als der Außendurchmesser der Zugstange 12, so daß die Zugstange 12 leicht durch die Lagerbüchsen 18 geschoben werden kann. Die axiale Länge des Hülsenteiles 30 ist etwas geringer als die halbe axiale Länge des zylindrischen Abschnittes der Lagerbohrung 14, so daß zwischen den einander zugekehrten Endflächen der in das Lagergehäuse 16 eingesetzten Lagerbüchsen 18 ein Abstand von einigen Millimetern verbleibt, dessen Funktion im weiteren noch erläutert wird.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 outside 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. In contrast, the inner diameter of the bearing bush is about 0.5 mm larger than the outer diameter of the pull rod 12, so that the pull rod 12 can be easily 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 facing end faces of the bearing bushes 18 inserted into the bearing housing 16, the function of which will be explained in the following .

Die Konusfläche 26 an dem Ringteil 28 geht an ihrem dem Hülsenteil 30 fernen Rand in eine in axialer Richtung schmale Zylinderfläche 32 über, die ihrerseits unter Bildung eines Randwulstes 34 in die im'wesentlichen achsnormale Stirnfläche 36 des Ringteiles 28 übergeht. Der Randwulst 34 steht dabei in axialer Richtung um einige Zehntel Millimeter, vorzugsweise etwa 0,2 mm, über die ringförmige Stirnfläche 36 vor. In der Stirnfläche 36 sind in gleichmäßigen Winkelabständen mehrere axial verlaufende Aussparungen oder Bohrungen 38 vorgesehen (Fig.-3), die der Materialersparnis und der Erhöhung der Deformierbarkeit des Ringteiles 28 dienen.The cone 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.

An der Umfangsfläche der Innenbohrung 40 der Lagerbüchse 18 sind schräg zur Achse verlaufende Rinnen 42 ähnlich den Drallzügen in einem Geschützrohr angeordnet, die zum Zuführen und Verteilen von Schmiermitteln dienen, wenn die Lagerbüchsen 18 auf der Zugstange 12 sitzen.On the circumferential surface of the inner bore 40 of the bearing bush 18, 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.

Bei der Montage der Lagerung werden die Lagerbüchsen 18 mit ihren zylindrischen Hülsenteilen 30 in die Lagerbohrung 14 des Lagergehäuses 16 eingepreßt, bis die Konusflächen 26 an den Ringteilen 28 an den Anlageflächen 24 des Lagergehäueses 16 anliegen. Dann wird die Zugstange 12 durch die Bohrungen 40 der beiden Lagerbüchsen 18 geschoben. Die Lagerringe werden dann durch eine auf das mit einem Gewinde 44 versehene freie Ende 46 der Zugstange 12 aufschraubbare Spannmutter 48 über zwei axial wirkende Federeinrichtungen 50 und 52 eingespannt. Die dem Kupplungskopf 10 nahe Federeinrichtung 50 umfaßt einen Gummipuffer 54, der einerseits an einem mit dem Kupplungskopf 10 einstückig ausgebildeten achsnormalen Flansch 56 und andererseits an dem im wesentlichen achsnormal gerichteten Boden 58 einer den Gummipuffer 54 übergreifenden Schutzkappe 60 anliegt. Die andere Seite des Bodens 58 der Schutzkappe 60 liegt an dem Stirnende der in Fig. 1 linken Lagerbüchse 18 an. Die Federungseinrichtung 52 auf der anderen Seite des Lagergehäuses 16 umfaßt ebenfalls einen Gummipuffer 62, der über eine mit der Schutzkappe 60 identische Schutzkappe 64 an dem axial äußeren Stirnende der in Fig. 1 rechten Lagerbüchse 18 anliegt. Zwischen dem Gummipuffer 62 und der Mutter 48 ist auf der Zugstange 12 noch eine Druckplatte 66 gelagert, deren Außendurchmesser etwa dem Außendurchmesser des Gummipuffers 62 entspricht. Die Druckplatte 66 sitzt auf einem sich zum Lagergehäuse 16 hin erweiternden konischen Abschnitt 68 der Zugstange 12, wobei die Durchtrittsbohrung 70 in der Druckplatte 66 ebenfalls mindestens auf einem Teil ihrer axialen Ausdehnung mit einer komplementären Konusfläche versehen ist, so daß die Druckplatte 66 beim Aufschrauben der Mutter 48 auf das Gewindeende 46 der Zugstange 12 nur so weit auf die Zugstanae 12 aufgeschoben werden kann, bis die Konusfläche der Bohrung 70 in der Druckplatte 66 an der Konusfläche 68 der Zugstange 12 anliegt. Damit wird vermieden, daß die Gummipuffer 54 und 62 beim Anziehen der Spannmutter 48 zu stark zusammengequetscht werden.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 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 which is 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 bears on the axially outer end face of the bearing bush 18 on the right in FIG. 1 via a protective cap 64 identical to the protective cap 60. Between the rubber buffer 62 and the nut 48, 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 over at least part of its axial extent, so that the pressure plate 66 is screwed on Nut 48 on the threaded end 46 of the tie rod 12 only so far can be pushed onto the tension 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.

Die Länge des Zugstangenabschnittes zwischen dem Flansch 56 und der Konusfläche 68 sowie die axialen Abmessungen der auf der Zugstange 12 gelagerten Teile sind so gewählt, daß beim Anziehen der Spannmutter 48 die Lagerbüchsen 18 fest in die Lagerbohrung 14 des Lagergehäuses 16 eingepreßt werden. Durch die sich konisch zum Inneren des Lagergehäuses 16 hin verjüngenden Anlageflächen 24 werden dabei mindestens die Rinqtelle 28 der Lagerbüchsen 18 auch in radialer Richtung zusammengepreßt, so daß sich die ursprünglich vorhandene Durchmesserdifferenz von 0,5 mm zwischen dem Innendurchmesser der Lagerbüchsen 18 und dem Aussendurchmesser der Zugstange 12 auf etwa 0,1 bis 0,2 mm verringert. Dadurch kann die Zugstange 12 zwar noch in axialer Richtung in den Lagerbüchsen 18 gleiten, hat jedoch keine Möglichkeit zu einer radialen Bewegung in dem Lagergehäuse 16. Durch die Federwirkung der Gummipuffer 54 und 62 werden die Lagerbüchsen 18 bei einem allmählichen Verschleiß derselben stets so in die Lagerbohrung 14 des Lagergehäuses 16 hineingepreßt, daß einerseits die Konusflächen 26 an den Anlageflächen 24 anliegen und andererseits ein Spiel zwischen der Zugstange 12 und dem Lagergehäuse 16 vermieden wird. Um diese Nachstellung der Lagerbüchsen 18 zu ermöglichen, muß der oben erwähnte kleine Zwischenraum zwischen den einander zugekehrten Enden der Lagerbüchsen 18 in der Lagerbohrung 14 vorgesehen sein.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 selected 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 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. Due to the spring action of the rubber buffers 54 and 62, the bearing bushes 18 are always so in the event of a gradual wear and tear 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. In order to enable this adjustment of the bearing bushes 18, the above-mentioned small space between the mutually facing ends of the La gerbüchsen 18 can be provided in the bearing bore 14.

Beim Anpressen der Schutzkappen 60 bzw. 64 gegen die Stirnenden der Lagerbüchsen 18 werden zunächst die Randwülste 34 deformiert, bis die Schutzkappen flach an den Stirnflächen 36 anliegen. Dadurch wirkt der Randwulst 34 als Dichtungsring, der verhindert, daß bei einer momentanen Entlastung eines Lagerringes bei einer axialen Verschiebung der Zugstange 12 zwischen diesem Lagerring und der betreffenden Schutzkappe Wasser in das Lagergehäuse eindringen kann. Dadurch daß die Zugstange 12 praktisch auf ihrer ganzen Länge innerhalb des Lagergehäuses 16 von den Lagerbüchsen 18 eingeschlossen ist, wird durch die Reibung der Lagerbüchsen auf der Zugstange 12 diese ständig poliert, so daß auch eine aufgrund von Kondenswasserbildung in dem verbleibenden Freiraum zwischen den Lagerbüchsen 18 auftretende Restfeuchtigkeit nicht zur Rostbildung an der Zugstange 12 führen kann.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. Characterized in that the tie rod 12 is virtually enclosed 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 means that the latter is constantly polished, so that condensation water forms in the remaining space between the bearing bushes 18 residual moisture cannot lead to rust formation on the pull rod 12.

Um die Oberfläche der Zugstange 12 gegen Korrosion zu schützen und die Reibung zwischen den Lagerbüchsen 18 und der Zugstange 12 zu verringern, kann durch die Rinnen 42 an der innenumfangsfläche der Lagerbüchsen 18 ein Schmiermittel eingeführt werden.In order to protect the surface of the pull rod 12 against corrosion and to reduce the friction between the bearing bushes 18 and the pull rod 12, a lubricant can be introduced through the grooves 42 on the inner peripheral surface of the bearing bushes 18.

Wie die vorstehende Beschreibung zeigt, ist die erfindungsgemäße Zugstangenlagerung praktisch wartungsfrei und gewährleistet eine zuverlässige spielfreie Führung der Zugstange 12, bis die Lagerbüchsen 18 so verschlissen sind, daß eine Nachstellung nicht mehr möglich ist.As the above description shows, 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.

Nach dem Anziehen wird die Spannmutter 48 jeweils durch einen Splint 72 gesichert. Die Spannmutter selber kann dann noch durch eine Schutzkappe 74 abgedeckt werden, die mit einem wulstartigen Rand 76 nach Art eines Schnappverschlusses über einen ringförmigen Kragen 78 an der Schutzkappe 64 greift.After tightening, 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.

Es muß noch betont werden, daß die Hülsenteile 30 nicht nur die Oberfläche der Zugstange 12 gegen Korrosion schützen, sondern auch eine zusätzliche Radiallagerung für die Zugstange 12 in dem Lagergehäuse 16 bewirken. Diese Wirkung zeigt sich insbesondere dann, wenn die konischen Ringteile 28 auf sehr starke Radialkräfte belastet werden. In diesem Fall bewirken die Hülsenteile 18 eine Belastungsbegrenzung für die konischen Ringteile 28.It must be emphasized that 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 cause a load limitation for the conical ring parts 28.

Es ist ferner noch zu ergänzen, daß die Gummipuffer 54 und 62 so dicht an der Zugstangenoberfläche anliegen,daß auch an diesen Stellen kein Wasser in das Lagergehäuse 16 eindringen kann.It must also be added that 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.

Claims (8)

1. Lagerung für eine einen Kupplungskopf tragende Zugstange einer insbesondere an Lastfahrzeugen anzubringenden Anhängerkupplung mit einem die Zugstange mit einem radialen Abstand umgebenden, am Lastfahrzeug unbeweglich angeordneten Lagergehäuse, in dem die Zugstange über an der Innenseite des Lagergehäuses anliegende Lagerringe um ihre Achse drehbar, in axialer Richtung gegen Federdruck verschiebbar und in radialer Richtung unbewegliche geführt ist, wobei das Lagergehäuse an seinen Enden sich nach axial außen hin konisch erweiternde Anlageflächen für am Außenumfang der Lagerringe komplementär ausgebildete Konusflächen aufweist und wobei die Lagerringe durch axial wirkende Federmittel gegen die Anlageflächen des Lagergehäuses gespannt und unter der axialen Vorspannung derart elastisch defdrmierbar sind, daß sie ein radiales Spiel zwischen Zugstange und Lagergehäuse im wesentlichen verhindern, dadurch gekennzeichnet, daß die Lagerringe (28) jeweils an ihrer zur Anlage an einer Druckfläche (58, 64) der Federmittel (50, 52) bestimmten im wesentlichen achsnormalen Stirnfläche (36) mit einem Dichtungsring (34) versehen sind.1.Bearing 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 with a radial distance and immovably arranged on the truck, in which the tie rod can be rotated about its axis via bearing rings lying on the inside of the bearing housing, in an axial direction Is displaceable in the direction against spring pressure and is immovable in the radial direction, the bearing housing at its ends having conically widening contact surfaces for conically expanding conical surfaces on the outer circumference of the bearing rings, and the bearing rings being tensioned by axially acting spring means against the contact surfaces of the bearing housing and can be elastically deformed under the axial pretension in such a way that they essentially prevent radial play between the tie rod and the bearing housing, characterized in that the bearing rings (28) each rest on their to bear against a pressure surface he (58, 64) of the spring means (50, 52) determine th substantially axially normal end face (36) are provided with a sealing ring (34). 2. Lagerung nach Anspruch 1, dadurch gekennzeichnet , daß die Lagerringe (28) aus Kunststoff hergestellt sind und der Dichtungsring als ein sich über die Stirnfläche (36) erhebender Randwulst (34) ausgebildet ist.2. Bearing according to claim 1, characterized in that the bearing rings (28) are made of plastic and the sealing ring is formed as an over the end face (36) rising edge bead (34). 3. Lagerung nach Anspruch 1 oder 2, dadurch gekennzeichnet ,daß die Lagerringe (28) an ihrer dem Inneren des Lagergehäuses (16) zugekehrten Seite mit einer zylindrischen Hülse (30) verbunden sind, deren Außendurchmesser im wesentlichen gleich dem Innendurchmesser des Lagergehäuses (16) und deren Innendurchmesser gleich dem Innendurchmesser der Lagerringe (28) ist.3. Storage according to claim 1 or 2, characterized in that the bearing rings (28) on their inside of the bearing housing (16) facing side are connected to a cylindrical sleeve (30) whose outer diameter is substantially equal to the inner diameter of the bearing housing (16 ) and whose inside diameter is equal to the inside diameter of the bearing rings (28). 4. Lagerung nach Anspruch 3, dadurch gekennzeichnet , daß die axiale Länge der Hülsen (30) etwas geringer ist als die halbe axiale Länge des zwischen den konischen Anlageflächen (24)) liegenden zylindrischen Lagergehäuseabschnittes.4. Storage according to claim 3, characterized in that the axial length of the sleeves (30) is slightly less than half the axial length of the cylindrical bearing housing section lying between the conical contact surfaces (24). 5 Lagerung nach Anspruch 3 oder 4, dadurch gekennzeichnet , daß die Lagerringe (28) mit der jeweiligen zylindrischen Hülse (30) als einstückige Lagerbüchse (18) ausgebildet sind.5 Bearing according to claim 3 or 4, characterized in that the bearing rings (28) with the respective cylindrical sleeve (30) are designed as a one-piece bearing bush (18). 6. Lagerung nach einem der Ansprüche 3 bis 5 dadurch gekennzeichnet , daß der Innendurchmesser der Lagerringe (28) etwa 0,5 mm größer ist als der Durchmesser der zugstange (12).6. Storage according to one of claims 3 to 5, characterized in that the inner diameter of the bearing rings (28) is about 0.5 mm larger than the diameter of the tie rod (12). 7. Lagerung nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet , daß an der Innenumfangsfläche der von Lagerring (28) und Hülse (30) gebildeten Lagerbüchse (18) mindestens eine schräg zur Achse verlaufende flache Rinne (42) ausgebildet ist.7. Storage according to one of claims 3 to 6, characterized in that on the inner circumferential surface of the bearing ring (28) and sleeve (30) formed bearing bush (18) at least one oblique to the axis extending flat channel (42) is formed. 8. Lagerung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet , daß in der Stirnfläche (36) der konischen Lagerringe (28) eine Vielzahl axialer Bohrungen (38) vorgesehen ist.8. Bearing according to one of claims 1 to 7, characterized in that a plurality of axial bores (38) is provided in the end face (36) of the conical bearing rings (28).
EP19780100075 1977-07-19 1978-06-01 Tow bar bearing for a trailer coupling Expired EP0000325B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2732610 1977-07-19
DE19772732610 DE2732610C3 (en) 1977-07-19 1977-07-19 Storage for a drawbar of a trailer coupling

Publications (2)

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

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EP19780100075 Expired EP0000325B1 (en) 1977-07-19 1978-06-01 Tow bar bearing for a trailer coupling

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DE (1) DE2732610C3 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0213284A3 (en) * 1985-08-27 1988-10-19 Rockinger Spezialfabrik Fur Anhangerkupplungen Gmbh & Co. Mounting of the coupling element of a trailer draw-gear in the cross-member
GB2206856A (en) * 1987-03-20 1989-01-18 Stuart Fraser Towing bracket adapter
EP0433471A1 (en) * 1989-12-18 1991-06-26 ROCKINGER Spezialfabrik für Anhängerkupplungen GmbH & Co. Trailer coupling having coupling mount with pressure disc
EP0457249A2 (en) * 1990-05-14 1991-11-21 ROCKINGER Spezialfabrik für Anhängerkupplungen GmbH & Co. Trailer coupling key word: securing device with mechanical play
EP1527910A1 (en) * 2003-10-29 2005-05-04 Schnabl, Peter Trailer coupling

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE849044C (en) * 1942-02-27 1952-09-11 Ehrenreich & Cie A Linkage with suspension
FR1131515A (en) * 1952-02-08 1957-02-22 A C F Ind Coupling device for railway vehicles
US3169783A (en) * 1962-07-30 1965-02-16 Western Unit Corp Drawbar hitch assembly
DE1241278B (en) * 1962-08-16 1967-05-24 Ade Werk G M B H Spring-loaded trailer coupling
DE2206617A1 (en) * 1972-02-11 1973-08-23 Rockinger Spezial Fab Joh TRAILER HITCH

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE849044C (en) * 1942-02-27 1952-09-11 Ehrenreich & Cie A Linkage with suspension
FR1131515A (en) * 1952-02-08 1957-02-22 A C F Ind Coupling device for railway vehicles
US3169783A (en) * 1962-07-30 1965-02-16 Western Unit Corp Drawbar hitch assembly
DE1241278B (en) * 1962-08-16 1967-05-24 Ade Werk G M B H Spring-loaded trailer coupling
DE2206617A1 (en) * 1972-02-11 1973-08-23 Rockinger Spezial Fab Joh TRAILER HITCH

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0213284A3 (en) * 1985-08-27 1988-10-19 Rockinger Spezialfabrik Fur Anhangerkupplungen Gmbh & Co. Mounting of the coupling element of a trailer draw-gear in the cross-member
GB2206856A (en) * 1987-03-20 1989-01-18 Stuart Fraser Towing bracket adapter
EP0433471A1 (en) * 1989-12-18 1991-06-26 ROCKINGER Spezialfabrik für Anhängerkupplungen GmbH & Co. Trailer coupling having coupling mount with pressure disc
EP0457249A2 (en) * 1990-05-14 1991-11-21 ROCKINGER Spezialfabrik für Anhängerkupplungen GmbH & Co. Trailer coupling key word: securing device with mechanical play
EP0457249A3 (en) * 1990-05-14 1993-01-20 Rockinger Spezialfabrik Fuer Anhaengerkupplungen Gmbh & Co. Trailer coupling key word: securing device with mechanical play
EP1527910A1 (en) * 2003-10-29 2005-05-04 Schnabl, Peter Trailer coupling

Also Published As

Publication number Publication date
DE2732610A1 (en) 1979-02-01
DE2732610C3 (en) 1980-12-04
EP0000325B1 (en) 1981-08-05
DE2732610B2 (en) 1980-04-10

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