EP0900635A2 - Tool guiding on a pnematic driven percussion device - Google Patents

Abstract

Impact tool is operated with reciprocating drive between end stops and is guided by one or more sleeve bearings inside an outer guide (10). Each bearing comprises an inner sleeve (16) which guides the shaft of the tool and an outer sleeve (17) of elastic material which slides inside the guide. The outer sleeve is contoured (17b) on the outside to allow a tilt action of the tool inside the support guide, thus preventing jamming of the tool and prolonging bearing life. The bearing tilts about in either direction about a central plane (18).

Description

The invention relates to a tool guide on a pressure medium-operated impact device, in particular Hydraulic hammer, with a housing in which the tool is in Movable in the longitudinal direction with at least one guide section in each case at least one bush-like guide element and one also bush-like bearing component elastic in the transverse direction supports, and which has a stop which the Tool freedom of movement against its Extending movement limited. One of the two interacting leadership components - leadership element and Bearing component - has a tiltable longitudinal surface with a linear one Vertex diameter, on the side of which surface sections with deviating, changing in the longitudinal direction Connect the diameter. Furthermore, the one facing the tool Inner surface of the guide element - viewed in longitudinal section - with Except for their front end sections, if necessary, straight educated.

Hydraulic-operated impact devices - which in particular for Serve to crush stone, concrete or other building material - are taken into account with regard to the high shredding capacity required in most cases as additional or add-on equipment for construction machines such as excavators, loaders or other carrier units used. Such an application is for example in the Document DE 40 36 918 A1 shown and described, the Impact device attached to the boom of a hydraulic excavator and is supplied with energy from it. The tool on which the impact device moves back and forth the impacted piston acts on the material to be shredded, is usually a chisel held movably in a housing educated. The housing forms part or the Extension of the striking mechanism housing, which holds the percussion piston in addition to control and other facilities.

Due to the rough working conditions and the high Shredding performance is the tool guide considerable Exposed to stress, especially kicking - conditionally too due to the relatively large play of the tool in the transverse direction - high edge pressures; these not only affect the Shredding performance but lead to a significant Wear in the area of the tool itself and the Tool guide with the result that this and / or this under Is damaged or fails completely. Depending on the structural conditions, the Tool guidance from a continuous guide section or from several spatially separated guide sections exist over which or which the tool in Is supported in the transverse direction on its associated housing.

In order to eliminate the disadvantages mentioned above, the proposal has already been made in document DE-U1-90 11 245 to support the chisel movably in its housing by means of two sliding pivot bearings in a device of the type mentioned at the outset. The two sliding pivot bearings are held together in an inner housing serving as a chisel receptacle, which in turn is arranged via elastic means within the housing of the pressure medium-operated impact device. Furthermore, the guide rings forming the sliding pivot bearings are designed in such a way that their vertices lying on the apex diameter represent the largest diameter of a tiltable outer surface.
The disadvantage of this known tool guide is that the guide sections formed by the sliding pivot bearings can have only a relatively small longitudinal extension for design reasons, so that an unfavorably high surface loading of the bearing sections cannot normally be avoided. In addition, there are unfavorably high loads with a very steep increase in power due to the fact that the power transmission between the chisel and its housing is purely metallic.

From the document DE-U1-295 10 818 the use of a metallic chisel bush is known which has a guide bush made of softer, non-metallic material on the side facing the chisel; To ensure emergency lubrication, the internal guide bushing consists of friction-reducing components or such components are embedded in the guide bushing.
The disadvantage of this known tool guide is the fact that the chisel acts directly on the non-metallic guide bush; This is accordingly subject to wear, with the result that the latitude of movement of the chisel in the transverse direction may assume an impermissible value in a relatively short time.

From the point of view of shock absorption, the German patent specification 860 630 has already made the proposal for pneumatic hammers or the like to support the hammer part indirectly or directly on the housing via soft rubber intermediate layers.
However, this training is not suitable to absorb the transverse forces emanating from the tool itself and to withstand this for a long time due to the tendency of the chisel to tilt.

The invention has for its object to provide a tool guide on a pressure medium operated impact device, which is designed such that each associated guide section can adapt to the position of the tool within its housing without any canting.
Furthermore, the tool guide should be such that its guide components are not substantially stressed by sliding friction even when large transverse forces occur.
Moreover, the new design is intended to ensure that the play between the tool and each guide section can be compensated for without the occurrence of significant forces.

The task is carried out by a tool guide with the characteristics of Claim 1 solved. After that, each leadership section sits down composed of a guide element and a bearing component, wherein the bearing component in contact with the guide element from a softer, elastic material than the guide element self.

Another feature of the invention is that the vertices lying on the apex diameter of at least one tiltable longitudinal surface are arranged eccentrically with respect to their extension in the longitudinal direction; apex diameter is to be understood as the linear area in which either a tiltable outer surface reaches its largest diameter or a tiltable inner surface reaches its smallest diameter. Furthermore, the subject matter of the invention is designed in such a way that each tiltable longitudinal surface lies opposite a counter surface which, viewed in longitudinal section, runs essentially in a straight line.
It is essential in this context that the counter surface facing the tiltable longitudinal surface is designed in such a way that it allows the rolling tiltable longitudinal surface to roll. In the simplest case, the counter surface is straight in longitudinal section; however, it can also have a curvature permitting the rolling movement - in particular a relatively large radius of curvature in longitudinal section.

The basic idea of the invention is, after all, to form the longitudinal surface of one of the two interacting guide components, taking into account the progressive effect of Hertzian contact; this progressive effect consists in the fact that with increasing loading of the relevant guide component in the transverse direction, an ever larger area contributes to the power transmission.
Furthermore, due to the above-mentioned design, only a movement with compressive stress, at least similar to a rolling process, occurs, but practically no stress due to sliding friction, which would result in a far higher material stress.

The eccentric position of the vertices has the effect that a tilting moment additionally acts on the guide section in question and thus supports its positional adaptation to the position of the tool.
Another advantage of the configuration according to the invention is that the internal guide element can consist of a metallic material which on the one hand is sufficiently wear-resistant and on the other hand has the required lubricity, in particular steel with a sliding coating. Since the power transmission always takes place with the interposition of the elastic bearing component, this leads to a softer increase in force, which in particular also protects the tool and the respective guide element together with the bearing component.

Within the framework of the teaching according to the invention, the interacting management components as follows be formed, the one facing the tiltable longitudinal surface Longitudinal section of the opposite surface is straight or slightly curved:

Either the outer surface of the bearing component facing the Guide element formed tiltable (claim 2) or one of the both longitudinal surfaces of the bearing component (inner surface or Outer surface) is shaped accordingly (claim 3 or 4).

If the chisel guide only has one guide section (with a Guide element and bearing component), the Vertices of the tiltable longitudinal surface in the direction of the Stop (i.e. towards the striking mechanism of the striking device) are shifted (claim 5).

In embodiments with two guide sections separated from one another, the vertices of both tiltable longitudinal surfaces are expediently displaced in the direction of the center plane between the guide sections.
Within the scope of the invention, however, the tiltable longitudinal surface of only one guide section can also be arranged correspondingly off-center.

The longitudinal surface in question is preferably designed to be tiltable in such a way that its apex is displaced by a maximum of 45% of the axial length of the guide component (claim 7).
In particular, the vertices can be shifted off-center by 10% to 30% of the axis length of the guide component (claim 8).

balliger Längsfläche" ist dabei eine Fläche des betreffenden Führungsbestandteils zu verstehen, die - im Längsschnitt des Führungsbestandteils gesehen - gerundet ist.
Der jeweils zugehörige Rundungsmittelpunkt kann innerhalb oder außerhalb des balligen Führungsbestandteils liegen, so daß sich die damit im Zusammenhang stehenden geometrischen Bedingungen den sonstigen konstruktiven Erfordernissen weitestgehend frei anpassen lassen.
Im Normalfall wird es ausreichend sein, daß die ballige Längsfläche eine konstante Krümmung aufweist. Unter Umständen lassen sich zusätzlich Vorteile dadurch erzielen, daß die Krümmung der balligen Längsfläche in der Nähe der Scheitelpunkte, d. h. in der näheren Umgebung des jeweiligen Größt- oder Kleinstdurchmessers, kleiner ist als in den sich daran anschließenden Bereichen (Anspruch 11).
Aufgrund des größeren Krümmungsradius in der Nähe der Scheitelpunkte bzw. des Scheiteldurchmessers steht mit zunehmender Beanspruchung in Querrichtung schneller eine größere an der Krattübertragung mitwirkende Fläche zur Verfügung.In an advantageous embodiment of the subject matter of the invention, the difference between the largest and smallest diameters of the tiltable longitudinal surface is at least 0.5 millimeters (claim 9).
In the context of the invention, the tiltable longitudinal surface can be spherical (claim 10). Under

spherical longitudinal surface "is to be understood as meaning a surface of the guide component in question which - seen in the longitudinal section of the guide component - is rounded.
The associated center of rounding can lie inside or outside the spherical guide component, so that the geometric conditions associated therewith can be largely freely adapted to the other structural requirements.
In normal cases it will be sufficient for the spherical longitudinal surface to have a constant curvature. Under certain circumstances, additional advantages can be achieved in that the curvature of the spherical longitudinal surface in the vicinity of the apex, that is to say in the vicinity of the respective largest or smallest diameter, is smaller than in the adjoining areas (claim 11).
Due to the larger radius of curvature in the vicinity of the apex or the apex diameter, the larger the surface that is involved in the Kratt transmission, the faster the load in the transverse direction becomes available.

The tiltable longitudinal surface can, however, also be composed of two longitudinal sections with opposite taper, which merge into one another in terms of the apex diameter (claim 12). In this embodiment, the respective longitudinal sections that belong together — viewed in the longitudinal section — are each formed in a straight line and form an angled longitudinal surface with one another.
In principle, the tiltable longitudinal surface can also have a different shape within the scope of the invention, provided that this does not hinder the tilting or pivoting movement of the guide section in question, which is necessary for the positional adjustment, and is suitable for absorbing the transverse forces caused by the tool.
In view of the high stress in the area of the tool guide, the material for the bearing component should have a high compressive strength and toughness as well as a high temperature resistance with sufficient elasticity. Thermoplastic materials (such as, in particular, polyamide or polyethylene), elastomers (such as, in particular, polyurethane) or thermosets can be considered as bearing component materials. Favorable properties show in this context
highly cross-linked plastics (claim 13), for example twelve-fold cross-linked, cast polyamide (PA 12 G) or resin-based fabric composite materials (claim 14). The latter materials from the group of thermosets can consist of glass, carbon or natural fibers, which are impregnated with a suitable resin.

Under certain circumstances, the guide sections can also be made from Individual segments exist that are movable relative to each other in the Tool housing are held. It is particularly so conceivable, the guide sections with a suitable design of the Tool cross-section and the tool housing from several to build plate-shaped individual segments that are relative to each other are mobile.

It goes without saying that the components of each guide section must be suitably fixed in the axial direction with respect to their housing; this fixation must be designed so that it does not affect the function of the guide section.
In the simplest case, each existing guide section can be secured in its position with respect to the housing by means of a bolt or the like, which also engages in the inner guide element with suitable play.

The invention is illustrated below with reference to the drawing Exemplary embodiments explained in detail:

Fig. 1

schematisiert ein als Hydraulikbagger ausgebildetes Trägergerät, an dem eine druckmittelbetriebene Schlagvorrichtung anstellbar angebracht ist;

Fig. 2

in gegenüber Fig. 1 vergrößertem Maßstab schematisiert einen Vertikalschnitt des unteren Teils der Schlagvorrichtung;

Fig. 3

ein Schemabild einer Werkzeugführung mit zwei voneinander getrennten Führungsabschnitten, die jeweils ein innenliegendes Führungselement mit balliger Außenfläche aufweisen;

Fig. 4

ein Schemabild einer Werkzeugführung mit zwei voneinander getrennten Führungsabschnitten, die jeweils ein Lagerbauteil mit balliger Innenfläche aufweisen;

Fig. 5

ein Schemabild einer Werkzeugführung mit zwei voneinander getrennten Führungsabschnitten, die jeweils ein Lagerbauteil mit balliger Außenfläche aufweisen, und

Fig. 6

einen Vertikalschnitt eines Führungsabschnitts in der Ausgestaltung gemäß Fig. 5.

Fig. 7

ein Schemabild einer Werkzeugführung in einer der Fig. 5 entsprechenden Ausgestaltung, wobei die Außenfläche des Lagerbauteils zwei Längsabschnitte mit gegenläufiger Konizität aufweist, die in dem Scheiteldurchmesser ineinander übergehen, und

Fig. 8

einen vertikalen Teilschnitt durch den in Fig. 7 dargestellten Führungsabschnitt 12 in verändertem Maßstab.

Show it:

Fig. 1

schematically shows a carrier device designed as a hydraulic excavator, on which a pressure medium-operated impact device is adjustably attached;

Fig. 2

in an enlarged scale compared to FIG. 1, a schematic vertical section of the lower part of the impact device;

Fig. 3

a schematic image of a tool guide with two separate guide sections, each having an inner guide element with a spherical outer surface;

Fig. 4

a schematic image of a tool guide with two separate guide sections, each having a bearing component with a spherical inner surface;

Fig. 5

a schematic image of a tool guide with two separate guide sections, each having a bearing component with a spherical outer surface, and

Fig. 6

5 shows a vertical section of a guide section in the configuration according to FIG. 5.

Fig. 7

5 shows a schematic image of a tool guide in an embodiment corresponding to FIG. 5, the outer surface of the bearing component having two longitudinal sections with opposite taper, which merge into one another in the apex diameter, and

Fig. 8

a vertical partial section through the guide section 12 shown in Fig. 7 in a changed scale.

The hydraulic excavator 1 shown in Fig. 1 is equipped with a supply unit 2 (consisting essentially of a diesel engine, not shown, and a hydraulic pump driven by this), which - as known for example from the document DE 40 36 918 A1 - via a pressure and a return line is connected to a pressure medium operated impact device 3. The latter is held adjustable on the boom 4 of the hydraulic excavator.
The striking device 3 has, as a guide unit, a supporting frame 5 which is articulated with respect to the boom and in which a pressure medium-operated striking mechanism 6 (partially shown in FIG. 2) is supported.
As can also be seen in FIG. 1, a tool in the form of a chisel 7 protrudes from the supporting frame 5, on which the above-mentioned percussion mechanism acts via its percussion piston 8 in a manner known per se. The latter is shown in Fig. 2 on the one hand in the return stroke position (left) and on the other hand in the impact position (right).

The striking mechanism 6 forming part of the striking device 3 can be of any desired design within the scope of the invention, in particular also with regard to its control.
As can be seen in FIG. 2, the striking mechanism housing 9 - which, among other things, receives the striking piston 8 - is connected as an extension to a housing 10 in which the chisel 7 is supported in a longitudinally movable manner via two guide sections 11 and 12; these are each secured by a bolt 13 against displacement in the axial direction.

The freedom of movement of the chisel 7 against it Extending movement (indicated by an arrow 14) is by a Limited stop 15, which in turn is fixed in the housing 10.

The guide sections 11 and 12 are only shown schematically in FIG. 2 for reasons of clarity; their structure and function will be explained in more detail below.
The holder by which the chisel 7 is secured against falling out of the housing 10 is also not shown in FIG. 2; in the simplest case, it consists of a bolt or projection which is arranged between the guide sections 11 and 12 and defines the freedom of movement of the chisel 7 in the direction of its extension movement (arrow 14).

3 to 6, each guide section 11 or 12 each has two interacting guide components, namely a bush-like guide element 16 which is internal to the chisel 7 and an outer bush-like bearing component 17 which also bears against the housing 10. The latter consists of a softer material than the metallic guide element 16, namely from a twelve-times cross-linked, cast polyamide.
The guide components 16, 17 of each guide section 11, 12 are fixed in the axial direction in the manner already mentioned.

All of the embodiments of the The subject of the invention has in common that one of the two each cooperating guide components 16, 17 a crowned Has longitudinal surface and that the chisel 7 facing Inner surface 16a of the guide element 16 - viewed in longitudinal section - Except for their end portions 16b and 16c even trained, i.e. forms the shape of a cylinder. The above Representations continue - just like FIGS. 7 and 8 - recognize that the facing the tiltable longitudinal surface Counter surface, so possibly also the inner wall of the housing 10, is linear in longitudinal section, so that a Rolling movement is made possible.

3 is the bearing component 17th facing outer surface 16d of the guide element 16 crowned trained, i.e. seen in the longitudinal cross section, it shows a steady Rounding up.

In contrast, in the embodiment according to FIG. 4 the Guide element 16 facing inner surface 17a of each bearing component 17 crowned, while the guide element 16 each Has the shape of a cylindrical sleeve.

In the exemplary embodiment according to FIG. 5, each guide element 16 is assigned a bearing component 17 in the form of a likewise cylindrical bushing, the outer surface 17b of which facing the housing 10 is spherical.
This configuration enables the respective interacting guide components 16 and 17 to be fastened directly to one another.

3 to 5 can also be seen, the bearing sections 11 and 12 - due to the spherical design of an associated guide component 16 or 17 - can adapt to an inclination of the chisel 7 caused by the guide play, thereby causing canting processes between the parts 7 and 16 are practically excluded. Due to the fact that the guide component 17, which is made of softer material, is arranged outside the area of the chisel 7, the latter is supported exclusively on the more wear-resistant guide element 16.
The spherical design of the longitudinal surfaces 16d, 17a and 17b also has the consequence that the surface cooperating in the power transmission becomes larger as the stress in the transverse direction of the chisel 7 increases.

The above-described embodiments (FIGS. 3 to 5) correspond in that the vertices SP (cf. FIG. 6) of the respective spherical longitudinal surface of a guide component are arranged eccentrically with respect to the extent of the longitudinal surface in the longitudinal direction, that is, they lie around a distance e with respect to the transverse median plane 18 of the guide component in question.
If the tool guide - as shown in FIGS. 2 to 5 - has two separate guide sections 11 and 12, the vertices SP of the spherical longitudinal surface 16d or 17a or 17b each lie in the direction of the central plane 19 (cf. FIG. 3 ) moved between the guide sections 11 and 12.
If the tool guide has only one guide section 11 (as shown in FIG. 6), the vertices SP of the spherical longitudinal surface are shifted off-center in the direction of the stop 15 shown in FIG. 2, ie to the right in FIG. 6.

Depending on which longitudinal surface of a guide component 16 or 17 is spherical, they are to the apex diameter associated vertices SP on the largest diameter - longitudinal surface 16d or 17b in Fig. 3 or 5 - or on the smallest diameter - Inner surface 17a in FIG. 4 - of the guide component 16 or 17th

The degree of crowning corresponds to the difference between the Largest and smallest diameters of the spherical longitudinal surface in question 16d, 17a and 17b, respectively; it is - depending on the length of the Guide section and the size of the game between this and the tool - at least 0.5 millimeters.

In the exemplary embodiment according to FIG. 6, the crowning (not shown to scale) corresponds to the difference between the largest diameter DG and the smallest diameter DK of the spherical outer surface 17b; it is several millimeters.
Furthermore, the representation in question reveals that the distance e - based on the axis length L of the bearing component 17 - amounts to 10%.

The spherical longitudinal surface (cf. FIGS. 3 to 5) can in principle have a constant, constant curvature. Deviating from this, however, there is also the possibility of designing the spherical longitudinal surface 16d, 17a or 17b to be differently curved over its longitudinal extent.
In this context, it can be seen from FIG. 6 that the spherical outer surface 17b has a smaller curvature in the vicinity of the vertices SP than in the regions adjoining it. This configuration is indicated by the radii of curvature RSP or R1 and R2, the radius of curvature RSP being greater than the radii of curvature R1 and R2.
If the tool guide is equipped with two spatially separate guide sections, these can, if necessary, also be designed differently with regard to the configuration of the spherical longitudinal surface - in particular with regard to the size of the crown and the position of the vertices SP. In this connection, it is possible, for example, to design only the guide section which is subject to higher loads in such a way that the vertices SP are eccentric in the manner described. Furthermore, it is possible to design only the spherical longitudinal surface of the guide section which is subject to higher loads to have different curvatures over its longitudinal extent.

Basically, within the scope of the invention, the tiltable or pivotable longitudinal surfaces (ie the outer surface of the guide element 16 or the inner surface or the outer surface of the bearing component 17) can be shaped or configured differently than shown in FIGS. 3 to 6.
7 and 8 show in this connection an embodiment with a bearing component 17, the tiltable or pivotable longitudinal surface of which is composed of two longitudinal sections 17c and 17d with opposite taper; these longitudinal sections merge into one another in the apex diameter - on which the apex points SP are arranged (cf. FIG. 8). The longitudinal sections 17c and 17d are then - viewed in the longitudinal section (FIG. 8) - rectilinear with the result that the diameter of the outer surface of the bearing component 17 - starting from the vertex diameter with the associated vertex SP - in both directions (ie in Fig. 8 to the left or right) decreases in a straight line.

7 and 8 also show some design data by means of which the shape of the tiltable or pivotable longitudinal surface can be determined; the distance e (shown in FIG. 8) is 20% of the axis length L of the guide section 12.
The distance between the vertices of the guide sections 11 and 12 is with LS "denotes the guide play between the guide elements 16 and the chisel 7 S ".

For the design of the tiltable or swiveling longitudinal surface (in the present case: the bearing component 17), one normally chooses a somewhat larger value for the guide play S than in the new state, in order to take into account an expected initial wear of the guide sections.
According to the equation sinA = S / LS you choose the angle at which the guide play between the chisel 7 and the guide sections 11, 12 is balanced and thus a linear contact between the parts 7 and 11 and 12 is achieved. The inclination of the larger longitudinal section 17c is formed in accordance with the angle A. The shorter longitudinal section 17d is formed inclined according to the angle B. Here is the angle B "larger than the angle A "so that the tilting or pivoting movement of the guide sections 11 and 12 is not hindered to adapt to the position of the chisel 7.

On the basis of the design criteria mentioned above, the relevant tiltable or pivotable longitudinal surface (as explained with reference to FIGS. 3 to 6) can also be spherical, the course of the crowning overall approximating the angle A "and B ".
8 therefore also shows the radii of curvature RSP, R1 and R2 for the case of a spherical longitudinal surface in question.

Basically, the tilting or swiveling longitudinal surfaces also from a larger number of sub-areas with different Radii of curvature or different inclinations (accordingly 7 and 8).

The tilting or swiveling design of the guide sections 11 and 12 with the participation of the elastically deformable bearing component 17 has the consequence that the latter under the influence of the chisel 7th outgoing lateral forces finally deformed so far that for the Power transmission in the direction of the housing 10 is sufficient large area is available.

The guide element 16, which interacts directly with the chisel 7, should consist of a highly wear-resistant, metallic material which can withstand an abrupt load and, in cooperation with the chisel 7, has sufficient sliding properties.
If necessary, the guide element 16 can also have a sliding coating on its inner surface facing the chisel.

The invention is advantageous in that it uses simple means Care is taken that between the interacting Management components 16 and 17 on the occasion of the adjustment to the Inclined position of the tool 7 only with a kind of rolling motion Pressure load takes place, only the more wear-resistant Guide component directly with the moving tool is in contact. The rolling motion is also thereby allows the facing the tiltable longitudinal surface Counter surface is designed accordingly, i.e. normally - in Seen longitudinal section - runs straight.

The bearing component 17 consisting of a softer material forms thereby a flexible covering of the inside Guide element 16; this configuration has the consequence that the the area involved in the power transmission increases with increasing Stress in the transverse direction of the guide section accordingly enlarged.

Claims (14)

Tool guide on a pressure medium operated impact device (3), in particular hydraulic hammer, with a housing (10) in which the tool (7) is movable in the longitudinal direction via at least one guide section (11, 12), each with at least one bush-like guide element (16) and one also supports bush-like bearing component (17) elastically in the transverse direction and has a stop (15) which limits the freedom of movement of the tool (7) against its extension movement (arrow 14),
one of the two interacting guide components - guide element (16) and bearing component (17) - has a tiltable longitudinal surface (16d, 17a to d) with a linear apex diameter (apex SP), on which surface sections (17c 17d) laterally deviate from it , connecting in the longitudinal direction changing diameter, and the inner surface (16a) of the guide element (16) facing the tool (7) - viewed in longitudinal section - with the exception of possibly its front end sections (16b, 16c) being rectilinear,
characterized by the following features: each guide section (11, 12) is composed of a guide element (16) and a bearing component (17), the bearing component (17) resting on the guide element (16) being made of a softer, elastic material than the guide element (16) even; the vertices (SP) lying on the apex diameter - corresponding to the maximum diameter (DG) of a tiltable outer surface (16d, 17b to d) or the smallest diameter of a tiltable inner surface (17a) - are at least one tiltable longitudinal surface (17b to d) with regard to their extension in The longitudinal direction is arranged eccentrically (distance e), each tiltable longitudinal surface being opposite a counter surface (guide element 16, bearing component 17 or housing 10) which is essentially rectilinear in longitudinal section. Apparatus according to claim 1, characterized in that the Bearing component (17) facing outer surface (16d) of the Guide element (16) is designed to be tiltable. Apparatus according to claim 1, characterized in that the Guide element (16) facing inner surface (17a) of the Bearing component (17) is designed to be tiltable. Apparatus according to claim 1, characterized in that the Housing (10) facing outer surface (17b; 17c, 17d) of the Bearing component (17) is designed to be tiltable. Device - which only a guide element (16) together with Bearing component (17) has - according to at least one of the preceding claims, characterized in that the Vertexes (SP) of the tiltable longitudinal surface (17b; 17c, d) in Lie in the direction of the stop (15). Device with two separate guide sections (11, 12), each a guide element (16) and a bearing component (17), according to at least one of claims 1 to 4, characterized in that the vertices (SP) of both tiltable longitudinal surfaces (16d; 17a to d) in the direction of the Central plane (19) between the guide sections (11, 12) are shifted. Device according to at least one of the preceding claims, characterized in that the vertices (SP) maximally around 45% of the axis length (L) of the guide component (17) off-center are shifted. Device according to at least one of the preceding claims, characterized in that the vertices (SP) around 10% to 30% of the axis length (L) of the guide component (17) are shifted off-center. Device according to at least one of the preceding claims, characterized in that the difference between the largest and Smallest diameter (DG or DK) of the tiltable longitudinal surface (17b; 17c, d) is at least 0.5 millimeters. Device according to at least one of the preceding claims, characterized in that the tiltable longitudinal surface (16d, 17a, 17b) is spherical. Device according to at least one of the preceding claims, characterized in that the curvature of the crowned formed longitudinal surface (17b) near the apex (SP) is smaller than in the adjoining areas. Device according to at least one of claims 1 to 9, characterized characterized in that the tiltable longitudinal surface consists of two Longitudinal sections (17c, 17d) with opposite taper composed in the vertex diameter (vertices SP) merge. Device according to at least one of the preceding claims, characterized in that the bearing component (17) from a highly cross-linked plastic. Device according to at least one of the preceding claims 1 to 12, characterized in that the bearing component (17) consists of a resin-based fabric composite.

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