EP3879032A1 - Positioning device for positioning a machining tool relative to a rail - Google Patents

Abstract

An actuating device is disclosed for positioning a machining tool, which is arranged on a frame (14) fixed on a rail vehicle and has an active section for machining a rail head, relative to a rail laid in the track and over which the rail vehicle travels. The adjusting device comprises a first adjusting mechanism for changing an angular position of the active section of the machining tool, seen transversely to a longitudinal direction of the rail laid in the track. The first adjusting mechanism has a first coupling gear (13) whose gear members in the form of couplings and rockers are connected to each other exclusively by swivel joints that are parallel to one another and which, due to its structure, allows the machining tool to pivot about a virtual pivot point (SP ) allows, which can lie in particular in the rail head.

Description

The present invention relates to an adjusting device for positioning a processing tool which is arranged on a frame fixed on a rail vehicle and has an active section for processing a rail head relative to a rail laid in the track and over which the rail vehicle travels, the adjusting device having a first adjusting mechanism for changing a transverse to a longitudinal direction of the angular position of the active section of the machining tool seen in the track and can also advantageously have a second adjusting mechanism for changing a distance between the active section of the machining tool and the rail head of the rail laid in the track.

It is known that rails laid in the track are subjected to processing for maintenance and repair purposes. In particular, driving with massive rail vehicles can lead to wear and tear on the rail head and to a change in its transverse profile. To this extent, they must be reprofiled at regular intervals. Also, when rail vehicles cross the rails over long periods of time, microcracks can form in the rail surface, in particular the surface of the rail head, which entail the risk of further cracking and possible rail breakage.

Various methods are therefore used in the context of servicing, maintenance and preventive maintenance work on rails laid in the track. There are milling devices that can be driven on the track, with which the rails laid in the track can be reprofiled. Nowadays, rails laid in the track, especially on high-speed lines, but also prophylactically ground in order to grind down microcracks with a low material yield or to prevent the formation of microcracks. This has been done successfully for many years with a process in which freely rotating, non-driven grinding bodies mounted on a rotation axis, the rotation axes of which are inclined to the rails at an angle different from 90 °, at a comparatively high speed (for example speeds of about 80 km / h), whereby due to the high speed and the friction effect, sufficient torque is generated to set the grinding wheels in rotation and thus to obtain a grinding effect on the surface of the rail head. Such a method and an apparatus for carrying it out are, for example, in US Pat EP 708 205 A1 and also in him EP 1 460 176 A1 described.

Particularly with such grinding methods and devices, but also with other rail machining processes, it is important to obtain an exact delivery of the machining tools to the rail machined during the passage. There are two basic directions of delivery. On the one hand, a distance between a machining surface of the machining tool and the rail head can be set, on the one hand to start the grinding process by lowering the machining tool onto the rail, or to end it again by lifting it, on the other hand to allow the machining tools to be defined for the grinding process to press advantageous contact pressure on the rail and to compensate for the continuous wear of the machining tools by repositioning them. On the other hand, the setting is a plane lying in a plane perpendicular to the longitudinal direction of the rail Pivot angle relevant at which the machining tool is brought up to the rail head. This swivel angle determines which section of the rail head is machined (for example the running edge or the running surface). A profile design can be made through a suitable choice of the resulting grinding marks.

So known processing devices, with which rails laid in the track can be processed during a pass, typically have adjusting devices that have two adjusting mechanisms, namely one for the delivery, ie. H. the adjustment of the distance between the machining tool and the rail, and one for adjusting the angular position at which the machining tool engages the rail head. The problem here is that an infeed movement is a linear movement in which linear guides, for example sliding guides, are used in a first and nowadays also widely used solution approach. The problem with linear guides of this type is that the bearing required for this is difficult to seal and that it is prone to failure in an environment with high levels of dust and dirt particles, as is the case with material-removing machining of rails. Linear bearings, such as plain bearings, are also sensitive to transverse forces and must be designed to be correspondingly stable, or are sensitive to deflection or tilting and the resulting blockage of the bearings. Via a rotary movement with small angles of rotation and the use of inexpensive, well-sealed and robust rotary bearings, a linearized stroke movement can be implemented with appropriate gears, but the circular movement inevitably leads to transverse movements perpendicular to the stroke movement, which is greater, the larger the angle of rotation or the Stroke is selected.

The angle can be adjusted using cheaper, robust and easy-to-seal swivel joints, but in the known solutions a rotation only takes place about a pivot point which is outside the rail to be machined. For an ideal shape of the spherical rail profile, the pivot point around which the angle adjustment takes place should, however, be within the Be located at the top of the rail. There is still no solution for this in existing systems.

Based on this, the object of the invention is to develop an actuating device of the type mentioned at the outset such that it enables the angular position to be set around a virtual pivot point that is not mapped by a swivel joint while dispensing with linear or link guides. This virtual pivot point should preferably be able to be positioned within the rail head when it is passed over the rail to be machined. In a further aspect of the invention, an adjusting device is also advantageously developed in such a way that it has an adjusting mechanism for changing a distance between the active section of the machining tool and the rail head, which also manages without linear guides and link guides.

According to the invention, this object is initially achieved by an actuating device having the features of claim 1. Advantageous developments of such an actuating device are identified in the dependent claims 2 to 11. In a further aspect set forth in claim 12, the invention also provides a grinding unit arranged in a rail vehicle for the grinding of rails laid in the track during a passage with several with an axis of rotation at an angle different from 90 ° transversely to a longitudinal direction of the rail being driven over arranged in the grinding unit, about the axis of rotation in each case freely and non-driven rotatable grinding body row indicated, which is characterized in that the grinding unit has an adjusting device as specified with this invention.

An actuating device according to the invention for positioning a processing tool, which is arranged on a frame fixed on a rail vehicle and has an active section for processing a rail head relative to a rail laid in the track and driven over by the rail vehicle, has, as is already common in the prior art, a first actuating mechanism for changing an angular position of the active section of the seen transversely to a longitudinal direction of the rail laid in the track Machining tool. It can also have a second adjusting mechanism for changing a distance between the active section of the machining tool and the rail head of the rail laid in the track.

The special feature of the adjusting device according to the invention is first of all the design of the first adjusting mechanism. According to the invention, this has a first coupling gear and a first actuator for moving the first coupling gear.

The first coupling gear exclusively has gear members in the form of rockers and couplings, which are connected to mutually parallel axes of rotation via rotatable swivel joints. Furthermore, the first adjusting mechanism enables the machining tool connected to it to be pivoted about a virtual pivot point, in particular located in the rail head during operation, by actuating only the one first actuator.

This measure means that, with the coupling gear according to the invention, no linear guides or link guides are used for the first adjusting mechanism, and has the advantage that the swivel joints used are low-maintenance and robust, especially when the rails are heavily contaminated with dirt and particles Environment with very abrasive media, and that the swivel joints, due to a certain angular play that they have, do not tend to misjudge even with high forces and block the adjusting mechanism.

According to the invention, the first coupling mechanism can contain at least two rockers, namely a first rocker pivotably attached to a first pivot point that is fixed in position relative to the frame and a second pivot arm pivotably attached to a second pivot point that is fixed relative to the frame. The axes of rotation of the two rockers are parallel to each other.

If the bearing points identified above are described here as being "fixed in position relative to the frame", then this aims at a positional stability in a normal operating state of the first linkage and closes In particular, it does not rule out that the bearing points can be shifted or relocated in their position relative to the frame by adjusting the frame or also by individually adjusting the bearing points, e.g. to move or align the first coupling gear or to deliberately detune the gear obtain.

Furthermore, a first coupling can be part of the first coupling mechanism, which is attached to a first contact point arranged on the first rocker and to a second contact point arranged on the second rocker and can be pivoted relative to the associated rocker, the axes of rotation being through the Contact points are parallel to the axes of rotation through the bearing points. The arrangement of the first and second rocker and the coupling connecting them can be selected according to the invention in such a way that a polygon formed from the respective straight connecting lines starting from the first bearing point via the first bearing point, the second bearing point, the second bearing point and back to the first bearing point first parallelogram results. The distance between the bearing points of the two arms and the length of the coupling are then the same, and the lengths from the bearing point to the bearing point on both arms are the same.

Furthermore, in the adjusting mechanism according to the invention, a third contact point spaced from a connecting line between the first contact point and the second contact point can be formed on the first coupling, and a third rocker can be swiveled at this third contact point. The position of the third contact point can be chosen so that a projection point of the third contact point lies on a straight line connecting the first contact point and the second contact point between these contact points, but also so that this projection lies outside the area between the two contact points. A second coupling can also be part of the first coupling mechanism, which is pivotably attached to the third rocker at a fourth contact point arranged on the third rocker, again with an axis of rotation parallel to the aforementioned axes of rotation. This third swing arm can continue with be pivotably attached to the first rocker at a fifth contact point arranged on the first rocker, again about an axis of rotation which runs parallel to the other named axes of rotation. The first rocker can be designed in such a way that the first abutment point is at a distance from a connecting line between the first bearing point and the fifth abutment point. However, the first abutment point can also lie on a straight connecting line between the first abutment point and the fifth abutment point; The three points, the first bearing point, the first bearing point and the fifth bearing point, can therefore lie on a common, straight connecting line.

According to the invention, the structure of the first coupling gear can then be designed in such a way that a section formed from the respective straight connecting lines starting from the first abutment point via the third abutment point, the fourth abutment point, the fifth abutment point and back to the first abutment point results in a second parallelogram.

In the embodiment as set out above, a coupling gear is formed which spans several parallelograms. Thus, a first parallelogram, already described above, is formed by the course of the line starting from the first bearing point via the first bearing point, the second bearing point, the second bearing point and back to the first bearing point. A second parallelogram, also already mentioned above, is formed by the course of the line starting from the first attachment point via the third attachment point, the fourth attachment point, the fifth attachment point and back to the first attachment point.

This general construction now leads to the fact that the third attachment point and the fourth attachment point are pivoted about a virtual pivot point when the coupling gear is adjusted, which is at an intersection between a line parallel to a connecting line between the first bearing point and the first attachment point and through the third attachment point running line and a line parallel to a connecting line between the first abutment point and the third abutment point and running through the first bearing point. This point of intersection - that is, the pivot point - forms itself in this case again a corner point of a third parallelogram, which is formed by the stretch of straight connecting lines lined up from the first bearing point via the first bearing point, third bearing point, the intersection and back to the first bearing point the line parallel to the first bearing point and the fifth bearing point and running through the fourth bearing point and the line parallel to the connecting line between the first bearing point and the third bearing point and running through the first bearing point, which also determines the pivot point. In this respect, it also forms a corner point of a fourth parallelgram, which is formed by the stretches of the straight connecting lines strung together from the first bearing point via the fifth abutment point, fourth abutment point, the intersection point and back to the first bearing point.

In other words, with a first adjusting mechanism as described above, it is possible to pivot the third rocker around a virtual pivot point (virtual pivot point) which is determined by the intersection point described above, the corner point of the third and fourth parallelograms.

This virtual pivot point can now be positioned in a targeted manner by appropriate positioning of the two bearing points and a corresponding design of the respective position of the bearing points and abutment points, thus also the respective distances between these points in space. This can be done in particular in such a way that the virtual pivot point when the actuating device is used in a rail vehicle lies within the rail head of a rail that has been driven over and is to be processed with the processing tool, which can be adjusted with the actuating device. However, other placements of the virtual pivot point are also conceivable and can be useful in practical application, especially in other areas of the track being driven over and the associated space in which a real pivot point, i.e. a machine part, cannot be placed, e.g. due to an otherwise committed so-called clearance violation, i.e. penetration into a for Track fixtures or section of the spatial profile belonging to the track that is closed for safety reasons. A placement of the virtual pivot point outside, for example just outside, that is to say close to the surface, of the rail head is also possible and conceivable.

In this way, not only is a particularly robust angular setting achieved solely by means of swivel joints, but also a swiveling movement of the tool, more precisely of an active section of the same around a fulcrum located within the rail head, can be obtained by placing the virtual pivot point or pivot point, which, as stated above, is of great advantage for machining the rail head and obtaining a profile that is as ideal as possible.

The first actuator can in principle be arranged in completely different positions. In practice, it will be arranged between two links of the first linkage or between the frame and one link of the first linkage where there is sufficient space and where the lever ratios are as favorable as possible, with the actuator providing an effective torque in the first linkage bring in.

In the embodiment as described above, a connecting line between the third attachment point and the fourth attachment point can basically be implemented in completely different orientations, in particular in an orientation that is not parallel to a connecting line pointing from the attachment points in the direction of the virtual pivot point, in particular not runs along this. In order to align the connecting line between the third abutment point and the fourth abutment point continuously in a direction towards the virtual pivot point, the first abutment point can advantageously lie on a connecting line connecting the first bearing point to the fifth abutment point in a straight line. As a result of this measure, the connecting line between the third contact point and the fourth contact point, and thus a longitudinal orientation of the third rocker, is aligned in alignment with the virtual pivot point.

In principle, the two bearing points can be firmly connected to a frame or chassis of the rail vehicle, which can also be a processing unit. For further setting options, however, it can also be provided that the bearing points are arranged on an adjusting rocker that can be detachably connected to the rail vehicle and pivoted about a fastening point located between the bearing points. By tilting this rocker arm around the fastening point, the positioning of the bearing points in relation to the rail vehicle can be adjusted for a further setting of the position of the virtual pivot point and thus a further degree of freedom in setting the machining tool in its position relative to the one to be machined Get rail.

In a further advantageous aspect of the invention, it is proposed that the adjusting device have a second adjusting mechanism for changing a distance between the active section of the machining tool and the rail head of the rail laid in the track.

Such a second adjusting mechanism can in principle be implemented in very different ways. For example, it can contain two synchronized and parallel length adjustment means for the simultaneous adjustment of the lengths of the first and the second rocker.

According to the invention, however, the second adjusting mechanism can also have a special design. In such a special design, the second adjusting mechanism can have a second coupling gear, which likewise has gear members in the form of rockers and couplings connected to one another exclusively via rotary joints rotatable about mutually parallel axes of rotation. In such an embodiment variant, the second adjusting mechanism is also only provided with swivel joints which, as already mentioned above, are robust and low-maintenance and at the same time, due to a certain play, do not tend to jamming or wedging even with high forces occurring. In this proposed variant, a frame element of the second linkage is on the third rocker arm of the first linkage set, and a second actuator moving the second linkage is provided.

The special feature of this variant of an actuating device according to the invention is that the second coupling gear has a Roberts straight-line guide, which has a first rocker pivotably secured in a first bearing point on the frame element and a second rocker arm pivotally secured at a second bearing point on the frame element and a with the first rocker at a first distance from the first bearing point arranged first contact point and with the second rocker in a second contact point arranged at the first distance from the first bearing point pivotably connected triangular coupling.

A Roberts linear guide is a gear element that is well known in mechanical engineering, so that it does not need any further explanation here. This straight guidance ensures that when the two rockers are rotated relative to the frame element, a tip of the triangular coupling formed as an isosceles triangle is guided over a section located between the two bearing points along a straight guide line. The adjusting device provided with the special second adjusting mechanism in this further development makes use of this property in order to obtain a guide for a straight advancing movement which can be obtained by means of a coupling gear exclusively comprising rotary joints.

For an orderly linear guide of a guided link of the second linkage, it can be provided in particular that a third link can be pivoted on the frame element of the second linkage in addition to the first and second link of the Roberts straight-line guide and adjacent to the first link of the Roberts straight-line guide in a third bearing point is fixed. This third rocker arm of the second coupling gear is then connected to a third coupling point with a first coupling, the first coupling being pivotably connected to the first rocker and the triangular coupling at the first contact point. In this case, a connecting line connecting the third bearing point and the third bearing point in a straight line is essentially parallel to aligned with the first swing arm of the Robertson straight line. The guided link of the second coupling mechanism is pivotably connected at a first connection point to the tip of the triangular coupling, which is guided on a straight path, and is furthermore pivotably connected to a second of the first connection point along a guide line parallel to the straight guide line on which the tip of the triangular coupling is guided, extending line spaced apart in a second connection point connected to a second coupling. This second coupling is pivotably connected to the third link and the first coupling of the second coupling mechanism at a third contact point. A connecting line between the first and the third abutment point is essentially parallel to the straight path on which the tip of the triangular coupling of the Roberts straight line is guided. This configuration translates the straight guidance of the tip of the triangular coupling of the Roberts straight line at the same time into a parallel straight guidance of the second connection point and thus provides a straight line of a rod-like link, the guided link of the second linkage.

The second actuator, with which the second coupling gear is moved, can now in particular be arranged so that it can apply an actuating force between the frame element and the guided link of the second coupling gear, in particular in a direction parallel to the direction of the straight path on which the tip of the triangular coupling of the Roberts straight line is guided. In an adjusting device provided with a second adjusting mechanism as described above, the frame element on the third rocker of the first coupling gear can be fixed in such a way that the straight guide line on which the tip of the triangular coupling is guided is essentially parallel to the fifth connecting line of the first Linkage extends. By this measure, the feed direction can be directed in particular in the direction of the virtual pivot point obtained by the first adjusting mechanism, so that the machining tool can be pivoted by moving the first coupling gear and lifted or delivered by actuating the second coupling gear, or a pressure can be applied by actuating the second coupling gear of the tool can be adjusted to the rail surface to be machined. In the case of a variant of the actuating device with the described second actuating mechanism, which is configured as above, a holder for the machining tool can be arranged in particular on the guided link of the second coupling gear. Such a holder can in turn, for example, be arranged so that it can be rotated about an axis if, for example, it has several tools or tool groups in the manner of a turret, which can be exchanged by rotation and, for example, rotated out of the machining position after wear, and replaced by a new one in the machining position rotated tool group or a tool can be replaced, which is then in turn delivered in the direction of the rail head.

As already mentioned, an actuating device as described above can, in particular, in a grinding unit arranged in a rail vehicle for the grinding processing of rails laid in the track during a pass with several with a rotation axis transversely arranged in the grinding unit in the longitudinal direction of the rails crossed, i.e. not driven grinding tools are used.

In particular, the first and / or the second adjusting mechanism of the adjusting device can each have coupling gears constructed and arranged parallel to one another, which are spaced apart from one another along a longitudinal extension of a longitudinally extending tool holder with tools arranged thereon and which via at least one torsion tube in at least one or more, in particular in all of the mutually corresponding swivel joints are coupled to one another in order to transmit a force applied via the first or the second actuator between the two corresponding, mutually opposite coupling gears, in particular in order to achieve a parallel and / or synchronous lifting and / or pivoting of the two coupling gears .

Fig. 1

in einer schematischen Prinzipdarstellung ein Schienenfahrzeug in Form eines Schleifaggregats mit einer darin verwirklichten erfindungsgemäßen Stelleinrichtung;

Fig. 2

in zwei Ansichten a) und b) prinzipiell die für eine Schienenbearbeitung, hier eine Schleifbearbeitung, erforderlichen Zustellrichtungen einer Winkeleinstellung sowie einer geradlinigen Zustellung;

Fig. 3

eine abstrahierte Funktionsskizze des Koppelgetriebes zum Verschwenken um einen virtuellen Drehpunkt, wobei in dieser Skizze der allgemeine Fall dargestellt ist, dass der erste Anlagerpunkt nicht auf der Verbindungslinie zwischen dem ersten Lagerpunkt und dem fünften Anlagerpunkt liegt, und nicht der Sonderfall, bei dem die genannten drei Punkte auf einer geraden Linie liegen.

Fig. 4

in zwei Darstellungen a) und b) in einem prinzipiellen Schaubild eine spezifische Ausführungsvariante eines Koppelgetriebes eines ersten Stellmechanismus einer erfindungsgemäßen Stelleinrichtung in zwei unterschiedlichen Stellpositionen;

Fig. 5

in zwei Darstellungen a) und b) in einem prinzipiellen Schaubild einen zweiten Stellmechanismus einer erfindungsgemäßen Stelleinrichtung in zwei unterschiedlichen Stellpositionen; und

Fig. 6

in einer Prinzipdarstellung das Zusammenfügen und Zusammenwirken von dem in Figur 4 gezeigten ersten Stellmechanismus, dem in Figur 5 dargestellten zweiten Stellmechanismus und einem Bearbeitungswerkzeug (hier Schleifbalken) in einem möglichen Ausführungsbeispiel einer erfindungsgemäßen Stelleinrichtung.

Further advantages and features of the invention emerge from the following description of a possible embodiment based on the attached figures. Show:

Fig. 1

a schematic representation of the principle of a rail vehicle in the form of a grinding unit with an actuating device according to the invention implemented therein;

Fig. 2

in two views a) and b), in principle, the infeed directions of an angle setting and a straight infeed required for a rail machining, here a grinding machining;

Fig. 3

an abstract functional sketch of the coupling mechanism for pivoting around a virtual pivot point, this sketch showing the general case that the first bearing point is not on the connecting line between the first bearing point and the fifth bearing point, and not the special case in which the three mentioned Points lie on a straight line.

Fig. 4

in two representations a) and b), in a basic diagram, a specific embodiment variant of a coupling mechanism of a first adjusting mechanism of an adjusting device according to the invention in two different adjusting positions;

Fig. 5

in two representations a) and b) in a basic diagram a second adjusting mechanism of an adjusting device according to the invention in two different adjusting positions; and

Fig. 6

in a schematic diagram of the joining and interaction of the in Figure 4 first adjusting mechanism shown in Figure 5 illustrated second adjusting mechanism and a processing tool (here grinding bar) in a possible embodiment of an adjusting device according to the invention.

In the figures, basic sketches are recorded in purely schematic representations, on the basis of which the design of an actuating device according to the invention, its mode of operation and its integration in a rail vehicle for the machining of rails in possible design variants will be explained below. In particular, the figures are not concrete Construction specifications. A person skilled in the art can, however, work out a concrete construction from the following schematic representations and with recourse to the following explanations using his specialist knowledge.

In Figure 1 a grinding unit 1 for processing rails S laid in the track is shown in a schematic side view. The grinding unit 1 has a frame 2 and rail wheels 3 arranged on the frame 2, with which it travels on the rails S laid in the track, be it self-propelled or pulled by another rail vehicle. In the sanding unit 1, a sanding beam 4 is arranged, on which rows of sanding bodies 5 are arranged offset in a turret-like arrangement, which are freely rotating about their axis of rotation and non-driven with the axis of rotation at an angle different from 90 ° obliquely to the longitudinal direction of the rail S. are. One of the rows with grinding bodies 5 arranged on the grinding beam 4 is shown as being fed onto the surface of the rail S. The sanding bar 4 can be lifted and rotated when a row of sanding bodies 5 resting on the rail S is worn in order to place a further row with fresh sanding bodies 5 on the rail S and continue the processing with this. The grinding beam 4 is suspended in an adjusting device 10 with which the grinding beam 4 and with it the processing tools in the form of the grinding bodies 5 can be positioned relative to the rail S laid in the track. The adjusting device 10 in any case has a first adjusting mechanism 11 for positioning the grinding bodies 5 with regard to an angular position relative to the rail S in a plane transverse, in particular perpendicular, to the longitudinal direction of the rail S. It can also have a second adjusting mechanism 12 for setting the distance between the grinding bodies 5 and the rail S.

These two setting parameters are in the Figure 2 once again illustrated. In Figure 2a ) the adjustable with the first adjusting mechanism 11 angular position is illustrated. With this adjusting mechanism 11, the grinding beam 4 is _{pivoted along the arrow P 1} and thus adjusted in its angular position relative to the rail S, more precisely to the rail head SK. Figure 2b ) shows the distance positioning achievable with the second adjusting mechanism 12, the along the arrow P ₂ in FIG Figure 2b ) takes place, along which the sanding bar 4 can be moved by means of the optionally available second adjusting mechanism 12 and can accordingly be moved towards or away from the rail S, more precisely the rail head SK.

In Figure 3 the basic structure of a first coupling gear 13 is shown - in a highly schematic schematic diagram - as it is used according to the invention in a first adjusting mechanism of an adjusting device according to the invention.

The first coupling gear 13 contains gear members in the form of rockers and couplings, all of which are connected to one another exclusively with swivel joints, these swivel joints each having axes of rotation that run parallel to one another and perpendicular to the plane of the drawing. In the manner according to the invention, it enables the execution of a pivoting movement of a guided member around a virtual pivot point with only a single actuator, which in particular can be in an inaccessible area, for example in a rail head. On a frame 14, which here is in particular the frame 2 of a grinding unit 1 (cf. Figure 1 ) are in the in Figure 3 The individual gear members of the coupling gear 13 are arranged as an embodiment variant shown as a schematic diagram. At a first bearing point 15, a first rocker 16 of the coupling gear 13 is arranged pivotably on the frame 14. At a second bearing point 17, which is spaced apart from the first bearing point 15, a second rocker 18 is pivotably fixed on the frame 14. A first coupling 20 is pivotably connected to the first rocker 16 at a first contact point 21 and to the second rocker at a second contact point 24. The coupling gear 13 also has a third rocker 19. This third rocker is pivotably connected to the first coupling 20 at a third contact point 25. The third attachment point 25 can lie at a distance from a straight connecting line between the first attachment point 21 and the second attachment point 24, here offset in the direction of the frame 14. Between a fourth contact point 26 formed on the third rocker 19 and one on the first rocker 16 formed fifth abutment point 23, a second coupling 22 is arranged and pivotally connected to the associated rocker 16, 19 in the respective abutment points 23, 26. In this case, the fifth abutment point 23 is further spaced from the first bearing point 15 than the first abutment point 21.

The hatching of the triangular shaped elements shown here, first rocker 16 and first coupler 20, is only intended to make it clear that these elements are coherent, rigid elements (gear members). However, these do not have to have a triangular shape, but can take any shape, such as in the Figure 3 illustrated arrangement, in particular the attachment and storage points, allowed. The further elements, which are only drawn in the form of lines, the second rocker 18, third rocker 19 and second coupling 22, can also assume other shapes, for example rod-shaped.

In the in Figure 3 It can be seen that the arrangement of the first bearing point 15, the first bearing point 21 and the fifth bearing point 23 along the first rocker 16 is out of alignment, i.e. not along a continuous straight line Line, can be made.

In the Figure 3 It can now be clearly seen that a line formed from the respective straight connecting lines starting from the first bearing point 15 via the first bearing point 21, the second bearing point 24, the second bearing point 17 and back to the first bearing point 15 results in a first parallelogram. The connecting line between the first bearing point 15 and the second bearing point 17 is shown in dashed lines for a better illustration of this first parallelogram.

It can also be seen that a line formed from the respective straight connecting lines starting from the first attachment point 21 via the third attachment point 25, the fourth attachment point 26, the fifth attachment point 23 and back to the first attachment point 21 results in a second parallelogram.

_{This configuration results in two further, a fourth and a fifth parallelogram: A line L 1} parallel to a connecting line between the first bearing point 15 and the first abutment point 21 and running through the third abutment point 25 intersects with a connecting line between the first Attachment point 21 and the third attachment point 25 parallel and running through the first bearing point (15), in Figure 3 dashed line shown in a pivot point SP. A route starting from the pivot point SP via the third attachment point 25, the first attachment point 21, the first pivot point 15 back to the pivot point SP describes a third parallelogram. A fourth parallelogram is then determined by the route starting from the pivot point via the fourth attachment point 26, the fifth attachment point 23, the first bearing point 15 back to the pivot point SP. The pivot point SP forms a corner point of both the third and the fourth parallelogram. The connecting line from the pivot point to the fourth bearing point 26 is in the Figure 3 shown in dashed lines as L2.

If the first coupling gear 13 is now moved or adjusted by pivoting the first and second rocker arms 16, 18, the third attachment point 25 moves along a circular path around the pivot point SP, and the fourth attachment point 26 also moves along a circular path the pivot point SP. Regardless of the respective pivot angle, the triangle formed by the polygon connecting the points pivot point SP, third attachment point 25, fourth attachment point 26 is always congruent, ie the distances of third 25 and fourth 26 attachment points from pivot point SP are always the same. In this way, a pivoting or rotary movement of the third rocker 19 about the pivot point SP can be obtained with the first coupling gear 13. Accordingly, a pivoting movement of a machining tool arranged on the third rocker 19 can also be realized about the pivot point SP, the tool remaining aligned radially to the rail head SK through the first coupling gear 13.

The first coupling gear 13 can now be designed in such a way that the pivot point lies within the rail head of the rail over which the rail vehicle travels and to be machined by the machining tool. In this way it can be achieved that the machining tool can be moved in an infeed direction in which it is pivoted about a pivot point located in the rail head in order to set a machining profile. It can therefore be a fixed on the third rocker 19 machining tool in a like in Figure 2a ) can be pivoted in the manner shown.

The first coupling gear 13 can be adjusted by a first actuator, for example a hydraulic ram, which is arranged at any position in the coupling gear, for example between the first rocker 16 and the first coupling 22.

In the Figures 4a) and 4b ) is a first coupling gear 13 contained in the first adjusting mechanism 11 according to the invention in one of the in Figure 3 The general form shown and explained above is illustrated in a special case deviating from the form, the two Figures 4a) and 4b ) show different setting positions of the coupling mechanism 13 and show how the above-mentioned pivoting movement about the virtual pivot point SP, which is shown here located inside the rail head SK of the rail S, can be pivoted with these different setting positions.

With regard to the general description of the first linkage 13, refer to the description of FIG Figure 3 to refer. The individual components of the in Figure 4 The coupling mechanism 13 shown are correspondingly provided with the same reference numerals as those in FIG Figure 3 shown components and are in the same relationship and with the same technical effect.

The special feature of the embodiment shown here is that the first bearing point 15, the first bearing point 21 and the fifth bearing point 23 are arranged on a straight connecting line along the first rocker 16. This measure ensures that the in general, in Figure 3 The design of the coupling mechanism 13 shown, in which the first bearing point 15, first abutment point 21 and fifth abutment point 23 do not lie on a straight connecting line, but at an angle to one another, i.e. lines L ₁ and L ₂ in the in Figure 4 The embodiment shown coincide in a single, common line L, which at the same time forms the extension of the connecting line of the third 25 and fourth 26 attachment points. This requires that a straight line laid through the abutment points 25 and 26 runs through the pivot point SP in every pivot position of the first coupling mechanism 13. This construction simplifies, in particular, a combination of the first coupling gear 13, or the first adjusting mechanism integrating it, with a second adjusting mechanism, as will be described in more detail below.

In the Figures 5a) and 5b ) shows a possible embodiment of a second adjusting mechanism 12 that can be used in an adjusting device according to the invention, it being mentioned here for clarification that the second adjusting mechanism 12, as it is shown in FIGS Figures 5a) and 5b ) is shown, represents only one possibility of providing the first adjusting mechanism in an adjusting device according to the invention with an adjustment possibility of the delivery. Even the one in the Figures 5a) and 5b ) The second adjusting mechanism 12 shown in a preferred variant is formed by a coupling gear, a second coupling gear 27, which in turn is composed of gear members in the form of rockers and couplers that are connected to one another exclusively via swivel joints that rotate about mutually parallel axes of rotation. Here, too, these axes of rotation are perpendicular to the plane of the drawing. The second coupling gear 27 has, so to speak, a frame element 28 as its base. A first rocker 30 is pivotably fixed on this frame element 28 at a first bearing point 29. At a second bearing point 31, a second rocker 32 is pivotably fixed on the frame element 28. The first rocker 30 is pivotably connected to a triangular coupling 34 at a first contact point 33, the second rocker 32 is pivotally connected to the triangular coupling 34 at a second contact point 35. First rocker 30 and second rocker 32 each point between the attachment point 29 or 31 and the attachment point 33 or 35 an equal distance. The triangular coupling 34 is pivotably connected to a guided link 37 at a first connection point 36. The first attachment point 33, the second attachment point 35 and the first connection point 36 are located on the triangular coupling 34 at the corners of an isosceles triangle with legs of equal length along the connecting lines between the first attachment point 33 and the first connection point 36 and the second attachment point 35 and the first connection point 36. In this embodiment, the two rockers, first rocker 30 and second rocker 32, and the triangular coupling 34 arranged between the two rockers 30 and 32, which are arranged on the frame element 28, form a known Roberts straight line, in which the connection point 36, which lies on a line between the bearing points 29 and 31, is guided on this connecting line along a largely straight guide line.

In order to guide not only the first connection point 36 but also the elongated guided member 37 along a straight line in the embodiment shown, a further gear part of the coupling gear 27 is connected to the Roberts straight-line guide. This consists of a third rocker 39 pivotally mounted on the frame element 28 at a third bearing point 38, a first coupling 41 pivotally connected to the third rocker 39 at a third bearing point 40, which is pivotable at the bearing point 35 with the second rocker 32 and the Triangular coupling 34 is connected and a second coupling 42 which is pivotably connected to the third coupling 39 and the first coupling 41 at the third contact point 40 and which is pivotably connected to the guided link 37 of the coupling gear 27 at a second connection point 43. These additional gear elements transmit the straight guideway of the connection point 36 obtained by the Roberts straight-line guidance to the connection point 43, so that the guided link 37 is guided as a whole along a largely straight path.

Between the guided member 37 and the frame element 28, an actuator 44, for example a hydraulic cylinder, is arranged, which has an actuating force parallel to it the straight path along which the guided member 37 is guided. A comparison of the Figures 4a) and 4b ) shows how, driven by the actuator 44 through the second coupling gear 27, a straight guidance of the guided member 37 is obtained.

In Figure 6 is finally shown schematically how the two adjusting mechanisms 11 (with one as in Figure 5 coupling gears 13) and 12 shown are connected to one another and how the grinding beam 4 is connected to the second adjusting mechanism 12 in order to realize the adjusting device 10 as a whole. It can be seen that the frame element 28 of the second adjusting mechanism 12 is firmly connected in its longitudinal direction to the third rocker 19 of the first coupling mechanism 13 of the first adjusting mechanism 11, for example welded, and that the sanding bar 4 is attached to the guided member 37 of the second adjusting mechanism 12 is determined. In this way, an overall connected structure and an adjusting device are obtained in which an angle adjustment by means of the adjusting mechanism 11 and an infeed adjustment by means of the adjusting mechanism 12 of the sanding beam 4 are possible independently of one another, so that both the infeed (the pressure) and also during a sanding process the angular position of the sanding bar 4 can be changed relative to the rail head SK, in particular also continuously. The grinding bar 4 is in particular fixed on the guided member 37 of the second coupling gear 27 so that it can be rotated about its longitudinal axis, so that the above-described turret function can be carried out.

From the above description of possible design variants it has once again become clear what advantages the design of an actuating device according to the invention brings with it.

List of reference symbols

1

Grinding unit

2

frame

3rd

Rail wheel

4th

Sanding bar

5

Grinding wheel

10

Adjusting device

11

first adjusting mechanism

12th

second adjusting mechanism

13th

first coupling gear

14th

frame

15th

first storage point

16

first swing arm

17th

second bearing point

18th

second swing arm

19th

third swing arm

20th

first coupling

21

first attachment point

22nd

second belt

23

fifth attachment point

24

second attachment point

25th

third attachment point

26th

fourth attachment point

27

second coupling gear

28

Frame element

29

first storage point

30th

first swing arm

31

second bearing point

32

second swing arm

33

first attachment point

34

Triangular coupling

35

second attachment point

36

first connection point

37

guided limb

38

third bearing point

39

third swing arm

40

third attachment point

41

first coupling

42

second belt

43

second connection point

44

Actuator

L.

line

L1

line

L2

line

P1

arrow

P2

arrow

SP

Pivot point

S.

rail

SK

Rail head

Claims (12)

Adjusting device (10) for positioning a processing tool (5) which is arranged on a frame (14) fixed on a rail vehicle (1) and has an active section for processing a rail head (SK) relative to a processing tool (5) laid in the track and overrun by the rail vehicle (1) Rail, wherein the adjusting device (10) has a first adjusting mechanism (11) for changing an angular position of the active section of the machining tool (5) seen transversely to a longitudinal direction of the rail (S) laid in the track, characterized in that the first adjusting mechanism (11) has a first coupling gear (13) and a first actuator for moving the first coupling gear (13), the first coupling gear (13) being connected to each other exclusively by means of swivel joints in the form of rockers (16, 18, 19) that are rotatable about mutually parallel axes of rotation. and coupling (20, 22) and wherein the first adjusting mechanism (11) pivots of the machining tool (5) connected to it about a virtual pivot point, particularly located in the rail head (SK) during operation, by actuating only the one first actuator. Adjusting device (10) for positioning a processing tool (5) which is arranged on a frame (14) fixed on a rail vehicle (1) and has an active section for processing a rail head (SK) relative to a processing tool (5) laid in the track and overrun by the rail vehicle (1) Rail (S), in particular according to claim 1, wherein the adjusting device (10) has a first adjusting mechanism (11) for changing an angular position of the active section of the machining tool (5) seen transversely to a longitudinal direction of the rail (S) laid in the track,
characterized in that the first adjusting mechanism (11) has a first coupling gear (13) and a first actuator for moving the first coupling gear (13), wherein the first coupling gear (13) has gear members connected to one another in the form of rocking and coupling exclusively via swivel joints that can be rotated about mutually parallel axes of rotation, wherein the first coupling gear (13) has a first rocker (16) pivotably mounted on a first bearing point (15) which is fixed in position relative to the frame (14) and a second rocker arm (16) which is fixed in position relative to the frame (14) in a second bearing point (17) has pivotably mounted rocker arm (18), wherein the first coupling gear (13) furthermore has a first coupling (20) which is connected to a first contact point (21) arranged on the first rocker arm (16) and to a second contact point (24) arranged on the second rocker arm (18) is mounted so that it can pivot relative to the associated rocker arm (16, 18), a line formed from the respective straight connecting lines starting from the first bearing point (15) via the first bearing point (21), the second bearing point (24), the second bearing point (17) and back to the first bearing point (15) results in a first parallelogram , a third attachment point (25), on which a third rocker (19) is pivotably attached, is furthermore formed on the first coupling (20) and is arranged at a distance from a connecting line between the first attachment point (21) and the second attachment point (24), wherein the first coupling mechanism (13) furthermore has a second coupling (22) which is pivotably attached to a fourth contact point (26) on the third rocker (19) arranged on the third rocker and to a fifth on the first rocker (16) arranged attachment point (23) is pivotably attached to the first rocker (16), a line formed from the respective straight connecting lines starting from the first abutment point (21) via the third abutment point (25), the fourth abutment point (26), the fifth abutment point (23) and back to the first abutment point (21) results in a second parallelogram . Adjusting device (10) according to Claim 2, characterized in that the two bearing points (15, 17) are positioned in such a way and that the positions of the bearing points (21, 23, 24, 25, 26) are selected such that an intersection point (SP ) between a line parallel to a connecting line between the first bearing point (15) and the first abutment point (21) and running through the third abutment point (25) and one to a connecting line between the first abutment point (21) and the third abutment point (25) parallel line running through the first bearing point (15) within the rail head (SK) of the rail (S) over which the rail vehicle (1) travels and to be processed by the processing tool (5), and that this intersection point (SP) and an intersection point (SP) between a line parallel to a connecting line between the first bearing point (15) and the fifth bearing point (23) and running through the fourth bearing point (26) and that to the connection The line between the first abutment point (21) and the third abutment point (25) parallel and through the first bearing point (15) coincides with the line. Adjusting device (10) according to one of Claims 2 or 3, characterized in that the first bearing point (15), the first bearing point (21) and the fifth bearing point (23) lie on a straight connecting line. Adjusting device (10) according to one of Claims 2 to 4, characterized in that the two bearing points (15, 17) are arranged on an adjusting rocker that can be detachably connected to the rail vehicle (1) and pivoted about a fastening point located between the bearing points (15, 17) are. Adjusting device (10) according to one of the preceding claims, characterized in that it has a second adjusting mechanism (12) for changing a distance between the active section of the machining tool (5) and the rail head (SK) of the rail (S) laid in the track. Adjusting device (10) according to claim 6, characterized in that the second adjusting mechanism (12) has a second coupling gear (27) with a frame element (28) fixed on the third rocker (19) of the first coupling gear (13) and a second coupling gear ( 27) having a moving second actuator (44), wherein the second coupling gear (27) has gear members in the form of rockers and couplings connected to one another exclusively via swivel joints that can be rotated about parallel axes of rotation, and the second coupling gear (27) has a first in a first Bearing point (29) pivotally attached to the frame element (28) and a second link (32) pivotally attached to a second bearing point (31) on the frame element (28) and one with the first link (30) in one first distance to the first bearing point (29) arranged first abutment point (33) and with the second rocker (32) at the first distance to the second layer Erpunkt (31) arranged second abutment point (35) pivotally connected triangular coupling (34) having Roberts straight line. Adjusting device (10) according to claim 7, characterized in that on the frame element (28) of the second coupling gear (27) in addition to the first (30) and the second (32) rocker of the Roberts straight-line guide and adjacent to the first rocker (30) a third rocker arm (39) is pivotally fixed to the Roberts straight-line guide in a third bearing point (38), the third rocker arm (39) of the second coupling gear (27) being connected to a first coupling (41) at a third bearing point (40), wherein the first coupling (41) is pivotally connected at the first bearing point (33) with the first rocker (30) and the triangular coupling (34), a connecting line connecting the third bearing point (38) and the third bearing point (40) in a straight line in the Is essentially parallel to the first rocker arm (30) of the Roberts straight line and wherein a guided link (37) of the second coupling gear (27) at a first connection point (36) with the Sp in the middle of the triangular coupling (34) is pivotably connected and in a second of the first Connection point (36) is connected to a second coupling (42) along a line running parallel to the straight guide line on which the tip of the triangular coupling (34) runs, spaced apart second connection point (43), the second coupling (42) being connected to the third attachment point (40) is pivotably connected to the third rocker (39) and the first coupling (41) of the second coupling gear (27), a connecting line between the first (33) and the third attachment point (40) being essentially parallel to is the straight path on which the tip of the triangular coupling (34) of the Roberts straight line is guided. Actuating device (10) according to Claim 8, characterized in that the second actuator (44) is arranged such that it can apply an actuating force between the frame element (28) and the guided link (37) of the second coupling gear (27). Adjusting device (10) according to one of claims 7 to 9, characterized in that the frame element (28) on the third rocker (19) of the first coupling gear (13) is fixed in such a way that the straight guide line on which the tip of the triangular coupling (34) is guided, extends essentially parallel to the first rocker (16) of the first coupling gear (13). Actuating device (10) according to one of Claims 7 to 10, characterized in that a holder (4) for the machining tool (5) is arranged on the guided link (37) of the second coupling gear (27). In a rail vehicle (1) disposed grinding unit for grinding of laid in the track rails (S) during a trip with multiple with a rotational axis transverse to a longitudinal direction of the traversed rail (S) in the grinding aggregate freely rotatably mounted grinding bodies (5), characterized that the grinding unit has an adjusting device (10) according to one of the preceding claims.

Images