GB2230546A

GB2230546A - A travelling track tamping machine comprising transversely and vertically displaceable tamping units

Info

Publication number: GB2230546A
Application number: GB9007962A
Authority: GB
Inventors: Josef Theurer
Original assignee: Franz Plasser Bahnbaumaschinen Industrie GmbH
Current assignee: Franz Plasser Bahnbaumaschinen Industrie GmbH
Priority date: 1989-04-18
Filing date: 1990-04-09
Publication date: 1990-10-24
Anticipated expiration: 2010-04-09
Also published as: NL193696C; JP2925234B2; GB9007962D0; SE508417C2; SK278889B6; CN1016626B; CZ279363B6; SE9001189L; CS9001904A2; CH685059A5; FI95065C; DE4001488A1; SE9001189D0; GB2230546B; AT392810B; NL193696B; FI95065B; ES2024163A6; DE4001488C2; SU1762763A3

Description

0 1 A travellin.7 track tamping machine comprising transversely and

vertically displaceable tamping units This invention relates to a travelling track tamping machine comprising a machine frame supported by undercarriages and a tool frame mounted to pivot laterally parallel to the plane of the track about a vertical axis and further comprising tamping units which are arranged adjacent one another transversely of the track, being designed for transverse and vertical displacement independently of one another under the power of drives, and which comprise pairs of tamping tools designed to be squeezed and vibrated by drives and incorporating tamping tines designed to penetrate into the ballast.

one already known travelling track tamping machine (cf. applicants' or patentees' US 3534 687 embodying the features described above comprises two tamping tool car riers which are arranged on such a tool frame mounted for lateral pivoting and overhanging freely in the working direction and which each carry two tamping units arranged one behind the other longitudinally of the track, together with the correcting arrangement, for simultaneously tamping two adjacent sleepers. Each tamping unit comprises pairs of tamping tools which are designed to be vertically displaced and squeezed together and also vibrated under the power of drives and which comprise tamping tines designed to penetrate into the ballast on the left and right of one or the other rail. The two carriers are mounted for trans verse displacement independently of one another under the power of drives on the tool frame which is designed to pivot laterally about a vertical axis relative to the machine frame. This known track tamping machine with its compact construction typical of older machines, in which the tamping units are overhangingly arranged on the machine frame or rather the laterally pivotal tool carrier, is also and in particular designed to function as a levelling and tamping machine for tamping switches and the like with the individual tamping tools designed to pivot independently of 2 one another in conjunction with a reference system.

In another known track tamping machine (cf. GB 1,213,381) of the older compact type, the tamping units are overhangingly arranged on a tool frame designed to pivot laterally relative to the machine frame, a total of two vertically displaceable tamping units each associated with a rail being arranged for transverse displacement independently of one another. The tamping units are mounted for vertical and transverse displacement in a transverse displacement path on the elongate tool frame which overhangs the leading undercarriage of the machine and which is designed to pivot laterally relative to the machine frame about a vertical axis, so that the tamping tools can be better adapted to changing inter-rail intervals in switches. This construction is complicated because the laterally pivotal tool frame extends to the rear over the entire machine frame and is fixed there to the machine frame via a sliding bearing for the pivoting movement. In addition, there is the disadvantage of inaccurate centring of all the pivotal tamping tools over the sleeper to be tamped because the axis of rotation of the tool f rame is arranged at a distance f rom the centre of the transverse displacement path. More particularly, this spaced arrangement gives rise to the disadvantage that, due to such inaccurate adaptation, the tamping tools cannot be positioned parallel to an oblique sleeper so that accurate and durable tamping is not possible.

Another known travelling track tamping machine (cf. applicantst or patentees' GB 2 148 361 is in the form of a tamping, levelling and lining machine of the so-called compact type. These machines have been particularly successful over the last twenty years compared with machines of the described overhanging type because the arrangement of the tamping units and the track lifting and lining unit between the undercarriages spaced far apart from one 3 is another provides for considerably more accurate correction of the vertical and lateral position of the track, in addition to which the arrangement of the undercarriages at a relatively large distance apart from one another provides for gentle curvature of the rails and avoids excessive flexural stressing. In this known tamping machine, a separate tool frame - with a tamping, lifting and lining unit pivotally connected to the tool frame at one end by a variable-length coupling mechanism is provided for each rail, each laterally pivotal tool frame comprising at its other end opposite the coupling a single supporting and guiding undercarriage in the form of a free steering undercarriage designed to travel on a rail. The tamping, lifting and lining units are in the form of so-called switch units comprising laterally pivotal tamping tools, pincer-type lifting tools and flanged lining rollers for working on track switches and the like.

Applicants' or patenteesf GB 2 148 988 relates to a track tamping machine comprising a tamping unit of the modern type consisting of two tamping units which are each associated with a rail, being designed for independent transverse displacement under the power of drives, and each of which comprises two pairs of tamping tools penetrating into the ballast on the left or right of a rail. To create separate tamping unit assemblies, each pair of tamping tools is designed for independent vertical displacement so that, even in difficult switches with a track obstacle at the side of a rail, the opposite tamping unit assembly can be lowered for unimpeded tamping.

In addition, GB- 2 201 178 A describes a track tamping machine of the overhanging type comprising four tamping units designed for vertical and transverse displacement independently of one another under the power of their own drives. This machine of the overhanging type is not equipped with lifting and lining units for positional 4 correction of the track. As described in GB 1 318 912 and, in particular, in the preamble of claim 1 of GB 2 035, the displaceable tamping units in question are associated in pairs with a rail, all four tamping units vertically displaceable independently of one another being designed for transverse displacement independently of one another under the power of their own drives on a guide frame arrangement provided on the machine frame. This known arrangement of, in all, four independently vertically and transversely displaceable tamping unit assemblies with a pair of tamping tools for penetration into the ballast on the left or right of one or the other rail enables a relatively wide area of switches to be covered, but does not fully satisfy the very stringent demands on the accuracy of the positional correction to the track, particularly in cases where the sleeper intervals vary or the sleepers are lying obliquely.

Now, the problem addressed by the present invention was to provide a travelling track tamping machine of the type described at the beginning which could be used in particular on difficult sections of track, for example at switches or even on tracks with obliquely lying sleepers or with often different sleeper intervals and with which the tamping tools could be rapidly, simply and accurately adapted for penetration into the ballast bed.

According to the invention, this problem was solved by a travelling track tamping machine of the type described at the beginning in that, out of a total of four tamping unit assemblies arranged adjacent one another transversely of the track and designed for independent vertical displacement under the power of their drives - each with a pair of tamping tools with tamping tines designed to penetrate into the ballast on the left or right of one or the other rail, at least the two outer tamping unit assemblies are mounted for transverse displacement with their vertical displace- 1 ment drives on pivotal tool frames which are designed to pivot.laterally relative to the machine frame about vertical axes independently of one another under the power of their own drives.

With this surprisingly simple, but very robust new basic construction, the problems attending the tamping unit assemblies designed for displacement independently of one another in regard to their arrangement and their independent displacement are solved by a simple, but very effective construction, the particular advantages of continuous tamping, even of difficult switches, afforded by the arrangement of these four individual tamping unit assemblies being retained and, in regard to sleeper adaptation, even improved. The special, transversely pivotal mounting of at least the outer tamping unit assemblies on their own pivotal tool frames establishes a mechanically very strong and structurally simple connection to the machine frame, the separate tool frame and transverse pivoting drive further increasing the independence of the individual tamping unit assemblies from one another for controlled and individual adaptation to the particular track obstacles. The design of at least the two outer tamping unit assemblies for independent lateral pivoting provides for rapid and unimpeded adaptation and centring of the tamping tools for tamping even those sleeper bearing surfaces of a switch section which are situated in the branch track and are still joined to the main track by the common long sleepers. This solution provides the machine operator with a particularly good view of, and hence with effective control of, the overall arrangement of the tamping unit assemblies both during centring and during the penetration and squeezing phase. Another particular structural simplification is that this highly advantageous lateral pivoting of the outer tamping units does not involve any transverse guides and associated mountings connected to the machine frame and 6 projecting far beyond the clearance profile. Because they are f ixed to a pivotal tool frame, the two outer tamping unit assemblies can rapidly be lowered back within the clearance profile without difficulty.

In one particularly advantageous embodiment of the invention, the two outer tamping unit assemblies are mounted at the ends of their pivotal tool frames, each of the elongate pivotal tool frames being additionally supported by a horizontal slide or guide path of the machine frame in the region adjoining the outer tamping unit assembly. This elongate and overhanging design of the pivotal tool frames creates a relatively wide overall lateral displacement range of the associated tamping unit assembly for simple, problem-free and uninterrupted tamping of both the main track and the branch track, the fact that each pivotal tool frame is supported by the slide and guide path ensuring safe support of the tamping unit assembly in any pivotal position. The arrangement of the of the tamping unit assemblies at the end of the pivotal tool frame affords the particular advantage that the end zone opposite the coupling with each of the outer tamping unit assemblies can clearly be seen for rapid and accurate centring and observation of the particular pair of tamping tools. This is of particular importance for the tamping of switches where there are various track obstacles, such as guide rails, connecting rods, etc., because the operator has to work with particular concentration in such difficult parts of a track as these in order to avoid damage to the track.

A very practical and advantageous embodiment of the invention is characterized in that each of the two elongate pivotal tool frames which overhang freely immediately in front of an undercarriage in the working direction is arranged to pivot out laterally with its outer tamping unit assembly from the particular inner tamping unit assembly 7 is about a vertical axis extending substantially over one or the other rail. By virtue of this freely overhanging and elongate construction of the two pivotal tool frames, the outer tamping unit assemblies can be laterally displaced over a relatively wide overall displacement range, especially for simple and uninterrupted tamping of areas situated adjacent the track, particularly branch tracks. The provision of two axes for the pivotal tool frames enables them to be simply designed and mounted without any mutual interference.

In another advantageous embodiment of the invention, the two inner tamping unit assemblies arranged between the outer tamping unit assemblies are arranged with their vertical displacement drives on the machine frame or on a tool carrier connected thereto. This arrangement of the two inner tamping unit assemblies independently of the outer tamping unit assemblies has the advantage that the outer tamping unit assemblies intended for tamping the outermost sections of track, particularly the branch tracks, can readily be displaced or rather centred together with the pivotal tool frame over a very wide displacement range independently of the inner tamping unit assemblies. At the same time, the inner tamping unit assemblies may advantageously be used as before in the middle part of the track. The arrangement on the machine frame or on a separate tool frame may advantageously be adapted for working on switches and/or plain track, depending on the type of machine, irrespective of the outer tamping unit assemblies. The different arrangement of the tamping unit assemblies also has the advantage that their weight is distributed between two different sections of the machine frame.

In another advantageous and practical embodiment of the invention, the two inner tamping unit assemblies arranged on the machine frame or tool carrier between the a two pivotal tool frames or outer tamping unit assemblies, together with their vertical displacement drives, are designed for transverse displacement independently of one another relative to the machine frame on transverse guides under the power of their own drives. By virtue of this mounting, the inner tamping unit assemblies may readily be transversely displaced independently both of one another and of the two outer tamping unit assemblies for corresponding rapid and exact adaptation or rather centring to track obstacles. At the same time, the transverse guides may readily be arranged within the clearance profile, even for a very wide displacement range, without interfering with the outer tamping unit assemblies each connected to a pivotal tool frame. This different mounting of the outer and inner tamping unit assemblies also has the advantage of relieving the transverse guides of the relatively high resistance forces attributable to the penetration of the tamping tines into the ballast.

In one particularly preferred embodiment of the invention, the tool carrier with the two tamping unit assemblies designed for displacement independently of one another - preferably together with the transverse guides and the two transverse displacement drives - are mounted on the machine frame for rotation parallel to the plane of the track about a vertical axis which extends in the transverse vertical plane - passing through the tamping unit assemblies - and through the longitudinal axis of the machine.

This rotatable mounting of the tool carrier has the particular advantage that the two inner tamping unit assemblies are additionally rotatable about a vertical axis while retaining their independent transverse displaceability. In this way, the tamping tines of the inner tamping unit assemblies, with very little extra design effort, may advantageously be aligned parallel to obliquely lying sleepers and, at the same time, may also be centred exactly 9 over the sleeper to be tamped by corresponding transverse displacement. By contrast, the areas situated further from the axis of the track and, more particularly, extending into the branch track are treated by the outer tamping unit assemblies by lateral pivoting of the pivotal tool frames in accordance with the particular position of the sleeper or rail. In this way, even the most difficult switches comprising a number of various track obstacles, particularly in the form of switch blades, can rapidly be tamped or rather corrected with uniform tamping quality. In addition, this special arrangement of the inner tamping unit assemblies without their own pivotal tool frames provides for substantially independent or unimpeded or rather simpler arrangement of the two pivotal tool frames connected to the outer tamping unit assemblies.

In another advantageous embodiment of the invention, each laterally pivotal outer tamping unit assembly and the associated inner tamping unit assembly are overhangingly arranged transversely of the track on their sides remote from one another, are substantially in line on their sides facing one another and are arranged in mirror-image relationship to one another relative to the plane of symmetry of the particular rail. This special asymmetrical construction advantageously provides for the immediately adjacent - very close - arrangement of an outer and an inner tamping unit assembly for particularly advantageous observation by the operator and for unimpeded and uninterrupted tamping of a rail-sleeper crossover.

In one particularly practical and advantageous embodiment of the invention, each of the two pivotal tool frames connected to an outer tamping unit assembly and preferably recessed or angled parallel to the plane of the track has a length of at least about 4 to 5 metres or approximately two to three and a half times the gauge of the track from its vertical axis to the particular outer tamping unit assembly and is preferably designed for an overall pivoting range of the particular tamping unit assembly of about 1.7 metres under the power of its particular drive. This particularly elongate design of the two pivotal tool frames provides for the relatively wide overall pivoting range of the outer tamping unit assemblies without any technical difficulties, more particularly with solid support on the machine frame. In addition, a further advantage is the favourable support within the machine frame which avoids the need for time-consuming and labour- intensive rerigging work. At the same time, a maximum displacement or pivoting angle range can be obtained for each tool frame, even - and in particular - in cases where sleepers are lying at a relatively pronounced oblique angle.

In another particularly preferred embodiment of the invention, the vertical axis of each pivotal tool frame is arranged - in the working direction - behind the middle axle of the undercarriage immediately following the outer and inner tamping unit assemblies or behind the central undercarriage - preferably in the form of a bogie and immediately adjacent the tamping unit assemblies - of a pivotal machine frame. This arrangement advantageously provides for particularly stable support of the supporting tool frame on the central undercarriage where, as a bogie, the weight of the tool frames and tamping unit assemblies is distributed between two axles. In addition, the pivotal construction of the machine frame enables the driver's cabin to be shifted from the central undercarriage for a completely unimpeded arrangement and construction of the two pivotal tool frames and the associated drives.

In another advantageous embodiment of the invention, the two outer tamping unit assemblies with their vertical displacement drives are mounted for rotation about another vertical axis at that end of the pivotal tool frame opposite the vertical axis and are each connected to a drive 11 is f or rotation towards the track axis or towards the particular inner tamping unit assembly. This double articulation of the pivotal tool frame provides for very extensive adaptation even to difficult switch sections to be tamped with no loss of the above-mentioned advantages of independent lateral pivoting of the outer tamping unit assemblies. By means of the second vertical axis, the tamping tines can readily be aligned into a position parallel to the longitudinal axis of obliquely lying sleepers, irrespective of the lateral position of the outer tamping unit assembly obtainable through the first vertical axis - for exact centring over the sleeper bearing surface to be tamped. In this way, even obliquely lying sleepers which, basically, are more difficult to tamp because of various track obstacles can be tamped more quickly, accurately and uniformly, particularly in conjunction with the inner tamping unit assemblies. It is an advantage in this regard that this double articulation of the pivotal tool frame involves very little extra design effort.

Another embodiment of the invention is characterized in that each elongate pivotal tool frame is arranged overhangingly from its vertical axis in the working direction) and, at its free end, is pivotally connected to the outer tamping unit assembly preferably immediately adjacent the slide or guide path. The arrangement of the outer tamping unit assemblies at the free end of the projecting pivotal tool frame has the advantage that the operator is given a better and substantially unimpeded view of and hence control of the outer tamping unit assemblies for rapid and exact centring thereof, particularly over the switch section lying outside the track. In addition, the arrangement of the slide or guide path immediately adjacent the tamping unit assemblies provides for particularly solid support of the tamping unit assemblies, relieving the load on the pivotal tool frames.

12 one particularly advantageous embodiment of the invention is characterized in that each of the two elongate pivotal tool frames is in several parts and, more particularly, is designed to be telescopically extended longitudinally of the frame and is connected to its.own drive for longitudinal displacement of the outer tamping unit assembly mounted on the end of the tool frame. This extendable construction of the pivotal tool frames readily provides for independent longitudinal displacement of each outer tamping unit assembly for the exact centring or adaptation thereof over a sleeper laid at a different sleeper interval or, more particularly, over an obliquely lying sleeper. The telescopic design enables the length of the tool frame to be readily altered for substantially the same stability.

In addition, in another advantageous embodiment of the invention, each of the two elongate pivotal tool frames connected to the outer tamping unit assemblies is in the form of a girder which is preferably designed to be telescopically extended longitudinally of the frame, extending vertically in cross-section, and which comprises hydraulic drives arranged at its upper end. This construction of the pivotal tool frame as a vertical girder has the advantage of high flexural rigidity, the arrangement of the hydraulic drives at the upper end of the girder ensuring that the two pivotal tool frames do not interfere with one another.

In another particularly advantageous and practical embodiment of the invention, the two pivotal tool frames connected to the outer tamping unit assemblies - with their vertical axes, their displacement drives and displacement ranges - and the two inner tamping unit assemblies - with their displacement drives - are arranged in mirror-image relationship to one another relative to the longitudinal axis of the 'machine. This mirror-image arrangement not only affords the advantage of rapid and easy operation of the tamping unit assemblies, it also provides for substan- 13 tially uniform load distribution over the machine frame. In addition, the same working range of, in particular, the two outer tamping unit assemblies is guaranteed for both longitudinal sides of the machine.

Another particularly advantageous embodiment of the invention is characterized in that, to form a compact track tamping, levelling and lining machine, the two outer tamping unit assemblies designed to pivot or rotate laterally parallel to the plane of the track with their respective pivotal tool frames are arranged together with the preferably transversely displaceable and rotatable inner tamping unit assemblies immediately behind - in the working direction - a track lifting and lining unit provided on the machine frame and designed for use at switches and, together with the rack lifting and lining unit, are arranged between two undercarriages, more particularly in the form of bogies, arranged far apart from one another. This advantageous arrangement of the outer and inner tamping unit assemblies and the track lifting and lining unit between the undercarriages spaced far apart from one another provides for highperformance tamping of even difficult sections of track with an accurate track position and avoids excessively high flexural stressing of the rails. In addition, the end undercarriages delimit the section of track to be corrected for an exact lateral and vertical position.

In one preferred embodiment of the invention, a lifting assembly preceding the track lifting and lining unit in the working direction and designed for use as required on the left-hand or right-hand branch track, i.e. for additional lateral pivoting, is associated with the two outer tamping unit assemblies designed to pivot laterally independently of one another with their respective pivotal tool frames and with the two inner tamping unit assemblies designed for transverse displacement independently of one 14 another and preferably for rotation together with one another. The laterally pivotal outer tamping unit assemblies specially designed for the tamping of branch tracks or the like, in conjunction with the additional lifting assembly, enables the switch section to be accurately lifted over its entire cross-section so that even the outer switch sections can be tamped with the same quality by the laterally pivotal outer tamping unit assemblies. In addition, the machine's own track lifting and lining unit is relieved of load.

Finally, in another advantageous embodiment of the invention, an operatorts cabin preceding the two pivotal tool frames and the tool carrier in the working direction and arranged within sight of the track lifting and lining unit and the additional lifting assembly, with a seat and control console facing against the working direction, is associated with the two outer and two inner tamping unit assemblies. By virtue of this arrangement, the outer and inner tamping unit assemblies, which are designed for individual centring through their independent transverse displaceability, are easier to see and can be better controlled with precision in conjunction with safer lifting of the track by the track lifting and lining unit, providing overall for more economical use of a machine constructed in accordance with the invention.

One example of embodiment of the invention is described by way of example in the following with reference to the accompanying drawings, wherein:

Figure 1 is a side elevation of a track tamping, levelling and lining machine according to the invention comprising outer tamping unit assemblies mounted on two overhanging tool frames pivotal laterally about a vertical axis independently of one another and two inner tamping unit assemblies mounted on a tool carrier connected to the machine frame and designed for transverse displacement independently of one another.

Figure 2 is a plan view of the track tamping machine shown in Figure 1, an outer tamping unit assembly together with the corresponding pivotal tool frame being laterally raised for tamping a switch section.

Figure 3 is an enlarged cross-section through the tamping machine on the line III-III in Figures 2 and 5.

Figure 4 is an enlarged side elevation of part of the outer tamping unit assembly connected to the pivotal tool frame shown in Figure 1.

Figure 5 is an enlarged plan view of part of the two pivotal tool frames each connected to an outer tamping unit assembly and designed for independent lateral pivoting under the power of their own drives and the inner tamping unit assemblies shown in Figure 2 which are connected to their own tool carriers and which are designed for transverse displacement independently of one another and for rotation with one another.

The track tamping, levelling and lining machine 1 shown in Figures 1 and 2 is designed to travel on two bogie-type undercarriages 2 and a single-axle undercarriage 3 along a track 7 consisting of sleepers 4 and rails 5, 6 under the power of an axle drive 8. An elongate machine frame 9 with driver's cabins 10 at either end and a central power supply system 11 is designed to pivot about a vertical axis 12. A levelling and lining reference system 13 consisting of feeler rollers and stretched wires is provided for detecting errors in the position of the track. As shown in Figure 2 in particular, the tamping units are formed by a total of four tamping unit assemblies 14 to 17 which are arranged adjacent one another transversely of the track and each of which comprises a pair of tamping tools 18 to 21 designed to penetrate into the ballast bed on the left or right of one or the other rail 5,6. Of these four tamping unit assemblies 14 to 17, the two outer tamping 16 unit assemblies 14 and 17 are mounted for transverse displacement on pivotal tool frames 26,27 which are designed to pivot laterally about a vertical axis 24,25 relative to the machine frame 9 independently of one another under the power of their own drives 22,23. The two inner tamping unit assemblies 15,16 arranged between the outer tamping unit assemblies 14,17 are arranged with their vertical displacement drives on a tool carrier 28 connected to the machine frame 9. To form the compact track tamping, levelling and lining machine 1, the tamping unit assemblies 14 to 17 designed for transverse displacement independently of one another are arranged immediately behind - in the working direction indicated by an arrow 29 - a track lifting and lining unit 31, which is mounted on the machine frame 9 and is designed for use at switches, being designed to travel along the track 7 on flanged rollers 30, and is arranged together with the track lifting and lining unit 31 between the two bogie-type undercarriages 2 spaced far apart from one another. An additionally laterally pivotal lifting assembly 32 designed for use as required on the left-hand or right-hand branch track is associated with the track lifting and lining unit 31 in the working direction. An operator's cabin 33 with a seat and control console 34 facing against the working direction is arranged within sight of the tamping unit assemblies 14,15,16,17, the track lifting and lining unit 31 and the lifting assembly 32. As shown in Figure 2, both the outer tamping unit assembly 17 and also the lifting assembly 32 are arranged over a branch track 37 consisting of rails 35,36.

As shown in Figure 3, one outer tamping unit assembly 17 is centred over the outer rail 36 of the branch track 37 while the opposite outer tamping unit assembly 14 of the inner tamping unit assembly 15 is arranged opposite for simultaneous tamping of the sleepers connected to the rail 6 of the main track 7. The other inner tamping unit 17 assembly 16 is centred over the inner rail 35 of the branch track 37. Each pair of tamping tools 18,19,20 and 21 designed to be squeezed and vibrated by drives comprises four tamping tines 38,39 facing one another longitudinally of the machine or track for penetration into the ballast bed. The tamping unit assemblies 14 to 17 are arranged overhanging transversely of the track on the sides remote from one another, are substantially in line on the sides facing one another and are arranged in mirror image relationship to one another relative to the plane of symmetry of the particular rail. The tool carrier 28, which is mounted on the machine frame 9 for rotation about its vertical axis 41 under the power of drives 40, is connected to transverse guides 42 which extend transversely of the longitudinal axis of the machine and on which unit frames 45,46 are mounted for transverse displacement, being provided with transverse displacement drives 43,44 and designed for the vertically displaceable mounting of the inner tamping unit assemblies 15,16. Drives 47,48 are provided for the independent transverse displacement of the two inner tamping unit assemblies 15,16. The track lifting and lining unit 31, which is provided with vertical displacement and lining drives and which is designed to run along the track, comprises laterally and vertically adjustable lifting hooks 49 and lifting rollers 50 which are designed to be brought into engagement with the rails 5,6 of the track 7. The additional lifting assembly 32 is also designed to run along the rail 36 of the branch track 37 on double flanged rollers and is connected to laterally pivotal lifting rollers 51 designed for application to the rail 36. The lifting rollers 51 are mounted on a support frame 52 which in turn is connected by a cable 53 to a drive 54 of a telescopic support 55. Another drive 56 is connected at one end to the telescopic support 55 and at its other end to a jib arm 57 designed to rotate about a vertical axis under 18 is the power of its own rotation drive. A guide roller 58 is arranged at the free end of the telescopic support 55.

As shown in Figure 4, the vertical axis 24,25 of each pivotal tool frame 26,27 is arranged - longitudinally of the track - behind a central axis 59 of the bogie-type undercarriage 2 immediately following the outer and inner tamping unit assemblies 14 to 17. Each pivotal tool frame 26,27 is overhangingly arranged from its vertical axis 24,25 in the working direction and, at its free end, is pivotally connected to the outer tamping unit assemblies 14 and 17 in the region of a slide or guide path 60.

As shown in particular in Figures 4 and 5, the two outer tamping unit assemblies 14,17 are each mounted for rotation about another vertical axis 61,62 at that end of the pivotal tool frame 26,27 opposite the vertical axis 24,25 and are each connected to a drive 64,65 for rotation towards the longitudinal axis 63 of the track or machine and towards the particular inner tamping unit assembly 15,16. The two pairs of tamping tools 18,21 of the two outer tamping unit assemblies 14 and 17 are mounted on unit frames 67,68 for vertical displacement under the power of vertical displacement drives 66. Each of the two pivotal tool frames 26, 27 is designed to extend telescopically longitudinally of the frame and is connected to its own drive 69,70 for the longitudinal displacement of the outer tamping unit assembly 14,17 mounted on the end 71 of the tool frame. The pivotal tool frame 26,27 in the form of vertical girders with an outer girder 72 and an inner girder 73 mounted for longitudinal displacement therein are recessed outwards or angled in the vicinity of the tamping unit assemblies 14 and 17 and, with their vertical axes 24,25, their displacement drives 22,23,64,65,69,70 and displacement paths, are arranged in mirror image relationship relative to the longitudinal axis 63 of the machine. The length of each pivotal tool frame 26,27 from the particular 19 vertical axis 24,25 to the corresponding outer tamping unit assembly 14 or 17 is at least about four to five metres or two to three and half times the track gauge. The total pivoting range a (Figure 5) of the particular outer tamping unit assembly 14,17 or end 71 of the tool frame from the innermost to the outermost position is at least about 1.7 M. The total lateral displacement path which each outer tamping unit assembly 14, 17 is able to cover under the power of the two drives 22,64 or 23,65 is at least about 2 m. However, this total displacement path can be made even larger by corresponding transverse displacement of the adjacent inner tamping unit assembly transversely of the machine (axis 63).

As shown in Figures 4 and 5, the two inner tamping unit assemblies 15,16 arranged with their vertical displacement drives 43,44 on the tool carrier 28 between the two pivotal tool frames 26,27 are each designed for independent transverse displacement relative to the machine frame 9 on the two transverse guides 42 under the power of their own drives 47,48. The tool carrier 28 with the two inner tamping unit assemblies 15,16 and the two transverse guides 42 is mounted on the machine frame 9 for rotation parallel to the plane of the track about the vertical axis 41 which extends in the transverse vertical plane 74 passing through the tamping unit assemblies 14 to 17 - and through the longitudinal axis 63 of the machine under the power of the drives 40. For this rotational movement, cross girders 75 connected to the transverse guides 42 rest on arcuate bearing/guide segments 76 connected to the machine frame 9. Guide rollers 77 are connected to the cross girders 75 for application to the arcuate inside of the bearing/guide segments 76. The two cross girders 75 of the tool carrier 28 are pivotally connected at one end to the bearing/guide segments 76 and to the machine frame 9 and, at their other end, to a central girder 78. The total pivoting angle of the tool support 28, together with the two inner tamping unit assemblies 15,16, about the vertical axis 41 is approximately 17.

The mode of operation of the track tamping, levelling and lining machine 1 according to the invention is described in detail in the following with reference to Figures 1 to 5.

For tamping a section of plain track, the tool carrier 28 is rotated about the vertical axis 41 under the power of the drive 40 until the longitudinal axes of the transverse guides 42 extend perpendicularly to the longitudinal axis 63 of the machine. By activation of the two drives 47,48, the two unit frames 45,46 are transversely displaced so that the associated pairs 19,20 of tamping tools of the two inner tamping unit assemblies 15,16 are each situated on the inside of the two rails 5,6. By activation of the two drives 22,23, the two outer tamping unit assemblies 14 and 17 are laterally displaced together with the two pivotal tool frames 26,27 until the associated pairs 18,21 of tamping tools are situated on the outside of each rail 5,6. By activation of the vertical displacement drives 66 and 43,44, the pairs 18 to 21 of tamping tools are then lowered into the ballast for tamping. When the branch track 37 is reached during the step-by-step advance, the sleeper is tamped both in the region of the two rails 5 and 6 of the main track and in the region of the two switch blades or rails 35,36 of the branch track 37. To this end, the outer tamping unit assembly 17, after tamping of the sleeper in the outer region of the rail 5 of the main track 7, is pivoted together with the associated pivotal tool frame 27 into the position shown in solid lines in Figure 2 by activation of the drive 23. During this pivoting movement, the tamping unit assembly 17 is rotated about the vertical axis 62 by activation of the drive 65, so that the tamping tines 38,39 are aligned parallel to the longitudinal axis 11 21 is of the sleeper 4 lying obliquely in this switch section. The opposite outer tamping unit assembly 14 is also adapted to the obliquely lying sleeper in the same way by corresponding activation of the drives 64. The tamping tines 38,39 of the inner tamping unit assemblies 15,16 are adapted by corresponding rotation of the tool carrier 28 about the vertical axis 41 under the power of the two drives 40 (cf. in particular Figure 5). By corresponding activation of the two drives 47,48, the two unit frames 45,46 are then transversely displaced until the two inner tamping unit assemblies 15,16 are situated over the region of the rails 6 or 35 to be tamped. At the same time, the lifting rollers 51 are brought into engagement with the rail 36 so that the additional lifting assembly 32 is formlockingly connected to the branch track 37. Before any tamping is carried out, the track 7 together with the branch track 37 is raised by activation of the vertical displacement and lining drives of the track lifting and lining unit 31 and the drive 5,1 of the lifting assembly 32 (see the three arrows in Figure 3) and brought into the correct set position with the aid of the lining and levelling reference system 13. At the same time, the pairs 18 to 21 of tamping tools previously centred over the tamping zone are lowered to tamp the raised switch section. The outer tamping unit assembly 17 is then briefly displaced in the transverse direction with the track still raised until the associated tamping tines 38,39 are situated on the opposite side of the rail (cf. the tamping tines represented by relatively faint dots in Figure 5). Similarly, the sleeper bearing surface situated between the inner switch blade and the rail 5 is tamped by corresponding transverse displacement of the inner tamping unit assembly 16 along the transverse guides 42. After all four tamping unit assemblies 14 to 17 have been lifted, the machine 1 advances to the next sleeper 4 where the described tamping operation begins again in the same way.

22

Claims

1. A travelling track tamping machine comprising a machine frame supported by undercarriages and a tool frame mounted to pivot laterally parallel to the plane of the track about a vertical axis and further comprising tamping units which are arranged adjacent one another transversely of the track, being designed for transverse and vertical displacement independently of one another under the power of drives, and which comprise pairs of tamping tools de signed to be squeezed and vibrated by drives and incorpor ating tamping tines designed to penetrate into the ballast, characterized in that, out of a total of four tamping unit assemblies arranged adjacent one another transversely of the track and designed for independent vertical displacement under the power of their drives - each with a pair of tamping tools with tamping tines designed to penetrate into the ballast on the left or right of one or the other rail F at least the two outer tamping unitassemblies are mounted for transverse displacement with their vertical displacement drives on pivotal tool frames which are designed to pivot laterally relative to the machine frame about vertical axes indepen dently of one another under the power of their own drives

2. A machine as claimed in claim 1, characterized in that the two outer tamping unit assemblies are mounted at the ends of their pivotal tool frames, each of beina additionallv the elongate pivotal tool frames supported by a horizontal slide or guide path of the machine frame in the region adjoining the outer tamping unit assembly

3. A machine as claimed in claim 1 or 2, characterized in that each of the two elongate pivotal tool frames which overhang freely immediately in front of an undercar- E 23 riage in the working direction is arranged to pivot out laterally with its outer tamping unit assembly from the particular inner tamping unit assembly about a vertical axis extending substantially over one or the other rail

4. A machine as claimed in claim 1, 2 or 3, characterized in that the two inner tamping unit assemblies arranged between the outer tamping unit assemblies are arranged with their vertical displacement drives on the machine frame or on a tool carrier connected thereto.

5. A machine as claimed in claim 4, characterized in that the two inner tamping unit assemblies the machine frame or tool carrier is arranged on between the two pivotal tool frames or outer tamping unit assem blies together with their vertical displacement drives are designed for transverse displacement independently of one another relative to the machine frame on transverse guides under the power of their own drives

6. A machine as claimed in claim 4 or 5, characterized in that the tool carrier with the two tamping unit assemblies designed for displacement independently of one another - preferably together with the transverse guides and the two transverse displacement drives - are mounted on the machine frame for rotation parallel to the plane of the track about a vertical axis which extends in the transverse vertical plane passing through the tamping unit assemblies - and through the longitudinal axis of the machine under the power of a separate drive

7. A machine as claimed in any of claims 1 to 6, charac terized in that each laterally pivotal outer tamping unit assembly assembly and the associated inner tamping unit are overhangingly arranged transversely of 24 the track on their sides remote from one another, are substantially in line on their sides facing one another and are arranged in mirror-image relationship to one another relative to the plane of symmetry of the particular rail.

8. A machine as claimed in any of claims 1 to 7, charac terized in that each of the two pivotal tool frames connected to an outer tamping unit assembly and preferably recessed or angled parallel to the plane of the track has a length of at least about 4 to 5 metres or approximately two to three and a half times the gauge of the track from its vertical axis to the particular outer tamping unit assembly and is preferably designed for an overall pivoting range of the particular tamping unit assembly of about 1.7 metres under the power of its particular drive

9. A machine as claimed in any of claims 1 to 8, charac terized in that the vertical axis of each pivotal tool frame is arranged - in the working direction - behind the middle axle of the undercarriage immediate ly following the outer and inner tamping unit assemblies or behind the central undercarriage preferab ly in the form of a bogie and immediately adjacent the tamping unit assemblies frame

10. A machine as claimed in any of claims 1 to 9, charac terized in that the two outer tamping unit assemblies with their vertical displacement drives are mounted for rotation about another vertical axis at that end of the pivotal tool f rame opposite the vertical axis and are each connected to a drive for rotation towards the track axis or towards the particular inner tamping unit assembly

11. A machine as claimed in claim 10, characterized in that each elongate pivotal tool frame overhangingly from its vertical axis - of a pivotal machine is arranged in the working direction and, at its free end, is pivotally connected to the outer tamping unit assembly 1 preferably im- mediately adjacent the slide or guide path

12. A machine as claimed in any of claims 1 to 11, charac terized in that each of the two elongate pivotal tool frames is in several parts and, more particularly, is designed to be telescopically extended longitudinally of the frame and is connected to its own drive for longitudinal displacement of the outer tamping unit assemb ly mounted on the end of the tool frame.

13. A machine as claimed in any of claims 1 to 12, charac terized in that each of the two elongate pivotal tool frames connected to the outer tamping unit as semblies is in the f orm of a girder which is preferably designed to be telescopically extended lon gitudinally of the frame, extending vertically in cross section, and which comprises hydraulic drives arranged at its upper end.

14. A machine as claimed in any of claims 1 to 13, charac terized in that the two pivotal tool frames con nected to the outer tamping unit assemblies - with their vertical axes.. their displacement drives and displacement ranges - and the two inner tamping unit assemblies - with their dis placement drives - are arranged in mirror-image relationship to one another relative to the longitudinal axis of the machine.

15. A machine as claimed in any of claims 1 to 14, characterized in that, to form a compact track tamping, levelling and lining machine, the two outer tamping unit assemblies designed to pivot or rotate laterally parallel to the plane of the track with their respective pivotal tool frames are arranged together with the preferably transversely and rotatable inner tamping unit assemblies (15,16) immediately behind - in the working direction - a 26 track lifting and lining unit provided on the machine frame and designed f or use at switches and, together with the track lifting and lining unit, are arranged between two undercarriages, more particularly in the form of bogies, arranged far apart from one another.

16. A machine as claimed in claim 15, characterized in that a lifting assembly preceding the track lifting and lining unit in the working direction and designed for use as required on the left-hand or right-hand branch track, i.e. for additional lateral pivoting, is associated with the two outer tamping unit assemblies designed to pivot laterally independently of one another with their respective pivotal tool f rames. and with the two inner tamping unit assemblies designed for trans verse displacement independently of one another and prefer ably for rotation together with one another.

17. A machine as claimed in claim 15 or 16, characterized in that an operator's cabin preceding the two pivotal tool frames and the tool carrier in the working direction and arranged within sight of the track lifting and lining unit and the additional lifting assembly, with a seat and control console facing against the working direction, is associated with the two outer and two inner tamping unit assemblies

18. A tamping machine, substantially as herein described with reference to the accompanying.drawings.

Published 1990 at The Patent Mce. State House. C6 '71 Holbom. londonWC1R4TP.PurLhereopleAmlYbe Obtained trom The Patentoffice &Cat Br, Et 3Ury Cray. Orpn, Kent SRS 3RD. Printed by MulUpex tachniquis it& St Mary Cray. Kent. Con. 1187