GB2231076A

GB2231076A - A travelling track tamping machine comprising transversely and vertically displaceable tamping units

Info

Publication number: GB2231076A
Application number: GB9007978A
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: 1990-11-07
Anticipated expiration: 2010-04-09
Also published as: SE9001188D0; SK278888B6; GB9007978D0; JP2960944B2; DE4001487A1; DD293854A5; FI95066B; CZ279364B6; NL194646C; FI901935A0; ZA902926B; ES2024164A6; CS9001905A2; FI95066C; CN1046578A; SE9001188L; UA13384A; NL9000029A; NL194646B; AT392498B

Description

1 is -7::2 3 I- Q- -,-7 6,= A travelling 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 3 534 687 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 is 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 mouted 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 frame is arranged at a distance from 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. applicants' 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 i 3 1 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.

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 is solved in a travelling track tamping machine of the type described at the beginning in that two tool frames designed to pivot laterally about a vertical axis independently of one another under the power of their own drives are provided on the machine frame for the independent transverse displacement and mounting of two tamping units provided with their own vertical displacement drives.

The solution according to the invention provides for a surprisingly simple and yet robust new basic construction 4 which is capable of withstanding in particular the relatively powerful forces generated in difficult and heavy track installations and which also opens up numerous other design paths for a range of design variations commensurate with the various known tamping units for switches or.even for plain track. Accordingly, the mounting of the tamping units in accordance with the invention on two tool frames designed to pivot laterally parallel to the plane of the track independently of one another provides very simply in design terms for a particularly robust arrangement which effectively withstands the very powerful and, above all, impact-like forces generated during tamping, the independent individual transverse displaceability under the power of the respective drives also providing very simply for rapid and individual, accurate pivoting of each tamping unit for centring away from the main track, for example over a switch blade. However, in addition to this highly advantageous use on difficult sections of track, particularly switches, the tamping units connected to a pivotal tool frame may also be used without restriction on plain track so that even relatively long sections of track, incorporating both plain track and switches, can be continuously tamped more economically with substantially the same quality of tamping. It is of particular advantage in this regard that, during the pivoting movement of the tamping units together with the pivotal tool frames about their vertical axes for the centring phase, the tamping tines may also be adapted relatively simply to the oblique position of the long sleepers present in switch sections.

In one advantageous embodiment of the invention, the two tamping units equipped with pairs of tamping tools f or tamping sleepers on the left and right of one or the other rail 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 V v, If' of the machine frame in the region adjoining the tamping unit. The arrangement of the tamping units at the ends of the pivotal tool frames has the particular advantage that the range within which the tamping units are laterally displaceable is kept free from other structural components and that the operator situated at the free opposite end has a clear, substantially unobstructed view of the tamping units because they are only connected at one end to the two pivotal tool frames, which ensures better and more accurate work. In addition, the elongate pivotal tool frames also provide for a widely overhanging arrangement of the tamping units for a relatively large overall displacement range so that, for example, branch tracks - in the switch section which are joined to the main track by long sleepers can be tamped and corrected together with the main track considerably better than before to obtain durable and more accurate positional correction. The slide or guide path guarantees uniform and safe supporting of the tamping units in any position on the machine frame.

one particularly 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 tamping unit over one or the other rail about a vertical axis extending substantially over one or the other rail. This special arrangement of the two pivotal tool frames enables them to be advantageously supported by the undercarriage following the tamping units, the free overhanging construction providing for free and unobstructed lateral pivoting and for an arrangement which in no way interferes with the function of the tamping tools. In addition to robust and trouble-free fixing of the two tool frames free from mutual inteference, the pivotal mounting about axes substantially above the rails provides in particular for an advantageous, 6 is central displacement range - adaptable to the particular rail - for simple adaptability to facilitate the centring of the tamping units relative to the position of the slightly different oblique sleepers in the switch section.

In another embodiment of the invention, each of the two pivotal tool frames recessed or angled away from the longitudinal axis of the machine 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 its tamping unit, preferably being designed for an overall pivoting range of the particular end of the pivotal tool frame of approximately 1.7 metres. This length of the pivotal tool frames, in conjunction with the appropriate recessing, provides for a highly advantageous, sufficiently large overall pivoting range for each tamping unit for adaptation to the oblique position of the sleepers in the switch section. More particularly, it provides for advantageous maximal adaptation of the particular displacement and pivoting angle range of each tool frame to the characteristics of the track for substantially automatic adaptation of the tamping units during the pivoting phase onto the obliquely lying sleepers in the switch section so that, for example, a switch section of the type in question can be tamped and, hence, fixed in a much more accurate position over the entire length of the long sleepers by a single tamping operation.

In another advantageous 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 tamping unit and behind the central undercarriage - preferably in the form of a bogie of a pivotal machine frame. Even allowing for very powerful forces generated during the tamping and correcting operation, a tamping machine constructed in this way provides both for safe supporting via the central bogie 1 1 7 is and for trouble-free arrangement of the two pivotal tool frames on the machine frame - with the two driver's cabins arranged appropriately over the front and rear undercarriages of the tamping machine.

Another advantageous embodiment of the invention is characterized in that the two tamping units with the vertical displacement drives are each mounted at the ends of the freely projecting pivotal tool frames for rotation about another vertical axis under the power of drives and for rotation towards the track axis, preferably for an overall lateral pivoting range of the tamping unit of the order of 2.0 metres. This construction advantageously combines the simple and robust laterally pivotal mounting of the tamping units for independent transverse displacement with the advantage of accurate alignment of the tamping tines which can be carried out at any time rapidly and independently of the transverse displacement - into a position parallel to the longitudinal axis of obliquely lying sleepers. This alignment can be achieved by pivoting of each tamping unit about the additional vertical axis independently under the power of its own drive. In this way, it is possible for the first time to tamp switches made particularly difficult by a number of track obstacles in conjunction with obliquely lying sleepers using tamping units which are designed for displacement independently of one another and highly individually about two pivoting axes and which are connected simply and robustly to the machine frame. With the overall displacement range of the tamping unit of approximately 2.0 metres, trouble-free and relatively simple tamping of even the outer switch regions still joined to one another by long sleepers is possible through the freely overhanging pivotal tool frames.

In another particularly advantageous embodiment of the invention, each of the two elongate pivotal tool frames is in several parts and, more particularly, is designed to be 8 telescopically extended longitudinally of the frame and is connected to its own drive f or longitudinal displacement of the tamping unit mounted on the end of the tool frame. Without affecting the advantages already mentioned, this advantageous, simple telescopic extension of the pivotal tool frames affords the possibility of rapid and accurate adaptation or independent longitudinal displacement of the two tamping units to enable them to be centred exactly over the possibly obliquely lying sleeper to be tamped.

In another advantageous embodiment of the invention, each of the two elongate pivotal tool f rames is in the f orm 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 simple and robust construction, particularly with the hydraulic drives arranged at the upper end of the girder, guarantees independent and trouble-free adjustment or longitudinal displacement of the tamping units in any position.

In another advantageous and practical embodiment of the invention, the two pivotal tool frames - with their vertical axes, their displacement drives and displacement ranges - are arranged in mirror-image relationship to one another relative to the longitudinal axis of the machine. This provides for substantially symmetrical load distribution between the two pivotal tool frames or over the machine frame while, at the same time, avoiding any mutual interference.

In one embodiment which is of particular advantage in the practical application of the machine according to the invention, preferably all the tamping tools of the two tamping units each designed to pivot laterally parallel to the plane of the track and, more particularly, comprising two pairs of tamping tools designed to penetrate into the ballast on the left and right of the rail are arranged in J1 9 known manner to pivot out laterally independently of one another with their associated tamping tines about axes extending parallel to the longitudinal axis of the track under the power of their own individual hydraulic drives.

This laterally pivotal design of the tamping tines, partic ularly in conjunction with the advantages afforded by the pivotal' tool frames and the adjustment possibilities of the tamping units, provides for an even further improved evading movement or lowering of the tamping units, even in the vicinity of track obstacles in the form of guide rails, switch blades and the like by the tamping tines situated over the obstacle being correspondingly raised or pivoted sideways.

Another particularly preferred and advantageous embodiment of the invention is characterized in that, to form a compact track tamping, levelling and lining machine, the two tamping units designed to pivot or rotate laterally and parallel to the plane of the track with their respec tive pivotal tool frames are arranged 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 track lifting and lining unit, are arranged between two undercarriages, more partic ularly in the form of bogies, arranged far apart from one another. The combination of the pivotal tool frames according to the invention with this compact machine provides for relatively quick tamping of high quality, even in difficult parts of switches, with accurate correction of the vertical and lateral position of the track, the spacing of the undercarriages relatively far apart from one another ensuring gentle curvature of the rails to avoid excessive flexural stressing, particularly at switches.

Q, Finally, in another advantageous and preferred embodi ment 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. f or additional lateral pivoting, is associated with the two tamping units respectively mounted on their pivotal tool frames designed to pivot laterally independently of one another. By means of this additional lifting assembly preceding the two pivotal tool -frames, even the branch track situated outside the range of the machine and still joined to the main track by long sleepers can be raised with particular advantage into an accurate set position by the tamping unit pivoted out laterally with the corresponding pivotal tool frame for fast and accurate tamping or positional correction of the track, so that switches of the type in question can now be tamped very economically, relatively easily and with high accuracy in one and the same operation.

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 tamping units mounted on two overhanging tool frames pivotal laterally about a vertical axis independently of one another.

Figure 2 is a plan view of the track tamping machine shown in Figure 1, a tamping unit 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 tamping unit 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 a tamping unit and designed for independent lateral pivoting under the power IQ 1 a 11 of their own drives as shown in Figure 2.

The track tamping, levelling and lining machine 1 shown in Figures 1 and 2 comprises a machine frame 2 and is designed to travel on two bogie-type undercarriages 3 and a single-axle undercarriage 4 along a track consisting of sleepers 5 and rails 6 and 7. A central power supply 9 is provided for activation of the axle drive 8 and the various other drives. The various drives are controlled from a central control console 11 in an operator's cabin-10. A levelling and lining reference system 12 consisting of feeler rollers and stretched wires is provided for accurate positional correction of the track. The machine frame 2, which has a driver's cabin 13 at either end, is designed to pivot about a vertical axis 14.

Two pivotal tool frames 21,22 designed to pivot laterally about vertical axes 19,20 independently of one another under the power of their own drives 17,18 are provided on the machine frame 2 between the two bogietype undercarriages 3 for the independent transverse displacement and mounting of two tamping units 15,16. To form this compact track tamping, levelling and lining machine 1, the two tamping units 15,16 designed to pivot or rotate laterally and parallel to the plane of the track with their respective pivotal tool frames 21,22 are arranged immediately behind - in the working direction indicated by an arrow 23 - a track lifting and lining unit 25 provided on the machine frame 2 and designed for use at switches and, together with the track lifting and lining unit, are arranged between two undercarriages 3 in the form of bogies arranged far apart from one another. For use on switches in particular, the track lifting and lining unit 25 designed to be supported on the rails 6,7 by flanged rollers 24 and adapted for vertical and lateral displacement under the power of drives 26,27 comprises lifting rollers 28 designed to be applied to the rail head and laterally displaced and 12 is gripping hooks 29 adapted for vertical and lateral displacement. A lifting assembly 30 immediately preceding the track lifting and lining unit 25 in the working direction and designed to be pivoted out sideways from one or the other longitudinal side of the machine is associated.with the two laterally pivotal tamping units 15,16. As shown in Figure 2 in particular, this additional lifting assembly 30 comprises a support frame 31 with double flanged and lifting rollers which is pivotally connected to the machine frame 2 by a support rod 32. In the drawing, the lifting assembly 30 and also the right-hand tamping unit 15 are pivoted out sideways onto a branch track 33 while the undercarriages 3 and 4 of the machine 1 remain on the main track 34.

As shown in Figure 3, each of the two tamping units 15,16 comprises two pairs 35,36 and 37,38 of tamping tools for penetration into the ballast on the left and right of a rail 6 or 7. These pairs of tamping tools comprise tamping tools 39140 and 41,42 designed to be squeezed and vibrated by drives. All the tamping tools 39 to 42 of the two tamping units 15,16 are designed to be pivoted out sideways independently of one another with their associated tamping tines 46,47 about axes 45 extending parallel to the longitudinal axis of the machine in known manner under the power of individual hydraulic drives 43 and 44. The tamping units 15, 16 are each mounted on the associated pivotal tool frame 21,22 for independent vertical displacement under the power of their own vertical displacement drives 48,49. Guide rails 50 are connected to the sleepers 5 laterally adjacent the rails 6. The additional lifting assembly 30 comprises a jib arm 51 rotatable about a vertical axis under the power of a rotation drive and a telescopic girder 53 designed for longitudinal displacement under the power of a drive 52. A cable 54 connected to the support frame 31 is guided around a guide roller 5 con- ti S 7 13 nected to the telescopic girder 53 and is connected to a hydraulic cylinder 56 for transmitting the lifting forces.

As shown in Figure 4, the two tamping units 15,16 are mounted at the end of the corresponding pivotal tool frames 21 and 22. These elongate pivotal tool frames 21,22 are each additionally supported by a horizontal slide or guide path 57 of the machine frame 2 in the region adjoining the tamping unit 15,16. Each of the two pivotal tool frames 21,22 is designed to extend telescopically longitudinally of the frame and is connected to its own drive 58,59 for longitudinal displacement of the tamping unit 15, 16 mounted on the end 60 of the tool frame. The tamping units 15,16 with their -vertical displacement drives 48,49 are each mounted for rotation about another vertical axis 61,62 under the power of drives 63,64 at the end.60 of the freely projecting pivotal tool frame 21,22 (see also Fig. 5) and are designed to be pivoted inwards towards the longitudinal axis 65 of the track or the machine. The vertical axis 19,20 of each pivotal tool frame 21,22 is arranged longitudinally of the track - behind a central axis 66 of the central undercarriage 3, immediately following the tamping unit 15,16, of the pivotal machine frame 2. The reference 67 denotes feeler rollers of the levelling and lining reference system 12 which are adapted to run along the track., To eliminate the undercarriage suspension, hydraulic drives 68 are connected to the bogie support frame and to the machine frame 2.

As shown in particular in Figure 5, the two pivotal tool frames 21,22 with their vertical axes 19,20 are pivotally mounted on a common bearing block 69 connected to the machine frame 2. Each of the two pivotal tool frames 21,22 consists of a rectangular inner girder 70 connected to the vertical axes 19,20 and an outer girder 71 adapted to be fitted onto the inner girder and designed for dis- placement longitudinally thereof. In theillustrated 14 is embodiment, the ends 60 of the pivotal tool frames 21,22 recessed or angled away from the longitudinal axis 65 of the machine have an overall displacement pivoting range a of approximately 1.7 metres, the innermost position shown in dash-dot-lines being situated within the two rails 6,7 forming the main track 34. The overall length of each pivotal tool frame 21,22, from its vertical axis 19,20 to the associated tamping unit 15,16, is at least 4 to 5 metres. The overall lateral displacement range which each tamping unit 15,16 is capable of covering under the power of the drives 17,64 and 18,63 is approximately 2 metres. The two rails of the branch track 33 are denoted by the references 72 and 73 and the rail frog point by the reference 74.

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 plain track, the two pivotal tool frames 21,22 are pivoted sideways so that the two tamping units 15,16 are situated centrally over the sleeper bearing surfaces to be tamped of the particular rail 6,7 (see also dash-dot right-hand tamping unit 15 in Figure 3). At the same time the main track 34 is raisedinto the set position by means of the track lifting and lining unit 25 without the additional lifting assembly 30. When the switch section - with the main track 34 and the branch track 35 shown in the drawing, pore particularly in Figures 2, 3 and 5, is reached, the right-hand tamping unit 15 pivots out sideways until it is centred over the outer rail 73 of the branch track 33 (Figures 2, 3 and 5). In addition to the pivoting movement carried out under the power of the drive 18, the pivotal tool frame 21 together with the tamping unit 15 can be subjected to slight longitudinal displacement by activation of the drive 58 until the associated te pairs 35,36 of tamping tools with their tamping tines 46,47 are situated exactly over the corresponding crossover point where the rail passes over the long sleeper 5, optionally with pivoting of one or the other tamping tine 46,47 to avoid an obstacle, for example the guide rail 50. Through simultaneous activation of the drive 63, the tamping unit 15 as a.whole is also pivoted slightly about the vertical axis 61 (Figure 5) until the tamping tines 46,47 are situated exactly parallel to the longitudinal axis of the sleeper 5 to be tamped which lies obliquely in this switch section. The opposite tamping unit 16 or rather the associated pivotal tool frame 22 remains in the plain-track position for tamping the outer rail. 6 of the main track 34. The two lifting hooks 29 are brought into engagement with the rails 6,7 of the main track 34, optionally in conjunction with the two lifting rollers 28.

After the lifting rollers of the additional lifting assembly 30 connectedto the support frame 31 have also been brought into engagement with the outer rail 73 of the branch track 33, the switch is lifted substantially simultaneously at three points or places (cf. the three small vertical arrows in Figure 3) by simultaneous activation of the drives 26,27 of the track lifting and lining unit 25 and the hydraulic cylinder 56 of the lifting assembly 30 until it is in the correct set position in which it is then tamped and fixed with its sleepers by means of the tamping units 15,16 previously centred over the corresponding rails. Before activation of the corresponding vertical displacement drive 48,49, the tamping tines 46,47 are correspondingly adapted in dependence upon the track obstacles, for example the guide rail 50, present in the tamping zone by lateral pivoting of the two adjacent tamping tines 46 and 47 independently of one another by corresponding activation of the drives 43,44 (Figure 3). On completion of tamping, the right-hand - and meanwhile 16 raised - tamping unit 15, by activation of the drive 18, is pivoted together with the associated pivotal tool frame 21 over the frog point 74 and centred thereover, optionally under the additional power of the drive 63. After adaptation of the tamping tines 46,47 to the guide rail 50 present on both sides in this region by lateral pivoting under the power of the drives 43,44, the tamping unit 15 is lowered into the ballast to tamp the sleepers or sleeper bearing surfaces in the region of the frog point 74. The tamping machine 1 then advances to the next sleeper, the right-hand tamping unit 15 again being pivoted together with the pivotal tool frame 21 over the outer rail 73 of the branch track 33 by activation of the drive 18. Another tamping cycle then begins in the same way as described above.

t is i% 17 7

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 two tool frames designed to pivot laterally about a vertical axis independently of one another under the power of their own drives are provided on the machine frame for the independent transverse displacement and mounting of two tamping units provided with their own vertical displacement drives

2. A machine as claimed in claim 1, characterized in that the two tamping units equipped with pairs of tamping tools for tamping sleepers on the left and right of one or the other rail 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 tamping unit

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 riage in the working direction is arranged to pivot out laterally with its tamping unit over one or the other rail about a vertical axis extending substan tially over one or the other rail

4. A machine as claimed in claim 1, 2 or 3, characterized in that each of the two pivotal tool frames reces- 18 sed or angled away from the longitudinal axis of the machine 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 its tamping unit -. preferably being designed for an ov - erall pivoting range of the particular end of the pivotal tool frame of approximately 1.7 metres.

5. A machine as claimed in any of claims 1 to 4, charac terized in that the vertical axis of each pivotal tool frame is arranged - in the working direction - behind the middle axle ly following the tamping unit central undercarriaae of the undercarriage immediateand behind the - preferably in the form of a bogie - of a pivotal machine frame

6. A machine as claimed in any of claims' 1 to 5, charac terized in that the two tamping units with the vertical displacement drives the ends of the freely projecting pivotal tool frames for rotation about another vertical axis under the power of drives are each mounted at and for rotation towards the track axis, preferably for an overall lateral pivoting range of the tamping unit of the order of 2.0 metres.

7. A machine as claimed in any of claims 1 to 6, 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 tamping unit mounted on the end of the tool frame.

8. A machine as claimed in any of claims 1 to 7, charac terized in that each of the two elongate pivotal tool frames is in the form of a girder which is prefer ably designed to be telescopically extended longitudinally of the frame, extending vertically in cross-section, and 1; 19 j which comprises hydraulic drives arranged at its upper end.

9. A machine as claimed in any of claims 1 to 8, charac terized in that the two pivotal tool frames - with their vertical axes. their displacement drives and displacement ranges (a) - are arranged in mirror-image relationship to one another relative to the longitudinal axis of the machine.

10. A machine as claimed in claim 1, characterized in that preferably all the tamping tools of the two tamping units each designed to pivot laterally parallel to the plane of the track and, more particularly, comprising two pairs 1 of tamping tools designed to penetrate into the ballast on the lef t and right of the rail are arranged in known manner to pivot out laterally independently of one another with their associated tamping tines. about axes extending parallel to the longitudinal axis of the track under the power of their own individual hydraulic drives

11. A machine as claimed in any of claims 1 to 10, characterized in that, to form a compact track tamping, levelling and lining machine 1 the two tamping units designed to pivot or rotate laterally and parallel to the plane of the track with their respective pivotal tool frames are arranged 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 track lifting and -lining unit., are arranged between two undercarriages. more particularly in the form of bogies, arranged far apart from one another.

12. A machine as claimed in claim 11, 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 tamping units respectively mounted on their pivotal tool frames designed to pivot later ally independently of one another.

13. A track tamping machine substantially as herein described with reference to the accompanying drawings 11 1 1 tain Offi I.N.1b12hed 1990,IsThe Patent Office,State House, 6671 Righ Holborn, London WC1R4TP.Flurther copies maybe ob edfromThePatent ce.

Sales Bra-nch, St Mary Cray, Orpington. Kent BR5 3PM. Printed by Multiplex techniques ltd, St Mary Cray, Kent. Con. 1187