GB2151675A

GB2151675A - Continuous-motion track tamping machine

Info

Publication number: GB2151675A
Application number: GB08410077A
Authority: GB
Inventors: Josef Theurer
Original assignee: Franz Plasser Bahnbaumaschinen Industrie GmbH
Current assignee: Franz Plasser Bahnbaumaschinen Industrie GmbH
Priority date: 1983-12-16
Filing date: 1984-04-18
Publication date: 1985-07-24
Also published as: HUT36197A; GB2151675B; SE8401563D0; ZA842929B; AU565230B2; AT382658B; DE3409852C2; ATA440783A; AU2712584A; GB8410077D0; FR2556752B1; DD216054A5; IT1196060B; FR2556752A1; DK156838B; DK156838C; DK163384A; SE457361B; JPH0373685B2; SE8401563L

Abstract

A tamping, levelling and lining machine has a bridge-like main frame 7 which carries the operators, propulsion system, power supply and control systems. All the lifting, lining, and tamping tools 17, 18 are mounted on a sub-frame 19 which can move longitudinally relative to the main frame under the operation of a drive 27 and is suspended from the main frame at two longitudinally separated positions 21, 24. In operation, the main frame moves continuously while the tool frame is operated by the longitudinal drive 27 so as to move intermittently for tamping successive sleepers. The described manner of mounting the tool frame on the main frame ensures that the entire weight of the machine is available to assist penetration of the tamping tools into the ballast, whereas the intermittently moving tool frame can be made relatively light and compact. <IMAGE>

Description

SPECIFICATION Continuous-motion track tamping machine This invention relates to a continuous-motion (non-stop) track tamping, levelling and lining machine comprising a main frame supported by undercarriages and carrying drive, power supply and control systems and at least one operator's cabin for visual observation of the tam ping, lifting and lining tools; a tool frame which is arranged between two machine undercarriages spaced far apart from one another for the lifting and lining operation, which carries at least one tamping unit and also a track lifting and lining unit together with their drives and which is connected to the main frame for longitudinal displacement by a drive; and levelling and lining reference systems associated with the track lifting and lining unit.

GB-PS 1320205 already proposes a continuousmotion (non-stop) track tamping machine of which the tamping units are each mounted on a tool frame displaceable relative to the main frame along guide posts arranged thereon and extending longitudinally of the machine under the power of a cylinder-and-piston drive. This known machine is also equipped with track lifting tools which precede the tamping units and which are directly connected to the main frame of the machine. During the continuous (non-stop) advance of the main frame together with the lifting tools, the tool frames together with the tamping units have to remain stationary until the tamping operation is over and are then accelerated in the working direction along their guide posts by means of the cylinder-andpiston drives until the tamping tools are centered over the next sleepers to be tamped.By lowering the tamping units, a new working cycle is initiated.

Figure 1 of the above-mentioned Patent also shows a side elevation of an embodiment with only one tool frame displaceable relative to the main frame of the machine.

In addition, GB-PS 2070670 describes a travelling train for cleaning the ballast bed of railway tracks comprising a ballast cleaning machine equipped with a track unit, a number of wagons for loading waste spoil and, incorporated between those wagons and the cleaning machine, a tamping machine comprising another two track lifting units. The tamping units of the machine together with the immediately preceding track lifting unit are arranged on the machine frame for longitudinal displacement by drives. The longitudinal displacement drives impart to the tamping units a movement relative to the continuously advancing machine frame or train which is necessary for their step-by-step advance.

By virtue of this arrangement, it is possible in the course of ballast cleaning work for the track to be lifted in a single operation by an overall amount, which previously could only be achieved by the repeated use of a track tam ping and levelling machine, by several successive lifting operations distributed over a relatively long section of the track.

The track is fixed at a provisional level by tamping without the permittedflexural stressing of the rails by the lifting operation being exceeded at any point of the track. In contrast to the function of conventional tamping machines, the object of the tamping operation in this case is not to create definitive, consolidated sleeper bearing surfaces for a track raised to the required level, but instead solely to provide provisional support for the track raised to an intermediate level for the ballast cleaning operation. In addition, this known train does not provide for any lateral correction to be made to the position of the track.

Finally, an advertisement in the Journal "Der Eisenbahningenieur", No. 6, June, 1983, refers to a prototype built by Applicants of the first continuousmotion (non-stop) track tamping, levelling and lining machine in which the tamping, lifting and lining units are arranged together on a tool frame which, at its rear end carrying the tamping unit, is supported on the track by a flanged wheel set and of which the front end, in the form of a beam-like longitudinal girder, is mounted on the main frame both for longitudinal displacement and also for universal pivoting. The movement of the tool frame relative to the continuously advancing main frame which is necessary for the step-by-step advance of the tamping unit is produced by means of a displacement drive in the form of a hydraulic cylinder-and-piston assembly. A machine of this construction has proved very successful in trials.

The object of the present invention is to provide a continuous-motion (non-stop) tracktamping, levelling and lining machine of the type described at the beginning which is distinguished by the particular simplicity of its construction.

According to the invention, this object is achieved in that, in the continuous-motion (non-stop) track tamping, levelling and lining machine of the type described at the beginning, the tool frame forms with the tamping, lifting and lining units a common working unit which is connected to the main frame for longitudinal displacement at at least two points spaced apart from one another longitudinally of the machine, a common longitudinal displacement drive being connected to the tool frame equipped with all the tamping, lifting and lining units intended for both rails of the track and to the main frame of the machine.

This construction according to the invention significantly reduces the amount of work involved in design and manufacture and also costs whilst, at the same time, affording the possibility of a further increase in output compared with known types of continuous-motion (non-stop) track tamping machines. This increase in output can be achieved because the masses which have to be accelerated and then braked again during the step-by-step advance of the working unit from one tamping site to the next merely comprises the tool frame with the tamping, lifting and lining units, so that, for the same power output of the longitudinal displacement drive, the advance movement can be completed more quickly and hence the overall working cycle of thetamping units shortened.

Another advantage of the machine according to the invention lies in the relatively rigid connection suitable for transmitting vertical forces - of the tool frame to the main frame of the machine at at least two points spaced apart from one another. It is well known that, when the tamping units are lowered, the ballast bed offers a relatively high resistance to the penetration of the tamping tools which can assume a value of several tonnes where the ballast bed is heavily encrusted or where the tamping units comprise a plurality of tamping tines, for example 16 tines in the case of two-sleeper tamping machines. Accordingly, by virtue of the vertically rigid connection of the tool frame to the main frame of the machine, the main frame with its considerable overall mass is available as a buffer for absorbing these vertical forces.The same also applies to the transmission of the lifting forces of the combined track lifting and lining unit to the main frame of the machine.

In addition, it is possible to reduce the longitudinal distance between the tamping units in the rear end position of the tool frame and the following undercarriage of the machine to the minimum of a mere safety distance and, hence, correspondingly to reduce the overall length of the machine without however, affecting the distance which has to be maintained between the track lifting and lining unit and the preceding undercarriage of the machine to obtain adequate lifting of the track without overstressing the rails.

In another embodiment of the invention, the active drive components of the longitudinal displacement drive which are connected to the power supply systems arranged on the main frame may be connected to the main frame or to the tool frame. This provides the design engineer with numerous options in regard to the most effective positioning of the active drive components on the machine both from the point of view of the most favorable application of power and from the point of view of optimal utilization of the available space.

According to another aspect of the invention, the common longitudinal displacement drive is in the form of a single, double-acting hydraulic cylinderand-piston assembly of which the cylinder designed to function as the active drive component is pivotally connected to the main frame of the machine, preferably at about the transverse center thereof. This version of the longitudinal displacement drive is distinguished by the simplicity of its construction, by its robustness and by its reliability. In addition, the displacement function itself may be controlled very sensitively and with simple technical means, in particular automatically.

In one preferred embodiment of the invention, the rear end of the tooi frame relative to the working direction is mounted in two longitudinal guides arranged at opposite lateral outsides of the main frame and the front end of the tool frame is formed by two longitudinal girders in the form of longitudinal guides, or by one such longitudinal girder, mounted at approximately the transverse center of the main frame. In the most simple case, this provides for a solid three-point support of the tool frame on the main frame, the rear end of the tool frame which bears the greater part of the weight of the working units and to which the working forces are applied receiving a double support on the main frame of the machine suitable for the safe transmission of those forces.

According to another advantageous aspect of the invention, those parts connected to the tool frame of the two rear longitudinal guides arranged at the lateral outsides of the main frame and formed by guide posts or by roller tracks orguideways are arranged in the upper part of the tool frame near the tamping unit. This arrangement promotes the direct flow of forces from the tamping units to those parts of the two longitudinal guides which are connected to the main frame.

Another advantageous embodiment of the invention is characterized in that the longitudinal girder(s) forming the longitudinal guide(s) arranged at the front end of the tool frame is/are mounted on the main frame, preferably on a downwardly projecting bracket, between the track lifting and lining unit and the preceding undercarriage of the machine. This arrangement enables the space situated above the front longitudinal guide(s) to be utilized in the usual way for accommodating the drive and power supply systems of the machine. On the other hand, where the front longitudinal girder(s) is/are arranged in a low-lying position, the resulting lowering of the overall center of gravity of the tool frame with the tamping, lifting and lining units provided for both rails of the track provides for even greater stability of the working unit.

In another, particularly preferred embodiment of the invention, the tool frame is longitudinally guided by roller guides each comprising at least two rollers which are mounted on the tool frame or on the main frame about horizontal shafts extending transversely of the longitudinal axis of the machine and which are respectively designed for application, preferably without any play, to an upper and a lower horizontal longitudinally extending roller track or guideway of the main frame or the tool frame. These roller guides reduce the frictional forces which have to be overcome during the step-by-step advance of the working unittothe minimum level of pure rolling resistance. This contributes significantly to a more rapid completion of the advance movement and, hence, of the working cycle of the machine.

Where the rollers are applied without play to both horizontal roller tracks or guideways, which may be obtained for example by mounting one of the two rollers for vertical displacement or adjustment, any jolting or vibration of the rollers and their guideways which may be produced by unavoidable play in the roller guides and the noise which this would generate are also avoided.

At least one roller of the roller guide is advantageously provided on one or both sides with side rims designed for application to the side edge(s) of the associated rollertrackorguideway.

Accordingly, this roller simultaneously performs the function of a vertical and lateral guide member.

Another advantageous embodiment of the invention is characterized in that the tool frame carrying the tamping, lifting and lining units intended for both rails of the track is additionally designed to be displaced and pivoted relative to the main frame by at least one drive in a plane substantially parallel to the plane of the track transversely of the longitudinal axis of the machine.

In this way, the tamping units can be kept exactly laterally centered over the associated rails, even around very tight curves in the track.

In another variant of this particular embodiment of the invention, the rear end at least of the tool frame is advantageously mounted for displacement along a horizontal shaft or guide post which extends transversely of the longitudinal axis of the machine and of which the outer ends are each connected to one of the two laterally opposite roller guides. This transversely displaceable connection of the tool frame to the main frame is distinguished by the simplicity of its construction and by its ability to withstand both the weight and also the working forces of the tamping, lifting and lining units.

In the case just mentioned, additional advantages are afforded if the shaft or guide post is in the form of a full-length piston rod, comprising a piston at its longitudinal center, of a double-acting hydraulic cylinder which surrounds it and which, with the piston, forms the transverse displacement drive, the associated end of the tool frame being connected to said double-acting hydraulic cylinder. Accordingly, crucial parts of the roller guides, the transverse guide for the tool frame and the transverse displacement drive are combined into a single, space-saving unit of very simple construction. This arrangement also contributes significantly towards a desirable reduction in manufacturing costs.

According to another aspect of the invention, the two roller guides connected to the rear end of the tool frame are formed on each side of the frame by rollers provided on at least one side with a side rim or by pairs of such rollers designed for application to the upper side and lower side of one of the two lateral main longitudinal girders of the main frame of the machine. This embodiment is distinguished by the particular simplicity of its construction because it eliminates the need to provide separate roller tracks or guideways, the upper, lower and at least one lateral boundary surface of the longitudinally extending, generally rectangular main longitudinal girder of the main frame of the machine being used for vertically and laterally guiding the rollers.

Another advantageous embodiment of the invention is characterized in that the tool frame and main frame are joined together in the region of the longitudinal guides by absorbing elements which absorb body noise and shocks. These absorbing measures on the longitudinal guides not only reduce the stressing of the main frame by the working forces and combined weights of the working units, they also provide for more comfortable working conditions for the machine operator.

Another advantageous embodiment of the invention is characterized in that the common longitudinal displacement drive consists of two double-acting hydraulic-and-cylinder piston assemblies of which the cylinders functioning as active drive components are connected to the tool frame, preferably above each of the tamping units associated with the particular rail. This arrangement provides for the application of relatively powerful displacementforces and for a very rapid step-bystep advance of the tool frame carrying the tamping, lifting and lining units for both rails of the track.

In another variant of the invention, the two rear longitudinal guides each consist of a longitudinally extending guide post which is connected to the main frame and on which a piston and a hydraulic cylinder connected to the tool frame are arranged to form the longitudinal displacement drive.

Accordingly, the longitudinal guides form with the longitudinal displacement drives a compact, structural and functional unit which is particularly suitable for equipping machines having main longitudinal girders arranged at a considerable distance above the two rails longitudinally of the machine.

Another embodiment of the invention is characterized in that, at its front and rear ends, the tool frame comprises two longitudinally extending guide posts which project over the two rails and which are slidably guided in guide sleeves or the like connected to the machine frame. This embodiment is distinguished by a very exact, substantially playfree vertical and lateral guiding of the tool frame relative to the main frame.

In another embodiment of the invention, the common longitudinal displacement drive is formed by an endless chain drive which is connected to a drive motor forming the active drive component, which is preferably arranged on the main frame of the machine, more especially at approximately its transverse center, and with one longitudinally extending flight of which the tool frame is drivingly connected. This embodiment of the longitudinal displacement drive is distinguished by its robust, substantially maintenace-free construction.

In an alternative embodiment of the invention, the common longitudinal displacement drive may consist of a rack-and-pinion drive comprising a longitudinally extending rack and, engaging therein, a pinion connected to a drive motor forming the active drive component, the rack preferably being arranged on the main frame of the machine and the pinion together with the drive motor on the tool frame. Both in this embodiment and in the previously described embodiment of the longitudinal displacement drive, it is possible to use either a hydraulic drive or an electric drive, optionally with a transmission gear in between.

In another variant of the invention, the front andl or rear end of the tool frame is suspended pendulum-fashion from the main frame by two longitudinally adjustable guide rods which are situated opposite one another relative to the longitudinal axis of the machine and which are mounted to pivot about a horizontal pivot extending transversely of the longitudinal axis of the machine, being formed in particular by hydraulic cylinderand-piston assemblies.In this connection, it is of particular advantage for the longitudinally adjustable guide rods each in the form of doubleacting hydraulic cylinder-and-piston assemblies and for the longitudinal displacement drive to be connected to a control unit through which the effective length of the guide rods is variable according to a predetermined angular function in dependence upon the displacement path of the longitudinal displacement drive. By virtue of this arrangement, the tool frame is able to remain at the same level over its entire displacement path between its front and rear end positions, despite its pendulum-like suspension from the main frame, i.e.

to be displaced exactly parallel longitudinally of the machine. In addition, the pendulum-like suspension of the tool frame from the main frame by variablelength guide rods enables the entire working unit to be raised when the machine is in transit.

Embodiments of the invention are described in detail in the following with reference to the accompanying drawings, wherein: Figure 1 is a side elevation of a continuous-motion (non-stop) tracktamping, levelling and lining machine according to the invention.

Figure 2 is a diagrammatically simplified plan view of the machine shown in Figure 1 negotiating a curve.

Figure 3 is a section on the line Ill-Ill in Figure 1.

Figure 4 is another section through the machine on the line IV--IV in Figure 1.

Figures 5 to 9 are each highly simplified, diagrammatic partial side elevations of various other embodiments of continuous-motion (nonstop) track tamping, levelling and lining machines according to the invention with tamping, lifting and lining units associated with each of the two rails.

Figures 1 to 4 show a continuous-motion (nonstop) tracktamping, levelling and lining machine 1 comprising a main frame 7 which is supported by two bogies 2,3 and which is designed to travel under the power of its own axle drive 6 along the track consisting of rails 4 and sleepers 5. The arrow 8 indicates the working direction of the continuousmotion machine 1. At the front end of the main frame 7, there is an operator's cabin 9 which contains a motion and function control console 10 and an input and recording unit 11 for track data written down on the track. The drive and power supply systems 14 of the machine are accommodated in a housing 13 arranged behind the cabin 9 between the two lateral main longitudinal girders 12 of the main frame 7.At the rear end of the main frame 7, there is a second operator's cabin 15 which, in addition to a motion and function control console 10 and the usual controls for the working units, also accommodates a central control unit 16.

The machine 1 is equipped with two tamping units 17 respectively associated with one of the two rails 4 and with a track lifting and lining unit 18 which precedes the tamping units 17 and which, in the interests of clarity, is only shown in Figure 1. The tamping units 17 and the track lifting and lining unit 18 are arranged on their own tool frame 19 with which they form a common structural and working unit and which is connected to the main frame 7 for longitudinal displacement at two points spaced apart from one another longitudinally of the machine. At its front end, this tool frame 19, which largely resembles a framework in the region of the working units, terminates in two beam-like longitudinal girders 20 which extend longitudinally of the machine over the two rails 4 and which are each mounted for longitudinal displacement relative to the main frame 7 in a roller guide 21.Each of the roller guides 21 consists of two rollers 23 which are mounted for rotation about horizontal shafts 22 extending transversely of the longitudinal axis of the machine and which are provided on both sides with side rims, being designed for direct application to the upper and lower horizontal boundary surface of the longitudinal girder 20 of rectangular crosssection.

The rear end of the tool frame 19 carrying the tamping units 17 is also connected to the main frame 7 for longitudinal displacement by another two roller guides 24. These roller guides 24 each comprise three rollers 25 provided on one side with a side rim which are mounted for rotation about horizontal shafts extending transversely of the longitudinal axis of the machine and two of which are applied to the upper side and one to the lower side of the associated main longitudinal girder 12.

For the step-by-step advance of the tamping unit 17 (symbolized by the arrows 26) relative to the continuously advancing main frame 7, the tool frame 19 is connected to the main frame 7 for universal pivoting by a linear displacement drive 27 in the form of a hydraulic cylinder-and-piston assembly. The front end position of the tool frame 19 carrying the working units is shown in solid lines in the drawing. The rear end position of the tool frame 19 is shown in chain lines in Figure 1.

The tool frame 19 is also designed for displacement relative to the main frame 7 transversely of the longitudinal axis of the machine.

To this end, the upper rollers 23 of the two roller guides 21 are respectively mounted on the ends of a full-length piston rod 28 which, at its longitudinal center, carries a piston 29 forming a transverse displacement drive with a hydraulic cylinder 31 arranged around the piston rod 28 and connected by brackets 30 to the main frame 7. Similarly, the lower rollers 25 of the two rear roller guides 24 are respectively mounted on the ends of a piston rod 32 of which the centrally arranged piston 33 forms another transverse displacement drive with a hydraulic cylinder 34 arranged around the piston rod 32. Where the track is straight, the pistons 29 and 33 of the two transverse displacement drives and, hence, the tool frame 19 are situated in their respective central positions relative to the main frame 7, as shown in Figures 3 and 4.Accordingly, the two tamping units 17 are centered in the correct lateral position relative to the two rails 4, as shown in Figure 3.

Figure 2 shows the machine 1 negotiating a curve of which the curved track axis 35 is represented by a dash-dot line. In order to keep the two tamping units 17 laterally centered relative to the rails 4 while the curve is being negotiated, the tool frame 19 is displaced parallel to the left-hand side of the machine by the simultaneous admission of pressure to the two hydraulic cylinders 31 and 34 to such an extentthatthetwotamping units 17 are situated in a mirror-symmetrical position relative to the track axis 35. The control of this transverse displacement from the operator's cabin 15 may be carried out either manually or, in known manner, automatically by means of feelers and sensors cooperating with the track.

The machine 1 is equipped with a levelling reference system 36 and with a lining reference system 37 which, in the interests of clarity, have only been shown in Figure 1. The levelling reference system 36 comprises two wires 38 which extend over the rails 4 between a front feeler member 39 supported on the as yet uncorrected track and a rear feeler member 40 supported on the already corrected track and with each of which a level sensor 42 supported on the associated rail 4 between the tamping units 17 and the track lifting and lining unit 18 by another feeler member 41 cooperates for determining the difference between the actual and prescribed levels.The lining reference system 37 comprises a wire 43 which extends between measuring trolieys (not shown) guided on the track in front of and behind the machine 1 and with which a versine sensor 44 connected to the feeler member 41 cooperates for determining the difference between the actual and prescribed versines.

Figure 5 is a highly simplified diagrammatic view of the tool frame 45 of another embodiment of a continuous-motion (non-stop) track tamping, levelling and lining machine of which only the front undercarriage 46 and points of connection of the tool frame 45 to the main frame 47 have been shown. The arrow 48 indicates the direction of travel of the continuously advancing machine or rather its main frame 47 during the working run. The two longitudinal girders 49, extending in the working direction, of the tool frame 45 which at its rear end is in the form of a box frame are mounted in roller guides 50 each comprising two side-rim rollers 51 arranged above one another, as in the previously described embodiment. The rear end of the tool frame 45 is mounted in two longitudinal guides 53 respectively arranged above one of the two rails 52.

Each of these longitudinal guides 53 consists of a longitudinally extending guide post 55 which is fixed to a bracket 54 of the main frame 47 and which is formed by the piston rod of a hydraulic cylinder 56 which, in turn, is fixed to the upper side of the tool frame 45 and which, with the piston 57 of the guide post 55, forms a longitudinal displacement drive for the step-by-step advance of the tool frame 45 in the direction of the arrows 58. Beneath the hydraulic cylinder 56, a twin tamping unit 59 is arranged on the tool frame 45 over each rail 52 for simultaneously tamping the ballast around and below two successive sleepers 60. The tamping units 59 are preceded by a combined track lifting and lining unit 61 of conventional construction.

Between this track lifting and lining unit 61 and the tamping unit 59, there is a feeler member 62 which is supported on both rails 52 of the track and which cooperates with the reference systems of the machine in the manner already described for determining the differences between the actual and prescribed levels and lateral positions of the track.

Figure 6 is another diagrammatically simplified view showing the tool frame 63 of another embodiment of the machine according to the invention together with the points of connection of the tool frame to the main frame 64 of that machine.

The arrow 65 denotes the working direction of the continuously advancing main frame 64. Both at its front end and its rear end, the tool frame 63 comprises two projecting guide posts 67 which extend longitudinally of the machine, each arranged over one of the two rails, and which are slidably guided in corresponding guide sleeves 68 of the main frame 64. For the step-by-step advance of the tool frame 63 equipped with tamping units 69, a feeler member 70 and a combined track lifting and lining unit 71 in the direction indicated by the arrows 72, an endless chain drive 74 reversible in the directions indicated by the double arrow 73 is arranged substantially midway across the main frame 64, the tool frame 63 being pivotally connected to the lower flight of this endless chain drive 74.The chain drive 74 is connected to a drive motor 75 which is also arranged on the main frame 64 and which may be formed for example buy a hydraulic motor transmission unit. The rear end position of the tool frame 63 which forms a single working assembly with the working units 69,71 is shown in chain lines on the left-hand side of Figure 6.

Figure 7 is a diagrammatic view of another embodiment of a displacement drive for the stepby-step advance of the tool frame 76 carrying the working units. This longitudinal displacement drive is formed by a rack-and-pinion drive 77 which comprises a longitudinally extending rack 79 fixed to the underneath of the main frame 78 substantially at its transverse center and, engaging in this rack 79, a pinion 81 and which is mounted on the upper side of the tool frame 76 and which is connected to a drive motor 80. In contrast to the longitudinal displacement drive shown in Figure 6, the active drive components of the longitudinal displacement drive are arranged on the tool frame 76 in this embodiment.

Figure 8 shows another embodiment of the invention in which the tool frame 85 equipped with twin spreading-and-tamping units 82, a feeler member 83 and a track lifting and lining unit 84 is suspended pendulum-fashion from the main frame 86 at two points spaced far apart from one another longitudinally of the machine. To this end, two longitudinally adjustable guide rods 89 in the form of hydraulic cylinder-and-piston assemblies arranged on the opposite outsides of the tool frame 85 and each mounted about a horizontal pivot extending transversely of the machine are provided both at the front end and at the rear end of the tool frame 85 (looking in the working direction as indicated by the arrow 87), being mounted at their upper ends on the main frame 86 about pivots 90 extending parallel to the pivots 88.In addition, the tool frame 85 and the main frame 86 are joined together for universal pivoting by a longitudinally extending longitudinal displacement drive 91 in the form of a double-acting hydraulic piston-andcylinder assembly. The cylinder chambers of the longitudinal displacement drive 91 and of the guide rods 89 are connected to a control unit 92, as indicated in chain lines. Through this control unit 92, the associated cylinder chambers of the guide rods 89 are activated in dependence upon the displacement path of the longitudinal displacement drive 91 in such a way that, despite its rotation about the pivots 90, the tool frame 85 remains at the same level, i.e. is disposed exactly parallel longitudinally of the machine, over its entire displacement range between its front and rear end positions each shown in chain lines.Accordingly, the exact relationship of the level sensor 93 connected to the feeler member 83 to the levelling reference system 94 and of the versine sensor 95 to the lining reference system 96 remains intact over the entire displacement path of the tool frame 85.

In the embodiment shown in Figure 9, the substantially box-like tool frame 100 provided with tamping units 97, a feeler member 98 and a track lifting and lining unit 99 terminates at its front end (relative to the working direction as indicated by the arrow 101) in a single, central longitudinal girder 102 which is guided for longitudinal displacement in a roller guide 103. This roller guide 103 is arranged between two brackets 105 projecting downwards from the main frame 104 and comprises two vertical guide rollers 106 applied to the upper and lower sides of the longitudinal girder 102 and two lateral guide rollers 107 applied to the opposite sides of the longitudinal girder 102.As in the previously described embodiment, the rear end of the tool frame 100 is suspended pendulum-fashion from the main frame 104 by two longitudinally adjustable guide rods 108 in the form of hydraulic cylinder-and piston assemblies. For the step-by-step advance of the tamping units 97 by one sleeper interval at a time, the tool frame 100 is connected for universal pivoting to the main frame 104 by a longitudinal displacement drive 109 which is in the form of a double-acting hydraulic cylinder-and-piston assembly guided through between the two brackets 105. As in the previously described embodiment, the guide rods 108 are controlled in dependence upon the displacement path of the longitudinal drive 109 in such a way that the rear end of the tool frame 100 remains at the same level over the entire displacement path.The rear end position of the tool frame 100 is shown in chain lines on the left of Figure 9.

Two features which all embodiments of the invention have in common are the equipping of the tool frame with tamping, lifting and lining units associated with each of the two rails of the track and also the considerable longitudinal interval separating the associated track lifting and lining unit from the preceding undercarriage of the machine.

This interval enables the trackto be lifted and laterally aligned by fairly considerable amounts withoutthe rails being excessively stressed and, hence, permanently deformed.

Many other variants differing from the embodiments described and illustrated, particularly in regard to the choice and special design of the working units, lie within the scope of the invention.

For example, the tool frame may be equipped with tamping, track lifting and lining units suitable for working on switches and crossings.

Claims

1. A continuous-motion (non-stop) track tamping, levelling and lining machine comprising a main frame supported by undercarriages and carrying drive, power supply and control systems and at least one operator's cabin for visual observation of the tramping, lifting and lining tools; a tool frame which is arranged between two machine undercarriages spaced far apart from one another forthe lifting and lining operation, which carries at least one tamping unit and also a track lifting and lining unit together with their drives and which is connected to the main frame for longitudinal displacement by a drive; and levelling and lining reference systems associated with the track lifting and lining unit, characterized in that the tool frame forms with the tamping, lifting and lining units a common working unit which is connected to the main frame for longitudinal displacement at at least two points spaced apart from one another longitudinally of the machine, a common longitudinal displacement drive being connected to the tool frame equipped with all the tamping, lifting and lining units intended for both rails of the track and to the main frame of the machine.

2. A machine as claimed in Claim 1, characterized in that the active drive components of the longitudinal displacement drive which are connected to the power supply systems arranged on the main frame are connected to the main frame or to the tool frame.

3. A machine as claimed in Claims 1 and 2, characterized in that the common longitudinal displacement drive is in the form of a single, double acting hydraulic cylinder-and-piston assembly of which the cylinder designed to function as the active drive component is pivotally connected to the main frame of the machine, preferably at about the transverse center thereof (Figures 1 to 4 and 8 to 9).

4. A machine as claimed in any of Claims 1 to 3, characterized in that the rear end of the tool frame relative to the working direction is mounted in two longitudinal guides arranged at the opposite lateral outsides of the main frame and in that the front end of the tool frame is formed by two longitudinal girders in the form of longitudinal guides, or by one such longitudinal girder, mounted at approximately the transverse center of the main frame (Figures 1 to 5 and 9).

5. A machine as claimed in Claim 4, characterized in that those parts connected to the tool frame of the two rear longitudinal guides arranged at the lateral outsides of the main frame and formed by guide posts or by roller tracks or guideways are arranged in the upper part of the tool frame near the tamping unit (Figures 1 to 5).

6. A machine as claimed in any of Claims 1 to 5, characterized in that the longitudinal girder(s) forming the longitudinal guide(s) arranged at the front end of the tool frame is/are mounted on the main frame, preferably on a downwardly projecting bracket, between the track lifting and lining unit and the preceding undercarriage of the machine.

7. A machine as claimed in any of Claims 1 to 6, characterized in that the tool frame is longitudinally guided by roller guides each comprising at least two rollers which are mounted on the tool frame or on the main frame about horizontal shafts extending transversely of the longitudinal axis of the machine and which are respectively designed for application, preferably without any play, to an upper and a lower horizontal, longitudinally extending roller track or guideway of the main frame or the tool frame (Figures 1 to 5 and 9).

8. A machine as claimed in Claim 7, characterized in that at least one roller of the roller guide is provided on one or both sides with side rims designed for application to the side edge(s) of the associated roller track or guideway (Figures 1 to 5).

9. A machine as claimed in any of Claims 1 to 8, characterized in that the tool frame carrying the tamping, lifting and lining units intended for both rails of the track is additionally designed to be displaced and pivoted relative to the main frame by at least one drive in a plane substantially parallel to the plane of the track transversely of the longitudinal axis of the machine (Figures 1 to 4).

10. A machine as claimed in Claim 9, characterized in that at least the rear end of the tool frame is mounted for displacement along a horizontal shaft or guide post which extends transversely of the longitudinal axis of the machine and of which the outer ends are each connected to one of the two laterally opposite roller guides (Figures 1 to 4).

11. A machine as claimed in Claim 10, characterized in that the shaft or guide post is in the form of a full-length piston rod, comprising a piston at its longitudinal center, of a double-acting hydraulic cylinder which surrounds it and which, with the piston, forms the transverse displacement drive, the associated end of the tool frame being connected to said double-acting hydraulic cylinder, Figures 1 to 4.

12. A machine as claimed in any of Claims 7 to 11, characterized in that the two roller guides connected to the rear end of the tool frame are formed on each side of the frame by rollers provided on at least one side with a side rim or by pairs of such rollers designed for application to the upper side and lower side of one of the two lateral main longitudinal girders of the main frame of the machine (Figures 1 to 4).

13. A machine as claimed in any of Claims 1 to 12, characterized in that the tool frame and main frame are joined together in the region of the longitudinal guides by absorbing elements which absorb body noise and shocks.

14. A machine as claimed in any of Claims 1 to 13, characterized in that the common longitudinal displacement drive consists of two double-acting hydraulic-and-cylinder piston assemblies of which the cylinders functioning as active drive components are connected to the tool frame, preferably above each of the tamping units associated with the particular rail (Figure 5).

15. A machine as claimed in any of Claims 1 to 6 and 14, characterized in that the two rear longitudinal guides each consist of a longitudinally extending guide post which is connected to the main frame and on which a piston and a hydraulic cylinder connected to the tool frame are arranged to form the longitudinal displacement drive (Figure 5).

16. A machine as claimed in any of Claims 1 to 6, characterized in that, at its front and rear ends, the tool frame comprises two longitudinally extending guide posts which project over the two rails and which are slidably guided in guide sleeves or the like connected to the main frame, Figure 6.

17. A machine as claimed in any of Claims 1 and 2 and 4to 13, characterized in that the common longitudinal displacement drive is formed by an endless chain drive which is connected to a drive motor forming the active drive component, which is preferably arranged on the main frame of the machine, more especially at approximately its transverse center, and with one, longitudinally extending flight of which the tool frame is drivingly connected (Figure 6).

18. A machine as claimed in any of Claims 1 and 2 and 4 to 13, characterized in that the common longitudinal displacement drive consists of a rackand-pinion drive comprising a longitudinally extending rack and, engaging therein, a pinion connected to a drive motor forming the active drive component, the rack preferably being arranged on the main frame of the machine and the pinion together with the drive motor on the tool frame, Figure 7.

19. A machine as claimed in Claims 1 and 2, characterized in that the front and/or rear end of the tool frame is suspended pendulum-fashion from the main frame by two longitudinally adjustable guide rods which are situated opposite one another relative to the longitudinal axis of the machine and which are mounted to pivot about a horizontal pivot extending transversely of the longitudinal axis of the machine, being formed in particular by hydraulic cylinder-and-piston assemblies (Figures 8 and 9)

20. A machine as claimed in Claim 19, characterized in that the longitudinally adjustable guide rods each in the form of double-acting hydraulic cylinder-and-piston assemblies and the longitudinal displacement drive are connected to a control unit through which the effective length of the guide rods is variable according to a predetermined angular function in dependence upon the displacement path of the longitudinal adjustment drive, Figure 8.

21. A tamping levelling and lining machine substantially as herein described with reference to Figures 1 to 4, or any of Figures 6 to 9, of the accompanying drawings.