Tamping equipment for track tamping machinery

Abstract

A tamping device for track tamping machinery includes multiple pairs of tamping tools mounted on a support, the support being height-adjustably guided within a frame of the tamping device. The pickaxe ends of the tamping tool pairs are driven in opposite directions by linear oscillating actuators and are hydraulically fed relative to each other. At least two tamping devices are arranged along a longitudinal axis of the tamping device parallel to the longitudinal direction of the track tamping machinery. At least two tamping devices are arranged side-by-side transversely to the longitudinal axis of the tamping device. Two spaced-apart planes perpendicular to the longitudinal axis of the tamping device on either side of the support form a working space. A rocker arm and the tamping tool pairs trace a motion trajectory within the working space via the pickaxe ends during feeding motion. The envelope of this motion trajectory lies only within the working space. The linear oscillating actuators of the tamping device are arranged overlapping each other in an oscillation plane extending transversely to the plane and are at least nearly parallel to each other and inclined relative to the longitudinal axis of the tamping device.

Description

Technical Field

[0001] This invention relates to a tamping device for track tamping machinery, comprising a plurality of tamping tool pairs designed as rockers mounted on a support, the support being height-adjustably guided within a frame of the tamping device. The lower pickaxe ends of these tamping tool pairs, for insertion into the ballast bed, are driven in opposite directions by linear oscillating actuators and are hydraulically fed relative to each other. At least two tamping devices are arranged sequentially along a longitudinal axis parallel to the longitudinal direction of the track tamping machinery, and at least two, preferably four, tamping devices are arranged side-by-side transversely to the longitudinal axis of the tamping device. For each tamping device, two planes spaced apart by the rail sleeper spacing and arranged perpendicular to the longitudinal axis of the tamping device on either side of their respective supports define a working space. The rockers and tamping tool pairs trace a motion trajectory within this working space via the pickaxe ends during oscillating feeding motion. The envelope of this trajectory lies only within the working space. The linear oscillating actuators of the tamping device are arranged overlapping each other in an oscillating plane extending transversely to the planes. Background Technology

[0002] Such tamping equipment is known from published document AT 522456B1, in which a linear oscillating actuator is arranged along the longitudinal axis of tamping. The known arrangement depends on the different lengths of the lever arms of the rockers that are paired with each other. Document CN101775765 A discloses a similar arrangement.

[0003] The tamping device (DE 24 24 829 A) inserts ballast from the track bed into the area between two sleepers (sleeper box) using tamping tools, into the ballast under the rail in the area of ​​the sleeper supports, and compacts the ballast between opposing, feedable picks using the dynamic vibration of the picks. The tamping device can be designed and arranged such that it tamps one, two, or more sleepers in its working cylinder.

[0004] Specialized turnout tamping equipment exists for tamping turnouts. This includes single-sleeper tamping equipment and double-sleeper tamping equipment, such as the so-called split-type tamping equipment. To tamp the sleepers on the side of the track, two tamping tools are inserted longitudinally along the left and right sides of the rail to the front and rear of the sleepers for compaction. In tamping equipment not designed as split-type, all eight tamping tools, along with the crank and actuator, are located on the tamping frame. In split-type tamping equipment, the equipment is designed separately. There is one half for tamping the inner left side of the rail and one half for tamping the right side. Each split-type tamping equipment has four tamping tools. These four tamping tools are laterally rotatable in equivalent turnout tamping equipment. The advantage provided by this is that these tamping tools can be positioned appropriately or completely rotated out of that position during the tamping process. This design is considered advantageous when tamping turnouts due to the presence of numerous obstacles (trains, frogs, turnout actuators, branch rails). Tamping equipment can also be constructed as a continuously moving machine on cyclic tamping machinery.

[0005] Multiple sleepers can be tamped separately in a single tamping cycle, allowing for faster operation. To date, a maximum of four sleepers can be tamped in one cycle on a continuous tamping machine. Single-sleeper and double-sleeper tamping machines are currently installed in turnout tamping machines. This allows for the versatile use of turnout tamping machines, as they can also achieve high operating speeds when tamping tracks or connecting lines. Therefore, this design can be applied flexibly to turnouts if separate tamping units are arranged sequentially along the track's longitudinal direction. Double-sleeper turnout tamping machines contain a total of eight separate tamping units (four on each side), which can be inserted independently of each other. In some tamping machines, the front separate unit on one side is designed as a "standard" track tamping unit, which is unusable in many areas with turnouts and remains in a waiting position. The rear separate unit is designed with a rotating pickaxe. The front pickaxe of the rear split-type device and the rear pickaxe of the front split-type device must be inserted into the same sleeper box and can be further fed after the insertion process. Thus, the available space of the split-type device can be smoothly utilized in the area of ​​the sleeper box. An eccentric shaft drive is typically used to generate vibration, causing the rocker arm to be in an oscillating motion. In this embodiment, the hydraulic cylinder for the feed motion must be centrally hinged to the eccentric shaft via a connecting rod. Therefore, the drive cylinder that applies force in the area of ​​the sleeper box must be designed to be very short and must operate through offset lever arms and force transmission conditions. This significantly increases the required pressure in such a short feed cylinder because the shorter stroke increases the requirements for piston sealing, piston and cylinder working surfaces, reducing equipment lifespan. In equivalent monorail sleeper split-type turnout tamping equipment, all four pickaxes are designed to be rotatable. This provides the highest flexibility of the equipment during turnout operation.

[0006] In the design of double-sleeper tamping equipment, due to space constraints and limitations imposed by the eccentric shaft drive, only the outermost picks in the sleeper box area are designed to be rotatable, located between the front and rear split units on one side. The inner pick is rigidly fixed to a rocker arm. This results in significant limitations in turnouts, as in the prior art the front and rear split units are also mounted on a common frame. Even though the tamping frame can move laterally, a common problem is that one of the non-rotatable picks may encounter an obstacle in the turnout and thus be unable to descend, reducing flexibility and operating speed in turnouts.

[0007] The movement of a tamping device includes the vertical insertion of a pickaxe into the ballast, a feed motion, and superimposed dynamic vibrations, in which the ends of the pickaxes close relative to each other during the feed motion, and the vibrations cause the ballast to be compacted. It is known to use a hydraulic cylinder in the feed motion, which is connected via a connecting rod to an eccentrically oriented oscillating shaft, and the feed motion is superimposed on the oscillating motion (AT 369 455B). This oscillating shaft and connecting rod are supported on rolling bearings, which typically require expensive maintenance. The magnitude of the resulting oscillation is mechanically determined and by hydraulic excitation. The amplitude cannot be freely set. Another known solution uses linear excitation via hydraulic cylinders. In this solution, two hydraulic cylinders are mechanically coupled in series. One cylinder is designed for the feed motion, and the other for the oscillating motion. In newer applications, a so-called hydraulic tamping drive is used, in which tamping oscillations and linear feed motion are simultaneously generated via a proportional valve integral with the hydraulic cylinders (EP 27701018 A1).

[0008] The ideal tamping frequency for compaction is known to be between 25-40 Hz, where a pickaxe can be inserted into the ballast more easily at a higher frequency because it produces only a lower insertion impact and thus reduces the support requirements for the pickaxe equipment. Summary of the Invention

[0009] The technical problem to be solved by the present invention is to further improve the aforementioned type of tamping equipment with simple devices, so that all the picks of the split equipment arranged longitudinally along the track can be designed to be rotatable, so that the opening width of all the rockers can be controlled independently, and multiple rockers can be designed to have the same transmission characteristics, and the linear drive does not need to be shortened, thus achieving a long service life.

[0010] The technical problem is solved according to the present invention by the fact that the linear oscillation driver of the tamping device is arranged at least almost parallel to the longitudinal axis of the tamping device.

[0011] This ensures that the working space of the tamping equipment, which is supported or defined by two planes during the feeding motion and continues until the adjacent sleepers are tamped, is not encroached upon by the components of the tamping equipment.

[0012] Thus, linear actuators are positioned at known eccentric actuator locations, arranged overlapping and side-by-side, such that their length is unrestricted. The geometry of the rocker and swing arm is designed such that they follow the outer boundary of the plane extending to the adjacent device, and the linear actuators moved out to close the pickaxe also follow a confined space. This allows the pickaxes of the split-type tamping device to rotate both inside and outside the rail, enabling these tamping tools to rotate laterally longitudinally relative to the rail tamping machinery, particularly via rotating cylinders. An additional advantage of the invention is its modular construction, which allows any number of tamping devices to be connected in series closely together along the rail longitudinal direction.

[0013] The linear oscillating actuators are preferably designed as identical components to achieve symmetrical tamping effects and to have the same stroke and piston diameter as hydraulic cylinders with the same structural length. The linear oscillating actuators are preferably inclined at an angle of 5 to 45°, particularly a maximum of 20° (up to 15° if necessary), relative to the longitudinal axis of the tamping device. This angle is preferably in the open position, where the ends of the pickaxe are maximally separated from each other. In the closed position of the pickaxe ends, the angles of the two linear oscillating actuators relative to the longitudinal axis of the tamping device may differ in some cases depending on the structural conditions, or vice versa. However, the linear oscillating actuators are inclined relative to the longitudinal axis of the tamping device in every position, even though the angles of the oscillating actuators relative to the longitudinal axis of the tamping device to which they belong may deviate from each other by a maximum of 15°, particularly a maximum of 10°, throughout the entire working stroke.

[0014] The essential advantage lies in its simple construction, utilizing linear actuators that offer numerous advantages. These linear oscillating actuators are preferably fully hydraulic, controllable by proportional valves. This allows for flexibility in turnout operations through the rotatability of all the pickaxes, improves actuator lifespan, imposes identical requirements and designs on the rocker arms, and allows for the close-connection of multiple identical devices—a modular construction. If the individual frames of the modular device are also designed to be independently laterally movable, maximum flexibility and mechanical efficiency in turnout operations are provided. Another advantage is the symmetrical structure, which allows for less inventory management of components and cost savings for the user. Attached Figure Description

[0015] The technical solution of the present invention is illustrated by way of example in the accompanying drawings. In the accompanying drawings:

[0016] Figure 1 A side view of the tamping device according to the invention is shown.

[0017] Figure 2A view of the tamping device according to the invention is shown.

[0018] Figure 3 This illustrates a turnout tamping device with a linear actuator for tamping a single sleeper, according to the prior art.

[0019] Figure 4 A schematic diagram of a continuous tamping machine is shown, which has two tamping devices arranged longitudinally, mounted on independent tamping frames that are movable transversely to the longitudinal direction of the track.

[0020] Figure 5 The diagram shows different arrangements and implementation methods of the tamping equipment. Detailed Implementation

[0021] The tamping device W1 for track tamping machinery A has multiple pairs of tamping tools 7, 8 mounted on a support 4 and designed as rockers 13. The support is height-adjustable within the frame of the tamping device. The lower pickaxe ends 10 of these tamping tool pairs, for insertion into the ballast bed, are driven in opposite directions by a linear oscillating driver 2 and are hydraulically fed relative to each other. Each pair of at least two tamping devices W1... H W1 V The tamping devices are arranged sequentially along a longitudinal axis L parallel to the longitudinal direction of the track tamping machine, and at least two, preferably four, tamping devices are arranged side by side transversely to the longitudinal axis L. For each tamping device W1, two planes 1, spaced apart by rail spacing a and arranged perpendicular to the longitudinal axis L on both sides of the respective support 4, support the working space R. The rocker arm 13 and the tamping tool pair 7, 8 trace a motion trajectory within the working space through the end of the pickaxe 10 during an oscillating feed motion 14. The envelope H of this motion trajectory lies only within the working space R.

[0022] The linear oscillation actuators 2 of the tamping device W1 are arranged overlapping each other in an oscillation plane extending transversely to the plane 1, and in particular, are arranged overlapping each other and at least almost parallel to each other, inclined relative to the longitudinal axis L of the tamping device. Furthermore, all tamping tool pairs 7 and 8 are capable of rotating transversely to the longitudinal direction of the track tamping machinery via rotating cylinders 6 and 9.

[0023] Figure 1A tamping device W1 for tamping a turnout, designed according to the present invention, is shown. It has a rocker arm 13 and correspondingly rotatable front pickaxe holder 7 and rear pickaxe holder 8, both equipped with pickaxes 10. Two tamping devices W1 arranged side-by-side along the longitudinal axis L parallel to the longitudinal direction of the track tamping machinery constitute a split device and are inserted into the ballast on the left and right sides of the rail 12 to compact the ballast under the sleeper 11 by means of the vibratory closing motion of the pickaxes 10. Linear actuators 2 are arranged obliquely overlapping each other, such that these linear actuators can be ideally and sustainably constructed in terms of their design length. For this purpose, hydraulic linear actuators 2 with proportional valves 3 are used. The rocker arm 13 is constructed such that the hinge point 17 is located within a reliable movement space 1 to such an extent that the removal of the linear actuator 2 does not interfere with the movement of subsequent tamping devices arranged longitudinally along the track. The hinge point 18 of the linear actuator is supported on the tamping frame 4. The tamping equipment frame 4 is lowered and raised by being guided on the vertical guide post 5. The pickaxe holders 7 and 8 rotate via rotating cylinders 6 and 9. The rotating cylinders 6 and 9 are fixed to the pickaxe holders 7 and 8 on one side and supported on the rocker arm 13 on the other side. The linear tamping actuators 2 are arranged obliquely, overlapping each other, as shown at 17 and 18. The linear oscillating actuators 2 are preferably inclined at angles α1 and α2 of 5 to 45°, especially a maximum of 20°, relative to the longitudinal axis L of the tamping equipment. Furthermore, the linear oscillating actuators 2 are particularly designed to be identical components.

[0024] Figure 2 A side view of the tamping device W1 according to the invention is shown. The rocker arm 13 supports a joint having pickaxe holders 7 and 8 and a pickaxe 10. The inner pickaxe holder 8 is rotatable by a rotary cylinder 6. The rocker arm moves via linear actuators 2 and 3. The tamping frame 4 moves up and down along a vertical guide post 5.

[0025] Figure 3 A split-type device C, designed in a conventional manner according to the prior art, is shown. It is characterized by a restricted area 1, which is utilized by an adjacent tamping device. 15 shows an area damaged by the extended rocker arm. 16 shows an area where the rocker arm has already damaged the area in the insertion position and will be further moved into the locked area 1 by the removal 14 of the linear actuator during feeding.

[0026] Figure 4 A continuous tamping machine A is schematically shown, which has two tamping devices W1 arranged longitudinally in sequence, and these two tamping devices can move laterally along the track independently of each other.

[0027] Figure 5The diagram schematically illustrates the arrangement and design scheme according to existing technology. S1 schematically illustrates a split-type monosleeper track tamping device, which has a non-rotatable inner pickaxe IN and an outer pickaxe AS. These pickaxes are arranged side by side along the transverse direction of the track, but they are only shown in a simplified, generally side by side, manner in the accompanying drawings. W1 schematically illustrates an equivalent turnout tamping device (such as...). Figure 3 The prior art (as shown in the diagram) has a rotatable inner pickaxe IN and an outer pickaxe AS. This type of device cannot be constructed sequentially along the track longitudinal direction because these devices would collide with each other in the sleeper box area. W2 schematically shows a standard double-sleeper turnout tamping device (SdT) driven by an eccentric shaft, which has a rotatable outer pickaxe and an inner pickaxe. For spatial reasons, the inner pickaxe is also designed to be non-rotatable in the area of ​​the inner sleeper box. Arrangement D, known from the prior art, shows the rear turnout tamping device W0.5. H It has a rotatable inner pickaxe and an outer pickaxe on the rear side, but a non-rotatable inner pickaxe in the area of ​​the common sleeper box. Line tamping device S1 V Arranged at the front, it features a normally non-rotatable pickaxe. Arrangement E shows two turnout tamping devices W0.5. H W0.5 V The two turnout tamping devices are designed in a mirror-symmetric manner. Arrangement F shows two identical turnout tamping devices W1. H W1 V According to the feasible design scheme of the present invention, in this design scheme of turnout tamping equipment arranged sequentially along the longitudinal direction of the track, all pickaxes can rotate as a unique arrangement. Furthermore, this arrangement can be extended with additional sleepers during simultaneous tamping (extending to a three-sleeper tamping machine or a four-sleeper tamping machine) thanks to its modular structure.

Claims

1. A tamping device for a track tamping machine (A) comprising a plurality of tamping tool pairs (7, 8) mounted on a support (4) and designed as rockers (13), the support being height-adjustably guided within a frame of the tamping device, wherein the lower ends of the pickaxe tips (10) of these tamping tool pairs for insertion into the ballast bed are driven opposite to each other by a linear oscillating driver (2) and are hydraulically fed relative to each other, wherein, At least two tamping devices are arranged sequentially along the longitudinal axis (L) of the tamping device parallel to the longitudinal direction of the track tamping machinery, and at least two tamping devices are arranged side by side transversely to the longitudinal axis (L). For each tamping device, two planes (1) arranged perpendicular to the longitudinal axis (L) of the tamping device on both sides of the respective support (4) and spaced apart by the rail sleeper spacing support the working space (R). The rocker arm (13) and the tamping tool pair (7, 8) trace a motion trajectory in the working space through the end of the pickaxe (10) during an oscillating feed motion (14). The envelope of the motion trajectory is located only in the working space (R). The linear oscillating driver (2) of the tamping device is arranged overlapping each other in an oscillating plane extending transversely to the plane (1). The linear oscillating driver (2) of the tamping device is characterized in that it is arranged at least almost parallel to the longitudinal axis (L) of the tamping device.

2. The tamping device according to claim 1, characterized in that, The linear oscillation driver (2) is a fully hydraulic linear oscillation driver (2) that is controllable by a proportional valve (3).

3. The tamping device according to claim 1, characterized in that, The tamping tools (7, 8) can rotate laterally to the longitudinal direction of the track tamping machine via rotating cylinders (6, 9).

4. The tamping device according to any one of claims 1 to 3, characterized in that, The linear oscillation driver (2) is tilted at an angle (α1, α2) of 5 to 45º relative to the longitudinal axis (L) of the tamping device.

5. The tamping device according to claim 4, characterized in that, The linear oscillation driver (2) is tilted at an angle (α1, α2) of up to 20º relative to the longitudinal axis (L) of the tamping device.

6. The tamping device according to claim 1, characterized in that, The linear oscillation driver (2) is designed with the same components.

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