DE2652760A1 - VIBRATING DRIVE MECHANISM FOR A VIBRATING TOOL, IN PARTICULAR A GRALL TAMPER - Google Patents

Description

Vibrating drive mechanism for a vibrating tool, in particular a ballast tamper

Opposing, pivotably arranged tamping arms are set in vibration by means of corresponding, single acting hydraulic piston assemblies provided by separate hydraulic double rotary distribution valves being controlled. The liquid inflow and outflow lines for each piston assembly are connected to a source of pressurized hydraulic fluid via the appropriate rotary valve tied together. Each valve has a stationary, apertured shroud that is cylindrical in shape Receives rotary valve stem having a pair of axially shifted inflow and outflow passages, which alternate with inflow and outflow openings in the cladding towards the / ms direction opening and closing the connections between the corresponding piston assembly and the inflow and Drain pipes. While the rotary valves are preferably driven by a common drive unit, the relative phase of the oscillations of the arms can be determined by rotating one of the valve spindles with respect to the others by the desired phaser.angle bestiirx.it v / earth.

The invention relates generally to the field of railroad ballast tampers or track tamping machine :! and hydraulic systems for forming a vibrating movement and in particular hydraulic vibrator systems for actuating the track tamping device.

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The subject of the invention is based on the prior art Track tamping machines such as those found, for example, in US Pat. No. 3,135,223. With this system, a pair is more plier-like Tamping arms can be swiveled on a specially designed railway wagon With a suitable hydraulic system arranged so that the tamping arms penetrate deeply into the ballast on each side the end of a threshold can be driven. The upper ends of the stuffing arms are yoke to an eccentric one Shaft coupled. The rotation of the eccentric shaft imparts the vibratory motion to the lower ends of the stuffing arms, thereby the ballast is compacted. The ends of the stuffing arms extend down into the gravel under the sleeper and are gradually moved by the hydraulic arrangement during the compaction process pressed together. Hydraulic systems for controlling the distance between the tamping arms are disclosed in US Pat U.S. Patents 3,211,064, 3,146,727, 3,372,651, 3,357,366, 3,608,498, 2 872 878 and 3 669 025, as well as 2 791 971.

As can be seen from the information in US Pat. No. 3,135,223, the Schotterstopfen.normally in connection with a Height straightening carried out. If it is found that a threshold is too low, the same is done by means of a hydraulic one Raised arrangement, which is located on the tamping device, while the ballast is compacted to the appropriate To raise sleeper ends that carry the rail section. In all of these systems, the vibration of the Stuffing tool caused by the eccentric arrangement and not so much by the hydraulic piston device. To the Disadvantages associated with using an eccentric vibratory mechanism include the cost of replacement and the maintenance of the eccentric mechanism and the overall complexity of the unit. Furthermore, the eccentric shaft is required a flywheel, which between the stuffing processes on adjacent Thresholds cannot be started and stopped. Even while lifting the stuffing arms to move them the vibrating movement continues to the next tamping point, which results in inappropriate wear and tear, Energy consumption and noise development results.

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According to the prior art, a hydraulic piston arrangement is axich has been considered in the context of imparting vibratory motion to stuffing arms. After US Pat. No. 2,973,719 is a double acting hydraulic piston which operates under the control of a rotary hydraulic distribution valve stands on, a rack that meshes with a pinion on a shaft, creating a pair of shifted jaws at the end of the Shaft is set in oscillatory motion. The rotary valve results in six reciprocating movements per revolution while applying a twisted double main line arrangement and chord-shaped Passages in the valve spindle inside the rotary valve. U.S. Patent No. 3,735,708 teaches the use of a hydraulic one Piston engine with an automatic flip-flop valve for the vibration of the tamping tool. The general explanations in US Pat. No. 3,735,708 point out the general disadvantages caused by the use of separate, coaxially arranged, hydraulic Cylinder for vibrating the tamping tools are conditioned.

U.S. Patent No. 2,022,738 discloses a highly intricate hydraulic one Rotary control valve for operating a pump. The rotary valve controls the supply and discharge hydraulically Fluid to and from double acting hydraulic twin pistons with uniform outlet velocity the liquid from the pump.

The general object underlying the invention is in giving a tool a vibrating or oscillating motion. The invention is particularly the task based on a simple hydraulic vibrating drive for a pair of opposing, pivotably arranged To create darning arms.

These objects of the invention are achieved in that a hydraulic system with a pair of corresponding, ram-operated = single-acting hydraulic piston for reciprocating the ends of a pair of corresponding pivotably arranged pincer-like stuffing arms is provided. Any single acting piston cylinder

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has inflow and outflow lines connected to a source of pressurized hydraulic fluid via a corresponding Rotary distribution valve assembly are in communication, which alternate the cylinder with the inflow and outflow lines connects. The corresponding rotary valves for a pair of stuffing arms are driven in unison at the same frequency. Each rotary valve has a rotating valve stem that has a pair of passages intersecting the axis of rotation and are alternately brought into line with aligned openings in the casing in which the valve stem rotates. at In the preferred embodiment, the aligned openings are located in the casing for the inflow line on a diameter which is rotated by 90 ° with respect to the diameter that of the aligned openings in the casing for the drain line lie. The relative oscillation phase of the two stuffing arms can be adjusted by rotating one of the valve spindles relative to the other to be set. The cross-sectional shape of the passages in the valve stem is different in various embodiments designed so that during the rotation of the valve spindle either a gradual or sudden opening and closing takes place with respect to the passage of liquid through the valve.

The subject matter of the invention is explained here, for example, in connection with a track tamping device, but it goes without saying that the vibration system can also be used with other vibration equipment, such as shredders for Rock, vibrators for concrete, hardeners for roadbeds, tools for driving nails and other impact or Vibrating devices, such as spacers for railway sleepers, Track aligner, impact wrench, hammer and drill.

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An embodiment of the invention is shown in. Drawings shown and is described in more detail below. Show it:

Figure 1 is a side elevational view with parts broken away are that arranged the track tamping device according to the invention shows on a corresponding vehicle;

FIG. 2 is an isometric view of the right rotary valve of FIG. 1 on an enlarged scale;

3 shows a sectional view of the rotary valve along the line 3-3 according to FIG. 2;

Figure 4 is a cross-sectional view of the rotary valve taken along line 4-4 of Figure 3;

FIG. 5 shows a view of the rotary valve which is identical to FIG. 4 with the exception that the valve spindle part is rotated by 90 °;

FIG. 6 is a sectional view of the rotary valve along line 6-6 of FIG. 5;

7 shows an isometric view of the valve spindle of the rotary valve according to FIGS. 2 to 6 showing details;

8 is a detailed isometric view of an optional embodiment of the passages in the valve stem;

Figure 8A is a broken away schematic view of the relationship between the triangular passage of Figure 8 and the opening in the casing of the rotary valve;

9 through 12 are similar views showing the relationships between the configurations of the passages in the valve stem portion and the Openings in the casing of the rotary valve.

Since the subject of the invention is neither with the movable carriage for the track tamper nor with devices for the Positional arrangement of the track tamp in relation to the end of the rail sleeper is concerned, the relevant elements are not shown in detail in connection with the explanation of the preferred embodiments, as each conventional type for these purposes in connection with the .Vibrationsvorrichtung invention can be applied.

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Figure 1 shows a pair of opposing stuffing arms 10 and 12, which are pivotably arranged at points P on the trough assembly 14, and this support assembly is on a special laid out railway wagon 16 carried. The lower ends 10a and 12a of the stuffing arms 10 and 12 carry stuffing vanes for compaction of the ballast present under a given sleeper 18. The upper ends 10b and 12b of the stuffing arms 10 and are pivotably articulated to identical single-acting hydraulic piston assemblies 20 and 22, which are in working connection between the upper ends 10b, 12b of the respective stuffing arms and the support assembly 14 are connected.

In a practical embodiment, the support arrangement would 14 may be provided with a hydraulic device by means of which the pivot points P of the two tamping arms 10 and 12 are drawn together are producing a compressive effect, whereby a further compaction of the ballast is achieved during the stuffing arms by the hydraulic piston assemblies 20 and vibrated.

Just like the piston assembly 22, the piston assembly 20 is through a pressurized fluid (typically oil) in the chamber 24 is actuated, which acts on the piston 26 against the force a compression spring 28 or equivalent resilient element acts. As soon as the chamber 24 receives the pressurized liquid, the piston 26 is driven in the liniks and takes the power output shaft 30 with it, which is pivotable at the end 1Ob of the Stuffing arm 10 is articulated. The hydraulic fluid will introduced into the chamber 24 and removed therefrom, by means of the inflow line 32, which passes through an open opening on the back · The lower end of the chamber 24 is connected, as well as the drain line 34, which passes through an open opening in the side of the chamber 24 is connected.

The inflow and outflow lines 32 and 34 are connected to a source 36 of pressurized hydraulic fluid a double rotary distribution valve 38 continuously driven by a main drive source 40

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like the power take-off shaft of the diesel engine, which is also drives the railroad car 16. In a similar way it is other hydraulic pistons 22 via the inflow and outflow lines 42 and 44 with the hydraulic fluid source 36 via a separate, but preferably identical, double rotary distribution valve 46, which is continuously driven preferably by the same main drive source 40.

As such, the hydraulic pressure source 36 is of conventional construction and typically has as separate components a sump or reservoir for the hydraulic fluid, to which the drain line 34 and the line 44 extend, as well as a pump, such as a gear pump, which draws the hydraulic fluid from the sump and the under Hydraulic fluid under pressure is available at the outlet. The outlet is with the inflow lines 32 and see Figure 1, connected. Weitenin is inside the hydraulic Source 36 typically a pressure regulating arrangement or a safety device with bypass lines between the outlet of the pump and the sump. All of these components are of conventional design, such as those at hydraulic systems is known that are used in a wide variety of applications. Possibly however, the same main drive source 40 can be used to drive the pump (not shown?) in the hydraulic source 36 will.

The rotary distribution valve 46 is shown in detail in FIGS. As FIGS. 2, 3 and 4 show, the rotary valve 46 has an inner, apertured, cylindrical valve spindle 48 which is present in a tubular, apertured, cylindrical casing 50 and therein for the purpose of revolving by means of end-face ball bearing arrangements 52 and 54 is mounted. An external drive source 56 is coaxially attached to the end of the valve stem 48 for rotating the stem 48 inside the enclosure 50. The drive means 56 and the spindle 48 are preferably formed in one piece as a single component. Lubricating rings 58 form annular reservoirs for lubricating the tightly dimensioned and matched surfaces of the valve stem

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and the casing 50. The lubricant is typically the hydraulic fluid. The valve stem 48 has therein formed either by a machining treatment or by casting a pair of axially spaced relationship Passages 60 and 62 which, according to the preferred embodiment, are centered on parallel diameters of the valve spindle 48 are and have cylindrical channels through the valve stem 48. The passages 60 and 62 are detailed with reference to the figure 7, which shows the valve spindle 48 without the casing 50.

The casing 50, see Figures 2 to 4, has a pair of aligned openings 64 and 66 with threaded counterbores, the corresponding threaded fittings 68 and 70 to which the threaded ends of the inflow line 42 are connected. the Openings 64 and 66 of the casing are along an oil diameter are aligned and axially aligned with casing 50 and are further sized to include openings 64 and 66 the passages 60 are always in alignment when the valve stem member 48 is properly oriented, see FIG FIGS. 3 and 4 for this purpose.

A similar set of aligned openings 72 and 74 in FIG Casing 50 is used for drain line 44. The counterbore openings 72 and 74, shown in dashed lines in FIGS. 4 and 5, accommodate corresponding fittings 76 and 78 on which the threaded ends of the drain line are attached. The aligned Openings 72 and 74 for the drain line have one such a size and are in such a spacing relationship that alignment with dome passage 62 takes place and are further centered on a diameter of the casing 50 that is rotated 90 ° with respect to the diameter on which the aligned Openings 64 and 66 are for the inflow line. If the valve spindle part is thus rotated through 90 °, see FIG. 5, the passage 60 becomes transverse with respect to the inflow line 42 reoriented, thereby interrupting the supply of the pressurized liquid, while, see FIG FIG. 6, the parallel passage 62 aligned with the openings 72 and? 4. This opens the drain line 44

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and the hydraulic fluid is discharged from the chamber (not shown) of the hydraulic piston 22, see FIG. 1 removed.

In operation, the connections between the tributary and Drain lines 32, 42 and 34,44 continuous through the Rotation of the valve spindles in the rotary valves 38 and 46, see Figure 1, changed, whereby a change in the Pressure build-up and pressure reduction of the single-acting hydraulic pistons 20 and 22 results in the stuffing arms 10 and 12 are vibrated at the same frequency. The phase relationship between the vibration of the respective arms 10 and 12 can be changed by changing the relative effective orientation of the valve spindles of the rotary valves 38 and 46 uia the desired phase angle is changed. While the valve spindle part executes one complete revolution, the inflow line is opened twice and closed twice / while the drain line is open, causing two full reciprocating movements of pistons 20 and 22 per Revolutions of the valves 38 and 46 result.

In FIG. 8, an optionally inventive embodiment is shown, in which there are parallel passages 80 and 82 with triangular cross-sectional parts. As shown schematically in FIG. 8, when the valve spindle 48 'is rotated, the passage 80 is brought into alignment with the opening 46 in the casing 50, and the tapered part of the opening first occurs when the valve spindle is rotated, so that there is a channel between the aligned openings 64 and 66 of the casing, see Figure 3, which gradually opens wider than the fillet is in the case of the cylindrical passages. In the embodiment of Figure 8, one side of the triangular cross-section is provided so that it is roughly parallel to the axis of rotation, so that as the valve spindle 48 'continues to rotate, the channel is suddenly interrupted after it has gradually opened. VJLg. As shown in FIGS. 9 to 12, the principle of the special provision of the cross-sectional shape of the passages or the opening for the purpose of influencing the opening or closing

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of the flow channels can be implemented in many different ways.

FIG. 9 shows the passage 84 with an ellipsoidal cross section in a modified valve spindle 48 ', which with. a cylindrical opening towards the / m direction. One ellipsoidal opening is also obtained on the valve spindle with a tendon-shaped, cylindrical passage. The figure 10 shows the cylindrical passage 60 of the first embodiment, the one with the triangular opening 86 according to the modified one Casing 50 'comes into alignment. Figure 11 shows one triangular passage 88 formed in the valve stem 48 * and aligns with a square opening 90 in the casing 50 '. FIG. 12 shows a passage 92 with a diamond-shaped cross-section that aligns with a square opening 90 in the casing 50 '* This last embodiment leads to a gradual opening and closing of the liquid channel. Of course, the diamond shaped Cross-section can also be approximated by an ellipse, the minor axis of which is a-general parallel to the The axis of rotation of the valve spindle 48 'runs "

A tamping machine constructed according to the invention is in practice equipped with hydraulic pistons, which have a stroke of 4.8 mm and lead to 2,600 vibrations per minute Es Of course, there is no problem of stopping the drive mechanism for the vibration movement afterwards each compression cycle has been completed and while the arms are moved to the next threshold. Intermittent stopping can be achieved by that a separate manual valve is installed in the supply line leading to the rotary distribution valves, or by temporarily removing the rotary valves (valve spindles) from the main drive source can be released. In contrast to stuffing devices, the work with flywheel according to the prior art, the vibration speed of the invention hydraulic drive can simply be modified by

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that a change in the rotational speed of the rotary valve takes place so as to adjust to a preferred vibration range from 0 to 5000 vibrations per minute.

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Claims (23)

Claims 1. Vibrating drive mechanism for a vibrating tool, characterized in that a simple v / irkende hydraulic piston arrangement with an opening Pressure chamber and a reciprocatingly movable force output member which can be brought into working connection for the purpose of vibration a tool, a rotary distribution valve, a liquid inflow and outflow unit for the work connection the piston pressure chamber via the rotary valve to a source of pressurized hydraulic fluid, the rotary valve an apertured, cylindrical casing part with a first pair of openings in communication with the inflow line and a second pair of openings in communication with the drain conduit and axially offset from the first pair of openings a cylindrical valve spindle part provided with openings, axially received in the casing for sealed circulation therein and first and second axially offset Passages arranged for alternating alignment with the first and second pairs of jacket openings and, respectively a drive assembly for imparting continuous rotation to the valve stem part in the casing part. 2. Drive mechanism according to Claim 1, characterized in that the pairs of openings are at corresponding diameters of the casing part are aligned and the passages present on corresponding diameters of the valve spindle part. 3. Drive mechanism according to A nspruch 2, characterized in that the passages of the valve spindle part are parallel to each other, as well as the diameters on which the first and second pairs of the casing part openings are aligned are angularly displaced about the axis of the casing. 4. Drive mechanism according to claim 3, characterized in that the openings on the first and second - 13 - 709820/0834 ORIGINAL INSPECTED Pairs of openings are aligned and rotated through an angle of about 90 ° relative to each other. 5. Drive mechanism neich claim 1, characterized in that one of the passages has a cross section which is elongated in a direction which is approximately perpendicular to the axis of rotation of the valve stem part for the purpose of Determining the rate of opening or closing of the rotary valve. 6. Drive mechanism according to claim 1, characterized in that one of the passages has an elongate Has cross section which extends in a "direction approximately parallel to the axis of rotation of the valve spindle part for the purpose Determining the rate of opening or closing of the rotary valve. 7. Vibrating tandem drive mechanism for a couple in common vibrating tools, characterized in that first and second hydraulic piston assemblies with power output assemblies present in working connection with vibration of the corresponding tools and corresponding with openings having provided pressure chambers, a pair of separate rotary valve assemblies for controlling the operation of the piston assemblies, first and second pairs of inflow and outflow conduits, the corresponding ones Pressure chambers of the piston assembly with a source of pressurized hydraulic fluid via a of the respective rotary valve assemblies, each of the rotary valve assemblies is an orifice cylinder-shaped a piece of clothing with first and second pairs of openings, which are axially offset from one another and are in communication with the inflow and outflow lines and one inside in it Cylindrical valve spindle part provided with openings coaxially is received therein for the purpose of sealed circulation in the casing, and has formed therein first and second passages, which are axially shifted to one another and for a corresponding alternating alignment with the first and second Pairs of openings are arranged, and a drive arrangement for imparting continuous rotation to each of the valve stem parts each of the rotary valve assemblies are provided. - 14 - 709820/0834 8. Tandem drive mechanism according to claim 7, characterized in that the pairs of openings at corresponding Diameters of the cladding part are aligned and the passages at corresponding diameters of the valve spindle part are trained. 9. tandem drive mechanism according to claim 7, characterized g e k e η η ζ e i c hn et that an arrangement for setting the oscillation phase of one of the rotary valve assemblies is present with respect to the other. 10. Tandeiii drive mechanism according to claim 8, characterized in that the passages are in parallel and the first and second pairs of openings in the cover are rotated relative to each other about the axis of the cover will. 11. A tandem drive mechanism according to claim 10, characterized in that the first and second pairs of openings in the garment are rotated by approximately 90 ° with respect to each other about the axis of the garment. 12. Tanden drive mechanism according to claim 7, characterized in that one of the passages has a cross section which is articulated in a direction approximately perpendicular to the axis of rotation of the valve spindle part Determining the rate of opening or closing of the valve assembly. 13. Tandem drive mechanism according to claim 7, characterized in that one of the passages has a cross section which is elongated in a direction approximately parallel to the direction of rotation of the valve stem part for the purpose Determining the rate of opening or closing of the valve assembly. 14. Track ballast tamping device with a pair of opposite ones vibrating tamping arms pivotally mounted on a carriage having an arrangement for the bearing arrangement the corresponding lower ends of the tamping arms on each side of a railroad tie and for contracting the vibrating ones Arms while compacting the gravel underneath - 15 - 709820 / 083A has, characterized in that a pair of hydraulic Piston assemblies are in operative communication between the carriage and the upper ends of the stuffing arms such that that the reciprocating movement of each piston assembly causes the corresponding stuffing arms to vibrate with compaction of the gravel, each of the hydraulic piston assemblies has an inflow and an outflow line for filling and emptying the piston assembly with respect to the hydraulic fluid, a pair of rotary valve assemblies with which piston assemblies communicate for alternate communication the inflow and outflow lines for the corresponding piston assemblies with a common source of pressurized hydraulic fluid and a drive arrangement for imparting continuous rotation to each of the rotary valves are provided. 15. Track ballast tamping device according to claim 14 ,, thereby characterized in that each rotary valve has an orifice provided cylindrical outer garment attached to the carriage and a first pair of openings with the inflow conduit the second pair of openings communicates with the drain line, axially displaced with respect to the first pair the openings are present, an apertured, coaxial, cylindrical valve spindle part sealingly inside the cladding part is rotatably received with a pair of axially displaced passages therein and for an alternate one Aligned with the first and second pairs of openings and an arrangement for the drive connection of the valve stem part with the drive assembly for imparting continuous rotation of the valve stem part inside the Clothing item is present. 16. Track ballast tamping device according to claim 15, characterized in that the pairs of openings are connected to corresponding ones Diameters of the cladding part are aligned and the passages at corresponding diameters of the valve spindle part are trained. 709820/0834 " ¹⁶ " 17. Track ballast tamping device according to claim 16, characterized characterized in that the passages at parallel Diameters of the valve spindle part are formed and the pairs of casing part openings angularly relative to one another are shifted. 18. Track ballast tamping device according to claim 17, characterized characterized in that the pairs of openings in the casing part at axially spaced diameters of the cladding part, which over an angle is rotated by about 90 °. 19. Track ballast tamping device according to claim 14, characterized characterized in that each rotary valve assembly includes an arrangement for changing the relative phase of the alternate Opening and closing operations of the inflow and outflow lines the corresponding valve arrangements. 20. Track ballast tamping device according to claim 19, characterized characterized in that one of the rotary valves is angularly about its axis of rotation with respect to the other rotary valve is offset introducing a phase difference between the corresponding alternating opening and closing operations of the inflow and outflow lines to the corresponding piston assemblies, 21. Track ballast tamping device according to claim 15, characterized It is indicated that one of the passages has an elongated Cross-section on v / eist oriented relative to the axis of rotation of the valve stem part, determining the rate of opening or closing of the rotary valve assembly. 22. Track ballast tamping device according to claim 21, characterized gekennzeic hn et that one of the passages has an elongated cross section that extends in one direction extends approximately parallel to the direction of rotation of the valve spindle part. 23. Track ballast tamping device according to claim 21, characterized in that one of the passages has an elongate Has cross section which extends in a direction approximately perpendicular to the direction of rotation of the valve spindle part. 709820 / Q834