Stabilizing assembly for stabilizing a track

Abstract

The invention relates to a stabilizing assembly (11) for stabilizing a track (2), having a vibration generator (12) and having assembly rollers (15, 16) for transmitting vibrations (14) generated by means of the vibration generator (12) to a track grid (4), which consists of sleepers (5) and rails (6) fastened thereon, of the track (2) that is to be stabilized. In said stabilizing assembly, assembly rollers (15, 16) assigned to a left-hand rail (6) of the track (2) are arranged on a first side frame (19), and assembly rollers (15, 16) assigned to a right-hand rail (6) of the track (2) are arranged on a second side frame (20), wherein the two side frames (19, 20) are connected by a self-supporting central part (18) that comprises the vibration generator (12). A lower center of gravity (21) of the stabilizing assembly (11) as a whole is thus achieved.

Description

Description Stabilization unit for stabilizing a track Technical area

[0001] The invention relates to a stabilization unit for stabilizing a track, comprising a vibration generator and with unit rollers for transmitting vibrations generated by the vibration generator to a track grid of the track to be stabilized, consisting of sleepers and rails fastened thereon. State of the art

[0002] A ballasted track is subjected to continuous wear and tear by rail traffic and environmental influences. For example, the position of a track grid within the ballast bed changes. The ballast bed itself becomes contaminated over time due to abrasion and the introduction of foreign matter. Maintenance measures such as tamping or cleaning can remedy these deficiencies. However, this temporarily loosens the ballast bed. Even after optimal compaction using a tamping unit, subsequent settlement can occur. A track stabilizing machine, also known as a dynamic track stabilizer, is used to anticipate such settlement.

[0003] The machine is movable on the track and includes a stabilizing unit that is clamped to the rails by means of unit rollers. A vibration generator arranged on the stabilizing unit generates vibrations that are transmitted to the track grid. The design and dimensions of the vibration generator determine an impact force that acts on the track at the vibration frequency. To generate a static load, the stabilizing unit is supported against a machine frame. The transmitted vibrations cause the grains in the grain structure of the ballast bed to become mobile, can be shifted, and are compressed into a denser Storage. This optimized ballast compaction results in an increase in the load-bearing capacity and lateral displacement resistance of the track.

[0004] AT 16604 U1 discloses an exemplary stabilization unit with variable impact force. The vibration generator comprises several rotating unbalanced masses arranged on parallel shafts. The unbalanced masses are driven with a variably adjustable phase shift relative to each other. Depending on the arrangement of the unbalanced masses, a changed phase shift changes both the direction and the strength of the impact force. Description of the invention

[0005] The invention is based on the object of improving a stabilization unit of the type mentioned above so that the impact force acts on the track in an optimized manner. Furthermore, the arrangement of the vibration generator on the stabilization unit is to be simplified.

[0006] According to the invention, these objects are achieved by the features of independent claim 1. Dependent claims specify advantageous embodiments of the invention.

[0007] In this case, the unit rollers assigned to a left rail of the track (as seen in the direction of travel) are arranged on a first side frame, the unit rollers assigned to a right rail of the track are arranged on a second side frame, and the two side frames are connected by a self-supporting center section that contains the vibration generator. This innovative design has several advantages. The self-supporting center section with the vibration generator is located between the two side frames and is not placed on a supporting frame as previously. This results in a low center of gravity for the entire stabilization unit. The effective plane of the impact force generated by the vibration generator is also located a short distance from the top edges of the rails of the track to be stabilized. Both the low center of gravity and the low-lying effective plane of the impact force prevent disruptive tipping moments during a stabilization process. With conventional stabilization units, such tipping moments, if severe, can lead to the sleepers becoming saddled on a ballast layer in the center of the track.

[0008] A further advantage of the invention lies in its modular design. The self-supporting center section, in particular, can be designed in various variants to meet different requirements. For example, by varying the width of the center section, the stabilization unit can be adapted to different track widths. The side frames remain identical in construction. Even different vibration generators only affect the center section and do not require any changes to the side frames. This makes it easy to implement variants with different drives and impact force ranges.

[0009] In an advantageous further development, the center section is designed as the housing of the vibration generator. The vibration generator itself thus forms the supporting center section that connects the two side frames.

[0010] In a cost-effective version, the vibration generator includes a hydraulic or pneumatic cylinder. This allows a flywheel to be set in oscillating motion to generate vibrations in a desired plane.

[0011] Another preferred variant of the vibration generator includes rotatable imbalance masses. These rotatable imbalance masses can be used to generate impact forces in different planes and with adjustable intensity.

[0012] The unbalanced masses are ideally coupled to a rotary drive, particularly an electric one, located on the center section. This eliminates the need for transmission elements such as cardan shafts to transmit rotational movement to the unbalanced masses. Furthermore, control is simplified if the rotary drive is designed as an electric motor, particularly a torque motor. Compared to hydraulic or pneumatic drives, this results in lower noise emissions. Furthermore, no Additional units such as pumps or coolers are required. Connection to an existing electrical power supply system is usually achieved simply via an electrical cable.

[0013] Imbalance masses arranged on several parallel rotating shafts are advantageous, with the rotating shafts and / or imbalance masses being coupled to one another. The type of coupling determines how the centrifugal forces generated by the imbalance masses produce the resulting impact forces. For example, the centrifugal forces in one plane of action amplify each other, whereas the centrifugal forces in another plane of action cancel each other out.

[0014] Advantageously, at least two rotating shafts and / or unbalanced masses are coupled to gear elements. This allows a common rotary drive to be used to drive the rotating shafts or unbalanced masses. Furthermore, the gear elements can be used to determine the phase shift of the unbalanced masses relative to each other during rotation, resulting in the desired impact forces.

[0015] In a further improvement, at least one unbalanced mass is rotatably mounted on each rotating shaft. This unbalanced mass can be driven with a variable angular position, rotational speed, and rotational direction relative to an unbalanced mass fixed on the rotating shaft. This allows the direction and magnitude of a resulting centrifugal force to be adjusted. Depending on the direction of rotation, two different resulting centrifugal forces can be generated if two unbalanced masses arranged on a rotating shaft assume different angular positions relative to each other. Consequently, the stabilization unit can be operated with different impact forces at the same vibration frequency.

[0016] In a particularly advantageous variant of the alternative design, the unbalance masses are arranged on at least two vertically aligned rotating shafts. This ensures a particularly low center of gravity of the stabilization unit and a particularly low-lying effective plane of the Impact force can be achieved. Furthermore, there are no vertical vibrations, which may have to be compensated for with other design variants.

[0017] Preferably, four rotating shafts are arranged symmetrically with respect to a vertical plane of symmetry in the longitudinal direction and a vertical plane of symmetry in the transverse direction. This allows the central section with the vibration generator to be constructed symmetrically along two axes, thereby avoiding disruptive inertial forces during operation due to uneven mass distribution.

[0018] This advantage is enhanced with a symmetrical drive arrangement, in which two rotary drives, each with a vertical axis in the vertical symmetry plane in the longitudinal direction, are arranged symmetrically to the vertical symmetry plane in the transverse direction. Advantageously, two groups of rotary shafts and / or unbalanced masses are each driven by their own rotary drive. The rotary drives are controlled by a common control device to couple the two groups. Various control algorithms are configured in the control device, which produce different drive states. For example, different combinations of the direction of rotation and / or angular velocity of the respective rotary shaft or unbalanced mass lead to a changed impact force and / or vibration frequency of the stabilization unit.

[0019] In an advantageous development, each rotating shaft and / or unbalanced mass is assigned a sensor for detecting a current rotation angle. The respective sensor is connected to the control device, and the control device is configured to control the respective rotary drive depending on the rotation angle. In this way, the phase positions and angular velocities of the rotating shafts or unbalanced masses can be precisely controlled. This allows for continuous adjustment of the impact force and vibration frequency during operation.

[0020] In a preferred embodiment, the central part comprises an oil pan with a predetermined filling level, whereby the unbalance masses are partially reach below the fill level. This allows for a particularly low-lying arrangement of the unbalanced masses and, at the same time, provides splash lubrication for lubricating and cooling the rotating components of the vibration generator.

[0021] The respective unbalance mass advantageously includes a scoop-shaped extension in the area below the fill level, which allows oil to be transported from the oil pan into lateral collecting trays during operation. This design of the unbalance masses ensures particularly efficient circulating lubrication. During operation, oil flows back from the collecting trays into the oil pan, ensuring continuous lubrication and cooling. The oil pan itself contains only a small amount of oil, allowing the unbalance masses to rotate without any braking effect.

[0022] A further improvement to the overall design concerns the side frames. Each side frame houses a front flanged roller and a rear flanged roller, with a clamp mechanism located between the two flanged rollers for pressing a pressure roller against the respective rail. This compact design ensures optimal transmission of the generated vibrations to the track grid.

[0023] An advantageous further development is characterized by the fact that the flanged rollers are mounted in at least one side frame so that they can be adjusted along a rotational axis and pressed against the associated rail by means of actuators supported on the same side frame. These device elements are arranged exclusively on the same side frame and do not require coupling via the center section. Thus, no prior art spreader axis is required to press the stabilizing unit against the inside of the rails. Short description of the drawings

[0024] The invention is explained below by way of example with reference to the accompanying figures. They show schematically: Fig. 1 Rail vehicle with stabilization unit Fig. 2 Track cross-section with stabilization unit Fig. 3 Front view of a stabilization unit with vertically aligned rotation shafts Fig. 4 Top view of the stabilization unit according to Fig. 3 Fig. 5 Side view of the stabilization unit according to Fig. 3 Fig. 6 Side frame with flanged roller in retracted state Fig. 7 Side frame with flanged roller in extended state Fig. 8 Middle section with four vertically aligned rotation shafts and two rotation drives Fig. 9 Middle part according to Fig. 8 with opened housing Fig. 10 Middle part according to Fig. 8 in a plan view Fig. 11 Middle part according to Fig. 8 with coupling of the rotating shafts Fig. 12 Rotating shaft with unbalance mass Description of the embodiments

[0025] A rail vehicle 1 shown in Fig. 1 is a so-called dynamic track stabilizer for stabilizing a ballasted track 2 following a tamping process. The track 2 comprises a ballast bed 3 in which a track grid 4, consisting of sleepers 5 and rails 6 fastened thereto, is mounted. During continuous forward travel of the rail vehicle 1 in a working direction 7, the track grid 4 is set into vibration and pressed into the ballast bed 3. This targeted settlement of the track grid 4 is recorded by means of a chord measuring system 8 or by means of optical measuring devices. The exemplary rail vehicle 1 comprises a machine frame 9, which is supported on rail bogies 10 and can be moved along the track 2 to be stabilized. Two stabilization units 11 are movably connected to the machine frame 9. In other machines, only a single stabilization unit 11 is arranged.

[0026] Fig. 2 shows a cross-section of track 2 with the stabilization unit 11 during a stabilization process. The stabilization unit 11 comprises a vibration generator 12 as its main component. Load cylinders 13 support the stabilization unit 11 against the machine frame 9. The vibration generator 12 preferably generates Horizontal vibrations 14 in the transverse direction of the track. Aggregate rollers 15, 16 transmit the vibrations 14 to the track grid 13, with flanged rollers 15 guided along the inner edges of the rails and pressure rollers 16 pressed against the rails 6 from the outside. A continuously adjustable load 17 is applied by means of the ballast cylinders 13. The vertical load 17 ensures the transmission of the vibrations 14 into the ballast bed and is important for the compaction effect and track subsidence.

[0027] According to the invention, the stabilization unit 11 comprises a self-supporting central section 18 with the vibration generator 12. Viewed in the longitudinal direction of the track, a first side frame 19 is connected to the central section 18 on the left side and a second side frame 20 on the right side (Fig. 2). The connection of the central section 18 to the respective side frames 19, 20 is achieved, for example, by means of screw connections on a circumferential flange. The respective side frames 19, 20 serve as a support for the unit rollers 15, 16 for the respectively assigned rail 6. The flanged rollers 15 and the pressure roller 16 for the left rail 6 of the track 2 are arranged on the first side frame 19, and the flanged rollers 15 and the pressure roller 16 for the right rail 6 are arranged on the second side frame 20. The bearings of the respective aggregate rollers 15, 16 are mounted exclusively on the associated side frames 19, 20.There is no common continuous axle for the left and right flanged rollers 15. The absence of a continuous axle creates space for the low arrangement of the center section. The result is a low center of gravity 21 of the entire stabilization unit 11 and a low operating plane 22 of the vibration generator 12. Preferably, the center of gravity 21 is located in the operating plane 22.

[0028] In a preferred embodiment, the vibration generator 12 comprises unbalanced masses 23 arranged on rotating shafts 24. Such a vibration generator 12 with reduced overall height is explained with reference to Figures 3-7. Here, four vertically aligned rotating shafts 24 are arranged symmetrically with respect to a longitudinal vertical plane of symmetry 25 and a transverse vertical plane of symmetry 26.

[0029] Viewed in working direction 7, the two front rotary shafts 24 form a first group, with the left rotary shaft 24 being directly connected to a rotary drive 27 located above it. The right rotary shaft 24 is coupled to the left rotary shaft 24 via gears. The two rear rotary shafts 24, which are also coupled via gears, form a second group. The right rotary shaft 24 is connected to its own rotary drive 27.

[0030] The largely symmetrical structure of the central section 18 thus achieved results in a uniform oscillation of the entire stabilization unit 11 . The individual unbalanced masses 23 each generate a dynamic excitation force F. In sum, these excitation forces F result in the resulting dynamic impact force Fs. With the mass m and the eccentricity e of the respective unbalance 23 as well as the vibration frequency f or the angular velocity ou in the center of rotation, the individual excitation force is calculated according to the following formula:

[0031] The resulting dynamic impact force Fs determines the applied compaction energy and significantly influences the subsidence of track 2. The rotation drives 27 of the two groups are connected to a common control device 28. Various drive modes are configured in this control device 28. This allows the two groups to be driven at different speeds and directions of rotation, resulting in different resulting dynamic impact forces Fs.

[0032] On both side frames 19, 20, a clamp mechanism 29 for adjusting the respective pressure roller 16 is arranged between the front and rear flange rollers 15. In the example shown, the respective clamp mechanism 29 comprises a double rocker and two hydraulic cylinders 30, which are arranged symmetrically to the transverse vertical axis of symmetry 26. Extending the piston rods causes the pressure rollers 18 to be pressed against the outer sides of the rails 6.

[0033] To ensure that the stabilizing unit 11 can be clamped onto the track grid 4 without play, the flanged rollers 15 must also be pressed against the rails 6 from the inside. Advantageously, no conventional spreader axle is used for this purpose, because elements of such a spreader axle would also have to be arranged or mounted on the center section 18. Instead, only one of the side frames 20 is provided with flanged rollers 15 that are adjustable in the axial direction 31.

[0034] For example, the two flanged rollers 15 of the second side frame 20 are each rotatably and displaceably mounted on a shaft 32, as shown in Figures 6 and 7. One end of each shaft 32 is mounted directly on the side frame 20, and the other end is supported on a bracket 33 of the side frame 20. The load is transferred to the associated rail 6 via this robust mounting.

[0035] For adjustment in the axial direction 31, a pivot lever 34 is provided, which is pivotally connected on one side to the side frame 20 and on the other side to an actuator 35 (e.g., a pneumatic or hydraulic cylinder). The actuator 35 is tiltably mounted on the same side frame 20. Between the two joints 36, the pivot lever 34 has a positive coupling with a bushing 37 guided on the shaft 32. When the actuator 35 is extended, the pivot lever 34 pushes the bushing 37 and the flanged roller 15 mounted thereon outwards. In this way, the flanged rollers 15 are pressed against the inner sides of the rails 6 without play.

[0036] Figures 8 to 12 show a further embodiment of the central part 18. A housing 38 comprises opposing connection surfaces 39 for connecting to the side frames 19, 20. As before, four vertically aligned rotary shafts 24 are mounted in a base 40 and a cover 41 of the housing 38. An oil pan 42 is also arranged in the housing. When the rotary shafts 24 are stationary, the oil pan 42 is filled with oil up to a certain level. The unbalanced masses 23 are partially arranged below this level, so that they are immersed in the oil bath.

[0037] During operation, the unbalanced masses 23 transport oil from the oil pan 42 upwards and outwards into adjacent collecting pans 43. To achieve this conveying effect, a scoop-shaped extension 44 with inclined surfaces is arranged in the lower region of the respective unbalanced mass 23. A corresponding scoop-shaped extension 44 is shown in Fig. 12. Oil flows back into the oil pan 42 via passages in the bottom 40 of the housing 38, thus creating a circulating lubrication system during operation.

[0038] To increase symmetry, two rotary drives 27 are arranged, whose vertical axes 45 lie in the longitudinal plane of symmetry 25 and are arranged symmetrically to the transverse plane of symmetry 26. A drive shaft 46 of the respective rotary drive 27 is coupled to the two nearest rotary shafts 24 via gears. Furthermore, all rotary shafts 24 are coupled to one another via gears, so that a clear position or phase relationship of the unbalanced masses 23 relative to one another is achieved via these gear elements 47. This eliminates the need for synchronous control of the two rotary drives 27.

Claims

Patent claims 1 . Stabilization unit (11) for stabilizing a track (2), with a vibration generator (12) and with unit rollers (15, 16) for transmitting vibrations (14) generated by means of the vibration generator (12) to a track grid (4) of the track to be stabilized (2), consisting of sleepers (5) and rails (6) fastened thereon, characterized in that unit rollers (15, 16) assigned to a left rail (6) of the track (2) are arranged on a first side frame (19), that unit rollers (15, 16) assigned to a right rail (6) of the track (2) are arranged on a second side frame (20), and that the two side frames (19, 20) are connected by a self-supporting central part (18) which comprises the vibration generator (12).

2. Stabilization unit (11) according to claim 1, characterized in that the central part (18) is designed as a housing (38) of the vibration generator (12).

3. Stabilization unit (11) according to claim 1 or 2, characterized in that the vibration generator (12) comprises a hydraulic or pneumatic cylinder.

4. Stabilization unit (11) according to claim 1 or 2, characterized in that the vibration generator (12) comprises rotatable unbalance masses (23).

5. Stabilization unit (11) according to claim 4, characterized in that the unbalance masses (23) are coupled to a rotary drive (27), in particular an electric one, arranged on the central part (18).

6. Stabilization unit (11) according to claim 5, characterized in that the unbalance masses (23) are mounted on several parallel rotating shafts (24) are arranged and that the rotation shafts (24) and / or unbalance masses (23) are coupled to one another.

7. Stabilization unit (11) according to claim 6, characterized in that at least two rotation shafts (24) and / or unbalance masses (23) are coupled to gear elements (47).

8. Stabilization unit (11) according to claim 6 or 7, characterized in that at least one unbalance mass (23) is rotatably mounted on each rotary shaft (24).

9. Stabilization unit (11) according to one of claims 6 to 8, characterized in that the unbalance masses (23) are arranged on at least two vertically aligned rotary shafts (24).

10. Stabilization unit (11) according to claim 9, characterized in that four rotation shafts (24) are arranged symmetrically with respect to a longitudinal vertical plane of symmetry (25) and a transverse vertical plane of symmetry (26).

11. Stabilization unit (11) according to claim 10, characterized in that two rotary drives (27) with a respective vertical axis (45) are arranged in the longitudinal vertical plane of symmetry (25) symmetrically to the transverse vertical plane of symmetry (26).

12. Stabilization unit (11) according to one of claims 4 to 11, characterized in that the central part (18) comprises an oil pan (42) with a predetermined filling level and that the unbalance masses (23) partially extend below the filling level.

13. Stabilization unit (11) according to claim 12, characterized in that the respective unbalance mass (19) in the area below the filling level comprises a scoop-shaped extension (44) by means of which oil can be conveyed from the oil pan (42) into lateral collecting pans (43) during operation.

14. Stabilization unit (11) according to one of claims 1 to 13, characterized in that a front flanged roller (15) and a rear flanged roller (15) are mounted in each side frame (19, 20) and that a clamp mechanism (29) for pressing a pressure roller (16) onto the respective rail (6) is arranged between the two flanged rollers (15).

15. Stabilization unit (11) according to claim 14, characterized in that in at least one side frame (20) the flanged rollers (15) are mounted so as to be adjustable in the axial direction (31) and can be pressed onto the associated rail (6) by means of actuators (35) supported on the side frame (20).

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