Stabilization unit for stabilizing the orbit

Abstract

The present invention relates to a stabilization unit (11) for stabilizing a track (2), comprising a vibration generator (12) and unit rollers (15, 16) for transmitting vibrations (14) generated by the vibration generator (12) to a track grid (4) consisting of sleepers (5) of the track (2) to be stabilized and rails (6) fixed on the sleepers (5). In this case, the unit rollers (15, 16) associated with the left rail (6) of the track (2) are arranged on a first side frame (19), and the unit rollers (15, 16) associated with the right rail (6) of the track (2) are arranged on a second side frame (20), the two side frames (19, 20) being connected by a self-supporting central section (18) including the vibration generator (12). This results in a low center of gravity (21) for the entire stabilization unit (11).

Description

[Technical Field]

[0001] The invention relates to a stabilizing unit for stabilizing a track, comprising a vibration generator and unit rollers for transmitting the vibrations generated by the vibration generator to a track grid consisting of sleepers of the track to be stabilized and rails fixed on the sleepers. [Background technology]

[0002] Ballast track is continuously subjected to loads due to rail traffic and environmental influences. For example, the position of the track grid in the ballast bed changes. The ballast bed itself becomes contaminated over time by wear and by introduced foreign components. Maintenance measures such as tamping or cleaning processes overcome these drawbacks, although they involve temporary demolition of the ballast bed. Even after optimal compaction by a tamping unit, subsequent settlement can occur. To prevent such settlement, track stabilization machines, also known as dynamic track stabilizers, are used.

[0003] The machine can travel on the track and has a stabilizing unit that is clamped to the track rails by unit rollers. A vibration generator located in the stabilizing unit generates vibrations that are transmitted to the track grid. The vibration generator's structural type and dimensional design determine the impact force acting on the track at a given vibration frequency. To generate a static load, the stabilizing unit is supported on the machine frame. The transmitted vibrations cause particles in the granular structure of the ballast bed to become mobile, i.e., to move, resulting in a denser deposit. This optimized ballast compaction improves the track's bearing capacity and lateral resistance to shear.

[0004] Austrian Utility Model No. 16604 discloses an exemplary stabilization unit with variable impact force. In this case, a vibration generator includes multiple rotating unbalanced masses arranged on parallel-oriented axes. These unbalanced masses are driven with a variably adjustable phase shift relative to one another. Depending on the arrangement of the unbalanced masses, the altered phase shift alters both the direction and the strength of the impact force. Summary of the Invention [Problem to be solved by the invention]

[0005] The object of the present invention is to improve a stabilization unit of the type mentioned at the beginning so that impact forces act optimally on the track. Furthermore, it is desirable to simplify the arrangement of the vibration generators in the stabilization unit. [Means for solving the problem]

[0006] According to the present invention, the above problem is solved by the features of independent claim 1. The dependent claims each show advantageous embodiments of the invention.

[0007] In this case, the unit rollers associated with the left rail of the track, as seen in the direction of travel, are arranged on a first side frame, and the unit rollers associated with the right rail of the track are arranged on a second side frame, with the two side frames connected by a self-supporting central section including the vibration generator. This novel design offers several advantages. The self-supporting central section with the vibration generator is located between the two side frames and is not mounted on a support frame as in the past. This achieves a low center of gravity for the entire stabilization unit. Furthermore, the plane of action of the impact force generated by the vibration generator is also close to the upper edge of the rail of the track to be stabilized. Both the low center of gravity and the low plane of action of the impact force avoid damaging tilting moments during the stabilization process. In the case of conventional stabilization units, such tilting moments, when applied strongly, would cause the sleepers to saddle up on the ballast bed in the center of the track.

[0008] Another advantage of the present invention is its modular design. The self-supporting central section, in particular, can be configured in various variants to meet various requirements. For example, by varying the width of the central section, the stabilization unit can be adapted to different track gauges. In this case, the side frames remain the same. Different vibration generators are also associated only with the central section and do not require modifications to the side frames. In this way, variants with different drives and impact force areas can be easily realized.

[0009] In an advantageous development, the central part is formed as a housing for the vibration generator, so that the vibration generator itself forms the supporting central part which interconnects the two lateral frames.

[0010] In one advantageous variant, the vibration generator comprises a hydraulic or pneumatic cylinder, which can put a seismic mass into oscillatory motion in order to generate vibrations in the desired plane of action.

[0011] Another preferred variant of the vibration generator includes a rotatable unbalanced mass, which allows the creation of impact forces with adaptable strength in different planes of action.

[0012] In this case, the unbalanced mass is advantageously coupled to a rotary drive, particularly an electric one, arranged in the central part. In this way, no transmission element, such as a cardan shaft, is needed to transmit the rotary motion to the unbalanced mass. Furthermore, if the rotary drive is configured as an electric motor, particularly a torque motor, the drive control is simplified. Lower noise emissions are achieved compared to hydraulic or pneumatic drives. Furthermore, no additional units, such as pumps or coolers, are needed. In most cases, connection to an existing electrical energy supply system is made in a simple manner via an electric cable.

[0013] Preferably, the unbalanced masses are arranged on multiple parallel rotating shafts, and the rotating shafts and / or the unbalanced masses are connected to one another. The type of connection determines how the centrifugal forces caused by the unbalanced masses form the resulting impact force. For example, the centrifugal forces in one plane of action are amplified, while the centrifugal forces in the other plane of action cancel each other out.

[0014] In this case, it is advantageous to couple at least two rotating shafts and / or unbalanced masses to a transmission element, so that one common rotary drive can be used to drive the rotating shafts or unbalanced masses, and the transmission element can be used to set a phase shift between the unbalanced masses during rotation, which phase shift results in the desired resultant impact force.

[0015] According to another refinement, at least one unbalanced mass is rotatably supported on each rotating shaft. The unbalanced mass can be driven at variable angular positions, rotational speeds, and rotational directions relative to the unbalanced mass fixed on the rotating shaft. This allows the direction and magnitude of the resulting centrifugal force to be adjusted. Optionally, if two unbalanced masses arranged on one rotating shaft take different angular positions relative to each other depending on the direction of rotation, two different magnitudes of resultant centrifugal forces are generated depending on the direction of rotation. As a result, the stabilization unit can be operated with different impact forces at the same vibration frequency.

[0016] According to a particularly advantageous feature of this alternative design, the unbalanced masses are arranged on at least two vertically oriented axes of rotation, which allows for a particularly low center of gravity and a particularly low impact force plane of the stabilization unit, and also prevents vertical vibrations that may have to be compensated for by further design variants.

[0017] In this case, the four rotation axes are preferably arranged symmetrically with respect to a vertical plane of symmetry in the longitudinal direction and with respect to a vertical plane of symmetry in the transverse direction, so that the central part with the vibration generators can be constructed symmetrically with respect to two axes, thereby avoiding inertial forces that would cause disturbances during operation due to uneven mass distribution.

[0018] This advantage is amplified by the symmetrical drives, where two rotary drives are arranged symmetrically with respect to the vertical symmetry plane in the longitudinal direction and the vertical symmetry plane in the lateral direction, along their respective vertical axes. Preferably, each of the two groups of rotary shafts and / or unbalanced masses is driven by its own rotary drive. In this case, the rotary drives are controlled so that the two groups are connected to a common control device. Various control algorithms are configured in the control device to generate different drive states. For example, various combinations of the rotation direction and / or angular velocity of each rotary shaft or each unbalanced mass result in changes in the impact force and / or vibration frequency of the stabilization unit.

[0019] In an advantageous development, a sensor for detecting the current rotation angle is associated with each rotating shaft and / or each unbalanced mass, and each sensor is connected to a control device that controls the rotation angle of each rotary drive. In this way, the phase position and angular velocity of the rotating shaft or unbalanced mass can be precisely controlled. This allows for continuous adaptation of impact forces and vibration frequencies during operation.

[0020] In a preferred feature, the central part is provided with an oil reservoir with a set filling level, below which the unbalanced mass partially reaches, which on the one hand ensures a particularly low positioning of the unbalanced mass and on the other hand achieves immersion lubrication for lubricating and cooling the rotatable components of the vibration generator.

[0021] In this case, each unbalanced mass preferably includes a shovel-shaped protrusion in the area below the filling level, which can pump oil from the oil reservoir into a lateral collecting tank during operation. This shape of the unbalanced mass results in particularly efficient circulating lubrication. During operation, oil is returned from the collecting tank to the oil layer, thereby ensuring continuous lubrication and cooling. In this case, only a small amount of oil is present inside the oil reservoir itself, allowing the unbalanced mass to rotate without braking.

[0022] Another improvement to the overall structure concerns the side frames, which each support a front flanged roller and a rear flanged roller, with a tongue mechanism located between the two flanged rollers that presses the pressure rollers against the respective rails. This compact design ensures optimal transmission of generated vibrations to the track grid.

[0023] An advantageous development is characterized in that the flanged rollers are supported on at least one side frame so as to be movable in the direction of the rotation axis and can be pressed against the associated rail by an adjusting drive supported on the same side frame. These device elements are arranged exclusively on the same side frame and do not require a connection via a central part, i.e., the spreading axis known from the prior art for pressing the stabilizing unit against the inner surface of the rail is not required.

[0024] The invention will now be described by way of example only and with reference to the accompanying drawings, in which: FIG. [Brief explanation of the drawings]

[0025] [Figure 1] FIG. 1 shows a railway vehicle equipped with a stabilization unit. [Figure 2] FIG. 1 is a cross-sectional view showing the track with the stabilization unit. [Figure 3] FIG. 10 is a front view of a stabilization unit with a vertically oriented rotation axis. [Figure 4]FIG. 4 is a plan view showing the stabilization unit of FIG. 3. [Figure 5] FIG. 4 is a side view of the stabilization unit of FIG. 3. [Figure 6] FIG. 10 shows a side frame with flanged rollers in a running-in state. [Figure 7] FIG. 10 shows a side frame with flanged rollers in the running state. [Figure 8] FIG. 1 shows a central section with four vertically oriented rotation axes and two rotation drives. [Figure 9] FIG. 9 shows the central portion of FIG. 8 with the housing open. [Figure 10] FIG. 9 is a plan view showing the central portion of FIG. 8. [Figure 11] 9 shows the central part of FIG. 8 with the coupling of the rotary shaft. [Figure 12] FIG. 1 is a diagram showing a rotating shaft equipped with an unbalanced mass. DETAILED DESCRIPTION OF THE INVENTION

[0026] The railway vehicle 1 shown in FIG. 1 is a so-called dynamic track stabilization system for stabilizing a ballast track 2 following a tamping process. The track 2 includes a ballast bed 3, in which a track grid 4 consisting of sleepers 5 and rails 6 fixed to the sleepers 5 is supported. During continuous forward movement of the railway vehicle 1 in a working direction 7, the track grid 4 is vibrated and pressed into the track bed 3. The targeted subsidence of the track grid 4 is detected by a visual or optical measuring system 8. The exemplary railway vehicle 1 has a machine frame 9 that is supported on a rail running mechanism 10 and can travel over the track 2 to be stabilized. Two stabilization units 11 are movably connected to the machine frame 9. On other machines, only one stabilization unit 11 is arranged.

[0027] Figure 2 shows a cross section of the track 2 with a stabilizing unit 11 during the stabilization process. The stabilizing unit 11 has a vibration generator 12 as its main component. Load cylinders 13 support the stabilizing unit 11 relative to the machine frame 9. Preferably, the vibration generator 12 generates horizontal vibrations 14 in the transverse track direction. Unit rollers 15, 16 transmit the vibrations 14 to the track grid 4, with the flanged rollers 15 guided along the inner rail edge and the pressure rollers 16 pressing against the rail 6 from the outside. A continuously adjustable load 17 is applied by the load cylinders 13. The vertical load 17 serves to transmit the vibrations 14 to the track bed and is important for compaction and track lowering.

[0028] According to the present invention, the stabilization unit 11 includes a self-supporting central section 18 equipped with a vibration generator 12. A first side frame 19 is connected to the left side of the central section 18, and a second side frame 20 is connected to the right side of the central section 18 (see FIG. 2). The central section 18 is connected to each of the side frames 19, 20, for example, by screw fasteners on annular flanges. Each of the side frames 19, 20 serves as a support for the unit rollers 15, 16 for the corresponding rail 6. The first side frame 19 accommodates the flanged rollers 15 and pressure rollers 16 for the left rail 6 of the track 2, while the second side frame 20 accommodates the flanged rollers 15 and pressure rollers 16 for the right rail 6. In this case, each of the unit rollers 15, 16 is supported exclusively by the corresponding side frame 19, 20. There is no common continuous axis between the left flanged roller 15 and the right flanged roller 15. The absence of a continuous axis provides space for a lower central portion, resulting in a low center of gravity 21 for the entire stabilization unit 11 and a low plane of action 22 for the vibration generator 12. Preferably, the center of gravity 21 is located within the plane of action 22.

[0029] In a preferred aspect, the vibration generator 12 includes unbalanced masses 23 arranged on rotation axes 24. Such a vibration generator 12 with reduced construction height is described with reference to Figures 3 to 7. In this case, four vertically oriented rotation axes 24 are arranged symmetrically with respect to a vertical plane of symmetry 25 extending in the longitudinal direction and with respect to a vertical plane of symmetry 26 extending in the transverse direction.

[0030] The two front rotary shafts 24, as seen in the working direction 7, form a first group; the left-hand rotary shaft 24 is directly connected to a rotary drive 27 arranged thereon. The right-hand rotary shaft 24 is connected to the left-hand rotary shaft 24 via a gear. The second group forms the two rear rotary shafts 24, which are also connected via a gear. The right-hand rotary shaft 24 is connected to its own rotary drive 27.

[0031] The resulting nearly symmetrical structure of the central portion 18 induces uniform vibration of the entire stabilization unit 11. Each of the individual unbalanced masses 23 generates a dynamic excitation force F. Overall, the excitation forces F here result in a dynamic resultant impact force F S The mass m and eccentricity e of each unbalanced mass 23 and the vibration frequency f or angular velocity ω at the center of rotation are U Using the above formula, the individual excitation forces are expressed as follows:

number

[0032] Dynamic resultant impact force F S determines the introduced compaction energy and substantially influences the settlement of the track 2. The two groups of rotary drives 27 are connected to a common control device 28, which is provided with different drive modes. Thus, the two groups can be driven at different rotation speeds and directions, resulting in different dynamic resultant impact forces F S occurs.

[0033] A tong mechanism 29 for adjusting each pressure roller 16 is disposed between the front flanged roller 15 and the rear flanged roller 15 on the two side frames 19, 20. In the illustrated example, each tong mechanism 29 includes a double swing arm and two hydraulic cylinders 30, which are disposed symmetrically with respect to a vertical axis of symmetry 26 extending laterally. The pressure roller 16 is pressed against the outer surface of the rail 6 as the piston rod extends.

[0034] To ensure that the stabilizing unit 11 can be clamped without play on the track grid 4, the flanged rollers 15 must also be pressed against the rails 6 from the inside. For this purpose, conventional expansion axes are preferably not used, since such expansion axis elements would also have to be arranged or supported on the central section 18. Instead, only one of the side frames 20 is provided with a flanged roller 15 that is adjustable in the axial direction 31.

[0035] For example, as shown in Figures 6 and 7, the two flanged rollers 15 of the second side frame 20 are each supported rotatably and shiftably on one shaft 32. One end of each shaft 32 is supported directly on the side frame 20, and the other end is supported on a boom 33 of the side frame 20. Loads are transmitted to the associated rails 6 via such robust supports.

[0036] For adjustment in the axial direction 31, a swivel lever 34 is arranged, which is pivotally connected on the one hand to the side frame 20 and on the other hand to an adjustment drive 35 (e.g., a pneumatic or hydraulic cylinder). The adjustment drive 35 is tiltably supported on the same side frame 20. Between the two joints 36, the swivel lever 34 has a form-locking connection with a bushing 37 guided on the shaft 32. When the adjustment drive 35 moves out, the swivel lever 34 pushes the bushing 37 and the flanged roller 15 supported on this bushing 37 outward. In this way, the flanged roller 15 is pressed against the inner surface of the rail 6 without play.

[0037] 8 to 12 show another embodiment of the central section 18. The housing 38 includes opposing connection surfaces 39 for connection to the side frames 19, 20. The bottom 40 and cover 41 of the housing 38 support the four vertically oriented rotating shafts 24, as described above. Additionally, an oil reservoir 42 is located within the housing. When the rotating shafts 24 are stationary, the oil reservoir 42 is filled with oil up to a fill level. The unbalanced mass 23 is located partially below this fill level, so that the unbalanced mass is immersed in the oil bath.

[0038] During operation, the unbalanced masses 23 pump oil from the oil reservoir 42 upwards and into the adjacent outer collecting reservoir 43. To achieve this transport function, a shovel-shaped projection 44 with an obliquely extending surface is arranged in the lower region of each unbalanced mass 23. A corresponding shovel-shaped projection 44 is shown in FIG. 12. Through a hole in the bottom 40 of the housing 38, the oil flows back to the oil reservoir 42, thereby creating a circulating lubrication zone during operation.

[0039] To enhance symmetry, two rotary drives 27 are provided, with their vertical axes 45 lying on the longitudinally extending plane of symmetry 25 and symmetrically positioned with respect to the transversely extending plane of symmetry 26. The drive shaft 46 of each rotary drive 27 is coupled to two adjacent rotary shafts 24 via gears. Since all rotary shafts 24 are coupled to one another via gears, the unbalanced masses 23 are uniquely positioned or phase-shifted relative to one another via these transmission elements 47. This eliminates the need for synchronous control of the two rotary drives 27.

Claims

1. A stabilization unit (11) for stabilizing a track (2), comprising a vibration generator (12) and unit rollers (15, 16) for transmitting vibrations (14) generated by the vibration generator (12) to a track grid (4) consisting of sleepers (5) of the track (2) to be stabilized and rails (6) fixed on the sleepers (5), The stabilization unit (11) is characterized in that the unit rollers (15, 16) associated with the left rail (6) of the track (2) are arranged on a first side frame (19), and the unit rollers (15, 16) associated with the right rail (6) of the track (2) are arranged on a second side frame (20), and the two side frames (19, 20) are connected by a self-supporting central part (18) including the vibration generator (12).

2. 2. The stabilization unit (11) according to claim 1, wherein the central part (18) is formed as a housing (38) of the vibration generator (12).

3. The stabilization unit (11) according to claim 1 or 2, wherein the vibration generator (12) comprises a hydraulic or pneumatic cylinder.

4. The stabilization unit (11) according to claim 1 or 2, wherein the vibration generator (12) comprises a rotatable unbalanced mass (23).

5. 5. The stabilization unit (11) according to claim 4, wherein the unbalanced mass (23) is coupled to a rotary drive (27), in particular an electric one, arranged in the central part (18).

6. 6. The stabilization unit (11) according to claim 5, wherein the unbalanced masses (23) are arranged on a plurality of parallel-arranged rotation shafts (24), and the rotation shafts (24) and / or the unbalanced masses (23) are connected to each other.

7. 7. The stabilization unit (11) according to claim 6, wherein at least two rotational shafts (24) and / or unbalanced masses (23) are connected to a transmission element (47).

8. 8. The stabilizing unit (11) according to claim 6 or 7, wherein at least one unbalanced mass (23) is rotatably supported on each rotation axis (24).

9. 9. The stabilization unit (11) according to any one of claims 6 to 8, wherein the unbalanced mass (23) is arranged on at least two vertically oriented rotation axes (24).

10. 10. The stabilizing unit (11) according to claim 9, wherein the four rotation axes (24) are arranged symmetrically with respect to a vertical plane of symmetry (25) extending in the longitudinal direction and a vertical plane of symmetry (26) extending in the transverse direction.

11. 11. The stabilization unit (11) according to claim 10, wherein two rotary drives (27) having respective vertical axes (45) are arranged symmetrically in the longitudinally extending vertical plane of symmetry (25) relative to the transversely extending vertical plane of symmetry (26).

12. 12. The stabilization unit (11) according to claim 4, wherein the central portion (18) comprises an oil reservoir (42) having a set filling level, and the unbalanced mass (23) extends partially below the filling level.

13. 13. The stabilization unit (11) according to claim 12, wherein each of the unbalanced masses (23) comprises a shovel-shaped protrusion (44) in an area below the filling level, which protrusion (44) allows oil to be pumped from the oil tank (42) into a lateral collection tank (43) during operation.

14. 14. The stabilizing unit (11) according to claim 1, wherein a front flanged roller (15) and a rear flanged roller (15) are supported on each side frame (19, 20), and a tong mechanism (29) is arranged between the two flanged rollers (15) to press the pressure roller (16) against each rail (6).

15. 15. The stabilizing unit (11) according to claim 14, wherein the flanged roller (15) is supported on at least one side frame (20) so as to be adjustably axially (31) and can be pressed against the associated rail (6) by an adjusting drive (35) supported on the side frame (20).

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