Stabilizing device for stabilizing track
By designing self-loaded intermediate components in the stabilization equipment to reduce the center of gravity and impact force action surface, the problem that existing stabilization equipment is prone to generate inclination torque during the stabilization process is solved, and the stability effect and equipment adaptability are improved.
Patent Information
- Application Number
- CN202380079256.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2022-11-22
- Filing Date
- 2023-11-14
- Publication Date
- 2025-06-20
AI Technical Summary
When existing stabilizing equipment applies impact force to the track, the center of gravity is high and the impact force is large, resulting in an interfering inclination torque easily generated during the stabilization process, affecting the stability effect.
A self-loaded intermediate component is designed, in which the vibration generator is located between the two side frames, forming a lower center of gravity and a lower impact force surface. The intermediate component can adapt to different gauge requirements through different deformation schemes and generate vibrations by driving the unbalanced mass through hydraulic cylinders or pneumatic cylinders.
By reducing the center of gravity and impact force action surface of the stabilizing equipment, the disturbing inclination torque generated during the stabilization process is reduced, the stability and efficiency of the stabilizing equipment are improved, and the arrangement of the equipment is simplified.
Smart Images
Figure CN120187922A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a stabilizing device for stabilizing a track, the stabilizing device having a vibration generator and device rollers for transmitting vibrations generated by the vibration generator to a track assembly composed of sleepers and rails fixed to the sleepers and to be stabilized. Background Art
[0002] Ballast tracks are constantly affected by railway traffic and the environment. For example, the position of the track assembly on the ballast bed changes. The ballast bed itself also becomes dirty over time due to wear and the entry of foreign objects. These defects can be eliminated by maintenance measures such as tamping processes or cleaning processes. However, this will cause the ballast bed to loosen temporarily here. Even after optimal compaction by a tamping device, subsequent settlement will occur. Machines for stabilizing tracks, also called dynamic track stabilizers, can be used to prevent such settlement.
[0003] The machine can move along the track and includes a stabilizing device that is clamped to the rails of the track by device rollers. A vibration generator arranged on the stabilizing device generates vibrations that are transmitted to the track assembly. The structural design and dimensions of the vibration generator determine the impact force acting on the track at the vibration frequency. To generate a static load, the stabilizing device is supported on the machine frame. The transmitted vibrations cause the particles in the granular structure of the ballast bed to move, shift, and be stored more densely. This optimized ballast compaction technology can improve the load-bearing capacity and lateral displacement resistance of the track.
[0004] Document AT 16604 U1 discloses a stabilizing device, for example, with variable impact force. Here, the vibration generator includes a plurality of rotating unbalanced mass blocks arranged on parallelly oriented shafts. The unbalanced mass blocks are driven in a manner with a variable phase shift relative to each other. Depending on the arrangement of the unbalanced mass blocks, the varying phase shift changes the direction and intensity of the impact force. Summary of the Invention
[0005] The technical problem to be solved by the present invention is to improve a stabilizing device of the aforementioned type so that the impact force acts on the track in an optimal manner. In addition, the arrangement of the vibration generator on the stabilizing device should be simplified.
[0006] The technical problem is solved according to the present invention by the technical features of independent claim 1. The dependent claims provide advantageous designs of the present invention.
[0007] Here, when observing in the driving direction, the equipment rollers assigned to the left rail of the track are arranged on the first side frame, the equipment rollers assigned to the right rail of the track are arranged on the second side frame, and these two side frames are connected by a self-supporting intermediate member, which includes the vibration generator. This innovative design has multiple advantages. The self-supporting intermediate member with the vibration generator is located between the two side frames, rather than being placed on the load-bearing frame as before. Therefore, the center of gravity of the entire stabilizing device is relatively low. The distance between the acting surface of the impact force generated by the vibration generator and the upper edge of the rail of the track to be stabilized is also small. The lower center of gravity and the lower acting surface of the impact force prevent the generation of disturbing tilting moments during the stabilization process. In traditional stabilizing devices, when such tilting moments are very obvious, they will cause the sleeper to have a saddle-shaped support on the ballast layer located at the center of the track.
[0008] Another advantage of the present invention lies in its modular structure. The self-supporting intermediate member can in particular be designed in different deformation schemes to meet different requirements. For example, the stabilizing device can adapt to different track gauges by changing the width of the intermediate member. Here, the structural design of the side frames remains unchanged. Different vibration generators only relate to the intermediate member and do not cause changes to the side frames. In this way, deformation schemes with different drives and impact force ranges can be easily realized.
[0009] In an advantageous improvement, the intermediate member is configured as the housing of the vibration generator. Thus, the vibration generator itself constitutes the self-supporting intermediate member connecting the two side frames.
[0010] In an advantageous deformation, the vibration generator includes a hydraulic cylinder or a pneumatic cylinder. Thereby, the oscillating mass can be placed in an oscillating motion in order to generate vibrations on the required acting surface.
[0011] Another preferred deformation of the vibration generator includes rotatable unbalanced mass blocks. With the aid of these rotatable unbalanced mass blocks, impact forces can be generated on different acting surfaces and have a strength that can be matched.
[0012] Here, it is meaningful that the unbalanced mass blocks are coupled to a rotational drive, especially an electrical one, arranged on the intermediate member. In this way, for example, there is no need for transmission components, such as cardan shafts, for transmitting the rotational motion to the unbalanced mass blocks. In addition, if the rotational drive is designed as an electric motor, especially a torque motor, the control can be simplified. Compared with hydraulic or pneumatic drives, this design can reduce noise emissions. Furthermore, no additional devices, such as pumps or coolers, are required. Connection to most existing power supply systems can be achieved simply by means of cables.
[0013] Advantageously, unbalanced mass blocks are arranged on a plurality of parallel rotating shafts, wherein these rotating shafts and / or unbalanced mass blocks are coupled to each other. The type of coupling determines how the centrifugal forces generated by the unbalanced mass blocks generate a resultant impact force. For example, the centrifugal forces are enhanced on one acting surface, while the centrifugal forces on another acting surface cancel each other out.
[0014] Here, it is advantageous that at least two rotating shafts and / or unbalanced mass blocks are coupled to a transmission element. In this way, a common rotary drive can be used to drive the rotating shafts or unbalanced mass blocks. In addition, by means of the transmission element, the phase shift of the unbalanced mass blocks can be determined relative to each other during rotational operation, thereby generating the required resultant impact force.
[0015] In a further refinement, at least one unbalanced mass block is rotatably supported on each rotating shaft. Compared with an unbalanced mass block fixed to the rotating shaft, this unbalanced mass block can be driven at a variable angular position, rotational speed and rotational direction. Thereby, the direction and magnitude of the resultant centrifugal force can be adjusted. Optionally, when the angular positions of two unbalanced mass blocks arranged on the rotating shaft relative to each other are different according to the rotational direction, two different magnitudes of resultant centrifugal forces are generated according to the rotational direction. Therefore, the stabilizing device can operate with different impact forces at the same vibration frequency.
[0016] In a particularly advantageous embodiment of an alternative design, the unbalanced mass blocks are arranged on at least two vertically oriented rotating shafts. Thereby, a particularly low center of gravity of the stabilizing device and a particularly low acting surface of the impact force can be achieved. In addition, no vertical vibrations are generated, which in other structural variants must be compensated for if necessary.
[0017] Here, it is preferred that the four rotating shafts are arranged symmetrically with respect to a vertically extending longitudinal symmetry plane and a vertically extending transverse symmetry plane. In this way, an intermediate component with a vibration generator can be symmetrically mounted on two shafts, thereby avoiding disturbing inertial forces caused by uneven mass distribution during operation.
[0018] The symmetrical drive arrangement enhances this advantage, wherein two rotary drives are arranged symmetrically with respect to a vertically extending transverse symmetry plane with their respective vertical axes, and this vertical axis is located in the vertically extending longitudinal symmetry plane. Advantageously, two sets of rotating shafts and / or unbalanced mass blocks are respectively driven by their respective rotary drives. Here, the rotary drives coupling the two sets are controlled by a common control device. Different control algorithms are provided in the control device, and these control algorithms cause different drive states. For example, different combinations of the rotational directions and / or angular velocities of the respective rotating shafts or unbalanced masses result in changing impact forces and / or vibration frequencies of the stabilizing device.
[0019] In an advantageous refinement, each rotating shaft and / or unbalanced mass is equipped with a sensor for detecting the current rotational angle, wherein the sensors are connected to a control device, and wherein the control device is configured to control the respective rotational drives based on the rotational angle. In this way, the phase and angular velocity of the rotating shaft or the unbalanced mass can be precisely controlled. This enables the continuous adjustment of the impact force and the vibration frequency during operation.
[0020] In a preferred design, the intermediate member includes an oil sump having a preset filling height, and the unbalanced mass projects partially below the filling height. Thereby, on the one hand, a low-level arrangement of the unbalanced mass is achieved, and on the other hand, immersion lubrication is achieved to lubricate and cool the rotatable components of the vibration generator.
[0021] Advantageously, each unbalanced mass in the region below the filling height includes paddle-shaped protrusions through which oil can be conveyed from the oil sump into a lateral collecting trough during operation. This design of the unbalanced mass ensures particularly efficient circulating lubrication. During operation, the oil flows back from the collecting trough into the oil sump, thereby ensuring continuous lubrication and cooling. Only a small amount of oil is present in the oil sump itself, enabling the unbalanced mass to rotate without a braking effect.
[0022] A further refinement of the overall structure relates to the side frames. Here, a front flanged roller and a rear flanged roller are respectively supported in each side frame, and a clamping mechanism is arranged between the two flanged rollers for pressing the squeezing roller against the corresponding rail. This compact design ensures that the generated vibration is transmitted to the track assembly in an optimal manner.
[0023] An advantageous refinement provides that the flanged roller is adjustably supported in at least one side frame in the direction of the rotating shaft, and the flanged roller can be pressed against the assigned rail by means of a servo drive supported on the same side frame. These device elements are only arranged on the same side frame and do not need to be connected by an intermediate member. Therefore, there is no need to use a lateral support shaft known in the prior art to press the stabilizing device against the inner side of the rail. Description of the Drawings
[0024] The present invention will be explained below in an exemplary manner with reference to the drawings. In the drawings:
[0025] Figure 1 A schematic view of a rail vehicle with a stabilizing device is shown,
[0026] Figure 2 A schematic cross-sectional view of a track with a stabilizing device is shown,
[0027] Figure 3 A front view schematic of a stabilizing device with a vertically oriented rotating shaft is shown,
[0028] Figure 4 Shows a top view schematic diagram of a stabilizing device according to Figure 3 of the stabilizing device,
[0029] Figure 5 Shows a side view schematic diagram of a stabilizing device according to Figure 3 of the stabilizing device,
[0030] Figure 6 Shows a schematic diagram of a side frame with flanged rollers in the moved-in state,
[0031] Figure 7 Shows a schematic diagram of a side frame with flanged rollers in the moved-out state,
[0032] Figure 8 Shows a schematic diagram of an intermediate member having four vertically oriented rotating shafts and two rotary drives,
[0033] Figure 9 Shows a schematic diagram of an intermediate member according to Figure 8 with an open housing,
[0034] Figure 10 Shows a top view schematic diagram of an intermediate member according to Figure 8 of the intermediate member,
[0035] Figure 11 Shows a schematic diagram of an intermediate member according to Figure 8 with connected rotating shafts,
[0036] Figure 12 Shows a schematic diagram of a rotating shaft with an unbalanced mass block. Detailed Description
[0037] Figure 1 The rail vehicle 1 shown is a so-called dynamic track stabilizer for stabilizing a ballast track 2 after a tamping process. The track 2 includes a ballast bed 3, on which a track assembly 4 composed of sleepers 5 and rails 6 fixed to the sleepers is supported. When the rail vehicle 1 continuously advances in the working direction 7, the track assembly 4 is in a vibrating state and is pressed into the ballast bed 3. This directional settlement of the track assembly 4 can be detected by a chord measurement system 8 or an optical measuring device. An exemplary rail vehicle 1 includes a frame 9, which is supported on a rail running gear 10 and is movable on the track 2 to be stabilized. Two stabilizing devices 11 are movably connected to the frame 9. In other machines, only a single stabilizing device 11 is arranged.
[0038] Figure 2Shows a cross-section of the track 2 with the stabilizer device 11 during the stabilization process. The stabilizer device 11 includes a vibration generator 12 as the main component. The load cylinder 13 supports the stabilizer device 11 on the machine frame 9. The vibration generator 12 preferably generates a horizontal vibration 14 transversely to the track. The device rollers 15, 16 transmit the vibration 14 to the track assembly 13, wherein the flanged roller 15 guides along the inner edge of the rail, and the squeezing roller 16 presses against the rail 6 from the outside. A steplessly variable load 17 is applied through the load cylinder 13. The vertical load 17 ensures the transmission of the vibration 14 into the ballast bed and is very important for the compaction effect and the reduction of the track height.
[0039] According to the invention, the stabilizer device 11 includes a self-supporting intermediate member 18 having a vibration generator 12. Viewed longitudinally along the track, the first side frame 19 is connected to the intermediate member 18 on the left side, and the second side frame 20 is connected to the intermediate member 18 on the right side ( Figure 2 ). The connection of the intermediate member 18 to the respective side frames 19, 20 is realized, for example, by bolt connection on a surrounding flange. The respective side frames 19, 20 serve as supports for the device rollers 15, 16 of the respective assigned rails 2. The flanged roller 15 and the squeezing roller 16 for the left rail 6 are arranged on the first side frame 19, and the flanged roller 15 and the squeezing roller 16 for the right rail 6 are arranged on the second side frame 20. Each device roller 15, 16 is only mounted on the assigned side frame 19, 20 here. The left and right flanged rollers 15 do not have a common through shaft. The absence of a through shaft creates space for a low arrangement of the intermediate member. Therefore, the center of gravity 21 of the entire stabilizer device 11 is low, and the acting surface 22 of the vibration generator 12 is also low. Preferably, the center of gravity 21 is located within the acting surface 22.
[0040] In a preferred embodiment, the vibration generator 12 includes unbalanced mass blocks 23 arranged on a rotating shaft 24. Figures 3 - 7 Describes such a vibration generator 12 with a reduced overall height. Here, four vertically oriented rotating shafts 24 are symmetrically arranged with respect to a vertically extending longitudinal symmetry plane 25 and a vertically extending transverse symmetry plane 26.
[0041] Viewed along the working direction 7, the two front rotating shafts 24 form a first group, wherein the left rotating shaft 24 is directly connected to a rotary drive 27 arranged above it. The right rotating shaft 24 is connected to the left rotating shaft 24 through a gear. The second group consists of two rear rotating shafts 24, which are also connected through a gear. The right rotating shaft 24 is connected to its own rotary drive 27.
[0042] The generally symmetric structure implemented by the intermediate member 18 enables the oscillation of the entire stabilizing device 11 to be uniform. Each individual unbalanced mass 23 generates a dynamic excitation force F. These excitation forces F are added together to produce a resultant dynamic impact force Fs. The individual excitation forces can be obtained according to the mass m and eccentricity e of each unbalanced mass 23, as well as the vibration frequency f or the angular velocity ωu relative to the center of rotation, using the following formula:
[0043]
[0044] The resultant dynamic impact force Fs determines the compaction energy introduced and greatly influences the lowering of the track 2. Two sets of rotary drives 27 are connected to a common control device 28. The control device 28 sets different drive modes. It is thus possible to drive the two sets at different rotational speeds and in different rotational directions, thereby generating different resultant dynamic impact forces Fs.
[0045] The clamping mechanism 29 for adjusting each squeezing roller 16 is arranged on the two side frames 19, 20 between the front edge roller 15 and the rear edge roller. In the example shown, each clamping mechanism 29 includes a double rocker arm and two hydraulic cylinders 30, which are symmetrically arranged relative to the laterally extending vertical axis of symmetry 26. The extension of the piston rod causes the squeezing roller 18 to press against the outer side of the rail 6.
[0046] Thereby, the stabilizing device 11 can be clamped without clearance on the track assembly 4, and the edge rollers 15 must also press against the rail 6 from the inside. It is preferably not to use a conventional lateral support shaft, because the elements of such a lateral support shaft must also be arranged or supported on the intermediate member 18. Instead, the axially adjustable edge roller 15 is only mounted on one of the side frames 20.
[0047] For example, as Figure 6 and Figure 7 shown, the two edge rollers 15 of the second side frame 20 are respectively rotatably and movably supported on the shaft 32. One end of each shaft 32 is directly supported on the side frame 20, and the other end is supported on the cantilever 33 of the side frame 20. The load is transmitted to the assigned rail 6 through a robust bearing.
[0048] For axial adjustment along the axis 31, a rocker arm 34 is arranged, which is hinged on the one hand to the side frame 20 and on the other hand to a servo drive 35 (such as a pneumatic cylinder or a hydraulic cylinder). The servo drive 35 is pivotally supported on the same side frame 20. Between the two joints 36, the rocker arm 34 is coupled in a form-fitting manner to a bushing 37 guided on the shaft 32. When the servo drive 35 extends, the rocker arm 34 moves the bushing 37 and the edge roller 15 supported on the bushing outwards. In this way, the edge roller 15 presses against the inside of the rail 6 without clearance.
[0049] InFigures 8 to 12 Another embodiment of the intermediate member 18 is shown. The housing 38 includes opposing connecting surfaces 39 for connecting the side frames 19, 20. As before, four vertically oriented rotating shafts 24 are supported in the bottom plate 40 and the cover plate 41 of the housing 38. In addition, an oil sump 42 is arranged within the housing. When the rotating shafts 24 are stationary, the oil sump 42 is filled with oil up to the filling level. The unbalanced mass blocks 23 are partially arranged below the filling level such that the unbalanced mass blocks are immersed in the oil sump.
[0050] During operation, the unbalanced mass blocks 23 convey the oil from the oil sump 42 upward and outward into the adjacent collecting sump 43. To achieve this conveying effect, paddle-shaped protrusions 44 with inclined extending surfaces are arranged in the lower regions of the respective unbalanced mass blocks 23. Figure 12 The corresponding paddle-shaped protrusions 44 are shown. The oil flows back to the oil sump 42 through the channels in the bottom plate 40 of the housing 38, thereby forming a circulating lubrication during operation.
[0051] To improve symmetry, two rotary drives 27 are arranged. The vertical axes 45 of the rotary drives are located in the longitudinally extending symmetry plane 25 and are arranged symmetrically with respect to the transversely extending symmetry plane 26. The drive shafts 46 of the respective rotary drives 27 are coupled to the two nearest rotating shafts 24 through gears. In addition, all the rotating shafts 24 are interconnected through gears, thereby achieving a definite position or phase of the unbalanced mass blocks 23 relative to each other through these transmission elements 47. Thus, there is no need for synchronous control of the two rotary drives 27.
Claims
1. A stabilizing device (11) for stabilizing a track (2), the stabilizing device having a vibration generator (12) and device rollers (15, 16) for transmitting vibrations (14) generated by means of the vibration generator (12) to a track assembly (4) of the track (2) to be stabilized, which consists of sleepers (5) and rails (6) fixed to the sleepers, characterized in that, The equipment rollers (15, 16) assigned to the left rail (6) of the track (2) are arranged on the first side frame (19), the equipment rollers (15, 16) assigned to the right rail (6) of the track (2) are arranged on the second side frame (20), and these two side frames (19, 20) are connected by a self-supporting intermediate member (18), which intermediate member includes the vibration generator (12).
2. The stabilizing device (11) according to claim 1, characterized in that, The intermediate member (18) is configured as the housing (38) of the vibration generator (12).
3. The stabilizing device (11) according to claim 1 or 2, characterized in that, The vibration generator (12) includes a hydraulic cylinder or a pneumatic cylinder.
4. The stabilizing device (11) according to claim 1 or 2, characterized in that, The vibration generator (12) includes a rotatable unbalanced mass (23).
5. The stabilizing device (11) according to claim 4, characterized in that, The unbalanced mass (23) is coupled to a rotary drive (27), in particular an electric one, arranged on the intermediate member (18).
6. The stabilizing device (11) according to claim 5, characterized in that, The unbalanced mass (23) is arranged on a plurality of parallel axes of rotation (24), and these axes of rotation (24) and / or the unbalanced masses (23) are coupled to one another.
7. The stabilizing device (11) according to claim 6, characterized in that, At least two axes of rotation (24) and / or unbalanced masses (23) are coupled to a transmission element (47).
8. The stabilizing device (11) according to claim 6 or 7, characterized in that, At least one unbalanced mass (23) is rotatably supported on each axis of rotation (24).
9. The stabilizing device (11) according to any one of claims 6 to 8, characterized in that, The unbalanced mass (23) is arranged on at least two vertically oriented axes of rotation (24).
10. The stabilizing device (11) according to claim 9, characterized in that, Four axes of rotation (24) are arranged symmetrically with respect to a longitudinally extending vertical symmetry plane (25) and a transversely extending vertical symmetry plane (26).
11. The stabilizing device (11) according to claim 10, characterized in that, Two rotary drives (27) are arranged symmetrically with respect to the transversely extending vertical symmetry plane (26) with their respective vertical axes (45), which vertical axes (45) are located in the longitudinally extending vertical symmetry plane (25).
12. The stabilizing device (11) according to any one of claims 4 to 11, characterized in that, The intermediate member (18) includes an oil sump (42) with a preset filling level, and the unbalanced mass (23) projects partially below the filling level.
13. The stabilizing device (11) according to claim 12, characterized in that, Each unbalanced mass (19) in the region below the filling level includes a blade-shaped projection (44), by means of which oil can be conveyed from the oil sump (42) into a lateral collecting trough (43) during operation.
14. The stabilizing device (11) according to any one of claims 1 to 13, characterized in that, In each side frame (19, 20), a front flanged roller (15) and a rear flanged roller (15) are respectively supported, and a clamping mechanism (29) is arranged between the two flanged rollers (15) for pressing the squeezing roller (16) against the corresponding rail (6).
15. The stabilizing device (11) according to claim 14, characterized in that, In at least one side frame (20), a flanged roller (15) is supported axially (31) adjustably, and the flanged roller (15) can be pressed against the assigned rail (6) by means of a servo drive (35) supported on the side frame (20).