MACHINE AND METHOD FOR STABILIZING A TRACK

Abstract

The invention relates to a machine for stabilising a track, having a machine frame supported on rail-based running gears and at least one height-adjustable stabilising unit which can be rolled on rails of the track by means of work unit rollers, comprising a vibration exciter with rotating unbalanced masses for generating an impact force acting dynamically in a track plane normal to a longitudinal direction of the track as well as a linear drive for generating a load acting on the track. It is provided that a main unbalanced mass and a secondary unbalanced mass produce different centrifugal forces at the same rotational speed depending on the direction of rotation, the two unbalanced masses being coupled in such a way that, during rotation in one direction of rotation, the unbalanced masses have a first phase shift in relation to one another and that, during rotation in the opposite direction of rotation, the unbalanced masses have a second phase shift relative to one another which differs from the first phase shift. Depending on the arrangement of the unbalanced masses, a changed phase shift changes both the direction and the strength of the impact force.

Claims

1. A machine for stabilising a track, with a machine frame supported on rail-based running gears and at least one height-adjustable stabilizing unit which can be rolled on rails of the track by means of work unit rollers, comprising a vibration exciter with rotating unbalanced masses for generating an impact force acting dynamically in a track plane normal to a longitudinal direction of the track, and a linear drive for generating a load acting on the track, wherein a main unbalanced mass and a secondary unbalanced mass produce different centrifugal forces at the same rotational speed depending on the direction of rotation, the two unbalanced masses being coupled in such a way that, during rotation in one direction of rotation, the unbalanced masses have a first phase shift with respect to one another, and that, when rotating in the opposite direction of rotation, the unbalanced masses have a second phase shift to each other which differs from the first phase shift.

2. The machine according to claim 1, wherein two unbalanced masses, each dependent on the direction of rotation, are mechanically coupled by means of positive engagement or constructive elements, so-called catches, thus forming a pair of unbalanced masses and one of two predetermined phase shifts results therefrom depending on the direction of rotation.

3. The machine according to claim 1, wherein at least two counter-rotating rotation shafts are coupled via gearwheels.

4. The machine according to claim 1, wherein the respective unbalanced mass is arranged on the stabilizing unit with an axis of rotation aligned in the longitudinal direction of the track.

5. The machine according to claim 1, wherein at least two pairs of unbalanced masses are assigned to a rotation shaft, the pairs of unbalanced masses each comprising a main unbalanced mass and a secondary unbalanced mass on the same axis of rotation.

6. The machine according to claim 1, wherein when at least two stabilising units are used, each stabilizing unit is assigned its separate drive.

7. The machine according to claim 6, wherein the respective drives are actuated by means of a shared control device.

8. The machine according to claim 1, wherein when at least two stabilizing units are used, a shared drive is assigned to the overall arrangement of the individual stabilizing units.

9. The machine according to claim 6, wherein the respective drive is designed as a hydraulic actuator.

10. The machine according to claim 6, wherein the respective drive is designed as an electric actuator.

11. A method for operating a machine according to claim 1, wherein the respective stabilizing unit is set down on the track via a linear drive, that a load is applied to it, and that the associated rotation shaft is driven by the assigned drive with a reversible direction of rotation.

12. The method according to claim 11, wherein an increase in the driving power of a drive of the stabilizing unit is controlled via a so-called soft start, wherein a predefined, increasing ramp is stored in a higher-level control system, which enables a targeted increase within a defined period of time.

13. The method according to claim 11, wherein a variable adjustment of the impact force in the range between possible impact force levels is enabled by changing the engine speed of the respective associated drive.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0027] In the following, the invention is explained by way of example with reference to the accompanying figures. The following figures show in schematic illustrations:

[0028] FIG. 1 Side view of a machine for stabilising a track

[0029] FIG. 2 Stabilising units, independent, with separate drives

[0030] FIG. 3 Stabilising units, coupled, with shared drive

[0031] FIG. 4 Detailed views of a stabilising unit/sectional views

[0032] FIG. 5 Unbalance adjustment depending on the direction of rotation via catches

[0033] FIG. 6 Unbalance adjustment via engine speed control in the intermediate range

DESCRIPTION OF THE EMBODIMENTS

[0034] FIG. 1 shows a simplified machine 1 for stabilising a track 3 resting on ballast 2, comprising a machine frame 6 supported on rails 5 by rail-based running gears 4. Two stabilising units 7 are arranged behind one another in the longitudinal direction of the track 8 between the two rail-based running gears 4 positioned at the ends. They are each connected to the machine frame 6 in a vertically adjustable manner by linear drives 9.

[0035] A measuring system 27 for recording the rail geometry is arranged on the machine frame 6. A control device 26 is set up for processing the data received from the measuring system 27 as well as for determining the adjustment parameters for operating and actuating the stabilising units 7, the linear drives 9, and the drives 13.

[0036] The embodiment shown in FIG. 1 shows independent, non-coupled stabilising units 7 with separate drives 13. The following figures (FIG. 2 and FIG. 3) show possible embodiments with coupled as well as non-coupled stabilising units 7.

[0037] FIG. 2 shows independent stabilising units with separate drives. By means of work unit rollers 10 that can roll on the rails 5, each stabilising unit 7 can be brought into positive engagement with the track 3 in order to cause it to vibrate at a desired vibration frequency. The work unit rollers 10 comprise, for each rail 5, two wheel flange rollers which roll on the inside of the rail 5 and a clamp roller. In operation, the clamp roller is pressed against the rail 5 from the outside by means of a clamp mechanism 11. A vertical static load is applied to the track 3 by the linear drives 9.

[0038] The drives 13 of the stabilising unit 7 are connected to a shared supply device 25. For electric drives 13, for example, this is a motor-generator unit supplied from an electrical storage unit. An overhead line can also be used to supply electric drives 13 if the machine 1 has pantographs and corresponding converters. If hydraulic drives 13 are used, it is useful if the supply device 25 is integrated into a hydraulic system of the machine 1.

[0039] FIG. 3 shows an alternative with coupled stabilising units and a shared drive. The basic set-up of the stabilising units 7 is identical to the embodiment shown in FIG. 2. The difference lies in the coupling of the arrangement in the longitudinal direction of the track 8 and the design of the drives 13. The stabilising units 7 are in drive connection via a connecting shaft 15. The drive 13 and the connecting shaft 14 are only singly realised.

[0040] In FIG. 4, one of the stabilising units 7 is shown in detail in sectional views. A vibration exciter 17 is arranged in a housing 16 and has two axes of rotation 21, each with one rotation shaft 18 with unbalanced masses arranged thereon. A main unbalanced mass 19 and a secondary unbalanced mass 20 form a pair of unbalanced masses. Each rotation shaft 18 is rotatably mounted on both sides in the housing 16 via roller bearings 22.

[0041] The unbalanced masses 19, 20 are coupled via so-called catches 24, herein designed as independent elements. They are congruently attached directly to the main unbalanced mass 19 as well as to the secondary unbalanced mass 20.

[0042] The counter-rotating rotation shafts 18 are mechanically coupled via gearwheels 23, wherein the power transmission to the rotation shaft 18 takes place positively via a feather key connection.

[0043] The secondary unbalanced masses 20 are freely rotatably mounted on the rotation shaft 18 via plain bearings, while the main unbalanced masses 19 are firmly connected to the rotation shaft 18 via a feather key connection.

[0044] The construction shown in FIG. 4 herein shows two pairs of unbalanced masses arranged axially on each of the rotation shafts 18, i.e. two main unbalanced masses 19 with two secondary unbalanced masses 20 each. The simplest possible technical solution is a set-up with only one rotation shaft 18 and only one pair of unbalanced masses arranged thereon.

[0045] FIG. 5 is a schematic illustration of the unbalance adjustment via catches 24, which depends on the direction of rotation. Illustrations A, B, C, D, E, F, G, H show the angular positions 0°, 90°, 180°, and 270° for both directions of rotation, wherein each illustration consists of an upper and a lower rotation shaft 18. The indicated direction of rotation always refers to the upper rotation shaft 18; the lower rotation shaft 18 rotates in the opposite direction of rotation due to mechanical coupling.

[0046] Illustrations A to D show clockwise operation (clockwise direction of rotation); illustrations E to H show anticlockwise operation (anticlockwise direction of rotation).

[0047] The set-up in illustration A (angular position 0°) comprises the upper, clockwise rotation shaft 18 with a pair of unbalanced masses arranged thereon. The main unbalanced mass 19 with associated catches 24 (finely hatched) produces a centrifugal force F1 from the pivot in the vertical direction. The secondary unbalanced mass 20 with associated catches 24 (roughly hatched) also produces a centrifugal force F3 from the pivot in the vertical direction. The sum of the two centrifugal forces F1 and F3 results in the total centrifugal force Fges1. At the lower rotation shaft 18 (anticlockwise), the total centrifugal force Fges1 acts as the sum of F2 and F4 with the same magnitude in the opposite direction. The forces thus cancel each other out, and, when reduced, act on the entire stabilising unit 7. No force acts in the vertical direction.

[0048] In illustration B (angular position 90°), the total centrifugal force Fges1 acts from the pivot in the horizontal direction. The force situation is the same at the lower rotation shaft 18 (anticlockwise). Here, the total centrifugal force Fges1 acts as the sum of F2 and F4 with the same magnitude in the same direction. The forces add up and with 2*Fges1 result in the maximum possible impact force in the horizontal direction on the track 3.

[0049] The resulting forces in illustrations C (angular position 180°) and D (angular position 270°) behave analogously to illustrations A and B; here, the total centrifugal forces Fges1 are also cancelled out (C) and doubled (D).

[0050] The set-up in illustration E (angular position 0°) now shows an anticlockwise rotation shaft 18 with a pair of unbalanced masses arranged thereon. The changed direction of rotation results in a different angular position of the two unbalanced masses 19, 20 in relation to each other. The main unbalanced mass 19 with associated catches 24 (finely hatched) produces a centrifugal force F1 from the pivot upwards in the vertical direction. The secondary unbalanced mass 20 with associated catches 24 (roughly hatched) produces a centrifugal force F3 from the pivot downwards in the vertical direction. The sum of the two centrifugal forces F1 and F3 results in the total centrifugal force Fges2. At the lower rotation shaft 18 (anticlockwise), the total centrifugal force Fges2 acts as the sum of F2 and F4 with the same magnitude in the opposite direction. The forces thus cancel each other out, and, when reduced, act on the entire stabilising unit 7. No force acts in the vertical direction.

[0051] In illustration F (angular position 90°), the total centrifugal force Fges2 acts from the pivot in the horizontal direction. The force situation is the same at the lower rotation shaft 18 (anticlockwise). Here, the total centrifugal force Fges2 acts as the sum of F2 and F4 with the same magnitude in the same direction. The forces add up and with 2*Fges2 result in the minimum possible impact force in the horizontal direction on the track 3.

[0052] The resulting forces in illustrations G (angular position 180°) and H (angular position 270°) behave analogously to illustrations E and F; here, the total centrifugal forces Fges2 are also cancelled out (G) and doubled (H).

[0053] FIG. 6 shows in a diagram how the impact force can be variably adjusted through low engine speed control. If two independently driven stabilising units 7 are used on a machine 1, up to eight impact forces with different magnitudes can be actuated; this results from 3.sup.2−1=8.

[0054] The range between the impact force levels can now be compensated by changing the engine speed of the respective associated drive 13 within a very narrow frequency band. When all intermediate areas of the impact force levels S1-S7 are passed through completely (thick lines), a so-called frequency control funnel is created (dotted lines). The ordinate shows the impact force F in % above the abscissa with the frequency f in Hz.